CO-ROTATING SCROLL COMPRESSOR

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a National Stage of International Application No. PCT/JP2023/027734 filed on Jul. 28, 2023, claiming priority based on Japanese Patent Application No. 2022-179610 filed on Nov. 9, 2022, the contents of all of which are incorporated herein by reference in their entirety.

TECHNICAL FIELD

The present disclosure relates to a co-rotating scroll compressor.

BACKGROUND ART

A co-rotating scroll compressor has been conventionally known. This co-rotating scroll compressor includes a driving mechanism, a driving scroll, a driven mechanism, a driven scroll, and a housing.

The housing has a scroll chamber accommodating a scroll compression part formed of the driving scroll and the driven scroll.

The driving scroll is driven to rotate around a driving axis by the driving mechanism. The driven scroll is disposed eccentric to the driving scroll, and is driven to rotate around a driven axis by the driving scroll and the driven mechanism.

The driving scroll has a driving scroll end plate, and a driving scroll spiral body. The driving scroll end plate extends so as to intersect with the driving axis. The driving scroll spiral body protrudes from the driving scroll end plate toward the driven scroll, and has a spiral shape.

The driven scroll has a driven scroll end plate and a driven scroll spiral body. The driven scroll end plate extends so as to intersect with the driven axis. The driven scroll spiral body protrudes from the driven scroll end plate toward the driving scroll, and has a spiral shape.

The driving scroll and the driven scroll form a compression chamber with the driving scroll spiral body and the driven scroll spiral body facing with each other. A volume of the compression chamber is changed by driving rotation of the driving scroll and driven rotation of the driven scroll, and fluid drawn from a suction chamber is compressed with the change of the volume of the compression chamber to be discharged to a discharge chamber.

In a rotary compressor in which a compression part rotates to compress fluid in a compression chamber, similarly to the co-rotating scroll compressor, a sliding portion such as a bearing that rotatably supports the compression part relative to the housing generates heat due to sliding friction. Additionally, there is created a vicious cycle in which sliding resistance is increased by a reduction of viscosity of lubricating oil inside the bearing by the heat and an amount of heat is increased by the increased sliding resistance. Furthermore, an increase in the sliding resistance of the sliding portion leads to a decrease in efficiency due to a sliding loss.

Therefore, during operation of the rotary compressor, it is necessary to supply a sufficient amount of lubricating oil to the sliding portion such as a bearing and to continuously cool the sliding portion to suppress the generation of sliding heat.

Therefore, in the rotary compressor described in Patent Document 1, lubricating oil is pumped up from an oil storage portion provided at the bottom inside the compressor by a pumping means, and the lubricating oil is supplied to the compression part and the bearings of a rotary shaft.

CITATION LIST

Patent Literature

• • Patent Literature 1: Japanese Patent Application Publication No. 2005-146987

SUMMARY OF INVENTION

Technical Problem

However, in consideration with heat capacity of lubricating oil and a temperature of lubricating oil stored in the oil storage portion in the compressor, there is a concern about insufficient cooling of the sliding portion in a measure in the above-described conventional rotary compressor, and the measure may not be sufficient.

Especially in the co-rotating scroll compressor, in the scroll chamber accommodating the scroll compression part, lubricating oil flows out from the scroll compression part which rotates, and due to an influence of centrifugal force of the scroll compression part which rotates, a flow of fluid in the rotational direction is generated, thereby generating centrifugal force. As a result, lubricating oil accumulates in an outermost peripheral portion in the scroll chamber. If an amount of lubricating oil accumulating in the outermost peripheral portion of the scroll chamber continues to increase, the amount of lubricating oil that is meant to be provided for the sliding portion decreases. If the amount of lubricating oil decreases, the sliding resistance increases, which may result in a decrease in efficiency.

The present disclosure has been made in view of the above-mentioned conventional circumstance, and is directed to providing a co-rotating scroll compressor that can suppress an increase in sliding resistance in the sliding portion, and hence a decrease in efficiency by supplying lubricating oil that accumulates in a scroll chamber during operation to the sliding portion and enhancing cooling efficiency in the sliding portion with the lubricating oil.

Solution to Problem

A co-rotating scroll compressor includes:

• • a housing; a driving mechanism; a driving scroll; a driven scroll; and a driven mechanism,
  • the housing having a scroll chamber in which the driving scroll and the driven scroll are accommodated, a storage chamber that separates a refrigerant drawn from an outside into gas and liquid and stores liquid refrigerant, and a partition wall that separates the storage chamber from the scroll chamber,
  • the driving scroll being configured to be driven to rotate around a driving axis by the driving mechanism,
  • the driven scroll being eccentric to the driving scroll, and configured to be driven to rotate around a driven axis by the driving scroll and the driven mechanism,
  • a supporting portion protruding from the partition wall into the scroll chamber with the driving axis at a center,
  • the driving scroll being supported by a bearing disposed between the driving scroll and the supporting portion so as to be driven to rotate around the driving axis,
  • a scroll compression part being formed of the driving scroll and the driven scroll, and
  • an oil storage portion in which lubricating oil is stored being provided in the scroll chamber
  • a lubricating oil supply passage in communication with the oil storage portion, through which the lubricating oil is supplied to the scroll compression part or the bearing, characterized in that
  • the lubricating oil supply passage has a lubricating oil cooling portion that cools the lubricating oil in the lubricating oil supply passage with the refrigerant in the storage chamber.

In the co-rotating scroll compressor of the present disclosure, an oil storage portion in which the lubricating oil is stored is provided in the scroll chamber. This oil storage portion is provided, for example, as follows. That is, during operation of the scroll compression part, lubricating oil supplied to the rotating scroll compression part flows out from the scroll compression part into the scroll chamber due to centrifugal force. In the scroll chamber, due to an influence of the centrifugal force of the rotating scroll compression part, a flow of fluid is generated in the rotation direction. Thus, lubricating oil accumulates in an outer peripheral portion of the scroll chamber due to the centrifugal force. In this way, the oil storage portion in which lubricating oil is stored is provided in the scroll chamber.

Here, in the scroll chamber, a portion closer to the rotation center of the scroll compression part is less affected by the centrifugal force of fluid. For this reason, when a pressure at the outer peripheral portion of the scroll chamber and a pressure on a side of the rotation center of the scroll compression part are compared, the pressure at the outer peripheral portion, which is more subject to the centrifugal force of the fluid, is higher. In addition, since fluid in the scroll chamber is drawn into the scroll compression part through an intake port provided in the driving scroll or the driven scroll, a pressure at the intake port of the scroll compression part is lower than the pressure at the outer peripheral portion of the scroll chamber.

Therefore, for example, if an inlet of the lubricating oil supply passage is opened to the outer peripheral portion of the scroll chamber and an outlet of the lubricating oil supply passage is opened, for example, to an inside of the scroll compression part, or on a side of the rotation center of the scroll compression part inside the scroll compression chamber, the pressure at the inlet of the lubricating oil supply passage is higher than the pressure at the outlet. Thus, due to the pressure difference, lubricating oil accumulated in the oil storage portion provided in the outer peripheral portion of the scroll chamber is introduced into the inlet of the lubricating oil supply passage, and is led to the inside of the scroll compression part and the side of the rotation center of the scroll compression part in the scroll chamber from the outlet of the lubricating oil supply passage. The lubricating oil coming out from the outlet of the lubricating oil supply passage flows to an outer peripheral side of the outlet due to the centrifugal force, and is supplied to the scroll compression part and the bearings, which are located on the outer peripheral side of the outlet.

