Dual rotation scroll compressor

Abstract

A housing (60) is provided with a suction chamber (61A) as a scroll chamber for accommodating a scroll compression unit (80), a reservoir chamber (70A) adjacent to the suction chamber (61A) with a first bottom wall (63) as a partition wall therebetween, and a lubricating oil supply passage (63H). A lubricating oil supply passage (63H) communicates with an oil storage section (83) provided in the suction chamber (61A), and supplies lubricating oil to the scroll compression section (80), the second bearing (72), the third bearing (73), and the like. A lubricating oil cooling part (78) for cooling the lubricating oil in the lubricating oil supply passage (63H) by using the liquid refrigerant in the storage chamber (70A) is arranged in the middle of the lubricating oil supply passage (63H).

Description

Technical Field

[0001] The present invention relates to a double-rotary scroll compressor. Background Art

[0002] Hitherto, a double-rotary scroll compressor has been known. The double-rotary scroll compressor includes a drive mechanism, a drive scroll member, a driven mechanism, a driven scroll member, and a housing.

[0003] The housing has a scroll member chamber that houses a scroll compression section formed by the drive scroll member and the driven scroll member.

[0004] The drive scroll member is driven to rotate around a drive axis by the drive mechanism. The driven scroll member is eccentric with respect to the drive scroll member and is driven to rotate by the drive scroll member and the driven mechanism around a driven axis.

[0005] The drive scroll member has a drive end plate and a drive scroll body. The drive end plate extends across the drive axis. The drive scroll body projects from the drive end plate toward the driven scroll member and is in a scroll shape.

[0006] The driven scroll member has a driven end plate and a driven scroll body. The driven end plate extends across the driven axis. The driven scroll body projects from the driven end plate toward the drive scroll member and is in a scroll shape.

[0007] In the drive scroll member and the driven scroll member, the drive scroll body and the driven scroll body face each other to form a compression chamber, and the volume of the compression chamber changes by the drive rotation and the driven rotation, and the fluid sucked from the suction chamber is compressed and discharged to the discharge chamber according to the volume change.

[0008] In a rotary compressor that compresses the fluid in the compression chamber by rotating the compression section as in the double-rotary scroll compressor, sliding parts such as bearings that support the compression section so as to be rotatable relative to the housing generate heat due to sliding friction. In addition, due to this heat, the viscosity of the lubricating oil in the bearing decreases, so that the sliding resistance increases, and furthermore, a vicious cycle of an increase in the amount of heat generated occurs. And if the sliding resistance of the sliding part increases, the efficiency is reduced due to sliding loss.

[0009] Therefore, in the operation of the rotary compressor, it is necessary to sufficiently supply lubricating oil to sliding parts such as bearings and continuously cool the sliding parts to suppress the generation of sliding heat.

[0010] Therefore, in the rotary compressor described in Patent Document 1, a lubricating oil is sucked from an oil storage section provided at the bottom in the compressor by a sucking unit and supplied to the compression section and the bearing of the rotary shaft.

[0011] Prior Art Documents

[0012] Patent Document

[0013] Patent Document 1: Japanese Patent Application Laid-Open No. 2005-146987 Summary of the Invention

[0014] Problems to be Solved by the Invention

[0015] However, in the above countermeasures for the conventional rotary compressor, considering the heat capacity of the lubricating oil and the temperature of the lubricating oil accumulated in the oil storage part inside the compressor, there may be insufficient cooling of the sliding part, and the countermeasures cannot be said to be sufficient enough.

[0016] In particular, in a twin rotary scroll compressor, in the scroll element chamber that houses the scroll compression part, the lubricating oil flows out from the rotating scroll compression part, and due to the influence of the centrifugal force of the rotating scroll compression part, a fluid flow is generated in its rotating direction to generate centrifugal force. As a result, the lubricating oil accumulates in the outermost peripheral part of the scroll element chamber. When the lubricating oil accumulated in the outermost peripheral part of the scroll element chamber continuously increases, the amount of lubricating oil required for the sliding part originally will decrease. If the amount of lubricating oil decreases, the sliding resistance increases, and therefore, the efficiency may decrease.

[0017] The present invention is made in view of the above-mentioned conventional situation, and the problem to be solved is to provide the following twin rotary scroll compressor: capable of suppressing an increase in the sliding resistance of the sliding part by supplying the lubricating oil accumulated in the scroll element chamber during operation to the sliding part and improving the cooling effect of the lubricating oil on the sliding part, and further suppressing a decrease in efficiency.

[0018] Technical Solution for Solving the Problem

[0019] The twin rotary scroll compressor of the present invention is characterized by comprising a housing, a drive mechanism, a driving scroll element, a driven scroll element, and a driven mechanism,

[0020] The housing has: a scroll element chamber that houses the driving scroll element and the driven scroll element; a storage chamber that separates the refrigerant sucked from the outside into gas and liquid and stores the liquid refrigerant inside; and a partition wall that divides the storage chamber and the scroll element chamber,

[0021] The driving scroll element is driven to rotate around the driving axis by the drive mechanism,

[0022] The driven scroll element is eccentric with respect to the driving scroll element and is driven to rotate around the driven axis by the driving scroll element and the driven mechanism,

[0023] A support portion is provided on the partition wall, and the support portion projects into the scroll element chamber with the driving axis as the center,

[0024] The driving scroll member is supported by a bearing disposed between the driving scroll member and the supporting portion so as to be capable of driving and rotating about the driving axis.

[0025] The scroll compression portion is constituted by the driving scroll member and the driven scroll member.

[0026] An oil storage portion for storing lubricating oil is provided in the scroll member chamber.

[0027] The double-rotary scroll compressor is provided with a lubricating oil supply passage which communicates with the oil storage portion and supplies lubricating oil to the scroll compression portion or the bearing.

[0028] A lubricating oil cooling portion is provided in the lubricating oil supply passage, and the lubricating oil cooling portion cools the lubricating oil in the lubricating oil supply passage by using the refrigerant in the storage chamber.

[0029] In the double-rotary scroll compressor of the present invention, an oil storage portion for storing lubricating oil is provided in the scroll member chamber. The oil storage portion is provided, for example, as follows. That is, during the operation of the scroll compression portion, the lubricating oil supplied into the rotating scroll compression portion flows out from the scroll compression portion to the scroll member chamber due to centrifugal force. In the scroll member chamber, a fluid flow is generated in the rotating direction due to the influence of the centrifugal force of the rotating scroll compression portion. Therefore, the lubricating oil accumulates in the outer peripheral portion of the scroll member chamber due to the action of the centrifugal force. Thus, an oil storage portion for storing lubricating oil is provided in the scroll member chamber.

[0030] Here, in the scroll member chamber, it is difficult for the fluid centrifugal force to act closer to the rotation center of the scroll compression portion. Therefore, when comparing the pressure of the outer peripheral portion of the scroll member chamber with the pressure on the rotation center side of the scroll compression portion, the outer peripheral portion that is more affected by the fluid centrifugal force becomes a high pressure. In addition, since the fluid in the scroll member chamber is sucked into the scroll compression portion through the suction port provided in the driving scroll member or the driven scroll member, the pressure at the suction port of the scroll compression portion becomes a low pressure compared with the pressure of the outer peripheral portion of the scroll member chamber.

[0031] Therefore, for example, if the inlet of the lubricating oil supply passage is opened to the outer peripheral portion of the scroll member chamber and the outlet of the lubricating oil supply passage is opened, for example, to the inside of the scroll compression portion and to the rotation center side of the scroll compression portion in the scroll member chamber, the inlet of the lubricating oil supply passage becomes a high pressure compared with the outlet. Therefore, by using this pressure difference, the lubricating oil accumulated in the oil storage portion provided in the outer peripheral portion of the scroll member chamber is introduced into the inlet of the lubricating oil supply passage, and the lubricating oil is led out from the outlet of the lubricating oil supply passage to the inside of the scroll compression portion and to the rotation center side of the scroll compression portion in the scroll member chamber. Then, the lubricating oil coming out from the outlet of the lubricating oil supply passage flows to the outer peripheral side than the outlet due to the action of the centrifugal force, and is supplied to the portion of the scroll compression portion and the bearing located at a position on the outer peripheral side than the outlet.

