Double-rotating scroll compressor

Abstract

To provide a double-rotating scroll compressor capable of supplying lubricant accumulated in a scroll chamber to a sliding part during operation, and capable of enhancing a cooling effect of the sliding part by the lubricant to suppress increase in sliding resistance in the sliding part and thus suppress efficiency deterioration.SOLUTION: A housing 60 is provided with: a suction chamber 61A as a scroll chamber for accommodating a scroll compression part 80; a storage chamber 70A adjacent to the suction chamber 61A across a first bottom wall 63 as a partition wall; and a lubricant supply passage 63H. The lubricant supply passage 63H is communicated with an oil storage part 83 provided in the suction chamber 61A, and supplies lubricant to the scroll compression part 80, a second bearing 72, a third bearing 73, etc. A lubricant cooling part 78 is provided in the middle of the lubricant supply passage 63H to cool the lubricant in the lubricant supply passage 63H using a liquid refrigerant in the storage chamber 70A.SELECTED DRAWING: Figure 1

Description

[[Technical Field]]

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

[0002] Double-rotation scroll compressors have been conventionally known. This double-rotation scroll compressor includes a drive mechanism, a driving scroll, a driven mechanism, a driven scroll, and a housing.

[0003] The housing has a scroll chamber that accommodates a scroll compression section formed of the driving scroll and the driven scroll.

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

[0005] The driving scroll includes a driving end plate and a driving spiral body. The driving end plate extends crossing the driving axis. The driving spiral body protrudes from the driving end plate toward the driven scroll, and forms a spiral shape.

[0006] The driven scroll includes a driven end plate and a driven spiral body. The driven end plate extends crossing the driven axis. The driven spiral body protrudes from the driven end plate toward the driving scroll, and forms a spiral shape.

[0007] In the driving scroll and the driven scroll, the driving spiral body and the driven spiral body face each other to form a compression chamber, and the volume of the compression chamber is changed by rotational driving and rotational driven movement, and fluid sucked from a suction chamber is compressed according to the volume change and discharged to a discharge chamber.

[0008] In rotary compressors, such as this double-rotation scroll compressor, where the compression section rotates to compress the fluid in the compression chamber, the sliding parts, such as bearings that rotatably support the compression section relative to the housing, generate heat due to sliding friction. Furthermore, this heat reduces the viscosity of the lubricating oil in the bearings, increasing sliding resistance and creating a vicious cycle of increased heat generation. Increased sliding resistance in the sliding parts leads to decreased efficiency due to sliding losses.

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

[0010] Therefore, in the rotary compressor described in Patent Document 1, lubricating oil is drawn up from an oil reservoir located at the bottom of the compressor by a pumping mechanism and supplied to the compression section and the bearings of the rotating shaft. [Prior art documents] [Patent Documents]

[0011] [Patent Document 1] Japanese Patent Publication No. 2005-146987 [Overview of the project] [Problems that the invention aims to solve]

[0012] However, considering the heat capacity of the lubricating oil and the temperature of the lubricating oil stored in the oil reservoir within the compressor, the conventional countermeasures described above raise concerns about insufficient cooling of the sliding parts, and therefore cannot be considered sufficient.

[0013] In particular, in a dual-rotation scroll compressor, lubricating oil flows out from the rotating scroll compression section within the scroll chamber that houses the scroll compression section. Simultaneously, the centrifugal force of the rotating scroll compression section causes fluid flow in the direction of rotation, generating centrifugal force. As a result, lubricating oil accumulates at the outermost edge of the scroll chamber. If the amount of lubricating oil accumulating at the outermost edge of the scroll chamber continues to increase, the amount of lubricating oil required for the sliding parts will decrease. A decrease in the amount of lubricating oil increases sliding resistance, which may lead to a decrease in efficiency.

[0014] The present invention has been made in view of the above-mentioned conventional circumstances, and aims to solve the problem of providing a double-rotation scroll compressor that can suppress the increase in sliding resistance in the sliding parts and, consequently, suppress the decrease in efficiency, by supplying lubricating oil accumulated in the scroll chamber during operation to the sliding parts and enhancing the cooling effect of the lubricating oil on the sliding parts. [Means for solving the problem]

[0015] The dual-rotation scroll compressor of the present invention comprises a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism. The housing has a scroll chamber in which the drive scroll and the driven scroll are housed, a storage chamber for separating the refrigerant drawn in from the outside into gas and liquid form and storing the liquid refrigerant inside, and a partition wall separating the storage chamber and the scroll chamber. The drive scroll is rotationally driven around the drive axis by the drive mechanism, The driven scroll is rotated and driven by the driven scroll and the driven mechanism around its driven axis, while being eccentric with respect to the driven scroll. The partition wall is provided with a support portion that protrudes into the scroll chamber with respect to the drive axis, The drive scroll is supported so as to be rotatable around the drive axis by a bearing disposed between the drive scroll and the support portion. The driven scroll is supported so as to be rotatable around the driven axis by the driven scroll and a driven shaft portion that extends in the direction of the driven axis while being eccentric with respect to the drive axis. The drive scroll and the driven scroll constitute the scroll compression section. The scroll chamber is provided with an oil reservoir for storing lubricating oil. It is provided with a lubricating oil supply passage that communicates with the oil reservoir and supplies lubricating oil to the scroll compression section or the bearing, A lubricating oil cooling section is provided in the middle of the lubricating oil supply passage, which cools the lubricating oil in the lubricating oil supply passage with the liquid coolant in the storage chamber. Occasionally, The drive scroll comprises a drive end plate, a drive spiral body integral with the drive end plate and projecting spirally toward the driven scroll, and a cover body connected to the drive end plate while sandwiching the driven scroll between them. The driven scroll has a driven end plate and a driven spiral body that is integral with the driven end plate and projects spirally toward the drive 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. It is characterized by the following:

[0016] In the double-rotating scroll compressor of the present invention, a reservoir for lubricating oil is provided in the scroll chamber. This reservoir is provided, for example, as follows: During the operation of the scroll compression section, the lubricating oil supplied to the rotating scroll compression section flows out of the scroll compression section into the scroll chamber due to centrifugal force. Within the scroll chamber, a fluid flow occurs in the direction of rotation due to the influence of the centrifugal force of the rotating scroll compression section. As a result, the lubricating oil accumulates on the outer circumference of the scroll chamber due to the action of centrifugal force. Thus, a reservoir for lubricating oil is provided in the scroll chamber.

[0017] In the scroll chamber, areas closer to the rotation center of the scroll compression section are less affected by the centrifugal force of the fluid. Therefore, when comparing the pressure at the outer periphery of the scroll chamber with the pressure on the rotation center side of the scroll compression section, the outer periphery, which is more affected by the centrifugal force of the fluid, will have a higher pressure. In addition, since the fluid in the scroll chamber is drawn into the scroll compression section through an intake port provided in the driving scroll or driven scroll, the pressure at the intake port of the scroll compression section will be lower than the pressure at the outer periphery of the scroll chamber.

