Co-rotating scroll compressor

Abstract

This co-rotating scroll compressor is provided with a driven member (16) between a protruding body (64) and a driven scroll (40) in a drive axis (O1) direction. A drive scroll (30) is rotatably supported by the protruding body (64) about the drive axis (O1). The driven scroll (40) is rotatably supported by the protruding body (64) via the driven member (16) about a driven axis (O2). A driven shaft support part (13) is provided between the driven scroll (40) and the driven member (16). The driven member (16) has a bush (53) supported by the driven shaft support part (13). The bush (53) extends in the drive axis (O1) direction further toward the protruding body (64) than the driven shaft support part (13).

Description

Dual-rotation scroll compressor

[0001] The present invention relates to a dual-rotation scroll compressor.

[0002] Patent Document 1 discloses a conventional dual-rotation scroll compressor (hereinafter simply referred to as compressor where appropriate). This compressor includes a housing, a driving scroll, a driven scroll, a driving mechanism, and a driven mechanism. The housing has a scroll chamber that accommodates the driving mechanism, the driving scroll, and the driven scroll. Fluid is sucked into the scroll chamber from the outside of the housing. In this document, the fluid is specifically refrigerant gas. Further, a protruding body is integrally formed on the housing. The protruding body extends toward the driving scroll and the driven scroll in the scroll chamber along the direction of the driving shaft center.

[0003] The driving mechanism includes a stator and a rotor. The driving scroll is fixed to the rotor and can be rotationally driven around the driving shaft center by the rotation of the rotor. The driven scroll is eccentric with respect to the driving scroll and can be rotatably driven around the driven shaft center by the driving scroll and the driven mechanism. Further, a driven member is provided between the protruding body and the driven scroll in the direction of the driving shaft center. The driven member includes a bush and a driven pin. The bush is held by the driven scroll. The driven pin is inserted through the bush and extends toward the protruding body in the direction of the driving shaft center.

[0004] In this compressor, the driving scroll is rotatably supported by the protruding body around the driving shaft center. Further, in the driven member, the driven pin is inserted through and fixed to the protruding body. Accordingly, the driven scroll is rotatably supported by the protruding body via the driven member around the driven shaft center. And in this compressor, the bush and the driven scroll face the protruding body from one side in the direction of the driving shaft center.

[0005] In this compressor, the driving scroll and the driven scroll rotate, respectively, creating a compression chamber between them that compresses the fluid. In this compressor, the fluid in the scroll chamber is drawn into the compression chamber and compressed there. The compressed fluid is then discharged to the outside of the housing, i.e., outside the compressor.

[0006] Japanese Patent Publication No. 2024-92284

[0007] In the conventional compressor described above, the compressive load associated with the compression of the fluid acts on the driven scroll, causing the driven scroll to rotate in an inclined position relative to the protruding body during operation.

[0008] Furthermore, a driven shaft support may be provided between the driven scroll and the driven member, or more specifically, between the driven scroll and the bush in the radial direction of the driven scroll, to rotatably support the bush. As a result, when the driven scroll is tilted relative to the projection as described above, there is a risk that the driven shaft support will come into contact with the projection. Therefore, if the driven scroll rotates in this state, the driven shaft support and the projection will slide against each other, raising concerns about reduced durability in this compressor due to wear and damage to the driven shaft support and projection. Moreover, the contact between the driven shaft support and the projection inevitably increases power loss during the rotation of the driven scroll, raising concerns about reduced operating efficiency in this compressor.

[0009] This 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 with excellent durability and operating efficiency.

[0010] The first double-rotation scroll compressor of the present invention comprises a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the drive scroll, the driven scroll, and the drive mechanism are housed, the drive mechanism has a stator and a rotor that is rotationally driven by the stator, the drive scroll is rotationally driven around a drive axis by the drive mechanism, the driven scroll is rotationally driven around a driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, and the drive scroll and the driven scroll form a compression chamber for compressing a fluid by the rotational drive and the rotational drive, wherein a projection is provided in the scroll chamber extending toward the drive scroll and the driven scroll in the direction of the drive axis, a driven member is provided between the projection and the driven scroll in the direction of the drive axis, and the drive scroll is rotatably supported by the projection around the drive axis. The driven scroll is rotatably supported on the projection via the driven member so as to be about the driven axis, a driven axis support is provided between the driven scroll and the driven member to rotatably support the driven member, the driven member has a bush supported by the driven axis support, and the bush extends in the direction of the drive axis toward the projection from the driven axis support.

[0011] In the first double-rotating scroll compressor of the present invention, the bush of the driven member extends in the direction of the drive axis toward the projection rather than from the driven shaft support. Therefore, the bush is closer to the projection than from the driven shaft support in the direction of the drive axis. As a result, in this compressor, when the driven scroll is tilted relative to the projection during operation, the bush can contact the projection before the driven shaft support. In this way, this compressor can prevent the driven shaft support from contacting the projection, and can prevent wear and damage to the driven shaft support and projection caused by contact between the driven shaft support and the projection. Furthermore, this compressor can also prevent power loss of the driven scroll during operation due to the driven shaft support contacting the projection.

[0012] Therefore, the first double-rotation scroll compressor of the present invention has excellent durability and operating efficiency.

[0013] Preferably, the bush has a bush body supported by a driven shaft support, and an extension that has a smaller diameter than the bush body, is integrally formed with the bush body, and extends in the direction of the drive axis toward the protruding body from the bush body.

[0014] In this case, the extension abuts against the projection, effectively preventing the driven shaft support from abutting against the projection. Furthermore, since the extension has a smaller diameter than the bush body, the contact area between the bush and the projection can be effectively reduced compared to the case where the bush body abuts against the projection. Additionally, by adjusting the position where the extension is formed on the bush body, the position where the extension abuts against the projection can be effectively adjusted.

[0015] The driven scroll, driven shaft support, and bushing may be located on one side of the projection in the direction of the drive axis. Preferably, the driven scroll, driven shaft support, and bushing move toward the projection to the other side in the direction of the drive axis due to a thrust load acting from one side in the direction of the drive axis.

[0016] As a result, in this compressor, the bush can contact the projection before the driven shaft support, not only when the driven scroll is tilted relative to the projection during operation, but also when the driven scroll, driven shaft support, and bush move toward the projection to the other side in the direction of the drive axis due to the thrust load. In this way, this compressor can effectively prevent the driven shaft support from contacting the projection.

[0017] A second double-rotation scroll compressor of the present invention comprises a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the drive scroll, the driven scroll, and the drive mechanism are housed, the drive mechanism has a stator and a rotor that is rotationally driven by the stator, the drive scroll is rotationally driven around a drive axis by the drive mechanism, the driven scroll is rotationally driven around a driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, and the drive scroll and the driven scroll form a compression chamber for compressing a fluid by the rotational drive and the rotational drive, wherein a projection is provided in the scroll chamber extending toward the drive scroll and the driven scroll in the direction of the drive axis, a driven member is provided between the projection and the driven scroll in the direction of the drive axis, and the drive scroll is rotatably supported by the projection around the drive axis. The driven scroll is rotatably supported on the projection via the driven member so as to be about the driven axis, a rolling bearing is provided between the driven scroll and the driven member to rotatably support the driven member, the driven member has a bush supported by the rolling bearing, the driven scroll, the rolling bearing and the bush are located on one side of the projection in the direction of the drive axis, the driven scroll, the rolling bearing and the bush are movable toward the projection to the other side in the direction of the drive axis by a thrust load acting from one side in the direction of the drive axis, the rolling bearing has an outer ring facing the driven scroll in the radial direction of the housing and an inner ring located inside the outer ring in the radial direction and facing the bush in the radial direction, and the bush extends toward the projection in the direction of the drive axis from the inner ring.

[0018] In the second double-rotating scroll compressor of the present invention, the bush of the driven member extends in the direction of the drive axis toward the projection body, beyond the inner ring of the rolling bearing. Therefore, the bush is closer to the projection body than the inner ring of the rolling bearing, and consequently the rolling bearing, in the direction of the drive axis. As a result, in this compressor, when the driven scroll is tilted relative to the projection body during operation, or when the driven scroll, rolling bearing, and bush move toward the projection body to the other side in the direction of the drive axis due to a thrust load acting from one side in the direction of the drive axis, the bush can contact the projection body before the rolling bearing. This prevents the rolling bearing from contacting the projection body, thus preventing wear and damage to the rolling bearing and projection body caused by contact between them. Furthermore, this compressor can also prevent power loss of the driven scroll during operation due to the rolling bearing contacting the projection body.

[0019] Therefore, the second double-rotation scroll compressor of the present invention is excellent in terms of durability and operating efficiency.

[0020] The outer ring can be clearance-fitted to the driven scroll, and the bush is preferably tight-fitted to the inner ring. In this case, although a thrust load acting from one side in the direction of the drive axis may cause the rolling bearing and the bush to move together toward the projection to the other side in the direction of the drive axis, the bush can contact the projection before the rolling bearing. This effectively prevents the rolling bearing from contacting the projection in this compressor.

