EVAPORATOR AND REFRIGERATION DEVICE

Description

CROSS REFERENCE TO RELATED APPLICATIONS

The present application claims the benefit of Chinese Patent Application Nos. 2024205503858 filed on Mar. 20, 2024, 2024103216853 filed on Mar. 20, 2024, 202410554314X filed on May 6, 2024, 2024216537538 filed on Jul. 12, 2024 and 2024109380194 filed on Jul. 12, 2024. All the above are hereby incorporated by reference in their entirety.

TECHNICAL FIELD

The present disclosure relates to the technical field of refrigeration, and in particular to an evaporator and a refrigeration device.

BACKGROUND

As a heat exchanger, the evaporator is an important component in the refrigeration device. A condensed fluid at a low temperature exchanges heat with outside air through the evaporator, and is vaporized to absorb heat, thereby realizing a refrigeration effect. The evaporator in most existing refrigeration devices (such as a smoothie maker) includes a main body and a coil. The main body includes an inner housing and an outer housing. The coil is sleeved on the inner housing and comes in contact with a wall of the outer housing. The condensed fluid is charged to the coil. The condensed fluid exchanges heat with the outside through a wall of the coil and the wall of the outer housing of the main body, thereby realizing the refrigeration effect. However, according to the above structure, the heat is transferred through the wall of the coil and the wall of the outer housing of the main body. Due to various heat transfer media, the heat transfer efficiency is low, the whole structure is complex, and the cost is high.

SUMMARY

A technical problem to be solved by the present disclosure is to provide an evaporator and a refrigeration device. The present disclosure can improve heat transfer efficiency and cold conduction performance of the evaporator, and has a simple overall structure and a low production cost.

To solve the above-mentioned technical problem, the present disclosure provides an evaporator, including an evaporator housing, a condensate input tube, a gas-guide tube, and a refrigerant region, where the refrigerant region is provided around an inner wall of the evaporator housing; the refrigerant region and the evaporator housing enclose at least one refrigerant passage; and the refrigerant passage includes an input end connected to a condenser through the condensate input tube, and an output end connected to a compressor through the gas-guide tube.

As an improvement to the above solution, the refrigerant region includes a refrigerant housing and at least one spiral turbulator sheet; the refrigerant housing is hermetically connected to the evaporator housing; the spiral turbulator sheet is located between the refrigerant housing and the evaporator housing; and the spiral turbulator sheet, the refrigerant housing, and the evaporator housing enclose the at least one refrigerant passage.

As an improvement to the above solution, a heat-exchange member is provided between the evaporator housing and the refrigerant housing; the heat-exchange member includes a heat insulating body and the spiral turbulator sheet; the heat insulating body is sleeved on or embedded into the refrigerant housing; and the spiral turbulator sheet is protruded from a sidewall of the heat insulating body.

As an improvement to the above solution, when a side of the heat-exchange member away from the spiral turbulator sheet is located on the refrigerant housing, the spiral turbulator sheet extends toward the evaporator housing to form the refrigerant passage where a condensed fluid exchanges heat with outside air through the evaporator housing.

As an improvement to the above solution, when a side of the heat-exchange member away from the spiral turbulator sheet is located on the evaporator housing, the spiral turbulator sheet extends toward the refrigerant housing to form the refrigerant passage where a condensed fluid exchanges heat with outside air through the refrigerant housing.

As an improvement to the above solution, a plurality of spiral turbulator sheets are provided between the refrigerant housing and the evaporator housing; the refrigerant housing, the evaporator housing, and the plurality of spiral turbulator sheets enclose a plurality of refrigerant passages; the plurality of refrigerant passages are arranged in parallel; and the plurality of refrigerant passages are spaced apart by the spiral turbulator sheets.

As an improvement to the above solution, the spiral turbulator sheet is made of metal, plastic or silica gel.

As an improvement to the above solution, the heat-exchange member is made of plastic or silica gel; and the heat insulating body and the spiral turbulator sheet are an integrated structure or a split structure.

As an improvement to the above solution, an input tube opening and an output tube opening communicating with the refrigerant passage in one-to-one correspondence are respectively provided at two ends of the refrigerant housing; the condensate input tube communicates with the refrigerant passage through the input tube opening; and the gas-guide tube communicates with the refrigerant passage through the output tube opening.

As an improvement to the above solution, the refrigerant housing is provided with a plurality of middle input tube openings at intervals along a flow direction of the refrigerant passage; the middle input tube openings communicate with the refrigerant passage; the middle input tube openings are located between the input tube opening and the output tube opening; and the middle input tube openings each are connected to the condenser through a corresponding condensate input tube.

As an improvement to the above solution, an input tube opening and an output tube opening communicating with the refrigerant passage in one-to-one correspondence are respectively provided at two ends of the evaporator housing; the condensate input tube communicates with the refrigerant passage through the input tube opening; and the gas-guide tube communicates with the refrigerant passage through the output tube opening.