[0018] Therefore, for example, if an inlet of a lubricating oil supply passage is opened to an outer peripheral portion of a scroll chamber, and an outlet of the lubricating oil supply passage is opened, for example, in a scroll compression section or on a rotation center side of the scroll compression section within the scroll chamber, the pressure at the inlet of the lubricating oil supply passage is higher than that at the outlet. Due to this pressure difference, the lubricating oil accumulated in an 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 the lubricating oil is discharged from the outlet of the lubricating oil supply passage into the scroll compression section or to the rotation center side of the scroll compression section within the scroll chamber. Then, the lubricating oil discharged from the outlet of the lubricating oil supply passage flows toward the outer peripheral side from the outlet under the action of centrifugal force, and is supplied to portions of the scroll compression section and 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 sliding portions of the scroll compression section and the bearings, so that an increase in sliding resistance caused by insufficient lubricating oil at these sliding portions can be suppressed.

[0020] Furthermore, the lubricating oil flowing through the lubricating oil supply passage is cooled by liquid refrigerant in a storage chamber in a lubricating oil cooling section. Therefore, lubricating oil having a lower temperature than that of the lubricating oil accumulated in the oil storage portion of the scroll chamber is supplied to the sliding portions of the scroll compression section and the bearings. As a result, the sliding portions can be lubricated by the lubricating oil with more appropriately maintained viscosity, and cooling of the sliding portions with the lower-temperature lubricating oil can suppress a decrease in the viscosity of the lubricating oil caused by heat from the sliding portions. Through these effects, an increase in sliding resistance at the sliding portions of the scroll compression section and the bearings can be suppressed.

[0021] Therefore, the dual-rotation scroll compressor of the present invention supplies the lubricating oil accumulated in the scroll chamber during operation to the sliding portions, and enhances the cooling effect of the sliding portions by the lubricating oil, thereby suppressing an increase in sliding resistance at the sliding portions and consequently suppressing a decrease in efficiency.

[0022] The drive scroll comprises a drive end plate, a drive spiral body integrated with the drive end plate and projecting spirally toward the driven scroll, and a cover body connected to the drive end plate while sandwiching the driven scroll between them. attitude Furthermore, the driven scroll has a driven end plate and a driven spiral body that is integrated with the driven end plate and protrudes spirally toward the drive end plate. attitude Lubricating oil is supplied from the lubricating oil supply passage to the sliding part between the driven end plate and the cover body. ru.

[0023] In this case, the sliding surface between the driven end plate and the cover body in the scroll compression section requires lubrication. Lubrication is supplied to this sliding surface between the driven end plate and the cover body through a lubrication supply passage. Therefore, lubrication cooled by the liquid coolant can be effectively supplied to this sliding surface between the driven end plate and the cover body.

[0024] It is preferable that lubricating oil is supplied to the bearing from a lubricating oil supply passage, and that the lubricating oil supply passage penetrates the support portion.

[0025] In this case, lubricating oil cooled by a liquid coolant can be effectively supplied to bearings located on the outer circumference side of the support portion through a lubricating oil supply passage that penetrates the support portion.

[0026] Furthermore, bearings are relatively close to the rotation center of the scroll compression section within the scroll chamber. Within the scroll chamber, the closer to the rotation center of the scroll compression section, the more likely it is that the amount of lubricating oil will be insufficient. If the lubricating oil supply passage penetrates the support section, it becomes possible to supply sufficient lubricating oil to bearings that are prone to insufficient lubricating oil.

[0027] Furthermore, the support portion does not rotate even while the scroll compression section is operating. Therefore, lubricating oil can be stably discharged from the outlet that penetrates the support portion and opens on its tip surface.

[0028] The driven scroll may be provided with a bush through which the driven shaft is inserted. A bush bearing may be provided between the driven scroll and the bush. It is preferable that lubricating oil is supplied to the bush bearing from a lubricating oil supply passage. It is also preferable that the lubricating oil supply passage penetrates the driven shaft or the bush.

[0029] In this case, lubricating oil cooled by liquid coolant can be effectively supplied to the bushing bearing located on the outer circumference side of the driven shaft or bushing through a lubricating oil supply passage that penetrates the driven shaft or bushing.

[0030] Furthermore, bush bearings are located near the rotation center of the scroll compression section within the scroll chamber, making them prone to insufficient lubrication. If the lubrication supply passage penetrates the driven shaft or bush, it becomes possible to supply sufficient lubrication to bush bearings, which are prone to insufficient lubrication.

[0031] The lubricating oil supply passage preferably penetrates the cover body.

[0032] In this case, lubricating oil cooled by the liquid coolant can be effectively supplied to the sliding portion between the driven end plate, which is located on the outer circumference side of the outlet of the lubricating oil supply passage that penetrates the cover body, and the cover body.

[0033] The lubricating oil cooling section is preferably formed by a groove recessed in the storage chamber side wall of the compartment wall, and a plate-shaped cover that extends in the direction in which the groove extends and is fixed to the wall so as to close the opening of the groove. Furthermore, it is preferable that the passage partitioned by the inner surface of the groove and the cover constitutes part of the lubricating oil supply passage.

[0034] In this case, the lubricating oil passing through the passage partitioned by the inner surface of the groove and the cover can be cooled by the liquid coolant in the storage chamber via the cover.

[0035] The lubricating oil cooling section is preferably formed by pipes arranged within the storage chamber. Furthermore, it is preferable that the passages within the pipes constitute a part of the lubricating oil supply passage.

[0036] In this case, the lubricating oil passing through the passage inside the pipe can be cooled by the liquid coolant in the storage chamber via the pipe's circumferential wall. [Effects of the Invention]

[0037] According to the double-rotation scroll compressor of the present invention, the lubricating oil that accumulates in the scroll chamber during operation is supplied to the sliding parts, and the cooling effect of the lubricating oil on the sliding parts is enhanced, thereby suppressing the increase in sliding resistance in the sliding parts and consequently suppressing the decrease in efficiency. [Brief explanation of the drawing]

[0038] [Figure 1] Figure 1 is a cross-sectional view of the double-rotation scroll compressor of Example 1. [Figure 2] Figure 2 is a partially enlarged cross-sectional view showing the main parts of the double-rotation scroll compressor of Embodiment 1. [Figure 3] Figure 3 is a partially enlarged cross-sectional view showing the main parts of the double-rotation scroll compressor of Example 2. [Figure 4] Figure 4 is a partially enlarged cross-sectional view showing the main parts of the double-rotation scroll compressor of Embodiment 3. [Figure 5] Figure 5 is a partially enlarged cross-sectional view showing the main parts of the double-rotation scroll compressor of Embodiment 4. [Figure 6] Figure 6 is a partially enlarged cross-sectional view showing the main parts of the double-rotation scroll compressor of Example 5. [Modes for carrying out the invention]

[0039] Examples 1 to 5 that embody the present invention will be described below with reference to the drawings.

[0040] (Example 1) As shown in Figure 1, the double-rotation scroll compressor of Embodiment 1 (hereinafter simply referred to as the compressor) comprises a housing 60, a scroll compression section 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" in the present invention. This compressor is mounted on a vehicle (not shown) and constitutes an air conditioning system for the vehicle.