[0032] In this way, the lubricating oil in the oil storage part provided in the scroll element chamber can be supplied to the scroll compression part and the sliding part of the bearing. Therefore, it is possible to suppress an increase in sliding resistance due to insufficient lubricating oil at these sliding parts.

[0033] Moreover, the lubricating oil flowing in the lubricating oil supply passage is cooled by the liquid refrigerant in the storage chamber in the lubricating oil cooling part. Therefore, the lubricating oil having a lower temperature than the lubricating oil accumulated in the oil storage part of the scroll element chamber is supplied to the scroll compression part and the sliding part of the bearing. As a result, it is possible to lubricate the sliding part with the lubricating oil whose viscosity is more appropriately ensured, and to cool the sliding part with the lower temperature lubricating oil. Thus, it is possible to suppress a decrease in the viscosity of the lubricating oil due to heat from the sliding part. In this way, it is possible to suppress an increase in sliding resistance at the scroll compression part and the sliding part of the bearing.

[0034] Therefore, the double-rotary scroll compressor of the present invention can suppress an increase in sliding resistance at the sliding part and further suppress a decrease in efficiency by supplying the lubricating oil accumulated in the scroll element chamber during operation to the sliding part and improving the cooling effect of the lubricating oil on the sliding part.

[0035] The driving scroll element may include: a driving end plate; a driving scroll body, which is integrated with the driving end plate and protrudes in a scroll shape toward the driven scroll element; and a cover body, which sandwiches the driven scroll element with respect to the driving end plate and is connected to the driving end plate. In addition, the driven scroll element may include: a driven end plate; and a driven scroll body, which is integrated with the driven end plate and protrudes in a scroll shape toward the driving end plate. And it is preferable to supply lubricating oil from the lubricating oil supply passage to the sliding part between the driven end plate and the cover body.

[0036] In this case, in the scroll compression part, the sliding part between the driven end plate and the cover body requires lubricating oil. In view of this, lubricating oil is supplied from the lubricating oil supply passage to the sliding part between the driven end plate and the cover body. Therefore, it is possible to supply the lubricating oil cooled by the liquid refrigerant to the sliding part between the driven end plate and the cover body well.

[0037] It is preferable to supply lubricating oil from the lubricating oil supply passage to the bearing, and the lubricating oil supply passage penetrates the support part.

[0038] In this case, it is possible to supply the lubricating oil cooled by the liquid refrigerant to the bearing located at a position on the outer peripheral side of the support part well from the lubricating oil supply passage penetrating the support part.

[0039] In addition, the bearing is relatively close to the rotation center of the scroll compression part in the scroll element chamber. In the scroll element chamber, the amount of lubricating oil is more likely to be insufficient the closer to the rotation center of the scroll compression part. If the lubricating oil supply passage penetrates the support part, it is possible to supply lubricating oil to the bearing where the amount of lubricating oil is likely to be insufficient well.

[0040] Moreover, even during the operation of the scroll compression section, the support section does not rotate. Therefore, lubricating oil can be stably discharged from the outlet that penetrates the support section and opens to its front end face.

[0041] A driven shaft section and a bushing may be provided. The driven shaft section is provided in the housing, is eccentric with respect to the drive axis, and extends in a direction parallel to the drive axis. The bushing is inserted through the driven shaft section. Additionally, a bearing for the bushing may be provided between the orbiting scroll and the bushing. And it is preferable to supply lubricating oil from the lubricating oil supply passage to the bearing for the bushing. Moreover, it is preferable that the lubricating oil supply passage penetrates the driven shaft section or the bushing.

[0042] In this case, lubricating oil cooled by the liquid refrigerant can be well supplied to the bearing for the bushing located at a position on the outer peripheral side of the driven shaft section or the bushing through the lubricating oil supply passage that penetrates the driven shaft section or the bushing.

[0043] In addition, the bearing for the bushing is close to the rotation center of the scroll compression section in the scroll chamber, and the amount of lubricating oil is likely to be insufficient. If the lubricating oil supply passage penetrates the driven shaft section or the bushing, good lubricating oil supply can be performed to the bearing for the bushing where the amount of lubricating oil is likely to be insufficient.

[0044] It is preferable that the lubricating oil supply passage penetrates the cover body.

[0045] In this case, lubricating oil cooled by the liquid refrigerant can be well supplied to the sliding portion between the driven end plate and the cover body located at a position on the outer peripheral side of the outlet of the lubricating oil supply passage that penetrates the cover body.

[0046] Preferably, the lubricating oil cooling section is formed by a groove recessed in the wall surface on the storage chamber side of the partition wall, and a plate-shaped cover body that extends in the extending direction of the groove and is fixed to the wall surface so as to close the opening of the groove. And it is preferable that the passage partitioned by the inner surface of the groove and the cover body constitutes a part of the lubricating oil supply passage.

[0047] In this case, the lubricating oil can be cooled by the liquid refrigerant in the storage chamber via the cover body during the passage of the lubricating oil through the passage partitioned by the inner surface of the groove and the cover body.

[0048] Preferably, the lubricating oil cooling section is formed by a pipe disposed in the storage chamber. And it is preferable that the passage in the pipe constitutes a part of the lubricating oil supply passage.

[0049] In this case, the lubricating oil can be cooled by the liquid refrigerant in the storage chamber via the peripheral wall of the pipe during the passage of the lubricating oil through the passage in the pipe.

[0050] Effects of the Invention

[0051] According to the double-rotary scroll compressor of the present invention, by supplying the lubricating oil accumulated in the scroll member chamber during operation to the sliding portion and improving the cooling effect of the lubricating oil on the sliding portion, an increase in the sliding resistance at the sliding portion can be suppressed, and thus a reduction in efficiency can be suppressed. BRIEF DESCRIPTION OF THE DRAWINGS

[0052] Figure 1 is a cross-sectional view of the double-rotary scroll compressor of Embodiment 1.

[0053] Figure 2 Relates to the double-rotary scroll compressor of Embodiment 1 and is a partially enlarged cross-sectional view showing the main part in an enlarged manner.

[0054] Figure 3 Relates to the double-rotary scroll compressor of Embodiment 2 and is a partially enlarged cross-sectional view showing the main part in an enlarged manner.

[0055] Figure 4 Relates to the double-rotary scroll compressor of Embodiment 3 and is a partially enlarged cross-sectional view showing the main part in an enlarged manner.

[0056] Figure 5 Relates to the double-rotary scroll compressor of Embodiment 4 and is a partially enlarged cross-sectional view showing the main part in an enlarged manner.

[0057] Figure 6 Relates to the double-rotary scroll compressor of Embodiment 5 and is a partially enlarged cross-sectional view showing the main part in an enlarged manner. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0058] Hereinafter, Embodiments 1 to 5 embodying the present invention will be described with reference to the drawings.

[0059] Embodiment 1

[0060] As Figure 1 shown, the double-rotary scroll compressor (hereinafter, simply referred to as the compressor) of Embodiment 1 includes a housing 60, a scroll compression section 80, an electric motor 10, a driving scroll member 30, a driven scroll member 40, a driven mechanism 20, and a storage chamber 70A. The electric motor 10 is an example of the "driving mechanism" in the present invention. This compressor is mounted on a vehicle (not shown) and constitutes a vehicle air conditioning device.

[0061] In the present embodiment, the front-rear direction and the up-down direction of the compressor are defined by the solid arrows shown in Figures 1 to 6 . In addition, the front-rear direction is an example for ease of explanation, and the compressor can appropriately change its posture according to the vehicle on which it is mounted. However, the compressor of the present embodiment is mounted on the vehicle with the inlet 63C of the lubricating oil supply passage 63H located at the lowermost part of the suction chamber 61A.