[0021] In this case, it is preferable that the bush has a bush body that is tightly fitted onto the inner ring, and an extension that has a smaller diameter than the bush body, is integrally formed with the bush body, and extends in the direction of the drive axis toward the protruding body from the bush body.

[0022] In this case, the extension abuts against the projection, effectively preventing the rolling bearing from abutting against the projection. Furthermore, since the extension has a smaller diameter than the bush body, the contact area between the bush and the projection can be effectively reduced in this compressor compared to the case where the bush body abuts against the projection. Additionally, by adjusting the position where the extension is formed on the bush body, the position where the extension abuts against the projection can be effectively adjusted.

[0023] Furthermore, the projection may have an end face facing the extension in the direction of the drive axis. The end face may be formed to have a larger diameter than the extension. Preferably, the extension is always located radially inward of the housing than the end face.

[0024] In this case, the entire extension can be brought into contact with the end face of the protruding body, thus effectively suppressing uneven wear of the protruding body and the extension compared to the case where only a part of the extension contacts the end face of the protruding body.

[0025] The outer ring can be clearance-fitted to the driven scroll. The bush can be clearance-fitted to the inner ring while being spaced apart from the driven scroll and the protruding body in the direction of the drive axis. The driven scroll may also be provided with a first restricting portion that restricts the amount of movement of the rolling bearing to the other side in the direction of the drive axis, and a second restricting portion that restricts the amount of movement of the rolling bearing to one side in the direction of the drive axis. The gap in the direction of the drive axis between the first restricting portion and the rolling bearing is set as the first gap, the gap in the direction of the drive axis between the second restricting portion and the rolling bearing is set as the second gap, the gap in the direction of the drive axis between the driven scroll and the bush is set as the third gap, and the gap in the direction of the drive axis between the bush and the protruding body is set as the fourth gap. It is also preferable that the sum of the third gap and the fourth gap is smaller than the sum of the first gap and the second gap.

[0026] In this case, a thrust load acting from one side in the direction of the drive axis can cause the rolling bearing and the bushing to move toward the projection to the other side in the direction of the drive axis. At this time, since the sum of the third and fourth gaps is smaller than the sum of the first and second gaps, the bushing that has moved toward the other side in the direction of the drive axis can come into contact with the projection before the rolling bearing. As a result, this compressor can effectively prevent the rolling bearing from coming into contact with the projection.

[0027] The first and second double-rotation scroll compressors of the present invention offer excellent durability and operating efficiency.

[0028] Figure 1 is a cross-sectional view of the compressor of Example 1. Figure 2 is an enlarged cross-sectional view of the main parts of the compressor of Example 1, showing the protruding body and bushings. Figure 3 is an enlarged cross-sectional view of the main parts of the compressor of Example 1, showing the state in which the protruding body and bushings are in contact. Figure 4 is an enlarged cross-sectional view of the main parts of the compressor of Example 1, similar to Figure 3, showing the state in which the driven scroll is inclined with respect to the protruding body. Figure 5 is an enlarged cross-sectional view of the main parts of the compressor of Example 2, similar to Figure 2, showing the protruding body and bushings. Figure 6 is an enlarged cross-sectional view of the main parts of the compressor of Example 2, showing the state in which the protruding body and bushings are in contact. Figure 7 is an enlarged cross-sectional view of the main parts of the compressor of Example 3, showing the protruding body and bushings. Figure 8 is an enlarged cross-sectional view of the main parts of the compressor of Example 3, similar to Figure 7, showing the state in which the protruding body and bushings are in contact.

[0029] The following describes three embodiments of the present invention with reference to the drawings. The compressors of embodiments 1 to 3 are mounted on a vehicle (not shown) and constitute the vehicle's air conditioning system.

[0030] As shown in Figure 1, the compressor of this embodiment comprises a housing 6, an electric motor 10, a drive scroll 30, a driven scroll 40, and a driven mechanism 20. The electric motor 10 is an example of a "drive mechanism" in the present invention.

[0031] In this embodiment, the front-rear and up-down directions of the compressor are defined by the solid arrows shown in Figure 1. The front-rear and up-down directions are orthogonal to each other. Then, in Figures 2 and onward, the front-rear and up-down directions of the compressor are defined in correspondence with Figure 1. Note that these front-rear and up-down directions are examples for the sake of explanation, and the compressor can change its own orientation as appropriate depending on the vehicle on which it is mounted.

[0032] As shown in Figure 1, the housing 6 is composed of a housing body 60, a first housing cover 61, and a second housing cover 62. These housing body 60, first housing cover 61, and second housing cover 62 are made of aluminum alloy. However, the housing body 60, first housing cover 61, and second housing cover 62 may also be made of steel or the like.

[0033] The housing body 60 is cylindrical with the drive shaft O1 as its center, and has openings at its front and rear ends. The drive shaft O1 is parallel to the front-rear direction. As a result, the front side of the compressor corresponds to "one side in the direction of the drive shaft" in this invention, and the rear side of the compressor corresponds to "the other side in the direction of the drive shaft" in this invention.

[0034] Furthermore, an intake port 68 is formed in the housing body 60. The intake port 68 extends radially from the housing body 60. The intake port 68 is connected to an evaporator (not shown) through piping (not shown).

[0035] The first housing cover 61 is located at the rear end of the housing body 60. The first housing cover 61 has a cover body portion 61a and a holding portion 61b. The cover body portion 61a is substantially disc-shaped with the drive shaft center O1 as its center and extends radially from the housing 6. The cover body portion 61a has a front surface 610a facing forward and a rear surface 610b located on the opposite side of the front surface 610a and facing rear.

[0036] The retaining portion 61b is integrally formed with the cover body portion 61a. The retaining portion 61b extends cylindrically forward from the front surface 610a of the cover body portion 61a in the direction of the drive axis O1. The retaining portion 61b consists of a base end portion 615 and a tip portion 616.

[0037] As shown in Figure 2, the base portion 615 constitutes the rear end portion of the holding portion 61b and is connected to the cover body portion 61a. The tip portion 616 is connected to the base portion 615 and extends forward from the base portion 615. The tip portion 616 is formed in a cylindrical shape with a smaller diameter than the base portion 615.

[0038] The retaining portion 61b has three retaining grooves 611 to 613 formed therein. More specifically, each retaining groove 611 to 613 is recessed in the outer circumferential surface 616a of the tip portion 616, forming an annular shape that encircles the outer circumferential surface 616a. The retaining grooves 611 to 613 are arranged in the order of retaining groove 611, retaining groove 612, and retaining groove 613, from the rear side to the front side of the tip portion 616. Furthermore, these retaining grooves 611 to 613 are arranged at equal intervals in the direction of the drive axis O1.

[0039] Furthermore, the other elastic body 70 is attached to the tip portion 616. The other elastic body 70 is composed of a first elastic body 70a, a second elastic body 70b, and a third elastic body 70c. These first to third elastic bodies 70a to 70c are made of an elastically deformable resin such as synthetic rubber. These first to third elastic bodies 70a to 70c are separate entities. These first to third elastic bodies 70a to 70c are formed in an annular shape with the same outer diameter. Note that the first to third elastic bodies 70a to 70c, that is, the other elastic body 70, may be made of a metal or the like with lower rigidity than the first housing cover 61.

[0040] The first elastic body 70a is housed in the retaining groove 611. The second elastic body 70b is housed in the retaining groove 612. The third elastic body 70c is housed in the retaining groove 613. In this way, the first to third elastic bodies 70a to 70c, that is, the other elastic body 70, are attached to the tip portion 616.

[0041] A projecting body 64 is attached to the first housing cover 61. The projecting body 64 is made of steel. The projecting body 64 includes a first diameter portion 64a and a second diameter portion 64b. The first diameter portion 64a constitutes a front portion of the projecting body 64. A pin hole 4 is formed in the first diameter portion 64a. The pin hole 4 extends inside the first diameter portion 64a in the direction of the drive axis O1, and is open to a front end face 641 of the first diameter portion 64a. The front end face 641 is an example of the "end face" in the present invention.

[0042] The second diameter portion 64b is integrated with the first diameter portion 64a at a front end thereof. Accordingly, the second diameter portion 64b constitutes a rear portion of the projecting body 64. The second diameter portion 64b has a larger diameter than the first diameter portion 64a, and is formed into a bottomed cylindrical shape that is open at the rear side. Here, an inner diameter of the second diameter portion 64b is larger than an outer diameter of a distal end portion 616 of the holding portion 61b, and is formed to be slightly smaller than the outer diameter of the other-side elastic body 70, that is, the outer diameter of the first to third elastic bodies 70a to 70c.

