OUTDOOR UNIT AND HEATING AND VENTILATION APPARATUS

Description

This application is a continuation of International Patent Application No. PCT/CN2023/093096, filed on May 9, 2023, the entire contents of which are incorporated herein by reference.

FIELD

The present disclosure relates to the field of heating and ventilation apparatus technologies, and more particularly, to an outdoor unit and a heating and ventilation apparatus.

BACKGROUND

A compressor in an outdoor unit is a main noise source of an entire unit. To meet the low noise requirement of an air conditioner, the compressor is usually enclosed in a soundproof hood to prevent the compressor from radiating noise outward. In the related art, the soundproof hood is independently manufactured, resulting in high costs of the entire unit. In addition, the soundproof hood requires a large mounting space, reducing a space utilization rate of the entire unit.

SUMMARY

Some embodiments of the present disclosure aims to solve at least one of the technical problems in the related art. To this end, an objective of the present disclosure is to provide an outdoor unit. By allowing at least part of a first partition plate to form part of a soundproof hood, overall costs of the soundproof hood can be saved, and mounting space of the soundproof hood can be reduced, making structure of an entire unit more compact and improving an overall space utilization rate. In addition, at least one of the first hood plate and the second hood plate is independent of the outdoor unit casing, which can make the soundproof hood independent of the outdoor unit casing, preventing noise in the soundproof hood from being directly transmitted to an outdoor unit casing. In this way, an overall soundproof and noise reduction effect of a compressor assembly can be better ensured.

The present disclosure further provides a heating and ventilation apparatus including the above-described outdoor unit.

The outdoor unit of the heating and ventilation apparatus according to some embodiments of the present disclosure includes: an outdoor unit casing having a fan chamber and a compressor chamber arranged in a left-right direction, a first partition plate being disposed between the fan chamber and the compressor chamber; an outdoor heat exchanger and an outdoor fan that are disposed in the fan chamber; and a compressor assembly disposed in the compressor chamber and including a compressor, the compressor assembly being externally covered by a soundproof hood, at least part of the first partition plate forming a part of the soundproof hood, and the soundproof hood including a first hood plate and a second hood plate that are opposite to and spaced apart from each other in a front-rear direction, both the first hood plate and the second hood plate being connected to the first partition plate, and at least one of the first hood plate and the second hood plate being independent of the outdoor unit casing.

With the outdoor unit according to some embodiments of the present disclosure, by allowing at least part of the first partition plate to form part of the soundproof hood, overall costs of the soundproof hood can be saved, and mounting space of the soundproof hood can be reduced, making structure of an entire unit more compact and improving an overall space utilization rate. In addition, at least one of the first hood plate and the second hood plate is independent of the outdoor unit casing, which can make the soundproof hood independent of the outdoor unit casing, preventing noise in the soundproof hood from being directly transmitted to an outdoor unit casing. In this way, an overall soundproof and noise reduction effect of a compressor assembly can be better ensured.

With the outdoor unit according to some embodiments of the present disclosure, a soundproof gap is formed between the outdoor unit casing and at least one of the first hood plate and the second hood plate.

According to some embodiments of the present disclosure, the outdoor unit further includes: a water-circuit heat-exchange assembly including a water-circuit heat exchanger. The water-circuit heat exchanger has a water flow passage and a refrigerant flow passage that exchange heat with each other. The outdoor unit casing has internally a water-circuit chamber. The water-circuit heat-exchange assembly is disposed in the water-circuit chamber. A second partition plate is disposed between the water-circuit chamber and the compressor assembly. At least part of the second partition plate forms part of the soundproof hood.

According to some embodiments of the present disclosure, the first partition plate is opposite to and spaced apart from the second partition plate in the left-right direction. The soundproof hood includes the first hood plate, the second hood plate, and a top cover. The first hood plate is opposite to and spaced apart from the second hood plate in the front-rear direction. Left and right ends of the first hood plate are connected to the first partition plate and the second partition plate, respectively. Left and right ends of the second hood plate are connected to the first partition plate and the second partition plate, respectively. The top cover covers a top of the first hood plate and a top of the second hood plate.

According to some embodiments of the present disclosure, each of the first hood plate, the second hood plate, and the top cover is independently formed; or at least two of the first hood plate, the second hood plate, and the top cover are integrally formed.

According to some embodiments of the present disclosure, the outdoor unit includes: a first electrical control box component configured to at least control the outdoor fan and the compressor. The first electrical control box component is disposed at an upper part of the first partition plate. The part of the first partition plate forming the soundproof hood is a soundproof portion. The soundproof hood includes a third hood plate and a top cover. The third hood plate has a lower end connected to an upper end of the soundproof portion and an upper end connected to the top cover. An avoidance space for avoiding the first electrical control box component is defined between the third hood plate and the first partition plate.

According to some embodiments of the present disclosure, the third hood plate includes an avoidance portion and an extension portion arranged at an angle. The avoidance portion has an end connected to the upper end of the soundproof portion and the other end extending towards the compressor chamber. The extension portion has a lower end connected to the other end of the avoidance portion and an upper end extending upwards and connected to the top cover.

According to some embodiments of the present disclosure, the first electrical control box component has a wire outlet formed at a bottom of the first electrical control box component. An electrical control wire harness of the first electrical control box component is led out through the wire outlet. The electrical control wire harness is partially received in the avoidance space.

According to some embodiments of the present disclosure, the electrical control wire harness includes a first electrical control wire harness and a second electrical control wire harness. The first electrical control wire harness is adapted to run upwards along the extension portion and run along an upper surface of the top cover, extend through the top cover downward, and be electrically connected to the compressor.

According to some embodiments of the present disclosure, the electrical control wire harness includes a second electrical control wire harness adapted to run rearward along the avoidance portion and run downward along the soundproof hood, extend into the fan chamber through the first partition plate, and be electrically connected to the outdoor fan.

According to some embodiments of the present disclosure, the first electrical control box component is provided with a radiator at an end of the first electrical control box component facing towards the fan chamber. The outdoor unit includes a second air guide hood located at a bottom of the radiator. The first partition plate includes a first sub-partition plate and a second sub-partition plate arranged in the left-right direction. The second sub-partition plate is located at a side of the first sub-partition plate adjacent to the compressor chamber and includes a partition plate body forming the soundproof portion. A second air guide chamber is defined by the second sub-partition plate, the first sub-partition plate, the second air guide hood, and the radiator. The second sub-partition plate has a second air guide opening in communication with the second air guide chamber. An airflow in the compressor chamber is adapted to flow into the second air guide chamber through the second air guide opening and flow upward through the radiator.

According to some embodiments of the present disclosure, a bottom of the soundproof hood is connected to a base. A vibration-damping pad is disposed between the bottom of the soundproof hood and the base.

According to some embodiments of the present disclosure, the soundproof hood includes a top cover having a pipeline outlet. A pipeline of the compressor assembly is adapted to be led out from the pipeline outlet. The top cover includes a first cover body and a second cover body that are detachably connected in a horizontal direction, the pipeline outlet being defined between the first cover body and the second cover body; or the top cover is formed from one single piece.

According to some embodiments of the present disclosure, the outdoor unit further includes: a water-circuit heat-exchange assembly including a water-circuit heat exchanger. The water-circuit heat exchanger has a water flow passage and a refrigerant flow passage that exchange heat with each other. The water-circuit heat exchanger is located outside the soundproof hood and fixed to the soundproof hood.

According to some embodiments of the present disclosure, the compressor assembly further includes a liquid reservoir fixed to a base of the outdoor unit.

According to some embodiments of the present disclosure, the soundproof hood is at least partially made of a composite panel; and/or the outdoor unit casing is at least partially made of a composite panel. The composite plate includes metal layers and a first damping layer stacked together. The first damping layer is located between two adjacent metal layers.

According to some embodiments of the present disclosure, the first damping layer has a thickness ranging from 0.002 mm to 3 mm. The metal layer has a thickness ranging from 0.1 mm to 5 mm.

According to some embodiments of the present disclosure, at least one of an inner wall of the soundproof hood and an outer circumferential wall of the compressor is provided with a soundproof cotton layer; and/or at least part of an inner wall of the outdoor unit casing is provided with the soundproof cotton layer.

According to some embodiments of the present disclosure, the soundproof cotton layer includes a sound absorption layer, a second damping layer, and a soundproof layer that are stacked in sequence. The sound absorption layer is a porous material layer. The second damping layer is a rubber layer. The soundproof layer is a plastic layer or a rubber layer.

According to some embodiments of the present disclosure, the sound absorption layer has a thickness ranging from 5 mm to 15 mm. The second damping layer has a thickness ranging from 2 mm to 6 mm. The soundproof layer has a thickness ranging from 1 mm to 3 mm.

According to some embodiments of the present disclosure, an outer circumferential wall of the compressor is covered with a soundproof cotton layer. A support structure is disposed between the soundproof cotton layer and the outer circumferential wall of the compressor to define an air layer between the soundproof cotton layer and the outer circumferential wall of the compressor. The support structure is an elastic support structure.

According to some embodiments of the present disclosure, a spacing between the soundproof cotton layer and the outer circumferential wall of the compressor ranges from 5 mm to 20 mm.

According to some embodiments of the present disclosure, damping particles are filled between the soundproof hood and the compressor assembly. An equivalent diameter of each of the damping particles is smaller than 3 mm.

According to some embodiments of the present disclosure, a vibration damping structure is disposed between the compressor and a base of the outdoor unit casing. The vibration damping structure includes a floating plate located above the base, and a vibration damping assembly. The vibration damping assembly includes at least one of a first vibration damping member and a second vibration damping member. The first vibration damping member is disposed between the compressor and the floating plate, and the second vibration damping member is disposed between the floating plate and the base.

According to some embodiments of the present disclosure, the compressor assembly further includes a liquid reservoir connected to the compressor. A projection of the compressor in a horizontal plane is a first projection, a projection of the floating plate in the horizontal plane is a second projection, and a projection of the liquid reservoir in the horizontal plane is a third projection. The first projection is located within the second projection, and the third projection is at least partially located within the second projection.

According to some embodiments of the present disclosure, the floating plate has an avoidance notch. The avoidance notch is configured to at least escape pipes.

According to some embodiments of the present disclosure, the compressor assembly further includes a liquid reservoir connected to the compressor. The floating plate has a plurality of first mounting holes for mounting of the compressor and a plurality of second mounting holes for mounting of the floating plate. Centers of the plurality of first mounting holes are located at a first reference circle, and centers of the plurality of second mounting holes are located at a second reference circle.

According to some embodiments of the present disclosure, a projection of a center of the second reference circle in a reference plane is spaced apart from a projection of a center of the first reference circle in the reference plane. The reference plane is parallel to a plane where an outer peripheral contour line of the base is located. The center of the second reference circle is located at a side of the center of the first reference circle adjacent to the liquid reservoir.

According to some embodiments of the present disclosure, the floating plate has a plurality of second mounting holes for mounting of the floating plate. Centers of the plurality of second mounting holes are located at a second reference circle. Projections of a center of mass of the compressor assembly and a center of the second reference circle in a reference plane are a first projection point and a second projection point, respectively, a spacing between the first projection point and the second projection point ranging from 0 mm to 5 mm; and/or projections of a center of mass of the floating plate and the center of the second reference circle in the reference plane are a third projection point and the second projection point, respectively, a spacing between the third projection point and the second projection point ranging from 0 mm to 5 mm. The reference plane is parallel to a plane where an outer peripheral contour line of the base is located.

According to some embodiments of the present disclosure, projections of a center of mass of the compressor assembly and a center of mass of the floating plate in a reference plane are a first projection point and a third projection point, respectively. A spacing between the first projection point and the third projection point ranges from 0 mm to 5 mm. The reference plane is parallel to a plane where an outer peripheral contour line of the base is located.

According to some embodiments of the present disclosure, a mass ratio of the floating plate to the compressor ranges from 0.1 to 0.6; or a ratio of static stiffness of the first vibration damping member to static stiffness of the second vibration damping member ranges from 0.6 to 1.5; or a damping ratio of each of the first vibration damping member and the second vibration damping member ranges from 0.01 to 0.7.

According to some embodiments of the present disclosure, static displacement of each of the first vibration damping member and the second vibration damping member is smaller than 2.5 mm. The static displacement is a maximum deformation amount of the corresponding vibration damping member in an up-down direction.

According to some embodiments of the present disclosure, the soundproof hood is supported on and connected to the floating plate.

According to some embodiments of the present disclosure, the damping particles are filled in a space defined by the soundproof hood and the floating plate. A second sealing structure is disposed between the soundproof hood and the floating plate to seal an assembly gap between the soundproof hood and the floating plate.

According to some embodiments of the present disclosure, the outdoor unit further includes: a water-circuit heat-exchange assembly including a water-circuit heat exchanger. The water-circuit heat exchanger has a water flow passage and a refrigerant flow passage that exchange heat with each other. The water-circuit heat exchanger is directly or indirectly supported on the floating plate.

According to some embodiments of the present disclosure, the soundproof hood is supported on and connected to the floating plate. The water-circuit heat exchanger is located outside the soundproof hood and fixed to the soundproof hood.

According to some embodiments of the present disclosure, the outdoor unit further includes an auxiliary fixing assembly. The auxiliary fixing assembly is detachably connected to the outdoor unit casing and the floating plate to fix the floating plate relative to the outdoor unit casing; and/or the auxiliary fixing assembly is detachably connected to the compressor and the floating plate to fix the compressor relative to the floating plate.

According to some embodiments of the present disclosure, the auxiliary fixing assembly includes at least one of a bolt and a fixing support. The bolt is adapted to be threadedly connected to the floating plate and the base of the outdoor unit casing. The fixing support includes a fixing plate and a connection plate that are connected to each other. The connection plate is detachably connected to the base of the outdoor unit casing. The fixing plate is directly or indirectly pressed against the floating plate to compress the floating plate.

According to some embodiments of the present disclosure, an air return pipe connected to the compressor assembly includes a plurality of U-shaped segments connected sequentially. The compressor assembly includes the compressor and a liquid reservoir. A third reference circle is defined with a center at an air discharge port of the compressor and a radius of R1. R1 is greater than a radius of the compressor with a difference ranging from 20 mm to 225 mm. A fourth reference circle is defined with a center at an air return port of the liquid reservoir and a radius of R2. R2 is greater than a radius of the liquid reservoir with a difference ranging from 20 mm to 200 mm. Projections of the plurality of U-shaped segments of the air return pipe in a horizontal plane are at least partially located in a region where the third reference circle overlaps the fourth reference circle.

According to some embodiments of the present disclosure, an air return pipe connected to the compressor assembly includes a plurality of U-shaped segments connected sequentially and a vertical segment, the vertical segment being connected between two adjacent U-shaped segments of the plurality of U-shaped segments, and at least part of the vertical segment being a corrugated pipe or a rubber hose; or at least part of the air return pipe connected to the compressor assembly is a metal pipe, at least part of the metal pipe being sleeved with a vibration-damping rubber sleeve or provided with a counterweight block.

The heating and ventilation apparatus according to some embodiments of the present disclosure includes the outdoor unit according to the above-described embodiments of the present disclosure.

With the heating and ventilation apparatus according to the embodiments of the present disclosure, through setting the above-described outdoor unit, by allowing at least part of the first partition plate to form part of the soundproof hood, overall costs of the soundproof hood can be saved, and mounting space of the soundproof hood can be reduced, making structure of an entire unit more compact and improving an overall space utilization rate. In addition, at least one of the first hood plate and the second hood plate is independent of the outdoor unit casing, which can make the soundproof hood independent of the outdoor unit casing, preventing noise in the soundproof hood from being directly transmitted to an outdoor unit casing. In this way, an overall soundproof and noise reduction effect of a compressor assembly can be better ensured.

Additional aspects and advantages of the present disclosure will be provided at least in part in the following description, or will become apparent at least in part from the following description, or can be learned from practicing of the present disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and/or additional aspects and advantages of the present disclosure will become more apparent and more understandable from the following description of embodiments taken in conjunction with the accompanying drawings.

FIG. 1 is a schematic view of an outdoor unit of a heating and ventilation apparatus according to some embodiments of the present disclosure.

FIG. 2 is a partial schematic view of the outdoor unit in FIG. 1.

FIG. 3 is a schematic assembly view of a compressor assembly and a base in FIG. 2.

FIG. 4 is a top view of the compressor assembly and the base in FIG. 3.

FIG. 5 is a top view of a floating plate in FIG. 4.

FIG. 6 is a schematic assembly view of an auxiliary fixing assembly and a compressor assembly of an outdoor unit according to some embodiments of the present disclosure.

FIG. 7 is a schematic mounting view of a water-circuit heat exchanger of an outdoor unit according to some embodiments of the present disclosure, in which the water-circuit heat exchanger is connected to a floating plate through a mounting support.

FIG. 8 is a schematic mounting view of a water-circuit heat exchanger of an outdoor unit according to some other embodiments of the present disclosure, in which the water-circuit heat exchanger is disposed outside a soundproof hood.

FIG. 9 is a partial schematic view of a compressor assembly of an outdoor unit according to some other embodiments of the present disclosure, in which a liquid reservoir is supported on a base.

FIG. 10 is a schematic assembly view of a top cover of a soundproof hood and a pipeline of a compressor assembly according to some embodiments of the present disclosure, in which the top cover includes a first cover body and a second cover body.

FIG. 11 is an exploded view of the top cover in FIG. 10.

FIG. 12 is a schematic assembly view of a soundproof hood and a base of an outdoor unit according to some embodiments of the present disclosure.

FIG. 13 is a partial cross-sectional view of the soundproof hood in FIG. 12.

FIG. 14 is an exploded view of the soundproof hood in FIG. 10, in which the top cover is formed from one single piece.

FIG. 15 is a schematic assembly view of a composite panel and a soundproof cotton layer in FIG. 14.

FIG. 16 is a partial cross-sectional view of the composite panel in FIG. 15.

FIG. 17 is a partial cross-sectional view of the soundproof cotton layer in FIG. 15.

FIG. 18 is a schematic assembly view of a compressor assembly and a soundproof cotton layer in FIG. 2.

FIG. 19 is a schematic view of an unfolded soundproof cotton layer in FIG. 18.

FIG. 20 is a schematic assembly view of a soundproof hood and a compressor assembly of an outdoor unit according to some other embodiments of the present disclosure, in which damping particles are filled between the soundproof hood and the compressor assembly.

FIG. 21 is a schematic view of a compressor assembly in FIG. 2.

FIG. 22 is a schematic view of a compressor assembly of an outdoor unit according to some other embodiments of the present disclosure, in which part of an air return pipe is a rubber hose.

FIG. 23 is a schematic view of the air return pipe in FIG. 22.

