Co-rotating scroll compressor

Abstract

Provided is a co-rotating scroll compressor which is excellent in quietness and for which it is possible to suppress an increase in size. This compressor comprises: a housing 6; a driving scroll 30; a driven scroll 40; and a driving mechanism 10. The driving mechanism 10 has a stator 17 and a rotor 11. The stator has a stator core 17a supported by the housing 6. A protruding body 64 fixed to the stator core 17a is provided in a scroll chamber 65. The driving scroll 30 has a cover body 37 rotationally driven by the rotor 11. The cover body 37 is rotatably supported by the protruding body 64 around a drive shaft center O1 farther on the compression chamber 12 side than the stator core 17a in the drive shaft center O1 direction. The driven scroll 40 is rotatably supported by the protruding body 64 around a driven shaft center O2 farther on the compression chamber 12 side than the stator core 17a in the drive shaft center O1 direction.

Description

Double-rotating scroll compressor

[0001] The present invention relates to a double-rotating scroll compressor.

[0002] Patent Document 1 discloses a conventional double-rotating scroll compressor (hereinafter simply referred to as a compressor, as 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 houses the driving mechanism, the driving scroll, and the driven scroll. A fluid is drawn into the scroll chamber from outside the housing. In this document, the fluid is specifically a refrigerant.

[0003] The drive mechanism includes a stator and a rotor. The stator is cylindrical and has its outer periphery fixed to the housing. The rotor is disposed on the inner periphery of the stator. The drive scroll includes a cover body. The cover body has a cylindrical extension portion. The rotor is fixed to the outer periphery of the extension portion. This allows the drive scroll to be rotationally driven about the drive axis by rotation of the rotor. The driven scroll is eccentric with respect to the drive scroll and can be rotationally driven about the driven axis by the drive scroll and driven mechanism. The drive scroll and driven scroll form a compression chamber that compresses a fluid by rotational driving and rotational following.

[0004] In this compressor, a protrusion is integrally provided on the housing. The protrusion is formed in a generally cylindrical shape with a constant outer diameter and extends into the scroll chamber in the drive axial direction toward the drive scroll and the driven scroll. The protrusion extends into the extension portion and rotatably supports the cover body via bearings. A fluid passage extending in the drive axial direction is formed inside the protrusion. The fluid passage communicates with the compression chamber on one side in the drive axial direction and with the outside of the housing on the other side in the drive axial direction.

[0005] In this compressor, fluid in the scroll chamber is drawn into the compression chamber and compressed in the compression chamber, and the fluid compressed in the compression chamber flows through a fluid passage and is discharged to the outside of the housing, i.e., to the outside of the compressor.

[0006] Japanese Patent Application Publication No. 2-227575

[0007] In this type of compressor, the torque of the drive mechanism required to rotate the drive scroll changes as the fluid is compressed in the compression chamber. In the conventional compressor described above, the rotor is fixed to the extension of the cover, and the extension is rotatably supported by the protrusion. As a result, in this compressor, torque fluctuations of the drive mechanism are transmitted from the extension to the protrusion and ultimately to the housing. Furthermore, torque fluctuations of the drive scroll are also transmitted to the protrusion via the extension. As a result, a moment acts on the protrusion in a direction that twists the protrusion, making the housing, including the protrusion, prone to vibration during operation. As a result, the compressor's quietness is compromised.

[0008] One possible solution to this problem is to increase the rigidity of the housing to suppress vibration of the housing during operation, but this would result in an increase in the size of the housing, and ultimately the compressor.

[0009] The present invention has been made in view of the above-described conventional circumstances, and an object to be achieved is to provide a double-rotation scroll compressor that is quiet and can be prevented from becoming large.

[0010] A first double-rotating scroll compressor of the present invention includes a housing, a driving scroll, a driven scroll, a driving mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the driving scroll, the driven scroll, and the driving mechanism are housed, the driving mechanism has a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator, the stator has a stator core supported by the housing, the driving scroll is rotationally driven about a drive axis by the drive mechanism, and the driven scroll is rotationally driven by the driving scroll and the driven mechanism about a driven axis while being eccentric with respect to the driving scroll, and the driving scroll and the driven scroll form a compression chamber that compresses a fluid by the rotational driving and the rotational driven, and within the scroll chamber is provided a protrusion that is fixed to the stator core and extends in the drive axis direction toward the driving scroll and the driven scroll, and the driving scroll has a cover body that is rotationally driven by the rotor, The cover body is rotatably supported around the drive axis by the protruding body on the compression chamber side of the stator core in the direction of the drive axis, and the driven scroll is rotatably supported around the driven axis by the protruding body on the compression chamber side of the stator core in the direction of the drive axis.

[0011] In the first double-rotary scroll compressor of the present invention, a protrusion is provided in the scroll chamber, and the stator core is fixed to the protrusion. As a result, in this compressor, torque fluctuations of the drive mechanism are inevitably transmitted from the stator core, i.e., the stator, to the protrusion during operation.

[0012] In this compressor, the driving scroll has a cover body, and the cover body is rotatably supported by the protruding body on the compression chamber side of the stator core in the drive shaft direction. Furthermore, in this compressor, the driven scroll is rotatably supported by the protruding body on the compression chamber side of the stator core in the drive shaft direction. For these reasons, in this compressor, torque fluctuations of the driving scroll are inevitably transmitted to the protruding body during operation, and torque fluctuations of the driven scroll are also inevitably transmitted to the protruding body.

[0013] Here, in this compressor, the fluid is compressed by the rotation of both the driving scroll and the driven scroll, so that the phase of the torque fluctuations transmitted from the driving scroll and the driven scroll to the protrusions during operation is opposite to the phase of the torque fluctuations transmitted from the stator core to the protrusions.

[0014] As a result, in this compressor, torque fluctuations transmitted from the stator core to the protrusions and torque fluctuations transmitted from the driving scroll and the driven scroll to the protrusions are offset at the protrusions. Therefore, in this compressor, although a moment in a direction that twists the protrusions inevitably acts on the protrusions during operation, this moment acting on the protrusions can be reduced. Therefore, since the moment transmitted from the protrusions to the housing can be reduced, this compressor can effectively suppress vibration of the housing during operation.

[0015] Furthermore, because the moment transmitted to the housing can be reduced in this way, there is no need to make the housing excessively rigid to suppress vibration of the housing during operation, and therefore the housing of this compressor is less likely to become large.

[0016] Therefore, the first double-rotating scroll compressor of the present invention is excellent in quietness and can be prevented from becoming large in size.

[0017] In the first compressor of the present invention, the housing may have a first wall extending radially of the housing, a peripheral wall connected to the outer periphery of the first wall and extending cylindrically from the first wall in the drive shaft direction, and a second wall extending radially and connected to the peripheral wall on the opposite side of the drive shaft direction from the first wall. The first wall may support the protrusion. The driving scroll may have a supported member located on the opposite side of the drive shaft direction from the cover body across the compression chamber. The cover body may be supported on the protrusion via a first bearing so as to be rotatable about the drive shaft. It is preferable that the supported member be supported on the second wall via a second bearing so as to be rotatable about the drive shaft center.