[0041] In this embodiment, the front-rear and up-down directions of the compressor are defined by the solid arrows shown in Figures 1 to 6. Note that the front-rear direction is just one example for the sake of explanation, and the compressor can change its orientation as appropriate depending on the vehicle on which it is mounted. However, in this embodiment, the compressor is mounted on the vehicle in a position where the inlet 63C of the lubricating oil supply passage 63H, which will be described later, is located at the lowest part of the intake chamber 61A.

[0042] The housing 60 consists of a housing body 61, a front cover 65, a bearing housing 67, and a rear cover 70.

[0043] The housing 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 a "partition wall" in the present invention. The first outer peripheral wall 62 is cylindrical with respect to the drive axis R1. The drive axis R1 is parallel to the front-rear direction. The first outer peripheral wall 62 also has an inner peripheral surface 62B. The first bottom wall 63 is located at the rear end of the housing body 61. The first bottom wall 63 extends in a substantially circular flat plate shape perpendicular to the drive axis R1.

[0044] The outer edge of the first bottom wall 63 is connected to the rear end of the first outer wall 62. The first bottom wall 63 has a front surface 631 and a rear surface 632 located opposite the front surface 631. A cylindrical second axial support portion 64 is provided in the center of the front surface 631 of the first bottom wall 63, projecting forward. The second axial support portion 64 is an example of a "support portion" in the present invention.

[0045] A cylindrical third shaft support 90 is positioned eccentrically with respect to the second shaft support 64 on its tip surface 641. The third shaft support 90 is an example of a "bushing" in the present invention. An eccentric shaft 91 is provided on the second shaft support 64. The eccentric shaft 91 is an example of a "driven shaft" in the present invention. The eccentric shaft 91 extends forward from the tip surface 641 of the second shaft support 64 parallel to the drive axis R1. The eccentric shaft 91 is eccentric with respect to the drive axis R1. The third shaft support 90 is rotatably mounted on the eccentric shaft 91. Furthermore, a third bearing 73 is fitted into a recess 74, which will be described later. The third bearing 73 is an example of a "bearing for a bushing" in the present invention. As a result, the third shaft support 90 is rotatable with respect to the recess 74 and the eccentric shaft 91, which will be described later.

[0046] The bearing housing 67 is positioned in front of the housing body 61. The bearing housing 67 extends in a substantially circular, flat plate shape perpendicular to the drive shaft R1. The bearing housing 67 is fastened to the first outer peripheral wall 62 of the housing body 61 together with the front cover 65 by bolts (not shown), with its outer peripheral edge in contact with the front end of the first outer peripheral wall 62 of the housing body 61. In this way, the bearing housing 67 closes the housing body 61 from the front. Thus, an intake chamber 61A is formed inside the housing body 61.

[0047] A cylindrical first shaft support portion 66 is provided in the center of the bearing housing 67, with the drive shaft center R1 as the center. The first bearing 71 is fitted inside the first shaft support portion 66.

[0048] The front cover 65 is positioned 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 its 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 perpendicular 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.

[0049] The front cover 65 is fastened to the first outer wall 62 together with the bearing housing 67 by bolts (not shown), with the rear end of the second outer wall 68 abutting against the front surface of the bearing housing 67. As a result, the front cover 65 forms a second discharge section 65A between itself and the bearing housing 67. The second discharge section 65A is located in front of the intake chamber 61A and is adjacent to the intake chamber 61A. The second discharge section 65A is separated from the intake chamber 61A by the bearing housing 67.

[0050] A discharge port 65B is formed in the front cover 65. The discharge port 65B is located near the outer edge of the front cover 65 and penetrates the front cover 65 in a direction parallel to the drive axis R1. The discharge port 65B connects the second discharge section 65A to the outside of the compressor. Piping is connected to the discharge port 65B, and the refrigerant discharged to the second discharge section 65A is circulated toward the condenser. The piping, evaporator, and condenser are not shown in the diagram.

[0051] The rear cover 70 is located behind the housing 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 its 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 perpendicular 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.

[0052] The rear cover 70 is fastened to the first outer wall 62 of the housing body 61 by bolts (not shown), with the front end of the third outer wall 75 abutting against the rear surface 632 of the first bottom wall 63 of the housing body 61. As a result, the rear cover 70 forms a storage chamber 70A between itself and the housing body 61. The storage chamber 70A is located behind the intake chamber 61A and is adjacent to the intake chamber 61A. The storage chamber 70A is separated from the intake chamber 61A by the first bottom wall 63 of the housing body 61.

[0053] An intake port 70B is formed in the third outer peripheral wall 75 of the rear cover 70. The intake port 70B penetrates the third outer peripheral wall 75 in a direction intersecting the drive shaft center R1. The intake port 70B connects the storage chamber 70A to the outside of the compressor. Piping is connected to the intake port 70B. As a result, low-temperature, low-pressure refrigerant that has passed through the evaporator is drawn into the storage chamber 70A through the piping.

[0054] A suction port 63A is formed in the first bottom wall 63 of the housing body 61. The suction port 63A is located near the outer edge of the first bottom wall 63 and near the suction connection port 70B, and penetrates the first bottom wall 63 in a direction parallel to the drive axis R1. The suction port 63A connects the suction chamber 61A and the storage chamber 70A.

[0055] As shown in Figure 2, a first passage 63B is formed at the lowest 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 of the first passage 63B on the intake chamber 61A side becomes the inlet 63C of the lubricating oil supply passage 63H, which will be described later. The inlet 63C is located at the outermost periphery of the intake chamber 61A, which is a scroll chamber, and more specifically at the lowest part of the intake chamber 61A.

[0056] 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 the portion of the second shaft support 64 in the first bottom wall 63. The opening of the second passage 63D on the intake chamber 61A side becomes the outlet 63E1 of the lubricating oil supply passage 63H, which will be described later. The second passage 63D is located above the eccentric shaft 91. The outlet 63E1 is located above the eccentric shaft 91 and is closer to the drive axis R1 than the third bearing 73.

[0057] A groove 63F is recessed in the rear surface 632 of the first bottom wall 63. One end of the groove 63F, the lower end, is connected to the first passage 63B, and the other end of the groove 63F, the upper end, 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 this invention.

[0058] A cover 77 made of a metal plate is fixed to the rear surface 632 of the first bottom wall 63 by bolts (not shown). The cover 77 extends in the direction in which the groove 63F extends, closing the opening edge of the groove 63F. As a result, the inner surface of the groove 63F and the cover 77 partition the third passage 63G. The third passage 63G connects the first passage 63B and the second passage 63D.

[0059] The lid 77 comes into contact with the liquid refrigerant accumulated in the storage chamber 70A, as well as with the gaseous refrigerant in the storage chamber 70A, which is at a lower temperature than the lubricating oil that accumulates on the outermost periphery of the intake chamber 61A immediately after being drawn into the compressor. Therefore, the third passage 63G becomes a lubricating oil cooling section 78 that cools the lubricating oil flowing through the third passage 63G with the liquid refrigerant and gaseous refrigerant in the storage chamber 70A.