[0043] In the projecting body 64, the distal end portion 616 and the other-side elastic body 70 are accommodated inside the second diameter portion 64b. Accordingly, the distal end portion 616 is arranged inside the second diameter portion 64b. Further, as described above, since the inner diameter of the second diameter portion 64b is smaller than the outer diameter of the other-side elastic body 70, the other-side elastic body 70, that is, the first to third elastic bodies 70a to 70c are each disposed between the distal end portion 616 and the second diameter portion 64b while being elastically deformed in the radial direction of the housing 6.

[0044] In this way, the projecting body 64 is attached to the first housing cover 61 via the other-side elastic body 70. The holding portion 61b holds the projecting body 64 from the inner side via the other-side elastic body 70. Accordingly, the first housing cover 61 supports the projecting body 64.

[0045] Further, in the protrusion 64, a first radial ball bearing 51 is provided on the first diameter portion 64a. The first radial ball bearing 51 has a first inner ring 51a and a first outer ring 51b. The first radial ball bearing 51 is provided on the first diameter portion 64a by inserting the first inner ring 51a through the first diameter portion 64a. More specifically, the first radial ball bearing 51 is provided on the first diameter portion 64a by clearance-fitting the first inner ring 51a to the outer circumferential surface of the first diameter portion 64a. In FIG. 2 and the like, for ease of explanation, the gap between the first inner ring 51a of the first radial ball bearing 51 and the first diameter portion 64a in the radial direction of the housing 6 is exaggerated in the illustration.

[0046] Furthermore, a first circlip 5 is attached to the first diameter portion 64a. The first circlip 5 is attached to a position rearward of the first radial ball bearing 51 in the first diameter portion 64a. The first radial ball bearing 51 and the first circlip 5 are spaced apart from each other in the direction of the drive axis O1. Accordingly, the first radial ball bearing 51 is allowed to relatively move in the direction of the drive axis O1 with respect to the first diameter portion 64a until it abuts against the first circlip 5.

[0047] As shown in FIG. 1, the second housing cover 62 is disposed forward of the housing main body 60. The second housing cover 62 is formed in a substantially disc shape centered on the drive axis O1, and extends in the radial direction of the housing 6. The second housing cover 62 has a front face 62a facing forward, and a rear face 62b located on the opposite side of the front face 62a and facing rearward.

[0048] Further, the second housing cover 62 is formed with a support portion 66 and a discharge communication port 69. The support portion 66 is integrally formed substantially at the center of the rear face 62b, and protrudes rearward from the rear face 62b. The support portion 66 is formed in a cylindrical shape centered on the drive axis O1, and a second radial ball bearing 52, a one-side elastic body 67, and a shaft sealing member 63 are provided inside the support portion 66. The second radial ball bearing 52 has a second inner ring 52a and a second outer ring 52b.

[0049] The one-sided elastic body 67 is formed of an elastically deformable resin such as synthetic rubber and has a cylindrical shape. The one-sided elastic body 67 is positioned between the support portion 66 and the second radial ball bearing 52, surrounding the second outer ring 52b of the second radial ball bearing 52 from the outside, and holding the second radial ball bearing 52 within the support portion 66. Although detailed illustrations are omitted, the one-sided elastic body 67 surrounds the second radial ball bearing 52 from the outside by being fitted with the second outer ring 52b. The one-sided elastic body 67 may be formed of a metal or the like with lower rigidity than the second housing cover 62. The thickness of the one-sided elastic body 67 can be designed as appropriate. Furthermore, a sliding bearing may be provided inside the support portion 66 instead of the second radial ball bearing 52.

[0050] The shaft seal member 63 is positioned inside the support portion 66, forward of the second radial ball bearing 52 and the one-sided elastic body 67. The shaft seal member 63 is formed in an annular shape.

[0051] The discharge port 69 penetrates the second housing cover 62 in the direction of the drive shaft center O1 and communicates with the inside of the support portion 66. The discharge port 69 is also connected to a condenser (not shown) through piping (not shown).

[0052] In the housing 6, the front surface 610a of the first housing cover 61 is in contact with the rear end of the housing body 60, and the rear surface 62b of the second housing cover 62 is in contact with the front end of the housing body 60. The housing body 60, the first housing cover 61, and the second housing cover 62 are fixed together in the direction of the drive axis O1 by a plurality of bolts (not shown).

[0053] Thus, in the housing 6, the housing body 60 is sandwiched in the front-rear direction by the first housing cover 61 and the second housing cover 62, and the front and rear ends of the housing body 60 are closed by the first housing cover 61 and the second housing cover 62, respectively. As a result, a scroll chamber 65 is formed inside the housing body 60 in the housing 6. The scroll chamber 65 is in communication with the intake port 68. Therefore, refrigerant is drawn into the scroll chamber 65 from outside the housing 6 through the intake port 68. The refrigerant is an example of a "fluid" in this invention.

[0054] Furthermore, as described above, the projection 64 is attached to the first housing cover 61, so the projection 64 is positioned within the scroll chamber 65. Within the scroll chamber 65, the projection 64 protrudes forward from the first housing cover 61 toward the drive scroll 30 and the driven scroll 40.

[0055] The electric motor 10 is housed within the scroll chamber 65. Thus, the scroll chamber 65 also serves as the motor chamber housing the electric motor 10.

[0056] As shown in Figure 2, the electric motor 10 is composed of a stator 17 and a rotor 11. The stator 17 has a stator core 17a and windings 17b. The stator core 17a is formed in a cylindrical shape with the drive axis O1 as the center. The windings 17b are wound around the stator core 17a. As a result, the windings 17b form a first coil end 171 and a second coil end 172.

[0057] The first coil end 171 protrudes cylindrically forward from the stator core 17a in the direction of the drive axis O1. The second coil end 172 is located on the opposite side of the stator core 17a from the first coil end 171. The second coil end 172 protrudes cylindrically backward from the stator core 17a in the direction of the drive axis O1.

[0058] In the stator 17, the stator core 17a is fitted onto the outer circumferential surface of the second diameter portion 64b. In other words, the stator core 17a is tightly fitted to the outer circumferential surface of the second diameter portion 64b. In this way, the stator core 17a is fixed to the outer circumferential surface of the second diameter portion 64b, and consequently to the outer circumferential surface of the protruding body 64. Although not shown in the figures, multiple slits extending in the direction of the drive axis O1 are formed on the inner circumferential surface of the stator core 17a. As a result, the slits form a gap between the stator core 17a and the outer circumferential surface of the second diameter portion 64b while the stator core 17a is fixed to the second diameter portion 64b.

[0059] The rotor 11 is cylindrical around the drive axis O1. 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. The rotor 11 is also formed to be larger in diameter than the stator core 17a. As a result, the rotor 11 covers the stator core 17a from the outside within the scroll chamber 65 and is rotationally driven by the stator 17. Furthermore, the rotor 11 has multiple first bolt holes 11a. Each first bolt hole 11a penetrates the rotor 11 in the direction of the drive axis O1.

[0060] As shown in Figure 1, the drive scroll 30 is housed in the scroll chamber 65. The drive scroll 30 is made of aluminum alloy. The drive scroll 30 includes a drive end plate 31, a drive spiral body 33, a drive peripheral wall 35, a cover body 37, and a case 39.

[0061] The drive end plate 31 extends in a substantially disc shape perpendicular to the drive axis O1 and the driven axis O2. The driven axis O2 extends parallel to the drive axis O1 while being eccentric with respect to the drive axis O1. In other words, the driven axis O2 is also parallel in the front-rear direction. The drive end plate 31 has a first front surface 311 facing forward and a first rear surface 312 located on the opposite side of the first front surface 311 and facing rear.

[0062] Furthermore, a discharge port 32 is formed in the drive end plate 31. The discharge port 32 penetrates the drive end plate 31 in the direction of the drive axis O1. In addition, a discharge reed valve 57 and a retainer 58 are fixed to the first front surface 311 of the drive end plate 31 by fixing bolts 59. As a result, the discharge reed valve 57 can open and close the discharge port 32. The retainer 58 can adjust the opening degree of the discharge reed valve 57.

[0063] The drive spiral body 33 is integral with the drive end plate 31 and protrudes from the first rear surface 312 toward the rear, i.e., toward the driven scroll 40, parallel to the drive axis O1 and the driven axis O2. Although detailed illustration is omitted, the drive spiral body 33 has the center of the drive end plate 31 as its spiral center and protrudes outward from the spiral center in a spiral shape.

[0064] The drive circumferential wall 35 is formed in a cylindrical shape, extending parallel to the drive axis O1 and the driven axis O2, with the drive axis O1 as its center. The front end of the drive circumferential wall 35 is integral with the outer peripheral edge of the drive end plate 31. As a result, the drive circumferential wall 35 surrounds the drive spiral body 33 from the outside and protrudes cylindrically toward the rear from the first rear surface 312. Although not shown in the figures, the outer peripheral end of the spiral in the drive spiral body 33 is connected to the inner peripheral surface of the drive circumferential wall 35.