Reference numerals of the accompanying drawings:

• • 100, outdoor unit; 101, outdoor air inlet; 102, outdoor air outlet;
  • 10, outdoor unit casing; 11, fan chamber; 111, outdoor fan; 112, outdoor heat exchanger; 113, first partition plate; 1131, first air guide hood; 1132, first air guide chamber; 1134, second air guide hood; 1135, second air guide chamber; 1136, first sub-partition plate; 1137, second sub-partition plate; 1137a, partition plate body; 1137b, partition plate flange; 1137c, soundproof portion; 1139, second air guide opening; 12, compressor chamber; 121, second partition plate; 13, water-circuit chamber; 14, vibration damping structure; 141, floating plate; 1411, avoidance notch; 142, first vibration damping member; 143, second vibration damping member; 144, first mounting hole; 1441, first fastener; 145, second first mounting hole; 1451, second fastener; 15, composite panel; 151, metal layer; 152; first damping layer; 16, base;
  • 20, compressor assembly; 21, compressor; 211, liquid receiving pipe; 212, air discharge port; 22, liquid reservoir; 221, air return pipe; 2211, rubber hose; 222, air return port; 23, soundproof cotton layer; 231, sound absorption layer; 232, second damping layer; 233, soundproof layer; 24, support structure; 241, support ring; 242, support bar; 243, support block; 25, soundproof hood; 251, top cover; 2511, first cover body; 2512, second cover body; 2513, pipeline outlet; 2514, first sealing structure; 2523, first hood plate; 2524, second hood plate; 2525, third hood plate; 2526, avoidance space; 253, damping particle; 254, soundproof chamber; 26, mounting support; 27, four-way valve;
  • 30, first electrical control box component;
  • 40, water-circuit heat-exchange assembly; 51, water-circuit heat exchanger; 52, electric heater; 53, water pump;
  • 50, second electrical control box component;
  • 60, auxiliary fixing assembly; 7, bolt; 8, fixing support; 81, fixing plate; 811, groove; 82, connection plate.

DETAILED DESCRIPTION

Embodiments of the present disclosure will be described in detail below with reference to examples thereof as illustrated in the accompanying drawings, throughout which same or similar elements, or elements having same or similar functions, are denoted by same or similar reference numerals. The embodiments described below with reference to the drawings are illustrative only, and are intended to explain, rather than limit, the present disclosure.

An outdoor unit 100 according to an embodiment of the present disclosure is described in detail below with reference to FIG. 1 to FIG. 23. A heating and ventilation apparatus may be an air conditioning system, a heat pump system, etc.

As illustrated in FIG. 12 to FIG. 14, the outdoor unit 100 of the heating and ventilation apparatus according to some embodiments of the present disclosure includes an outdoor unit casing 10, an outdoor heat exchanger 112, an outdoor fan 111, and a compressor assembly 20.

The outdoor unit casing 10 has a fan chamber 11 and a compressor chamber 12 arranged in a left-right direction. A first partition plate 113 is disposed between the fan chamber 11 and the compressor chamber 12. The first partition plate 113 can separate the fan chamber 11 from the compressor chamber 12 in the outdoor unit casing 10, which can make a layout of an entire unit more reasonable, facilitating maintenance and replacement of different components.

The outdoor unit casing 10 has an outdoor air inlet 101 and an outdoor air outlet 102 that are both formed at the outdoor unit casing at a circumference of the fan chamber 11. For example, the outdoor air outlet 102 is formed at a front side wall of the outdoor unit casing 10, and the outdoor air inlet 101 is formed at a rear side wall and a left side wall of the outdoor unit casing 10.

It should be noted that, an air outlet side of the outdoor unit 100 is defined as a front side.

The outdoor heat exchanger 112 and the outdoor fan 111 are disposed in the fan chamber 11. The outdoor fan 111 is configured to drive outdoor air to enter the outdoor unit casing 10 through the outdoor air inlet 101 and exchange heat with the outdoor heat exchanger 112. The heat-exchanged air is discharged from the outdoor air outlet 102.

The compressor assembly 20 is disposed in the compressor chamber 12 and includes a compressor 21. The compressor assembly 20 can play a role in compressing and driving a refrigerant in a refrigerant circuit.

According to some embodiments of the present disclosure, as illustrated in FIG. 12 to FIG. 14, the compressor assembly 20 is externally covered by a soundproof hood 25. The compressor 21 radiates noise to the outside during operation. The soundproof hood 25 is disposed outside the compressor assembly 20, which can reduce the noise radiated to the outside by the compressor assembly 20 and provide a soundproof effect on the compressor assembly 20. For example, while covering the outside of the compressor assembly 20, the soundproof hood 25 can also cover an outside of a refrigerant pipeline related component (such as a four-way valve, an air discharge pipe, an air return pipe, a valve body, and a sensor assembly).

In some embodiments, at least part of the first partition plate 113 forms part of the soundproof hood 25. For example, part of the first partition plate 113 forms part of the soundproof hood 25, or the entire first partition plate 113 forms part of the soundproof hood 25. Such an arrangement can reduce space occupied by the soundproof hood 25 within the compressor chamber 12, make a structure in the compressor chamber 12 more compact, and improve a space utilization rate of an entire unit. Moreover, costs of the entire soundproof hood 25 can also be saved.

With the outdoor unit 100 according to some embodiments of the present disclosure, by allowing at least part of the first partition plate 113 to form part of the soundproof hood 25, the costs of the entire soundproof hood 25 can be saved, and mounting space of the soundproof hood 25 can be reduced, making a structure of the entire unit more compact and improving a space utilization rate of the entire outdoor unit 100.

In some embodiments, the soundproof hood 25 includes a first hood plate 2523 and a second hood plate 2524 that are opposite to and spaced apart from each other in a front-rear direction, both the first hood plate 2523 and the second hood plate 2524 are connected to the first partition plate 113, and at least one of the first hood plate 2523 and the second hood plate 2524 is independent of the outdoor unit casing 10. For example, the first hood plate 2523 is independent of the outdoor unit casing 10, or the second hood plate 2524 is independent of the outdoor unit casing 10, or both the first hood plate 2523 and the second hood plate 2524 are independent of the outdoor unit casing 10. Such an arrangement can make the soundproof hood 25 independent of the outdoor unit casing 10, which facilitates assembly of the entire soundproof hood 25, and can prevent the noise in the soundproof hood 25 from being directly transmitted to the outdoor unit casing 10. In this way, a soundproof and noise reduction effect of the entire soundproof hood 25 on the compressor assembly 20 can be better ensured.

For example, the first hood plate 2523 can be located at a front side of the second hood plate 2524, and both the first hood plate 2523 and the second hood plate 2524 are flat-plate shaped. Each of the first hood plate 2523 and the second hood plate 2524 can be connected to the first partition plate 113 through a fastener, which is structurally simple and provides a reliable connection, and facilitates mounting and disassembly of the entire soundproof hood, facilitating assembly of the entire unit.

With the outdoor unit 100 according to some embodiments of the present disclosure, by arranging at least one of the first hood plate 2523 and the second hood plate 2524 to be independent of the outdoor unit casing 10, the soundproof hood 25 can be made independent of the outdoor unit casing 10, preventing the noise in the soundproof hood 25 from being directly transmitted to the outdoor unit casing 10. In this way, the soundproof and noise reduction effect of the entire soundproof hood 25 on the compressor assembly 20 can be better ensured.

According to some embodiments of the present disclosure, as illustrated in FIG. 12 to FIG. 14, a soundproof gap is formed between the outdoor unit casing 10 and at least one of the first hood plate 2523 and the second hood plate 2524. For example, the soundproof gap is formed between the first hood plate 2523 and the outdoor unit casing 10, or the soundproof gap is formed between the second hood plate 2524 and the outdoor unit casing 10, or the soundproof gap is formed between each of the first hood plate 2523 and the second hood plate 2524 and the outdoor unit casing 10. The soundproof gap can prevent the noise in the soundproof hood from being directly transmitted to the outdoor unit casing through the first hood plate 2523 or the second hood plate 2524, ensuring the soundproof and noise reduction effect of the entire soundproof hood 25 on the compressor assembly 20. Moreover, the air in the soundproof gap can also attenuate or absorb part of energy of the noise, improving the overall soundproof and noise reduction effect of the entire soundproof hood 25 on the compressor assembly 20.

According to some embodiments of the present disclosure, as illustrated in FIG. 2 and FIG. 12 to FIG. 14, the outdoor unit 100 further includes a water-circuit heat-exchange assembly 40. The water-circuit heat-exchange assembly can realize temperature regulation of a water circuit. The water-circuit heat-exchange assembly 40 includes a water-circuit heat exchanger 51. The water-circuit heat exchanger 51 has a water flow passage and a refrigerant flow passage that exchange heat with each other. A refrigerant in the refrigerant flow passage can exchange heat with water flow in the water flow passage, allowing the water-circuit heat exchanger 51 to provide heating or cooling for the water flow. The water-circuit heat-exchange assembly 40 can regulate a temperature of passing water flow, allowing the entire unit to provide heating or cooling for the water flow. The water flow flowing out of the water-circuit heat exchanger 51 can be transported to the room to regulate a temperature of indoor domestic water or an indoor temperature.

The outdoor unit casing 10 has internally a water-circuit chamber 13, and the water-circuit heat-exchange assembly 40 is disposed in the water-circuit chamber 13. A second partition plate 121 is disposed between the water-circuit chamber 13 and the compressor chamber 12. Part of space in the outdoor unit casing 10 is divided into the water-circuit chamber 13 and the compressor chamber 12 by the second partition plate 121, which can make a layout of the entire unit more reasonable, facilitating maintenance and replacement of different components.

At least part of the second partition plate 121 forms part of the soundproof hood 25. For example, part of the second partition plate 121 forms part of the soundproof hood 25 or the entire second partition plate 121 forms part of the soundproof hood 25. Such an arrangement can reduce the space occupied by the soundproof hood 25 within the compressor chamber 12, make the structure in the compressor chamber 12 more compact, and improve the space utilization rate of the entire unit. Moreover, the costs of the entire soundproof hood 25 can also be saved.

Both the second partition plate 121 and the first partition plate 113 form part of the soundproof hood 25, which can reduce the mounting space occupied by the soundproof hood 25 less, make the structure of the entire unit more compact, and better improve the space utilization rate of the entire unit. Moreover, the costs of the entire soundproof hood 25 can be better saved.

According to some embodiments of the present disclosure, as illustrated in FIG. 2 and FIG. 12 to FIG. 14, the first partition plate 113 is opposite to the second partition plate 121 in the left-right direction, and the first partition plate 113 is spaced apart from the second partition plate 121. The first partition plate 113 and the second partition plate 121 can sequentially divide the outdoor unit casing 10 into the fan chamber 11, the compressor chamber 12, and the water-circuit chamber 13 in the left-right direction, making the layout of the entire unit more reasonable and facilitating the maintenance and replacement of different components.

The first partition plate 113 is located at a left side of the compressor chamber 12, and the second partition plate 121 is located at a right side of the compressor chamber 12. The first partition plate 113 and the second partition plate 121 can form a part of the soundproof hood 25 at a left side of the compressor and a part of the soundproof hood 25 at a right side of the compressor, respectively, making the entire structure more compact and improving the space utilization rate of the entire unit.

The soundproof hood 25 includes the first hood plate 2523, the second hood plate 2524, and a top cover 251. The first hood plate 2523 is opposite to and spaced apart from the second hood plate 2524 in the front-rear direction. Left and right ends of the first hood plate 2523 are connected to the first partition plate 113 and the second partition plate 121, respectively, and left and right ends of the second hood plate 2524 are connected to the first partition plate 113 and the second partition plate 121, respectively. The top cover 251 covers a top of the first hood plate 2523 and a top of the second hood plate 2524. Such an arrangement can enable the first hood plate 2523, the second hood plate 2524, the top cover 251, part of the first partition plate 113, and part of the second partition plate 121 to jointly form the entire soundproof hood. Compared with independent manufacturing of the soundproof hood as a whole, this design can reduce the mounting space occupied by the soundproof hood 25, make the structure of the entire unit more compact, and better improve the space utilization rate of the entire unit. Moreover, the costs of the entire soundproof hood 25 can be better saved.

For example, the first hood plate 2523 may be located in the front side of the second hood plate 2524, and both the first hood plate 2523 and the second hood plate 2524 are flat-plate shaped. The first hood plate 2523 and the second hood plate 2524 can be connected to the first partition plate 113, the second partition plate 121, and the top cover 251 through fasteners, which is structurally simple and provides a reliable connection, and is convenient for the mounting and disassembly of the entire soundproof hood, facilitating the assembly of the entire unit. The top cover 251 may be provided with flanges at peripheral sides of the top cover 251, and the fasteners can penetrate the flanges, in such a manner that fixation between the top cover 251 and each of the first hood plate 2523, the second hood plate 2524, the first partition plate 113, and the second partition plate 121 can be easily realized.

According to some embodiments of the present disclosure, as illustrated in FIG. 12 to FIG. 14, each of the first hood plate 2523, the second hood plate 2524, and the top cover 251 is independently formed, which can facilitate assembly and transportation of the entire soundproof hood 25, and improve strength and rigidity of the entire soundproof hood 25. Also, processing technology of the entire soundproof hood 25 can be simplified, reducing processing difficulty of the entire soundproof hood 25.

According to some embodiments of the present disclosure, as illustrated in FIG. 12 to FIG. 14, at least two of the first hood plate 2523, the second hood plate 2524, and the top cover 251 are integrally formed. For example, the first hood plate 2523 and the second hood plate 2524 are integrally formed, or the first hood plate 2523 and the top cover 251 are integrally formed, or the second hood plate 2524 and the top cover 251 are integrally formed, or the first hood plate 2523, the second hood plate 2524, and the top cover 251 are integrally formed.

Such an arrangement can enhance connection strength of various parts of the soundproof hood 25 and improve stability and reliability of the connection between the first hood plate 2523 or the second hood plate 2524 and the top cover 251. Moreover, it can facilitate the mounting and disassembly of the entire soundproof hood 25, and improve an assembly efficiency of the entire soundproof hood 25.

According to some embodiments of the present disclosure, as illustrated in FIG. 2 and FIG. 12 to FIG. 14, the outdoor unit 100 includes a first electrical control box component 30 configured to at least control the outdoor fan 111 and the compressor 21. For example, the first electrical control box component 30 is partially used to control the compressor 21 and the outdoor fan 111, or the first electrical control box component 30 is entirely used to control the compressor 21 and the outdoor fan 111. The first electrical control box component 30 is disposed at an upper part of the first partition plate 113, which can make distance between the first electrical control box component 30 and each of the outdoor fan 111 and the compressor 21 relatively short. Therefore, length of a connection wire harness between the first electrical control box component 30 and each of the outdoor fan 111 and the compressor 21 can be reduced, facilitating control connection of the outdoor fan 111 and the compressor 21 by the first electrical control box component 30.

The part of the first partition plate 113 forming the soundproof hood 25 is a soundproof portion 1137c. The soundproof portion 1137c of the first partition plate 113 has an effect of soundproof and noise reduction, which can effectively prevent the noise generated by the compressor assembly 20 from being transmitted to the fan chamber 11 through the first partition plate 113. In this way, the noise reduction and soundproof effect of the entire soundproof hood 25 on the compressor assembly 20 can be ensured.

The soundproof hood 25 includes a third hood plate 2525 and a top cover 251. The third hood plate 2525 has a lower end connected to an upper end of the soundproof portion 1137c and an upper end connected to the top cover 2521. An avoidance space 2526 for avoiding the first electrical control box component 30 is defined between the third hood plate 2525 and the first partition plate 113, which can avoid interference between the first electrical control box component 30 and the soundproof hood 25 and ensure normal mounting of the first electrical control box component 30 and the soundproof hood 25. Also, the avoidance space 2526 defined between the third hood plate 2525 and the first partition plate 113 can make the structure of the entire unit more compact and improve the space utilization rate of the entire unit.

For example, in some specific embodiments of the present disclosure, the soundproof hood 25 includes the first hood plate 2523, the second hood plate 2524, the third hood plate 2525, and the top cover 251, and each of the first hood plate 2523, the second hood plate 2524, the third hood plate 2525, and the top cover 251 is independently formed. The first hood plate 2523 is opposite to and spaced apart from the second hood plate 2524 in the front-rear direction. The left and right ends of the first hood plate 2523 are connected to the first partition plate 113 and the second partition plate 121, respectively, and the left and right ends of the second hood plate 2524 are connected to the first partition plate 113 and the second partition plate 121, respectively. Front and rear ends of the third hood plate 2525 are connected to the first hood plate 2523 and the second hood plate 2524 through the fasteners, respectively. The flanges may be disposed at the front and rear ends of the third hood plate 2525, and the fasteners can penetrate the flanges, in such a manner that fixation between the third hood plate 2525 and each of the first hood plate 2523 and the second hood plate 2524 can be easily realized.

The top cover 251 covers the top of the first hood plate 2523, the top of the second hood plate 2524, and a top of the third hood plate 2525. The top cover 251 is connected to the first hood plate 2523, the second hood plate 2524, the third hood plate 2525, and the second partition plate 121 through the fasteners, which is structurally simple, and is convenient for the mounting and disassembly of the entire soundproof hood 25. The flanges may be disposed at the peripheral sides of the top cover 251, and the fasteners can penetrate the flanges, in such a manner that fixation between the top cover 251 and each of the first hood plate 2523, the second hood plate 2524, the third hood plate 2525, and the second partition plate 121 can be easily realized.

According to some embodiments of the present disclosure, as illustrated in FIG. 12 and FIG. 14, the third hood plate 2525 includes an avoidance portion and an extension portion arranged at an angle. An end of the avoidance portion is connected to the upper end of the soundproof portion 1137c, and the other end of the avoidance portion extends towards the compressor chamber 12. The extension portion has a lower end connected to the other end of the avoidance portion and an upper end extending upwards and connected to the top cover. Such an arrangement can enable the avoidance space 2526 for avoiding the first electrical control box component 30 to be defined among the avoidance portion, the extension portion, and the first partition plate 113, which can better avoid the interference between the first electrical control box component 30 and the soundproof hood 25, and ensure the normal mounting of the first electrical control component 30 and the soundproof hood 25. Also, the structure of the entire unit can be made more compact and the space utilization rate of the entire unit can be improved.

According to some embodiments of the present disclosure, as illustrated in FIG. 12 and FIG. 14, the first electrical control box component 30 has a wire outlet formed at a bottom of the first electrical control box component 30. An electrical control wire harness of the first electrical control box component 30 is led out through the wire outlet, and the electrical control wire harness is partially received in the avoidance space 2526. The bottom of the first electrical control box component 30 is partially received in the avoidance space 2526, in such a manner that the wire outlet is located in the avoidance space 2526 and opposite to the avoidance portion. The electrical control wire harness of the first electrical control box component 30 is partially received in the avoidance space 2526, and the avoidance space 2526 can be used to avoid lead-out of the electrical control wire harness, which can facilitate routing of the electrical control wire harness in the outdoor unit casing 10, facilitating control connection between the first electrical control box component 30 and each of the outdoor fan 111 and the compressor 21.

According to some embodiments of the present disclosure, the electrical control wire harness includes a first electrical control wire harness and a second electrical control wire harness. The first electrical control box component 30 can control an operating state of the compressor 21 through electrical connection between the first electrical control wire harness and the compressor 21.

The first electrical control wire harness is adapted to run upwards along the extension portion and run along an upper surface of the top cover 251, extend through the top cover 251 downward, and be electrically connected to the compressor 21. Such an arrangement can make a routing path of the first electrical control wire harness more reasonable and avoid a problem of excessive length of the first electrical control wire harness due to messy routing, facilitating control connection between the first electrical control wire harness and the compressor 21. Also, the routing of the first electrical control wire harness can be made clearer, which can facilitate replacement and maintenance of the first electrical control wire harness and improve a maintenance efficiency of the entire unit.

According to some embodiments of the present disclosure, the electrical control wire harness includes a second electrical control wire harness. The first electrical control box component 30 can control an operating state of the outdoor fan 111 through electrical connection between the second electrical control wire harness and the outdoor fan 111.

The second electrical control wire harness is adapted to run rearward along the avoidance portion and run downward along the soundproof hood 25, extend into the fan chamber 11 through the first partition plate 113, and be electrically connected to the outdoor fan 11. Such an arrangement can make a routing path of the second electrical control wire harness more reasonable and avoid a problem of excessive length of the second electrical control wire harness due to messy routing, facilitating control connection between the second electrical control wire harness and the outdoor fan 111. Also, the routing of the second electrical control wire harness can be made clearer, which can facilitate replacement and maintenance of the second electrical control wire harness, and improve the maintenance efficiency of the entire unit.