[0018] In this case, in the driving scroll, the cover body is rotatably supported by the protruding body about the drive axis, and the supported member is rotatably supported by the second wall about the drive axis, so that the driving scroll is suitably supported in the housing by both the cover body and the supported member. Here, because the cover body is supported by the protruding member via the first bearing, torque fluctuations transmitted from the driving scroll to the protruding member can be minimized by the first bearing. Similarly, because the supported member is supported by the second wall via the second bearing, torque fluctuations transmitted from the supported member to the second wall can also be minimized by the second bearing.

[0019] The first wall may have a retaining portion extending into the scroll chamber in the drive shaft direction. The protrusion is preferably fitted into the retaining portion. In this case, the first wall can suitably retain the protrusion through the retaining portion. Furthermore, since the moment acting on the protrusion is less likely to be transmitted to the retaining portion, the housing, including the first wall, is less likely to vibrate.

[0020] Preferably, an elastically deformable first elastic body is provided between the protrusion and the first wall. In this case, the elastic deformation of the first elastic body can suitably suppress the moment acting on the protrusion from being transmitted to the first wall. As a result, in this compressor, the housing is less likely to vibrate, thereby achieving even quieter operation.

[0021] Furthermore, it is preferable that an elastically deformable second elastic body be provided between the second bearing and the second wall. In this case, the elastic deformation of the second elastic body can suitably suppress the transmission of moment from the supported object to the second wall. This also makes it more difficult for the housing to vibrate in this compressor, thereby achieving even quieter operation.

[0022] A second double-rotating scroll compressor of the present invention includes a housing, a driving scroll, a driven scroll, a drive mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the driving scroll, the driven scroll, and the drive mechanism are housed, the drive mechanism has a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator, the stator has a stator core supported by the housing, the driving scroll is rotationally driven about a drive axis by the drive mechanism, and the driven scroll is rotationally driven by the driving scroll and the driven mechanism about a driven axis while being eccentric with respect to the driving scroll, and the driving scroll and the driven scroll form a compression chamber that compresses a fluid by the rotational driving and the rotational driven, and within the scroll chamber is provided a protrusion that is fixed to the stator core and extends in the drive axis direction toward the driving scroll and the driven scroll, and the driving scroll has a cover body that is rotationally driven by the rotor, The cover body is supported by the protrusion so as to be rotatable around the drive axis, the driven scroll is supported by the protrusion so as to be rotatable around the driven axis, and the protrusion is attached to the housing via an elastic body that can be elastically deformed.

[0023] In the second double-rotary scroll compressor of the present invention, a protrusion is provided in the scroll chamber, and a stator core is fixed to the protrusion. The protrusion supports the cover body of the drive scroll rotatably about the drive axis and the driven scroll rotatably about the driven axis.

[0024] As a result, in this compressor, as in the first compressor of the present invention described above, torque fluctuations transmitted from the stator core to the protruding body and torque fluctuations transmitted from the driving scroll and the driven scroll to the protruding body are offset at the protruding body, and therefore, in this compressor as well, the moment acting on the protruding body can be reduced.

[0025] In this compressor, the protrusion is attached to the housing via an elastic body that is elastically deformable. Therefore, in this compressor, the elastic body elastically deforms, thereby effectively suppressing the moment acting on the protrusion from being transmitted to the housing. As a result, this compressor also effectively suppresses vibration of the housing during operation.

[0026] Furthermore, as with the first compressor of the present invention described above, in this compressor, there is no need to make the housing excessively rigid in order to suppress vibration of the housing during operation, and therefore the housing of this compressor is unlikely to become large.

[0027] Therefore, the second double-rotating scroll compressor of the present invention is excellent in quietness and can be prevented from becoming large in size.

[0028] In the second compressor of the present invention, the housing may have a first wall extending radially of the housing, a peripheral wall connected to the outer periphery of the first wall and extending cylindrically from the first wall in the drive shaft direction, and a second wall extending radially and connected to the peripheral wall on the opposite side of the drive shaft direction from the first wall. The first wall may have a protrusion attached thereto and may hold an elastic body. The driving scroll may have a supported member located on the opposite side of the drive shaft direction from the cover body across the compression chamber. The cover body may be supported by the protrusion via a first bearing so as to be rotatable about the drive shaft. It is preferable that the supported member be supported by the second wall via a second bearing so as to be rotatable about the drive shaft center.

[0029] In this case, in the driving scroll, the cover body is rotatably supported by the protruding body about the drive axis, and the supported member is rotatably supported by the second wall about the drive axis, so that the driving scroll is suitably supported in the housing by both the cover body and the supported member. Here, because the cover body is supported by the protruding member via the first bearing, torque fluctuations transmitted from the driving scroll to the protruding member can be minimized by the first bearing. Similarly, because the supported member is supported by the second wall via the second bearing, torque fluctuations transmitted from the supported member to the second wall can also be minimized by the second bearing.

[0030] The first wall may have a retaining portion extending into the scroll chamber in the drive shaft direction. The protrusion may engage with the retaining portion while allowing the elastic body and the retaining portion to enter the scroll chamber. The elastic body is preferably provided between the retaining portion and the protrusion in the radial direction and sandwiched between the retaining portion and the protrusion in the radial direction.

[0031] In this case, the protrusion can be easily attached to the first wall and thus to the housing by inserting the elastic body and the retaining portion into the protrusion and fitting the protrusion to the retaining portion. Also, since the elastic body is sandwiched between the retaining portion and the protrusion in the radial direction, the elastic body can be easily provided between the retaining portion and the protrusion, and therefore between the first wall and the protrusion.

[0032] The elastic body preferably includes a first elastic body provided between the protrusion and the first wall, and a second elastic body provided between the second bearing and the second wall.

[0033] In this case, the first elastic body can effectively prevent the moment acting on the protrusion from being transmitted from the protrusion to the first wall, and the second elastic body can effectively prevent the moment from the supported object from being transmitted to the second wall, making the housing of this compressor less susceptible to vibration.

[0034] In the first compressor of the present invention, it is preferable that at least a portion of the first elastic body overlaps with the stator core in the radial direction. In this case, compared to a case in which the first elastic body and the stator core are arranged without overlapping with each other in the radial direction, it is possible to prevent the compressor from becoming large in size in the drive shaft direction while ensuring contact areas between the retaining portion and the protrusion and the first elastic body.

[0035] In the second compressor of the present invention, it is preferable that at least a portion of the elastic body overlaps with the stator core in the radial direction. In this case, the contact area between the retaining portion and the protrusion and the elastic body can be secured while preventing the compressor from becoming large in size in the axial direction, compared to when the elastic body and the stator core are arranged without overlapping with each other in the radial direction.

[0036] In the first compressor and the second compressor of the present invention, the protrusion may have a first radial portion in which the cover body is rotatably supported about the drive shaft via a first bearing and the driven scroll is rotatably supported about the driven shaft, and a second radial portion having a diameter larger than that of the first radial portion and in which the stator core is disposed on an outer peripheral surface thereof. The first radial portion is preferably located closer to the compression chamber than the second radial portion in the direction of the drive shaft.

