Rotating scroll compressor

Abstract

This co-rotating scroll compressor is provided in a housing (60) with: a suction chamber (61A) serving as a scroll chamber for accommodating a scroll compressor unit (80); a retention chamber (70A) adjacent to the suction chamber (61A), having a first base wall (63) serving as a partition wall separating the retention chamber and the suction chamber; and a lubricating oil supply passage (63H). The lubricating oil supply passage (63H) communicates with an oil storage unit (83) provided in the suction chamber (61A) and supplies lubricating oil to the scroll compressor unit (80), a second bearing (72), a third bearing (73), and the like. Partially along the lubricating oil supply channel (63H), a lubricating oil cooling unit (78) is provided, which cools the lubricating oil within the lubricating oil supply channel (63H) by using a liquid refrigerant in the retention chamber (70A).

Description

Technical area

[0001] The present invention relates to a co-rotating scroll compressor. State of the art

[0002] A co-rotating scroll compressor is conventionally known. This co-rotating scroll compressor comprises a drive mechanism, a drive scroll, a driven mechanism, a driven scroll, and a housing.

[0003] The housing has a scroll chamber that houses a scroll compression part formed from the drive scroll and the driven scroll.

[0004] The drive spiral is driven by the drive mechanism to rotate about a drive axis. The driven spiral is arranged eccentrically to the drive spiral and is driven by the drive spiral and the driven mechanism to rotate about a driven axis.

[0005] The drive scroll has a drive scroll end plate and a drive scroll body. The drive scroll end plate extends to intersect the drive axis. The drive scroll body protrudes from the drive scroll end plate toward the driven scroll and has a spiral shape.

[0006] The driven scroll has a driven scroll end plate and a driven scroll body. The driven scroll end plate extends to intersect the driven axis. The driven scroll body protrudes from the driven scroll end plate toward the drive scroll and has a spiral shape.

[0007] The drive scroll and the driven scroll form a compression chamber with the drive scroll and driven scroll facing each other. The volume of the compression chamber is changed by the drive rotation of the drive scroll and the driven rotation of the driven scroll. Fluid drawn from a suction chamber is compressed with the change in the volume of the compression chamber and discharged to a discharge chamber.

[0008] In a rotary compressor in which a compression member rotates to compress fluid in a compression chamber, a sliding portion, such as a bearing, that rotatably supports the compression member relative to the housing generates heat due to sliding friction, similar to a co-rotating scroll compressor. Furthermore, a continuous loop is created in which sliding resistance is increased by a reduction in lubricating oil viscosity within the bearing due to heat, and a heat amount is increased by the increased sliding resistance. Furthermore, an increase in the sliding resistance of the sliding portion due to sliding loss leads to a reduction in efficiency.

[0009] Therefore, during the 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.

[0010] 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 listPatent literature

[0011] Patent Literature 1: Japanese Patent Application Laid-Open No. 2005-146987 Summary of the inventionTechnical problem

[0012] However, in view of a 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 of the above-described conventional rotary compressor, and the measure may be insufficient.

[0013] Specifically, in the co-rotating scroll compressor, in the scroll chamber accommodating the scroll compression part, lubricating oil flows out from the rotating scroll compression part. Due to the influence of centrifugal force of the rotating scroll compression part, fluid flow is generated in the rotation direction, thereby generating centrifugal force. As a result, lubricating oil accumulates in an outermost peripheral portion of the scroll chamber. If the amount of lubricating oil accumulated at the outermost peripheral portion of the scroll chamber further increases, the amount of lubricating oil to be supplied to the sliding portion decreases. If the amount of lubricating oil decreases, sliding resistance increases, which may lead to a reduction in efficiency.

[0014] The present invention has been made in view of the above-mentioned conventional circumstance and is directed to providing a co-rotating scroll compressor which can suppress an increase in sliding resistance in the sliding portion and thus a reduction in efficiency by supplying lubricating oil, which accumulates in the scroll chamber during operation, to the sliding portion and improving a cooling efficiency in the sliding portion with the lubricating oil. Solution to the problem

[0015] A rotating scroll compressor has the following features: a housing; a drive mechanism; a drive spiral; a driven spiral; and a driven mechanism, wherein the housing has a spiral chamber in which the drive spiral and the driven spiral are accommodated, a storage chamber which separates a refrigerant sucked from an outside into a gas and a liquid and stores liquid refrigerant, and a partition wall which separates the storage chamber from the spiral chamber, the drive spiral is configured to be driven by the drive mechanism to rotate about a drive axis, the driven scroll is eccentric to the drive scroll and is configured to be driven by the drive scroll and the driven mechanism to rotate about a driven axis, a support section with the drive axis at a center protrudes from the dividing wall into the spiral chamber, the drive spiral is supported by a bearing arranged between the drive spiral and the support section to be driven to rotate about the drive axis, a spiral compression part is formed from the drive spiral and the driven spiral and an oil storage section in which lubricating oil is stored is provided in the spiral chamber, a lubricating oil supply passage in communication with the oil storage section 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 section that cools the lubricating oil in the lubricating oil supply passage with the refrigerant in the storage chamber.

[0016] In the co-rotating scroll compressor of the present invention, an oil storage portion in which 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, a fluid flow in the rotational direction is generated due to an influence of the centrifugal force of the rotating scroll compression part. 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.

[0017] 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 the fluid. For this reason, the pressure at the outer peripheral portion, which is more subject to the centrifugal force of the fluid, is higher when comparing a pressure at the outer peripheral portion of the scroll chamber and a pressure on one side of the rotation center of the scroll compression part. Furthermore, a pressure at the suction port of the scroll compression part is lower than the pressure at the outer peripheral portion of the scroll chamber because fluid in the scroll chamber is sucked into the scroll compression part through the suction port provided in the drive scroll or the driven scroll.