According to some embodiments of the present disclosure, as illustrated in FIG. 12 to FIG. 14, the first electrical control box component 30 is provided with a radiator at an end of the first electrical control box component 30 facing towards the fan chamber 11, and the radiator can have a heat dissipation and refrigeration effect on the first electrical control box component 30. Heat generated by the first electrical control box component 30 during operation is transferred to the radiator, and the radiator can dissipate the heat of the first electrical control box component 30, realizing the heat dissipation and refrigeration effect of the radiator on an electrical control assembly 32.

Since the outdoor fan 111 is disposed in the fan chamber 11, the outdoor fan 111 can use flow of air to enhance heat exchange between the outdoor heat exchanger 112 and the air. The radiator is disposed at a side of the first electrical control box component 30 adjacent to the fan chamber 11. During operation of the outdoor fan 111, the air flow in the fan chamber 11 can be used to quickly take away the heat of the radiator, improving the heat dissipation effect of the entire radiator. Therefore, a heat dissipation efficiency of the radiator on the first electrical control box component 30 can be improved.

The outdoor unit 100 includes a second air guide hood 1134 located at a bottom of the radiator. The first partition plate 113 includes a first sub-partition plate 1136 and a second sub-partition plate 1137 arranged in the left-right direction. The second sub-partition plate 1137 is located at a side of the first sub-partition plate 1136 adjacent to the compressor chamber 12 and includes a partition plate body 1137a forming the soundproof portion 1137c. Such an arrangement can reduce the costs of the entire soundproof hood 25 and reduce the space occupied by the soundproof hood 25 within the compressor chamber 12, making the structure in the compressor chamber 12 more compact and improving the overall space utilization rate.

A second air guide chamber 1135 is defined by the second sub-partition plate 1137, the first sub-partition plate 1136, the second air guide hood 1134, and the radiator. The second sub-partition plate 1137 has a second air guide opening 1139 in communication with the second air guide chamber 1135, and an airflow in the compressor chamber 12 is adapted to flow into the second air guide chamber 1135 through the second air guide opening 1139 and flow upward through the radiator. Such an arrangement can facilitate the air in the compressor chamber 12 to flow into the second air guide chamber 1135 through the second air guide opening 1139, ensuring a ventilation volume of the second air guide chamber 1135 and improving the overall heat dissipation effect on the radiator and the electrical control box component 30.

For example, the second sub-partition plate includes a partition plate flange 1137b connected to each of front and rear sides of the partition plate body 1137a, and the second air guide opening 1139 is formed at the partition plate flange 1137b, which can allow the second air guide opening 1139 to be located outside of the soundproof hood 25. Therefore, the noise of the compressor assembly 20 inside the soundproof hood 25 can be prevented from spreading out from the air guide opening, ensuring the overall noise reduction effect on the compressor assembly 20.

When the outdoor fan 111 is operating, the outdoor fan 111 drives the air to flow in the fan chamber 11, making air pressure in the fan chamber 11 lower than air pressure in the compressor chamber 12. Since the compressor chamber 12 is connected to a lower part of the radiator through the second air guide chamber 1135, and the radiator is disposed in the fan chamber, under action of an air pressure difference between the fan chamber 11 and the compressor chamber 12, the air in the compressor chamber 12 can enter the second air guide chamber 1135 from the second air guide opening 1139, flow upward along the second air guide chamber 1135, flow to the bottom of the radiator and flow upward along the surface of the radiator, and finally enter the fan chamber 11 through the radiator. During flow of the air along the surface of the radiator, the heat of the radiator is taken away, achieving the heat dissipation effect on the radiator, and dissipating heat from the first electrical control box component 30.

According to some embodiments of the present disclosure, as illustrated in FIG. 12, a bottom of the soundproof hood 25 is connected to a base 16, which can make fixation of the entire unit on the soundproof hood 25 more stable, and improve stability and reliability of the soundproof hood 25 during use. A vibration-damping pad is disposed between the bottom of the soundproof hood 25 and the base 16. The vibration-damping pad can block vibration transmitted from the soundproof hood 25 to the base 16, which avoids a problem of vibration and noise generation of the base 16 caused by transmitting of the vibration of the soundproof hood 25 to the base 16. In this way, the overall noise reduction and soundproof effect on the compressor assembly 20 can be ensured.

According to some embodiments of the present disclosure, as illustrated in FIG. 10 to FIG. 14, the soundproof hood 25 includes a top cover 251 having a pipeline outlet 2513. A pipeline of the compressor assembly 20 is adapted to be led out from the pipeline outlet 2513. The pipeline outlet 2513 at the top cover 251 can be used to lead out the pipeline of the compressor assembly 20, which is convenient for connection between the compressor assembly 20 inside the soundproof hood 25 and external components. For example, the pipeline can refer to a refrigerant pipeline and electrical control wiring harnesses.

According to some embodiments of the present disclosure, as illustrated in FIG. 10 to FIG. 12, the top cover 251 includes a first cover body 2511 and a second cover body 2512 that are detachably connected in a horizontal direction. The pipeline outlet 2513 is defined between the first cover body 2511 and the second cover body 2512, which can facilitate a pipeline of the compressor assembly 20 to be led out from the pipeline outlet 2513. When mounting the top cover 251, the first cover body 2511 can be fixed to a side of the pipeline of the compressor assembly 20, and then the second cover body 2512 can be fixed to another side of the pipeline of the compressor assembly 20. In this way, the pipeline of the compressor assembly 20 can be led out from the pipeline outlet 2513, which is structurally simple and is easy to operate. For example, the pipeline outlet 2513 can be formed at the first cover body, or the pipeline outlet 2513 can be formed at the second cover body.

According to some embodiments of the present disclosure, as illustrated in FIG. 14, the top cover 251 is formed from one single piece, which can enhance structural strength and rigidity of the top cover 251, and improve the assembly efficiency of the entire soundproof hood 25. For example, when the top cover 251 is formed from one single piece, a projection of the pipeline outlet 2513 at the top cover 251 in a horizontal plane may be U-shaped, and the pipeline outlet 2513 can penetrate a side edge of the top cover 251.

According to some embodiments of the present disclosure, as illustrated in FIG. 10 and FIG. 11, the top cover 251 is provided with a first sealing structure 2514 for sealing a gap between the pipeline of the compressor assembly 20 and an inner wall of the pipeline outlet 2513. In this way, on the one hand, the first sealing structure 2514 can prevent the noise from leaking through the pipeline outlet 2513, better ensuring the noise reduction and soundproof effect of the soundproof hood 25 on the internal compressor assembly 20. On the other hand, the first sealing structure 2514 can prevent external liquid from entering the soundproof hood 25, ensuring normal use of the compressor assembly 20. For example, the first sealing structure 2514 may be made of a porous material or an elastic rubber material, etc., which can ensure a noise reduction and soundproof effect of the first sealing structure 2514.

According to some embodiments of the present disclosure, as illustrated in FIG. 7 and FIG. 8, the outdoor unit 100 further includes the water-circuit heat-exchange assembly 40 including the water-circuit heat exchanger 51. The water-circuit heat exchanger 51 has the water flow passage and the refrigerant flow passage that exchange heat with each other. The refrigerant in the refrigerant flow passage can exchange heat with the water flow in the water flow passage, allowing the water-circuit heat exchanger 51 to provide heating or cooling for the water flow. The water-circuit heat-exchange assembly 40 can regulate the temperature of the passing water flow, allowing the entire unit to provide heating or cooling for the water flow. The water flow flowing out of the water-circuit heat exchanger 51 can be transported to the room to regulate the temperature of indoor domestic water or the indoor temperature.

The water-circuit heat exchanger 51 is located outside the soundproof hood 25 and fixed to the soundproof hood 25, which can make distance between the water-circuit heat exchanger 51 and the compressor assembly 20 relatively short, facilitating connection between the water-circuit heat exchanger 51 and the compressor assembly 20. Moreover, the water-circuit heat exchanger 51 is fixed to the soundproof hood 25, which can attenuate vibration transmitted from the water-circuit heat exchanger 51 to the base 16. In this way, it can play a vibration damping role in the water-circuit heat exchanger 51 and improve the overall vibration and noise reduction effect.

For example, the water-circuit heat exchanger 51 can be rigidly connected to the soundproof hood 25 through a mounting support 26, which can enhance structural strength and rigidity of a joint between the water-circuit heat exchanger 51 and the soundproof hood 25, and ensure stability and reliability of connection between the water-circuit heat exchanger 51 and the soundproof hood 25.

According to some embodiments of the present disclosure, as illustrated in FIG. 9, the compressor assembly 20 further includes a liquid reservoir 22 fixed to a base 16. In the related art, the liquid reservoir 22 of the compressor assembly 20 is fixed at the compressor 21 and is in a suspended state. When the compressor 21 vibrates, the liquid reservoir 22 also resonates with the compressor 21, increasing vibration of the entire compressor assembly 20, and further leading to an increase in overall noise. The liquid reservoir 22 is fixed to the base 16, and the air return port 222 of the compressor 21 can be connected to the liquid reservoir 22 through a liquid receiving pipe 211. The base 16 can stably support the liquid reservoir 22 and prevent the liquid reservoir 22 from being in the suspended state. When the compressor 21 vibrates, the base 16 can ensure stability of the liquid reservoir 22 and reduce the vibration of the liquid reservoir 22, reducing the vibration of the entire compressor assembly 20 and lowering the overall noise.

According to some embodiments of the present disclosure, as illustrated in FIG. 14, the soundproof hood 25 is at least partially made of a composite panel 15. For example, part of the soundproof hood 25 may be made of the composite panel 15, or the entire soundproof hood 25 may be made of the composite panel 15. The composite panel 15 includes metal layers 151 and a first damping layer 152 stacked together, and the first damping layer 152 is located between two adjacent metal layers 151. When the compressor assembly 20 is operating, the composite panel 15 is forced to vibrate, and bending vibration generated by the composite panel 15 causes a phase difference between the two adjacent metal layers 151, resulting in shear deformation of the first damping layer 152 between the two adjacent metal layers 151. The first damping layer 152 can absorb a large amount of vibrational mechanical energy, and convert the vibrational mechanical energy into heat energy and dissipate the heat energy, in such a manner that the soundproof hood 25 can have a better noise reduction and soundproof effect.

According to some embodiments of the present disclosure, as illustrated in FIG. 16, the outdoor unit casing 10 is at least partially made of a composite panel 15. For example, part of the outdoor unit casing 10 may be made of the composite panel 15, or the entire outdoor unit casing 10 may be made of the composite panel 15. The composite panel 15 includes the metal layers 151 and the first damping layer 152 stacked together, and the first damping layer 152 is located between the two adjacent metal layers 151. The first damping layer 152 can consume energy of passing noise, allowing the composite panel 15 to have a better noise reduction and soundproof effect. When the compressor assembly 20 is operating, the composite panel 15 is forced to vibrate, and the bending vibration generated by the composite panel 15 causes the phase difference between the two adjacent metal layers 151, resulting in the shear deformation of the first damping layer 152 between the two adjacent metal layers 151. The first damping layer 152 can absorb a large amount of vibrational mechanical energy and convert the vibrational mechanical energy into the heat energy and dissipate the heat energy, in such a manner that the composite panel 15 can have the better noise reduction and soundproof effect, effectively reducing the overall noise.

According to some embodiments of the present disclosure, as illustrated in FIG. 16, the first damping layer 152 has a thickness ranging from 0.002 mm to 3 mm. If the thickness of the first damping layer 152 in the composite panel 15 is too large, the thickness of the entire composite panel 15 is too large, which is not conducive to bending and flanging processing of the entire composite panel 15 and increases production costs of the entire composite panel 15. If the thickness of the first damping layer 152 in the composite panel 15 is too small, it makes the noise reduction and soundproof effect of the composite panel 15 poor and a vibration isolation rate low. Therefore, the thickness of the first damping layer 152 is set to range from 0.002 mm to 3 mm, which can make the noise reduction and soundproof effect of the composite panel 15 better, ensure the vibration isolation rate of the composite panel 15, facilitate the bending and flanging processing of the entire composite panel 15, and reduce costs. For example, the thickness of the first damping layer 152 may be 0.002 mm, 0.01 mm, 0.2 mm, 3 mm, etc.

According to some embodiments of the present disclosure, as illustrated in FIG. 16, the first damping layer 152 has a thickness ranging from 0.02 mm to 0.2 mm, which can make the noise reduction and soundproof effect of the composite panel 15 better, and improve the vibration isolation rate of the composite panel 15, facilitate the bending and flanging processing of the entire composite panel 15, and reduce the costs.

According to some embodiments of the present disclosure, as illustrated in FIG. 16, the metal layer 151 has a thickness ranging from 0.1 mm to 5 mm. If the thickness of the metal layer 151 in the composite panel 15 is too large, a thickness of the entire composite panel 15 is too large, which is not conducive to the bending and flanging processing of the entire composite panel 15 and increases the production costs and weight of the entire composite panel 15. If the thickness of the metal layer 151 in the composite panel 15 is too small, it makes the structural strength and rigidity of the entire composite panel 15 poor and the composite panel prone to cracking or damage. Therefore, the thickness of the metal layer 151 is set to range from 0.1 mm to 5 mm, which can ensure the structural strength and rigidity of the entire composite panel 15, facilitate the bending and flanging processing of the entire composite panel 15, and reduce the costs. For example, the thickness of the metal layer 151 may be 0.1 mm, 0.5 mm, 1 mm, 2 mm, 5 mm, etc.

According to some embodiments of the present disclosure, as illustrated in FIG. 16, the metal layer 151 has a thickness ranging from 0.4 mm to 0.8 mm, which can better ensure the structural strength and rigidity of the entire composite panel 15, facilitate the bending and flanging processing of the entire composite panel 15, and reduce the costs.

According to some embodiments of the present disclosure, as illustrated in FIG. 14 and FIG. 18, at least one of an inner wall of the soundproof hood 25 and an outer circumferential wall of the compressor 21 is provided with a soundproof cotton layer 23. For example, one of the inner wall of the soundproof hood 25 and the outer circumferential wall of the compressor 21 is provided with the soundproof cotton layer 23, or both the inner wall of the soundproof hood 25 and the outer circumferential wall of the compressor 21 are provided with the soundproof cotton layer 23. The soundproof cotton layer 23 can have a sound absorption and soundproof effect on the compressor assembly 20, reducing noise transmitted outward by the compressor assembly 20. The soundproof cotton layer 23 is disposed at the inner wall of the soundproof hood 25 and can engage with the soundproof hood 25, achieving a better noise reduction and soundproof effect on the compressor assembly 20.

According to some embodiments of the present disclosure, at least part of an inner wall of the outdoor unit casing 10 is provided with the soundproof cotton layer 23. For example, part of the inner wall of the outdoor unit casing 10 is provided with the soundproof cotton layer 23, or the entire inner wall of the outdoor unit casing 10 are provided with the soundproof cotton layer 23. The soundproof cotton layer 23 can have a sound absorption and soundproof effect on noise, improving the soundproof and sound absorption effect of the entire outdoor unit casing 10 and reducing the overall noise.

According to some embodiments of the present disclosure, as illustrated in FIG. 17, the soundproof cotton layer 23 has a thickness ranging from 5 mm to 50 mm. If the thickness of the soundproof cotton layer 23 is too large, the soundproof cotton layer 23 occupies more space inside the compressor chamber 12, which is not conducive to mounting of pipelines and components inside the compressor chamber 12. If the thickness of the soundproof cotton layer 23 is too small, a noise reduction level of the soundproof cotton layer 23 is reduced, resulting in a poor noise reduction and soundproof effect of the soundproof cotton layer 23. Therefore, when the thickness of the soundproof cotton layer 23 ranges from 5 mm to 50 mm, the noise reduction level of the soundproof cotton layer 23 can be guaranteed, improving the noise reduction and soundproof effect of the soundproof cotton layer 23. Also, an internal space of the compressor chamber 12 can be saved, which is convenient for the mounting of the pipelines and components inside the compressor chamber 12. For example, the thickness of the soundproof cotton layer 23 may be 5 mm, 20 mm, 30 mm, 50 mm, etc.

According to some embodiments of the present disclosure, as illustrated in FIG. 17, the soundproof cotton layer 23 includes a sound absorption layer 231, a second damping layer 232, and a soundproof layer 233 that are stacked in sequence. When the compressor assembly 20 is operating, the noise generated by the compressor assembly 20 passes through the sound absorption layer 231, the second damping layer 232, and the soundproof layer 233 in sequence during its outward radiation. When passing through the sound absorption layer 231, a part of energy of high-frequency noise is first absorbed. When the noise is transmitted to the second damping layer 232, the second damping layer 232 converts energy of medium-and-low-frequency noise into heat energy through its own creep and dissipates the heat energy, in such a manner that a prat of the energy of the medium-and-low-frequency noise is dissipated. Finally, when the noise is transmitted to the soundproof layer 233, a part of the energy of the noise is reflected by the soundproof layer 233, and this part of the energy passes through the second damping layer 232 and the sound absorption layer 231 in sequence for secondary consumption, blocking the noise from being transmitted outward.

Compared with a conventional soundproof cotton layer 23, such an arrangement can increase the noise reduction level of the entire soundproof cotton layer 23, and can more effectively reduce the noise transmitted by the compressor assembly 20, achieving the better noise reduction and soundproof effect.

For example, the sound absorption layer 231, the second damping layer 232, and the soundproof layer 233 can form the entire soundproof cotton layer 23 by means of gluing or sewing, which can prevent the sound absorption layer 231, the second damping layer 232, and the soundproof layer 233 from falling off the entire soundproof cotton layer 23, ensuring the normal use of the soundproof cotton layer 23.

According to some embodiments of the present disclosure, as illustrated in FIG. 17, the sound absorption layer 231 is a porous material layer. When the noise is transmitted to the sound absorption layer 231, the noise is reflected and refracted multiple times in the pores, in such a manner that the sound absorption layer 231 can absorb more noise and achieve a noise reduction effect. For example, the sound absorption layer 231 may be made of a porous material with a sound absorption coefficient greater than 0.8, making a sound absorption effect of the sound absorption layer 231 better. The second damping layer 232 is a rubber layer. Rubber has a characteristic of high elasticity and can better convert vibration into the heat energy, enabling the second damping layer 232 to achieve a better noise reduction effect. For example, the second damping layer 232 may be a rubber layer with a loss factor greater than 0.4, making a noise reduction effect of the second damping layer 232 better. The soundproof layer 233 is a plastic layer or a rubber layer. The plastic layer and the rubber layer have a certain surface density, in such a manner that the soundproof layer 233 can reflect more noise energy, achieving a better soundproof effect.

According to some embodiments of the present disclosure, as illustrated in FIG. 17, the sound absorption layer 231 has a thickness ranging from 5 mm to 15 mm. If the thickness of the sound absorption layer 231 is too large, a thickness of the entire soundproof cotton layer 23 is too large, which is not conducive to the mounting of the entire soundproof cotton layer 23 and increases the costs of the entire soundproof cotton layer 23. If the thickness of the sound absorption layer 231 is too small, sound absorption capacity of the sound absorption layer 231 is reduced, reducing the sound absorption and soundproof effect of the entire soundproof cotton layer 23. Therefore, when the thickness of the sound absorption layer 231 ranges from 5 mm to 15 mm, noise absorption capacity of the sound absorption layer 231 can be guaranteed, improving the noise reduction effect of the entire soundproof cotton layer 23. Also, the thickness of the entire soundproof cotton layer 23 can be guaranteed, which is convenient for the mounting of the soundproof cotton layer 23 and saves the costs. For example, the thickness of the sound absorption layer 231 may be 5 mm, 8 mm, 10 mm, 15 mm, etc.