[0065] As shown in Figure 2, the cover body 37 has a wall portion 37a, an inner cylindrical portion 37b, and an outer cylindrical portion 37c. The wall portion 37a extends in a substantially plate-like shape in the radial direction of the housing 6. The wall portion 37a has a second front surface 371 facing forward and a second rear surface 372 located on the opposite side of the second front surface 371 and facing rear.

[0066] A recess 373 and an intake port 374 are formed in the wall portion 37a. The recess 373 is located approximately in the center of the second front surface 371 and is recessed from the second front surface 371 toward the rear.

[0067] The intake port 374 is located radially outward from the recess 373 of the housing 6. The intake port 374 penetrates the wall portion 37a in the front-rear direction, with its front end opening to the second front surface 371 and its rear end opening to the second rear surface 372. Multiple intake ports 374 may be formed in the wall portion 37a.

[0068] Furthermore, in the wall portion 37a, multiple rings 22 are attached between the recess 373 and the intake port 374. Although detailed illustrations are omitted, each ring 22 is arranged at equal intervals in the circumferential direction of the recess 373 when facing forward, and surrounds the recess 373 from the outside. In this embodiment, there are six rings 22. Figures 1 and 2, etc., illustrate one of the six rings 22.

[0069] As shown in Figure 2, the inner cylindrical portion 37b is located inside the stator 17 in the radial direction of the housing 6, and extends cylindrically backward from the second rear surface 372 of the wall portion 37a in the direction of the drive axis O1. The inner cylindrical portion 37b is in communication with the recess 373 in the direction of the drive axis O1. The inner diameter of the inner cylindrical portion 37b is larger than the outer diameter of the first diameter portion 64a of the protruding body 64, and slightly smaller than the outer diameter of the first radial ball bearing 51. The outer diameter of the inner cylindrical portion 37b is smaller than the outer diameter of the second diameter portion 64b.

[0070] The outer cylindrical portion 37c is connected to the wall portion 37a and extends cylindrically backward from the wall portion 37a in the direction of the drive axis O1. The outer diameter of the outer cylindrical portion 37c is formed to be approximately the same as the outer diameter of the wall portion 37a, the outer diameter of the drive peripheral wall 35, and the outer diameter of the rotor 11.

[0071] Furthermore, the inner diameter of the outer cylindrical portion 37c is formed to be larger than the outer diameter of the inner cylindrical portion 37b. As a result, in the cover body 37, the inner cylindrical portion 37b is positioned on the inner circumference side of the outer cylindrical portion 37c, separated from the outer cylindrical portion 37c in the radial direction of the housing 6. In this way, the cover body 37 has a housing portion 38 formed by the wall portion 37a, the inner cylindrical portion 37b, and the outer cylindrical portion 37c. The housing portion 38 has a bottomed annular shape that opens at the rear.

[0072] The intake port 374 formed in the wall portion 37a is located radially outward from the inner cylindrical portion 37b and inward from the outer cylindrical portion 37c of the housing 6. Thus, the intake port 374 communicates with the housing portion 38 between the inner cylindrical portion 37b and the outer cylindrical portion 37c.

[0073] Furthermore, multiple second bolt holes 376 are formed in the outer cylindrical portion 37c and the wall portion 37a. Each second bolt hole 376 penetrates the outer cylindrical portion 37c and the wall portion 37a in the direction of the drive axis O1. Although not shown in the figures, the number of second bolt holes 376 is equal to the number of first bolt holes 11a formed in the rotor 11. In Figures 1 and 2, etc., one of the multiple first bolt holes 11a and one of the second bolt holes 376 are shown.

[0074] As shown in Figure 1, the cover body 37 has its second front surface 371 of the wall portion 37a in contact with the rear end of the drive peripheral wall 35. The cover body 37 also has the rotor 11 in contact with the rear end of the outer cylindrical portion 37c. In this state, the first bolts 34a are inserted from the rotor 11 side through the first bolt holes 11a and the second bolt holes 376 in that order, and the first bolts 34a are screwed into the drive peripheral wall 35. In this way, the cover body 37 is fixed to the drive peripheral wall 35 and the rotor 11, while being sandwiched in the front-rear direction between the drive peripheral wall 35 and the rotor 11. As a result, the drive scroll 30 is integrated with the rotor 11.

[0075] Case 39 is a bottomed cylindrical member having an outer peripheral wall 39a and a front wall 39b. The outer peripheral wall 39a is cylindrical with the drive axis O1 as its center. Here, the outer diameter of the outer peripheral wall 39a is formed to be approximately the same as the outer diameter of the drive peripheral wall 35.

[0076] The front wall 39b is located at the front end of the case 39. The front wall 39b extends in a substantially disc shape perpendicular to the drive axis O1 and the driven axis O2. The outer edge of the front wall 39b is connected to the front end of the outer wall 39a. A boss 39c is also formed on the front wall 39b.

[0077] The boss 39c is integrally formed in the center of the front wall 39b and protrudes forward from the front wall 39b in the direction of the drive axis O1. The outer diameter of the boss 39c is formed to be slightly larger than the inner diameter of the second inner ring 52a, that is, the inner diameter of the second radial ball bearing 52. The outer diameter of the boss 39c is also formed to be approximately the same as the inner diameter of the shaft sealing member 63. A discharge passage 390 is formed in the boss 39c. The discharge passage 390 penetrates the boss 39c in the direction of the drive axis O1. The discharge passage 390 opens to the front end face 391 of the boss 39c.

[0078] Furthermore, third bolt holes 39d are formed in the outer periphery wall 39a and the front wall 39b. The third bolt holes 39d penetrate the outer periphery wall 39a and the front wall 39b in the direction of the drive axis O1. Although not shown in the figure, multiple third bolt holes 39d are formed in the outer periphery wall 39a and the front wall 39b. Figure 1 shows one of these multiple third bolt holes 39d.

[0079] The case 39 has its rear end surface of the outer peripheral wall 39a in contact with the front end of the drive peripheral wall 35. In this state, the second bolts 34b are inserted through each of the third bolt holes 39d, and the second bolts 34b are screwed into the drive peripheral wall 35. In this way, the case 39 is fixed to the drive peripheral wall 35 in the drive scroll 30.

[0080] As the case 39 is fixed to the drive peripheral wall 35, a discharge chamber 14 is formed inside the case 39, that is, inside the outer peripheral wall 39a, between the front wall 39b of the case 39 and the drive end plate 31. The discharge chamber 14 is in communication with the discharge port 32 and also with the discharge passage 390.

[0081] Furthermore, because the case 39 is fixed to the drive peripheral wall 35 in this manner, in the drive scroll 30, the case 39 and the cover body 37 are positioned separated in the front-rear direction, with the drive end plate 31, the drive spiral body 33, and the drive peripheral wall 35 in between. Also, the boss 39c formed on the front wall 39b of the case 39 protrudes forward from the front wall 39b in the direction of the drive axis O1. In other words, the boss 39c extends toward the opposite side of the cover body 37 in the direction of the drive axis O1.

[0082] The driven scroll 40 is also made of aluminum alloy. The driven scroll 40 has a driven end plate 41 and a driven spiral body 43.

[0083] The driven end plate 41 extends in a substantially disc shape perpendicular to the drive axis O1 and the driven axis O2. The driven end plate 41 has a third front surface 411 facing forward and a third rear surface 412 located on the opposite side of the third front surface 411 and facing rear.

[0084] As shown in Figures 2 to 4, a receiving recess 15 is formed in the driven end plate 41. The receiving recess 15 is located in the center of the driven end plate 41. The receiving recess 15 is recessed in a cylindrical shape from the third rear surface 412 of the driven end plate 41 toward the front, with the driven axis O2 as the center. As a result, the receiving recess 15 opens toward the rear of the driven end plate 41, and consequently toward the first diameter portion 64a of the protruding body 64.

[0085] A driven member 16 and a sliding bearing 13 are provided within the housing recess 15. The sliding bearing 13 is an example of a "driven shaft support" in the present invention. The sliding bearing 13 is formed in a cylindrical shape extending in the direction of the drive shaft O1. Here, the outer diameter of the sliding bearing 13 is formed to be slightly larger than the inner diameter of the housing recess 15. The sliding bearing 13 is fixed to the driven end plate 41 by being tightly fitted into the housing recess 15 and is positioned within the housing recess 15.

[0086] The driven member 16 has a bush 53 and a driven pin 55. The bush 53 is made of metal. The bush 53 consists of a bush body 53a and an extension 53b. The bush body 53a is formed to be slightly smaller in diameter than the inner diameter of the sliding bearing 13. The extension 53b is formed integrally with the bush body 53a. The extension 53b is formed to be smaller in diameter than the bush body 53a. Furthermore, the extension 53b, including the front end surface 641 of the first diameter portion 64a, is formed to be smaller in diameter than the first diameter portion 64a, and consequently, the protruding body 64. The extension 53b protrudes rearward in the direction of the drive axis O1 from the bush body 53a.