[0060] Thus, the lubricating oil supply passage 63H is formed by the first passage 63B, the third passage 63G, and the second passage 63D.

[0061] An inverter case with a connector is attached to the rear of the rear cover 70. Inside the inverter case is an inverter circuit containing a circuit board and switching elements. The inverter circuit is electrically connected to the vehicle's battery through the connector and is also electrically connected to the stator 17, which will be described later, through airtight passages provided in the third bottom wall 76 and the first bottom wall 63. As a result, the inverter circuit supplies power to the stator 17 while converting the DC current supplied from the battery into AC current. The connector, inverter case, inverter circuit, and battery are not shown in the diagram.

[0062] The electric motor 10 is housed within the intake chamber 61A. Thus, the intake chamber 61A also serves as the motor chamber housing the electric motor 10. The electric motor 10 consists of a stator 17 and a rotor 11.

[0063] The stator 17 is cylindrical with the drive shaft center R1 as its center and has windings 18. The stator 17 is fixed to the housing body 61 and, by extension, the housing 60, by fitting into the inner surface 62B of the first outer peripheral wall 62 of the housing body 61.

[0064] The rotor 11 is cylindrical around the drive shaft R1 and is located inside the stator 17. Although detailed illustrations are omitted, the rotor 11 is composed of multiple permanent magnets corresponding to the stator 17 and laminated steel plates that fix each permanent magnet.

[0065] The scroll compression section 80 is housed within the intake chamber 61A. Thus, the intake chamber 61A also serves as the scroll chamber housing the scroll compression section 80. In other words, the intake chamber 61A is an example of a "scroll chamber" in this invention. The scroll compression section 80 is composed of a drive scroll 30 and a driven scroll 40.

[0066] As shown in Figure 1, the drive scroll 30 includes a drive end plate 31, a drive peripheral wall 32, a drive spiral body 33, a bearing cover body 34, and a cover body 35.

[0067] The drive end plate 31 extends in a substantially disc shape perpendicular 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.

[0068] A discharge valve chamber 36 is formed on the front surface 311 of the drive end plate 31. The discharge valve chamber 36 is formed by a recess in the front surface 311 that is partially recessed toward the compression chamber 55, which will be described later. The discharge valve chamber 36 has an inner surface shape that substantially corresponds to the outer surface shape of the discharge valve mechanism 56, which will be described later, so that it can accommodate the discharge valve mechanism 56. In addition, a discharge port 37 is formed near the center of the drive end plate 31, penetrating the drive end plate 31 in the front-rear direction. One end of the discharge port 37 opens into the compression chamber 55, which will be described later, and the other end of the discharge port 37 opens to the bottom surface of the discharge valve chamber 36, so that the discharge port 37 connects the compression chamber 55 and the discharge valve chamber 36. The discharge port 37 is located near the drive shaft center R1.

[0069] A discharge valve mechanism 56 is installed inside the discharge valve chamber 36. The discharge valve mechanism 56 includes a discharge reed valve 57, a retainer 58, and a fixing bolt 59. The discharge reed valve 57 and the retainer 58 are fixed to the bottom surface of the discharge valve chamber 36 by the fixing bolt 59. The discharge reed valve 57 can open and close the discharge port 37. The retainer 58 can adjust the opening degree of the discharge reed valve 57. In the discharge reed valve 57, the tip valve portion that opens and closes the discharge port 37 is positioned closer to the drive axis R1 than the base fixing portion which is fixed by the fixing bolt 59.

[0070] The drive spiral body 33 is integrally formed with the drive end plate 31 and is located inside the drive peripheral wall 32. The drive spiral body 33 extends from the rear surface 312 of the drive end plate 31 toward the rear parallel to the drive axis R1. The drive spiral body 33 is spiral-shaped around the drive axis R1. More specifically, when viewed from the front, the drive spiral body 33 is formed clockwise around the drive axis R1 from the spiral center.

[0071] The drive circumferential wall 32 is composed of a rotor 11 positioned on the outer peripheral edge of the rear surface 312 of the drive end plate 31, and a cylindrical portion 51 of the cover body 35, which will be described later, positioned behind the rotor 11. The drive circumferential wall 32 extends from the outer peripheral edge of the drive end plate 31 towards the rear, i.e., toward the driven scroll 40, parallel to the drive axis R1. The drive circumferential wall 32 has a substantially cylindrical shape centered on the drive axis R1.

[0072] 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 cylindrical in shape with the drive axis R1 as the center. 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 shape perpendicular to the drive axis R1.

[0073] The outer edge of the bottom wall portion 52 is connected to the rear end of the cylindrical portion 51. A second boss 53 is provided in the center of the bottom wall portion 52, projecting toward the rear. A second bearing 72 is fitted inside the second boss 53. The second boss 53 extends cylindrically in the direction of the drive axis R1, with the drive axis R1 as its center.

[0074] An intake port 54 is formed near the outer edge of the bottom wall portion 52. The intake port 54 is formed in a substantially elliptical shape that extends in the circumferential direction of the cover body 35. The intake port 54 penetrates the bottom wall portion 52 in the direction of the drive axis R1, i.e., in the front-to-back direction. The shape and number of intake ports 54 can be designed as appropriate.

[0075] The bearing cover body 34 has a cover portion 38 and a first boss 39 integrally formed with the cover portion 38.

[0076] The cover portion 38 extends in a substantially disc shape perpendicular to the drive shaft center 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 in the center of the cover portion 38.

[0077] The first boss 39 protrudes forward from the inner periphery of the cover portion 38, that is, from the center of the front surface 381 of the cover portion 38. The first boss 39 extends cylindrically in the direction of the drive axis R1, with the drive axis R1 as the center. The cylindrical internal space of the first boss 39 constitutes the first discharge portion 39A. The inner diameter of the first discharge portion 39A, which is the cylindrical internal space of the first boss 39, and the outer diameter of the first boss 39 are shorter than the length of the longest part of the discharge valve mechanism 56. In this compressor, the discharge chamber is composed of the discharge valve chamber 36, the first discharge portion 39A, and the second discharge portion 65A.

[0078] A disc-shaped gasket (not shown) is positioned between the rear surface 382 of the cover portion 38 and the front surface 311 of the drive end plate 31. A communication opening having the same diameter as the inner diameter of the first boss 39 is provided in the center of the gasket. The gasket is sandwiched between the front surface 311 of the drive end plate 31 and the rear surface 382 of the cover portion 38, sealing the space between them.

[0079] The cover portion 38 of the bearing cover body 34, a gasket (not shown), the drive end plate 31 of the drive scroll 30, the rotor 11, and the cylindrical portion 51 of the cover body 35 are fastened together by a number of bolts 50 extending parallel to the drive axis R1. The connection of these components by bolts 50 is performed after the driven mechanism 20 and the driven scroll 40 are set on the cover body 35, and the discharge valve mechanism 56 is set on the drive end plate 31.