[0018] Therefore, the pressure at the inlet of the lubricating oil supply passage is higher than the pressure at the outlet if, for example, 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 to an inside of the scroll compression part or a rotation center side of the scroll compression part within the scroll compression chamber. Thus, due to the pressure difference, lubricating oil accumulated in the oil storage portion provided at the outer peripheral portion of the scroll chamber is introduced into the inlet of the lubricating oil supply passage and is supplied from the outlet of the lubricating oil supply passage to the inside of the scroll compression part and the rotation center side of the scroll compression part in the scroll chamber.The lubricating oil coming out of the outlet of the lubricating oil supply passage flows to an outer peripheral side of the outlet due to centrifugal force and is supplied to the scroll compression part and the bearings located on the outer peripheral side of the outlet.

[0019] In this way, 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 at the sliding portion.

[0020] 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 is supplied to the scroll compression part and the sliding portion of the bearing at a temperature lower than the lubricating oil stored in the oil storage portion of the scroll chamber. As a result, the sliding portion can be lubricated with lubricating oil having an appropriate viscosity and is cooled with cooler lubricating oil, making it possible to prevent the viscosity of the lubricating oil from decreasing due to heat from the sliding portion. This suppresses an increase in sliding resistance in the scroll compression part and the sliding portion of the bearing.

[0021] Thus, according to the co-rotating scroll compressor of the present invention, lubricating oil accumulated in the scroll chamber during operation is supplied to the sliding portion, and cooling efficiency by such lubricating oil in the sliding portion is improved, so that an increase in sliding resistance at the sliding portion is suppressed and thus a reduction in efficiency is suppressed.

[0022] The drive scroll may include a drive scroll end plate and a drive scroll scroll body integrally formed with the drive scroll end plate and projecting in a spiral shape toward the driven scroll, and a cover body connected to the drive scroll end plate, which is held between the cover body and the drive scroll end plate. Furthermore, the driven scroll may include a driven scroll end plate and a driven scroll scroll body integrally formed with the driven scroll end plate and projecting in a spiral shape toward the drive scroll end plate. Further, it is preferable that the lubricating oil be supplied from the lubricating oil supply passage to a sliding portion between the driven scroll end plate and the cover body.

[0023] In this case, the sliding portion between the driven scroll end plate and the cover body in the scroll compression part requires lubricating oil. In this regard, the lubricating oil is supplied from the lubricating oil supply passage to the sliding portion between the driven scroll end plate and the cover body. Therefore, the lubricating oil cooled by the liquid refrigerant can be properly supplied to the sliding portion between the driven scroll end plate and the cover body.

[0024] 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 support portion.

[0025] In this case, the lubricating oil cooled by the liquid refrigerant can be appropriately supplied from the lubricating oil supply passage extending through the support portion to the bearing located on the outer peripheral side of the support portion.

[0026] 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 the rotation center of the scroll compression part approaches. If the lubricating oil supply passage extends through the support portion, it becomes possible to supply an appropriate amount of lubricating oil to the bearing where the amount of lubricating oil tends to be insufficient.

[0027] Furthermore, the support portion does not rotate even during operation of the scroll compression part. This allows lubricating oil to be stably discharged from the outlet of the lubricating oil supply passage extending through the support portion and opened at a distal end surface thereof.

[0028] A driven shaft portion, which is eccentric to the drive axis and extends parallel to the drive axis, may be provided in the housing, and a bushing into which the driven shaft portion is fitted may be provided. Furthermore, a sliding bearing may be arranged between the driven scroll and the bushing. It is preferable that lubricating oil be supplied to the sliding bearing from the lubricating oil supply passage. Furthermore, it is preferable that the lubricating oil supply passage extends through the driven shaft portion or the bushing.

[0029] In this case, the lubricating oil cooled by the liquid refrigerant can be appropriately supplied from the lubricating oil supply passage extending through the driven shaft portion or the bearing to the sliding bearing located on the outer peripheral side relative to the driven shaft portion or the bushing.

[0030] In addition, the journal bearing is located 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 section or the housing, it is possible to supply sufficient lubricating oil to the journal bearing where the amount of lubricating oil tends to be insufficient.

[0031] It is preferable that the lubricating oil supply passage extends through the cover body.

[0032] In this case, the lubricating oil cooled by the liquid refrigerant can be appropriately 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.

[0033] It is preferable that the lubricating oil cooling portion is formed from a groove recessed in a wall surface of the partition wall on the storage chamber side, and a cover having a plate shape, extending in a direction in which the groove extends, and fixed to the wall surface to close an opening of the groove. It is preferable that a passage defined by an inner surface of the groove and the cover forms part of the lubricating oil supply passage.

[0034] In this case, the lubricating oil flowing through the passage defined by the inner surface of the groove and the cover can be cooled by the liquid refrigerant in the storage chamber through the cover.

[0035] It is preferable that the lubricating oil cooling portion be formed from a tube disposed in the storage chamber. It is preferable that a passage within the tube forms part of the lubricating oil supply passage.