As an improvement to the above solution, the evaporator housing is provided with a plurality of middle input tube openings at intervals along a flow direction of the refrigerant passage; the middle input tube openings communicate with the refrigerant passage; the middle input tube openings are located between the input tube opening and the output tube opening; and the middle input tube openings each are connected to the condenser through a corresponding condensate input tube.

As an improvement to the above solution, one end of the refrigerant housing is provided with an outward extending limit ring; the limit ring is hermetically connected to one end of the evaporator housing; the other end of the evaporator housing away from the limit ring is provided with an inward extending support ring; and the support ring is hermetically connected to the other end of the refrigerant housing.

As an improvement to the above solution, the evaporator housing or the refrigerant housing has a diameter of A, and a thickness of B, the A being 60-100 mm, and the B being 0.5-1.2 mm; a width of the refrigerant passage is the same as a pitch of the spiral turbulator sheet; the spiral turbulator sheet has the pitch of C, a width of E, and a thickness of F, the C being 5-20 mm, the E being 2-10 mm, and the F being 0.4-2 mm; and a ratio of the thickness of the evaporator housing or the refrigerant housing to the pitch of the spiral turbulator sheet is G, the G satisfying 0.06≤G≤0.1.

As an improvement to the above solution, the A is 80-90 mm, the B is 0.8-1.0 mm, the C is 8-16 mm, the E is 5-8 mm, the F is 0.9-1.5 mm, and the G satisfies 0.0625≤G≤0.1.

As an improvement to the above solution, the refrigerant region includes at least one spiral raised member; the raised member is hermetically connected to the inner wall of the evaporator housing; and an inner chamber of the raised member and the evaporator housing enclose the at least one refrigerant passage.

As an improvement to the above solution, the refrigerant region includes a plurality of spiral raised members; inner chambers of the raised members and the evaporator housing enclose a plurality of refrigerant passages; the plurality of refrigerant passages are arranged in parallel; and the plurality of refrigerant passages are spaced apart by the raised members.

As an improvement to the above solution, the raised member and the inner wall of the evaporator housing are an integrally punch-formed structure; an input port and an output port communicating with the refrigerant passage in one-to-one correspondence are respectively provided at two ends of the raised member at intervals; the condensate input tube communicates with the refrigerant passage through the input port; and the gas-guide tube communicates with the refrigerant passage through the output port.

As an improvement to the above solution, the raised member is provided with a plurality of middle input ports at intervals along a flow direction of the refrigerant passage; the middle input ports communicate with the refrigerant passage; the middle input ports are located between the input port and the output port; and the middle input ports each are connected to the condenser through a corresponding condensate input tube.

As an improvement to the above solution, the evaporator housing has a diameter of A, and a thickness of B, the A being 60-100 mm, and the B being 0.5-1.2 mm; a width of the refrigerant passage is the same as a diameter of the raised member; the raised member has the diameter of D, and a thickness of H, the D being 5-10 mm, and the H being 0.4-0.8 mm; and a ratio of the thickness of the evaporator housing to the diameter of the raised member is I, the I satisfying 0.1≤I≤0.12.

As an improvement to the above solution, the A is 80-90 mm, the B is 0.8-1.0 mm, the D is 6-8 mm, the H is 0.5-0.6 mm, and the I satisfies 0.1≤I≤0.11.

The present disclosure further provides a refrigeration device, including a machine body, where the evaporator is provided in the machine body; and the refrigeration device includes any one of an ice cream maker, a smoothie maker, a cold beverage maker, and an ice maker.

The present disclosure has the following beneficial effects:

By guiding the condensed fluid through the refrigerant passage, the condensed fluid is vaporized fully to improve a heat exchange effect. The condensed fluid can exchange heat with the outside directly through the single heat transfer medium. By reducing the heat transfer medium, the present disclosure can effectively improve heat transfer efficiency of the evaporator, thereby improving cold conduction performance of the evaporator. Moreover, the present disclosure can simplify an overall structure, save an assembly space, and lower a production cost.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic structural view of an evaporator according to a first embodiment of the present disclosure;

FIG. 2 is a schematic sectional view of the evaporator shown in FIG. 1;

FIG. 3 is a schematic structural view of a refrigerant region shown in FIG. 1;

FIG. 4 is a partially enlarged view of A shown in FIG. 2;

FIG. 5 is a partially enlarged view of B shown in FIG. 2;

FIG. 6 is a schematic structural view of an evaporator according to a second embodiment of the present disclosure;

FIG. 7 is a schematic structural view of an evaporator according to a third embodiment of the present disclosure;

FIG. 8 is a schematic structural view of an evaporator according to a fourth embodiment of the present disclosure;

FIG. 9 is a structural schematic view of a heat-exchange member and a refrigerant housing according to the present disclosure;

FIG. 10 is a schematic structural view of an evaporator according to a fifth embodiment of the present disclosure;

FIG. 11 is a partially enlarged view of A shown in FIG. 10;

FIG. 12 is a schematic structural view of an evaporator according to a sixth embodiment of the present disclosure.