In this manner, the lubricating oil in the oil storage portion provided in the scroll chamber can be supplied to the scroll compression part and the sliding portion of the bearing, thereby preventing an increase in sliding resistance due to insufficient lubricating oil in the sliding portion.

Furthermore, the lubricating oil flowing through the lubricating oil supply passage is cooled by the liquid refrigerant in the storage chamber at the lubricating oil cooling portion. Thus, the lubricating oil at a temperature lower than the lubricating oil stored in the oil storage portion of the scroll chamber is supplied to the scroll compression part and the sliding portion of the bearing. As a result, the sliding portion can be lubricated with lubricating oil with an appropriate viscosity, and is cooled with cooler lubricating oil, whereby it is possible to prevent the viscosity of the lubricating oil from decreasing due to heat from the sliding portion. These suppress an increase in sliding resistance in the scroll compression part and the sliding portion of the bearing.

Thus, according to the co-rotating scroll compressor of the present disclosure, lubricating oil accumulating in the scroll chamber during operation is supplied to the sliding portion and cooling efficiency by such lubricating oil in the sliding portion is enhanced, so that an increase in sliding resistance in the sliding portion is suppressed, and hence a decrease in efficiency is suppressed.

The driving scroll may have a driving scroll end plate, and a driving scroll spiral body that is formed integrally with the driving scroll end plate and protrudes toward the driven scroll in a spiral shape, and a cover body connected to the driving scroll end plate with the driven scroll held between the cover body and the driving scroll end plate. In addition, the driven scroll may have a driven scroll end plate, and a driven scroll spiral body that is formed integrally with the driven scroll end plate and protrudes toward the driving scroll end plate in a spiral shape. Furthermore, it is preferable that the lubricating oil is supplied from the lubricating oil supply passage to a sliding portion between the driven scroll end plate and the cover body.

In this case, in the scroll compression part, the sliding portion between the driven scroll end plate and the cover body requires lubricating oil. In this regard, the lubricating oil is supplied to the sliding portion between the driven scroll end plate and the cover body from the lubricating oil supply passage. Therefore, the lubricating oil cooled by the liquid refrigerant can be suitably supplied to the sliding portion between the driven scroll end plate and the cover body.

It is preferable that the lubricating oil is supplied from the lubricating oil supply passage to the bearing, and the lubricating oil supply passage extends through the supporting portion.

In this case, the lubricating oil cooled by the liquid refrigerant can be suitably supplied from the lubricating oil supply passage extending through the supporting portion to the bearing located on the outer peripheral side of the supporting portion.

Furthermore, the bearing is located relatively close to the rotation center of the scroll compression part in the scroll chamber. In the scroll chamber, the amount of lubricating oil tends to become insufficient as it approaches the rotation center of the scroll compression part. If the lubricating oil supply passage extends through the supporting portion, it becomes possible to supply an adequate amount of lubricating oil to the bearing where the amount of lubricating oil tends to be insufficient.

Furthermore, the supporting portion does not rotate even during operation of the scroll compression part. This allows the lubricating oil to be discharged stably from the outlet of the lubricating oil supply passage that extends through the supporting portion and is opened at a distal end surface thereof.

A driven shaft portion that is eccentric to the driving axis and extends in parallel to the driving axis may be provided in the housing, and a bushing into which the driven shaft portion is inserted may be provided. In addition, a bushing bearing may be disposed between the driven scroll and the bushing. It is preferable that lubricating oil is supplied from the lubricating oil supply passage to the bushing bearing. In addition, it is preferable that the lubricating oil supply passage extends through the driven shaft portion or the bushing.

In this case, the lubricating oil cooled by the liquid refrigerant can be suitably supplied from the lubricating oil supply passage extending through the driven shaft portion or the bushing to the bushing bearing located on the outer peripheral side relative to the driven shaft portion or the bushing.

In addition, the bushing bearing is close to the rotation center of the scroll compression part in the scroll chamber, and the amount of lubricating oil tends to be insufficient. If the lubricating oil supply passage extends through the driven shaft portion or the bushing, it is possible to sufficiently supply lubricating oil to the bushing bearing where the amount of lubricating oil tends to be insufficient.

It is preferable that the lubricating oil supply passage extends through the cover body.

In this case, the lubricating oil cooled by the liquid refrigerant can be suitably supplied to the sliding portion between the cover body and the driven end plate located on the outer peripheral side of the outlet of the lubricating oil supply passage extending through the cover body.

It is preferable that the lubricating oil cooling portion is formed of a groove that is recessed in a wall surface of the partition wall on the storage chamber side, and a lid that has a plate shape, extends in a direction in which the groove extends, and is fixed to the wall surface so as to close an opening of the groove. It is preferable that a passage defined by an inner surface of the groove and the lid forms a part of the lubricating oil supply passage.

In this case, the lubricating oil flowing through the passage defined by the inner surface of the groove and the lid can be cooled by the liquid refrigerant in the storage chamber through the lid.

It is preferable that the lubricating oil cooling portion is formed of a pipe disposed in the storage chamber. It is preferable that a passage inside the pipe forms a part of the lubricating oil supply passage.

In this case, the lubricating oil flowing through the passage in the pipe can be cooled by liquid refrigerant in the storage chamber through the peripheral wall of the pipe.

Advantageous Effects of Invention

According to the co-rotating scroll compressor of the present disclosure, lubricating oil accumulating in the scroll chamber during operation is supplied to the sliding portion and cooling efficiency by such lubricating oil in the sliding portion is enhanced, so that an increase in sliding resistance in the sliding portion is suppressed, and hence a decrease in efficiency is suppressed.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a cross-sectional view of a co-rotating scroll compressor of a first embodiment. 30

FIG. 2 is a partially enlarged cross-sectional view illustrating a main part of the co-rotating scroll compressor according to the first embodiment.

FIG. 3 is a partially enlarged cross-sectional view illustrating a main part of a co-rotating scroll compressor according to a second embodiment.

FIG. 4 is a partially enlarged cross-sectional view illustrating a main part of a co-rotating scroll compressor according to a third embodiment.

FIG. 5 is a partially enlarged cross-sectional view illustrating a main part of the co-rotating scroll compressor according to a fourth embodiment.

FIG. 6 is a partially enlarged cross-sectional view illustrating a main part of the co-rotating scroll compressor according to a fifth embodiment.

DESCRIPTION OF EMBODIMENTS

The following will describe a first embodiment to a fifth embodiment of the present disclosure with reference to the drawings.

First Embodiment

As illustrated in FIG. 1, a co-rotating scroll compressor (hereinafter, simply referred to as a compressor) of a first embodiment includes a housing 60, a scroll compression part 80, an electric motor 10, a driving scroll 30, a driven scroll 40, a driven mechanism 20, and a storage chamber 70A. The electric motor 10 is an example of a “driving mechanism” of the present disclosure. This compressor is mounted on a vehicle (not illustrated), and forms a part of a vehicle air conditioner.

In the present embodiment, a front-rear direction and an up-down direction of the compressor are defined by solid arrows illustrated in FIGS. 1 to 6. It is noted that the front-rear direction is an example for convenience of explanation, and a posture of the compressor may be changed, as appropriate, depending on the vehicle on which the compressor is mounted. However, the compressor of the present embodiment is mounted on the vehicle in such a manner that an inlet 63C of a lubricating oil supply passage 63H, which will be described later, is located at a bottom of a suction chamber 61A.

The housing 60 is formed of a housing body 61, a front cover 65, a bearing housing 67, and a rear cover 70.