According to some embodiments of the present disclosure, as illustrated in FIG. 17, the second damping layer 232 has a thickness ranging from 2 mm to 6 mm. If the thickness of the second damping layer 232 is too large, a thickness of the entire soundproof cotton layer 23 is too large, which is not conducive to the mounting of the entire soundproof cotton layer 23 and increases the costs of the entire soundproof cotton layer 23. If the thickness of the second damping layer 232 is too small, noise energy dissipation capacity of the second damping layer 232 is low, reducing the noise reduction effect of the entire soundproof cotton layer 23. Therefore, when the thickness of the second damping layer 232 ranges from 2 mm to 6 mm, the noise energy dissipation capacity of the second damping layer 232 can be guaranteed, improving the noise reduction effect of the entire soundproof cotton layer 23. Also, the thickness of the entire soundproof cotton layer 23 can be guaranteed, which is convenient for the mounting of the soundproof cotton layer 23 and saves the costs. For example, the thickness of the second damping layer 232 may be 2 mm, 3 mm, 4 mm, 6 mm, etc.

According to some embodiments of the present disclosure, as illustrated in FIG. 17, the soundproof layer 233 has a thickness ranging from 1 mm to 3 mm. If the thickness of the soundproof layer 233 is too large, the thickness of the entire soundproof cotton layer 23 is too large, which is not conducive to the mounting of the entire soundproof cotton layer 23 and increases the costs of the entire soundproof cotton layer 23. If the thickness of the soundproof layer 233 is too small, noise reflected by the soundproof layer 233 can be reduced, reducing the sound absorption and soundproof effect of the entire soundproof cotton layer 23. Therefore, when the thickness of the soundproof layer 233 ranges from 2 mm to 6 mm, noise reflection capacity of the soundproof layer 233 can be guaranteed, improving the noise reduction effect of the entire soundproof cotton layer 23. Also, the overall thickness of the soundproof cotton layer 23 can be guaranteed, which is convenient for the mounting of the soundproof cotton layer 23 and saves costs. For example, the thickness of the soundproof layer 233 may be 1 mm, 2 mm, 3 mm, etc.

According to some embodiments of the present disclosure, as illustrated in FIG. 18 and FIG. 19, an outer circumferential wall of the compressor 21 is covered with a soundproof cotton layer 23. The soundproof cotton layer 23 can have sound absorption and soundproof effects on the compressor 21, effectively reducing the noise of the entire unit. For example, the outer circumferential wall of the compressor 21 and an outer circumferential wall of the liquid reservoir 22 can be covered with multiple layers of soundproof cotton layers 23, which can better improve the soundproof effect on the compressor assembly 20.

A support structure 24 is disposed between the soundproof cotton layer 23 and the outer circumferential wall of the compressor 21 to define an air layer between the soundproof cotton layer 23 and the outer circumferential wall of the compressor 21. If the soundproof cotton layer 23 is directly coated at the outer circumferential wall of the compressor 21 by means of gluing, since the soundproof cotton layer 23 is mostly made of porous material, when the soundproof cotton layer 23 is closely attached to the compressor 21, pores of the soundproof cotton layer 23 are squeezed, reducing the sound absorption effect. In this way, the air layer is defined between the soundproof cotton layer 23 and the outer circumferential wall of the compressor 21 by the support structure 24. On the one hand, the pores of the soundproof cotton layer 23 can be prevented from being squeezed, ensuring the noise reduction and sound absorption effect of the soundproof cotton layer 23. On the other hand, during a process of noise propagation in the air layer, the air can absorb part of energy of sound waves. Therefore, introduction of the air layer can improve the overall noise reduction effect.

According to some embodiments of the present disclosure, as illustrated in FIG. 18 and FIG. 19, the support structure 24 is an elastic support structure 24. The elastic support structure 24 has good elasticity. When the compressor 21 vibrates, the support structure 24 can attenuate the vibration transmitted from the compressor 21 to the soundproof cotton layer 23, and can play a partial role in vibration damping and noise reduction, improving the overall noise reduction effect. In addition, the support structure 24 has good elasticity, which can facilitate the mounting of the support structure 24 and improve the assembly efficiency.

According to some embodiments of the present disclosure, as illustrated in FIG. 18 and FIG. 19, a spacing between the soundproof cotton layer 23 and the outer circumferential wall of the compressor 21 ranges from 5 mm to 20 mm. If the spacing between the soundproof cotton layer 23 and the outer circumferential wall of the compressor 21 is too large, the soundproof cotton layer 23 interferes with a pipeline near the compressor 21, which is not conducive to pipeline layout of the compressor 21. If the spacing between the soundproof cotton layer 23 and the outer circumferential wall of the compressor 21 is too small, the thickness of the air layer is too small, reducing the overall noise reduction and soundproof effect.

Therefore, when the spacing between the soundproof cotton layer 23 and the outer circumferential wall of the compressor 21 ranges from 5 mm to 20 mm, the soundproof cotton layer 23 can have a better noise reduction and sound absorption effect, better reducing the overall noise. Also, interference between the soundproof cotton layer 23 and the pipeline around the compressor 21 can be avoided, ensuring reasonable layout of the pipeline of the compressor 21. For example, the spacing between the soundproof cotton layer 23 and the outer circumferential wall of the compressor 21 may be 5 mm, 10 mm, 15 mm, 20 mm, etc.

According to some embodiments of the present disclosure, as illustrated in FIG. 18 and FIG. 19, the support structure 24 includes a plurality of support rings 241 arranged at intervals in an up-down direction, and the plurality of support rings 241 surround the outer circumferential wall of the compressor 21. Such an arrangement can ensure a connection area between the support structure 24 and the soundproof cotton layer 23, and improve stability and reliability of connection between the support structure 24 and the soundproof cotton layer 23. Also, a coverage area of the air layer can be ensured, guaranteeing noise energy absorption capacity of the air layer and improving the overall noise reduction and sound absorption effect. For example, each of the outer circumferential wall of the compressor 21 and the outer circumferential wall of the liquid reservoir 22 can be provided with the support structure 24. The support structure 24 includes two support rings 241 that are spaced apart from each other in the up-down direction, the two support rings 241 of the support structure 24 disposed at the outer circumferential wall of the compressor 21 are disposed at upper and lower parts of the outer circumferential wall of the compressor 21, respectively, and the two support rings 241 of the support structure 24 disposed at the outer circumferential wall of the liquid reservoir 22 are disposed at upper and lower parts of the outer circumferential wall of the liquid reservoir 22, respectively.

According to some embodiments of the present disclosure, as illustrated in FIG. 18 and FIG. 19, the support structure 24 includes a plurality of support bars 242 or support blocks 243 arranged at intervals in a circumferential direction of the compressor 21. Such an arrangement can ensure the connection area between the support structure 24 and the soundproof cotton layer 23, and improve the stability and reliability of the connection between the support structure 24 and the soundproof cotton layer 23. Also, the coverage area of the air layer can also be ensured, guaranteeing the noise energy absorption capacity of the air layer and improving the overall noise reduction and sound absorption effect. For example, each of the plurality of support bars 242 can extend in the up-down directions, and the plurality of support bars 242 or support blocks 243.

According to some embodiments of the present disclosure, as illustrated in FIG. 2 to FIG. 4, a vibration damping structure 14 is disposed between the compressor 21 and a base 16 of the outdoor unit casing 10. The vibration damping structure 14 can play a vibration damping role on the compressor assembly 20, reducing the overall noise. During operation of the outdoor unit 100, the vibration transmitted from the compressor assembly 20 to the base 16 is attenuated by the vibration damping structure 14, reducing the vibration transmitted to the base 16. Therefore, the noise generated when the outdoor unit 100 is operating can be reduced, making the vibration and noise transmitted outward by the compressor assembly 20 relatively small.

The vibration damping structure 14 includes a floating plate 141 and a vibration damping assembly. The vibration damping assembly includes at least one of a first vibration damping member 142 and a second vibration damping member 143. For example, the vibration damping assembly includes the first vibration damping member 142, or the vibration damping assembly includes the second vibration damping member 143, or the vibration damping assembly includes the first vibration damping member 142 and the second vibration damping member 143. The vibration damping assembly can reduce the vibration transmitted from the compressor 21 to the base 16, reducing the overall noise.

The floating plate 141 is located above the base 16. The first vibration damping member 142 is disposed between the compressor 21 and the floating plate 141, and the second vibration damping member 143 is disposed between the floating plate 141 and the base 16. When the compressor 21 vibrates, vibration of the compressor 21 can be first transmitted to the floating plate 141, and then transmitted to the base 16. When the vibration damping assembly includes the first vibration damping member 142, the first vibration damping member 142 disposed between the compressor 21 and the floating plate 141 can reduce the vibration of the compressor 21 during a process of transmitting the vibration of the compressor 21 to the floating plate 141. Reduced vibration is then transmitted from the floating plate 141 to the base, in such a manner that the vibration of the compressor 21 can be attenuated during a process of transmitting to the base 16, achieving an overall vibration damping and noise reduction effect.

When the vibration damping assembly includes the second vibration damping member 143, the vibration of the compressor 21 can be first transmitted to the floating plate 141, and then transmitted from the floating plate 141 to the base. During the process of transmitting from the floating plate 141 to the base 16, the second vibration damping member 143 disposed between the floating plate 141 and the base 16 can reduce the vibration. Therefore, the vibration of the compressor 21 can be attenuated during the process of transmitting to the base 16, achieving the overall vibration damping and noise reduction effect.

When the vibration damping assembly includes the first vibration damping member 142 and the second vibration damping member 143, during the process of transmitting the vibration of the compressor 21 to the floating plate 141, the first vibration damping member 142 disposed between the compressor 21 and the floating plate 141 can reduce the vibration of the compressor 21 for the first time. During a process of transmitting the reduced vibration from the floating plate 141 to the base 16, the second vibration damping member 143 disposed between the floating plate 141 and the base 16 can reduce the vibration for the second time. In this way, the first vibration damping member 142 cooperates with the second vibration damping member 143, which can achieve secondary attenuation of the vibration of the compressor 21 during the process of transmitting to the base 16, achieving a better overall vibration damping and noise reduction effect.

For example, both the first vibration damping member 142 and the second vibration damping member 143 may be rubber members. The rubber member has a characteristic of high elasticity, which can allow both the first vibration damping member 142 and the second vibration damping member 143 to have a better vibration damping effect.

According to some embodiments of the present disclosure, as illustrated in FIG. 4, the compressor assembly 20 further includes a liquid reservoir 22 connected to the compressor 21. A projection of the compressor 21 in a horizontal plane is a first projection, a projection of the floating plate 141 in the horizontal plane is a second projection, and a projection of the liquid reservoir 22 in the horizontal plane is a third projection. The first projection is located within the second projection, and the third projection is at least partially located within the second projection. For example, part of the third projection is located within the second projection or the entire third projection is located within the second projection. Since the floating plate 141 supports the compressor assembly 20, such an arrangement enables most of the entire compressor assembly 20 to be located directly above the floating plate 141, which can shorten distance between a center of gravity of the entire compressor assembly 20 and a center of gravity of the floating plate 141. During the operation of the compressor assembly 20, a degree of eccentric shaking between the entire compressor assembly 20 and the floating plate 141 can be reduced, improving stability of the compressor assembly 20 and the floating plate 141 as a whole. Therefore, the vibration damping and noise reduction effect of the vibration damping structure 14 on the entire compressor assembly 20 can be made better.

In addition, it also allows the compressor assembly 20 and the floating plate 141 as a whole to have a lower center of gravity and a more stable overall structure. In this way, a vibration amplitude of the compressor assembly 20 and the floating plate 141 as a whole can be reduced, which can further reduce the vibration transmitted to the base 16, reducing the overall vibration and noise.

According to some embodiments of the present disclosure, as illustrated in FIG. 3 to FIG. 5, the floating plate 141 has an avoidance notch 1411. The avoidance notch 1411 can prevent the floating plate from interfering with other structures or components, which facilitates mounting and disassembly of the floating plate, ensuring normal use of the vibration damping structure. Moreover, the avoidance notch 1411 can make the overall structure more compact, which is conducive to improving the overall space utilization rate.

For example, the avoidance notch 1411 can be used to avoid the refrigerant pipeline between the compressor assembly 20 and other components, or the avoidance notch 1411 is used to avoid other structures at the base. When the avoidance notch 1411 is used to avoid the refrigerant pipeline, a certain spacing can be formed between the refrigerant pipeline and the floating plate 141 to avoid the refrigerant pipeline from contacting the floating plate 141. Therefore, the floating plate 141 can be prevented from transmitting the vibration of the compressor assembly 20 to the refrigerant pipeline, affecting the overall vibration damping and noise reduction effect. Also, a problem of damage to the refrigerant pipeline caused by friction between the floating plate 141 and the refrigerant pipeline due to the vibration of the compressor assembly 20 can be avoided, prolonging a service life of the refrigerant pipeline.

For example, the avoidance notch 1411 may be in a form of a groove, or a corner of the floating plate can be cut off to form an avoidance notch at a position where the corner is missing.

According to some embodiments of the present disclosure, as illustrated in FIG. 5, the compressor assembly 20 further includes a liquid reservoir 22 connected to the compressor 21. The floating plate 141 has a plurality of first mounting holes 144 for mounting of the compressor 21 and a plurality of second mounting holes 145 for mounting of the floating plate 141. For example, the compressor 21 can be fastened and connected to the floating plate 141 by a first fastener 1441 passing through the first mounting hole 144, which is structurally simple and facilitates mounting and disassembly the compressor 21. The first fastener 1441 can sequentially penetrate the compressor 21, the first vibration damping member 142, and the floating plate 141 in the up-down direction, which allows the first vibration damping member 142 to be fixed between the compressor 21 and the floating plate 141, attenuating the vibration transmitted from the compressor 21 to the floating plate 141. The floating plate 141 can be fastened and connected to the base 16 by a second fastener 1451 passing through the second mounting hole 145, which is structurally simple and facilitates mounting and disassembly of the floating plate 141. The second fastener 1451 can sequentially penetrate the floating plate 141, the second vibration damping member 143, and the base 16 in the up-down direction, which allows the second vibration damping member 143 to be fixed between the floating plate 141 and the base 16, attenuating the vibration transmitted from the floating plate 141 to the base 16. In this way, the first mounting hole 144 is used for mounting between the compressor 21 and the floating plate 141, and the second mounting hole 145 is used for mounting between the floating plate 141 and the base 16.

Centers of the plurality of first mounting holes 144 are located at a first reference circle a1, in such a manner that distances from the plurality of first mounting holes 144 to a center o1 of the first reference circle a1 can be the same. In addition, the plurality of first mounting holes 144 can be evenly arranged at intervals along a circumference of the first reference circle a1, which can allow the floating plate 141 to support the compressor 21 more stably. Centers of the plurality of second mounting holes 145 are located at a second reference circle a2, in such a manner that distances from the plurality of second mounting holes 145 to a center o2 of the second reference circle a2 can be the same. In addition, the plurality of second mounting holes 145 can be evenly arranged at intervals along a circumference of the second reference circle a2, which can allow the base 16 of the outdoor unit 100 to support the floating plate 141 more stably.

For example, the plurality of first mounting holes 144 may include three first mounting holes 144. The three first mounting holes 144 are evenly arranged at intervals along the circumference of the first reference circle a1, which can guarantee stability and reliability of connection between the compressor 21 and the floating plate 141. The plurality of second mounting holes 145 may include four second mounting holes 145. The four second mounting holes 145 are evenly arranged at intervals along the circumference of the second reference circle a2, which can improve stability and reliability of connection between the floating plate 141 and the base 16.

According to some embodiments of the present disclosure, as illustrated in FIG. 5, a projection of a center o2 of the second reference circle a2 in a reference plane is spaced apart from a projection of a center o1 of the first reference circle a1 in the reference plane, and the reference plane is parallel to a plane where an outer peripheral contour line of the base 16 is located. The center o2 of the second reference circle a2 is located at a side of the center o1 of the first reference circle a1 adjacent to the liquid reservoir 22. Since the liquid reservoir 22 is connected to the compressor 21, the floating plate 141 supports both the compressor 21 and the liquid reservoir 22. Usually, to stably mount the compressor 21 at the floating plate 141, a plurality of connection points (i.e., the plurality of first mounting holes 144 described above) between the compressor 21 and the floating plate 141 are evenly distributed and located at the same circle. Moreover, a projection of a center of the circle where the plurality of connection points between the compressor 21 and the floating plate 141 are located in the horizontal plane is roughly coincident with a projection of a center of the compressor 21 in the horizontal plane. However, a center of mass of the compressor assembly 20 including the liquid reservoir 22 deviates from the center of the compressor 21 and is located at a side of the center of the compressor 21 adjacent to the liquid reservoir 22.

By locating the center o2 of the second reference circle a2 at the side of the center o1 of the first reference circle a1 adjacent to the liquid reservoir 22, that is, allowing a mounting center of the floating plate 141 (that is, the center o2 of the second reference circle a2) to deviate from a mounting center of the compressor 21 (the center o1 of the first reference circle a1), and locating the mounting center of the floating plate 141 at a side of the mounting center of the compressor 21 adjacent to the liquid reservoir 22, a projection of the mounting center of the floating plate 141 in the horizontal plane can be made closer to a projection of the center of mass of the compressor assembly 20 in the horizontal plane. Therefore, the floating plate 141 can support the compressor assembly 20 more stably, which can improve a vibration isolation rate of the vibration damping structure 14.

According to some embodiments of the present disclosure, as illustrated in FIG. 3 to FIG. 5, the floating plate 141 has a plurality of second mounting holes 145 for mounting the floating plate 141, and centers of the plurality of second mounting holes 145 are located at the second reference circle a2, in such a manner that distances from the plurality of second mounting holes 145 to the center o2 of the second reference circle a2 can be the same, and the plurality of second mounting holes 145 can be evenly arranged at intervals along the circumference of the second reference circle a2.

Projections of a center of mass of the compressor assembly 20 and a center o2 of the second reference circle a2 in a reference plane are a first projection point and a second projection point, respectively, and the reference plane is parallel to a plane where an outer peripheral contour line of the base 16 is located. A spacing between the first projection point and the second projection point ranges from 0 mm to 5 mm. The compressor assembly 20 includes the compressor 21 and the liquid reservoir 22 connected to the compressor 21, and the entire compressor assembly 20 can be disposed at the floating plate 141 through the compressor 21. The spacing between the first projection point and the second projection point ranges from 0 mm to 5 mm, which can shorten distance between the projection of the center of mass of the compressor assembly 20 in the reference plane and a projection of the mounting center of the floating plate 141 (i.e., the center o2 of the second reference circle a2) in the reference plane, allowing the floating plate 141 to support the compressor assembly 20 more stably. Therefore, the vibration damping effect of the vibration damping structure 14 can be enhanced, improving the vibration isolation rate of the vibration damping structure 14.

The vibration damping effect of the entire vibration damping structure 14 becomes better, and the vibration isolation rate of the vibration damping structure 14 becomes higher as the spacing between the first projection point and the second projection point decreases. When the spacing between the first projection point and the second projection point is 0 mm, that is, the first projection point coincides with the second projection point, the vibration damping effect of the vibration damping structure 14 can be the best.