FIG. 13 is a schematic sectional view of the evaporator shown in FIG. 8;

FIG. 14 is a schematic structural view of a refrigerant region shown in FIG. 8;

FIG. 15 is a schematic structural view of an evaporator according to a seventh embodiment of the present disclosure; and

FIG. 16 is a schematic structural view of an evaporator according to an eighth embodiment of the present disclosure.

DETAILED DESCRIPTION

In order to make the objectives, technical solutions, and advantages of the present disclosure clearer, the present disclosure will be further described in detail below with reference to the accompanying drawings.

FIG. 1 to FIG. 3 illustrate a schematic structural view of an evaporator according to a first embodiment of the present disclosure. As shown in FIG. 1 to FIG. 3, the evaporator includes an evaporator housing 1, a condensate input tube 2, a gas-guide tube 3, and a refrigerant region 4. The refrigerant region 4 is provided around an inner wall of the evaporator housing 1. The refrigerant region 4 and the evaporator housing 1 enclose a refrigerant passage 5. A condensed fluid in the refrigerant passage 5 acts on the inner wall of the evaporator housing 1, to realize an external refrigeration function of the evaporator. The refrigerant passage 5 includes an input end connected to a condenser through the condensate input tube 2, and an output end connected to a compressor through the gas-guide tube 3. When the evaporator works, the condenser conveys the condensed fluid to the refrigerant passage 5 through the condensate input tube 2. The condensed fluid flowing to the refrigerant passage 5 can absorb heat from the outside directly through the evaporator housing 1, thereby realizing heat exchange with outside air. A vaporized gas from the condensed fluid is exhausted back to the compressor through the gas-guide tube 3. By guiding the condensed fluid through the refrigerant passage, the condensed fluid is vaporized fully to improve a heat exchange effect. The refrigerant region 4 around the inner wall of the evaporator housing 1 can increase a heat transfer area. The condensed fluid can exchange heat with the outside only through the evaporator housing 1 (namely a single heat transfer medium). By reducing the heat transfer medium, the present disclosure can effectively improve heat transfer efficiency, thereby improving cold conduction performance of the evaporator. Moreover, the present disclosure can simplify an overall structure, save an assembly space, and lower a production cost.

The refrigerant region 4 includes a refrigerant housing 41 and a spiral turbulator sheet 42. The refrigerant housing 41 is hermetically connected to the evaporator housing 1, such that an airtight space is formed between the refrigerant housing 41 and the evaporator housing 1. The spiral turbulator sheet 42 is located between the refrigerant housing 41 and the evaporator housing 1. The spiral turbulator sheet 42, the refrigerant housing 41 and the evaporator housing I enclose the refrigerant passage 5. The refrigerant passage 5 of a spiral structure can guide the condensed fluid therein to improve a flow velocity, such that the condensed fluid is vaporized fully, thereby improving the heat transfer efficiency, and further improving the cold conduction performance of the evaporator.

Preferably, a wall of the evaporator housing 1 is preferably made of metal. The metal has a good heat transfer effect, and can improve the cold conduction performance. However, the material of the wall of the evaporator housing 1 is not limited thereto, and may further be other heat conductive materials with the good heat transfer effect.

Preferably, the spiral turbulator sheet 42 is preferably made of metal or plastic, but is not limited thereto.

Further, an input tube opening 411 and an output tube opening 412 communicating with the refrigerant passage 5 are respectively provided at two ends of the refrigerant housing 41. The condensate input tube 2 communicates with the refrigerant passage 5 through the input tube opening 411. The condenser allows the condensed fluid to flow in the refrigerant passage 5 through the condensate input tube 2 and the input tube opening 411. The condensed fluid is vaporized gradually in the refrigerant passage 5 to realize heat exchange. The gas-guide tube 3 communicates with the refrigerant passage 5 through the output tube opening 412. After the condensed fluid in the refrigerant passage 5 is vaporized, the vaporized gas from the condensed fluid is exhausted back to the compressor through the output tube opening 412 and the gas-guide tube 3 to realize cold conduction circulation.

Both the gas-guide tube 3 and the condensate input tube 2 are provided inside the refrigerant housing 41. This makes the structure compact, reduces the overall footprint of the evaporator, improves the space utilization rate of the evaporator, and ensures that one side of the evaporator housing 1 comes in contact with a heat exchange surface maximally for refrigeration to achieve the better refrigeration effect.