[0036] In this case, the lubricating oil flowing through the passage in the tube can be cooled by the liquid refrigerant in the storage chamber through the peripheral wall of the tube. Advantageous effect in the invention

[0037] According to the co-rotating hospital compressor of the present invention, lubricating oil accumulated in the scroll chamber during operation is supplied to the sliding portion, and cooling efficiency by such lubricating oil in the sliding portion is improved, so that an increase in sliding resistance in the sliding portion is suppressed and thus a reduction in efficiency is suppressed. Brief description of the drawings [ Fig. 1] Fig. 1 is a sectional view of a co-rotating scroll compressor of a first embodiment. [ Fig. 2] Fig. 2 is a partially enlarged sectional view showing a main part of the co-rotating scroll compressor according to the first embodiment. [ Fig. 3] Fig. 3 is a partially enlarged sectional view showing a main part of a co-rotating scroll compressor according to a second embodiment. [ Fig. 4] Fig. 4 is a partially enlarged sectional view showing a main part of a co-rotating scroll compressor according to a third embodiment. [ Fig. 5] Fig. 5 is a partially enlarged sectional view showing a main part of the co-rotating scroll compressor according to a fourth embodiment. [ Fig. 6] Fig. 6 is a partially enlarged sectional view showing a main part of the co-rotating scroll compressor according to a fifth embodiment. Description of the embodiments

[0038] Hereinafter, a first embodiment to a fifth embodiment of the present invention will be described with reference to the drawings. First embodiment

[0039] As in Fig. 1, a co-rotating scroll compressor (hereinafter referred to simply as a compressor) of a first embodiment includes a housing 60, a scroll compression part 80, an electric motor 10, a drive scroll 30, a driven scroll 40, a driven mechanism 20, and a storage chamber 70A. The electric motor 10 is an example of a "drive mechanism" of the present invention. This compressor is mounted in a vehicle (not shown) and forms part of a vehicle air conditioner.

[0040] In the present embodiment, a front / rear direction and an up / down direction of the compressor are defined by solid arrows shown in Fig. 1 to 6. Note that the front-rear direction is an example for explanatory purposes, and a position of the compressor can be changed as appropriate depending on the vehicle in which the compressor is mounted. However, the compressor of the present embodiment is mounted in 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.

[0041] The housing 60 is formed of a housing body 61, a front cover 65, a bearing housing 67 and a rear cover 70.

[0042] The housing body 61 is a bottomed tubular member having a first outer peripheral wall 61 and a first bottom wall 63. The first bottom wall 63 is an example of a "partition wall" of the present invention. The first outer peripheral wall 62 is formed in a cylindrical shape extending around a drive axis R1. The drive axis R1 is parallel to the front-rear direction. Moreover, the first outer peripheral surface 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 flat circular plate shape extending perpendicular to the drive axis R1.

[0043] 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 the front surface 631. A second shaft support portion 64 has a columnar shape that protrudes forward from a center of the front surface 631 of the first bottom wall 63. The second shaft support portion 64 is an example of a "support portion" of the present invention.

[0044] A third shaft support portion 90 has a columnar shape and is arranged eccentrically to the second shaft support portion 64 at a distal end surface 641 of the second shaft support portion 64. The third shaft support portion 90 is an example of a "bushing" of the present invention. An eccentric shaft 91 is provided at the second shaft support portion 64. The eccentric shaft 91 is an example of the "driven shaft portion" of the present embodiment. The eccentric shaft 91 extends forward from the distal end surface 641 of the second shaft support portion 64 parallel to the drive axis R1. The eccentric shaft 91 is eccentric to the drive axis R1. The third shaft support portion 90 is fixed to the eccentric shaft 91 to be rotatable. Furthermore, a third bearing 73 is fitted in a recess 74, which will be described later. The third bearing 73 is an example of a "sliding bearing" of the present invention.This allows the third shaft support portion 90 to rotate relative to the recess 74, which will be described later, and the eccentric shaft 91.

[0045] The bearing housing 67 is arranged in front of the housing body 61. The bearing housing 67 has a substantially flat circular plate shape extending perpendicular to the drive axis R1. The bearing housing 67 is fixed to the first outer peripheral wall 62 by a bolt (not shown) with an outer peripheral edge of the bearing housing 67 in contact with a front end of the first outer peripheral surface 62 of the housing body 61, together with the front cover 65. Accordingly, 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.

[0046] A first shaft support portion 66 is formed at a center of the bearing housing 67 and has a cylindrical shape extending around the drive axis R1. A first bearing 71 is fitted in the first shaft support portion 66.

[0047] The front cover 65 is arranged 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 drive 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 flat circular plate shape extending perpendicular to the drive 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.

[0048] The front cover 65 is fixed to the first outer peripheral wall 62 by a screw (not shown) with a rear end of the second outer peripheral wall 68 in contact with a front surface of the bearing housing 67, together with 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.

[0049] A discharge connection port 65B is formed in the front cover 65. The discharge connection port 65B is located closer to an outer peripheral edge of the front cover 65 and extends through the front cover 65 in a direction parallel to the drive axis R1. The discharge connection port 65B provides communication between the second discharge portion 65A and an outside of the compressor. A piping is connected to the discharge connection port 65B and allows refrigerant discharged from the second discharge portion 65A to flow toward a condenser. Note that illustrations of the piping, an evaporator, and the condenser are omitted.

[0050] The rear cover 70 is arranged 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 drive 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 flat circular plate shape extending perpendicular to the drive 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.

[0051] The rear cover 70 is fixed to the first outer peripheral wall 62 of the housing body 61 by a screw (not shown) 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.

[0052] A suction connection port 70B is formed in the third outer peripheral wall 75 of the rear cover 70. The suction connection port 70B extends through the third outer peripheral wall 75 in a direction crossing the drive axis R1. The suction connection port 70B provides communication between the storage chamber 70A and the outside of the compressor. A piping is connected to the suction connection port 70B. Accordingly, refrigerant at a low temperature and low pressure is sucked into the storage chamber 70A through the piping after passing through the evaporator. The storage chamber 70A separates the refrigerant sucked from the outside into a gas and a liquid and stores liquid refrigerant therein.

[0053] A suction connection port 63A is formed in the first bottom wall 63 of the housing body 61. The suction connection port 63A is located near the outer peripheral edge of the first bottom wall 63 and near the suction connection port 70B, and extends through the first bottom wall 63 in a direction parallel to the drive axis R1. The suction connection port 63A provides communication between the suction chamber 61A and the storage chamber 70A.