According to some embodiments of the present disclosure, as illustrated in FIG. 3 to FIG. 5, projections of a center of mass of the floating plate 141 and the center o2 of the second reference circle a2 in the reference plane are a third projection point and the second projection point, respectively, and a spacing between the third projection point and the second projection point ranges from 0 mm to 5 mm. Such an arrangement can shorten distance between the projection of the center of mass of the floating plate 141 in the reference plane and the projection of the mounting center of the floating plate 141 (i.e., the center o2 of the second reference circle a2) in the reference plane, allowing the floating plate 141 to support the compressor assembly 20 more stably. Therefore, the vibration damping effect of the vibration damping structure 14 is enhanced, improving the vibration isolation rate of the vibration damping structure 14.

The vibration damping effect of the entire vibration damping structure 14 becomes better, and the vibration isolation rate of the vibration damping structure 14 becomes higher as the spacing between the second projection point and the third projection point decreases. When the spacing between the second projection point and the third projection point is 0 mm, that is, the second projection point coincides with the third projection point, the vibration damping effect of the vibration damping structure 14 can be the best.

According to some embodiments of the present disclosure, as illustrated in FIG. 3 to FIG. 5, projections of a center of mass of the compressor assembly 20 and a center of mass of the floating plate 141 in the reference plane are a first projection point and a third projection point, respectively, and the reference plane is parallel to a plane where an outer peripheral contour line of the base 16 is located. A spacing between the first projection point and the third projection point ranges from 0 mm to 5 mm. Such an arrangement can make distance between the projection of the center of mass of the compressor assembly 20 in the reference plane and the projection of the center of mass of the floating plate 141 in the reference plane shorter, allowing the floating plate 141 to support the compressor assembly 20 more stably, and improving the stability of the compressor assembly 20 and the floating plate 141 as a whole. Therefore, the vibration damping effect of the vibration damping structure 14 is enhanced, improving the vibration isolation rate of the vibration damping structure 14.

The vibration damping effect of the entire vibration damping structure 14 becomes better, and the vibration isolation rate of the vibration damping structure 14 becomes higher as the spacing between the first projection point and the third projection point decreases. When the spacing between the first projection point and the third projection point is 0 mm, that is, the first projection point coincides with the third projection point, the vibration damping effect of the vibration damping structure 14 can be the best.

According to some embodiments of the present disclosure, a mass ratio of the floating plate 141 to the compressor 21 ranges from 0.1 to 0.6. A numerical unit of the mass of the floating plate 141 is consistent with a numerical unit of the mass of the compressor 21. If the mass ratio of the floating plate 141 to the compressor 21 is too small, when the compressor 21 is operating, the floating plate 141 vibrate to a large extent under the action of the compressor 21, making the vibration damping effect of the vibration damping structure 14 on the compressor assembly 20 poor. If the mass ratio of the floating plate 141 to the compressor 21 is too large, the mass of the floating plate 141 itself is too large, increasing the production costs of the floating plate 141, and making the mounting of the entire floating plate 141 inconvenient.

Therefore, when the mass ratio of the floating plate 141 to the compressor 21 ranges from 0.1 to 0.6, the vibration damping effect of the entire vibration damping structure 14 can be improved, and the mass of the floating plate 141 can be ensured to be appropriate, reducing the production costs of the floating plate 141. For example, the mass ratio of the floating plate 141 to the compressor 21 may be 0.1, 0.2, 0.3, 0.4, 0.5, 0.6, etc.

In some embodiments, the mass ratio of the floating plate 141 to the compressor 21 ranges from 0.1 to 0.4, which can better improve the vibration damping effect of the entire vibration damping structure 14 and better ensure mass of the floating plate 141 to be appropriate, reducing the production costs of the floating plate 141. For example, when the mass ratio of the floating plate 141 to the compressor 21 is 0.15, the vibration damping effect of the entire vibration damping structure 14 can be better, and the mass of the floating plate 141 can be ensured to be more appropriate.

According to some embodiments of the present disclosure, a ratio of static stiffness of the first vibration damping member 142 to static stiffness of the second vibration damping member 143 ranges from 0.6 to 1.5. If the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 is too large, the vibration damping effects of the first vibration damping member 142 and the second vibration damping member 143 are poor, reducing the vibration damping effect of the entire vibration damping structure 14. If the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 is too small, the stability of the first vibration damping member 142 and the second vibration damping member 143 is poor, making them prone to damage and reducing a service life of the vibration damping structure 14.

Therefore, the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 ranges from 0.6 to 1.5, which can improve the vibration damping effect of the entire vibration damping structure 14 and prevent the first vibration damping member 142 and the second vibration damping member 143 from being damaged, guaranteeing normal service performance of the vibration damping structure 14. For example, the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 may be 0.6, 1, 1.2, 1.5, etc.

In some embodiments, the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 ranges from 0.8 to 1.2, which can better improve the vibration damping effect of the entire vibration damping structure 14 and better prevent the first vibration damping member 142 and the second vibration damping member 143 from being damaged, guaranteeing the normal service performance of the vibration damping structure 14. For example, the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 is 1.0, the vibration damping effect of the entire vibration damping structure 14 can be better, and the normal use of the vibration damping structure 14 can be better guaranteed.

According to some embodiments of the present disclosure, a damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 ranges from 0.01 to 0.7. If the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 is too large, the vibration isolation effect of the vibration damping structure 14 is poor when the compressor 21 is operating. If the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 is too small, the vibration amplitude of the floating plate 141 is too large, resulting in failure of the first vibration damping member 142 and the second vibration damping member 143. Therefore, the vibration damping structure 14 is damaged, which does not have the vibration damping effect.

Therefore, the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 ranges from 0.01 to 0.7, which can improve the vibration damping effect of the entire vibration damping structure 14 and avoid the failure of the first vibration damping member 142 and the second vibration damping member 143, guaranteeing the normal service performance of the vibration damping structure 14. For example, the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 may be 0.01, 0.2, 0.5, 0.7, etc.

In some embodiments, the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 ranges from 0.05 to 0.2, which can improve the vibration damping effect of the entire vibration damping structure 14 and better avoid the failure of the first vibration damping member 142 and the second vibration damping member 143, guaranteeing the normal service performance of the vibration damping structure 14. For example, when the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 is 0.05, the vibration damping effect of the entire vibration damping structure 14 can be better, and the normal use of the vibration damping structure 14 can be better guaranteed.

According to some embodiments of the present disclosure, static displacement of each of the first vibration damping member 142 and the second vibration damping member 143 is smaller than 2.5 mm, and the static displacement is a maximum deformation amount of the corresponding vibration damping member in an up-down direction. Since both the first vibration damping member 142 and the second vibration damping member 143 have a certain degree of elasticity, when the compressor assembly 20 is stationary, the first vibration damping member 142 and the second vibration damping member 143 are deformed under action of gravity of the compressor assembly 20, and the static displacement is the maximum deformation amount of the first vibration damping member 142 and the second vibration damping member 143 in the up-down direction. If the static displacement of each of the first vibration damping member 142 and the second vibration damping member 143 is greater than 2.5 mm, the stability of the entire compressor assembly 20 is poor, which makes the vibration amplitude of the compressor assembly 20 large, easily causing problems such as failure of the first vibration damping member 142 and the second vibration damping member 143. Therefore, the static displacement of each of the first vibration damping member 142 and the second vibration damping member 143 is smaller than 2.5 mm, which can make the vibration damping and noise reduction effects of the first vibration damping member 142 and the second vibration damping member 143 on the compressor assembly 20 better and avoid the problems such as the failure of the first vibration damping member 142 and the second vibration damping member 143, guaranteeing the normal use of the first vibration damping member 142 and the second vibration damping member 143.

According to some embodiments of the present disclosure, as illustrated in FIG. 8, the soundproof hood 25 is supported on and connected to the floating plate 141. Since the second vibration damping member 143 is disposed between the floating plate 141 and the base 16, when the compressor assembly 20 is operating, the compressor assembly 20 transmits the vibration to the soundproof hood 25, and the vibration transmitted to the base 16 by the soundproof hood 25 can be attenuated by the second vibration damping member 143, which can prevent the vibration of the compressor assembly 20 from being directly transmitted to the base 16 through the soundproof hood 25, improving the overall vibration damping and noise reduction effect on the compression assembly.

According to some embodiments of the present disclosure, as illustrated in FIG. 20, the damping particles 253 are filled in a space defined by the soundproof hood 25 and the floating plate 141, and the damping particle 253 can play a vibration damping and noise reduction role in the compressor assembly 20. The damping particles 253 are filled in the space defined by the soundproof hood 25 and the floating plate 141, which can improve the overall vibration damping and noise reduction effect on the compressor assembly 20.

When the compressor assembly 20 is operating, on the one hand, the vibration generated by the compressor assembly 20 can be transmitted to the damping particle 253, and the damping particles 253 between the soundproof hood 25 and the compressor assembly 20 can collide and rub against each other. In this way, the vibrational mechanical energy of the compressor assembly 20 can be converted into heat energy and dissipated through the soundproof hood 25, attenuating the vibration of the compressor assembly 20 and reducing operating noise of the compressor assembly 20. On the other hand, the damping particle 253 surrounds an outer circumferential wall of the compressor assembly 20, which can attenuate the vibration amplitude of the compressor assembly 20, reducing the operating noise of the compressor assembly 20. In addition, because the damping particle 253 surrounds a vibration source, sound waves of the vibration noise pass through the damping particle 253 and then propagate to the external environment during a transmission process. The damping particle 253 weakens the sound waves, reducing the energy of the sound waves and further reducing the operating noise of the compressor assembly 20.

According to some embodiments of the present disclosure, a second sealing structure is disposed between the soundproof hood 25 and the floating plate 141 to seal an assembly gap between the soundproof hood 25 and the floating plate 141, which can prevent the damping particle 253 in the soundproof hood 25 from leaking, better ensuring the vibration damping and noise reduction effect of the damping particle 253 on the compressor assembly 20 and prevent the vibration and noise in the soundproof hood 25 from leaking from the assembly gap, affecting the overall vibration damping and noise reduction effect.

According to some embodiments of the present disclosure, as illustrated in FIG. 20, an equivalent diameter of the damping particle 253 is smaller than 3 mm, which can well achieve mutual friction between a plurality of damping particles 253. In this way, vibrational kinetic energy of the compressor assembly 20 can be converted into frictional heat energy and dissipated through the soundproof hood 25, which can slow down the vibration of the compressor assembly 20 and reduce the operating noise of the compressor assembly 20. Also, an air gap between the plurality of damping particles 253 can be made smaller, in such a manner that the plurality of damping particles 253 can better weaken the sound waves, improving the overall noise reduction effect.

According to some embodiments of the present disclosure, as illustrated in FIG. 7 to FIG. 8, the outdoor unit 100 further includes a water-circuit heat-exchange assembly 40 including a water-circuit heat exchanger 51. The water-circuit heat exchanger 51 has a water flow passage and a refrigerant flow passage that exchange heat with each other. The refrigerant flow passage of the water-circuit heat exchanger 51 can be connected to the compressor assembly 20, and the refrigerant in the refrigerant flow passage can exchange heat with the water flow in the water flow passage, allowing the water-circuit heat exchanger 51 to provide heating or cooling for the water flow. The water-circuit heat-exchange assembly 40 can regulate the temperature of the passing water flow, allowing the entire unit to provide heating or cooling for the water flow. The water flow flowing out of the water-circuit heat exchanger 51 can be transported to the room to regulate the temperature of indoor domestic water or the indoor temperature.

The water-circuit heat exchanger 51 is directly or indirectly supported on the floating plate 141. The compressor assembly 20 can be connected to the refrigerant flow passage of the water-circuit heat exchanger 51 through a pipeline, and the vibration and noise generated by the compressor assembly 20 during operation are transmitted to the water-circuit heat exchanger 51 through the pipeline. If the water-circuit heat exchanger 51 is directly disposed at the base 16, the vibration and noise of the water-circuit heat exchanger 51 are directly transmitted to the base 16, resulting in relatively large vibration and noise of the entire unit.

Since the second vibration damping member 143 is disposed between the floating plate 141 and the base 16, the water-circuit heat exchanger 51 is directly or indirectly supported on the floating plate 141. In this way, the vibration transmitted from the water-circuit heat exchanger 51 to the base 16 can be attenuated by the second vibration damping member 143, improving the vibration damping and noise reduction effect of the vibration damping structure 14 on the entire unit. In addition, since the compressor assembly 20 is disposed at the floating plate 141, and the water-circuit heat exchanger 51 is directly or indirectly supported on the floating plate 141, the distance between the water-circuit heat exchanger 51 and the compressor assembly 20 at the floating plate 141 can be shortened, facilitating the connection between the water-circuit heat exchanger 51 and the compressor assembly 20.

For example, the water-circuit heat exchanger 51 can be directly supported on the floating plate 141 through the fastener, which can improve structural strength and rigidity of a joint between the water-circuit heat exchanger 51 and the floating plate 141 and ensure stability and reliability of connection between the water-circuit heat exchanger 51 and the floating plate 141, achieving a vibration damping effect on the water-circuit heat exchanger 51.

For example, the water-circuit heat exchanger 51 can be indirectly supported on the floating plate 141 through the mounting support 26 for rigid connection, which can improve the stability and reliability of the connection between the water-circuit heat exchanger 51 and the floating plate 141 and facilitate the overall reasonable layout.

According to some embodiments of the present disclosure, as illustrated in FIG. 7 and FIG. 8, the soundproof hood 25 is supported on and connected to the floating plate 141. Since the second vibration damping member 143 is disposed between the floating plate 141 and the base 16, when the compressor assembly 20 is operating, the compressor assembly 20 transmits the vibration to the soundproof hood 25, and the vibration transmitted from the soundproof hood 25 to the base 16 can be attenuated by the second vibration damping member 143, which can prevent the vibration of the compressor assembly 20 from being directly transmitted to the base 16 through the soundproof hood 25, improving the vibration damping and noise reduction effect on the compression assembly.

The water-circuit heat exchanger 51 is located outside the soundproof hood 25 and fixed to the soundproof hood 25, in such a manner that the water-circuit heat exchanger 51 can be indirectly supported on and connected to the floating plate 141 through the soundproof hood 25. Since the second vibration damping member 143 is disposed between the floating plate 141 and the base 16, the vibration transmitted from the water-circuit heat exchanger 51 to the base 16 can be attenuated by the second vibration damping member 143, improving the vibration damping and noise reduction effect of the vibration damping structure 14 on the entire unit. Also, the distance between the water-circuit heat exchanger 51 and the compressor assembly 20 can be shortened, which facilitates the connection between the water-circuit heat exchanger 51 and the compressor assembly 20.

For example, the water-circuit heat exchanger 51 can be rigidly connected to the soundproof hood 25 through the mounting support 26, which can improve the structural strength and rigidity of the joint between the water-circuit heat exchanger 51 and the soundproof hood 25 and ensure the stability and reliability of the connection between the water-circuit heat exchanger 51 and the soundproof hood 25.

According to some embodiments of the present disclosure, as illustrated in FIG. 6, the outdoor unit 100 further includes an auxiliary fixing assembly 60 detachably connected to the outdoor unit casing 10 and the floating plate 141 to fix the floating plate 141 relative to the outdoor unit casing 10. Since the second vibration damping member 143 is disposed between the floating plate 141 and the base 16, and the second vibration damping member 143 has a certain degree of elasticity, the floating plate 141 is elastically or flexibly connected to the base 16. Therefore, during transportation of the entire unit, the compressor assembly 20 shakes, and the floating plate 141 also shakes along with the compressor 21 by disposing the floating plate 141 at a bottom surface of the compressor 21. During the transportation, if the auxiliary fixing assembly 60 is not disposed, excessive shaking of the floating plate 141 can cause failure of the second vibration damping member 143, resulting in damage to the vibration damping structure 14 and affecting the overall vibration damping and noise reduction effect.

In this way, by fixing the floating plate 141 relative to the outdoor unit casing 10 through the auxiliary fixing assembly 60, the problem of failure of the second vibration damping member 143 caused by severe shaking of the floating plate 141 can be avoided, which can improve safety and reliability of the vibration damping structure 14 and guarantee the vibration and noise reduction effect of the vibration damping structure 14 on the compressor assembly 20. For example, during transportation of the outdoor unit 100, the auxiliary fixing assembly 60 needs to be mounted to improve the safety and reliability of the vibration damping structure 14. When the outdoor unit 100 is operating, the auxiliary fixing assembly 60 needs to be removed to ensure normal use of the vibration damping structure 14.

According to some embodiments of the present disclosure, as illustrated in FIG. 6, the outdoor unit 100 further includes the auxiliary fixing assembly 60 detachably connected to the compressor 21 and the floating plate 141 to fix the compressor 21 relative to the floating plate 141. Since the first vibration damping member 142 is disposed between the compressor 21 and the floating plate 141, and the first vibration damping member 142 has a certain degree of elasticity, the compressor 21 is elastically or flexibly connected to the floating plate 141. Therefore, the compressor assembly 20 shakes during the transportation of the entire unit. During the transportation, if the auxiliary fixing assembly 60 is not disposed, excessive shaking of the compressor can cause failure of the first vibration damping member 142, resulting in the damage to the vibration damping structure 14, and affecting the overall vibration damping and noise reduction effect. In addition, the compressor assembly 20 is connected to the refrigerant pipeline. Therefore, the excessive shaking of the compressor assembly 20 can cause breaking of the refrigerant pipeline connected to the compressor assembly 20, affecting the normal use of the entire unit.

In this way, by fixing the compressor 21 relative to the floating plate 141 through the auxiliary fixing assembly 60, the problem of failure of the first vibration damping member 142 due to severe shaking of the compressor assembly 20 can be avoided, which can improve the safety and reliability of the vibration damping structure 14 and guarantee the vibration and noise reduction effect of the vibration damping structure 14 on the compressor assembly 20. Also, the refrigerant pipeline connected to the compressor assembly 20 can be prevented from breaking, ensuring the normal use of the entire unit. For example, during the transportation of the outdoor unit 100, the auxiliary fixing assembly 60 needs to be mounted to improve the safety and reliability of the vibration damping structure 14. When the outdoor unit 100 is operating, the auxiliary fixing assembly 60 needs to be removed to ensure the normal use of the vibration damping structure 14.

According to some embodiments of the present disclosure, as illustrated in FIG. 6, the auxiliary fixing assembly 60 includes at least one of a bolt 7 and a fixing support 8. For example, the auxiliary fixing assembly 60 may include the bolt 7 or the fixing support 8, or the auxiliary fixing assembly 60 may include the bolt 7 and the fixing support 8. The bolt 7 is adapted to be threadedly connected to the floating plate 141 and the base 16 of the outdoor unit casing 10. By fixing the floating plate 141 relative to the base 16 through the bolt 7, advantages such as simple structure, reliable connection, and easy disassembly and mounting can be provided.

The fixing support 8 includes a fixing plate 81 and a connection plate 82 that are connected to each other, the connection plate 82 is detachably connected to the base 16 of the outdoor unit casing 10, and the fixing plate 81 is directly or indirectly pressed above the floating plate 141 to press the floating plate 141. In this way, when the fixing support 8 is used as a whole, the fixing plate 81 can play a position-limiting role on the floating plate 141 and the compressor 21, and the connection between the connection plate 82 and the base 16 can achieve a fixing effect on the entire fixing support 8, allowing the fixing support 8 to achieve a better fixing effect on the floating plate 141, and guaranteeing the safety and reliability of the vibration damping structure 14. In addition, the connection plate 82 is detachably connected to the base 16, which can facilitate the mounting and disassembly of the fixing support 8.