Further, as shown in FIG. 4 to FIG. 5, one end of the refrigerant housing 41 is provided with an outward extending limit ring 413. The limit ring 413 is hermetically connected to one end of the evaporator housing 1. The other end of the evaporator housing 1 away from the limit ring 413 is provided with an inward extending support ring 11. The support ring 11 is hermetically connected to the other end of the refrigerant housing 41. Through the limit ring 413 and the support ring 11, the refrigerant housing 41 is fixed, supported and limited, the airtight space for storing the condensed fluid is formed between the refrigerant housing 41 and the evaporator housing 1, and the condensed fluid does not flow out to affect the cold conduction performance of the evaporator.

Preferably, as shown in FIG. 1 and FIG. 4, an inward extending input tube 414 is provided on the input tube opening 411, such that the condensate input tube 2 is stably inserted into the input tube 414 and welded to improve connection stability and airtightness. Correspondingly, an inward extending output tube 415 is provided on the output tube opening 412, such that the gas-guide tube 3 is stably inserted into the output tube 415 and welded to improve connection stability and airtightness.

Further, the evaporator housing 1 has a diameter of A. The A is 60-100 mm. Further, the A is preferably 80-90 mm. The evaporator housing 1 has a thickness of B. The B is 0.5-1.2 mm. Further, the B is preferably 0.8-1.0 mm.

A width of the refrigerant passage 5 is the same as a pitch of the spiral turbulator sheet 42. The spiral turbulator sheet 42 has the pitch of C. The spiral turbulator sheet 42 has a width of E. The spiral turbulator sheet 42 has a thickness of F. The C is 5-20 mm, the E is 2-10 mm, and the F is 0.4-2 mm. Further, the C is 8-16 mm, the E is 5-8 mm, and the F is 0.9-1.5 mm.

A ratio of the thickness of the evaporator housing 1 to the pitch of the spiral turbulator sheet 42 is G. The G satisfies 0.06≤G=(B/C)≤0.1. Further, the G satisfies 0.0625≤G≤0.1.

The width of the refrigerant passage 5 and the thickness of the evaporator housing 1 jointly determine the heat exchange efficiency and the heat exchange effect of the evaporator. When the ratio G of the thickness of the evaporator housing 1 to the pitch of the spiral turbulator sheet 42 satisfies 0.6≤G≤0.1, the heat exchange effect is desirable, and the evaporator has the desirable cold conduction performance. In principle, the larger the width of the refrigerant passage 5 (namely a larger contact width between the refrigerant passage 5 and the inner wall of the evaporator housing 1), the larger the heat exchange area, the higher the heat exchange efficiency and the better the heat exchange effect. The smaller the thickness of the evaporator housing 1, namely the thinner the heat transfer medium, the higher the heat transfer efficiency and the better the heat transfer effect. However, in case of the excessively large width of the refrigerant passage 5, the flow velocity of the condensed fluid is slowed down to cause the poor heat exchange effect of the condensed fluid. Meanwhile, the evaporator housing 1, the refrigerant housing 41 and the spiral turbulator sheet 42 are required to be thicker to cause a high cost, or event affect a service life. In addition, if the evaporator housing 1 is too thin, and the refrigerant passage 5 has an overlarge fluid flow rate or an overlarge pressure, the evaporator housing 1 deforms to even affect the airtightness, thereby affecting normal operation. If the evaporator housing 1 is too thick, the heat transfer efficiency and the heat transfer effect are also affected. In view of this, if the ratio G of the thickness of the evaporator housing 1 to the pitch of the spiral turbulator sheet 42 exceeds an appropriate range, namely G<0.06 and G>0.1, the heat exchange effect is affected, the cost is increased, and the stability in use is reduced.

Correspondingly, on the basis of the satisfied ratio G of the thickness of the evaporator housing 1 to the pitch of the spiral turbulator sheet 42, other parameters of the evaporator housing 1 and the spiral turbulator sheet 42 also fall within corresponding ranges, such that the overall structure is compact and firm, the stability is high, and the cost is optimal.

Preferably, a width of a section of the refrigerant passage 5 becomes increasingly large along a flow direction of the refrigerant passage, so as to improve an influx of the condensed fluid to enhance the heat exchange effect. Alternatively, the width of the section of the refrigerant passage 5 becomes increasingly small along the flow direction of the refrigerant passage, so as to improve a heat exchange velocity of the condensed fluid to enhance the heat exchange effect, thereby improving the cold conduction effect of the evaporator.

Preferably, in other embodiments, the width of the section of the refrigerant passage 5 may also be unchanged along the flow direction of the refrigerant passage according to an actual need of the user, so as to lower a difficulty of a manufacturing process and achieve the better heat exchange effect.