[0087] The bush 53 is positioned inside the sliding bearing 13 in the housing recess 15 by fitting the bush body 53a into the sliding bearing 13. In this way, the bush body 53a is supported by the sliding bearing 13 within the housing recess 15. The sliding bearing 13 is then able to move relative to the bush body 53a in the direction of the drive axis O1 within the housing recess 15.

[0088] Furthermore, with the bush 53 attached to the sliding bearing 13 in this manner, the extension portion 53b extends rearward from the housing recess 15, i.e., the driven end plate 41. In Figures 2 to 4, for the sake of clarity, the gap between the sliding bearing 13 and the bush body portion 53a in the radial direction of the housing 6 is exaggerated. Also, in Figure 4, for the sake of clarity, the first radial ball bearing 51, the first circlip 5, and the cover body 37 are omitted from the illustration.

[0089] The driven pin 55 is made of metal and is inserted through the bush 53. More specifically, the driven pin 55 is inserted through the bush body 53a and extension 53b at a position eccentric to the center of the bush 53, i.e., the driven axis O2. As a result, the driven pin 55 protrudes rearward from the bush 53 and, consequently, from the driven end plate 41.

[0090] Furthermore, as shown in Figure 1, a pivot pin 21 is fixed to the driven end plate 41 at the location facing the ring 22. The pivot pin 21 protrudes rearward from the third rear surface 412. Six pivot pins 21 are fixed to the driven end plate 41, the same number as the rings 22. In Figure 1 and other figures, one of the six pivot pins 21 is shown.

[0091] The driven mechanism 20 is then composed of these pivot pins 21 and rings 22. Here, the number of pivot pins 21 and rings 22 can be designed as appropriate, as long as there are three or more of each.

[0092] The driven spiral body 43 is integral with the driven end plate 41 and extends forward from the third front surface 411 of the driven end plate 41 parallel to the drive axis O1 and the driven axis O2. The driven spiral body 43 has the center of the driven end plate 41 as its spiral center and extends outward from the spiral center.

[0093] In this compressor, a driven scroll 40 is housed within the drive scroll 30, more specifically, between the drive end plate 31 and the drive peripheral wall 35 and the cover body 37. The drive spiral body 33 and the driven spiral body 43 are meshed together. As a result, the drive spiral body 33 and the driven spiral body 43 face each other to form a compression chamber 12.

[0094] Furthermore, a suction section 30a is formed between the drive peripheral wall 35 and the driven scroll 40. In other words, the drive spiral body 33 and the driven spiral body 43 are located within the suction section 30a. The suction section 30a is separated from the scroll chamber 65 by the drive peripheral wall 35 and the cover body 37, and is also separated from the discharge chamber 14 by the drive end plate 31. The suction section 30a is also in communication with the suction port 374.

[0095] Furthermore, by housing the driven scroll 40 within the driven scroll 30, each orbital pin 21 is positioned within each ring 22. In this way, the driven scroll 30 and the driven scroll 40 are assembled in the front-rear direction, and the driven scroll 30 and the driven scroll 40 constitute the scroll compression section 100. More precisely, after the driven spiral body 33 and the driven spiral body 43 are meshed and each orbital pin 21 is inserted into each ring 22, the cover body 37 of the driven scroll 30 is fixed to the drive peripheral wall 35 and the rotor 11.

[0096] Furthermore, when the drive scroll 30 and the driven scroll 40 are assembled, the housing recess 15 of the driven end plate 41 and the driven member 16 face the recess 373 of the cover body 37. As a result, the driven member 16 is positioned between the protruding body 64 and the driven scroll 40 in the direction of the drive axis O1.

[0097] The drive scroll 30 is positioned in front of the stator 17 within the scroll chamber 65. As shown in Figure 2, in the drive scroll 30, the inner cylindrical portion 37b of the cover body 37 is inserted into the inner circumference of the first coil end 171. In this state, the first diameter portion 64a of the protruding body 64 and the first radial ball bearing 51 are inserted into the inner cylindrical portion 37b.

[0098] Here, as described above, the inner diameter of the inner cylinder portion 37b is formed to be slightly smaller than the outer diameter of the first radial ball bearing 51. As a result, in the first radial ball bearing 51, the first outer ring 51b is tightly fitted to the inner circumferential surface of the inner cylinder portion 37b. In this way, the first radial ball bearing 51 is integrated with the inner cylinder portion 37b and, by extension, the drive scroll 30. The cover body 37 is rotatably supported on the first diameter portion 64a via the first radial ball bearing 51. In other words, the cover body 37 is rotatably supported on the first diameter portion 64a and, by extension, the protruding body 64, behind the driven scroll 40 via the first radial ball bearing 51.

[0099] Furthermore, because the cover body 37 is rotatably supported on the first diameter portion 64a in this manner, the housing portion 38 is in communication with the scroll chamber 65. The first coil end 171 is housed within the housing portion 38. As a result, within the housing portion 38, the first coil end 171 is covered from the front by the wall portion 37a and covered from the radially inner side of the housing 6 by the inner cylindrical portion 37b. The first coil end 171 is also covered from the radially outer side of the housing 6 by the outer cylindrical portion 37c within the housing portion 38.

[0100] Furthermore, as shown in Figure 1, in the drive scroll 30, the boss 39c of the case 39 is inserted through the second radial ball bearing 52 and the shaft sealing member 63. Here, as described above, the outer diameter of the boss 39c is formed to be slightly larger than the inner diameter of the second radial ball bearing 52. For this reason, the boss 39c is interlocked with the second inner ring 52a of the second radial ball bearing 52.

[0101] Thus, the case 39 is rotatably supported by the support portion 66 via the second radial ball bearing 52. As a result, the drive scroll 30 is positioned within the scroll chamber 65 and is rotatably supported by the housing 6 by both the protruding body 64 and the support portion 66, so as to be around the drive axis O1. In addition, the one-sided elastic body 67 elastically supports the drive scroll 30 via the second radial ball bearing 52.

[0102] Furthermore, by inserting the boss 39c through the second radial ball bearing 52 and the shaft sealing member 63 in this manner, a discharge communication chamber 88 is formed inside the support portion 66. The discharge communication chamber 88 communicates with the discharge chamber 14 through the discharge passage 390. The discharge communication chamber 88 also communicates with the discharge port 69. In other words, the discharge chamber 14 and the discharge port 69 communicate with each other through the discharge passage 390 and the discharge communication chamber 88.

[0103] Furthermore, the front portion of the boss 39c enters the discharge communication chamber 88. As a result, the front end surface 391 of the boss 39c faces the discharge communication chamber 88. In addition, the shaft sealing member 63 seals the space between the discharge communication chamber 88 and the scroll chamber 65.

[0104] On the other hand, in the driven scroll 40, the driven pin 55 of the driven member 16 is inserted into the pin hole 4. As a result, the driven scroll 40 is positioned in front of the projection 64 within the scroll chamber 65, and is rotatably supported around the driven axis O2 relative to the first diameter portion 64a of the projection 64. In addition, the extension portion 53b of the bush 53 is located radially inward of the housing 6 than the front end surface 641 of the projection 64, and faces the front end surface 641 from the front.

[0105] Thus, unlike the drive scroll 30, the driven scroll 40 is supported by the housing 6 solely by the protruding body 64 so as to be rotatable around the driven axis O2.

[0106] As described above, in this compressor, the first radial ball bearing 51 is integrated with the drive scroll 30 by being tightly fitted into the inner cylindrical portion 37b. Therefore, in this compressor, as shown in Figures 2 and 3, as the first radial ball bearing 51 moves relative to the first diameter portion 64a in the direction of the drive axis O1, the drive scroll 30 is also permitted to move relative to the first diameter portion 64a, and consequently to the protruding body 64, in the direction of the drive axis O1. Although detailed illustrations are omitted, at this time, the boss 39c also moves relative to the drive axis O1 within the support portion 66 together with the second radial ball bearing 52.

[0107] Furthermore, in this compressor, the bush body 53a is gap-fitted into the sliding bearing 13, and the sliding bearing 13 is tightly fitted into the housing recess 15. This allows the driven scroll 40 to move relative to the driven member 16 in the direction of the drive axis O1. In other words, the driven scroll 40 is allowed to move in the direction of the drive axis O1, corresponding to the movement of the drive scroll 30 in the direction of the drive axis O1 as described above.

[0108] Furthermore, as shown in Figures 3 and 4, the bush 53 is able to move backward relative to the driven pin 55 by contacting the driven end plate 41 within the housing recess 15 and being pressed backward by the driven end plate 41. The bush 53's backward movement is restricted when the extension 53b contacts the front end surface 641 of the first diameter portion 64a. As a result, the backward movement of the driven scroll 40 is also restricted in this compressor.