[0054] As in Fig. As shown 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 drive 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, which serves as a spiral chamber, and specifically, at the bottom of the suction chamber 61A.

[0055] A second passage 63D is formed near the center of the first bottom wall 63. The second passage 63D is located near the drive axis R1 and extends through the first bottom wall 63 in a direction parallel to the drive axis R1. The second passage 63D extends through a portion of the first bottom wall 63 where the second shaft support 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 closer to the drive axis R1 than the third bearing 73 above the eccentric shaft 91.

[0056] A groove 63F is recessed in the rear surface 632 of the first bottom wall 63. A lower end of the groove 63F, that is, one end of the groove 63F, is connected to the first passage 63B, and an upper end of the groove 63F, that is, 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 invention.

[0057] A cover 77 made of a metal plate is fixed by a screw (not shown) to the rear surface 632 of the first bottom wall 63. The cover 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 cover 77. The third passage 63G provides communication between the first passage 63B and the second passage 63D.

[0058] The lid 77 is in contact with liquid refrigerant accumulated in the storage chamber 70A and with gaseous refrigerant in the storage chamber 70A, that is, the gaseous refrigerant that is immediately after suction in the compressor and is at a temperature lower than lubricating oil collected at 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 the gaseous refrigerant in the storage chamber 70A.

[0059] Accordingly, the first passage 63B, the third passage 63G and the second passage 63D form the lubricating oil supply passage 63H.

[0060] An inverter box having a connector portion is connected to the rear cover 70 on the rear side thereof. An inverter circuit including a circuit board, switching elements, and the like is housed in the inverter box. 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 direct current supplied from the battery into alternating current and supplies its power to the stator 17. Note that illustrations of the connector, inverter box, inverter circuit, and battery are omitted.

[0061] The electric motor 10 is housed in the suction chamber 61A. Thus, the suction chamber 61A serves as a motor chamber in which the electric motor 10 is housed. The electric motor 10 has the stator 17 and a rotor 11.

[0062] The stator 17 has a cylindrical shape extending around the drive 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 thus to the housing 60.

[0063] The rotor 11 is formed in a cylindrical shape extending around the drive axis R1 and disposed within the stator 17. Although detailed illustration is omitted, the rotor 11 is formed of a plurality of permanent magnets corresponding to the stator 17 and stacked steel plates for fixing the permanent magnets.

[0064] The scroll compression part 80 is housed in the suction chamber 61A. Thus, the suction chamber 61A also serves as a scroll chamber in which the scroll compression part 80 is housed. The suction chamber 61A is an example of the "scroll chamber" of the present invention. The scroll compression part 80 is formed from the drive scroll 30 and the driven scroll 40.

[0065] As in Fig. 1, the drive scroll 30 has a drive scroll end plate 31, a drive scroll peripheral wall 32, a drive scroll scroll body 33, a bearing cover body 34, and a cover body 35.

[0066] The drive scroll end plate 31 is formed in a substantially circular plate shape extending perpendicular to the drive axis R1. The drive scroll end plate 31 has a front surface 311 and a rear surface 312 located opposite the front surface 311.

[0067] A discharge valve chamber 36 is formed in the drive scroll end plate 31 and opens on the front surface 311 of the drive scroll end plate 31. The discharge valve chamber 36 is formed from a recess 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. Further, a discharge port 37 is formed near a center of the drive scroll end plate 31 and extends in the front-rear direction through the drive scroll end plate 31. One end of the discharge port 37 opens to the compression chamber 55, which will be described later, and the other end of the discharge port 37 opens on a bottom surface of the discharge valve chamber 36.Thus, the discharge port 37 provides a connection between the compression chamber 55 and the discharge valve chamber 36. The discharge port 37 is located near the drive axis R1.

[0068] The discharge valve mechanism 56 is arranged in the discharge valve chamber 36. The discharge valve mechanism 56 includes a discharge reed valve 57, a retainer 58, and a fixing screw 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 screw 59. The discharge reed valve 57 is capable of opening and closing the discharge port 37. Furthermore, the retainer 58 is capable of adjusting an opening degree of the discharge reed valve 57. In the discharge reed valve 57, a distal valve end portion that opens and closes the discharge port 37 is located closer to the drive axis R1 than a fixed proximal end portion that is fixed by the fixing screw 59.

[0069] The drive scroll volute 33 is integrally formed with the drive scroll end plate 31 and is located within the drive scroll peripheral wall 32. The drive scroll volute 33 extends rearward from the rear surface 312 of the drive scroll end plate 31 parallel to the drive axis R1. The drive scroll volute 33 has a spiral shape about the drive axis R1. Specifically, when viewed from the front, the drive scroll volute 33 is formed in a right-hand spiral shape from a center of the scroll about the drive axis R1.

[0070] The drive scroll circumferential wall 32 has the rotor 11 formed on an outer peripheral edge of the rear surface 312 of the drive scroll end plate 31, and a tube portion 51, which will be described later, of the cover body 35 behind the rotor 11. The drive scroll circumferential wall 32 extends from the outer peripheral edge of the drive scroll end plate 31 parallel to the drive axis R1 rearward, that is, toward the driven scroll 40. The drive scroll circumferential wall 32 has a substantially cylindrical shape extending around the drive axis R1.

[0071] The cover body 35 is a bottomed tubular member including the tubular portion 51 and a bottom wall portion 52. The tubular portion 51 has a cylindrical shape extending around the drive 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 flat circular plate shape extending perpendicular to the drive axis R1.