[0037] In this case, torque fluctuations transmitted from the stator core to the protruding body and torque fluctuations transmitted from the driving scroll and the driven scroll to the protruding body are offset at the protruding body. Also, in this compressor, the cover body and the driven scroll can be suitably supported by the protruding body on the compression chamber side of the stator core.

[0038] The driven scroll is preferably supported at the first radial portion radially inward of the cover body so as to be rotatable about the driven axis.

[0039] In this case, the driven scroll may have a driven shaft supported by the first radial portion, and it is preferable that the stator core, the first bearing, and the driven shaft are arranged in this order in the drive shaft direction from the first wall side toward the compression chamber side.

[0040] In these cases, it is possible to suitably prevent the housing from becoming large in size in the drive shaft direction.

[0041] The first and second double-rotary scroll compressors of the present invention are excellent in quietness and can be prevented from becoming large in size.

[0042] FIG. 1 is a cross-sectional view of a compressor according to a first embodiment. FIG. 2 is an enlarged cross-sectional view of a main part of the compressor according to the first embodiment, showing a protrusion, a cover body, etc. FIG. 3 is an enlarged cross-sectional view of a main part of a compressor according to a second embodiment, similar to FIG. 2, showing a protrusion, a cover body, etc. FIG. 4 is an enlarged cross-sectional view of a main part of a compressor according to a third embodiment, similar to FIG. 2, showing a protrusion, a cover body, etc. FIG. 5 is an enlarged cross-sectional view of a main part of a compressor according to a fourth embodiment, similar to FIG. 2, showing a protrusion, a cover body, etc. FIG. 6 is an enlarged cross-sectional view of a main part of a compressor according to a fifth embodiment, similar to FIG. 2, showing a protrusion, a cover body, etc.

[0043] Hereinafter, first to fifth embodiments of the present invention will be described with reference to the drawings. The compressors of the first to fifth embodiments are mounted on a vehicle (not shown) and form an air conditioning system for the vehicle.

[0044] 1, a compressor according to a first embodiment includes a housing 6, an electric motor 10, a driving scroll 30, a driven scroll 40, and a driven mechanism 20. The electric motor 10 is an example of the "driving mechanism" of the present invention.

[0045] In this embodiment, the front-rear direction and the up-down direction of the compressor are defined by solid arrows shown in Fig. 1. The front-rear direction and the up-down direction are perpendicular to each other. In Fig. 2 and subsequent figures, the front-rear direction and the up-down direction of the compressor are defined in accordance with Fig. 1. Note that these front-rear directions are examples for the convenience of explanation, and the compressor's position can be changed as appropriate depending on the vehicle in which it is installed.

[0046] 1, the housing 6 is composed of a housing main body 60, a first housing cover 61, and a second housing cover 62. The housing main body 60 is an example of a "peripheral wall" in the present invention, the first housing cover 61 is an example of a "first wall" in the present invention, and the second housing cover 62 is an example of a "second wall" in the present invention.

[0047] The housing body 60 is made of an aluminum alloy and has a cylindrical shape with a drive axis O1 at its center, and is open at both the front and rear ends. The drive axis O1 is parallel to the front-to-rear direction.

[0048] An intake communication port 68 is also formed in the housing body 60. The intake communication port 68 extends in the radial direction of the housing body 60. The intake communication port 68 is connected to an evaporator (not shown) through a pipe (not shown).

[0049] The first housing cover 61 is made of an aluminum alloy. The first housing cover 61 is located at the rear end of the housing main body 60. The first housing cover 61 is generally disk-shaped and centered on the drive axis O1, extending in the radial direction of the housing 6. The first housing cover 61 has a front surface 61a facing forward and a rear surface 61b facing rearward and located on the opposite side of the front surface 61a. The first housing cover 61 may also be made of steel.

[0050] The first housing cover 61 has a holding portion 611. The holding portion 611 is formed integrally with the first housing cover 61. The holding portion 611 has a cylindrical shape and protrudes forward from the center of the front surface 61 a in the direction of the drive axis O1.

[0051] An elastic body 67 and a protrusion 64 are provided inside the housing 6, more specifically, inside a scroll chamber 65 described later. The elastic body 67 is composed of a first elastic body 67a and a second elastic body 67b. Details of the second elastic body 67b will be described later.

[0052] As shown in Fig. 2, the first elastic body 67a is made of synthetic rubber. The first elastic body 67a is cylindrical and extends in the direction of the drive axis O1 with approximately the same length as the holding portion 611. The first elastic body 67a is attached to the outer circumferential surface of the holding portion 611. This allows the holding portion 611 to hold the first elastic body 67a. Meanwhile, the first elastic body 67a attached to the holding portion 611 covers the holding portion 611 from the outside. The material and thickness of the first elastic body 67a can be designed as appropriate.

[0053] The protrusion 64, including the retaining portion 611, is formed as a separate part from the first housing cover 61. The protrusion 64 is made of steel. The protrusion 64 is composed of a first radial portion 641 and a second radial portion 642. The first radial portion 641 forms the front portion of the protrusion 64. The first radial portion 641 has an outer diameter length of a first length L1. As a result, the first radial portion 641 is formed with a smaller diameter than the insertion hole 375, which will be described later. A pin hole 4 is formed in the first radial portion 641. The pin hole 4 extends inside the first radial portion 641 in the direction of the drive axis O1 and opens at the front end surface of the first radial portion 641.

[0054] A first radial ball bearing 51 is provided on the outer peripheral surface of the first diameter portion 641. The first radial ball bearing 51 is an example of the "first bearing" in the present invention. Note that instead of the first radial ball bearing 51, a sliding bearing may be provided on the outer peripheral surface of the first diameter portion 641.

[0055] The second diameter portion 642 is formed in a cylindrical shape with a bottom that is open at the rear. The second diameter portion 642 has an outer diameter of a second length L2. This second length L2 is longer than the first length L1. As a result, the second diameter portion 642 is formed to have a larger diameter than the first diameter portion 641. The inner diameter of the second diameter portion 642 is formed to have a third length L3. This third length L3 is longer than the first length L1 and is approximately the same as the outer diameter of the first elastic body 67a. As a result, the inner diameter of the second diameter portion 642 is larger than the retaining portion 611 and approximately the same as the outer diameter of the first elastic body 67a.

[0056] The second diameter portion 642 is integral with the first diameter portion 641 at the front end thereof. As a result, the second diameter portion 642 constitutes the rear portion of the protrusion 64.

[0057] The retaining portion 611 and the first elastic body 67a are inserted into the second radial portion 642, i.e., the inside of the protruding body 64. As a result, the retaining portion 611 and the second radial portion 642 are fitted together with the first elastic body 67a interposed between them in the radial direction of the housing 6. The first elastic body 67a is sandwiched between the retaining portion 611 and the second radial portion 642 in the radial direction of the housing 6. In this manner, in this compressor, the protruding body 64 is attached to the first housing cover 61. In other words, the protruding body 64 is attached to the first housing cover 61 while covering the retaining portion 611 and the first elastic body 67a from the outside. As a result, the first housing cover 61 supports the protruding body 64.