FIG. 6 illustrates a schematic structural view of an evaporator according to a second embodiment of the present disclosure. As shown in FIG. 6, different from the first embodiment shown by FIG. 2, the refrigerant housing 41 may further be provided with a plurality of middle input tube openings 416 at intervals along a flow direction of the refrigerant passage 5.

The middle input tube openings 416 communicate with the refrigerant passage 5. The middle input tube openings 416 are located between the input tube opening 411 and the output tube opening 412. The middle input tube openings 416 each are connected to the condenser through a corresponding condensate input tube. When the evaporator works, the condensed fluid of the condenser flows to different positions of the refrigerant passage 5 synchronously through the input tube opening 411 and the plurality of middle input tube openings 416, and acts on the evaporator housing 1. As a result, the condensed fluid at the low temperature performs heat exchange more quickly at different positions of the evaporator, thereby accelerating a circulation rate and a heat transfer rate of the whole condensed fluid, and improving the cold conduction efficiency of the evaporator.

FIG. 7 illustrates a schematic structural view of an evaporator according to a third embodiment of the present disclosure. As shown in FIG. 7, different from the first embodiment shown by FIG. 3, three spiral turbulator sheets 42 are provided between the refrigerant housing 41 and the evaporator housing.

The refrigerant housing 41, the evaporator housing and the spiral turbulator sheets 42 enclose three refrigerant passages 5. The three refrigerant passages 5 are arranged in parallel. The three refrigerant passages 5 are spaced apart by the spiral turbulator sheets 42. Through the three independent refrigerant passages 5, the condensed fluid can flow to the evaporator synchronously for heat exchange. This can effectively improve the heat exchange efficiency and the heat exchange effect of the condensed fluid, thereby improving the cold conduction efficiency of the evaporator.

FIG. 8 to FIG. 9 illustrate a schematic structural view of an evaporator according to a fourth embodiment of the present disclosure. As shown by FIG. 8 to FIG. 9, different from the first embodiment shown by FIG. 1 to FIG. 3, a heat-exchange member 44 is provided between the evaporator housing 1 and the refrigerant housing 41. The heat-exchange member 44 includes a heat insulating body 45 and the spiral turbulator sheet 42. The heat insulating body 45 is sleeved on or embedded into the refrigerant housing 41. The spiral turbulator sheet 42 is protruded from a sidewall of the heat insulating body 45. That is, the spiral turbulator sheet 42 is a spiral convex rib on the sidewall of the heat insulating body 45. When a side (namely the heat insulating body 45) of the heat-exchange member 44 away from the spiral turbulator sheet 42 is located on the refrigerant housing 41, the spiral turbulator sheet 42 extends toward the evaporator housing 1 to form the refrigerant passage 5 where a condensed fluid exchanges heat with outside air through the evaporator housing 1, to realize the external refrigeration function of the evaporator.

Meanwhile, a width of a cross section of the refrigerant passage 5 becomes increasingly large in a direction from the refrigerant housing 41 to the evaporator housing 1. This increases a contact area between the condensed fluid and the sidewall of the evaporator housing 1, thereby improving the heat exchange efficiency and the refrigeration effect.

Preferably, the heat insulating body 45 is sleeved on the refrigerant housing 41, or the heat insulating body 45 is embedded into the refrigerant housing 41. Through one heat insulating body 45 (namely the heat insulating layer), heat dissipated by the condensed fluid through the refrigerant housing 41 can be effectively reduced, the structure is more stable, and the displacement between components is reduced. A thickness of the heat insulating body 45 is far greater than a thickness of the evaporator housing 1, which ensures that more heat is exchanged with the outside through the evaporator housing 1.

When the evaporator works, the condenser conveys the condensed fluid to the refrigerant passage 5 through the condensate input tube. The condensed fluid flowing to the refrigerant passage 5 can absorb heat from the outside directly through the evaporator housing 1, thereby realizing heat exchange with outside air. A vaporized gas from the condensed fluid is exhausted back to the compressor through the gas-guide tube. The spiral turbulator sheet 42 on an outer surface of the sidewall of the heat-exchange member 44 not only increases the heat exchange area, but also improves a flow velocity and a degree of mixing of the condensed fluid in the refrigerant passage 5 through a turbulence effect, thereby enhancing the heat exchange effect. The condensed fluid can exchange heat with the outside only through the evaporator housing 1 (namely a single heat transfer medium). By reducing the heat transfer medium, the present disclosure can effectively improve heat transfer efficiency, thereby improving cold conduction performance of the evaporator. Moreover, the present disclosure can simplify an overall structure, save an assembly space, and lower a production cost.