[0109] In this compressor configured as described above, as shown by the dashed arrows in Figures 1 and 2, low-temperature, low-pressure refrigerant that has passed through the evaporator is drawn into the scroll chamber 65 from the intake port 68. When the electric motor 10 operates and the rotor 11 rotates, the rotation of the rotor 11 is transmitted to the drive scroll 30, causing the drive scroll 30 to rotate around the drive axis O1 within the scroll chamber 65. In other words, the drive scroll 30 and the rotor 11 rotate together as a single unit. At this time, in the driven mechanism 20, each orbital pin 21 slides against the inner circumferential surface of each ring 22, causing each ring 22 to rotate relatively around the center of each orbital pin 21. In this way, the driven mechanism 20 transmits the torque of the drive scroll 30 to the driven scroll 40.

[0110] As a result, the driven scroll 40 is rotated by the drive scroll 30 and the driven mechanism 20 around the driven axis O2. At this time, the driven mechanism 20 restricts the driven scroll 40 from rotating relative to the drive scroll 30. This causes the driven scroll 40 to revolve relative to the drive scroll 30 around the driven axis O2. Then, as the drive vortex 33 and the driven vortex 43 rotate within the intake section 30a, the drive vortex 33 and the driven vortex 43 change the volume of the compression chamber 12.

[0111] The refrigerant drawn into the scroll chamber 65 flows between the rotor 11 and the stator 17 to the storage section 38, and is then drawn into the compression chamber 12 through the intake port 374 and the intake section 30a. Alternatively, the refrigerant drawn into the scroll chamber 65 can also reach the storage section 38 by flowing through the slits formed in the stator core 17a, and is then drawn into the compression chamber 12 through the intake port 374 and the intake section 30a.

[0112] The compression chamber 12 compresses the refrigerant by reducing its own volume while confining it within itself, through the rotational drive of the drive scroll 30 and the rotational movement of the driven scroll 40. In this way, the high-pressure refrigerant, compressed to the discharge pressure, is discharged from the discharge port 32 into the discharge chamber 14. Therefore, the atmosphere inside the discharge chamber 14 is higher pressure than inside the scroll chamber 65.

[0113] The high-temperature, high-pressure refrigerant discharged into the discharge chamber 14 flows through the discharge port 69 to the discharge port 88, and is then discharged outside the compressor through piping connected to the discharge port 69 from the discharge port 88.

[0114] As high-pressure refrigerant flows through the discharge communication chamber 88, the pressure inside the discharge communication chamber 88 is approximately the same as the pressure inside the discharge chamber 14. This results in a higher-pressure atmosphere inside the discharge communication chamber 88 compared to the scroll chamber 65. In this compressor, the space between the discharge communication chamber 88 and the scroll chamber 65 is sealed by the shaft seal member 63, preventing refrigerant leakage from the discharge communication chamber 88 into the scroll chamber 65.

[0115] In this compressor, the compression load due to the refrigerant in the compression chamber 12 acts on the drive scroll 30 and the driven scroll 40. As a result, as shown in Figure 4, the driven scroll 40 inevitably rotates around the driven axis O2 in a tilted position relative to the projection 64 during operation. Due to this tilting of the driven scroll 40, a portion of the driven end plate 41, specifically the portion of the driven end plate 41 surrounding the housing recess 15, approaches the first diameter portion 64a of the projection 64 from the front. In this compressor, since the sliding bearing 13 is tightly fitted to the inner circumferential surface of the housing recess 15, the sliding bearing 13 also approaches the first diameter portion 64a from the front together with the driven end plate 41.

[0116] Furthermore, as shown in Figure 1, in this compressor, the front portion of the boss 39c, which is inserted through the second radial ball bearing 52 and the shaft sealing member 63, is located inside the discharge communication chamber 88. The front end surface 391 of the boss 39c faces the discharge communication chamber 88. As a result, the pressure of the refrigerant in the discharge communication chamber 88, that is, the high pressure of the refrigerant, acts on the front end surface 391.

[0117] Therefore, as shown by the white arrow in Figure 1, a thrust load F acts on the front end surface 391, directed from the front to the rear in the direction of the drive axis O1, due to the pressure difference between the pressure in the discharge communication chamber 88 and the pressure in the scroll chamber 65. In addition, since the driven scroll 40 is located inside the drive scroll 30 in this compressor, a thrust load F also acts on the driven scroll 40 through the drive scroll 30, directed from the front to the rear in the direction of the drive axis O1. Furthermore, in this compressor, the compressive load acting on the driven scroll 40 also becomes a thrust load F on the driven scroll 40.

[0118] In this compressor, the thrust load F acting upon the drive scroll 30, together with the first radial ball bearing 51, allows it to move relative to the first diameter portion 64a from the position shown in Figure 2 to the position shown in Figure 3, in the direction of the drive axis O1. In other words, the drive scroll 30 can move relative to the first diameter portion 64a while maintaining its position supported by the first radial ball bearing 51. Here, the relative rearward movement of the drive scroll 30 and the first radial ball bearing 51 is restricted by the contact of the first radial ball bearing 51 with the first circlip 5.

[0119] Furthermore, the driven scroll 40 can also move relative to the driven member 16 in the direction of the drive axis O1. In other words, the driven scroll 40 can move backward toward the first diameter portion 64a and, consequently, toward the protruding body 64, while maintaining its position supported by the first diameter portion 64a. Here, since the sliding bearing 13 is tightly fitted to the inner circumferential surface of the housing recess 15, it moves backward together with the driven scroll 40.

[0120] Then, as shown in Figures 3 and 4, when the driven scroll 40 moves backward, as described above, the bush 53 is pressed backward by the bottom surface of the housing recess 15, that is, by the driven end plate 41, so that the bush 53 moves backward relative to the driven pin 55. As a result, the extension portion 53b of the bush 53 comes into contact with the front end surface 641 of the first diameter portion 64a. Consequently, in this compressor, the backward movement of the driven scroll 40 is restricted. Here, in this compressor, the extension portion 53b is formed to have a smaller diameter than the front end surface 641 of the first diameter portion 64a, and the extension portion 53b always comes into contact with the front end surface 641 while being located radially inward of the housing 6 compared to the front end surface 641.

[0121] Thus, in this compressor, when the driven scroll 40 is inclined relative to the projection 64 during operation, and even when the driven scroll 40 moves backward due to a thrust load F, the extension 53b of the bush 53 contacts the first diameter portion 64a of the projection 64 before the sliding bearing 13. In this way, this compressor can prevent the sliding bearing 13 from contacting the first diameter portion 64a, and can prevent wear and damage to the sliding bearing 13 and the projection 64 caused by contact between the sliding bearing 13 and the first diameter portion 64a. Furthermore, this compressor can also prevent power loss of the driven scroll 40 during operation due to the sliding bearing 13 contacting the first diameter portion 64a. In addition, this compressor can also prevent the driven end plate 41 from contacting the first diameter portion 64a.

[0122] Therefore, the compressor of Example 1 has excellent durability and operating efficiency.

[0123] In particular, in this compressor, the extension portion 53b of the bush 53 is formed to have a smaller diameter than the bush body portion 53a. As a result, in this compressor, the contact area between the bush 53 and the first diameter portion 64a is smaller compared to the case where the bush body portion 53a, i.e., the entire bush 53, is in contact with the first diameter portion 64a.

[0124] Furthermore, in this compressor, the extension portion 53b is formed to have a smaller diameter than the front end surface 641 of the first diameter portion 64a, and as the bush 53 moves backward, the extension portion 53b always comes into contact with the front end surface 641 while remaining radially inward of the housing 6 compared to the front end surface 641. As a result, in this compressor, the entire extension portion 53b can come into contact with the front end surface 641, making it difficult for both the front end surface 641 and the extension portion 53b to wear unevenly.

[0125] As shown in Figures 5 and 6, in the compressor of Embodiment 2, a housing recess 19 is formed in the driven end plate 41 instead of the housing recess 15 in the compressor of Embodiment 1. Similar to the housing recess 15, the housing recess 19 is located in the center of the driven end plate 41 and is recessed in a cylindrical shape from the third rear surface 412 of the driven end plate 41 toward the front, with the driven axis O2 as the center. As a result, the housing recess 19 opens to the rear of the driven end plate 41. Here, the housing recess 19 is formed to have a larger diameter than the first diameter portion 64a of the protruding body 64. In addition, a contact surface 19a is formed inside the housing recess 19. Due to this contact surface 19a, a step exists inside the housing recess 19.

[0126] Furthermore, in this compressor, a third radial ball bearing 81 is provided in the housing recess 19 in place of the sliding bearing 13 in the compressor of Example 1. The third radial ball bearing 81 is an example of a "rolling bearing" in the present invention.