[0058] 1, the second housing cover 62 is disposed in front of the housing main body 60. The second housing cover 62 is made of an aluminum alloy. The second housing cover 62 is generally disk-shaped and centered on the drive axis O1, extending in the radial direction of the housing 6. The second housing cover 62 has a front surface 62a facing forward and a rear surface 62b facing rearward and located on the opposite side of the front surface 62a.

[0059] The second housing cover 62 is also formed with a support portion 66 and a discharge communication port 69. The support portion 66 is integrally formed approximately at the center of the rear surface 62b and protrudes rearward from the rear surface 62b. The support portion 66 is formed in a cylindrical shape centered on the drive axis O1, and is provided therein with the second radial ball bearing 52, a second elastic body 67b, and a shaft seal member 63. The second radial ball bearing 52 is an example of the "second bearing" in the present invention.

[0060] The second elastic body 67b is made of synthetic rubber, just like the first elastic body 67a. The second elastic body 67b is cylindrical. The second elastic body 67b is disposed between the support portion 66 and the second radial ball bearing 52, surrounding the second radial ball bearing 52 from the outside and holding the second radial ball bearing 52 within the support portion 66. The second elastic body 67b may be made of a metal or other material with lower rigidity than the second housing cover 62. The thickness of the second elastic body 67b 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.

[0061] The shaft seal member 63 is disposed in front of the second radial ball bearing 52 and the second elastic body 67b inside the support portion 66. The shaft seal member 63 is formed in an annular shape.

[0062] The discharge communication port 69 penetrates the second housing cover 62 in the direction of the drive axis O1 and communicates with the interior of the support portion 66. The discharge communication port 69 is also connected to a condenser (not shown) through piping (not shown).

[0063] In the housing 6, a front surface 61a of the first housing cover 61 abuts against the rear end of the housing main body 60, and a rear surface 62b of the second housing cover 62 abuts against the front end of the housing main body 60. Then, a plurality of bolts (not shown) secure the housing main body 60, the first housing cover 61, and the second housing cover 62 in the direction of the drive axis O1.

[0064] Thus, in the housing 6, the housing main body 60 is sandwiched in the front-to-rear direction between the first housing cover 61 and the second housing cover 62, and the front and rear ends of the housing main 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 within the housing main body 60 in the housing 6. The scroll chamber 65 communicates with the suction communication port 68. Therefore, refrigerant is drawn into the scroll chamber 65 from outside the housing 6 through the suction communication port 68. The refrigerant is an example of the "fluid" in the present invention.

[0065] Furthermore, by attaching the protrusion 64 to the first housing cover 61 as described above, the protrusion 64 protrudes from the first housing cover 61 in the direction of the drive axis O1 into the scroll chamber 65. More specifically, the protrusion 64 protrudes forward from the first housing cover 61 toward the driving scroll 30 and the driven scroll 40.

[0066] The electric motor 10 is housed in the scroll chamber 65. As a result, the scroll chamber 65 also serves as a motor chamber that houses the electric motor 10.

[0067] 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 a winding 17b. The stator core 17a is formed in a cylindrical shape centered on the drive shaft center O1. The winding 17b is wound around the stator core 17a. As a result, the winding 17b forms a first coil end 171 and a second coil end 172.

[0068] The first coil end 171 protrudes forward from the stator core 17a in the direction of the drive axis O1 in a cylindrical shape. 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 rearward from the stator core 17a in the direction of the drive axis O1 in a cylindrical shape.

[0069] In the stator 17, the stator core 17a is fitted onto the outer peripheral surface of the second radial portion 642. In this way, the stator core 17a is fixed to the outer peripheral surface of the second radial portion 642, and therefore to the outer peripheral surface of the protrusion 64. Although not shown, the inner peripheral surface of the stator core 17a has a plurality of slits formed therein that extend in the direction of the drive axis O1. As a result, when the stator core 17a is fixed to the second radial portion 642, the slits form a gap between the stator core 17a and the outer peripheral surface of the second radial portion 642.

[0070] Furthermore, by fixing the stator core 17a to the protrusion 64 in this manner, the first elastic body 67a is disposed more inward than the stator 17 in the radial direction of the housing 6. A portion of the first elastic body 67a overlaps with the stator core 17a in the radial direction of the housing 6. That is, within the range of region X1 shown in FIG. 2 , the first elastic body 67a and the stator core 17a overlap with each other in the radial direction of the housing 6. Note that the entire first elastic body 67a may be configured to overlap with the stator core 17a in the radial direction of the housing 6 by changing the length of at least one of the first elastic body 67a and the stator core 17a in the direction of the drive axis O1.

[0071] The rotor 11 is cylindrical around the drive axis O1. Although not shown in detail, the rotor 11 is composed of a plurality of permanent magnets corresponding to the stator 17 and laminated steel plates that secure the permanent magnets. The rotor 11 has a larger 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. The rotor 11 also has a plurality of first bolt holes 11a. Each of the first bolt holes 11a penetrates the rotor 11 in the direction of the drive axis O1.

[0072] As shown in Figure 1, the driving scroll 30 is housed in the scroll chamber 65. The driving scroll 30 is made of an aluminum alloy and includes a driving end plate 31, a driving scroll 33, a driving peripheral wall 35, a cover body 37, and a case 39.

[0073] The drive end plate 31 extends in a generally disk-like 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 to the front-to-rear direction. The drive end plate 31 has a first front surface 311 facing forward and a first rear surface 312 located opposite the first front surface 311 and facing rearward.

[0074] 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. A discharge reed valve 57 and a retainer 58 are fixed to the first front surface 311 of the drive end plate 31 with fixing bolts 59. This allows the discharge reed valve 57 to open and close the discharge port 32. The retainer 58 can adjust the opening degree of the discharge reed valve 57.

[0075] The drive scroll 33 is integral with the drive end plate 31 and protrudes rearward from the first rear surface 312, i.e., parallel to the drive axis O1 and the driven axis O2, toward the driven scroll 40. Although not shown in detail, the drive scroll 33 has a spiral center located on the central side of the drive end plate 31 and protrudes outward from the spiral center in a spiral shape.

[0076] The drive circumferential wall 35 is formed in a cylindrical shape centered on the drive axis O1 and extending parallel to the drive axis O1 and the driven axis O2. The front end of the drive circumferential wall 35 is integral with the outer periphery of the drive end plate 31. As a result, the drive circumferential wall 35 surrounds the drive scroll 33 from the outside and protrudes cylindrically rearward from the first rear surface 312. Although not shown, the outer periphery of the drive scroll 33 is connected to the inner periphery of the drive circumferential wall 35.

[0077] 2, the cover body 37 has a wall portion 37a, an inner cylindrical portion 37b, a connecting portion 37c, and an outer cylindrical portion 37d. The wall portion 37a extends in a generally plate-like shape in the radial direction of the cover body 37. 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 rearward.