The fixing plate 81 may have a groove 811. When the fixing support 8 is used as a whole, each of the first fastener 1441 between the floating plate 141 and the compressor 21 and the second fastener 1451 between the floating plate 141 and the base 16 can be partially received in the groove 811, in such a manner that movement of the floating plate 141 and the compressor 21 in a horizontal direction can be better limited, ensuring the safety and reliability of the vibration damping structure 14. For example, the fixing support 8 may be formed from one single piece, which can improve structural strength and rigidity of a joint between the fixing plate 81 and the connection plate 82 and avoid breaking of the fixing support 8 due to stress concentration.

For example, the fixing plate 81 is directly pressed against the floating plate 141 to compress the floating plate 141 downward, or the fixing plate 81 can be pressed against a bottom of the compressor, in such a manner that the bottom of the compressor presses the floating plate 141, allowing the fixing plate 81 to be indirectly pressed against the floating plate 141 to compress the floating plate 141.

According to some embodiments of the present disclosure, as illustrated in FIG. 21 and FIG. 22, an air return pipe 221 connected to the compressor assembly 20 includes a plurality of U-shaped segments connected sequentially, and the plurality of U-shaped segments includes an even number of U-shaped segments. When the compressor assembly 20 is operating, the vibration of the liquid reservoir 22 is transmitted to the air return pipe 221, and the vibration of the air return pipe 221 is in turn transmitted to other components, enabling the entire unit to generate relatively large low-frequency noise. By setting the air return pipe 221 into a plurality of U-shaped pipes that are connected to each other, flexibility and structural damping of the air return pipe 221 can be increased, which can effectively reduce a natural frequency of the air return pipe 221 and attenuate a vibration rate transmitted from the compressor 21 and the liquid reservoir 22 to other components through the air return pipe 221, achieving the vibration damping and noise reduction effect.

For example, the air return pipe 221 of the compressor assembly 20 has an end connected to an air return port 222 of the liquid reservoir 22 and another end connected to a four-way valve 27 located above the air return pipe 221. The plurality of U-shaped segments includes the even number of U-shaped segments, which can guarantee normal connection between the air return pipe 221 and each of the liquid reservoir 22 and the four-way valve 27 and effectively attenuate the vibration transmitted from the air return pipe 221 to the other components, achieving the overall vibration damping and noise reduction effect. For example, the number of U-shaped segments may be 2, 4, 6, etc.

According to some embodiments of the present disclosure, as illustrated in FIG. 21, the plurality of U-shaped segments includes four U-shaped segments, which can more effectively attenuate the vibration transmitted from the air return pipe 221 to the other components, and achieve a better overall vibration damping and noise reduction effect. Also, overall size can be guaranteed, and the air return pipe 221 can be prevented from occupying more space, saving costs.

According to some embodiments of the present disclosure, as illustrated in FIG. 21 and FIG. 22, the air return pipe 221 connected to the compressor assembly 20 includes the plurality of U-shaped segments connected sequentially. When the compressor assembly 20 is operating, the vibration of the liquid reservoir 22 is transmitted to the air return pipe 221, and the vibration of the air return pipe 221 is in turn transmitted to the other components, enabling the entire unit to generate the relatively large low-frequency noise. By setting the air return pipe 221 into the plurality of U-shaped pipes that are connected to each other, the flexibility and structural damping of the air return pipe 221 can be increased, which can effectively reduce the natural frequency of the air return pipe 221 and attenuate the vibration rate transmitted from the compressor 21 and the liquid reservoir 22 to the other components through the air return pipe 221, achieving the vibration damping and noise reduction effect.

The compressor assembly 20 includes the compressor 21 and the liquid reservoir 22. A third reference circle is defined with a center at an air discharge port 212 of the compressor 21 and a radius of R1, and R1 is greater than a radius of the compressor 21 with a difference ranging from 20 mm to 225 mm. A fourth reference circle is defined with a center at an air return port 222 of the liquid reservoir 22 and a radius of R2, and R2 is greater than a radius of the liquid reservoir 22 with a difference ranging from 20 mm to 200 mm. Projections of the plurality of U-shaped segments of the air return pipe 221 in a horizontal plane are at least partially located in a region where the third reference circle overlaps the fourth reference circle. Such an arrangement can make distance between the plurality of U-shaped segments of the air return pipe 221 and both the compressor 21 and the liquid reservoir 22 relatively short and prevent the air return pipe 221 from interfering with the compressor 21 and the liquid reservoir 22, affecting the normal use of the air return pipe 221. When the compressor 21 and the liquid reservoir 22 vibrate, the plurality of U-shaped segments of the air return pipe 221 can be made more stable and the vibration amplitude can be smaller, ensuring the vibration damping and noise reduction effect on the compressor assembly 20. In addition, such the arrangement can not only make the structure of the entire compressor assembly 20 more compact, improving the overall space utilization rate, but also avoid the air return pipe 221 from interfering with the compressor 21 or the liquid reservoir 22, affecting the use of the compressor assembly 20.

According to some embodiments of the present disclosure, as illustrated in FIG. 22 and FIG. 23, an air return pipe 221 connected to the compressor assembly 20 includes a plurality of U-shaped segments connected sequentially and a vertical segment. The vertical segment is connected between two adjacent U-shaped segments of the plurality of U-shaped segments, and at least part of the vertical segment is a corrugated pipe or a rubber hose 2211. For example, part of the vertical segment is the corrugated pipe or the rubber hose 2211 or the entire vertical segment is the corrugated pipe or the rubber hose 2211. When the compressor assembly 20 is operating, the vibration of the liquid reservoir 22 is transmitted to the air return pipe 221, and the vibration of the air return pipe 221 is in turn transmitted to the other components, enabling the entire unit to generate the relatively large low-frequency noise. By setting the air return pipe 221 into the plurality of U-shaped pipes that are connected to each other, the flexibility and structural damping of the air return pipe 221 can be increased, which can effectively reduce the natural frequency of the air return pipe 221 and attenuate the vibration rate transmitted from the compressor 21 and the liquid reservoir 22 to the other components through the air return pipe 221, achieving the vibration damping and noise reduction effect.

The corrugated pipe or the rubber hose 2211 each has a certain degree of elasticity. When the vibration is transmitted to the vertical segment, the corrugated pipe or the rubber hose 2211 can attenuate the vibration of the vertical segment, reducing the vibration of the entire air return pipe 221 and achieving the overall vibration damping and noise reduction effect.

According to some embodiments of the present disclosure, as illustrated in FIG. 22 and FIG. 23, the corrugated pipe has a length ranging from 150 mm to 450 mm; or the rubber hose 2211 has a length ranging from 150 mm to 450 mm. If the length of the corrugated pipe or the rubber hose 2211 is too long, the structural strength and rigidity of the entire air return pipe 221 is poor, making it prone to damage during use. If the length of the corrugated pipe or the rubber hose 2211 is too short, the vibration damping and noise reduction effect of the corrugated pipe or the rubber hose 2211 on the vertical segment of the air return pipe 221 is reduced. Therefore, when the length of the corrugated pipe ranges from 150 mm to 450 mm, or when the length of the rubber hose 2211 ranges from 150 mm to 450 mm, the vibration damping and noise reduction effect of the corrugated pipe or the rubber hose 2211 on the vertical segment of the air return pipe 221 can be better guaranteed, and the structural strength and rigidity of the entire air return pipe 221 can be guaranteed.

According to some embodiments of the present disclosure, at least part of the air return pipe 221 connected to the compressor assembly 20 is a metal pipe. For example, a part of the air return pipe 221 is the metal pipe or the entire air return pipe 221 is the metal pipe. At least part of the metal pipe is sleeved with a vibration-damping rubber sleeve or provided with a counterweight block. For example, a part of the metal pipe may be sleeved with the vibration-damping rubber sleeve or provided with the counterweight block. When the compressor assembly 20 is operating, the vibration of the liquid reservoir 22 is transmitted to the air return pipe 221, and the vibration of the air return pipe 221 is in turn transmitted to the other components, causing the entire unit to generate the relatively large low-frequency noise. The air return pipe 221 is sleeved with the vibration-damping rubber sleeve or provided with the counterweight block, which can attenuate the vibration of the air return pipe 221, achieving the vibration damping and noise reduction effect of the entire unit on the air return pipe 221.

A heating and ventilation apparatus according to some embodiments of the present disclosure includes the outdoor unit 100 according to some above-described embodiments of the present disclosure. The heating and ventilation apparatus may be an air conditioning system, a heat pump system, etc.

With the heating and ventilation apparatus of the present disclosure, by setting the above-described outdoor unit 100, by allowing at least part of the first partition plate 113 to form the part of the soundproof hood 25, the costs of the entire soundproof hood 25 can be saved, and the mounting space of the soundproof hood 25 can be reduced, making the structure of the entire unit more compact and improving the overall space utilization rate. In addition, at least one of the first hood plate 2523 and the second hood plate 2524 is independent of the outdoor unit casing 10, which can make the soundproof hood 25 independent of the outdoor unit casing 10, preventing the noise in the soundproof hood 25 from being directly transmitted to the outdoor unit casing 10. In this way, the soundproof and noise reduction effect of the entire unit on the compressor assembly 20 can be better ensured.

As illustrated in FIG. 1 to FIG. 8 and FIG. 20, an outdoor unit 100 according to some embodiments of the present disclosure includes: an outdoor unit casing 10, an outdoor heat exchanger 112, an outdoor fan 111, a compressor assembly 20, and a vibration damping structure 14.

The outdoor heat exchanger 112 and the outdoor fan 111 are disposed in the fan chamber 10. The outdoor unit casing 10 has an outdoor air inlet 101 and an outdoor air outlet 102. The outdoor fan 111 is configured to drive outdoor air to enter the outdoor unit casing 10 through the outdoor air inlet 101 and exchange heat with the outdoor heat exchanger 112. The heat-exchanged air is discharged from the outdoor air outlet 102. The compressor assembly 20 is disposed in the outdoor unit casing 10 and includes the compressor 21. The compressor assembly 20 can play a role in compressing and driving a refrigerant in a refrigerant circuit.

The outdoor unit casing 10 includes the base 16. The vibration damping structure 14 is disposed between the bottom surface of the compressor assembly 20 and the base 16. The vibration-damping structure 14 can play the vibration damping role on the compressor assembly 20, reducing the overall noise. During the operation of the outdoor unit 100, the vibration transmitted from the compressor assembly 20 to the base 16 is attenuated by the vibration damping structure 14, reducing the vibration transmitted to the base 16. Therefore, the noise generated when the outdoor unit 100 is operating can be reduced, making the vibration and noise transmitted outward by the compressor assembly 20 relatively small.

With the outdoor unit 100 according to the embodiments of the present disclosure, by disposing the vibration damping structure 14 between the bottom surface of the compressor assembly 20 and the base 16, the vibration transmitted from the compressor assembly 20 to the base 16 can be reduced, reducing the noise generated when the outdoor unit 100 is operating.

According to some embodiments of the present disclosure, as illustrated in FIG. 2 to FIG. 4, the vibration damping structure 14 includes a floating plate 141 and a vibration damping assembly. The vibration damping assembly includes at least one of a first vibration damping member 142 and a second vibration damping member 143. For example, the vibration damping assembly includes the first vibration damping member 142, or the vibration damping assembly includes the second vibration damping member 143, or the vibration damping assembly includes the first vibration damping member 142 and the second vibration damping member 143. The vibration damping assembly can reduce the vibration transmitted from the compressor 21 to the base 16, reducing overall noise.

The floating plate 141 is located above the base 16. The first vibration damping member 142 is disposed between the compressor 21 and the floating plate 141, and the second vibration damping member 143 is disposed between the floating plate 141 and the base 16. When the compressor 21 vibrates, vibration of the compressor 21 can be first transmitted to the floating plate 141, and then transmitted to the base 16. When the vibration damping assembly includes the first vibration damping member 142, the first vibration damping member 142 disposed between the compressor 21 and the floating plate 141 can reduce the vibration of the compressor 21 during a process of transmitting the vibration of the compressor 21 to the floating plate 141. Reduced vibration is then transmitted from the floating plate 141 to the base, in such a manner that the vibration of the compressor 21 can be attenuated during a process of transmitting to the base 16, achieving an overall vibration damping and noise reduction effect.

When the vibration damping assembly includes the second vibration damping member 143, the vibration of the compressor 21 can be first transmitted to the floating plate 141, and then transmitted from the floating plate 141 to the base. During the process of transmitting from the floating plate 141 to the base 16, the second vibration damping member 143 disposed between the floating plate 141 and the base 16 can reduce the vibration. Therefore, the vibration of the compressor 21 can be attenuated during the process of transmitting to the base 16, achieving the overall vibration damping and noise reduction effect.

When the vibration damping assembly includes the first vibration damping member 142 and the second vibration damping member 143, during the process of transmitting the vibration of the compressor 21 to the floating plate 141, the first vibration damping member 142 disposed between the compressor 21 and the floating plate 141 can reduce the vibration of the compressor 21 for the first time. During a process of transmitting the reduced vibration from the floating plate 141 to the base 16, the second vibration damping member 143 disposed between the floating plate 141 and the base 16 can reduce the vibration for the second time. In this way, the first vibration damping member 142 cooperates with the second vibration damping member 143, which can achieve secondary attenuation of the vibration of the compressor 21 during the process of transmitting to the base 16, achieving a better overall vibration damping and noise reduction effect.

For example, both the first vibration damping member 142 and the second vibration damping member 143 may be rubber members. The rubber member has a characteristic of high elasticity, which can allow both the first vibration damping member 142 and the second vibration damping member 143 to have a better vibration damping effect.

According to some embodiments of the present disclosure, as illustrated in FIG. 4, the compressor assembly 20 further includes a liquid reservoir 22 connected to the compressor 21. A projection of the compressor 21 in a horizontal plane is a first projection, a projection of the floating plate 141 in the horizontal plane is a second projection, and a projection of the liquid reservoir 22 in the horizontal plane is a third projection. The first projection is located within the second projection, and the third projection is at least partially located within the second projection. For example, part of the third projection is located within the second projection or the entire third projection is located within the second projection. Since the floating plate 141 supports the compressor assembly 20, such an arrangement enables most of the entire compressor assembly 20 to be located directly above the floating plate 141, which can shorten distance between a center of gravity of the entire compressor assembly 20 and a center of gravity of the floating plate 141. During the operation of the compressor assembly 20, a degree of eccentric shaking between the entire compressor assembly 20 and the floating plate 141 can be reduced, improving stability of the compressor assembly 20 and the floating plate 141 as a whole. Therefore, the vibration damping and noise reduction effect of the vibration damping structure 14 on the entire compressor assembly 20 can be made better.

In addition, it also allows the compressor assembly 20 and the floating plate 141 as a whole to have a lower center of gravity and a more stable overall structure. In this way, a vibration amplitude of the compressor assembly 20 and the floating plate 141 as a whole can be reduced, which can further reduce the vibration transmitted to the base 16, reducing the overall vibration and noise.

According to some embodiments of the present disclosure, as illustrated in FIG. 3 to FIG. 5, the floating plate 141 has an avoidance notch 1411. The avoidance notch 1411 can prevent the floating plate from interfering with other structures or components, which facilitates mounting and disassembly of the floating plate, ensuring normal use of the vibration damping structure. Moreover, the avoidance notch 1411 can make the overall structure more compact, which is conducive to improving the overall space utilization rate.

For example, the avoidance notch 1411 can be used to avoid the refrigerant pipeline between the compressor assembly 20 and other components, or the avoidance notch 1411 is used to avoid other structures at the base. When the avoidance notch 1411 is used to avoid the refrigerant pipeline, a certain spacing can be formed between the refrigerant pipeline and the floating plate 141 to avoid the refrigerant pipeline from contacting the floating plate 141. Therefore, the floating plate 141 can be prevented from transmitting the vibration of the compressor assembly 20 to the refrigerant pipeline, affecting the overall vibration damping and noise reduction effect. Also, a problem of damage to the refrigerant pipeline caused by friction between the floating plate 141 and the refrigerant pipeline due to the vibration of the compressor assembly 20 can be avoided, prolonging a service life of the refrigerant pipeline.

For example, the avoidance notch 1411 may be in a form of a groove, or a corner of the floating plate can be cut off to form an avoidance notch at a position where the corner is missing.

According to some embodiments of the present disclosure, as illustrated in FIG. 5, the compressor assembly 20 further includes a liquid reservoir 22 connected to the compressor 21. The floating plate 141 has a plurality of first mounting holes 144 for mounting of the compressor 21 and a plurality of second mounting holes 145 for mounting of the floating plate 141. For example, the compressor 21 can be fastened and connected to the floating plate 141 by a first fastener 1441 passing through the first mounting hole 144, which is structurally simple and facilitates mounting and disassembly the compressor 21. The first fastener 1441 can sequentially penetrate the compressor 21, the first vibration damping member 142, and the floating plate 141 in the up-down direction, which allows the first vibration damping member 142 to be fixed between the compressor 21 and the floating plate 141, attenuating the vibration transmitted from the compressor 21 to the floating plate 141. The floating plate 141 can be fastened and connected to the base 16 by a second fastener 1451 passing through the second mounting hole 145, which is structurally simple and facilitates mounting and disassembly of the floating plate 141. The second fastener 1451 can sequentially penetrate the floating plate 141, the second vibration damping member 143, and the base 16 in the up-down direction, which allows the second vibration damping member 143 to be fixed between the floating plate 141 and the base 16, attenuating the vibration transmitted from the floating plate 141 to the base 16. In this way, the first mounting hole 144 is used for mounting between the compressor 21 and the floating plate 141, and the second mounting hole 145 is used for mounting between the floating plate 141 and the base 16.

Centers of the plurality of first mounting holes 144 are located at a first reference circle a1, in such a manner that distances from the plurality of first mounting holes 144 to a center o1 of the first reference circle a1 can be the same. In addition, the plurality of first mounting holes 144 can be evenly arranged at intervals along a circumference of the first reference circle a1, which can allow the floating plate 141 to support the compressor 21 more stably. Centers of the plurality of second mounting holes 145 are located at a second reference circle a2, in such a manner that distances from the plurality of second mounting holes 145 to a center o2 of the second reference circle a2 can be the same. In addition, the plurality of second mounting holes 145 can be evenly arranged at intervals along a circumference of the second reference circle a2, which can allow the base 16 of the outdoor unit 100 to support the floating plate 141 more stably.

For example, the plurality of first mounting holes 144 may include three first mounting holes 144. The three first mounting holes 144 are evenly arranged at intervals along the circumference of the first reference circle a1, which can guarantee stability and reliability of connection between the compressor 21 and the floating plate 141. The plurality of second mounting holes 145 may include four second mounting holes 145. The four second mounting holes 145 are evenly arranged at intervals along the circumference of the second reference circle a2, which can improve stability and reliability of connection between the floating plate 141 and the base 16.

According to some embodiments of the present disclosure, as illustrated in FIG. 5, a projection of a center o2 of the second reference circle a2 in a reference plane is spaced apart from a projection of a center o1 of the first reference circle a1 in the reference plane, and the reference plane is parallel to a plane where an outer peripheral contour line of the base 16 is located. The center o2 of the second reference circle a2 is located at a side of the center o1 of the first reference circle a1 adjacent to the liquid reservoir 22. Since the liquid reservoir 22 is connected to the compressor 21, the floating plate 141 supports both the compressor 21 and the liquid reservoir 22. Usually, to stably mount the compressor 21 at the floating plate 141, a plurality of connection points (i.e., the plurality of first mounting holes 144 described above) between the compressor 21 and the floating plate 141 are evenly distributed and located at the same circle. Moreover, a projection of a center of the circle where the plurality of connection points between the compressor 21 and the floating plate 141 are located in the horizontal plane is roughly coincident with a projection of a center of the compressor 21 in the horizontal plane. However, a center of mass of the compressor assembly 20 including the liquid reservoir 22 deviates from the center of the compressor 21 and is located at a side of the center of the compressor 21 adjacent to the liquid reservoir 22.