[0062] The housing 60 is composed of a housing main body 61, a front cover 65, a bearing housing 67, and a rear cover 70.

[0063] The housing main body 61 is a bottomed cylindrical member having a first outer peripheral wall 62 and a first bottom wall 63. The first bottom wall 63 is an example of the "partition wall" in the present invention. The first outer peripheral wall 62 is in a cylindrical shape centered on the 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 the rear end of the housing main body 61. The first bottom wall 63 extends in a substantially circular flat shape orthogonally to the driving axis R1.

[0064] The outer peripheral edge of the first bottom wall 63 is connected to the rear end of the first outer peripheral wall 62. The first bottom wall 63 has a front surface 631 and a rear surface 632 located on the opposite side of the front surface 631. At the center of the front surface 631 of the first bottom wall 63, a cylindrical second shaft support portion 64 protruding forward is provided. The second shaft support portion 64 is an example of the "support portion" in the present invention.

[0065] On the front end face 641 of the second shaft support portion 64, a cylindrical third shaft support portion 90 eccentrically arranged with respect to the second shaft support portion 64 is arranged. The third shaft support portion 90 is an example of the "bushing" in the present invention. An eccentric shaft 91 is provided on the second shaft support portion 64. The eccentric shaft 91 is an example of the "driven shaft portion" in the present invention. The eccentric shaft 91 extends forward parallel to the driving axis R1 from the front end face 641 of the second shaft support portion 64. The eccentric shaft 91 is eccentric with respect to the driving axis R1. The third shaft support portion 90 is installed so as to be rotatable with respect to the eccentric shaft 91. In addition, a third bearing 73 is embedded in a recess 74 described later. The third bearing 73 is an example of the "bearing for bushing" in the present invention. In this way, the third shaft support portion 90 can rotate with respect to the recess 74 and the eccentric shaft 91 described later.

[0066] The bearing housing 67 is arranged in front of the housing main body 61. The bearing housing 67 extends in a substantially circular flat shape orthogonally to the driving axis R1. The bearing housing 67 is fastened and connected to the first outer peripheral wall 62 together with the front cover 65 by bolts (not shown) in a state where its outer peripheral edge abuts against the front end of the first outer peripheral wall 62 of the housing main body 61. Thus, the bearing housing 67 closes the housing main body 61 from the front. In this way, a suction chamber 61A is formed in the housing main body 61.

[0067] A cylindrical first shaft support portion 66 centered on the driving axis R1 is provided at the center of the bearing housing 67. A first bearing 71 is embedded in the first shaft support portion 66.

[0068] The front cover 65 is disposed in front of the bearing housing 67. The front cover 65 is a bottomed cylindrical member having a second outer peripheral wall 68 and a second bottom wall 69. The second outer peripheral wall 68 is cylindrical with the drive axis R1 as the center. The second bottom wall 69 is located at the front end of the front cover 65. The second bottom wall 69 extends in a substantially circular flat shape orthogonally to the drive axis R1. The outer peripheral edge of the second bottom wall 69 is connected to the front end of the second outer peripheral wall 68.

[0069] The front cover 65 is fastened and connected to the first outer peripheral wall 62 together with the bearing housing 67 by bolts (not shown) in a state where the rear end of the second outer peripheral wall 68 abuts against the 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 adjacent to the suction chamber 61A in front of the suction chamber 61A. The second discharge portion 65A and the suction chamber 61A are partitioned by the bearing housing 67.

[0070] A discharge connection port 65B is formed in the front cover 65. The discharge connection port 65B is located near the outer peripheral edge in the front cover 65 and penetrates the front cover 65 in the direction parallel to the drive axis R1. The discharge connection port 65B communicates the second discharge portion 65A with the outside of the compressor. A pipe is connected to the discharge connection port 65B to allow the refrigerant discharged to the second discharge portion 65A to flow toward the condenser. In addition, the illustration of the pipe, the evaporator, and the condenser is omitted.

[0071] The rear cover 70 is disposed behind the housing main body 61. The rear cover 70 is a bottomed cylindrical member having a third outer peripheral wall 75 and a third bottom wall 76. The third outer peripheral wall 75 is cylindrical with the drive axis R1 as the center. The third bottom wall 76 is located at the rear end of the rear cover 70. The third bottom wall 76 extends in a substantially circular flat shape orthogonally to the drive axis R1. The outer peripheral edge of the third bottom wall 76 is connected to the rear end of the third outer peripheral wall 75.

[0072] The rear cover 70 is fastened and connected to the first outer peripheral wall 62 of the housing main body 61 by bolts (not shown) in a state where the front end of the third outer peripheral wall 75 abuts against the rear surface 632 of the first bottom wall 63 of the housing main body 61. Thus, a storage chamber 70A is formed between the rear cover 70 and the housing main body 61. The storage chamber 70A is adjacent to the suction chamber 61A behind the suction chamber 61A. The storage chamber 70A and the suction chamber 61A are partitioned by the first bottom wall 63 of the housing main body 61.

[0073] An intake connection port 70B is formed in the third outer peripheral wall 75 of the rear cover 70. The intake connection port 70B penetrates the third outer peripheral wall 75 in a direction intersecting with the drive axis R1. The intake connection port 70B communicates the storage chamber 70A with the outside of the compressor. A pipe is connected to the intake connection port 70B. Thus, the low-temperature and low-pressure refrigerant that has passed through the evaporator through the pipe is inhaled into the storage chamber 70A. The storage chamber 70A separates the inhaled refrigerant from the outside into gas and liquid, and stores the liquid refrigerant inside.

[0074] An intake communication port 63A is formed in the first bottom wall 63 of the housing main body 61. The intake communication port 63A is located near the outer peripheral edge of the first bottom wall 63 and near the intake connection port 70B, and penetrates the first bottom wall 63 in a direction parallel to the drive axis R1. The intake communication port 63A communicates the intake chamber 61A with the storage chamber 70A.

[0075] As Figure 2 shown, a first passage 63B is formed at the lowermost part of the first bottom wall 63. The first passage 63B penetrates the first bottom wall 63 in a direction parallel to the drive axis R1. The opening on the intake chamber 61A side in the first passage 63B becomes the inlet 63C of a lubricating oil supply passage 63H described later. The inlet 63C is located at the outermost peripheral part of the intake chamber 61A which is a scroll member chamber, and more specifically, at the lowermost part of the intake chamber 61A.

[0076] 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 penetrates the first bottom wall 63 in a direction parallel to the drive axis R1. The second passage 63D penetrates a part of the second shaft support portion 64 in the first bottom wall 63. The opening on the intake chamber 61A side in the second passage 63D becomes the outlet 63E1 of the lubricating oil supply passage 63H described later. The second passage 63D is located above the eccentric shaft 91. The outlet 63E1 is located on the drive axis R1 side above the eccentric shaft 91 and closer to the drive axis R1 than the third bearing 73.

[0077] A groove 63F is recessed in the rear surface 632 of the first bottom wall 63. The lower end, which is one end of the groove 63F, is connected to the first passage 63B, and the upper end, which 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 the "wall surface on the storage chamber side of the partition wall" in the present invention.

[0078] On the rear surface 632 of the first bottom wall 63, a cover body 77 formed of a metal plate is fixed by bolts (not shown). The cover body 77 extends in the direction in which the groove 63F extends, and seals the opening edge of the groove 63F. Thus, a third passage 63G is defined by the inner surface of the groove 63F and the cover body 77. The third passage 63G communicates the first passage 63B with the second passage 63D.

[0079] The liquid refrigerant accumulated in the storage chamber 70A comes into contact with the cover body 77, and the gaseous refrigerant in the storage chamber 70A, that is, the gaseous refrigerant which is colder than the lubricating oil accumulated in the outermost peripheral portion of the suction chamber 61A after being newly sucked into the compressor, comes into contact with the cover body 77. Therefore, the third passage 63G serves as a lubricating oil cooling portion 78 that cools the lubricating oil flowing in the third passage 63G through the liquid refrigerant and the gaseous refrigerant in the storage chamber 70A.