The housing body 61 is a bottomed tubular member having a first outer peripheral wall 62 and a first bottom wall 63. The first bottom wall 63 is an example of a “partition wall” of the present disclosure. The first outer peripheral wall 62 is formed in a cylindrical shape extending around a driving axis R1. The driving axis R1 is parallel to the front-rear direction. In addition, the first outer peripheral wall 62 has an inner peripheral surface 62B. The first bottom wall 63 is located at a rear end of the housing body 61. The first bottom wall 63 is formed in a substantially circular flat plate shape extending perpendicularly to the driving axis R1.

An outer peripheral edge of the first bottom wall 63 is connected to a rear end of the first outer peripheral wall 62. The first bottom wall 63 has a front surface 631, and a rear surface 632 opposite from the front surface 631. A second shaft supporting portion 64 has a columnar shape protruding forward from a center of the front surface 631 of the first bottom wall 63. The second shaft supporting portion 64 is an example of a “supporting portion” of the present disclosure.

A third shaft supporting portion 90 has a columnar shape and is disposed eccentric to the second shaft supporting portion 64 on a distal end surface 641 of the second shaft supporting portion 64. The third shaft supporting portion 90 is an example of a “bushing” of the present disclosure. An eccentric shaft 91 is provided in the second shaft supporting portion 64. The eccentric shaft 91 is an example of the “driven shaft portion” of the present disclosure. The eccentric shaft 91 extends forward in parallel to the driving axis R1 from the distal end surface 641 of the second shaft supporting portion 64. The eccentric shaft 91 is eccentric to the driving axis R1. The third shaft supporting portion 90 is attached to the eccentric shaft 91 so as to be rotatable. In addition, a third bearing 73 is fitted into a recess 74, which will be described later. The third bearing 73 is an example of a “bushing bearing” of the present disclosure. These allows the third shaft supporting portion 90 to rotate relative to the recess 74, which will be described later, and the eccentric shaft 91.

The bearing housing 67 is disposed in front of the housing body 61. The bearing housing 67 has a substantially circular flat plate shape extending perpendicularly to the driving axis R1. The bearing housing 67 is fastened together with the front cover 65 to the first outer peripheral wall 62 by a bolt (not illustrated) with an outer peripheral edge of the bearing housing 67 in contact with a front end of the first outer peripheral wall 62 of the housing body 61. According to this, the bearing housing 67 closes the housing body 61 from the front thereof. Thus, a suction chamber 61A is formed in the housing body 61.

A first shaft supporting portion 66 is formed at a center of the bearing housing 67 and has a cylindrical shape extending around the driving axis R1. A first bearing 71 is fitted into the first shaft supporting portion 66.

The front cover 65 is disposed in front of the bearing housing 67. The front cover 65 is a bottomed tubular member having a second outer peripheral wall 68 and a second bottom wall 69. The second outer peripheral wall 68 is formed in a cylindrical shape extending around the driving axis R1. The second bottom wall 69 is located at a front end of the front cover 65. The second bottom wall 69 has a substantially circular flat plate shape extending perpendicularly to the driving axis R1. An outer peripheral edge of the second bottom wall 69 is connected to a front end of the second outer peripheral wall 68.

The front cover 65 is fastened together with the bearing housing 67 to the first outer peripheral wall 62 by a bolt (not illustrated) with a rear end of the second outer peripheral wall 68 in contact with a front surface of the bearing housing 67. Thus, a second discharge portion 65A is formed between the front cover 65 and the bearing housing 67. The second discharge portion 65A is located in front of and adjacent to the suction chamber 61A. The second discharge portion 65A is separated from the suction chamber 61A by the bearing housing 67.

A discharge communication port 65B is formed in the front cover 65. The discharge communication port 65B is located near an outer peripheral edge of the front cover 65 and extends through the front cover 65 in a direction parallel to the driving axis R1. The discharge communication port 65B provides communication between the second discharge portion 65A and an outside of the compressor. A tube is connected to the discharge communication port 65B, and allows refrigerant discharged to the second discharge portion 65A to flow toward a condenser. It is noted that illustrations of the tube, an evaporator, and the condenser are omitted.

The rear cover 70 is disposed behind the housing body 61. The rear cover 70 is a bottomed tubular member having a third outer peripheral wall 75 and a third bottom wall 76. The third outer peripheral wall 75 is formed in a cylindrical shape extending around the driving axis R1. The third bottom wall 76 is located at a rear end of the rear cover 70. The third bottom wall 76 has a substantially circular flat plate shape extending perpendicularly to the driving axis R1. An outer peripheral edge of the third bottom wall 76 is connected to a rear end of the third outer peripheral wall 75.

The rear cover 70 is fastened to the first outer peripheral wall 62 of the housing body 61 by a bolt (not illustrated) with a front end of the third outer peripheral wall 75 in contact with the rear surface 632 of the first bottom wall 63 of the housing body 61. As a result, the storage chamber 70A is formed between the rear cover 70 and the housing body 61. The storage chamber 70A is adjacent to and behind the suction chamber 61A. The storage chamber 70A is separated from the suction chamber 61A by the first bottom wall 63 of the housing body 61.

An intake communication port 70B is formed in the third outer peripheral wall 75 of the rear cover 70. The intake communication port 70B extends through the third outer peripheral wall 75 in a direction intersecting with the driving axis R1. The intake communication port 70B provides communication between the storage chamber 70A and the outside of the compressor. A tube is connected to the intake communication port 70B. Accordingly, refrigerant at low temperature and low pressure after flowing through the evaporator is drawn into the storage chamber 70A through the tube. The storage chamber 70A separates the refrigerant drawn in from the outside into gas and liquid, and stores therein liquid refrigerant.

An intake communication port 63A is formed in the first bottom wall 63 of the housing body 61. The intake communication port 63A is located near the outer peripheral edge of the first bottom wall 63 and near the intake communication port 70B, and extends through the first bottom wall 63 in a direction parallel to the driving axis R1. The intake communication port 63A provides communication between the suction chamber 61A and the storage chamber 70A.

As illustrated in FIG. 2, a first passage 63B is formed in a bottom portion of the first bottom wall 63. The first passage 63B extends through the first bottom wall 63 in a direction parallel to the driving axis R1. An opening of the first passage 63B on the suction chamber 61A side serves as an inlet 63C of a lubricating oil supply passage 63H, which will be described later. The inlet 63C is located at an outermost peripheral portion of the suction chamber 61A serving as a scroll chamber, and more specifically, at the bottom of the suction chamber 61A.

A second passage 63D is formed near the center of the first bottom wall 63. The second passage 63D is located near the driving axis R1 and extends through the first bottom wall 63 in a direction parallel to the driving axis R1. The second passage 63D extends through a portion of the first bottom wall 63 where the second shaft supporting portion 64 is formed. An opening of the second passage 63D on the suction chamber 61A side serves as an outlet 63E1 of the lubricating oil supply passage 63H, which will be described later. The second passage 63D is located above the eccentric shaft 91. The outlet 63E1 is located closer to the driving axis R1 than the third bearing 73 above the eccentric shaft 91.

A groove 63F is recessed in the rear surface 632 of the first bottom wall 63. A lower end of the groove 63F, i.e., one end of the groove 63F, is connected to the first passage 63B, and an upper end of the groove 63F, i.e., the other end of the groove 63F, is connected to the second passage 63D. The rear surface 632 of the first bottom wall 63 corresponds to a “wall surface of the partition wall on the storage chamber side” in the present disclosure.