[0127] The third radial ball bearing 81 has a third inner ring 81a and a third outer ring 81b. The third inner ring 81a is an example of an "inner ring" in the present invention, and the third outer ring 81b is an example of an "outer ring" in the present invention. The inner diameter of the third inner ring 81a, i.e., the inner diameter of the third radial ball bearing 81, is formed to be slightly smaller than the outer diameter of the bush body portion 53a of the bush 53. The outer diameter of the third outer ring 81b, i.e., the outer diameter of the third radial ball bearing 81, is formed to be smaller than the inner diameter of the housing recess 19.

[0128] In this compressor, the bush body 53a is inserted through the third inner ring 81a of the third radial ball bearing 81. In this case, since the inner diameter of the third inner ring 81a is smaller than the outer diameter of the bush body 53a, the bush body 53a is tightly fitted onto the third inner ring 81a. Thus, in this compressor, the third radial ball bearing 81 and the bush 53 are integrated. In this case, the extension portion 53b of the bush 53 protrudes rearward from the third radial ball bearing 81. Note that in Figures 5 and 6, for the sake of clarity, the gap between the housing recess 19 in the radial direction of the housing 6 and the third radial ball bearing 81 is exaggerated in the illustration.

[0129] Furthermore, in this compressor, the third outer ring 81b of the third radial ball bearing 81 is fitted into the housing recess 19. Thus, in this compressor, the third radial ball bearing 81 and the bush 53 are provided within the housing recess 19. In this compressor, the driven end plate 41 can move relative to the third radial ball bearing 81 and the bush 53 in the direction of the drive axis O1. Also, within the housing recess 19, the contact surface 19a contacts the third radial ball bearing 81 from the front. The other configurations of this compressor are the same as those of the compressor in Embodiment 1, and the same reference numerals are used for the same configurations, and detailed descriptions of the configurations are omitted.

[0130] In this compressor, if the driven scroll 40 is tilted relative to the projection 64 during operation, or if the driven scroll 40 moves backward due to a thrust load F, the extension 53b of the bush 53 will contact the first diameter portion 64a of the projection 64 before the third radial ball bearing 81 (see Figure 6). In this way, this compressor can prevent the third radial ball bearing 81 from contacting the first diameter portion 64a. As a result, this compressor can perform the same function as the compressor in Embodiment 1.

[0131] As shown in Figures 7 and 8, in the compressor of Embodiment 3, a fourth radial ball bearing 83 is provided in the housing recess 19 in place of the third radial ball bearing 81 in the compressor of Embodiment 2. The fourth radial ball bearing 83 is also an example of a "rolling bearing" in the present invention. In this compressor as well, a housing recess 19 is formed in the driven end plate 41, similar to the compressor of Embodiment 2. As a result, a contact surface 19a is formed in the housing recess 19 in this compressor as well. Furthermore, in this compressor, a driven member 16a is provided in the housing recess 19 in place of the driven member 16. The driven member 16a has a bush 56 and a driven pin 55.

[0132] The fourth radial ball bearing 83 has a fourth inner ring 83a and a fourth outer ring 83b. The fourth inner ring 83a and the fourth outer ring 83b are also examples of the "inner ring" and "outer ring" in the present invention, respectively. The inner diameter of the fourth inner ring 83a, i.e., the inner diameter of the fourth radial ball bearing 83, is formed to be slightly larger than the outer diameter of the bush 56. The outer diameter of the fourth outer ring 83b, i.e., the outer diameter of the fourth radial ball bearing 83, is formed to be the same diameter as the outer diameter of the third radial ball bearing 81. As a result, the outer diameter of the fourth outer ring 83b is smaller than the inner diameter of the housing recess 19.

[0133] Unlike bush 53, bush 56 does not have an extension 53b. Bush 56 is formed to be longer in the direction of the drive axis O1 than the fourth radial ball bearing 83. The driven pin 55 is inserted into bush 56 at a position eccentric to the center of bush 56.

[0134] In this compressor, the fourth radial ball bearing 83 is positioned behind the contact surface 19a within the housing recess 19. In this compressor, the bush 56 is clearance-fitted to the fourth inner ring 83a of the fourth radial ball bearing 83. The fourth outer ring 83b of the fourth radial ball bearing 83 is also clearance-fitted to the housing recess 19. Note that in Figures 7 and 8, for the sake of clarity, the gap between the housing recess 19 and the fourth radial ball bearing 83 in the radial direction of the housing 6 is exaggerated, as is the gap between the fourth radial ball bearing 83 and the bush 56 in the radial direction of the housing 6.

[0135] Furthermore, in this compressor, a second circlip 7 is attached to the driven end plate 41. The second circlip 7 is an example of the "first restricting portion" in the present invention. The second circlip 7 is positioned behind the fourth radial ball bearing 83 within the housing recess 19. Moreover, in this compressor, the contact surface 19a is designated as the "second restricting portion" in the present invention.

[0136] In this compressor, the gap between the second circlip 7 and the fourth radial ball bearing 83 in the direction of the drive axis O1 is defined as the first gap S1, and the gap between the contact surface 19a and the fourth radial ball bearing 83 in the direction of the drive axis O1 is defined as the second gap S2. Furthermore, in this compressor, the gap between the bottom surface 190 of the housing recess 19 and the bush 56 in the direction of the drive axis O1 is defined as the third gap S3, and the gap between the bush 56 and the front end surface 641 of the first diameter portion 64a in the direction of the drive axis O1 is defined as the fourth gap S4. Thus, in this compressor, the bush 56 can move relative to the fourth radial ball bearing 83 in the direction of the drive axis O1 within the range of the third gap S3 and the fourth gap S4. Also, the driven end plate 41 can move relative to the fourth radial ball bearing 83 in the direction of the drive axis O1 within the range of the first gap S1 and the second gap S2.

[0137] Here, the third gap S3 is formed to be smaller than the first gap S1, and the fourth gap S4 is formed to be smaller than the second gap S2. As a result, the distance between the bush 56 and the bottom surface 190 and the front end surface 641 in the direction of the drive axis O1 is smaller than the distance between the fourth radial ball bearing 83 and the second circlip 7 and the contact surface 19a in the direction of the drive axis O1. In addition, in this compressor, the second gap S2 is formed to be smaller than the first gap S1, and the third gap S3 is formed to be smaller than the fourth gap S4. Thus, in this compressor, the sum of the third gap S3 and the fourth gap S4 is smaller than the sum of the first gap S1 and the second gap S2. As a result, the range in which the bush 56 can move relative to the fourth radial ball bearing 83 in the direction of the drive axis O1 is smaller than the range in which the driven end plate 41 can move relative to the fourth radial ball bearing 83 in the direction of the drive axis O1. The other configurations in this compressor are the same as those of the compressor in Embodiment 1. In other words, the second circlip 7 restricts the amount of movement backward in the direction of the drive axis O1, and the contact surface 19a restricts the amount of movement forward in the direction of the drive axis O1.

[0138] In this compressor, since the sum of the third gap S3 and the fourth gap S4 is smaller than the sum of the first gap S1 and the second gap S2, even if the driven scroll 40 is tilted relative to the projection 64 during operation, or if the driven scroll 40 moves backward due to a thrust load F, it is possible to prevent the fourth radial ball bearing 83 from coming into contact with the first diameter portion 64a. In other words, in this compressor, since the third gap S3 is smaller than the first gap S1, if the driven scroll 40 is tilted relative to the projection 64 during operation, or if the driven scroll 40 moves backward due to a thrust load F, the bottom surface 190 of the housing recess 19 comes into contact with the bush 56 before the fourth radial ball bearing 83 comes into contact with the second circlip 7 and further with the first diameter portion 64a. The bush 56 is then pressed backward by the bottom surface 190, causing it to move backward relative to the fourth radial ball bearing 83. Furthermore, because the fourth gap S4 is smaller than the second gap S2, the bush 56 contacts the front end surface 641 of the first diameter portion 64a before the contact surface 19a contacts the fourth radial ball bearing 83. As a result, the bush 56 comes into contact with both the bottom surface 190 and the front end surface 641 in the direction of the drive axis O1, and the rearward movement of the driven scroll 40 is restricted by the bush 56 in this state. Therefore, from this point onward, the fourth radial ball bearing 83 is not pressed rearward by the driven end plate 41 through the contact surface 19a.

[0139] Thus, in this compressor, when the driven scroll 40 is tilted relative to the projection 64 during operation, or when the driven scroll 40 moves backward due to a thrust load F, the bush 56 contacts the first diameter portion 64a of the projection 64 rather than the fourth radial ball bearing 83 (see Figure 8). This prevents the fourth radial ball bearing 83 from contacting the first diameter portion 64a in this compressor. As a result, this compressor can perform the same function as the compressor in Embodiment 1.

[0140] Although the present invention has been described above in reference to Examples 1 to 3, it goes without saying that the present invention is not limited to Examples 1 to 3, and can be applied with appropriate modifications without departing from its spirit.