By locating the center o2 of the second reference circle a2 at the side of the center o1 of the first reference circle a1 adjacent to the liquid reservoir 22, that is, allowing a mounting center of the floating plate 141 (that is, the center o2 of the second reference circle a2) to deviate from a mounting center of the compressor 21 (the center o1 of the first reference circle a1), and locating the mounting center of the floating plate 141 at a side of the mounting center of the compressor 21 adjacent to the liquid reservoir 22, a projection of the mounting center of the floating plate 141 in the horizontal plane can be made closer to a projection of the center of mass of the compressor assembly 20 in the horizontal plane. Therefore, the floating plate 141 can support the compressor assembly 20 more stably, which can improve a vibration isolation rate of the vibration damping structure 14.

According to some embodiments of the present disclosure, as illustrated in FIG. 3 to FIG. 5, the floating plate 141 has a plurality of second mounting holes 145 for mounting the floating plate 141, and centers of the plurality of second mounting holes 145 are located at the second reference circle a2, in such a manner that distances from the plurality of second mounting holes 145 to the center o2 of the second reference circle a2 can be the same, and the plurality of second mounting holes 145 can be evenly arranged at intervals along the circumference of the second reference circle a2.

Projections of a center of mass of the compressor assembly 20 and a center o2 of the second reference circle a2 in a reference plane are a first projection point and a second projection point, respectively, and the reference plane is parallel to a plane where an outer peripheral contour line of the base 16 is located. A spacing between the first projection point and the second projection point ranges from 0 mm to 5 mm. The compressor assembly 20 includes the compressor 21 and the liquid reservoir 22 connected to the compressor 21, and the entire compressor assembly 20 can be disposed at the floating plate 141 through the compressor 21. The spacing between the first projection point and the second projection point ranges from 0 mm to 5 mm, which can shorten distance between the projection of the center of mass of the compressor assembly 20 in the reference plane and a projection of the mounting center of the floating plate 141 (i.e., the center o2 of the second reference circle a2) in the reference plane, allowing the floating plate 141 to support the compressor assembly 20 more stably. Therefore, the vibration damping effect of the vibration damping structure 14 can be enhanced, improving the vibration isolation rate of the vibration damping structure 14.

The vibration damping effect of the entire vibration damping structure 14 becomes better, and the vibration isolation rate of the vibration damping structure 14 becomes higher as the spacing between the first projection point and the second projection point decreases. When the spacing between the first projection point and the second projection point is 0 mm, that is, the first projection point coincides with the second projection point, the vibration damping effect of the vibration damping structure 14 can be the best.

According to some embodiments of the present disclosure, as illustrated in FIG. 3 to FIG. 5, projections of a center of mass of the floating plate 141 and the center o2 of the second reference circle a2 in the reference plane are a third projection point and the second projection point, respectively, and a spacing between the third projection point and the second projection point ranges from 0 mm to 5 mm. Such an arrangement can shorten distance between the projection of the center of mass of the floating plate 141 in the reference plane and the projection of the mounting center of the floating plate 141 (i.e., the center o2 of the second reference circle a2) in the reference plane, allowing the floating plate 141 to support the compressor assembly 20 more stably. Therefore, the vibration damping effect of the vibration damping structure 14 is enhanced, improving the vibration isolation rate of the vibration damping structure 14.

The vibration damping effect of the entire vibration damping structure 14 becomes better, and the vibration isolation rate of the vibration damping structure 14 becomes higher as the spacing between the second projection point and the third projection point decreases. When the spacing between the second projection point and the third projection point is 0 mm, that is, the second projection point coincides with the third projection point, the vibration damping effect of the vibration damping structure 14 can be the best.

According to some embodiments of the present disclosure, as illustrated in FIG. 3 to FIG. 5, projections of a center of mass of the compressor assembly 20 and a center of mass of the floating plate 141 in the reference plane are a first projection point and a third projection point, respectively, and the reference plane is parallel to a plane where an outer peripheral contour line of the base 16 is located. A spacing between the first projection point and the third projection point ranges from 0 mm to 5 mm. Such an arrangement can make distance between the projection of the center of mass of the compressor assembly 20 in the reference plane and the projection of the center of mass of the floating plate 141 in the reference plane shorter, allowing the floating plate 141 to support the compressor assembly 20 more stably, and improving the stability of the compressor assembly 20 and the floating plate 141 as a whole. Therefore, the vibration damping effect of the vibration damping structure 14 is enhanced, improving the vibration isolation rate of the vibration damping structure 14.

The vibration damping effect of the entire vibration damping structure 14 becomes better, and the vibration isolation rate of the vibration damping structure 14 becomes higher as the spacing between the first projection point and the third projection point decreases. When the spacing between the first projection point and the third projection point is 0 mm, that is, the first projection point coincides with the third projection point, the vibration damping effect of the vibration damping structure 14 can be the best.

According to some embodiments of the present disclosure, a mass ratio of the floating plate 141 to the compressor 21 ranges from 0.1 to 0.6. A numerical unit of the mass of the floating plate 141 is consistent with a numerical unit of the mass of the compressor 21. If the mass ratio of the floating plate 141 to the compressor 21 is too small, when the compressor 21 is operating, the floating plate 141 vibrate to a large extent under the action of the compressor 21, making the vibration damping effect of the vibration damping structure 14 on the compressor assembly 20 poor. If the mass ratio of the floating plate 141 to the compressor 21 is too large, the mass of the floating plate 141 itself is too large, increasing the production costs of the floating plate 141, and making the mounting of the entire floating plate 141 inconvenient.

Therefore, when the mass ratio of the floating plate 141 to the compressor 21 ranges from 0.1 to 0.6, the vibration damping effect of the entire vibration damping structure 14 can be improved, and the mass of the floating plate 141 can be ensured to be appropriate, reducing the production costs of the floating plate 141. For example, the mass ratio of the floating plate 141 to the compressor 21 may be 0.1, 0.2, 0.3, 0.4, 0.5, 0.6, etc.

In some embodiments, the mass ratio of the floating plate 141 to the compressor 21 ranges from 0.1 to 0.4, which can better improve the vibration damping effect of the entire vibration damping structure 14 and better ensure mass of the floating plate 141 to be appropriate, reducing the production costs of the floating plate 141. For example, when the mass ratio of the floating plate 141 to the compressor 21 is 0.15, the vibration damping effect of the entire vibration damping structure 14 can be better, and the mass of the floating plate 141 can be ensured to be more appropriate.

According to some embodiments of the present disclosure, a ratio of static stiffness of the first vibration damping member 142 to static stiffness of the second vibration damping member 143 ranges from 0.6 to 1.5. If the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 is too large, the vibration damping effects of the first vibration damping member 142 and the second vibration damping member 143 are poor, reducing the vibration damping effect of the entire vibration damping structure 14. If the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 is too small, the stability of the first vibration damping member 142 and the second vibration damping member 143 is poor, making them prone to damage and reducing a service life of the vibration damping structure 14.

Therefore, the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 ranges from 0.6 to 1.5, which can improve the vibration damping effect of the entire vibration damping structure 14 and prevent the first vibration damping member 142 and the second vibration damping member 143 from being damaged, guaranteeing normal service performance of the vibration damping structure 14. For example, the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 may be 0.6, 1, 1.2, 1.5, etc.

In some embodiments, the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 ranges from 0.8 to 1.2, which can better improve the vibration damping effect of the entire vibration damping structure 14 and better prevent the first vibration damping member 142 and the second vibration damping member 143 from being damaged, guaranteeing the normal service performance of the vibration damping structure 14. For example, the ratio of the static stiffness of the first vibration damping member 142 to the static stiffness of the second vibration damping member 143 is 1.0, the vibration damping effect of the entire vibration damping structure 14 can be better, and the normal use of the vibration damping structure 14 can be better guaranteed.

According to some embodiments of the present disclosure, a damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 ranges from 0.01 to 0.7. If the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 is too large, the vibration isolation effect of the vibration damping structure 14 is poor when the compressor 21 is operating. If the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 is too small, the vibration amplitude of the floating plate 141 is too large, resulting in failure of the first vibration damping member 142 and the second vibration damping member 143. Therefore, the vibration damping structure 14 is damaged, which does not have the vibration damping effect.

Therefore, the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 ranges from 0.01 to 0.7, which can improve the vibration damping effect of the entire vibration damping structure 14 and avoid the failure of the first vibration damping member 142 and the second vibration damping member 143, guaranteeing the normal service performance of the vibration damping structure 14. For example, the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 may be 0.01, 0.2, 0.5, 0.7, etc.

In some embodiments, the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 ranges from 0.05 to 0.2, which can improve the vibration damping effect of the entire vibration damping structure 14 and better avoid the failure of the first vibration damping member 142 and the second vibration damping member 143, guaranteeing the normal service performance of the vibration damping structure 14. For example, when the damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 is 0.05, the vibration damping effect of the entire vibration damping structure 14 can be better, and the normal use of the vibration damping structure 14 can be better guaranteed.

According to some embodiments of the present disclosure, static displacement of each of the first vibration damping member 142 and the second vibration damping member 143 is smaller than 2.5 mm, and the static displacement is a maximum deformation amount of the corresponding vibration damping member in an up-down direction. Since both the first vibration damping member 142 and the second vibration damping member 143 have a certain degree of elasticity, when the compressor assembly 20 is stationary, the first vibration damping member 142 and the second vibration damping member 143 are deformed under action of gravity of the compressor assembly 20, and the static displacement is the maximum deformation amount of the first vibration damping member 142 and the second vibration damping member 143 in the up-down direction. If the static displacement of each of the first vibration damping member 142 and the second vibration damping member 143 is greater than 2.5 mm, the stability of the entire compressor assembly 20 is poor, which makes the vibration amplitude of the compressor assembly 20 large, easily causing problems such as failure of the first vibration damping member 142 and the second vibration damping member 143. Therefore, the static displacement of each of the first vibration damping member 142 and the second vibration damping member 143 is smaller than 2.5 mm, which can make the vibration damping and noise reduction effects of the first vibration damping member 142 and the second vibration damping member 143 on the compressor assembly 20 better and avoid the problems such as the failure of the first vibration damping member 142 and the second vibration damping member 143, guaranteeing the normal use of the first vibration damping member 142 and the second vibration damping member 143.

According to some embodiments of the present disclosure, as illustrated in FIG. 8, the compressor assembly 20 is externally covered by a soundproof hood 25. The compressor 21 radiates noise to the outside during operation. The soundproof hood 25 is disposed outside the compressor assembly 20, which can reduce the noise radiated to the outside by the compressor assembly 20 and provide a soundproof effect on the compressor assembly 20. The soundproof hood 25 is supported on and connected to the floating plate 141. Since the second vibration damping member 143 is disposed between the floating plate 141 and the base 16, when the compressor assembly 20 is operating, the compressor assembly 20 transmits the vibration to the soundproof hood 25, and the vibration transmitted to the base 16 by the soundproof hood 25 can be attenuated by the second vibration damping member 143, which can prevent the vibration of the compressor assembly 20 from being directly transmitted to the base 16 through the soundproof hood 25, improving the overall vibration damping and noise reduction effect on the compression assembly.

According to some embodiments of the present disclosure, as illustrated in FIG. 20, the damping particles 253 are filled in a space defined by the soundproof hood 25 and the floating plate 141, and the damping particles 253 can play a vibration damping and noise reduction role in the compressor assembly 20. The damping particles 253 are filled in the space defined by the soundproof hood 25 and the floating plate 141, which can improve the overall vibration damping and noise reduction effect on the compressor assembly 20.

When the compressor assembly 20 is operating, on the one hand, the vibration generated by the compressor assembly 20 can be transmitted to the damping particle 253, and the damping particles 253 between the soundproof hood 25 and the compressor assembly 20 can collide and rub against each other. In this way, the vibrational mechanical energy of the compressor assembly 20 can be converted into heat energy and dissipated through the soundproof hood 25, attenuating the vibration of the compressor assembly 20 and reducing operating noise of the compressor assembly 20. On the other hand, the damping particle 253 surrounds an outer circumferential wall of the compressor assembly 20, which can attenuate the vibration amplitude of the compressor assembly 20, reducing the operating noise of the compressor assembly 20. In addition, because the damping particle 253 surrounds a vibration source, sound waves of the vibration noise pass through the damping particle 253 and then propagate to the external environment during a transmission process. The damping particle 253 weakens the sound waves, reducing the energy of the sound waves and further reducing the operating noise of the compressor assembly 20.

According to some embodiments of the present disclosure, a second sealing structure is disposed between the soundproof hood 25 and the floating plate 141 to seal an assembly gap between the soundproof hood 25 and the floating plate 141, which can prevent the damping particle 253 in the soundproof hood 25 from leaking, better ensuring the vibration damping and noise reduction effect of the damping particle 253 on the compressor assembly 20 and prevent the vibration and noise in the soundproof hood 25 from leaking from the assembly gap, affecting the overall vibration damping and noise reduction effect.

According to some embodiments of the present disclosure, as illustrated in FIG. 20, an equivalent diameter of the damping particle 253 is smaller than 3 mm, which can well achieve mutual friction between a plurality of damping particles 253. In this way, vibrational kinetic energy of the compressor assembly 20 can be converted into frictional heat energy and dissipated through the soundproof hood 25, which can slow down the vibration of the compressor assembly 20 and reduce the operating noise of the compressor assembly 20. Also, an air gap between the plurality of damping particles 253 can be made smaller, in such a manner that the plurality of damping particles 253 can better weaken the sound waves, improving the overall noise reduction effect.

According to some embodiments of the present disclosure, as illustrated in FIG. 7 to FIG. 8, the outdoor unit 100 further includes a water-circuit heat-exchange assembly 40 including a water-circuit heat exchanger 51. The water-circuit heat exchanger 51 has a water flow passage and a refrigerant flow passage that exchange heat with each other. The refrigerant flow passage of the water-circuit heat exchanger 51 can be connected to the compressor assembly 20, and the refrigerant in the refrigerant flow passage can exchange heat with the water flow in the water flow passage, allowing the water-circuit heat exchanger 51 to provide heating or cooling for the water flow. The water-circuit heat-exchange assembly 40 can regulate the temperature of the passing water flow, allowing the entire unit to provide heating or cooling for the water flow. The water flow flowing out of the water-circuit heat exchanger 51 can be transported to the room to regulate the temperature of indoor domestic water or the indoor temperature.

The water-circuit heat exchanger 51 is directly or indirectly supported on the floating plate 141. The compressor assembly 20 can be connected to the refrigerant flow passage of the water-circuit heat exchanger 51 through a pipeline, and the vibration and noise generated by the compressor assembly 20 during operation are transmitted to the water-circuit heat exchanger 51 through the pipeline. If the water-circuit heat exchanger 51 is directly disposed at the base 16, the vibration and noise of the water-circuit heat exchanger 51 are directly transmitted to the base 16, resulting in relatively large vibration and noise of the entire unit.

Since the second vibration damping member 143 is disposed between the floating plate 141 and the base 16, the water-circuit heat exchanger 51 is directly or indirectly supported on the floating plate 141. In this way, the vibration transmitted from the water-circuit heat exchanger 51 to the base 16 can be attenuated by the second vibration damping member 143, improving the vibration damping and noise reduction effect of the vibration damping structure 14 on the entire unit. In addition, since the compressor assembly 20 is disposed at the floating plate 141, and the water-circuit heat exchanger 51 is directly or indirectly supported on the floating plate 141, the distance between the water-circuit heat exchanger 51 and the compressor assembly 20 at the floating plate 141 can be shortened, facilitating the connection between the water-circuit heat exchanger 51 and the compressor assembly 20.

For example, the water-circuit heat exchanger 51 can be directly supported on the floating plate 141 through the fastener, which can improve structural strength and rigidity of a joint between the water-circuit heat exchanger 51 and the floating plate 141 and ensure stability and reliability of connection between the water-circuit heat exchanger 51 and the floating plate 141, achieving a vibration damping effect on the water-circuit heat exchanger 51.

For example, the water-circuit heat exchanger 51 can be indirectly supported on the floating plate 141 through the mounting support 26 for rigid connection, which can improve the stability and reliability of the connection between the water-circuit heat exchanger 51 and the floating plate 141 and facilitate the overall reasonable layout.

According to some embodiments of the present disclosure, as illustrated in FIG. 7 and FIG. 8, the soundproof hood 25 is supported on and connected to the floating plate 141. Since the second vibration damping member 143 is disposed between the floating plate 141 and the base 16, when the compressor assembly 20 is operating, the compressor assembly 20 transmits the vibration to the soundproof hood 25, and the vibration transmitted from the soundproof hood 25 to the base 16 can be attenuated by the second vibration damping member 143, which can prevent the vibration of the compressor assembly 20 from being directly transmitted to the base 16 through the soundproof hood 25, improving the vibration damping and noise reduction effect on the compression assembly.

The water-circuit heat exchanger 51 is located outside the soundproof hood 25 and fixed to the soundproof hood 25, in such a manner that the water-circuit heat exchanger 51 can be indirectly supported on and connected to the floating plate 141 through the soundproof hood 25. Since the second vibration damping member 143 is disposed between the floating plate 141 and the base 16, the vibration transmitted from the water-circuit heat exchanger 51 to the base 16 can be attenuated by the second vibration damping member 143, improving the vibration damping and noise reduction effect of the vibration damping structure 14 on the entire unit. Also, the distance between the water-circuit heat exchanger 51 and the compressor assembly 20 can be shortened, which facilitates the connection between the water-circuit heat exchanger 51 and the compressor assembly 20.

For example, the water-circuit heat exchanger 51 can be rigidly connected to the soundproof hood 25 through the mounting support 26, which can improve the structural strength and rigidity of the joint between the water-circuit heat exchanger 51 and the soundproof hood 25 and ensure the stability and reliability of the connection between the water-circuit heat exchanger 51 and the soundproof hood 25.

The heating and ventilation apparatus according to some embodiments of the present disclosure includes: the outdoor unit 100 according to the above-described embodiments of the present disclosure. The heating and ventilation apparatus may be the air conditioning system, the heat pump system, etc.

With the heating and ventilation apparatus according to some embodiments of the present disclosure, by setting the above-described outdoor unit 100, by disposing the vibration damping structure 14 between the bottom surface of the compressor assembly 20 and the base 16, the vibration transmitted from the compressor assembly 20 to the base 16 can be reduced, reducing the noise generated when the outdoor unit 100 is operating.

An outdoor unit 100 according to an embodiment of the present disclosure is described in detail below with reference to FIG. 1 to FIG. 23.

As illustrated in FIG. 1 to FIG. 23, in this embodiment, the outdoor unit 100 includes an outdoor unit casing 10, an outdoor heat exchanger 112, an outdoor fan 111, a compressor assembly 20, a water-circuit heat-exchange assembly 40, a first electrical control box component 30, and a second electrical control box component 50. The outdoor unit casing 10 has an outdoor air inlet 101 and an outdoor air outlet 102. The outdoor unit casing 10 has a fan chamber 11, a compressor chamber 12, and a water-circuit chamber 13 that are arranged sequentially from left to right. The fan chamber 11 is spaced apart from the compressor chamber 12 in a left-right direction by a first partition plate 113, and the compressor chamber 12 is spaced apart from the water-circuit chamber 13 by a second partition plate 121. The first electrical control box component 30 is disposed at the first partition plate 113, and the second electrical control box component 50 is disposed at the second partition plate 121. Both the first electrical control box component 30 and the second electrical control box component 50 are placed perpendicular to the left-right direction.