[0080] In this way, the first passage 63B, the third passage 63G, and the second passage 63D constitute a lubricating oil supply passage 63H.

[0081] In addition, an inverter housing provided with a connector portion is coupled to the rear of the rear cover 70. An inverter circuit having a circuit board, a switching element, etc. is housed in the inverter housing. The inverter circuit is electrically connected to the vehicle battery through a connector, and is electrically connected to a stator 17 described later through airtight passages provided in the third bottom wall 76, the first bottom wall 63, etc. Thereby, the inverter circuit converts the direct current supplied from the battery into an alternating current and supplies power to the stator 17. In addition, illustrations of the connector portion, the inverter housing, the inverter circuit, and the battery are omitted.

[0082] The electric motor 10 is housed in the suction chamber 61A. Thus, the suction chamber 61A also serves as a motor chamber for housing the electric motor 10. The electric motor 10 is composed of a stator 17 and a rotor 11.

[0083] The stator 17 is cylindrical with the drive axis R1 as the center and has a winding 18. The stator 17 is fixed to the housing body 61 by being embedded in the inner peripheral surface 62B of the first outer peripheral wall 62 of the housing body 61, and is further fixed to the housing 60.

[0084] The rotor 11 is cylindrical around the drive axis R1 and is disposed inside the stator 17. Although detailed illustrations are omitted, the rotor 11 is composed of a plurality of permanent magnets corresponding to the stator 17 and laminated steel plates for fixing each permanent magnet.

[0085] The scroll compression section 80 is housed in the suction chamber 61A. Thus, the suction chamber 61A also serves as a scroll element chamber for housing the scroll compression section 80. That is, the suction chamber 61A is an example of the "scroll element chamber" in the present invention. The scroll compression section 80 is composed of a driving scroll element 30 and a driven scroll element 40.

[0086] As Figure 1 shown, the driving scroll element 30 has a driving end plate 31, a driving peripheral wall 32, a driving scroll body 33, a bearing cover body 34, and a cover body 35.

[0087] The drive end plate 31 extends in a substantially circular plate shape orthogonally to the drive axis R1. The drive end plate 31 has a front surface 311 and a rear surface 312 located on the opposite side of the front surface 311.

[0088] On the front surface 311 of the drive end plate 31, a discharge valve chamber 36 is formed. The discharge valve chamber 36 is formed by a recess that is locally recessed from the front surface 311 toward the compression chamber 55 described later. The discharge valve chamber 36 has an inner surface shape that substantially corresponds to the outer shape of the discharge valve mechanism 56 described later so as to be able to accommodate the discharge valve mechanism 56. In addition, near the center of the drive end plate 31, a discharge port 37 that penetrates the drive end plate 31 in the front-rear direction is formed. One end of the discharge port 37 opens into the compression chamber 55 described later, and the other end of the discharge port 37 opens into the bottom surface of the discharge valve chamber 36. The discharge port 37 communicates the compression chamber 55 with the discharge valve chamber 36. The discharge port 37 is disposed near the drive axis R1.

[0089] In the discharge valve chamber 36, a discharge valve mechanism 56 is disposed. The discharge valve mechanism 56 has a discharge reed valve 57, a holding member 58, and a fixing bolt 59. The discharge reed valve 57 and the holding member 58 are fixed to the bottom surface of the discharge valve chamber 36 by the fixing bolt 59. The discharge reed valve 57 can open / close the discharge port 37. In addition, the holding member 58 can adjust the opening degree of the discharge reed valve 57. In the discharge reed valve 57, a tip valve portion that opens and closes the discharge port 37 is disposed at a position closer to the drive axis R1 than a base end fixing portion fixed by the fixing bolt 59.

[0090] The drive scroll 33 is integrally formed with the drive end plate 31 and is located inside the drive peripheral wall 32. The drive scroll 33 extends rearward from the rear surface 312 of the drive end plate 31 in parallel with the drive axis R1. The drive scroll 33 is formed in a spiral shape around the drive axis R1. More specifically, when viewed from the front, the drive scroll 33 is formed to rotate rightward around the drive axis R1 from the spiral center.

[0091] The drive peripheral wall 32 is composed of a rotor 11 disposed on the outer peripheral edge of the rear surface 312 of the drive end plate 31 and a cylindrical portion 51 of a cover body 35 described later disposed behind the rotor 11. The drive peripheral wall 32 extends rearward from the outer peripheral edge of the drive end plate 31, that is, toward the driven scroll member 40, in parallel with the drive axis R1. The drive peripheral wall 32 is formed in a substantially cylindrical shape centered on the drive axis R1.

[0092] The cover body 35 is a bottomed cylindrical member having a cylindrical portion 51 and a bottom wall portion 52. The cylindrical portion 51 is formed in a cylindrical shape centered on the drive axis R1. The bottom wall portion 52 is located at the rear end of the cover body 35. The bottom wall portion 52 extends in a substantially circular flat plate shape orthogonally to the drive axis R1.

[0093] The outer peripheral edge of the bottom wall portion 52 is connected to the rear end of the cylindrical portion 51. A second protrusion (boss) 53 protruding rearward is provided at the center of the bottom wall portion 52. A second bearing 72 is embedded in the second protrusion 53. The second protrusion 53 extends in a cylindrical shape in the direction of the drive axis R1 with the drive axis R1 as the center.

[0094] 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 the circumferential direction of the cover body 35. The suction port 54 penetrates the bottom wall portion 52 in the direction of the drive axis R1, that is, in the front-rear direction. In addition, the shape and number of the suction ports 54 can be appropriately designed.

[0095] The bearing cover body 34 has a cover portion 38 and a first protrusion 39 formed integrally with the cover portion 38.

[0096] The cover portion 38 extends in a substantially circular plate shape orthogonally to the drive axis R1. The cover portion 38 has a front surface 381 and a rear surface 382 located on the opposite side of the front surface 381. A through hole 38A is formed at the center of the cover portion 38.

[0097] The first protrusion 39 protrudes forward from the inner peripheral edge of the cover portion 38, that is, the center of the front surface 381 of the cover portion 38. The first protrusion 39 extends in a cylindrical shape in the direction of the drive axis R1 with the drive axis R1 as the center. The cylindrical inner space of the first protrusion 39 constitutes the first discharge portion 39A. The length ratio of the inner diameter of the first discharge portion 39A, which is the cylindrical inner space of the first protrusion 39, and the outer diameter of the first protrusion 39 is shorter than the length of the longest portion of the discharge valve mechanism 56. In addition, in this compressor, the discharge chamber is constituted by the discharge valve chamber 36, the first discharge portion 39A, and the second discharge portion 65A.

[0098] A disc-shaped washer (not shown) is disposed between the rear surface 382 of the cover portion 38 and the front surface 311 of the drive end plate 31. A communication port having the same diameter as the inner diameter of the first protrusion 39 is provided through the center of the washer. The washer is clamped between the front surface 311 of the drive end plate 31 and the rear surface 382 of the cover portion 38 to seal the space therebetween.

[0099] The cover portion 38 of the bearing cover body 34, the washer (not shown), the drive end plate 31 of the drive scroll member 30, the rotor 11, and the cylindrical portion 51 of the cover body 35 are fastened and connected by a plurality of bolts 50 extending parallel to the drive axis R1. The combination of these members achieved by the bolts 50 is performed after the driven mechanism 20 and the driven scroll member 40 are provided on the cover body 35 and the discharge valve mechanism 56 is provided on the drive end plate 31. That is, the cover body 35 sandwiches the driven scroll member 40 with respect to the drive end plate 31 and is connected to the drive end plate 31.

[0100] The driven scroll member 40 has a driven end plate 41 and a driven scroll body 43.

[0101] The driven end plate 41 extends in a substantially circular plate shape orthogonally to the driven axis R2. The driven axis R2 is eccentric with respect to the drive axis R1 and extends parallel to the drive axis R1. That is to say, the driven axis R2 is also parallel to the front-rear direction. The driven end plate 41 has a front surface 411 and a rear surface 412 located on the opposite side of the front surface 411.