[0072] An outer peripheral edge of the bottom wall portion 52 is connected to a rear end of the tube portion 51. A second boss 53 is formed at a center of the bottom wall portion 52 to protrude rearward. A second bearing 72 is fitted in the second boss 53. The second boss 53 has a cylindrical shape extending around the drive axis R1 in a direction in which the drive axis R1 extends.

[0073] 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 drive axis R1 extends, that is, in the front-rear direction. Note that a shape of the suction port 54 and the number of suction ports 54 can be designed as appropriate.

[0074] The bearing cover body 34 has a cover portion 38 and a first projection 39 formed integrally with the cover portion 38.

[0075] The cover portion 38 has a substantially circular plate shape extending perpendicular to the drive axis R1. The cover portion 38 has a front surface 381 and a rear surface 382 opposite the front surface 381. A through hole 38A is formed at a center of the cover portion 38.

[0076] 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 around the drive axis R1 in the direction in which the drive axis R1 extends. An internal 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 internal 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. Note 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.

[0077] A gasket (not shown) having a circular plate shape is disposed between the rear surface 382 of the cover portion 38 and the front surface 311 of the drive scroll end plate 31. A connection 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 drive scroll end plate 31 and the rear surface 382 of the cover portion 38, providing a seal therebetween.

[0078] The cover portion 38 of the bearing cover body 34, the gasket (not shown), the drive scroll end plate 31 of the drive scroll 30, the rotor 11, and the tube portion 51 of the cover body 35 are secured with a plurality of bolts 50 extending parallel to the drive axis R1. These members are secured with the bolts 50 after the driven mechanism 20 and the driven scroll 40 are fitted to the cover body 35 and the discharge valve mechanism 56 is fitted to the drive scroll end plate 31. In other words, the cover body 35, with the driven scroll 40 held between the cover body 35 and the drive scroll end plate 31, is connected to the drive scroll end plate 31.

[0079] The driven scroll 40 has a driven scroll end plate 41 and a driven scroll scroll body 43.

[0080] The driven scroll end plate 41 is formed in a substantially circular plate shape extending perpendicular to a driven axis R2. The driven axis R2 is eccentric to the drive axis R1 and extends parallel to the drive 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 opposite the front surface 411.

[0081] 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 columnar shape with a bottom. The recess 74 extends in a columnar shape around the driven axis R2 in the direction in which the driven axis R2 extends. The recess 74 has an inner surface shape corresponding to an outer surface of the third shaft support portion 90.

[0082] The driven scroll scroll body 43 is integrally formed with the driven scroll end plate 41 and extends forward from the front surface 411 of the driven scroll end plate 41 parallel to the driven axis R2, that is, toward the drive scroll end plate 31 of the drive scroll 30. The driven scroll scroll body 43 has a spiral shape around the driven axis R2. Specifically, the driven scroll scroll body 43 is formed in a right-hand spiral shape from a center of the scroll around the driven axis R2 when viewed from the front.

[0083] The driven mechanism 20 is formed of four anti-rotation pins 21 and four rings 22. It should be noted that the number of anti-rotation pins 31 and the number of rings 22 can 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 in Fig. 1 shown.

[0084] 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 protrude rearward from the driven scroll end plate 41.

[0085] The rings are provided in a front surface 521 of the bottom wall portion 52 of the cover body 35 of the drive scroll 30 to face their corresponding anti-rotation pins 21. The rings 22 are fitted in circular blind holes recessed in the front surface 521 of the bottom wall portion 52.

[0086] In this compressor, the scroll compression part 80, which is formed of the drive scroll 30 and the driven scroll 40, is arranged in the suction chamber 61A.

[0087] In the drive scroll 30, the rotor 11 is integrated with the drive scroll peripheral wall 32. Furthermore, in the drive scroll 30, the first bearing 71 is interposed between the first shaft support 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 support portion 64 of the first bottom wall 63 and the second boss 53 of the cover body 35. Thus, the drive scroll 30 is supported by the housing 60 to be rotatable about the drive axis R1. Here, in this compressor, the drive scroll 30 is supported by the housing 60 in a so-called double-supported manner.

[0088] On the other hand, the driven scroll 40, with the driven scroll scroll body 43 facing the driven scroll end plate 31, is located behind the drive scroll end plate 31 at the drive scroll 30. Thus, the rear surface 312 of the drive 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 drive axis R1 extends and in the direction in which the driven axis R2 extends. Then, in the drive scroll 30 and the driven scroll 40, the drive scroll scroll body 33 is engaged with the driven scroll scroll body 43 within the drive scroll peripheral wall 32, and the rotation prevention pins 31 are inserted into their corresponding rings 22.Thus, the driven scroll 40 is installed in the drive scroll 30 with the drive scroll end plate 31 and the driven scroll end plate 41 facing each other in the front-rear direction. The drive scroll scroll body 33 and the driven scroll scroll body 43 form the compression chamber 55 therebetween.

[0089] In the driven scroll 40, the third bearing 73 is interposed between the third shaft support portion 90, which is eccentric to the second shaft support 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 casing 60 to be rotatable about the driven axis R2. Here, in this compressor, the driven scroll 40 is supported by the casing 60 in a so-called cantilevered manner.

[0090] In this compressor having the above-described configuration, the inverter circuit (not shown) supplies power to the stator 17 while controlling the operation of the electric motor 10, which drives the electric motor 10. This rotates the rotor 11, which drives the drive scroll 30 to rotate in the suction chamber 61A around the drive axis R1. That is, the drive scroll 30, which has the drive scroll peripheral wall 32 integrated with the rotor 11, is rotationally driven. At this time, in the driven mechanism 20, the rotation-preventing pins 21 slide on the inner peripheral surfaces of their corresponding rings 22, respectively, to rotate the rings 22 about the center thereof relative to the rotation-preventing pins 21. Thus, the driven mechanism 20 transmits torque of the drive scroll 30 to the driven scroll 40.