Specifically, as shown in FIG. 8 to FIG. 9, the spiral turbulator sheets 42 are arranged at intervals along a length direction of the heat-exchange member 44. This facilitates uniform distribution of the turbulence effect along the length direction of the whole heat-exchange member 44, such that the condensed fluid can be agitated continuously in the flowing process to make the heat exchange more uniform and efficient. When flowing through the spiral turbulator sheets 42, the condensed fluid has a same flowing trend in the refrigerant passages 5 formed by the spiral turbulator sheets 42. This reduces a vortex and a resistance possibly resulting from different directions, and further improves the flow velocity and the heat exchange efficiency.

Preferably, the heat-exchange member 44 is made of plastic or silica gel. That is, both the heat insulating body 45 and the spiral turbulator sheet 42 are made of the plastic or the silica gel. The heat insulating body 45 and the spiral turbulator sheet 42 are an integrated structure by injection molding or punching, which reduces the production cost and improves the production efficiency. Alternatively, the heat insulating body 45 and the spiral turbulator sheet 42 are a split structure. The heat insulating body 45 and the spiral turbulator sheet 42 are manufactured respectively and then connected together by welding, bonding or clamping, so as to facilitate subsequent maintenance and replacement. When one component is damaged, replacement is made only to the component rather than the whole evaporator, thereby greatly improving the maintenance efficiency and the maintenance cost.

Preferably, the refrigerant housing 41 may further be provided with a plurality of middle input tube openings at intervals along a flow direction of the refrigerant passage 5. The middle input tube openings and the input tube opening communicate with the refrigerant passage 5 through the heat insulating body 45. This can also realize the technical effect in the second embodiment of the present disclosure, and is not repeated one by one herein.

Preferably, a plurality of spiral turbulator sheets 42 may be provided between the refrigerant housing 41 and the evaporator housing 1. That is, the plurality of spiral turbulator sheets 42 are arranged at intervals on the sidewall of the heat insulating body 45 to form a plurality of refrigerant passages 5. This can also realize the technical effect in the third embodiment of the present disclosure, and is not repeated one by one herein.

FIG. 10 to FIG. 11 illustrate a schematic structural view of an evaporator according to a fifth embodiment of the present disclosure. As shown in FIG. 10 to FIG. 11, different from the fourth embodiment shown by FIG. 8 to FIG. 9, when a side (namely the heat insulating body 45) of the heat-exchange member 44 away from the spiral turbulator sheet 42 is located on the refrigerant housing 41, the spiral turbulator sheet 42 extends toward the evaporator housing 1 to form the refrigerant passage 5 where a condensed fluid exchanges heat with outside air through the evaporator housing 1, to realize the internal refrigeration function of the evaporator.

Through the heat insulating body 45, heat dissipated by the condensed fluid through the evaporator housing I can be effectively reduced, the structure is more stable, and the displacement between components is reduced. A thickness of the heat insulating body 45 is far greater than a thickness of the refrigerant housing 41, which ensures that more heat is exchanged with the inside through the refrigerant housing 41. Both the gas-guide tube and the condensate input tube are provided outside the evaporator housing 1. This makes the structure compact, reduces the overall footprint of the evaporator, improves the space utilization rate of the evaporator, and ensures that one side of the refrigerant housing 41 comes in contact with a heat exchange surface maximally for refrigeration to achieve the better refrigeration effect. Meanwhile, a width of a cross section of the refrigerant passage 5 becomes increasingly large in a direction from the refrigerant housing 41 to the evaporator housing 1. This increases a contact area between the condensed fluid and the sidewall of the refrigerant housing 41, thereby improving the heat exchange efficiency and the refrigeration effect.

When the evaporator works, the condenser conveys the condensed fluid to the refrigerant passage 5 through the condensate input tube. The condensed fluid flowing to the refrigerant passage 5 can absorb heat from the inside directly through the refrigerant housing 41, thereby realizing heat exchange with outside air in the refrigerant housing 41. A vaporized gas from the condensed fluid is exhausted back to the compressor through the gas-guide tube. The spiral turbulator sheet 42 on an outer surface of the sidewall of the heat-exchange member 44 not only increases the heat exchange area, but also improves a flow velocity and a degree of mixing of the condensed fluid in the refrigerant passage 5 through a turbulence effect, thereby enhancing the heat exchange effect. The condensed fluid can exchange heat with the outside only through the refrigerant housing 41 (namely a single heat transfer medium). By reducing the heat transfer medium, the present disclosure can effectively improve heat transfer efficiency, thereby improving cold conduction performance of the evaporator. Moreover, the present disclosure can simplify an overall structure, save an assembly space, and lower a production cost.

Further, the refrigerant housing 41 has a diameter of A. The A is 60-100 mm. Further, the A is preferably 80-90 mm. The refrigerant housing 41 has a thickness of B. The B is 0.5-1.2 mm. Further, the B is preferably 0.8-1.0 mm.