[0078] The wall portion 37a is formed with a recess 373 and an intake port 374. 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.

[0079] The suction port 374 is disposed radially outward of the cover body 37 relative to the recess 373. The suction 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.

[0080] Additionally, a plurality of rings 22 are attached to the wall portion 37a between the recess 373 and the intake port 374. Although not shown in detail, the rings 22 are disposed at equal intervals around the circumferential direction of the recess 373 while facing forward, and surround the recess 373 from the outside. In this embodiment, the number of rings 22 is six. One of the six rings 22 is shown in Figures 1 and 2. The same applies to Figure 3, which will be described later.

[0081] The inner cylindrical portion 37b is formed radially inward of the stator 17 of the cover body 37 and extends cylindrically rearward in the direction of the drive axis O1. The inner diameter of the inner cylindrical portion 37b is larger than the first diameter portion 641 of the protrusion 64 and is formed to be approximately the same as the outer diameter of the first radial ball bearing 51.

[0082] The connecting portion 37c is located between the wall portion 37a and the inner cylindrical portion 37b and is integral with the wall portion 37a and the inner cylindrical portion 37b. The connecting portion 37c connects the wall portion 37a and the inner cylindrical portion 37b while increasing in diameter from the inner cylindrical portion 37b toward the wall portion 37a in the direction of the drive axis O1. This allows the outer peripheral surface of the inner cylindrical portion 37b to be continuous with the second rear surface 372 of the wall portion 37a through the connecting portion 37c.

[0083] An insertion hole 375 is formed in the cover body 37 at a location inside the connecting portion 37c. The insertion hole 375 extends in the direction of the drive axis O1 and connects the inner cylindrical portion 37b and the recess 373.

[0084] The outer cylindrical portion 37d is integral with the wall portion 37a at the outer peripheral edge thereof. As a result, the outer cylindrical portion 37d is connected to the wall portion 37a and extends cylindrically from the wall portion 37a rearward in the direction of the drive axis O1. The outer diameter of the outer cylindrical portion 37d is substantially the same as the outer diameter of the drive circumferential wall 35 and the outer diameter of the rotor 11.

[0085] The inner diameter of the outer cylindrical portion 37d is larger than those of the inner cylindrical portion 37b and the connecting portion 37c. As a result, in the cover body 37, the inner cylindrical portion 37b and the connecting portion 37c are disposed on the inner peripheral side of the outer cylindrical portion 37d while being spaced apart from the outer cylindrical portion 37d in the radial direction of the cover body 37. In this manner, in the cover body 37, the wall portion 37a, the inner cylindrical portion 37b, the connecting portion 37c, and the outer cylindrical portion 37d form a storage portion 38. The storage portion 38 is annular in shape with a bottom and an open rearward end. The storage portion 38 is in communication with the suction port 374.

[0086] Additionally, a plurality of second bolt holes 376 are formed in the outer cylindrical portion 37d. Each second bolt hole 376 penetrates the outer cylindrical portion 37d in the direction of the drive axis O1. Although not shown, the number of second bolt holes 376 is equal to the number of first bolt holes 11a formed in the rotor 11. 1 to 3 illustrate only one of the plurality of first bolt holes 11a and one of the plurality of second bolt holes 376.

[0087] The cover body 37 has the front end of the outer cylindrical portion 37d 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 37d. In this state, first bolts 34a are inserted into the first bolt holes 11a and the second bolt holes 376 from the rotor 11 side and 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 between them. As a result, the drive scroll 30 is integral with the rotor 11.

[0088] 1, the case 39 is a cylindrical member with a bottom and an outer peripheral wall 39a and a front wall 39b. The outer peripheral wall 39a is cylindrical and has its center on the drive axis O1. The outer diameter of the outer peripheral wall 39a is approximately the same as the outer diameter of the drive peripheral wall 35.

[0089] The front wall 39b is located at the front end of the case 39. The front wall 39b extends in a generally disk-like shape, perpendicular to the drive axis O1 and the driven axis O2. The outer peripheral edge of the front wall 39b is connected to the front end of the outer peripheral wall 39a. A boss 39d is formed on the front wall 39b. The boss 39d is an example of the "supported member" of the present invention. The boss 39d is integrally formed at 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 39d is generally the same as the inner diameter of the second radial ball bearing 52 and the inner diameter of the shaft seal member 63. A discharge passage 390 is formed in the boss 39d. The discharge passage 390 penetrates the boss 39d in the direction of the drive axis O1.

[0090] Third bolt holes 39e are formed in the outer peripheral wall 39a and the front wall 39b. The third bolt holes 39e penetrate the outer peripheral wall 39a and the front wall 39b in the direction of the drive axis O1. Although not shown, a plurality of third bolt holes 39e are formed in the outer peripheral wall 39a and the front wall 39b. One of the plurality of third bolt holes 39e is shown in FIG. 1.

[0091] The rear surface of the outer peripheral wall 39a of the case 39 abuts against the front end of the driving peripheral wall 35. In this state, the second bolts 34b are inserted into the third bolt holes 39e, respectively, and the second bolts 34b are screwed into the driving peripheral wall 35. In this way, the case 39 of the driving scroll 30 is fixed to the driving peripheral wall 35.

[0092] By fixing the case 39 to the driving peripheral wall 35 in this manner, a discharge chamber 14 is formed inside the peripheral wall 39a between the front wall 39b of the case 39 and the driving end plate 31. The discharge chamber 14 communicates with the discharge port 32 and also with the discharge passage 390.

[0093] The driven scroll 40 is also made of an aluminum alloy. The driven scroll 40 has a driven end plate 41 and a driven scroll 43.

[0094] The driven end plate 41 has a generally disk-like shape and extends 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 rearward.

[0095] An accommodating recess 15 is formed in the driven end plate 41. The accommodating recess 15 is located in the center of the driven end plate 41. The accommodating recess 15 is recessed in a cylindrical shape centered on the driven axis O2 and extending forward from the third rear surface 412 of the driven end plate 41. As a result, the accommodating recess 15 faces the rear of the driven end plate 41, and ultimately faces the first diameter portion 641 of the protrusion 64.

[0096] As shown in FIG. 2 , a driven shaft 16 is provided in the accommodation recess 15. The driven shaft 16 has a bushing 53 and a driven pin 55. The bushing 53 is accommodated in the accommodation recess 15 via the sliding bearing 13. The driven pin 55 is inserted through the bushing 53. More specifically, the driven pin 55 is inserted through the bushing 53 at a position eccentric to the center of the bushing 53, i.e., the driven axis O2. The driven pin 55 protrudes rearward from the bushing 53 and, therefore, from the driven end plate 41.

[0097] Furthermore, a rotation-preventing pin 21 is fixed to the driven end plate 41 at a position facing the ring 22. The rotation-preventing pin 21 protrudes rearward from the third rear surface 412. Six rotation-preventing pins 21 are fixed to the driven end plate 41, the same number as the number of rings 22. Also, only one of the six rotation-preventing pins 21 is shown in FIGS. 1 to 3.