[0091] As a result, the driven scroll 40 is driven by the drive scroll 30 and the driven mechanism 20 to rotate around the driven axis R2. At this time, the driven mechanism 20 prevents the driven scroll 40 from rotating. Thus, with the drive scroll 30 and the driven scroll 40 rotationally driven, the driven scroll 40 performs an orbital motion around the drive axis R1 relative to the drive scroll 30, which changes a volume of the compression chamber 55.

[0092] As a result, refrigerant in the suction chamber 61A is sucked 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 through the first discharge portion 39A, and is further discharged to the condenser through the discharge connection port 65B. In this way, air conditioning is performed by the vehicle air conditioner.

[0093] Here, the scroll compression part 80 has a plurality of sliding sections 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 support 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 drive scroll scroll body 33 and the driven scroll scroll body 43, a sliding portion between the distal end surface of the drive scroll scroll 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 scroll body 43 and the rear surface 312 of the drive spiral end plate 31.These sliding sections must be lubricated and cooled by supplying lubricating oil.

[0094] In this compressor, lubricating oil accumulated 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 section during operation.

[0095] That is, the lubricating oil is separated from the refrigerant by centrifugation because a centrifugal force acts on the rotating scroll compression part 80, 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 fluid flow in a rotational direction is generated due to an influence of the centrifugal force of the rotating scroll compression part 80. Therefore, the lubricating oil is accumulated at the outermost peripheral portion of the suction chamber 61A due to the centrifugal force, which forms an oil storage portion 83.

[0096] 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 support portion 64. That is, the outlet 63E1 is located inside the scroll compression part 80, outside the compression chamber 55, and near the drive axis R1.

[0097] A pressure in the suction chamber 61A is highest at the bottom of the suction chamber 61A, which corresponds 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. Moreover, since the refrigerant in the suction chamber 61A (scroll chamber) is sucked 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 at the outer peripheral portion of the suction chamber 61A. In particular, the pressure near the drive axis R1, where the second shaft support portion 64 is located, is a portion where a pressure in the scroll compression part 80 outside the compression chamber 55 is comparatively low.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, which accumulates at the bottom of the suction chamber 61A, is introduced into the inlet 63C of the lubricating oil supply passage 63H, and the lubricating 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 support portion 64. During operation of the compressor, lubricating oil is continuously supplied from the lubricating oil supply passage 63H.

[0098] 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 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 support 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 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 support 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 sliding portion to which lubricating oil is supplied.

[0099] 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 sliding portion to which lubricating oil is supplied, thereby effectively preventing an increase in sliding resistance due to insufficient lubricating oil at the sliding portion to which lubricating oil is supplied.

[0100] Furthermore, the lubricating oil flowing through the lubricating oil supply passage 63H is cooled by the liquid refrigerant and the gas refrigerant in the storage chamber 70A in the lubricating oil cooling section 78. Therefore, the sliding section to which lubricating oil is supplied can be lubricated with lubricating oil having an appropriate viscosity. Moreover, since the sliding section to which lubricating oil is supplied 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 sliding section to which lubricating oil is supplied. As a result, an increase in sliding resistance in the sliding section to which lubricating oil is supplied can be suppressed.

[0101] Therefore, the compressor of the first embodiment supplies the lubricating oil accumulated in the scroll chamber during operation to the sliding portions and improves the cooling effect of the lubricating oil at the sliding portion, so that an increase in sliding resistance at the sliding portion is suppressed and thus a reduction in efficiency is suppressed.

[0102] Furthermore, in this compressor, the lubricating oil supply passage 63H is formed from the first passage 63B, the third passage 63G, and the second passage 63D formed in the first bottom wall 63, which do not rotate even during operation of the compressor. That is, the lubricating oil supply passage 63H extends through the second shaft support portion 64, which is a non-rotating body, and is opened at the distal end surface 641 of the second shaft support portion 64. Therefore, supply of lubricating oil through the lubricating oil supply passage 63H becomes stable.

[0103] Furthermore, the second bearing 72 and the third bearing 73 are located near the drive 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 drive axis R1. In this regard, in this compressor, the lubricating oil supply passage 63H extends through the second shaft support portion 64, and the outlet 63E1 of the lubricating oil supply passage 63H is opened at a position closer to the drive axis R1 than the third bearing 73, so that lubricating oil can be effectively supplied to the second bearing 72 and the third bearing 73 where the amount of lubricating oil tends to become insufficient. Second embodiment

[0104] As 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.

[0105] 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 drive 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.

[0106] 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. Moreover, 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 cover 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.

[0107] 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.

[0108] As a result, lubricating oil flowing out from the outlet 63E2 of the lubricating oil supply passage 63H 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 of the driven mechanism 20, which are located on the outer peripheral side of the outlet 63E2, by the action of centrifugal force.

[0109] This makes it possible to directly supply lubricating oil cooled by the liquid refrigerant and the gas refrigerant in the storage chamber 70A 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.

[0110] 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 a detailed description of the components is omitted. Third embodiment

[0111] As 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.

[0112] That is, a seventh passage 63M is formed in the third shaft support portion 90, which is located on the distal end surface 641 of the second shaft support portion 64. The seventh passage 63M extends through the third shaft support portion 90 in a direction parallel to the drive axis R1. The seventh passage 63M is located near the top of the third shaft support portion 90. A front opening of the seventh passage 63M serves as the outlet 63E3 of the lubricating oil supply passage 63H.

[0113] 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. Furthermore, 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 cover 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.

[0114] In the compressor of the third embodiment, the seventh passage 63M is formed in the third shaft support 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 support portion 90. In a similar manner 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 support 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 63E3.