[0080] The driven scroll 40 has a driven end plate 41 and a driven spiral body 43.

[0081] The driven end plate 41 extends in a substantially disc shape perpendicular to the driven axis R2. The driven axis R2 extends parallel to the drive axis R1 while being eccentric with respect to the drive axis R1. In other words, the driven axis R2 is also parallel in 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.

[0082] A bottomed cylindrical recess 74 is formed on the rear surface 412 of the driven end plate 41, partially recessed from the center of the driven end plate 41 toward the compression chamber 55. The recess 74 extends cylindrically in the direction of the driven axis R2, with the driven axis R2 as its center. The recess 74 has an inner shape that corresponds to the outer shape of the third axial support 90.

[0083] The driven spiral body 43 is integrally formed with the driven end plate 41 and extends forward from the front surface 411 of the driven end plate 41, that is, toward the driven end plate 31 of the drive scroll 30, parallel to the driven axis R2. The driven spiral body 43 is spiral-shaped around the driven axis R2. More specifically, when viewed from the front, the driven spiral body 43 is formed clockwise around the driven axis R2 from the spiral center.

[0084] The driven mechanism 20 consists of four rotation-stopping pins 21 and four rings 22. The number of rotation-stopping pins 21 and rings 22 can be designed as needed, as long as there are at least three of each. Figure 1 shows two of each rotation-stopping pin 21 and ring 22.

[0085] Each rotation-preventing pin 21 is inserted through and fixed to the rear surface 412 of the driven end plate 41. As a result, each rotation-preventing pin 21 is fixed to the driven end plate 41 in a state where it protrudes rearward from the driven end plate 41.

[0086] Each ring 22 is positioned on the front surface 521 of the bottom wall 52 of the cover body 35 of the drive scroll 30, facing each rotation-preventing pin 21. Each ring 22 is fitted into a circular, bottomed hole recessed in the front surface 521 of the bottom wall 52.

[0087] In this compressor, a scroll compression section 80, which consists of a drive scroll 30 and a driven scroll 40, is located within the intake chamber 61A.

[0088] In the drive scroll 30, the rotor 11 is integrated with the drive peripheral wall 32. Furthermore, in the drive scroll 30, a first bearing 71 is interposed between the first shaft support 66 of the bearing housing 67 and the first boss 39 of the bearing cover body 34, and a second bearing 72 is interposed between the second shaft support 64 of the first bottom wall 63 and the second boss 53 of the cover body 35. As a result, the drive scroll 30 is supported by the housing 60 so as to be rotatable around the drive axis R1. In this compressor, the drive scroll 30 is supported by the housing 60 in a so-called double-supported manner.

[0089] Meanwhile, the driven scroll 40 is positioned behind the drive end plate 31 within the drive scroll 30, with the driven spiral body 43 facing the drive end plate 31. As a result, 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 direction of the drive axis R1 and the driven axis R2. The drive scroll 30 and the driven scroll 40 mesh with the drive spiral body 33 and the driven spiral body 43 inside the drive peripheral wall 32, and their respective rotation-preventing pins 21 enter into their respective rings 22. In this way, the driven scroll 40 is assembled within the drive scroll 30 with the drive end plate 31 and the driven end plate 41 facing each other in the front-rear direction. Furthermore, the drive spiral body 33 and the driven spiral body 43 form a compression chamber 55 between them.

[0090] In the driven scroll 40, a third bearing 73 is interposed between a third pivot 90, which is eccentrically positioned relative to the second pivot 64 of the first bottom wall 63, and a recess 74 in the driven end plate 41. As a result, the driven scroll 40 is supported by the housing 60 so as to be rotatable around the driven axis R2. In this compressor, the driven scroll 40 is supported by the housing 60 in a so-called cantilevered manner.

[0091] In this compressor configured as described above, an inverter circuit (not shown) supplies power to the stator 17 and controls the operation of the electric motor 10, thereby operating the electric motor 10. As a result, the rotor 11 rotates, causing the drive scroll 30 to rotate around the drive axis R1 within the intake chamber 61A. In other words, the drive scroll 30, which integrally includes the rotor 11 in the drive peripheral wall 32, is driven to rotate. At this time, in the driven mechanism 20, each rotation-stopping pin 21 slides against the inner surface of each ring 22, causing each ring 22 to rotate relative to each other around the center of each rotation-stopping pin 21. In this way, the driven mechanism 20 transmits the torque of the drive scroll 30 to the driven scroll 40.

[0092] As a result, the driven scroll 40 is rotated by the drive scroll 30 and the driven mechanism 20 around the driven axis R2. In this process, the driven mechanism 20 restricts the rotation of the driven scroll 40. Thus, the drive scroll 30 and the driven scroll 40 change the volume of the compression chamber 55 by causing the driven scroll 40 to revolve relative to the drive scroll 30 around the drive axis R1 through their rotational drive and rotational drive.

[0093] Therefore, the refrigerant in the intake chamber 61A is drawn into the compression chamber 55 through the intake port 54 and compressed in the compression chamber 55. The refrigerant, compressed to the discharge pressure in the compression chamber 55, is then discharged from the discharge port 37 to the discharge valve chamber 36, passes through the first discharge section 39A and is discharged to the second discharge section 65A, and further discharged to the condenser through the discharge connection port 65B. In this way, air conditioning is performed by the vehicle air conditioning system.

[0094] In the scroll compression section 80, there are several sliding parts that can generate sliding heat. 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 surface 641 of the second shaft support 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 52 of the cover body 35, the driven mechanism 20, the sliding part between the drive spiral body 33 and the driven spiral body 43, the sliding part between the front surface of the drive spiral body 33 and the front surface 411 of the driven end surface 41, and the sliding part between the front of the driven spiral body 43 and the rear surface 312 of the drive end plate 31. These sliding parts need to be lubricated by supplying lubricating oil and cooled.

[0095] In this compressor, the lubricating oil that accumulates in the suction chamber 61A, which is the scroll chamber, during operation is cooled by the liquid refrigerant in the storage chamber 70A before being supplied to the sliding parts.

[0096] In other words, centrifugal force acts within the rotating scroll compression section 80, causing the lubricating oil to be separated from the refrigerant by centrifugal force, and the separated lubricating oil flows out of the scroll compression section 80 into the suction chamber 61A. Within the suction chamber 61A, a fluid flow is generated in the direction of rotation due to the centrifugal force of the rotating scroll compression section 80. As a result, the lubricating oil accumulates at the outermost periphery of the suction chamber 61A due to the action of centrifugal force, forming an oil reservoir 83.

[0097] An inlet 63C of a lubricating oil supply passage 63H opens at the bottom of the intake chamber 61A. The outlet 63E1 of this lubricating oil supply passage 63H opens at the tip surface 641 of the second shaft support 64. In other words, the outlet 63E1 opens inside the scroll compression section 80 and outside the compression chamber 55, near the drive shaft center R1.