A lid 77 made of a metal plate is fixed to the rear surface 632 of the first bottom wall 63 by a bolt (not illustrated). The lid 77 extends in a direction in which the groove 63F extends, and closes an opening edge of the groove 63F. As a result, a third passage 63G is defined by an inner surface of the groove 63F and the lid 77. The third passage 63G provides communication between the first passage 63B and the second passage 63D.

The lid 77 is in contact with liquid refrigerant accumulated in the storage chamber 70A, as well as with gas refrigerant in the storage chamber 70A, i.e., the gas refrigerant that is immediately after drawn into the compressor and at a temperature lower than lubricating oil accumulating in the outermost peripheral portion of the suction chamber 61A. Therefore, the third passage 63G serves as a lubricating oil cooling portion 78 that cools lubricating oil flowing through the third passage 63G by the liquid refrigerant and gas refrigerant in the storage chamber 70A.

Accordingly, the first passage 63B, the third passage 63G, and the second passage 63D form the lubricating oil supply passage 63H.

An inverter case having a connector portion is connected to the rear cover 70 on the rear side thereof. An inverter circuit having a circuit board, switching elements, and the like, is accommodated in the inverter case. The inverter circuit is electrically connected to a battery of the vehicle through a connector and to a stator 17, which will be described later, through a hermetic passage formed in the third bottom wall 76, the first bottom wall 63, and the like. Accordingly, the inverter circuit converts DC current supplied from the battery to AC current and supplies its power to the stator 17. It is noted that illustrations of the connector, the inverter case, the inverter circuit, and the battery are omitted.

The electric motor 10 is accommodated in the suction chamber 61A. Thus, the suction chamber 61A also serves as a motor chamber in which the electric motor 10 is accommodated. The electric motor 10 includes the stator 17 and a rotor 11.

The stator 17 has a cylindrical shape extending around the driving axis R1, and has a winding 18. The stator 17 is fitted into the inner peripheral surface 62B of the first outer peripheral wall 62 of the housing body 61, so that the stator 17 is fixed to the housing body 61, and hence the housing 60.

The rotor 11 is formed in a cylindrical shape extending around the driving axis R1 and disposed inside the stator 17. Although a detailed illustration is omitted, the rotor 11 is formed of a plurality of permanent magnets corresponding to the stator 17 and stacking steel plates for fixing the permanent magnets.

The scroll compression part 80 is accommodated in the suction chamber 61A. Thus, the suction chamber 61A also serves as a scroll chamber in which the scroll compression part 80 is accommodated. The suction chamber 61A is an example of the “scroll chamber” of the present disclosure. The scroll compression part 80 is formed of the driving scroll 30 and the driven scroll 40.

As illustrated in FIG. 1, the driving scroll 30 has a driving scroll end plate 31, a driving scroll peripheral wall 32, a driving scroll spiral body 33, a bearing cover body 34, and a cover body 35.

The driving scroll end plate 31 is formed in a substantially circular plate shape extending perpendicularly to the driving axis R1. The driving scroll end plate 31 has a front surface 311 and a rear surface 312 located opposite from the front surface 311.

A discharge valve chamber 36 is formed in the driving scroll end plate 31 and opened at the front surface 311 of the driving scroll end plate 31. The discharge valve chamber 36 is formed of a recess that is partially recessed in the front surface 311 toward a compression chamber 55, which will be described later. The discharge valve chamber 36 has an inner surface shape substantially corresponding to an outer shape of a discharge valve mechanism 56, which will be described later, so that the discharge valve chamber 36 can accommodate the discharge valve mechanism 56. Furthermore, a discharge port 37 is formed near a center of the driving scroll end plate 31 and extends through the driving scroll end plate 31 in the front-rear direction. One end of the discharge port 37 is opened to the compression chamber 55, which will described later, and the other end of the discharge port 37 is opened at a bottom surface of the discharge valve chamber 36. Thus, the discharge port 37 provides communication between the compression chamber 55 and the discharge valve chamber 36. The discharge port 37 is located near the driving axis R1.

The discharge valve mechanism 56 is disposed in the discharge valve chamber 36. The discharge valve mechanism 56 has a discharge reed valve 57, a retainer 58, and a fixing bolt 59. The discharge reed valve 57 and the retainer 58 are fixed to the bottom surface of the discharge valve chamber 36 by the fixing bolt 59. The discharge reed valve 57 is capable of opening and closing the discharge port 37. In addition, the retainer 58 is capable of adjusting an opening degree of the discharge reed valve 57. In the discharge reed valve 57, a valve distal end portion that opens and closes the discharge port 37 is located closer to the driving axis R1 than a fixed proximal end portion that is fixed by the fixing bolt 59.

The driving scroll spiral body 33 is formed integrally with the driving scroll end plate 31 and located inside the driving scroll peripheral wall 32. The driving scroll spiral body 33 extends rearward in parallel to the driving axis R1 from the rear surface 312 of the driving scroll end plate 31. The driving scroll spiral body 33 has a spiral shape around the driving axis R1. More specifically, as viewed from the front, the driving scroll spiral body 33 is formed in a right-handed spiral shape around the driving axis R1 from a center of the spiral.

The driving scroll peripheral wall 32 has the rotor 11 disposed on an outer peripheral edge of the rear surface 312 of the driving scroll end plate 31 and a tubular portion 51, which will be described later, of the cover body 35 behind the rotor 11. The driving scroll peripheral wall 32 extends rearward, i.e., toward the driven scroll 40, in parallel to the driving axis R1 from the outer peripheral edge of the driving scroll end plate 31. The driving scroll peripheral wall 32 has a substantially cylindrical shape extending around the driving axis R1.

The cover body 35 is a bottomed tubular member having the tubular portion 51 and a bottom wall portion 52. The tubular portion 51 has a cylindrical shape extending around the driving axis R1. The bottom wall portion 52 is located at a rear end of the cover body 35. The bottom wall portion 52 has a substantially circular flat plate shape extending perpendicularly to the driving axis R1.

An outer peripheral edge of the bottom wall portion 52 is connected to a rear end of the tubular portion 51. A second boss 53 is formed at a center of the bottom wall portion 52 so as to protrude rearward. A second bearing 72 is fitted into the second boss 53. The second boss 53 has a cylindrical shape extending in a direction in which the driving axis R1 extends around the driving axis R1.

A suction port 54 is formed near the outer peripheral edge of the bottom wall portion 52. The suction port 54 is formed in a substantially elliptical shape extending in a circumferential direction of the cover body 35. The suction port 54 extends through the bottom wall portion 52 in the direction in which the driving axis R1 extends, that is, in the front-rear direction. It is noted that a shape of the suction port 54 and the number of the suction ports 54 may be designed as appropriate.

The bearing cover body 34 has a cover portion 38, and a first boss 39 formed integrally with the cover portion 38.

The cover portion 38 has a substantially circular plate shape extending perpendicularly to the driving axis R1. The cover portion 38 has a front surface 381, and a rear surface 382 located opposite from the front surface 381. A through hole 38A is formed at a center of the cover portion 38.

The first boss 39 protrudes forward from an inner peripheral edge of the cover portion 38, that is, a center of the front surface 381 of the cover portion 38. The first boss 39 has a cylindrical shape extending in the direction in which the driving axis R1 extends around the driving axis R1. An inner space having a columnar shape in the first boss 39 forms a first discharge portion 39A. An inner diameter of the first discharge portion 39A, which is the inner space having the columnar shape in the first boss 39, and an outer diameter of the first boss 39 are smaller than a length of the longest part of the discharge valve mechanism 56. It 20) is noted that the discharge valve chamber 36, the first discharge portion 39A, and the second discharge portion 65A cooperate to form a discharge chamber in this compressor.