A width of the refrigerant passage 5 is the same as a pitch of the spiral turbulator sheet 42. The spiral turbulator sheet 42 has the pitch of C. The spiral turbulator sheet 42 has a width of E. The spiral turbulator sheet 42 has a thickness of F. The C is 5-20 mm, the E is 2-10 mm, and the F is 0.4-2 mm. Further, the C is 8-16 mm, the E is 5-8 mm, and the F is 0.9-1.5 mm.

A ratio of the thickness of the refrigerant housing 41 to the pitch of the spiral turbulator sheet 42 is G. The G satisfies 0.06≤G=(B/C)≤0.1. Further, the G satisfies 0.0625≤G≤0.1.

It is to be noted that the width of the refrigerant passage 5 and the thickness of the refrigerant housing 41 jointly determine the heat exchange efficiency and the heat exchange effect of the evaporator. If the ratio G of the thickness of the refrigerant housing 41 to the pitch of the spiral turbulator sheet 42 exceeds an appropriate range, namely G<0.06 and G>0.1, the heat exchange effect is affected, the cost is increased, and the stability in use is reduced. Correspondingly, on the basis of the satisfied ratio G of the thickness of the refrigerant housing 41 to the pitch of the spiral turbulator sheet 42, other parameters of the refrigerant housing 41 and the spiral turbulator sheet 42 also fall within corresponding ranges, such that the overall structure is compact and firm, the stability is high, and the cost is optimal.

Preferably, the refrigerant housing 41 may further be provided with a plurality of middle input tube openings at intervals along a flow direction of the refrigerant passage 5. The middle input tube openings and the input tube opening communicate with the refrigerant passage 5 through the heat insulating body 45. This can also realize the technical effect in the second embodiment of the present disclosure, and is not repeated one by one herein.

Preferably, a plurality of spiral turbulator sheets 42 may be provided between the refrigerant housing 41 and the evaporator housing 1. That is, the plurality of spiral turbulator sheets 42 are arranged at intervals on the sidewall of the heat insulating body 45 to form a plurality of refrigerant passages 5. This can also realize the technical effect in the third embodiment of the present disclosure, and is not repeated one by one herein.

FIG. 12 to FIG. 14 illustrate a schematic structural view of an evaporator according to a sixth embodiment of the present disclosure. As shown in FIG. 12 to FIG. 14, different from the first embodiment shown by FIG. 1 to FIG. 3, the refrigerant region 4 includes a spiral raised member 43. The raised member 43 and the inner wall of the evaporator housing 1 are an integrally punch-formed structure, so as to simplify the structure, and improve the assembly efficiency. An inner chamber of the raised member 43 and the evaporator housing 1 enclose the refrigerant passage 5. The condensed fluid in the refrigerant passage 5 can exchange heat with the outside only through the evaporator housing 1. With the few heat transfer medium, the present disclosure can effectively improve the heat transfer efficiency, thereby improving the cold conduction performance of the evaporator. Moreover, the present disclosure can simplify the overall structure, save the assembly space, and reduce the production cost. The refrigerant passage 5 of the spiral structure can guide the condensed fluid therein, such that the condensed fluid is vaporized fully, thereby improving the heat transfer efficiency, and further improving the cold conduction performance of the evaporator.

Specifically, an input port 431 and an output port 432 communicating with the refrigerant passage 5 in one-to-one correspondence are respectively provided at two ends of the raised member 43 at intervals. The condensate input tube 2 is inserted into the input port 431 and welded, such that the condenser provides the condensed fluid for the refrigerant passage 5 through the condensate input tube 2 and the input port 431, and the condensed fluid is vaporized gradually in the refrigerant passage 5 to realize heat exchange. The gas-guide tube 3 communicates with the refrigerant passage 5 through the output port 432. After the condensed fluid in the refrigerant passage 5 is vaporized, the vaporized gas from the condensed fluid is exhausted back to the compressor through the output port 432 and the gas-guide tube 3 to realize cold conduction circulation.

A cross section of the raised member 43 is formed by a plurality of arranged semicircles. Two adjacent semicircles contact to each other, without a gap therebetween, so as to maximize a heat exchange contact area between the condensed fluid and the evaporator housing, improve the heat transfer efficiency of the condensed fluid, and improve the cold conduction efficiency of the evaporator. Preferably, in other embodiments, the cross section of the raised member 43 may further be triangular or square, and is not limited excessively herein.

Further, the evaporator housing 1 has a diameter of A. The A is 60-100 mm. Further, the A is preferably 80-90 mm. The evaporator housing 1 has a thickness of B. The B is 0.5-1.2 mm. Further, the B is preferably 0.8-1.0 mm.

A width of the refrigerant passage 5 is the same as a diameter of the raised member 43. The raised member 43 has the diameter of D. The raised member 43 has a thickness of H. The D is 5-10 mm, and the H is 0.4-0.8 mm. Further, the D is 6-8 mm, and the H is 0.5-0.6 mm.