[0141] For example, in the compressor of Embodiment 1, the bush body 53a may be fitted tightly onto the sliding bearing 13, and the sliding bearing 13 may be fitted loosely into the housing recess 15. Alternatively, the bush body 53a may be fitted loosely onto the sliding bearing 13, and the sliding bearing 13 may be fitted loosely into the housing recess 15. Furthermore, the bush body 53a may be fitted tightly onto the sliding bearing 13, and the sliding bearing 13 may be fitted loosely into the housing recess 15.

[0142] Furthermore, in the compressor of Embodiment 2, the bush body portion 53a may be fitted with a clearance onto the third inner ring 81a of the third radial ball bearing 81, and the third outer ring 81b of the third radial ball bearing 81 may be fitted into the housing recess 19. Alternatively, the bush body portion 53a may be fitted with a clearance onto the third inner ring 81a, and the third outer ring 81b may be fitted with a clearance onto the housing recess 19. Furthermore, the bush body portion 53a may be fitted into the third inner ring 81a, and the third outer ring 81b may be fitted into the housing recess 19.

[0143] Furthermore, in the compressor of Embodiment 1, the extension portion 53b may always be in contact with the front end surface 641 of the first diameter portion 64a, regardless of the position of the driven scroll 40 during operation or the thrust load F acting on the driven scroll 40. The same applies to the compressor of Embodiment 2.

[0144] Furthermore, in the compressor of Embodiment 1, the formation of the extension portion 53b may be omitted, and the entire bush body portion 53a may be shaped to protrude rearward from the sliding bearing 13. The same applies to the compressor of Embodiment 2.

[0145] Furthermore, in the compressor of Example 3, the second circlip 7 is designated as the "first restricting part" in the present invention, and the contact surface 19a is designated as the "second restricting part" in the present invention. However, the "first restricting part" and the "second restricting part" are not limited to this configuration and may have other configurations.

[0146] Furthermore, in the compressor of Embodiment 1, the first inner ring 51a of the first radial ball bearing 51 may be fitted tightly into the first diameter portion 64a of the protruding body 64, and the first outer ring 51b of the first radial ball bearing 51 may be fitted with clearance into the inner cylindrical portion 37b of the cover body 37. Alternatively, both the first inner ring 51a and the first outer ring 51b may be fitted with clearance. The same applies to the compressors of Embodiments 2 and 3.

[0147] Furthermore, in the compressor of Example 1, the second inner ring 52a of the second radial ball bearing 52 may be fitted into the boss 39c of the case 39. The same applies to the compressors of Examples 2 and 3.

[0148] Furthermore, in the compressor of Example 1, the protruding body 64 has a first diameter portion 64a and a second diameter portion 64b. However, it is not limited to this, and the protruding body 64 may be formed only of the first diameter portion 64a, or the protruding body 64 may be formed only of the second diameter portion 64b. The same applies to the compressors of Examples 2 and 3.

[0149] Furthermore, in the compressor of Embodiment 1, the stator 17 is fixed to the second diameter portion 64b, and the stator 17 is covered from the outside by the rotor 11. However, the compressor is not limited to this, and the stator 17 may be fixed to the housing 6, and the rotor 11 may be fixed to the cover body 37 inside the stator 17. The same applies to the compressors of Embodiments 2 and 3.

[0150] Furthermore, in the compressor of Example 1, the other elastic body 70 is composed of the first to third elastic bodies 70a to 70c. However, it is not limited to this, and the other elastic body 70 may have other configurations. Also, the other elastic body 70 may be omitted, or the one elastic body 67 may be omitted. The same applies to the compressors of Examples 2 and 3.

[0151] Furthermore, in the compressor of Example 1, the protrusion 64 may be integrally formed on the first housing cover 61. The same applies to the compressors of Examples 2 and 3.

[0152] This invention can be used in vehicle air conditioning systems and the like.

[0153] 6 Housing 7 Second circlip (first restricting part) 10 Electric motor (drive mechanism) 11 Rotor 12 Compression chamber 13 Sliding bearing (driven shaft support part) 16, 16a Driven member 19a Contact surface (second restricting part) 20 Driven mechanism 30 Driven scroll 40 Driven scroll 53, 56 Bushing 53a Bushing body 53b Extension 64 Projection 65 Scroll chamber 81 Third radial ball bearing (rolling bearing) 81a Third inner ring (inner ring) 81b Third outer ring (outer ring) 83 Fourth radial ball bearing (rolling bearing) 83a Fourth inner ring (inner ring) 83b Fourth outer ring (outer ring) 641 Front end face (end face) O1 Drive shaft center O2 Driven shaft center S1 First clearance S2 Second gap S3 Third gap S4 Fourth gap

Claims

1. A double-rotation scroll compressor comprising a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the drive scroll, the driven scroll, and the drive mechanism are housed, the drive mechanism has a stator and a rotor that is rotationally driven by the stator, the drive scroll is rotationally driven around a drive axis by the drive mechanism, the driven scroll is rotationally driven around a driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, and the drive scroll and the driven scroll form a compression chamber for compressing fluid by the rotational drive and the rotational drive, wherein a projection is provided in the scroll chamber extending toward the drive scroll and the driven scroll in the direction of the drive axis, a driven member is provided between the projection and the driven scroll in the direction of the drive axis, the drive scroll is rotatably supported by the projection around the drive axis, and the driven scroll is rotatably supported by the projection around the driven axis via the driven member, A double-rotating scroll compressor is characterized in that a driven shaft support is provided between the driven scroll and the driven member, the driven member has a bush supported by the driven shaft support, and the bush extends in the direction of the drive axis toward the projection from the driven shaft support.

2. The double-rotating scroll compressor according to claim 1, wherein the bush comprises a bush body supported by the driven shaft support, and an extension having a smaller diameter than the bush body and formed integrally with the bush body, and extending in the direction of the drive axis toward the protruding body from the bush body.

3. The driven scroll, the driven shaft support, and the bush are located on one side in the direction of the drive axis relative to the projection, and the driven scroll, the driven shaft support, and the bush move toward the projection and to the other side in the direction of the drive axis due to a thrust load acting from one side in the direction of the drive axis.

4. A double-rotation scroll compressor comprising a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the drive scroll, the driven scroll, and the drive mechanism are housed, the drive mechanism has a stator and a rotor that is rotationally driven by the stator, the drive scroll is rotationally driven around a drive axis by the drive mechanism, the driven scroll is rotationally driven around a driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, and the drive scroll and the driven scroll form a compression chamber for compressing a fluid by the rotational drive and the rotational drive, wherein a projection is provided in the scroll chamber extending toward the drive scroll and the driven scroll in the direction of the drive axis, a driven member is provided between the projection and the driven scroll in the direction of the drive axis, the drive scroll is rotatably supported by the projection around the drive axis, and the driven scroll is rotatably supported by the projection around the driven axis via the driven member, A double-rotating scroll compressor is characterized in that a rolling bearing is provided between the driven scroll and the driven member to rotatably support the driven member, the driven member has a bush supported by the rolling bearing, the driven scroll, the rolling bearing and the bush are located on one side of the drive axis direction relative to the protruding body, the driven scroll, the rolling bearing and the bush are movable toward the protruding body toward the other side of the drive axis direction by a thrust load acting from one side of the drive axis direction, the rolling bearing has an outer ring facing the driven scroll in the radial direction of the housing and an inner ring located inside the outer ring in the radial direction and facing the bush in the radial direction, and the bush extends toward the protruding body toward the drive axis direction relative to the inner ring.

5. The double-rotating scroll compressor according to claim 4, wherein the outer ring is clearance-fitted to the driven scroll and the bushing is tight-fitted to the inner ring.

6. The double-rotation scroll compressor according to claim 5, wherein the bush has a bush body portion that is tightly fitted onto the inner ring, and an extension portion that has a smaller diameter than the bush body portion, is integrally formed with the bush body portion, and extends in the direction of the drive axis toward the protruding body from the bush body portion.

7. The dual-rotation scroll compressor according to claim 2 or 6, wherein the projection has an end face facing the extension in the direction of the drive axis, the end face is formed to be larger in diameter than the extension, and the extension is always located radially inward of the housing than the end face.

8. The outer ring is clearance-fitted to the driven scroll, the bush is clearance-fitted to the inner ring while being spaced apart from the driven scroll and the protruding body in the direction of the drive axis, the driven scroll is provided with a first restricting portion that restricts the amount of movement of the rolling bearing to the other side in the direction of the drive axis, and a second restricting portion that restricts the amount of movement of the rolling bearing to one side in the direction of the drive axis, the gap in the direction of the drive axis between the first restricting portion and the rolling bearing is the first gap, the gap in the direction of the drive axis between the second restricting portion and the rolling bearing is the second gap, the gap in the direction of the drive axis between the driven scroll and the bush is the third gap, the gap in the direction of the drive axis between the bush and the protruding body is the fourth gap, and the sum of the third gap and the fourth gap is smaller than the sum of the first gap and the second gap, as described in claim 4.

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