[0102] A bottomed cylindrical concave portion 74 that is recessed locally from the center of the driven end plate 41 toward the compression chamber 55 is formed on the rear surface 412 of the driven end plate 41. The concave portion 74 extends cylindrically in the direction of the driven axis R2 with the driven axis R2 as the center. The concave portion 74 has an inner surface shape corresponding to the outer shape of the third shaft support portion 90.

[0103] The driven scroll body 43 is integrally formed with the driven end plate 41 and extends parallel to the driven axis R2 from the front surface 411 of the driven end plate 41 toward the front, that is, toward the drive end plate 31 of the drive scroll member 30. The driven scroll body 43 is formed in a scroll shape around the driven axis R2. More specifically, when viewed from the front, the driven scroll body 43 is formed to rotate rightward around the driven axis R2 from the scroll center.

[0104] The driven mechanism 20 is composed of four anti-rotation pins 21 and four rings 22. In addition, three or more anti-rotation pins 21 and rings 22 are sufficient respectively, and the number thereof can be appropriately designed. In addition, Figure 1 In, two of each anti-rotation pin 21 and each ring 22 are respectively shown.

[0105] Each anti-rotation pin 21 is respectively inserted through and fixed to the rear surface 412 of the driven end plate 41. Thus, each anti-rotation pin 21 is fixed to the driven end plate 41 in a state of protruding rearward from the driven end plate 41.

[0106] Each ring 22 is provided on the front surface 521 of the bottom wall portion 52 of the cover body 35 of the drive scroll member 30 so as to face each anti-rotation pin 21. Each ring 22 is respectively fitted into a circular bottomed hole recessed in the front surface 521 of the bottom wall portion 52.

[0107] In this compressor, the scroll compression portion 80 composed of the drive scroll member 30 and the driven scroll member 40 is disposed in the suction chamber 61A.

[0108] In the driving scroll member 30, the driving peripheral wall 32 is integrated with the rotor 11. Further, in the driving scroll member 30, a first bearing 71 is interposed between the first shaft support portion 66 of the bearing housing 67 and the first protrusion 39 of the bearing cover 34, and a second bearing 72 is interposed between the second shaft support portion 64 of the first bottom wall 63 and the second protrusion 53 of the cover 35. Thus, the driving scroll member 30 is supported by the housing 60 so as to be rotatable about the driving axis R1. Here, in this compressor, the driving scroll member 30 is supported by the housing 60 in a so-called double-supported state.

[0109] On the other hand, the driven scroll member 40 is disposed behind the drive end plate 31 in a state where the driven scroll body 43 faces the drive end plate 31 side within the driving scroll member 30. Thus, the rear surface 312 of the drive end plate 31 and the front surface 411 of the driven end plate 41 face each other in the driving axis R1 direction and the driven axis R2 direction. And the driving scroll member 30 and the driven scroll member 40 engage the driving scroll body 33 and the driven scroll body 43 inside the driving peripheral wall 32, and insert the respective anti-rotation pins 21 into the respective rings 22. In this way, the driven scroll member 40 is assembled into the driving scroll member 30 in a state where the drive end plate 31 and the driven end plate 41 face each other in the front-rear direction. Further, a compression chamber 55 is formed between both the driving scroll body 33 and the driven scroll body 43.

[0110] In the driven scroll member 40, a third bearing 73 is interposed between a third shaft support portion 90 eccentrically disposed with respect to the second shaft support portion 64 of the first bottom wall 63 and a recess 74 of the driven end plate 41. Thus, the driven scroll member 40 is supported by the housing 60 so as to be rotatable about the driven axis R2. Here, in this compressor, the driven scroll member 40 is supported by the housing 60 in a so-called single-supported (cantilever) state.

[0111] In the compressor configured as described above, power is supplied to the stator 17 by an inverter circuit (not shown) and the operation of the electric motor 10 is controlled, and the electric motor 10 operates. Thus, by the rotation of the rotor 11, within the suction chamber 61A, the driving scroll member 30 is driven to rotate about the driving axis R1. That is, the driving scroll member 30 integrally including the rotor 11 is driven to rotate. At this time, in the driven mechanism 20, the respective anti-rotation pins 21 slide on the inner peripheral surfaces of the respective rings 22 while causing the respective rings 22 to rotate relatively about the centers of the respective anti-rotation pins 21. In this way, the driven mechanism 20 transmits the torque of the driving scroll member 30 to the driven scroll member 40.

[0112] As a result, the driven scroll member 40 rotates followingly about the driven axis R2 by means of the driving scroll member 30 and the follower mechanism 20. At this time, the follower mechanism 20 restricts the driven scroll member 40 from rotating on its own axis. Thus, by means of the driving rotation of the driving scroll member 30 and the following rotation of the driven scroll member 40, the driven scroll member 40 revolves relative to the driving scroll member 30 about the driving axis R1, causing the volume of the compression chamber 55 to change.

[0113] Therefore, the 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 compressed to the discharge pressure in the compression chamber 55 is discharged from the discharge port 37 to the discharge valve chamber 36, discharged to the second discharge portion 65A through the first discharge portion 39A, and further discharged from the discharge connection port 65B to the condenser. In this way, air conditioning based on the vehicle air conditioner is carried out.

[0114] Here, in the scroll compression section 80, there are a plurality of sliding parts where sliding heat is generated. For example, the first bearing 71, the second bearing 72, the third bearing 73, the sliding part 81 between the rear surface 412 of the driven end plate 41 and the front end surface 641 of the second shaft support portion 64, the sliding part 82 between the rear surface 412 of the driven end plate 41 and the front surface 521 of the bottom wall portion 52 of the cover body 35, the follower mechanism 20, the sliding part between the driving scroll body 33 and the driven scroll body 43, the sliding part between the front end surface of the driving scroll body 33 and the front surface 411 of the driven end plate 41, and the sliding part between the front end of the driven scroll body 43 and the rear surface 312 of the driving end plate 31. It is necessary to supply lubricating oil to these sliding parts for lubrication and cooling.

[0115] In this compressor, after cooling the lubricating oil accumulated in the suction chamber 61A, which serves as a scroll member chamber, with the liquid refrigerant in the storage chamber 70A, it is supplied to the sliding parts.

[0116] That is, since centrifugal force acts within the rotating scroll compression section 80, the lubricating oil is centrifugally separated from the refrigerant, and the lubricating oil separated from the refrigerant flows out from the scroll compression section 80 to the suction chamber 61A. Then, in the suction chamber 61A, a fluid flow is generated in the rotation direction due to the influence of the centrifugal force of the rotating scroll compression section 80. Therefore, due to the action of centrifugal force, the lubricating oil accumulates in the outermost peripheral portion of the suction chamber 61A, forming an oil storage portion 83.

[0117] At the lowermost part of the suction chamber 61A, the inlet 63C of the lubricating oil supply passage 63H is opened. And the outlet 63E1 of this lubricating oil supply passage 63H is opened on the front end surface 641 of the second shaft support portion 64. That is, the outlet 63E1 is opened near the driving axis R1 within the scroll compression section 80 and outside the compression chamber 55.

[0118] The lowermost part of the outermost periphery of the suction chamber 61A has the highest pressure inside the suction chamber 61A. On the other hand, the pressure inside the scroll compression section 80 and outside the compression chamber 55 is lower than the pressure inside the suction chamber 61A and outside the scroll compression section 80. In addition, the refrigerant inside the suction chamber 61A (scroll member chamber) is sucked into the scroll compression section 80 through the suction port 54. Therefore, the pressure at the suction port 54 of the scroll compression section 80 is lower than the pressure at the outer peripheral portion of the suction chamber 61A. In particular, the pressure near the driving axis R1 where the second shaft support portion 64 is located is the lower one among the pressures inside the scroll compression section 80 and 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 accumulated in the oil storage portion 83 at the lowermost part of the suction chamber 61A is introduced into the inlet 63C of the lubricating oil supply passage 63H, and this lubricating oil flows through the lubricating oil supply passage 63H and is led out from the outlet 63E1 to the front end face 641 of the second shaft support portion 64. The supply of lubricating oil from the lubricating oil supply passage 63H is continuously carried out during the operation of the compressor.