A ratio of the thickness of the evaporator housing 1 to the diameter of the raised member 43 is I. The I satisfies 0.1≤I=(B/D)≤0.12. Further, the I satisfies 0.1≤I≤0.11.

The width of the refrigerant passage 5 and the thickness of the evaporator housing 1 jointly determine the heat exchange efficiency and the heat exchange effect of the evaporator. When the ratio I of the thickness of the evaporator housing 1 to the diameter of the raised member 43 satisfies 0.1≤I≤0.12, the heat exchange effect is desirable, and the evaporator has the desirable cold conduction performance. In principle, the larger the width of the refrigerant passage 5 (namely a larger contact width between the refrigerant passage 5 and the inner wall of the evaporator housing 1), the larger the heat exchange area, the higher the heat exchange efficiency and the better the heat exchange effect. The smaller the thickness of the evaporator housing 1, namely the thinner the heat transfer medium, the higher the heat transfer efficiency and the better the heat transfer effect. However, in case of the excessively large width of the refrigerant passage 5, the flow velocity of the fluid is slowed down, such that the pressure is increased, and the condensed fluid has the poor heat exchange effect. Meanwhile, the evaporator housing 1 and the raised member 43 are required to be thicker to cause a high cost, or event affect a service life. In addition, if the evaporator housing 1 is too thin, and the refrigerant passage 5 has an overlarge fluid flow rate or an overlarge pressure, the evaporator housing 1 deforms to even affect the airtightness, thereby affecting normal operation. If the evaporator housing 1 is too thick, the heat transfer efficiency and the heat transfer effect are also affected. In view of this, if the ratio I of the thickness of the evaporator housing 1 to the diameter of the raised member 43 exceeds an appropriate range, namely G<0.1 and G>0.12, the heat exchange effect is affected, the cost is increased, and the stability in use is reduced.

Correspondingly, on the basis of the satisfied ratio I of the thickness of the evaporator housing 1 to the diameter of the raised member 43, other parameters of the evaporator housing 1 and the raised member 43 also fall within corresponding ranges, such that the overall structure is compact and firm, the stability is high, and the cost is optimal.

FIG. 15 illustrates a schematic structural view of an evaporator according to a seventh embodiment of the present disclosure. As shown in FIG. 15, different from the fourth embodiment shown by FIG. 13, the raised member 43 may further be provided with a plurality of middle input ports 433 at intervals along a flow direction of the refrigerant passage 5.

The middle input ports 433 communicate with the refrigerant passage 5. The middle input ports 433 are located between the input port and the output port. The middle input ports 433 each are connected to the condenser through a corresponding condensate input tube. When the evaporator works, the condensed fluid of the condenser flows to different positions of the refrigerant passage synchronously through the input port and the plurality of middle input ports 433, and acts on the evaporator housing 1. As a result, the condensed fluid at the low temperature performs heat exchange more quickly at different positions of the evaporator, thereby accelerating a circulation rate and a heat transfer rate of the whole condensed fluid, and improving the cold conduction efficiency of the evaporator.

FIG. 16 illustrates a schematic structural view of an evaporator according to an eighth embodiment of the present disclosure. As shown in FIG. 16, different from the fourth embodiment shown by FIG. 13, the refrigerant region 4 includes three spiral raised members 43.

Inner chambers of the raised members 43 and the evaporator housing 1 enclose three refrigerant passages 5. The three refrigerant passages 5 are arranged in parallel. The three refrigerant passages 5 are spaced apart by the raised members 43. Through the three independent refrigerant passages 5, the condensed fluid can flow to the evaporator synchronously for heat exchange. This can effectively improve the heat exchange efficiency and the heat exchange effect of the condensed fluid, thereby improving the cold conduction efficiency of the evaporator.

The present disclosure further provides a refrigeration device, including a machine body. The evaporator is provided in the machine body. The refrigeration device includes, but is not limited to, any one of an ice cream maker, a smoothie maker, a cold beverage maker, and an ice maker.

By guiding the condensed fluid through the refrigerant passage, the condensed fluid is vaporized fully to improve a heat exchange effect. The condensed fluid can exchange the heat with the outside directly through the single heat transfer medium to realize external or internal heat exchange of the evaporator. By reducing the heat transfer medium, the present disclosure can effectively improve heat transfer efficiency of the evaporator, thereby greatly improving cold conduction performance of the evaporator. Moreover, the present disclosure can simplify an overall structure, save an assembly space, and lower a production cost.

The descriptions above are preferred implementations of the present disclosure. It should be noted that for a person of ordinary skill in the art, various improvements and modifications can be made without departing from the principles of the present disclosure. These improvements and modifications should also be regarded as falling into the protection scope of the present disclosure.