[0098] These rotation-preventing pins 21 and rings 22 constitute the driven mechanism 20. The number of rotation-preventing pins 21 and rings 22 can be appropriately designed as long as there are three or more of each.

[0099] 1, the driven spiral 43 is integral with the driven end plate 41 and extends forward from the third front surface 411 of the driven end plate 41 in parallel with the drive axis O1 and the driven axis O2. The driven spiral 43 has a center on the center side of the driven end plate 41 and extends spirally outward from the center.

[0100] In this compressor, the driven scroll 40 is housed within the driving scroll 30, more specifically, in a location in the driving scroll 30 between the driving scroll 33 and the driving peripheral wall 35 and the cover body 37. The driving scroll 33 and the driven scroll 43 are meshed with each other. As a result, the driving scroll 33 and the driven scroll 43 face each other to form a compression chamber 12.

[0101] Furthermore, a suction section 30a is formed between the driving peripheral wall 35 and the driven scroll 40. That is, the driving scroll 33 and the driven scroll 43 are located within the suction section 30a. The suction section 30a is separated from the scroll chamber 65 by the driving peripheral wall 35 and the cover body 37, and is also separated from the discharge chamber 14 by the driving end plate 31. The suction section 30a also communicates with the suction port 374. As a result, the suction section 30a communicates with the accommodation section 38 through the suction port 374.

[0102] Furthermore, by accommodating the driven scroll 40 within the driving scroll 30, the second front surface 371 of the wall portion 37a and the third rear surface 412 of the driven end plate 41 face each other in the direction of the drive axis O1. Each rotation-preventing pin 21 enters each ring 22. In this manner, the driving scroll 30 and the driven scroll 40 are assembled in the front-to-rear direction, and the driving scroll 30 and the driven scroll 40 form a scroll compression section 100. Strictly speaking, after the driving scroll 33 and the driven scroll 43 are engaged with each other and the rotation-preventing pins 21 enter each ring 22, the cover body 37 of the driving scroll 30 is fixed to the driving peripheral wall 35 and the rotor 11.

[0103] Furthermore, by assembling the driving scroll 30 and the driven scroll 40 together, the accommodating recess 15 of the driven end plate 41 and the driven shaft portion 16 face the recess 373 of the cover body 37 .

[0104] As shown in FIG. 2 , the driving scroll 30 is disposed forward of the stator core 17a within the scroll chamber 65. In addition, in the driving scroll 30, the inner cylindrical portion 37b of the cover body 37 is inserted into the inner circumferential side of the first coil end 171. In this state, the first radial ball bearing 51 is inserted into the inner cylindrical portion 37b. As a result, the inner cylindrical portion 37b, and therefore the cover body 37, are rotatably supported around the drive axis O1 by the first radial ball bearing 51 relative to the first radial portion 641 of the protruding body 64. The accommodating portion 38 is in communication with the scroll chamber 65. The front portion of the first radial portion 641 is inserted into the insertion hole 375.

[0105] Here, since the cover body 37 is rotatably supported on the first radial portion 641, in this compressor, the compression chamber 12, including the stator core 17a, is located forward of the electric motor 10 in the direction of the drive axis O1. More specifically, the compression chamber 12 is located forward of the electric motor 10 in the direction of the drive axis O1, with the cover body 37 and the driven end plate 41 sandwiched between them.

[0106] As described above, the first radial portion 641 forms the front portion of the protrusion 64, and the second radial portion 642 forms the rear portion of the protrusion 64. The stator core 17a is fixed to the outer peripheral surface of the second radial portion 642. Therefore, the inner cylindrical portion 37b is rotatably supported by the first radial portion 641 via the first radial ball bearing 51, and the cover body 37 is rotatably supported by the protrusion 64 in front of the stator core 17a. In other words, the cover body 37 is rotatably supported by the protrusion 64 around the drive axis O1 on the compression chamber 12 side of the stator core 17a.

[0107] Furthermore, the inner cylindrical portion 37b that extends into the inner peripheral side of the first coil end 171 faces the second radial portion 642 in the direction of the drive axis O1. Here, with the cover body 37 rotatably supported by the protrusion 64, the inner cylindrical portion 37b and the first coil end 171 are spaced apart in the radial direction of the cover body 37.

[0108] Furthermore, by rotatably supporting the cover body 37 on the protrusion 64 in this manner, the wall portion 37a of the cover body 37 faces the first coil end 171 from the front. Furthermore, the outer cylindrical portion 37d of the cover body 37 is located outside the first coil end 171 in the radial direction of the cover body 37. In this case, the outer cylindrical portion 37d and the first coil end 171 are spaced apart in the radial direction of the cover body 37. In other words, by rotatably supporting the cover body 37 on the protrusion 64, the first coil end 171 is accommodated in the accommodation portion 38.

[0109] Furthermore, in this compressor, when the cover body 37 is rotatably supported by the protrusion 64, the first radial portion 641, the first radial ball bearing 51, the inner cylindrical portion 37b, the first coil end 171, and the outer cylindrical portion 37d are arranged in this order from the drive axis O1 side toward the outside in the radial direction of the cover body 37. The first radial portion 641, the first radial ball bearing 51, the inner cylindrical portion 37b, the first coil end 171, and the outer cylindrical portion 37d are arranged while overlapping each other in the radial direction.

[0110] 1 , in the driving scroll 30, the boss 39d of the case 39 is inserted through the second radial ball bearing 52 and the shaft seal member 63. As a result, the boss 39d is rotatably supported around the drive axis O1 relative to the support portion 66 via the second radial ball bearing 52 and the second elastic body 67b. In this way, the driving scroll 30 is disposed in the scroll chamber 65 and is supported by the housing 6 by both the protrusion 64 and the support portion 66 so as to be rotatable around the drive axis O1.

[0111] Furthermore, since the case 39 is supported by the support portion 66, the discharge passage 390 faces the discharge communication port 69 from the rear. As a result, the discharge chamber 14 and the discharge communication port 69 communicate with each other through the discharge passage 390. The shaft seal member 63 seals the discharge passage 390 and the discharge communication port 69 from the scroll chamber 65.

[0112] On the other hand, in the driven scroll 40, the driven pin 55 of the driven shaft portion 16 is inserted into the pin hole 4. As a result, the driven scroll 40 is disposed in the scroll chamber 65 and rotatably supported about the driven axis O2 with respect to the first radial portion 641. Furthermore, by being rotatably supported by the first radial portion 641 in this manner, the driven scroll 40 is also rotatably supported by the protruding body 64 forward of the stator core 17a. In other words, the driven scroll 40 is rotatably supported about the driven axis O2 by the protruding body 64 on the compression chamber 12 side of the stator core 17a. Furthermore, by inserting the driven pin 55 into the pin hole 4, the driven scroll 40 is rotatably supported about the driven axis O2 by the first radial portion 641 inward of the inner cylindrical portion 37b in the radial direction of the cover body 37. Unlike the driving scroll 30, the driven scroll 40 is supported by the housing 6 only by the protrusion 64 so as to be rotatable about the driven axis O2.