[0115] 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 a detailed description of the components is omitted. Fourth embodiment

[0116] As 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.

[0117] That is, a tenth passage 63Q is formed in the eccentric shaft 91 provided in the second shaft support portion 64. The tenth passage 63Q extends through the eccentric shaft 91 in a direction parallel to the drive axis R1. A front opening of the tenth passage 63Q serves as the outlet 63E4 of the lubricating oil supply passage 63H.

[0118] 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. Furthermore, 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 cover 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.

[0119] 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. In a similar manner 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 support 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-start side relative to the outlet 63E4.

[0120] 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 a detailed description of the components is omitted. Fifth embodiment

[0121] As 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.

[0122] 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 arranged in the storage chamber 70A and extends in the up-down direction. One end and the other end of the pipe 84 are bent, respectively forming a lower bent portion 841 and an upper bent portion 842, which are respectively connected to the first passage 63B and the second passage 63D.

[0123] Thus, the first passage 63B, a thirteenth passage 63T in the tube 84, and the second passage 63D cooperate to form the lubricating oil supply passage 63H. A portion of the tube 84 disposed in the storage chamber 70A serves as the lubricating oil cooling portion 78.

[0124] In this embodiment, lubricating oil passing through the thirteenth passage 63T in the tube 84 can be cooled by a peripheral wall of the tube 84 of liquid refrigerant and gas refrigerant in the storage chamber 70A.

[0125] 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 a detailed description of the components is omitted.

[0126] Although the present invention has been described above based on the first to fifth embodiments, the present invention is not limited to the above-described first to fifth embodiments and can be modified as appropriate within the gist of the present invention.

[0127] 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 invention is not limited to this, 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. Furthermore, the position of the inlet of the lubricating oil supply passage 63H does not need to be at the outermost peripheral portion, as long as it is at a position communicating with the oil storage portion in the scroll chamber.

[0128] Further, 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 invention is not limited thereto, and the lubricating oil supply passage 63H may have a plurality of outlets.

[0129] In each of the compressors of the first to fifth embodiments, the lubricating oil cooling portion 78 is formed by the groove 63F recessed on the storage chamber 70A side in the wall surface of the first bottom wall 63 serving as the partition wall, and the lid 77 or the pipe 84 provided in the storage chamber 70A, but the present invention 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 within the partition wall, or the lubricating oil cooling portion may be formed on the scroll chamber side.

[0130] Furthermore, in each of the compressors of the first to fifth embodiments, the drive scroll 30 is supported in a double-supported manner relative to the casing 60, and the driven scroll 40 is supported in a cantilevered manner relative to the casing 60. However, the present invention is not limited to this; both the drive scroll 30 and the driven scroll 40 may be supported in a cantilevered manner relative to the casing 60.

[0131] In each of the compressors of the first to fifth embodiments, the suction port 54 is formed in the cover body 35 of the drive scroll 30. However, the present invention is not limited to this, and the suction port may be formed in the drive scroll end plate 31 of the drive scroll 30. In the compressor in which the drive scroll 30 and the driven scroll 40 are each supported by the casing in a cantilever manner, the suction port may be formed in either the drive scroll end plate 31 or the driven scroll end plate 41.

[0132] In each of the compressors of the first to fifth embodiments, in the drive scroll 30, the bearing cover body 34, which has the cover portion 38 covering part of the discharge valve chamber 36 and part of the discharge valve mechanism, is connected to the front surface 311 of the drive scroll end plate 31, in which the discharge valve chamber 36 is recessed, which accommodates the discharge valve mechanism 56. Moreover, the first discharge portion 39A, which is the interior of the first boss 39 of the bearing cover body 34, is in communication with the discharge valve chamber 36. However, the present invention is not limited to this, and the bearing cover body may be omitted, and the discharge valve mechanism may be accommodated in the boss protruding from and formed integrally with the drive scroll end plate or the driven scroll end plate, and the bearing may be fixed to the boss.

[0133] 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 invention is not limited to this, 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 a free ring, a pin-and-pin mechanism in which outer peripheral surfaces of two pins slide against each other, a mechanism using an Oldham coupling, or the like.

[0134] In the compressors of the first to fifth embodiments, the drive scroll 30 is integrated with the rotor 11 by integrating the rotor 11 with the drive scroll peripheral wall 32. However, the present invention is not limited to this, and the compressor may have a configuration in which the drive scroll 30 is spaced apart from the rotor 11 in the direction where the drive axis R1 extends by connecting the drive scroll 30 to the rotor 11 via a drive shaft, thereby transmitting drive power. (Supplementary Note 1)

[0135] Rotating scroll compressor with: a housing; a drive mechanism; a drive spiral; a driven spiral; and a driven mechanism, wherein the housing has a spiral chamber in which the drive spiral and the driven spiral are accommodated, a storage chamber which separates a refrigerant sucked from an outside into a gas and a liquid and stores liquid refrigerant, and a partition wall which separates the storage chamber from the spiral chamber, the drive spiral is configured to be driven by the drive mechanism to rotate about a drive axis, the driven scroll is eccentric to the drive scroll and is configured to be driven by the drive scroll and the driven mechanism to rotate about a driven axis, a support section with the drive axis at a center protrudes from the dividing wall into the spiral chamber, the drive spiral is supported by a bearing arranged between the drive spiral and the support section to be driven to rotate about the drive axis, a spiral compression part is formed from the drive spiral and the driven spiral, an oil storage section in which lubricating oil is stored is provided in the spiral chamber and a lubricating oil supply passage in communication with the oil storage section 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 section that cools the lubricating oil in the lubricating oil supply passage with the refrigerant in the storage chamber. (Supplementary Note 2)