The outdoor heat exchanger 112 and the outdoor fan 111 are disposed in the fan chamber 11. The outdoor heat exchanger 112 is located at left and rear sides of the outdoor fan 111. The outdoor fan 111 is an axial flow fan. The outdoor fan 111 can enable air in the fan chamber 11 to flow to an outside of the fan chamber 11, achieving a heat dissipation and cooling effect of the outdoor heat exchanger 112.

The first partition plate 113 is disposed between the fan chamber 11 and the compressor chamber 12. The first electrical control box component 30 is disposed at an upper side of the first partition plate 113, and the first electrical control box component 30 can be slidably mounted at the first partition plate 113 in an up-down direction. The first electrical control box component 30 includes a radiator. A first air guide hood 1131 is disposed at the first partition plate 113 and located at a top of the radiator. A first air guide chamber 1132 is defined by the first air guide hood 1131, the radiator, and the first partition plate 113. A second air guide hood 1134 is disposed at the first partition plate 113 and located at a bottom of the radiator.

The first partition plate 113 includes a first sub-partition plate 1136 and a second sub-partition plate 1137. The second sub-partition plate 1137 is located at a side of the first sub-partition plate 1136 adjacent to the compressor chamber 12 and includes a partition plate body 1137a and a partition plate flange 1137b connected to each of front and rear sides of the partition plate body 1137a. A second air guide chamber 1135 is defined by the second sub-partition plate 1137, the first sub-partition plate 1136, the second air guide hood 1134 and the radiator, and the partition plate flange 1137b has a second air guide opening 1139.

When the outdoor fan 111 is operating, the outdoor fan 111 drives the air to flow in the fan chamber 11, making air pressure in the fan chamber 11 lower than air pressure in the compressor chamber 12. Since the compressor chamber 12 is connected to a lower part of the radiator through the second air guide chamber 1135, and the radiator is disposed in the fan chamber, under action of an air pressure difference between the fan chamber 11 and the compressor chamber 12, the air in the compressor chamber 12 can enter the second air guide chamber 1135 from the second air guide opening 1139 at the partition plate flange 1137b, flow upward along the second air guide chamber 1135, flow to the bottom of the radiator and flow upward along the surface of the radiator, and finally enter the fan chamber 11 through the radiator. During flow of the air along the surface of the radiator, heat of the radiator is taken away, achieving a heat dissipation effect on the radiator, and dissipating heat from the first electrical control box component 30.

The compressor assembly 20 is disposed in the compressor chamber 12 and includes a compressor 21 and a liquid reservoir 22 connected to the compressor 21. The compressor assembly is externally covered by a soundproof hood 25 connected to a base 16. A soundproof chamber 254 configured to accommodate the compressor assembly 20 is defined between the soundproof hood 25 and the base 16 of the outdoor unit casing 10, and a vibration-damping pad is disposed between the soundproof hood 25 and the base 16. The first partition plate and the second partition plate form parts of left and right sides of the soundproof hood, respectively. The part of the first partition plate forming the soundproof hood is a soundproof portion 1137c.

The soundproof hood 25 includes a top cover 251, a first hood plate 2523, a second hood plate 2524, and a third hood plate 2525, and all parts of the soundproof hood 25 can be connected through fasteners. The first hood plate 2523 and the second hood plate 2524 are both flat-plate shaped, the first hood plate 2523 is connected to both the first partition plate 113 and the second partition plate 121, and the second hood plate 2524 is connected to both the first partition plate 113 and the second partition plate 121. The first hood plate 2523 is disposed at a front side of the second hood plate 2524. The third hood plate 2525 is disposed between the top cover 251 and the first partition plate 113, and a cross-sectional shape of the third hood plate 2525 is L-shaped. The front and rear sides of the third hood plate 2525 are connected to the first hood plate 2523 and the second hood plate 2524, respectively. A top of the third hood plate 2525 is connected to the top cover 251. A left side of the third hood plate 2525 is connected to an upper part of the soundproof portion 1137c of the first partition plate 113. An avoidance space 2526 for avoiding the first electrical control box component 30 is defined between the third hood plate 2525 and the first partition plate 113.

Flanges are disposed at the front and rear sides of the third hood plate 2525 and surrounding sides of the top cover 251, respectively, and the flange has a connection hole, in such a manner that both the third hood plate 2525 and the top cover 251 can be connected to other parts of the soundproof hood 25 through the fasteners.

The top cover 251 includes a first cover body 2511 and a second cover body 2512 that are connected in the left-right direction, or the top cover 251 is formed from one single piece. The top cover 251 has a pipeline outlet 2513 in which a first sealing structure 2514 is provided. A shape of the first sealing structure 2514 is the same as that of the pipeline outlet 2513, and the first sealing structure 2514 may be made of an elastic rubber material. When the top cover 251 is formed from one single piece, one pipeline outlet 2513 is provided for the top cover 251 and the pipeline outlet 2513 is U-shaped in shape, and a U-shaped opening of the pipeline outlet 2513 faces rearward. When the top cover 251 is divided into the first cover body 2511 and the second cover body 2512, the pipeline outlet 2513 is circular in shape, and two pipeline outlets 2513 are disposed at the top cover 251. When the top cover 251 is mounted, the pipeline outlet 2513 is defined by the first cover body 2511 and the second cover body 2512.

In other embodiments, the soundproof hood 25 is supported on and connected to the floating plate 141, and the soundproof hood 25 may be formed from one single piece. The compressor assembly 20 is located in a space defined by the soundproof hood 25 and the floating plate 141, and a damping particles 253 are filled in the space defined by the soundproof hood 25 and the floating plate 141. An equivalent diameter of each of the damping particles 253 is smaller than 3 mm. A second sealing structure is disposed between the soundproof hood 25 and the floating plate 141 to seal an assembly gap between the soundproof hood 25 and the floating plate 141.

A soundproof cotton layer 23 is disposed at each of an inner wall of the outdoor unit casing 10 that encloses the compressor chamber 12, an inner wall of the soundproof hood 25, an outer circumferential wall of the compressor assembly 20, an outer circumferential wall of the compressor 21, and an outer circumferential wall of the liquid reservoir 22. The soundproof cotton layer 23 may have a thickness ranging from 5 mm to 50 mm. The soundproof cotton layer 23 includes a sound absorption layer 231, a second damping layer 232, and a soundproof layer 233 that are stacked in sequence. The sound absorption layer 231, the second damping layer 232, and the soundproof layer 233 can form an integral soundproof cotton layer 23 by means of gluing or sewing. The sound absorption layer 231 is closest to a noise source, the soundproof layer 233 is the farthest from the noise source, and the second damping layer 232 is located between the sound absorption layer 231 and the soundproof layer 233. The sound absorption layer 231 may be a porous material layer and have a thickness ranging from 5 mm to 15 mm. The second damping layer 232 may be a rubber layer and have a thickness ranging from 2 mm to 6 mm. The soundproof layer 233 is a rubber layer or a plastic layer and may have a thickness ranging from 1 mm to 3 mm.

A support structure 24 is disposed between the soundproof cotton layer 23 and each of the outer circumferential wall of the compressor 21 and the outer circumferential wall of the liquid reservoir 22. The outer circumferential wall of the compressor 21 may be spaced apart from the soundproof cotton layer 23 disposed at the outer circumferential wall of the compressor 21 through the support structure 24, defining an air layer between the outer circumferential wall of the compressor 21 and the soundproof cotton layer 23. The support structure 24 enables a spacing between the outer circumferential wall of the compressor 21 and the soundproof cotton layer 23 to range from 5 mm to 20 mm. The support structure 24 disposed at the outer circumferential wall of the compressor 21 may include two support rings 241 that are spaced apart from each other in the up-down direction, and the two support rings 241 are disposed at upper and lower parts of the outer circumferential wall of the compressor 21, respectively. Alternatively, the support structure 24 disposed at the outer circumferential wall of the compressor 21 may include a plurality of support bars 242 and support blocks 243 that are evenly arranged at intervals in a circumferential direction of the compressor 21, and the plurality of support bars 242 may extend in the up-down direction.

The outer circumferential wall of the liquid reservoir 22 may be spaced apart from the soundproof cotton layer 23 disposed at the outer circumferential wall of the liquid reservoir 22 through the support structure 24, defining the air layer between the outer circumferential wall of the liquid reservoir 22 and the soundproof cotton layer 23. The support structure 24 enables a spacing between the outer circumferential wall of the liquid reservoir 22 and the soundproof cotton layer 23 to range from 5 mm to 20 mm. The support structure 24 disposed at the outer circumferential wall of the liquid reservoir 22 may include the two support rings 241 that are arranged at intervals in the up-down direction, and the two support rings 241 are disposed at the upper and lower parts of the outer circumferential wall of the liquid reservoir 22, respectively. Alternatively, the support structure 24 disposed at the outer circumferential wall of the liquid reservoir 22 may include the plurality of support bars 242 and support blocks 243 that are evenly arranged at intervals in a circumferential direction of the liquid reservoir 22, and the plurality of support bars 242 may extend in the up-down direction.

To make a sound absorption and soundproof effect of the entire compressor assembly 20 better, a layer of the soundproof cotton layer 23 can be firstly disposed at each of the outer circumferential wall of the compressor 21 and the outer circumferential wall of the liquid reservoir 22, and finally another layer of the soundproof cotton layer 23 can be disposed at the outer circumferential wall of the entire compressor assembly 20.

The soundproof cotton layer 23 may be spaced apart from the outer circumferential wall of the compressor 21 through the support structure 24, defining the air layer between the outer circumferential wall of the compressor 21 and the soundproof cotton layer 23. The support structure 24 enables the spacing between the outer circumferential wall of the compressor 21 and the soundproof cotton layer 23 to range from 5 mm to 20 mm. The support structure 24 may include the two support rings 241 that are arranged at intervals in the up-down direction, and the two support rings 241 are disposed at the upper and lower parts of the outer circumferential wall of the compressor 21, respectively. Alternatively, the support structure 24 may include the plurality of support bars 242 and support blocks 243 that are evenly arranged at intervals in the circumferential direction of the compressor 21, and the plurality of support bars 242 may extend in the up-down direction.

A vibration damping structure 14 is disposed between a bottom surface of the compressor assembly 20 and the base 16. The vibration damping structure 14 can reduce vibration transmitted from the compressor assembly 20 to the base 16, reducing overall noise. The vibration damping structure 14 includes the floating plate 141, a first vibration damping member 142, and a second vibration damping member 143. The floating plate 141 is located at a bottom surface of the compressor 21, the first vibration damping member 142 is disposed between the compressor 21 and the floating plate 141, and the second vibration damping member 143 is disposed between the floating plate 141 and the base 16. Each of the first vibration damping member 142 and the second vibration damping member 143 may be a rubber member. In other embodiments, the liquid reservoir 22 of the compressor assembly 20 is fixed to the base 16, which can reduce the vibration of the entire compressor assembly 20 and reduce the overall noise. The compressor 21 may be connected to the liquid reservoir 22 through a liquid receiving pipe 211.

A projection of the compressor 21 in a horizontal plane is a first projection, a projection of the floating plate 141 in the horizontal plane is a second projection, and a projection of the liquid reservoir 22 in the horizontal plane is a third projection. Both the first projection and the third projection are located in the second projection. The floating plate 141 has an avoidance notch 1411 formed at a right rear side and a left front side of the floating plate 141.

The floating plate 141 has three first mounting holes 144 for mounting of the compressor 21 and four second mounting holes 145 for mounting of the floating plate 141. Centers of the three first mounting holes 144 are located at a first reference circle a1, and the three first mounting holes 144 are evenly arranged at intervals along a circumference of the first reference circle a1. Centers of the four second mounting holes 145 are located at the second reference circle a2, and the four second mounting holes 145 are evenly arranged at intervals along the circumference of the second reference circle a2. The compressor 21 may be connected to the floating plate 141 through a first fastener 1441. The first fastener 1441 may sequentially penetrate the bottom of the compressor 21, the first vibration damping member 142, and the first mounting hole 144 of the floating plate 141 from top to bottom, in such a manner that the compressor 21 can be mounted at the floating plate 141. The floating plate 141 may be connected to the base 16 through a second fastener 1451. The second fastener 1451 may sequentially penetrate the second mounting hole 145 of the floating plate 141, the second vibration damping member 143, and the base 16 from top to bottom, in such a manner that the floating plate 141 can be mounted at the base 16.

A projection of a center o1 of the first reference circle a1 in a reference plane does not coincide with a projection of a center o2 of the second reference circle a2 in the reference plane, and the reference plane is parallel to a plane where an outer peripheral contour line of the base 16 is located. The center o2 of the second reference circle a2 is located at a side of the center o1 of the first reference circle a1 adjacent to the liquid reservoir 22. Projections of a center of mass of the compressor assembly 20, the center o2 of the second reference circle a2, and a center of mass of the floating plate 141 in the reference surface are a first projection point, a second projection point, and a third projection point, respectively. The first projection point, the second projection point, and the third projection point coincide, which can improve stability of the entire vibration damping structure 14 and ensure a vibration damping effect of the vibration damping structure 14.

A mass ratio of the floating plate 141 to the compressor 21 is 0.15, a ratio of stiffness of the first vibration damping member 142 to stiffness of the second vibration damping member 143 is 1.0, a damping ratio of each of the first vibration damping member 142 and the second vibration damping member 143 is 0.05, and a maximum deformation amount of the first vibration damping member 142 and a maximum deformation amount of the second vibration damping member 143 are each smaller than 2.5 mm in the up-down direction. In this way, a vibration damping effect of the entire vibration damping structure 14 can be better improved and the vibration of the entire compressor assembly 20 can be attenuated.

When the compressor assembly 20 is in an operating state, the compressor 21 generates significant vibration, and the vibration of the compressor 21 can be transmitted to the floating plate 141 and then to the base 16. During a process of transmitting the vibration of the compressor 21 to the floating plate 141, the first vibration damping member 142 disposed between the compressor 21 and the floating plate 141 can reduce the vibration of the compressor 21 for the first time. During a process of transmitting the reduced vibration from the floating plate 141 to the base 16, the second vibration damping member 143 disposed between the floating plate 141 and the base 16 can reduce the vibration for the second time. In this way, the first vibration damping member 142 cooperates with the second vibration damping member 143, which can achieve multiple attenuation of the vibration between the compressor 21 and the base 16, reducing the overall noise.

An air return pipe 221 connected to the compressor assembly 20 includes four U-shaped segments connected sequentially and a vertical segment. A third reference circle is defined with a center at an air discharge port 212 of the compressor 21 and a radius of R1, and R1 is greater than a radius of the compressor 21 with a difference ranging from 20 mm to 225 mm. A fourth reference circle is defined with a center at an air return port 222 of the liquid reservoir 22 and a radius of R2, and R2 is greater than a radius of the liquid reservoir 22 with a difference ranging from 20 mm to 200 mm. Projections of the four U-shaped segments of the air return pipe 221 in a horizontal plane are located in a region where the third reference circle overlaps the fourth reference circle. The vertical segment is connected between two adjacent U-shaped segments of the four U-shaped segments and is a corrugated pipe or rubber hose 2211. The corrugated pipe has a length ranging from 150 mm to 450 mm. Alternatively, the rubber hose 2211 has a length ranging from 150 mm to 450 mm. A part where the air return pipe 221 is a metal pipe may be sleeved with a vibration-damping rubber sleeve or provided with a counterweight block, which can attenuate the vibration of the air return pipe 221, achieving the vibration damping and noise reduction effect of the entire air return pipe 221.

A water-circuit heat-exchange assembly 40 is disposed in the water-circuit chamber 13 and includes a water-circuit heat exchanger 51, an electric heater 52, and a water pump 53. The water-circuit heat exchanger 51 is fixed at the second partition plate 121, and the water-circuit heat exchanger 51 has a water flow passage and a refrigerant flow passage that exchange heat with each other.

The refrigerant flow passage in the water-circuit heat exchanger 51 can be connected to the compressor assembly 20, and a refrigerant in the refrigerant flow passage can exchange heat with water flow in the water flow passage, allowing the water-circuit heat exchanger 51 to provide heating or cooling for the water flow. The water-circuit heat-exchange assembly 40 can regulate a temperature of passing water flow, allowing the entire unit to provide heating or cooling for the water flow. The water flow flowing out of the water-circuit heat exchanger 51 can be transported to the room to regulate an indoor temperature or the indoor temperature.

In other embodiments, to attenuate the vibration transmitted from the water-circuit heat exchanger 51 to the base 16 using the vibration damping structure 14, the vibration damping and noise reduction effect of the entire vibration damping structure 14 is improved. The water-circuit heat exchanger 51 may be directly or indirectly supported on the floating plate 141. The water-circuit heat exchanger 51 may be directly supported on the floating plate 141 through the fastener. Alternatively, the water-circuit heat exchanger 51 may be indirectly supported on the floating plate 141 through the mounting support 26. Alternatively, when the soundproof hood 25 is supported on and connected to the floating plate 141, the water-circuit heat exchanger 51 can be rigidly connected to the soundproof hood 25 through the mounting support 26, in such a manner that the water-circuit heat exchanger 51 is indirectly supported on the floating plate 141 through the soundproof hood 25.

The outdoor unit 100 further includes an auxiliary fixing assembly 60 detachably connected to the outdoor unit casing 10 and the floating plate 141 to fix the floating plate 141 relative to the outdoor unit casing 10, or the auxiliary fixing assembly 60 is detachably connected to the compressor 21 and the floating plate 141 to fix the compressor 21 relative to the floating plate 141. When the outdoor unit 100 is operating, the auxiliary fixing assembly 60 is removed. The auxiliary fixing assembly 60 includes a bolt 7 and a fixing support 8. The bolt 7 is adapted to be threadedly connected to the floating plate 141 and the base 16 of the outdoor unit casing 10. The fixing support 8 includes a fixing plate 81 and a connection plate 82 that are connected to each other, the connection plate 82 is detachably connected to the base 16 of the outdoor unit casing 10, and the fixing plate 81 is directly or indirectly pressed against the floating plate 141 to compress the floating plate 141 downward. The fixing plate 81 may have a groove 811. When the fixing support 8 is used as a whole, each of the first fastener 1441 between the floating plate 141 and the compressor 21 and the second fastener 1451 between the floating plate 141 and the base 16 can be partially received in the groove 811.

In the description of the present disclosure, it should be understood that the orientation or the position indicated by terms such as “center”, “longitudinal”, “transverse”, “length”, “width”, “thickness”, “over”, “below”, “front”, “rear”, “left”, “right”, “vertical”, “horizontal”, “top”, “bottom”, “inner”, “outer”, “clockwise”, “anti-clockwise”, “axial”, “radial”, and “circumferential” should be construed to refer to the orientation or the position as shown in the drawings, and is only for the convenience of describing the present disclosure and simplifying the description, rather than indicating or implying that the pointed device or element must have a specific orientation, or be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present disclosure.

In the description of the present disclosure, “plurality” means two or more.

In the description of the present disclosure, the first feature “above” the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply mean that the level of the first feature is higher than that of the second feature.

Reference throughout this specification to “an embodiment”, “some embodiments”, “schematic embodiments”, “an example”, “a specific example”, or “some examples” means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. In this specification, exemplary descriptions of aforesaid terms are not necessarily referring to the same embodiment or example. Further, the particular features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

Although embodiments of the present disclosure have been illustrated and described, it is conceivable for those of ordinary skill in the art that various changes, modifications, replacements, and variations can be made to these embodiments without departing from the principles and spirit of the present disclosure. The scope of the present disclosure shall be defined by the claims as appended and their equivalents.