[0098] The lowest part of the outermost periphery of the intake chamber 61A has the highest pressure within the intake 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 intake chamber 61A and outside the scroll compression section 80. Furthermore, since refrigerant from the scroll chamber 61A is drawn into the scroll compression section 80 through the intake port 54, the pressure at the intake port 54 of the scroll compression section 80 is lower than the pressure at the outer periphery of the intake chamber 61A. In particular, the pressure near the drive axis R1 where the second shaft support 64 is located is among the lowest pressures inside the scroll compression section 80 and outside the compression chamber 55. For this reason, 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 reservoir 83 at the bottom of the intake 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 led out from the outlet 63E1 to the tip surface 641 of the second shaft support 64. This supply of lubricating oil from the lubricating oil supply passage 63H is performed continuously while the compressor is operating.

[0099] Then, the lubricating oil that exits from the outlet 63E1 of the lubricating oil supply passage 63H flows outward from the outlet 63E1 due to the action of centrifugal force. As a result, lubricating oil is supplied to the third bearing 73, the sliding part 81 between the rear surface 412 of the driven end plate 41 and the front surface 641 of the second shaft support 64, the second bearing 72, the sliding part 82 between the rear surface 412 of the driven end plate 41 and the front surface 521 of the bottom wall 52 of the cover body 35, and the driven mechanism 20, which are located on the outer circumference side of the outlet 63E1. The third bearing 73, the sliding part 81 between the rear surface 412 of the driven end plate 41 and the front surface 641 of the second shaft support 64, the second bearing 72, the sliding part 82 between the rear surface 412 of the driven end plate 41 and the front surface 521 of the bottom wall 52 of the cover body 35, and the driven mechanism 20 are sometimes collectively referred to as the lubricating oil supply sliding part.

[0100] In this way, the lubricating oil in the oil reservoir 83 accumulated at the bottom of the intake chamber 61A can be continuously supplied to the lubricating oil supply sliding parts, effectively suppressing the increase in sliding resistance due to insufficient lubricating oil in these lubricating oil supply sliding parts.

[0101] Furthermore, the lubricating oil flowing through the lubricating oil supply passage 63H is cooled in the lubricating oil cooling section 78 by the liquid and gaseous refrigerants in the storage chamber 70A. As a result, the lubricating oil supply sliding section can be lubricated with lubricating oil that has a more appropriate viscosity. In addition, since the lubricating oil supply sliding section can be cooled with lubricating oil at a lower temperature, it is possible to suppress the decrease in viscosity of the lubricating oil due to heat from the lubricating oil supply sliding section. As a result, it is possible to suppress the increase in sliding resistance in the lubricating oil supply sliding section.

[0102] Therefore, the compressor of Example 1 can suppress the increase in sliding resistance in the sliding parts and, consequently, suppress the decrease in efficiency by supplying the lubricating oil that accumulates in the scroll chamber during operation to the sliding parts and by enhancing the cooling effect of the lubricating oil on the sliding parts.

[0103] Furthermore, 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, which are formed in the first bottom wall 63, which does not rotate even when the compressor is operating. In other words, the lubricating oil supply passage 63H penetrates the second shaft support 64, which is a non-rotating body, and opens to the tip surface 641 of the second shaft support 64. As a result, the supply of lubricating oil through the lubricating oil supply passage 63H becomes stable.

[0104] Furthermore, the second bearing 72 and the third bearing 73 are located close to the drive axis R1 within the scroll compression section 80. Within the scroll compression section 80, the amount of lubricating oil tends to be insufficient closer to the drive axis R1. In this compressor, the lubricating oil supply passage 63H penetrates the second shaft support 64, and the outlet 63E1 of the lubricating oil supply passage 63H opens closer to the drive axis R1 than the third bearing 73, so that lubricating oil can be supplied well to the second bearing 72 and the third bearing 73, which tend to have insufficient lubricating oil.

[0105] (Example 2) As shown in Figure 3, in the compressor of Example 2, the position of the outlet 63E1 of the lubricating oil supply passage 63H has been changed to the position of outlet 63E2 compared to the compressor of Example 1.

[0106] In other words, a fourth passage 63J is formed in the second boss 53 of the bottom wall portion 52. The fourth passage 63J penetrates 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. The front opening of the fourth passage 63J becomes the outlet 63E2 of the lubricating oil supply passage 63H.

[0107] With the formation of the fourth passage 63J, the position of the second passage 63D is changed to the position of the fifth passage 63K. The fifth passage 63K and the fourth passage 63J are located on the same straight line, and the opening of the fifth passage 63K is connected to the rear opening 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 inner surface of the groove 63F and the cover 77 partition the sixth passage 63L. The sixth passage 63L connects the first passage 63B and the fifth passage 63K. Thus, the first passage 63B, the sixth passage 63L, the fifth passage 63K, and the fourth passage 63J constitute the lubricating oil supply passage 63H.

[0108] In the compressor of Embodiment 2, 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 opens to the front surface 521 of the bottom wall portion 52 of the cover body 35.

[0109] Therefore, the lubricating oil that exits from the outlet 63E2 of the lubricating oil supply passage 63H, which opens on the front surface 521 of the bottom wall portion 52 of the cover body 35, is supplied by 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, which are located on the outer circumference side of the outlet 63E2, and to the driven mechanism 20.

[0110] As a result, lubricating oil cooled by the liquid and gaseous refrigerants 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 to the driven mechanism 20, without passing through other sliding parts, thereby effectively cooling 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 to the driven mechanism 20.

[0111] The other components and operations of this compressor are the same as those of the compressor in Example 1, and the same reference numerals are used for identical components, and a detailed explanation of the components is omitted.

[0112] (Example 3) As shown in Figure 4, in the compressor of Example 3, the position of the outlet 63E1 of the lubricating oil supply passage 63H has been changed to the position of outlet 63E3 compared to the compressor of Example 1.

[0113] Specifically, a seventh passage 63M is formed in the third shaft support 90, which is located on the tip surface 641 of the second shaft support 64. The seventh passage 63M penetrates the third shaft support 90 in a direction parallel to the drive axis R1. The seventh passage 63M is located near the top of the third shaft support 90. The front opening of the seventh passage 63M becomes the outlet 63E3 of the lubricating oil supply passage 63H.

[0114] With the formation of the seventh passage 63M, the position of the second passage 63D is changed to the position of the eighth passage 63N. The eighth passage 63N and the seventh passage 63M are located on the same straight line, and the opening of the eighth passage 63N is connected to the rear opening of the seventh passage 63M. In addition, with the change in position from the second passage 63D to the eighth passage 63N, the length of the groove 63F is also changed, and the inner surface of the groove 63F and the cover 77 partition the ninth passage 63P. The ninth passage 63P connects the first passage 63B and the eighth passage 63N. Thus, the first passage 63B, the ninth passage 63P, the eighth passage 63N, and the seventh passage 63M constitute the lubricating oil supply passage 63H.

[0115] In the compressor of Embodiment 3, the seventh passage 63M is formed in the third shaft support 90, and the outlet 63E3 of the lubricating oil supply passage 63H opens to the front end surface 901 of the third shaft support 90. Therefore, similar to the compressor of Embodiment 1, lubricating oil is supplied to 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 64, the second bearing 72, 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, and the driven mechanism 20, which are located on the outer circumference side of the outlet 63E3.