A gasket (not illustrated) having a circular plate shape is disposed between the rear surface 382 of the cover portion 38 and the front surface 311 of the driving scroll end plate 31. A communication port having a diameter equal to the inner diameter of the first boss 39 is formed through the gasket at a center thereof. The gasket is held between the front surface 311 of the driving scroll end plate 31 and the rear surface 382 of the cover portion 38, and provides sealing therebetween.

The cover portion 38 of the bearing cover body 34, the gasket (not illustrated), the driving scroll end plate 31 of the driving scroll 30, the rotor 11, and the tubular portion 51 of the cover body 35 are fastened with a plurality of bolts 50 extending in parallel to the driving axis R1. These members are fastened with the bolts 50 after the driven mechanism 20 and the driven scroll 40 are set to the cover body 35, and the discharge valve mechanism 56 is set to the driving scroll end plate 31. In other words, the cover body 35 is connected to the driving scroll end plate 31 with the driven scroll 40 held between the cover body 35 and the driving scroll end plate 31.

The driven scroll 40 has a driven scroll end plate 41, and a driven scroll 10) spiral body 43.

The driven scroll end plate 41 is formed in a substantially circular plate shape extending perpendicularly to a driven axis R2. The driven axis R2 is eccentric to the driving axis R1 and extends in parallel to the driving axis R1. That is, the driven axis R2 is also parallel to the front-rear direction. The driven scroll end plate 41 has a front surface 411 and a rear surface 412 located opposite from the front surface 411.

The rear surface 412 of the driven scroll end plate 41 is partially recessed from a center of the driven scroll end plate 41 toward the compression chamber 55 to form a recess 74 having a bottomed columnar shape. The recess 74 extends in a columnar shape extending in the direction in which the driven axis R2 extends around the driven axis R2. The recess 74 has an inner surface shape corresponding to an outer shape of the third shaft supporting portion 90.

The driven scroll spiral body 43 is formed integrally with the driven scroll end plate 41, and extends forward, that is, toward the driving scroll end plate 31 of the driving scroll 30, in parallel to the driven axis R2 from the front surface 411 of the driven scroll end plate 41. The driven scroll spiral body 43 has a spiral shape around the driven axis R2. More specifically, as viewed from the front, the driven scroll spiral body 43 is formed in a right-handed spiral shape around the driven axis R2 from a center of the spiral.

The driven mechanism 20 is formed of four anti-rotation pins 21 and four rings 22. It is noted that the number of the anti-rotation pins 21 and the number of the rings 22 may be designed appropriately as long as each of them is three or more. In addition, two of the anti-rotation pins 21 and two of the rings 22 are illustrated in FIG. 1.

The anti-rotation pins 21 are inserted into and fixed to the rear surface 412 of the driven scroll end plate 41. Thus, the anti-rotation pins 21 are fixed to the driven scroll end plate 41 so that the anti-rotation pins 21 protrudes rearward from the driven scroll end plate 41.

The rings 22 are provided in a front surface 521 of the bottom wall portion 52 of the cover body 35 of the driving scroll 30 so as to face their associated anti-rotation pins 21. The rings 22 are fitted into bottomed circular holes that are recessed in the front surface 521 of the bottom wall portion 52.

In this compressor, the scroll compression part 80, which is formed of the driving scroll 30 and the driven scroll 40, is disposed in the suction chamber 61A.

In the driving scroll 30, the rotor 11 is integrated with the driving scroll peripheral wall 32. Furthermore, in the driving scroll 30, the first bearing 71 is interposed between the first shaft supporting portion 66 of the bearing housing 67 and the first boss 39 of the bearing cover body 34, and the second bearing 72 is interposed between the second shaft supporting portion 64 of the first bottom wall 63 and the second boss 53 of the cover body 35. Thus, the driving scroll 30 is supported by the housing 60 so as to be rotatable around the driving axis R1. Here, in this compressor, the driving scroll 30 is supported in a so-called double-supported manner by the housing 60.

On the other hand, the driven scroll 40 is located behind the driving scroll end plate 31 in the driving scroll 30 with the driven scroll spiral body 43 facing the driving scroll end plate 31. Thus, the rear surface 312 of the driving scroll end plate 31 and the front surface 411 of the driven scroll end plate 41 face each other in the direction in which the driving axis R1 extends and in the direction in which the driven axis R2 extends. Then, in the driving scroll 30 and the driven scroll 40, the driving scroll spiral body 33 meshes with the driven scroll spiral body 43 inside the driving scroll peripheral wall 32, and the anti-rotation pins 21 are inserted into their associated rings 22. Thus, the driven scroll 40 is assembled into the driving scroll 30 with the driving scroll end plate 31 and the driven scroll end plate 41 facing each other in the front-rear direction. The driving scroll spiral body 33 and the driven scroll spiral body 43 form therebetween the compression chamber 55.

In the driven scroll 40, the third bearing 73 is interposed between the third shaft supporting portion 90, which is eccentric to the second shaft supporting portion 64 of the first bottom wall 63, and the recess 74 of the driven scroll end plate 41. Thus, the driven scroll 40 is supported by the housing 60 so as to be rotatable around the driven axis R2. Here, in this compressor, the driven scroll 40 is supported in a so-called cantilever manner by the housing 60.

In this compressor having the above-described configuration, the inverter circuit (not illustrated) supplies power to the stator 17 while controlling operation of the electric motor 10, which operates the electric motor 10. This rotates the rotor 11, which drives the driving scroll 30 to rotate around the driving axis R1 in the suction chamber 61A. That is, the driving scroll 30 including the driving scroll peripheral wall 32 integrated with the rotor 11 is rotatably driven. At this time, in the driven mechanism 20, the anti-rotation pins 21 each slide on inner peripheral surfaces of their associated rings 22 to rotate the rings 22 relative to the anti-rotation pins 21 around the center thereof. Thus, the driven mechanism 20 transmits torque of the driving scroll 30 to the driven scroll 40.

As a result, the driven scroll 40 is driven to rotate around the driven axis R2 by the driving scroll 30 and the driven mechanism 20. At this time, the driven mechanism 20 prevents the driven scroll 40 from rotating. Thus, with the driving scroll 30 and the driven scroll 40 rotationally driven, the driven scroll 40 makes orbital motion around the driving axis R1 relative to the driving scroll 30, which changes a volume of the compression chamber 55.

As a result, refrigerant in the suction chamber 61A is drawn into the compression chamber 55 through the suction port 54, and compressed in the compression chamber 55. Then, the refrigerant gas compressed to a discharge pressure in the compression chamber 55 is discharged to the discharge valve chamber 36 through the discharge port 37, is then discharged to the second discharge portion 65A though the first discharge portion 39A, and is further discharged to the condenser through the discharge communication port 65B. In this manner, air conditioning is performed by the vehicle air conditioner.

Here, the scroll compression part 80 has a plurality of sliding portions that can generate sliding heat. For example, the sliding portions are the first bearing 71, the second bearing 72, the third bearing 73, a sliding portion 81 between the rear surface 412 of the driven scroll end plate 41 and the distal end surface 641 of the second shaft supporting portion 64, a sliding portion 82 between the rear surface 412 of the driven scroll end plate 41 and the front surface 521 of the bottom wall portion 52 of the cover body 35, the driven mechanism 20, a sliding portion between the driving scroll spiral body 33 and the driven scroll spiral body 43, a sliding portion between the distal end surface of the driving scroll spiral body 33 and the front surface 411 of the driven scroll end plate 41, and a sliding portion between the distal end of the driven scroll spiral body 43 and the rear surface 312 of the driving scroll end plate 31. These sliding portions need to be lubricated and cooled by supplying lubricating oil.