[0113] In addition, in this compressor, the stator core 17a, the first radial ball bearing 51, and the bushing 53 of the driven shaft portion 16 are arranged in this order from the first housing cover 61 side toward the compression chamber 12 side in the direction of the drive axis O1.

[0114] In the compressor configured as described above, as indicated 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 through the suction port 68. When the electric motor 10 is operated and the rotor 11 rotates, the rotation of the rotor 11 is transmitted to the driving scroll 30, causing the driving scroll 30 to rotate about the drive axis O1 within the scroll chamber 65. In other words, the driving scroll 30 and the rotor 11 rotate integrally. At this time, in the driven mechanism 20, each rotation-preventing pin 21 slides against the inner circumferential surface of each ring 22, causing the rings 22 to rotate relatively about the center of the rotation-preventing pin 21. In this way, the driven mechanism 20 transmits the torque of the driving scroll 30 to the driven scroll 40.

[0115] As a result, the driven scroll 40 is rotated around the driven axis O2 by the driving scroll 30 and the driven mechanism 20. At this time, the driven mechanism 20 restricts the rotation of the driven scroll 40. As a result, the driven scroll 40 revolves around the driven axis O2 relative to the driving scroll 30. Then, as the driving scroll 33 and the driven scroll 43 each rotate within the suction section 30a, the driving scroll 33 and the driven scroll 43 change the volume of the compression chamber 12.

[0116] 1 and 2, the refrigerant drawn into the scroll chamber 65 flows between the rotor 11 and the stator 17 and reaches the accommodating portion 38. The refrigerant drawn into the scroll chamber 65 also reaches the accommodating portion 38 by flowing through slits formed in the stator core 17a. The refrigerant drawn into the scroll chamber 65 also reaches the accommodating portion 38 by flowing through slots (not shown) formed in the stator core 17a that accommodate the windings 17b and the gaps between the windings 17b. In this way, the refrigerant in the accommodating portion 38 is drawn into the compression chamber 12 from the suction port 374 through the suction portion 30a.

[0117] The compression chambers 12 compress the refrigerant by reducing their volumes while trapping the refrigerant therein due to the rotational drive of the drive scroll 30 and the driven rotation of the driven scroll 40. The high-pressure refrigerant compressed to discharge pressure is discharged from the discharge port 32 to the discharge chamber 14, and then discharged to the outside of the compressor via the discharge passage 390 and the discharge communication port 69. At this time, in this compressor, the shaft seal member 63 seals the discharge passage 390 and the discharge communication port 69 from the scroll chamber 65, preventing the refrigerant flowing from the discharge passage 390 toward the discharge communication port 69 from circulating within the scroll chamber 65.

[0118] In this compressor, the stator core 17a is fixed to the second diameter portion 642 of the protrusion 64. Therefore, in this compressor, torque fluctuations of the electric motor 10 caused by the compression of the refrigerant in the compression chamber 12 are inevitably transmitted from the stator core 17a to the protrusion 64 during operation.

[0119] Furthermore, in this compressor, the inner cylindrical portion 37b of the cover body 37 is rotatably supported by the first radial portion 641 of the protruding body 64. Therefore, in this compressor, torque fluctuations of the driving scroll 30 caused by the compression of the refrigerant in the compression chamber 12 are inevitably transmitted to the protruding body 64 during operation. Furthermore, in this compressor, the driven scroll 40 is also rotatably supported by the first radial portion 641, so torque fluctuations of the driven scroll 40 caused by the compression of the refrigerant in the compression chamber 12 are also inevitably transmitted to the protruding body 64 during operation. These torque fluctuations transmitted to the protruding body 64 cause a moment to act on the protruding body 64 in a direction that twists the protruding body 64.

[0120] Here, in this compressor, because both the driving scroll 30 and the driven scroll 40 rotate to compress the refrigerant, the phase of the torque fluctuation of the electric motor 10 transmitted from the stator core 17a to the protruding body 64 during operation is opposite to the phase of the torque fluctuation transmitted from the driving scroll 30 and the driven scroll 40 to the protruding body 64. As a result, in this compressor, the torque fluctuation transmitted from the stator core 17a to the protruding body 64 and the torque fluctuation transmitted from the driving scroll 30 and the driven scroll 40 to the protruding body 64 cancel each other out at the protruding body 64. Therefore, in this compressor, the torque fluctuation transmitted to the protruding body 64 during operation can be reduced. As a result, in this compressor, the moment acting on the protruding body 64 can be reduced.

[0121] Furthermore, in this compressor, the protrusion 64, including the retaining portion 611, is a separate part from the first housing cover 61, and the protrusion 64 is attached to the first housing cover 61 by a clearance fit between the retaining portion 611 and the protrusion 64. For this reason, torque fluctuations transmitted from the stator core 17a, the driving scroll 30, and the driven scroll 40 to the protrusion 64, and ultimately moments acting on the protrusion 64, are less likely to be transmitted to the first housing cover 61.

[0122] Therefore, in this compressor, it is possible to minimize the moment transmitted from the protrusion 64 to the first housing cover 61. As a result, in this compressor, it is possible to effectively suppress vibration of the first housing cover 61, and ultimately the housing 6, due to the moment during operation.

[0123] Furthermore, because the moment transmitted to the housing 6 can be reduced in this way, in this compressor, it is not necessary to excessively increase the rigidity of the housing main body 60 and the first and second housing covers 61, 62 in order to suppress vibration of the housing 6 during operation. Therefore, in this compressor, it is difficult for the housing 6 to be large.

[0124] Therefore, the compressor of the first embodiment is quiet and can be prevented from becoming large in size.

[0125] In particular, in this compressor, the inner cylindrical portion 37b of the cover body 37 is rotatably supported on the first radial portion 641 via the first radial ball bearing 51. Therefore, in this compressor, the first radial ball bearing 51 can suitably reduce torque fluctuations that are inevitably transmitted from the driving scroll 30 to the protruding body 64.

[0126] Furthermore, in this compressor, the boss 39d of the case 39 is rotatably supported on the support portion 66 via the second radial ball bearing 52. As a result, in this compressor, torque fluctuations of the driving scroll 30 are inevitably transmitted through the boss 39d to the support portion 66 and ultimately to the second housing cover 62, but the torque fluctuations transmitted from the boss 39d to the support portion 66 can be suitably reduced by the second radial ball bearing 52. Therefore, in this compressor, although a moment in a direction that twists the boss 39d inevitably acts on the boss 39d during operation, the moment transmitted from the boss 39d to the housing cover 62 can be reduced. Therefore, in this compressor, vibration of the second housing cover 62 can also be suitably suppressed.

[0127] Furthermore, in this compressor, a first elastic body 67a is provided between the second diameter portion 642 of the protrusion 64 and the retaining portion 611, and a second elastic body 67b is provided between the support portion 66 and the second radial ball bearing 52. As a result, the first elastic body 67a can elastically deform to preferably prevent a moment acting on the protrusion 64 from being transmitted from the protrusion 64 to the retaining portion 611 and ultimately to the first housing cover 61. Similarly, the second elastic body 67b can elastically deform to preferably prevent a moment acting on the boss 39d from being transmitted from the second radial ball bearing 52 to the support portion 66 and ultimately to the second housing cover 62. In this respect as well, the housing 6 is less likely to vibrate in this compressor.