[0119] Moreover, the lubricating oil coming out from the outlet 63E1 of the lubricating oil supply passage 63H flows to a position on the outer peripheral side relative to the outlet 63E1 due to the action of centrifugal force. Thereby, lubricating oil is supplied to the third bearing 73 existing on the outer peripheral side of the outlet 63E1, the sliding portion 81 between the rear surface 412 of the driven end plate 41 and the front end face 641 of the second shaft support portion 64, the second bearing 72, the sliding portion 82 between the rear surface 412 of the driven end plate 41 and the front surface 521 of the bottom wall portion 52 of the cover body 35, and the driven mechanism 20. Sometimes, the sliding portions such as the third bearing 73, the sliding portion 81 between the rear surface 412 of the driven end plate 41 and the front end face 641 of the second shaft support portion 64, the second bearing 72, the sliding portion 82 between the rear surface 412 of the driven end plate 41 and the front surface 521 of the bottom wall portion 52 of the cover body 35, and the driven mechanism 20 are collectively referred to as the lubricating oil supply sliding portions.

[0120] In this way, the lubricating oil accumulated in the oil storage portion 83 at the lowermost part of the suction chamber 61A can be continuously supplied to the lubricating oil supply sliding portions. Therefore, it is possible to effectively suppress the increase in sliding resistance due to insufficient lubricating oil at these lubricating oil supply sliding portions.

[0121] Moreover, the lubricating oil flowing through the lubricating oil supply passage 63H is cooled by the liquid refrigerant and the gaseous refrigerant in the storage chamber 70A in the lubricating oil cooling unit 78. Therefore, the lubricating oil supply sliding portion can be lubricated with the lubricating oil whose viscosity is more appropriately ensured. In addition, the lubricating oil supply sliding portion can be cooled with the lower-temperature lubricating oil. Therefore, it is possible to suppress a decrease in the viscosity of the lubricating oil due to heat from the lubricating oil supply sliding portion. As a result, it is possible to suppress an increase in the sliding resistance at the lubricating oil supply sliding portion.

[0122] Therefore, in the compressor of Embodiment 1, by supplying the lubricating oil accumulated in the scroll member chamber during operation to the sliding portion and improving the cooling effect of the lubricating oil on the sliding portion, it is possible to suppress an increase in the sliding resistance at the sliding portion, and further suppress a decrease in efficiency.

[0123] In addition, in this compressor, the lubricating oil supply passage 63H is formed by a first passage 63B, a third passage 63G, and a second passage 63D formed in the first bottom wall 63 that does not rotate even during the operation of the compressor. That is, the lubricating oil supply passage 63H penetrates the second shaft support portion 64 that is a non-rotating body and opens at the front end surface 641 of the second shaft support portion 64. Therefore, the supply of the lubricating oil through the lubricating oil supply passage 63H is stable.

[0124] Moreover, the second bearing 72 and the third bearing 73 are located closer to the drive axis R1 in the scroll compression unit 80. In the scroll compression unit 80, the amount of lubricating oil is more likely to be insufficient closer to the drive axis R1. In view of this, in this compressor, the lubricating oil supply passage 63H penetrates the second shaft support portion 64, and the outlet 63E1 of the lubricating oil supply passage 63H opens at a position closer to the drive axis R1 than the third bearing 73. Therefore, it is possible to supply the lubricating oil to the second bearing 72 and the third bearing 73 where the amount of lubricating oil is likely to be insufficient, well.

[0125] Embodiment 2

[0126] As Figure 3 shown, in the compressor of Embodiment 2, the position of the outlet 63E1 of the lubricating oil supply passage 63H in the compressor of Embodiment 1 is changed to the position of the outlet 63E2.

[0127] That is, a fourth passage 63J is formed in the second projection 53 of the bottom wall portion 52. The fourth passage 63J penetrates the second projection 53 in a direction parallel to the drive axis R1. The fourth passage 63J is located near the uppermost part of the second projection 53. The front-side opening of the fourth passage 63J becomes the outlet 63E2 of the lubricating oil supply passage 63H.

[0128] With the formation of the fourth passage 63J, the position of the second passage 63D changes to the position of the fifth passage 63K. The fifth passage 63K is on the same straight line as the fourth passage 63J, and the opening of the fifth passage 63K is connected to the opening on the rear side of the fourth passage 63J. In addition, with the change in position from the second passage 63D to the fifth passage 63K, the groove 63F extends upward, and the sixth passage 63L is delimited by the inner surface of the groove 63F and the cover body 77. The sixth passage 63L connects the first passage 63B and the fifth passage 63K. Thus, the lubricating oil supply passage 63H is constituted by the first passage 63B, the sixth passage 63L, the fifth passage 63K, and the fourth passage 63J.

[0129] In the compressor of Embodiment 2, the fourth passage 63J is formed in the second protrusion 53 in the cover body 35, and the outlet 63E2 of the lubricating oil supply passage 63H opens on the front surface 521 of the bottom wall portion 52 of the cover body 35.

[0130] Therefore, the lubricating oil discharged from the outlet 63E2 of the lubricating oil supply passage 63H that opens on the front surface 521 of the bottom wall portion 52 of the cover body 35 is supplied, under the action of centrifugal force, to the sliding portion 82 between the rear surface 412 of the driven end plate 41 and the front surface 521 of the bottom wall portion 52 and the driven mechanism 20, which are located at positions on the outer peripheral side relative to the outlet 63E2.

[0131] Thus, the lubricating oil cooled by the liquid refrigerant and the gas refrigerant in the storage chamber 70A can be directly supplied to the sliding portion 82 between the rear surface 412 of the driven 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, and the sliding portion 82 between the rear surface 412 of the driven end plate 41 and the front surface 521 of the bottom wall portion 52 and the driven mechanism 20 can be effectively cooled.

[0132] The other configurations and operations of this compressor are the same as those of the compressor of Embodiment 1. The same reference numerals are assigned to the same configurations, and the detailed descriptions related to the configurations are omitted.

[0133] Embodiment 3

[0134] As Figure 4 shown, in the compressor of Embodiment 3, the position of the outlet 63E1 of the lubricating oil supply passage 63H in the compressor of Embodiment 1 is changed to the position of the outlet 63E3.

[0135] That is, a seventh passage 63M is formed in the third shaft support portion 90 disposed on the front end surface 641 of the second shaft support portion 64. The seventh passage 63M penetrates the third shaft support portion 90 in a direction parallel to the drive axis R1. The seventh passage 63M is located near the uppermost part of the third shaft support portion 90. The opening on the front side in the seventh passage 63M becomes the outlet 63E3 of the lubricating oil supply passage 63H.

[0136] With the formation of the seventh passage 63M, the position of the second passage 63D changes to the position of the eighth passage 63N. The eighth passage 63N and the seventh passage 63M are on the same straight line, and the opening of the eighth passage 63N is connected to the opening on the rear side of the seventh passage 63M. In addition, with the position change from the second passage 63D to the eighth passage 63N, the length of the groove 63F also changes, and the ninth passage 63P is defined by the inner surface of the groove 63F and the cover body 77. The ninth passage 63P connects the first passage 63B and the eighth passage 63N. Thus, the lubricating oil supply passage 63H is constituted by the first passage 63B, the ninth passage 63P, the eighth passage 63N, and the seventh passage 63M.

[0137] In the compressor of Embodiment 3, the seventh passage 63M is formed in the third shaft support portion 90, and the outlet 63E3 of the lubricating oil supply passage 63H opens on the front end face 901 of the third shaft support portion 90. Therefore, similar to the compressor of Embodiment 1, lubricating oil is supplied to the third bearing 73, the sliding portion 81 of the rear surface 412 of the driven end plate 41 and the front end face 641 of the second shaft support portion 64, the second bearing 72, the sliding portion 82 of the rear surface 412 of the driven 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 at positions on the outer peripheral side relative to the outlet 63E3.