In this compressor, lubricating oil that accumulates in the suction chamber 61A corresponding to the scroll chamber is cooled by liquid refrigerant in the storage chamber 70A and then supplied to the sliding portion during operation.

That is, since centrifugal force acts in the rotating scroll compression part 80, the lubricating oil is separated from the refrigerant by centrifugation, and the lubricating oil separated from the refrigerant flows out of the scroll compression part 80 into the suction chamber 61A. In the suction chamber 61A, a flow of fluid is generated in a rotational direction due to an influence of the centrifugal force of the rotating scroll compression part 80. Therefore, the lubricating oil is accumulated in the outermost peripheral portion of the suction chamber 61A due to the centrifugal force, which forms an oil storage portion 83.

The inlet 63C of the lubricating oil supply passage 63H is opened at the bottom of the suction chamber 61A. Then, the outlet 63E1 of the lubricating oil supply passage 63H is opened at the distal end surface 641 of the second shaft supporting portion 64. That is, the outlet 63E1 is located inside the scroll compression part 80, outside the compression chamber 55, and near the driving axis R1.

Pressure in the suction chamber 61A is highest at the bottom of the suction chamber 61A corresponding to the outermost peripheral portion. On the other hand, the pressure in the scroll compression part 80 outside the compression chamber 55 is lower than the pressure in the suction chamber 61A outside the scroll compression part 80. In addition, since the refrigerant in the suction 20) chamber 61A (scroll chamber) is drawn into the scroll compression part 80 through the suction port 54, the pressure at the suction port 54 of the scroll compression part 80 becomes lower than the pressure in the outer peripheral portion of the suction chamber 61A. In particular, the pressure near the driving axis R1 where the second shaft supporting portion 64 is located is a portion where a pressure is relatively low in the scroll compression part 80 outside the compression chamber 55. Therefore, the pressure at the outlet 63E1 of the lubricating oil supply passage 63H is lower than the pressure at the inlet 63C of the lubricating oil supply passage 63H, and there is a pressure difference between the outlet 63E1 and the inlet 63C. As a result, the lubricating oil in the oil storage portion 83 accumulating at the bottom of the suction chamber 61A is introduced into the inlet 63C of the lubricating oil supply passage 63H, and the lubrication oil flows through the lubricating oil supply passage 63H and is discharged from the outlet 63E1 to the distal end surface 641 of the second shaft supporting portion 64. Lubricating oil from the lubricating oil supply passage 63H is continuously supplied during the operation of the compressor.

The lubricating oil discharged from the outlet 63E1 of the lubricating oil supply passage 63H flows toward the outer periphery of the outlet 63E1 due to the centrifugal force. This allows lubricating oil to be supplied to the third bearing 73, the sliding portion 81 between the rear surface 412 of the driven scroll end plate 41 and the distal end surface 641 of the second shaft supporting portion 64, the second bearing 72, the sliding portion 82 between the rear surface 412 of the driven scroll end plate 41 and the front surface 521 of the bottom wall portion 52 of the cover body 35, and the driven mechanism 20, which are located on the outer peripheral side of the outlet 63E1. These sliding portions, i.e., the third bearing 73, the sliding portion 81 between the rear surface 412 of the driven scroll end plate 41 and the distal end surface 641 of the second shaft supporting portion 64, the second bearing 72, the sliding portion 82 between the rear surface 412 of the driven scroll end plate 41 and the front surface 521 of the bottom wall portion 52 of the cover body 35, and the driven mechanism 20, may be collectively referred to as a lubricating oil supplied sliding portion.

In this way, the lubricating oil accumulated in the oil storage portion 83 at the bottom of the suction chamber 61A can be continuously supplied to the lubricating oil supplied sliding portion, thereby effectively preventing an increase in sliding resistance due to insufficient lubricating oil in the lubricating oil supplied sliding portion.

Moreover, the lubricating oil flowing through the lubricating oil supply passage 63H is cooled in the lubricating oil cooling portion 78 by the liquid refrigerant and gas refrigerant in the storage chamber 70A. Therefore, the lubricating oil supplied sliding portion can be lubricated with lubricating oil with an appropriate viscosity. In addition, since the lubricating oil supplied sliding portion can be cooled with lubricating oil at a lower temperature, it is possible to prevent the viscosity of the lubricating oil from decreasing due to heat from the lubricating oil supplied sliding portion. As a result, an increase in sliding resistance in the lubricating oil supplied sliding portion can be suppressed.

Therefore, the compressor of the first embodiment supplies the lubricating oil that accumulates in the scroll chamber during operation to the sliding portions and enhances the cooling effect of the lubricating oil on the sliding portion, so that an increase in the sliding resistance in the sliding portion is suppressed, and a decrease in efficiency is thus suppressed.

In addition, in this compressor, the lubricating oil supply passage 63H is formed of the first passage 63B, the third passage 63G, and the second passage 63D formed in the first bottom wall 63 that do not rotate even during the operation of the compressor. That is, the lubricating oil supply passage 63H extends through the second shaft supporting portion 64, which is a non-rotating body, and is opened at the distal end surface 641 of the second shaft supporting portion 64. Therefore, supplying of lubricating oil through the lubricating oil supply passage 63H becomes stable.

Furthermore, the second bearing 72 and the third bearing 73 are located close to the driving axis R1 in the scroll compression part 80. In the scroll compression part 80, the amount of lubricating oil tends to become insufficient as it is closer to the driving axis R1. In this regard, in this compressor, the lubricating oil supply passage 63H extends through the second shaft supporting portion 64, and the outlet 63E1 of the lubricating oil supply passage 63H is opened at a position close to the driving axis R1 than the third bearing 73 is, so that lubricating oil can be supplied effectively to the second bearing 72 and the third bearing 73 where the amount of lubricating oil tends to become insufficient.

Second Embodiment

As illustrated in FIG. 3, in the compressor of the second embodiment, the position of the outlet 63E1 of the lubricating oil supply passage 63H in the compressor of the first embodiment is changed to a position of an outlet 63E2.

That is, a fourth passage 63J is formed in the second boss 53 of the bottom wall portion 52. The fourth passage 63J extends through the second boss 53 in a direction parallel to the driving axis R1. The fourth passage 63J is located near the top of the second boss 53. A front opening of the fourth passage 63J serves as the outlet 63E2 of the lubricating oil supply passage 63H.

With the formation of the fourth passage 63J, the position of the second passage 63D is changed to a position of a fifth passage 63K. The fifth passage 63K and the fourth passage 63J are positioned on the same straight line, and an opening of the fifth passage 63K and an opening of the fourth passage 63J on the rear side are connected to each other. In addition, with the change in position from the second passage 63D to the fifth passage 63K, the groove 63F extends upward, and a sixth passage 63L is defined by an inner surface of the groove 63F and the lid 77. The sixth passage 63L provides communication between the first passage 63B and the fifth passage 63K. As a result, the first passage 63B, the sixth passage 63L, the fifth passage 63K, and the fourth passage 63J cooperate to form the lubricating oil supply passage 63H.

In the compressor of the second embodiment, the fourth passage 63J is formed in the second boss 53 of the cover body 35, and the outlet 63E2 of the lubricating oil supply passage 63H is opened at the front surface 521 of the bottom wall portion 52 of the cover body 35.