[0116] The other components and operations of this compressor are the same as those of the compressor in Example 1, and the same reference numerals are used for identical components, and a detailed explanation of the components is omitted.

[0117] (Example 4) As shown in Figure 5, in the compressor of Example 4, the position of the outlet 63E1 of the lubricating oil supply passage 63H has been changed to the position of outlet 63E4 compared to the compressor of Example 1.

[0118] In other words, a tenth passage 63Q is formed in the eccentric shaft 91 provided in the second shaft support 64. The tenth passage 63Q penetrates the eccentric shaft 91 in a direction parallel to the drive shaft center R1. The front opening of the tenth passage 63Q becomes the outlet 63E4 of the lubricating oil supply passage 63H.

[0119] With the formation of the 10th passage 63Q, the position of the 2nd passage 63D is changed to the position of the 11th passage 63R. The 11th passage 63R and the 10th passage 63Q are located on the same straight line, and the opening of the 11th passage 63R is connected to the rear opening of the 10th passage 63Q. In addition, with the change in position from the 2nd passage 63D to the 11th passage 63R, the length of the groove 63F is also changed, and the inner surface of the groove 63F and the cover 77 partition the 12th passage 63S. The 12th passage 63S connects the 1st passage 63B and the 11th passage 63R. Thus, the 1st passage 63B, the 12th passage 63S, the 11th passage 63R, and the 10th passage 63Q constitute the lubricating oil supply passage 63H.

[0120] In the compressor of Embodiment 4, the tenth passage 63Q is formed on the eccentric shaft 91, and the outlet 63E4 of the lubricating oil supply passage 63H opens to the tip surface 911 of the eccentric shaft 91. Therefore, similar to the compressor of Embodiment 1, lubricating oil is supplied to the third bearing 73, the sliding part 81 between the rear surface 412 of the driven end plate 41 and the tip surface 641 of the second shaft support 64, the second bearing 72, 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, and the driven mechanism 20, which are located on the outer circumference side of the outlet 63E4.

[0121] The other components and operations of this compressor are the same as those of the compressor in Example 1, and the same reference numerals are used for identical components, and a detailed explanation of the components is omitted.

[0122] (Example 5) As shown in Figure 6, the compressor of Example 5 has been modified in terms of the formation of the lubricating oil supply passage 63H and the lubricating oil cooling section 78.

[0123] In the compressor of Embodiment 5, the first passage 63B and the second passage 63D are formed in the same positions as in the compressor of Embodiment 1. A pipe 84 is connected to the first passage 63B and the second passage 63D. The pipe 84 is located within the storage chamber 70A and extends vertically. A downward bend 841, formed by bending one end of the pipe 84, is connected to the first passage 63B, and an upward bend 842, formed by bending the other end of the pipe 84, is connected to the second passage 63D.

[0124] As a result, the lubricating oil supply passage 63H is formed by the first passage 63B, the 13th passage 63T and the second passage 63D within the pipe 84. The portion of the pipe 84 located within the storage chamber 70A is designated as the lubricating oil cooling section 78.

[0125] In this embodiment, the lubricating oil passing through the 13th passage 63T in the pipe 84 can be cooled by the liquid refrigerant and gaseous refrigerant in the storage chamber 70A via the peripheral wall of the pipe 84.

[0126] The other components and operations of this compressor are the same as those of the compressor in Example 1, and the same reference numerals are used for identical components, and a detailed explanation of the components is omitted.

[0127] Although the present invention has been described above in reference to Examples 1 to 5, it goes without saying that the present invention is not limited to Examples 1 to 5, and can be applied with appropriate modifications without departing from its spirit.

[0128] For example, in the compressors of Examples 1 to 5, the inlet 63C of the lubricating oil supply passage 63H is located at the bottom of the scroll chamber. However, the inlet of the lubricating oil supply passage 63H may be located at any other outermost part of the scroll chamber besides the bottom. Furthermore, the location of the inlet of the lubricating oil supply passage 63H does not have to be at the outermost part, as long as it is in a position that communicates with the oil reservoir provided in the scroll chamber.

[0129] Furthermore, in the compressors of Examples 1 to 5, one outlet 63E1 to 63E4 is provided for each of the lubricating oil supply passages 63H, but the lubricating oil supply passages 63H may have multiple outlets.

[0130] In the compressors of Examples 1 to 5, a lubricating oil cooling section 78 is formed by a groove 63 recessed in the wall surface on the storage chamber 70A side of the first bottom wall 63 which serves as a partition wall, and a cover 77, or by a pipe 84 provided inside the storage chamber 70A. However, the invention is not limited to these, and a lubricating oil cooling section may be formed by providing a passage extending from the outer circumference to the inner circumference inside the partition wall, or by forming a lubricating oil cooling section on the scroll chamber side.

[0131] In the compressors of Examples 1 to 5, the drive scroll 30 is supported by the housing 60 in a double-supported manner, while the driven scroll 40 is supported by the housing 60 in a cantilevered manner. However, the design is not limited to this, and both the drive scroll 30 and the driven scroll 40 may be supported by the housing 60 in a cantilevered manner.

[0132] In the compressors of Examples 1 to 5, an intake port 54 is formed in the cover body 35 of the drive scroll 30. However, the compressor is not limited to this, and an intake port may also be formed in the drive end plate 31 of the drive scroll 30. In a compressor in which both the drive scroll 30 and the driven scroll 40 are supported by the housing 60 in a cantilevered manner, an intake port may be formed in either the drive end plate 31 or the driven end plate 41.

[0133] In the compressors of Examples 1 to 5, in the drive scroll 30, a bearing cover body 34 having a cover portion 38 that covers a part of the discharge valve chamber 36 and a part of the discharge valve mechanism 56 is attached to the front surface 311 of the drive end plate 31, which has a recessed discharge valve chamber 36 for housing the discharge valve mechanism 56. The first discharge portion 39A, which is the internal space of the first boss 39 of the bearing cover body 34, is connected to the discharge valve chamber 36. However, the invention is not limited to this, and the bearing cover body may be omitted, and the discharge valve mechanism may be housed in a boss integrally projecting from the drive end plate or driven end plate, with a bearing mounted on that boss.

[0134] In the compressors of Examples 1 to 5, the driven mechanism 20 is composed of a rotation-preventing pin 21 and a ring 22. However, the driven mechanism 20 is not limited to this and may be composed of a pin-ring-pin system in which two pins slide against the inner surface of a single free ring, a pin-pin system in which the outer surfaces of two pins slide against each other, or a system using an Oldham joint.

[0135] In the compressors of Examples 1 to 5, the drive scroll 30 and the rotor 11 are integrated by integrating the rotor 11 with the drive peripheral wall 32. However, the configuration is not limited to this, and the drive scroll 30 and the rotor 11 may be arranged spaced apart in the direction of the drive axis R1 by connecting them to the drive shaft so as to transmit power.