[0138] The other configurations and operations of this compressor are the same as those of the compressor of Embodiment 1. The same reference numerals are assigned to the same configurations, and the detailed descriptions related to the configurations are omitted.

[0139] Embodiment 4

[0140] As Figure 5 shown, in the compressor of Embodiment 4, the position of the outlet 63E1 of the lubricating oil supply passage 63H in the compressor of Embodiment 1 is changed to the position of the outlet 63E4.

[0141] 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 penetrates the eccentric shaft 91 in a direction parallel to the driving axis R1. The front - side opening in the tenth passage 63Q becomes the outlet 63E4 of the lubricating oil supply passage 63H.

[0142] With the formation of the tenth passage 63Q, the position of the second passage 63D changes to the position of the eleventh passage 63R. The eleventh passage 63R is on the same straight line as the tenth passage 63Q, and the opening of the eleventh passage 63R is connected to the opening on the rear side of the tenth passage 63Q. In addition, with the position change from the second passage 63D to the eleventh passage 63R, the length of the groove 63F also changes, and the twelfth passage 63S is defined by the inner surface of the groove 63F and the cover body 77. The twelfth passage 63S connects the first passage 63B and the eleventh passage 63R. Thus, the lubricating oil supply passage 63H is constituted by the first passage 63B, the twelfth passage 63S, the eleventh passage 63R, and the tenth passage 63Q.

[0143] In the compressor of Embodiment 4, the tenth passage 63Q is formed in the eccentric shaft 91, and the outlet 63E4 of the lubricating oil supply passage 63H opens on the front end surface 911 of the eccentric shaft 91. Therefore, similar to the compressor of Embodiment 1, lubricating oil is supplied to the third bearing 73 located at a position on the outer peripheral side of the outlet 63E4, the sliding portion 81 between the rear surface 412 of the driven end plate 41 and the front 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 end plate 41 and the front surface 521 of the bottom wall portion 52 of the cover body 35, and the driven mechanism 20.

[0144] The other configurations and operations of this compressor are the same as those of the compressor of Embodiment 1. The same reference numerals are used for the same configurations, and the detailed descriptions related to the configurations are omitted.

[0145] Embodiment 5

[0146] As Figure 6 shown, in the compressor of Embodiment 5, the formation of the lubricating oil supply passage 63H and the lubricating oil cooling portion 78 is changed.

[0147] The first passage 63B and the second passage 63D in the compressor of Embodiment 5 are formed at the same positions as the first passage 63B and the second passage 63D in the compressor of Embodiment 1. And 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 vertical direction. The lower bent portion 841 formed by bending one end side of the pipe 84 is connected to the first passage 63B, and the upper bent portion 842 formed by bending the other end side of the pipe 84 is connected to the second passage 63D.

[0148] Thus, the lubricating oil supply passage 63H is constituted by the first passage 63B, the thirteenth passage 63T in the pipe 84, and the second passage 63D. And the portion of the pipe 84 disposed in the storage chamber 70A becomes the lubricating oil cooling portion 78.

[0149] In this embodiment, the lubricating oil during the passage of the first passage 63T in the pipe 84 can be cooled by using the liquid refrigerant and the gas refrigerant in the storage chamber 70A through the peripheral wall of the pipe 84.

[0150] The other configurations and operations of this compressor are the same as those of the compressor in Embodiment 1. The same reference numerals are assigned to the same configurations, and the detailed descriptions related to the configurations are omitted.

[0151] As described above, the present invention has been described with respect to Embodiments 1 to 5. However, the present invention is not limited to the above Embodiments 1 to 5, and can of course be appropriately modified and applied without departing from the gist thereof.

[0152] For example, in the compressors of Embodiments 1 to 5, the inlet 63C of the lubricating oil supply passage 63H is provided at the lowermost part of the scroll chamber, but it is not limited thereto. The inlet of the lubricating oil supply passage 63H may also be provided at other outermost peripheral parts other than the lowermost part in the scroll chamber. In addition, the position of the inlet of the lubricating oil supply passage 63H may be any position that communicates with the oil storage part provided in the scroll chamber, and it may not be the outermost peripheral part.

[0153] In addition, in the compressors of Embodiments 1 to 5, one outlet 63E1 - 4 is provided for each of the lubricating oil supply passages 63H, but it is not limited thereto. The lubricating oil supply passage 63H may also be provided with a plurality of outlets.

[0154] In the compressors of Embodiments 1 to 5, the lubricating oil cooling part 78 is formed by the groove 63F recessed in the wall surface on the storage chamber 70A side of the first bottom wall 63 as the partition wall and the cover body 77, and the lubricating oil cooling part 78 is formed by the pipe 84 provided in the storage chamber 70A. However, it is not limited thereto. The lubricating oil cooling part may also be formed by providing a passage extending from the outer peripheral side to the inner peripheral side inside the partition wall, or a lubricating oil cooling part may be formed on the scroll chamber side.

[0155] In the compressors of Embodiments 1 to 5, the driving scroll member 30 is supported in a double - supported state with respect to the housing 60, and the driven scroll member 40 is supported in a single - supported state. However, it is not limited thereto. It is also possible to support both the driving scroll member 30 and the driven scroll member 40 in a single - supported state with respect to the housing 60.

[0156] In the compressors of Embodiments 1 to 5, the suction port 54 is formed on the cover body 35 of the driving scroll member 30. However, it is not limited thereto. The suction port may also be formed on the driving end plate 31 of the driving scroll member 30. In a compressor in which both the driving scroll member 30 and the driven scroll member 40 are supported in a single - supported state with respect to the housing 60, the suction port may also be formed on either the driving end plate 31 or the driven end plate 41.

[0157] In the compressors of Embodiments 1 to 5, in the driving scroll member 30, on the front surface 311 of the driving end plate 31 in which a discharge valve chamber 36 accommodating a discharge valve mechanism 56 is recessed, a bearing housing 34 having a cover portion 38 covering a part of the discharge valve chamber 36 and a part of the discharge valve mechanism 56 is joined. Further, a first discharge portion 39A which is an internal space of a first projection 39 of the bearing housing 34 is communicated with the discharge valve chamber 36. However, it is not limited thereto, and the bearing housing may be omitted, the discharge valve mechanism may be accommodated in a projection integrally protruding from the driving end plate or the driven end plate, and a bearing may be mounted on the projection.

[0158] In the compressors of Embodiments 1 to 5, the driven mechanism 20 is composed of an anti-rotation pin 21 and a ring 22. However, it is not limited thereto, and the driven mechanism 20 may also be configured by a pin / ring / pin method in which two pins are slidably contacted with an inner peripheral surface of a free ring, a pin / pin method in which outer peripheral surfaces of two pins are slidably contacted with each other, a method using a crosshead coupling, or the like.

[0159] In the compressors of Embodiments 1 to 5, the driving scroll member 30 is integrated with the rotor 11 by integrating the rotor 11 on the driving peripheral wall 32. However, it is not limited thereto, and it may also be configured such that the driving scroll member 30 and the rotor 11 are connected by a driving shaft in a manner capable of transmitting power, and the driving scroll member 30 and the rotor 11 are separately arranged in the driving axis R1 direction.

[0160] (Supplementary Note 1)

[0161] A twin rotary scroll compressor, characterized in that

[0162] it includes a housing, a driving mechanism, a driving scroll member, a driven scroll member, and a driven mechanism,

[0163] the housing has: a scroll member chamber accommodating the driving scroll member and the driven scroll member; a storage chamber for gas-liquid separation of refrigerant sucked from the outside and storing liquid refrigerant therein; and a partition wall partitioning the storage chamber and the scroll member chamber,

[0164] the driving scroll member is driven to rotate around a driving axis by the driving mechanism,

[0165] the driven scroll member is eccentric with respect to the driving scroll member and is driven to rotate around a driven axis by the driving scroll member and the driven mechanism,

[0166] a support portion is provided on the partition wall, and the support portion projects into the scroll member chamber with the driving axis as the center,

[0167] The driving scroll member is supported by a bearing disposed between the driving scroll member and the support portion so as to be capable of driving and rotating about the driving axis.