As a result, lubricating oil flowing out from the outlet 63E2 of the lubricating oil supply passage 63H, which is opened at the front surface 521 of the bottom wall portion 52 of the cover body 35, is supplied to the sliding portion 82 between the rear surface 412 of the driven scroll end plate 41 and the front surface 521 of the bottom wall portion 52 and the driven mechanism 20, which are located on the outer peripheral side of the outlet 63E2 by the action of centrifugal force.

This allows lubricating oil cooled by the liquid refrigerant and gas refrigerant in the storage chamber 70A to be supplied directly to the sliding portion 82 between the rear surface 412 of the driven scroll end plate 41 and the front surface 521 of the bottom wall portion 52, and the driven mechanism 20 without passing through other sliding portions, thereby effectively cooling the sliding portion 82 between the rear surface 412 of the driven scroll end plate 41 and the front surface 521 of the bottom wall portion 52 and the driven mechanism 20.

The other components and operation of this compressor are the same as those of the compressor of the first embodiment, and the identical components are designated by the same reference numerals and detailed description of the components is omitted.

Third Embodiment

As illustrated in FIG. 4, in the compressor of a third embodiment, the position of the outlet 63E1 of the lubricating oil supply passage 63H in the compressor of the first embodiment is changed to a position of an outlet 63E3.

That is, a seventh passage 63M is formed in the third shaft supporting portion 90 disposed on the distal end surface 641 of the second shaft supporting portion 64. The seventh passage 63M extends through the third shaft supporting portion 90 in a direction parallel to the driving axis R1. The seventh passage 63M is located near the top of the third shaft supporting portion 90. A front opening of the seventh passage 63M serves as the outlet 63E3 of the lubricating oil supply passage 63H.

With the formation of the seventh passage 63M, the position of the second passage 63D is changed to a position of an eighth passage 63N. The eighth passage 63N and the seventh passage 63M are positioned on the same straight line, and an opening of the eighth passage 63N and an opening of the seventh passage 63M on the rear side are connected to each other. In addition, with the change in position from the second passage 63D to the eighth passage 63N, a length of the groove 63F is changed, and a ninth passage 63P is defined by the inner surface of the groove 63F and the lid 77. The ninth passage 63P provides communication between the first passage 63B and the eighth passage 63N. As a result, the first passage 63B, the ninth passage 63P, the eighth passage 63N, and the seventh passage 63M cooperate to form the lubricating oil supply passage 63H.

In the compressor of the third embodiment, the seventh passage 63M is formed in the third shaft supporting portion 90, and the outlet 63E3 of the lubricating oil supply passage 63H is opened at a distal end surface 901 of the third shaft supporting portion 90. Similarly to the compressor of the first embodiment, this allows lubricating oil to be supplied to the third bearing 73, the sliding portion 81 between the rear surface 412 of the driven scroll end plate 41 and the distal end surface 641 of the second shaft supporting portion 64, the second bearing 72, the sliding portion 82 between the rear surface 412 of the driven scroll end plate 41 and the front surface 521 of the bottom wall portion 52 of the cover body 35, and the driven mechanism 20, which are located on the outer periphery side of the outlet 63E3.

The other components and operation of this compressor are the same as those of the compressor of the first embodiment, and the identical components are designated by the same reference numerals and detailed description of the components is omitted.

Fourth Embodiment

As illustrated in FIG. 5, in the compressor of a fourth embodiment, the position of the outlet 63E1 of the lubricating oil supply passage 63H in the compressor of the first embodiment is changed to a position of an outlet 63E4.

That is, a tenth passage 63Q is formed in the eccentric shaft 91 provided in the second shaft supporting portion 64. The tenth passage 63Q extends through the eccentric shaft 91 in a direction parallel to the driving axis R1. A front opening of the tenth passage 63Q serves as the outlet 63E4 of the lubricating oil supply passage 63H.

With the formation of the tenth passage 63Q, the position of the second passage 63D is changed to a position of an eleventh passage 63R. The eleventh passage 63R and the tenth passage 63Q are positioned on the same straight line, and an opening of the eleventh passage 63R and an opening of the tenth passage 63Q on the rear side are connected to each other. In addition, with the change in position from the second passage 63D to the eleventh passage 63R, the length of the groove 63F is changed, and a twelfth passage 63S is defined by the inner surface of the groove 63F and the lid 77. The twelfth passage 63S provides communication between the first passage 63B and the eleventh passage 63R. As a result, the first passage 63B, the twelfth passage 63S, the eleventh passage 63R, and the tenth passage 63Q cooperate to form the lubricating oil supply passage 63H.

In the compressor of the fourth embodiment, the tenth passage 63Q is formed in the eccentric shaft 91, and the outlet 63E4 of the lubricating oil supply passage 63H is opened at a distal end surface 911 of the eccentric shaft 91. Similarly to the compressor of the first embodiment, this allows lubricating oil to be supplied to the third bearing 73, the sliding portion 81 between the rear surface 412 of the driven scroll end plate 41 and the distal end surface 641 of the second shaft supporting portion 64, the second bearing 72, the sliding portion 82 between the rear surface 412 of the driven scroll end plate 41 and the front surface 521 of the bottom wall portion 52 of the cover body 35, and the driven mechanism 20, which are located on the outer periphery side relative to the outlet 63E4.

The other components and operation of this compressor are the same as those of the compressor of the first embodiment, and the identical components are designated by the same reference numerals and detailed description of the components is omitted.

Fifth Embodiment

As illustrated in FIG. 6, in the compressor of a fifth embodiment, the configurations of the lubricating oil supply passage 63H and the lubricating oil cooling portion 78 are changed.

The first passage 63B and the second passage 63D in the compressor of the fifth embodiment are formed at the same positions as those in the compressor of the first embodiment. A pipe 84 is connected to the first passage 63B and the second passage 63D. The pipe 84 is disposed in the storage chamber 70A and extends in the up-down direction. One end and the other end of the pipe 84 are bent and form a lower bent portion 841 and an upper bent portion 842, respectively, which are connected to the first passage 63B and the second passage 63D, respectively.

Thus, the first passage 63B, a thirteenth passage 63T in the pipe 84, and the second passage 63D cooperate to form the lubricating oil supply passage 63H. A portion of the pipe 84 disposed in the storage chamber 70A serves as the lubricating oil cooling portion 78.

In this embodiment, lubricating oil passing through the thirteenth passage 63T in the pipe 84 can be cooled by liquid refrigerant and gas refrigerant in the storage chamber 70A through a peripheral wall of the pipe 84.

The other components and operation of this compressor are the same as those of the compressor of the first embodiment, and the identical components are designated by the same reference numerals and detailed description of the components is omitted.

Although the present disclosure has been described above based on the first to fifth embodiments, the present disclosure is not limited to the above-described first to fifth embodiments, and may be modified as appropriate within the gist of the present disclosure.

For example, in each of the compressors of the first to fifth embodiments, the inlet 63C of the lubricating oil supply passage 63H is provided at the bottom of the scroll chamber, but the present disclosure is not limited thereto, and the inlet of the lubricating oil supply passage 63H may be provided at an outermost peripheral portion, other than the bottom, of the scroll chamber. In addition, the position of the inlet of the lubricating oil supply passage 63H does not have to be at the outermost peripheral portion as long as it is in a position that is in communication with the oil storage portion in the scroll chamber.

Furthermore, in each of the compressors of the first to fifth embodiments, the lubricating oil supply passage 63H has one outlet 63E1 to 63E4, but the present disclosure is not limited thereto, and the lubricating oil supply passage 63H may have a plurality of outlets.