[0136] (Note 1) The system comprises a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism. The housing has a scroll chamber in which the drive scroll and the driven scroll are housed, a storage chamber for separating the refrigerant drawn in from the outside into gas and liquid form and storing the liquid refrigerant inside, and a partition wall separating the storage chamber and the scroll chamber. The drive scroll is rotationally driven around the drive axis by the drive mechanism, The driven scroll is rotated and driven by the driven scroll and the driven mechanism around its driven axis, while being eccentric with respect to the driven scroll. The partition wall is provided with a support portion that protrudes into the scroll chamber with respect to the drive axis, The drive scroll is supported so as to be rotatable around the drive axis by a bearing disposed between the drive scroll and the support portion. The driven scroll is supported so as to be rotatable around the driven axis by the driven scroll and a driven shaft portion that extends in the direction of the driven axis while being eccentric with respect to the drive axis. The drive scroll and the driven scroll constitute the scroll compression section. The scroll chamber is provided with an oil reservoir for storing lubricating oil. It is provided with a lubricating oil supply passage that communicates with the oil reservoir and supplies lubricating oil to the scroll compression section or the bearing, A double-rotating scroll compressor characterized in that a lubricating oil cooling section is provided in the middle of the lubricating oil supply passage, which cools the lubricating oil in the lubricating oil supply passage with the liquid refrigerant in the storage chamber.

[0137] (Note 2) The drive scroll comprises a drive end plate, a drive spiral body integral with the drive end plate and projecting spirally toward the driven scroll, and a cover body connected to the drive end plate while sandwiching the driven scroll between them. The driven scroll has a driven end plate and a driven spiral body that is integral with the driven end plate and projects spirally toward the drive end plate. The double-rotating scroll compressor described in Appendix 1, wherein lubricating oil is supplied from the lubricating oil supply passage to the sliding portion between the driven end plate and the cover body.

[0138] (Note 3) Lubricating oil is supplied to the bearing from the lubricating oil supply passage. The lubrication oil supply passage penetrates the support portion in the double-rotation scroll compressor as described in Appendix 1 or 2.

[0139] (Note 4) The bush through which the driven shaft portion is inserted is provided. A bushing bearing is provided between the driven scroll and the bushing. Lubricating oil is supplied to the bush bearing from the lubricating oil supply passage. The lubrication oil supply passage penetrates the driven shaft portion or the bush in the double-rotation scroll compressor as described in Appendix 2.

[0140] (Note 5) The aforementioned lubrication oil supply passage penetrates the cover body of the double-rotating scroll compressor as described in Appendix 2.

[0141] (Note 6) The lubricating oil cooling section is formed by a groove recessed in the wall surface of the compartment wall on the storage chamber side, and a plate-shaped cover 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. A double-rotation scroll compressor according to any one of the appendices 1 to 5, wherein the passage partitioned by the inner surface of the groove and the cover constitutes part of the lubricating oil supply passage.

[0142] (Note 7) The lubricating oil cooling section is formed by pipes arranged in the storage chamber. A double-rotation scroll compressor according to any one of the appendices 1 to 5, wherein the passage within the pipe constitutes part of the lubricating oil supply passage. [Industrial applicability]

[0143] This invention can be used in vehicle air conditioning systems and the like. [Explanation of Symbols]

[0144] 10…Electric motor (drive mechanism) 20…Following mechanism 30…Drive Scroll 31…Drive end plate 33…Driving vortex 35... Cover body 40...Driven Scroll 41…Driven end plate 43... Driven vortex 55... Compression chamber 60… Housing 61A...Inhalation chamber (scroll chamber) 63...First bottom wall (compartment wall) 632…Rear surface (wall surface) 63F…Groove 63H…Lubricating oil supply passage 64…Second axis support (support part) 70A...Storage Room 72…Second bearing (bearing, sliding part) 73…Third bearing (bearing for bushing, sliding part) 77... Lid 78…Lubricating oil cooling section 80...Scroll compression section 81, 82... Sliding parts 83...Oil storage section 84... Pipe 90...Third axis support (bush) 91...Eccentric shaft (driven shaft part) R1...Drive shaft center R2…driven shaft center

Claims

1. The system comprises a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism. The housing has a scroll chamber in which the drive scroll and the driven scroll are housed, a storage chamber for separating the refrigerant drawn in from the outside into gas and liquid form and storing the liquid refrigerant inside, and a partition wall separating the storage chamber and the scroll chamber. The drive scroll is rotationally driven around the drive axis by the drive mechanism, The driven scroll is rotated and driven by the driven scroll and the driven mechanism around its driven axis, while being eccentric with respect to the driven scroll. The partition wall is provided with a support portion that protrudes into the scroll chamber with respect to the drive axis, The drive scroll is supported so as to be rotatable around the drive axis by a bearing disposed between the drive scroll and the support portion. The driven scroll is supported so as to be rotatable around the driven axis by the driven scroll and a driven shaft portion that extends in the direction of the driven axis while being eccentric with respect to the drive axis. The drive scroll and the driven scroll constitute the scroll compression section. The scroll chamber is provided with an oil reservoir for storing lubricating oil. It is provided with a lubricating oil supply passage that communicates with the oil reservoir and supplies lubricating oil to the scroll compression section or the bearing, A lubricating oil cooling section is provided in the middle of the lubricating oil supply passage, which cools the lubricating oil in the lubricating oil supply passage with the liquid coolant in the storage chamber. The drive scroll comprises a drive end plate, a drive spiral body integral with the drive end plate and projecting spirally toward the driven scroll, and a cover body connected to the drive end plate while sandwiching the driven scroll between them. The driven scroll has a driven end plate and a driven spiral body that is integral with the driven end plate and projects spirally toward the drive end plate. A double-rotating scroll compressor characterized in that lubricating oil is supplied from the lubricating oil supply passage to the sliding portion between the driven end plate and the cover body.

2. Lubricating oil is supplied to the bearing from the lubricating oil supply passage. The double-rotating scroll compressor according to claim 1, wherein the lubricating oil supply passage penetrates the support portion.

3. The bush through which the driven shaft portion is inserted is provided. A bushing bearing is provided between the driven scroll and the bushing. Lubricating oil is supplied to the bush bearing from the lubricating oil supply passage. The double-rotating scroll compressor according to claim 1, wherein the lubricating oil supply passage penetrates the driven shaft portion or the bushing.

4. The double-rotating scroll compressor according to claim 1, wherein the lubricating oil supply passage penetrates the cover body.

5. The lubricating oil cooling section is formed by a groove recessed in the wall surface of the compartment wall on the storage chamber side, and a plate-shaped cover 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. The double-rotating scroll compressor according to any one of claims 1 to 4, wherein the passage partitioned by the inner surface of the groove and the cover constitutes a part of the lubricating oil supply passage.

6. The lubricating oil cooling section is formed by pipes arranged in the storage chamber. The double-rotation scroll compressor according to any one of claims 1 to 4, wherein the passage in the pipe constitutes part of the lubricating oil supply passage.

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