[0168] The scroll compression portion is constituted by the driving scroll member and the driven scroll member.

[0169] An oil storage portion for storing lubricating oil is provided in the scroll member chamber.

[0170] The double-rotary scroll compressor includes a lubricating oil supply passage that communicates with the oil storage portion and supplies lubricating oil to the scroll compression portion or the bearing.

[0171] A lubricating oil cooling portion is provided in the lubricating oil supply passage, and the lubricating oil cooling portion cools the lubricating oil in the lubricating oil supply passage using the refrigerant in the storage chamber.

[0172] (Supplementary Note 2)

[0173] The double-rotary scroll compressor according to Supplementary Note 1.

[0174] The driving scroll member has: a driving end plate; a driving scroll body, which is integral with the driving end plate and protrudes in a scroll shape toward the driven scroll member; and a cover body, which sandwiches the driven scroll member with respect to the driving end plate and is connected to the driving end plate.

[0175] The driven scroll member has: a driven end plate; and a driven scroll body, which is integral with the driven end plate and protrudes in a scroll shape toward the driving end plate.

[0176] Lubricating oil is supplied from the lubricating oil supply passage to the sliding portion between the driven end plate and the cover body.

[0177] (Supplementary Note 3)

[0178] The double-rotary scroll compressor according to Supplementary Note 1 or 2.

[0179] Lubricating oil is supplied from the lubricating oil supply passage to the bearing.

[0180] The lubricating oil supply passage penetrates through the support portion.

[0181] (Supplementary Note 4)

[0182] The double-rotary scroll compressor according to Supplementary Note 2.

[0183] It includes a driven shaft portion and a bushing. The driven shaft portion is provided in the housing, is eccentric with respect to the driving axis, and extends in a direction parallel to the driving axis. The bushing is inserted through the driven shaft portion.

[0184] A bearing for the bushing is provided between the driven scroll member and the bushing.

[0185] Lubricating oil is supplied from the lubricating oil supply passage to the bearing for the bushing.

[0186] The lubricating oil supply passage penetrates the driven shaft portion or the bushing.

[0187] (Supplementary Note 5)

[0188] The twin rotary scroll compressor according to Supplementary Note 2.

[0189] The lubricating oil supply passage penetrates the cover body.

[0190] (Supplementary Note 6)

[0191] The twin rotary scroll compressor according to any one of Supplementary Notes 1 to 5.

[0192] The lubricating oil cooling portion is formed by a groove recessed in the wall surface on the storage chamber side of the partition wall, and a plate-like cover body that extends in the direction in which the groove extends and is fixed to the wall surface so as to close the opening of the groove.

[0193] The passage partitioned by the inner surface of the groove and the cover body constitutes a part of the lubricating oil supply passage.

[0194] (Supplementary Note 7)

[0195] The twin rotary scroll compressor according to any one of Supplementary Notes 1 to 5.

[0196] The lubricating oil cooling portion is formed by a pipe disposed in the storage chamber.

[0197] The passage inside the pipe constitutes a part of the lubricating oil supply passage.

[0198] Industrial Applicability

[0199] The present invention can be used in an air conditioning device for a vehicle or the like.

[0200] Explanation of Reference Numerals

[0201] 10 Electric motor (drive mechanism)

[0202] 20 Driven mechanism

[0203] 30 Driving scroll member

[0204] 31 Driving end plate

[0205] 33 Driving scroll body

[0206] 35 Cover body

[0207] 40 Driven scroll member

[0208] 41 Driven end plate

[0209] 43 Driven scroll

[0210] 55 Compression chamber

[0211] 60 Housing

[0212] 61A Suction chamber (scroll chamber)

[0213] 63 First bottom wall (partition wall)

[0214] 632 Rear surface (wall surface)

[0215] 63F Groove

[0216] 63H Lubricating oil supply passage

[0217] 64 Second shaft support portion (support portion)

[0218] 70A Storage chamber

[0219] 72 Second bearing (bearing, sliding portion)

[0220] 73 Third bearing (bushing bearing, sliding portion)

[0221] 77 Cover body

[0222] 78 Lubricating oil cooling portion

[0223] 80 Scroll compression portion

[0224] 81, 82 Sliding portion

[0225] 83 Oil storage portion

[0226] 84 Pipe

[0227] 90 Third shaft support portion (bushing)

[0228] 91 Eccentric shaft (driven shaft portion)

[0229] R1 Driving axis

[0230] R2 Driven axis

Claims

1. A double-rotary scroll compressor, characterized in that, it includes a housing, a drive mechanism, a driving scroll member, a driven scroll member and a driven mechanism, the housing has: a scroll member chamber for accommodating the driving scroll member and the driven scroll member; a storage chamber for gas-liquid separation of the refrigerant sucked from the outside and storing the liquid refrigerant therein; and a partition wall for partitioning the storage chamber and the scroll member chamber, the driving scroll member is driven to rotate around a driving axis by the drive mechanism, the driven scroll member is eccentric with respect to the driving scroll member and is driven to rotate by the driving scroll member and the driven mechanism around a driven axis, a support portion is provided on the partition wall, and the support portion projects into the scroll member chamber with the driving axis as the center, the driving scroll member is supported by a bearing disposed between the driving scroll member and the support portion so as to be able to be driven to rotate around the driving axis, a scroll compression portion is constituted by the driving scroll member and the driven scroll member, an oil storage portion for storing lubricating oil is provided in the scroll member chamber, the double-rotary scroll compressor is provided with a lubricating oil supply passage communicating with the oil storage portion and supplying lubricating oil to the scroll compression portion or the bearing, a lubricating oil cooling portion is provided in the lubricating oil supply passage, and the lubricating oil cooling portion cools the lubricating oil in the lubricating oil supply passage by using the refrigerant in the storage chamber.

2. The double-rotary scroll compressor according to claim 1, the driving scroll member has: a driving end plate; a driving scroll body which is integral with the driving end plate and projects in a scroll shape toward the driven scroll member ； and a cover body which sandwiches the driven scroll member with respect to the driving end plate and is connected to the driving end plate, the driven scroll member has: a driven end plate; and a driven scroll body which is integral with the driven end plate and projects in a scroll shape toward the driving end plate, lubricating oil is supplied from the lubricating oil supply passage to the sliding portion between the driven end plate and the cover body.

3. The double-rotary scroll compressor according to claim 1 or 2, lubricating oil is supplied from the lubricating oil supply passage to the bearing, the lubricating oil supply passage penetrates through the support portion.

4. The double-rotary scroll compressor according to claim 2, it includes a driven shaft portion and a bushing, the driven shaft portion is provided on the housing, is eccentric with respect to the driving axis and extends parallel to the driving axis, and the bushing is inserted through by the driven shaft portion, a bearing for the bushing is provided between the driven scroll member and the bushing, lubricating oil is supplied from the lubricating oil supply passage to the bearing for the bushing, the lubricating oil supply passage penetrates through the driven shaft portion or the bushing.

5. The double-rotary scroll compressor according to claim 2, the lubricating oil supply passage penetrates through the cover body.

6. The double-rotary scroll compressor according to claim 1 or 2, The lubricating oil cooling part is formed by a groove recessed in the wall surface on the storage chamber side of the partition wall, and a plate-shaped cover body that extends in the extending direction of the groove and is fixed to the wall surface so as to close the opening of the groove. The passage partitioned by the inner surface of the groove and the cover body constitutes a part of the lubricating oil supply passage.

7. The double rotary scroll compressor according to claim 1 or 2, The lubricating oil cooling part is formed by a pipe disposed in the storage chamber. The passage in the pipe constitutes a part of the lubricating oil supply passage.

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