In each of the compressors of the first to fifth embodiments, the lubricating oil cooling portion 78 is formed by the groove 63F recessed into the wall surface of the first bottom wall 63 on the storage chamber 70A side serving as the partition wall and the lid 77, or the pipe 84, provided in the storage chamber 70A, but the present disclosure is not limited thereto. The lubricating oil cooling portion may be formed by providing a passage extending from the outer peripheral side to the inner peripheral side inside the partition wall, or the lubricating oil cooling portion may be formed on the scroll chamber side.

In addition, in each of the compressors of the first to fifth embodiments, the driving scroll 30 is supported relative to the housing 60 in the double-supported manner, and the driven scroll 40 is supported relative to the housing 60 in the cantilever manner. However, the present disclosure is not limited thereto, both the driving scroll 30 and the driven scroll 40 may be supported relative to the housing 60 in the cantilever manner.

In each of the compressors of the first to fifth embodiments, the suction port 54 is formed in the cover body 35 of the driving scroll 30. However, the present disclosure is not limited thereto, and the suction port may be formed in the driving scroll end plate 31 of the driving scroll 30. In the compressor in which the driving scroll 30 and the driven scroll 40 are each supported in the cantilever manner by the housing 60, the suction port may be formed either in the driving scroll end plate 31 or in the driven scroll end plate 41.

In each of the compressors of the first to fifth embodiments, in the driving scroll 30, the bearing cover body 34 having the cover portion 38 that covers a part of the discharge valve chamber 36 and a part of the discharge valve mechanism 56 is connected to the front surface 311 of the driving scroll end plate 31 in which the discharge valve chamber 36 accommodating the discharge valve mechanism 56 is recessed. In addition, the first discharge portion 39A, which is the inner space of the first boss 39 of the bearing cover body 34, is in communication with the discharge valve chamber 36. However, the present disclosure is not limited thereto, and the bearing cover body may be omitted, the discharge valve mechanism may be accommodated in the boss protruding from and formed integrally with the driving scroll end plate or the driven scroll end plate, and the bearing may be attached to the boss.

In each of the compressors of the first to fifth embodiments, the driven mechanism 20 is formed of the anti-rotation pins 21 and the rings 22. However, the present disclosure is not limited thereto, and the driven mechanism 20 may be formed of a pin-ring-pin mechanism in which two pins slide on an inner peripheral surface of one free ring, a pin-and-pin mechanism in which outer peripheral surfaces of two pins slide on each other, a mechanism using an Oldham coupling, or the like.

In the compressors of the first to fifth embodiments, the driving scroll 30 is integrated with the rotor 11 by integrating the rotor 11 with the driving scroll peripheral wall 32. However, the present disclosure is not limited thereto, and the compressor may have a configuration in which the driving scroll 30 is disposed spaced from the rotor 11 in the direction where the driving axis R1 extends by connecting the driving scroll 30 to the rotor 11 via a driving shaft so that motive power is transmitted.

Additional Note 1

A co-rotating scroll compressor comprising:

• • a housing; a driving mechanism; a driving scroll; a driven scroll; and a driven mechanism,
  • the housing having a scroll chamber in which the driving scroll and the driven scroll are accommodated, a storage chamber that separates a refrigerant drawn from an outside into gas and liquid and stores liquid refrigerant, and a partition wall that separates the storage chamber from the scroll chamber,
  • the driving scroll being configured to be driven to rotate around a driving axis by the driving mechanism,
  • the driven scroll being eccentric to the driving scroll, and configured to be driven to rotate around a driven axis by the driving scroll and the driven mechanism,
  • a supporting portion protruding from the partition wall into the scroll chamber with the driving axis at a center,
  • the driving scroll being supported by a bearing disposed between the driving scroll and the supporting portion so as to be driven to rotate around the driving axis,
  • a scroll compression part being formed of the driving scroll and the driven scroll,
  • an oil storage portion in which lubricating oil is stored being provided in the scroll chamber, and
  • a lubricating oil supply passage in communication with the oil storage portion, through which the lubricating oil is supplied to the scroll compression part or the bearing, characterized in that
  • the lubricating oil supply passage has a lubricating oil cooling portion that cools the lubricating oil in the lubricating oil supply passage with the refrigerant in the storage chamber.

Additional Note 2

The co-rotating scroll compressor according to Additional note 1, wherein

• • the driving scroll has a driving scroll end plate, and a driving scroll spiral body that is formed integrally with the driving scroll end plate and protrudes toward the driven scroll in a spiral shape, and a cover body connected to the driving scroll end plate with the driven scroll held between the cover body and the driving scroll end plate,
  • the driven scroll has a driven scroll end plate, and a driven scroll spiral body that is formed integrally with the driven scroll end plate and protrudes toward the driving scroll end plate in a spiral shape, and
  • the lubricating oil is supplied from the lubricating oil supply passage to a sliding portion between the driven scroll end plate and the cover body.

Additional note 3

The co-rotating scroll compressor according to Additional note 1 or 2, wherein

• • the lubricating oil is supplied from the lubricating oil supply passage to the bearing, and
  • the lubricating oil supply passage extends through the supporting portion.

Additional note 4

The co-rotating scroll compressor according to Additional note 2, further comprising:

a driven shaft portion that is eccentric to the driving axis and extends in parallel to the driving axis in the housing; and a bushing into which the driven shaft portion is inserted, wherein

• • a bushing bearing is disposed between the driven scroll and the bushing,
  • the lubricating oil is supplied from the lubricating oil supply passage to the bushing bearing, and
  • the lubricating oil supply passage extends through the driven shaft portion or the bushing.

Additional note 5

The co-rotating scroll compressor according to Additional note 2, wherein

• • the lubricating oil supply passage extends through the cover body.

Additional Note 6

The co-rotating scroll compressor according to Additional note 1 to 5, wherein

• • the lubricating oil cooling portion is formed of a groove that is recessed in a wall surface of the partition wall on the storage chamber side, and a lid that has a plate shape, extends in a direction in which the groove extends, and is fixed to the wall surface so as to close an opening of the groove, and
  • a passage defined by an inner surface of the groove and the lid forms a part of the lubricating oil supply passage.

Additional Note 7

The co-rotating scroll compressor according to any one of Additional note 1 to 5, wherein

• • the lubricating oil cooling portion is formed of a pipe disposed in the storage chamber, and
  • a passage inside the pipe forms a part of the lubricating oil supply passage.

INDUSTRIAL APPLICABILITY

The present disclosure is applicable to an air conditioner for a vehicle, or the like.

REFERENCE SIGNS LIST

• • 10 electric motor (driving mechanism)
  • 20 driven mechanism
  • 30 driving scroll
  • 31 driving scroll end plate
  • 33 driving scroll spiral body
  • 35 cover body
  • 40 driven scroll
  • 41 driven scroll end plate
  • 43 driven scroll spiral body
  • 55 compression chamber
  • 60 housing
  • 61A suction chamber (scroll chamber)
  • 63 first bottom wall (partition wall)
  • 632 rear surface (wall surface)
  • 63F groove
  • 63H lubricating oil supply passage
  • 64 second shaft supporting portion (supporting portion)
  • 70A storage chamber
  • 72 second bearing (bearing, sliding portion)
  • 73 third bearing (bushing bearing, sliding portion)
  • 77 lid
  • 78 lubricating oil cooling portion
  • 80 scroll compression part
  • 81, 82 sliding portion
  • 83 oil storage portion
  • 84 pipe
  • 90 third shaft supporting portion (bushing)
  • 91 eccentric shaft (driven shaft portion)
  • R1 driving axis
  • R2 driven axis