[0136] Co-rotating scroll compressor according to supplementary note 1, where the drive scroll has a drive scroll end plate, a drive scroll spiral body formed integrally with the drive scroll end plate and projecting in a spiral shape toward the driven scroll, and a cover body connected to the driven scroll held between the cover body and the drive scroll end plate, the driven scroll has a driven scroll end plate and a driven scroll scroll body formed integrally with the driven scroll end plate and projecting in a spiral shape toward the drive scroll end plate, 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. (Supplementary Note 3)

[0137] Co-rotating scroll compressor according to supplementary note 1 or 2, where the lubricating oil is supplied from the lubricating oil supply passage to the bearing and the lubricating oil supply passage extends through the support section. (Supplementary Note 4)

[0138] Rotating scroll compressor according to supplementary note 2, further comprising: a driven shaft portion which is eccentric to the drive axis and extends in the housing parallel to the drive axis; and a bushing in which the driven shaft portion is inserted, wherein a plain bearing is arranged between the driven spiral and the bushing, the lubricating oil is supplied from the lubricating oil supply passage to the sliding bearing and the lubricating oil supply passage extends through the driven shaft section or the bushing. (Supplementary Note 5)

[0139] Rotating scroll compressor according to supplementary note 2, where the lubricating oil supply passage extends through the cover body. (Supplementary Note 6)

[0140] Co-rotating scroll compressor according to one of the supplementary notes 1 to 5, wherein the lubricating oil cooling section consists of a groove recessed in a wall surface of the partition wall on the storage chamber side, and a cover having a plate shape, extending in a direction in which the groove extends, and fixed to the wall surface to close an opening of the groove, and a passage defined by an inner surface of the groove and the cover forms part of the lubricating oil supply passage. (Supplementary Note 7)

[0141] Co-rotating scroll compressor according to one of the supplementary notes 1 to 5, wherein the lubricating oil cooling section is formed from a pipe arranged in the storage chamber, and a passage within the tube forms part of the lubricating oil supply passage. Industrial applicability

[0142] The present invention is applicable to an air conditioner for a vehicle or the like. List of reference symbols 10 Electric motor (drive mechanism) 20 driven mechanism 30 drive spiral 31 Drive spiral end plate 33 Drive spiral-spiral body 35 cover bodies 40 driven spiral 41 Driven spiral end plate 43 Driven-spiral-spiral bodies 55 compression chamber 60 housings 61A Suction chamber (spiral chamber) 63 first floor wall (dividing wall) 632 rear area (wall area) 63F groove 63H Lubricating oil supply passage 64 second shaft support section (support section) 70A storage chamber 72 second bearing (bearing, sliding section) 73 third bearing (sliding bearing, sliding section) 77 lids 78 Lubricating oil cooling section 80 spiral compression section 81, 82 sliding section 83 Oil storage section 84 pipe 90 third shaft support section (bushing) 91 Eccentric shaft (driven shaft section) R1 drive axle R2 driven axle QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] JP 2005-146987

[0011]

Claims

[1] Rotating scroll compressor with: a housing; a drive mechanism; a drive spiral; a driven spiral; and a driven mechanism, wherein the housing has a spiral chamber in which the drive spiral and the driven spiral are accommodated, a storage chamber which separates a refrigerant sucked from an outside into a gas and a liquid and stores liquid refrigerant, and a partition wall which separates the storage chamber from the spiral chamber, the drive spiral is configured to be driven by the drive mechanism to rotate about a drive axis, the driven scroll is eccentric to the drive scroll and is configured to be driven by the drive scroll and the driven mechanism to rotate about a driven axis, a support section with the drive axis at a center protrudes from the dividing wall into the spiral chamber, the drive spiral is supported by a bearing arranged between the drive spiral and the support section to be driven to rotate about the drive axis, a spiral compression part is formed from the drive spiral and the driven spiral, an oil storage section in which lubricating oil is stored is provided in the spiral 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 by , that the lubricating oil supply passage has a lubricating oil cooling section that cools the lubricating oil in the lubricating oil supply passage with the refrigerant in the storage chamber. [2] Co-rotating scroll compressor according to claim 1, wherein the drive scroll has a drive scroll end plate, a drive scroll spiral body formed integrally with the drive scroll end plate and projecting in a spiral shape toward the driven scroll, and a cover body connected to the driven scroll held between the cover body and the drive scroll end plate, the driven scroll has a driven scroll end plate and a driven scroll scroll body formed integrally with the driven scroll end plate and projecting in a spiral shape toward the drive scroll end plate, 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. [3] Co-rotating scroll compressor according to claim 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 support section. [4] A co-rotating scroll compressor according to claim 2, further comprising: a driven shaft portion which is eccentric to the drive axis and extends in the housing parallel to the drive axis; and a bushing in which the driven shaft portion is inserted, wherein a plain bearing is arranged between the driven spiral and the bushing, the lubricating oil is supplied from the lubricating oil supply passage to the sliding bearing and the lubricating oil supply passage extends through the driven shaft section or the bushing. [5] A co-rotating scroll compressor according to claim 2, wherein the lubricating oil supply passage extends through the cover body. [6] Co-rotating scroll compressor according to claim 1 or 2, wherein the lubricating oil cooling section is formed of a groove recessed on the storage chamber side in a wall surface of the partition wall, and a cover having a plate shape, extending in a direction in which the groove extends, and fixed to the wall surface to close an opening of the groove, and a passage defined by an inner surface of the groove and the cover forms part of the lubricating oil supply passage. [7] Co-rotating scroll compressor according to claim 1 or 2, wherein the lubricating oil cooling section is formed from a pipe arranged in the storage chamber, and a passage within the tube forms part of the lubricating oil supply passage.

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