[0128] The first elastic body 67a and the stator core 17a overlap in the radial direction of the housing 6 within the range of region X1 shown in Fig. 2. That is, the first elastic body 67a is sandwiched between the retaining portion 611 and the second radial portion 642 of the protruding body 64, and a portion of the first elastic body 67a overlaps with the stator core 17a in the radial direction of the housing 6. This makes it possible to ensure the length of the first elastic body 67a in the direction of the drive axis O1 and the contact area between the retaining portion 611, the protruding body 64, and the first elastic body 67a, while suitably preventing the compressor from becoming large in size in the direction of the drive axis O1, compared to a case in which the first elastic body 67a is spaced apart from the stator core 17a in the direction of the drive axis O1 so that the first elastic body 67a and the stator core 17a do not overlap in the radial direction.

[0129] In this compressor, the cover body 37 and the driven scroll 40 are each rotatably supported by the first diameter portion 641 of the protrusion 64. This makes it possible for the cover body 37 and the driven scroll 40 to be suitably supported by the protrusion 64 on the compression chamber 12 side relative to the stator core 17a.

[0130] Furthermore, in this compressor, the driven pin 55 of the driven shaft portion 16 is inserted into the pin hole 4, so that the driven scroll 40 is rotatably supported by the first radial portion 641 radially inward of the inner cylindrical portion 37b of the cover body 37 about the driven axis O2. Also, in this compressor, the stator core 17a, the first radial ball bearing 51, and the bushing 53 of the driven shaft portion 16 are arranged in this order from the first housing cover 61 side toward the compression chamber 12 side in the direction of the drive axis O1. Also, in this compressor, the driven pin 55, the first radial portion 641, the first radial ball bearing 51, the inner cylindrical portion 37b, the first coil end 171, and the outer cylindrical portion 37d are arranged so as to overlap each other in the radial direction of the cover body 37. As a result, in this compressor, it is possible to suitably prevent the housing 6 from becoming large in the direction of the drive axis O1.

[0131] Furthermore, in this compressor, the second diameter portion 642 of the protrusion 64 is formed to have a larger diameter than the retaining portion 611. Therefore, by inserting the retaining portion 611 into the second diameter portion 642, the second diameter portion 642 and the retaining portion 611 can suitably ensure the rigidity of the protrusion 64. Furthermore, in the protrusion 64, the first diameter portion 641 has a smaller diameter than the second diameter portion 642, so that in this compressor, it is possible to prevent the first radial ball bearing 51 and the inner cylindrical portion 37b from becoming larger in diameter.

[0132] Furthermore, in this compressor, the stator 17 and the rotor 11 can be suitably cooled by the refrigerant in the scroll chamber 65 as it is drawn into the suction port 374. In particular, in this compressor, the first coil end 171 is disposed within the accommodation portion 38, and therefore the first coil end 171 can be sufficiently cooled by the refrigerant that has reached the accommodation portion 38.

[0133] 3, in a compressor according to a second embodiment, a protrusion 71 is attached to the first housing cover 61 instead of the protrusion 64. In this compressor, the elastic body 67 is composed only of the second elastic body 67b (see FIG. 1).

[0134] 3, in this compressor, a holding portion 612 is formed on the first housing cover 61 instead of the holding portion 611. The holding portion 612 protrudes cylindrically from the center of the front surface 61a of the first housing cover 61 forward in the direction of the drive axis O1. The holding portion 612 has an outer diameter of a second length L2. A plurality of fitting holes 612b are formed in the front end surface 612a of the holding portion 612.

[0135] The protrusion 71 is formed as a separate part from the first housing cover 61. The protrusion 71 is made of steel and has a solid cylindrical shape. The protrusion 71 is composed of a first radial portion 711 and a second radial portion 712. The first radial portion 711 forms the front portion of the protrusion 71. The first radial portion 711 has a configuration similar to that of the first radial portion 641 in the compressor of the first embodiment. As a result, the length of the outer diameter of the first radial portion 711 is formed to be a first length L1. Furthermore, a pin hole 4 is formed in the first radial portion 711.

[0136] The second diameter portion 712 constitutes the rear portion of the protrusion 71 and is integral with the first diameter portion 711. The second diameter portion 712 has an outer diameter of a second length L2. As a result, the second diameter portion 712 is formed to have a larger diameter than the first diameter portion 711. The second diameter portion 712 is also formed to have the same diameter as the holding portion 612.

[0137] The same number of connection pins 71c as the above-mentioned fitting holes 612b are fixed to the second diameter portion 712. In this case, each connection pin 71c is fixed to the second diameter portion 712 in a state where it protrudes rearward from a rear end surface 713 of the second diameter portion 712. The numbers of fitting holes 612b and connection pins 71c can be designed as appropriate.

[0138] In the protrusion 71, the connection pins 71c are fitted into the fitting holes 612b, thereby positioning the retaining portion 612 and the protrusion 71 and fixing the protrusion 71 to the retaining portion 612. In this manner, in this compressor, the protrusion 71 is attached to the first housing cover 61, and the first housing cover 61 supports the protrusion 71. The protrusion 71 protrudes forward beyond the retaining portion 612 within the scroll chamber 65.

[0139] In this compressor, the stator core 17a is fixed to the second radial portion 712. Furthermore, the inner cylindrical portion 37b of the cover body 37 is rotatably supported about the drive axis O1 relative to the first radial portion 711 via the first radial ball bearing 51. The driven scroll 40 is rotatably supported about the driven axis O2 relative to the first radial portion 711. As a result, in this compressor as well, the cover body 37 and the driven scroll 40 are rotatably supported by the protruding body 71 forward of the stator core 17a. The other configurations of this compressor are similar to those of the compressor of Example 1, and the same components are designated by the same reference numerals, and detailed description of the configurations will be omitted.

[0140] As in the compressor of Example 1, in this compressor, torque fluctuations transmitted from the stator core 17a to the protruding body 71 and torque fluctuations transmitted from the driving scroll 30 and the driven scroll 40 to the protruding body 71 are offset in the protruding body 71. Therefore, torque fluctuations transmitted from the stator core 17a, the driving scroll 30, and the driven scroll 40 to the protruding body 71, and consequently, moments acting on the protruding body 71, are less likely to be transmitted to the retaining portion 612 and further to the first housing cover 61. Furthermore, because the protruding body 71 is a separate part from the retaining portion 612, the moment acting on the protruding body 71 is less likely to be transmitted to the first housing cover 61 than when the protruding body 71 is formed integrally with the retaining portion 612, i.e., the first housing cover 61. In this way, this compressor can achieve the same function as the compressor of Example 1.

[0141] (Embodiment 3) As shown in Fig. 4 , in a compressor of embodiment 3, the housing 6 has a first housing cover 81 instead of the first housing cover 61. The first housing cover 81 is also an example of the "first wall" in the present invention. As a result, in this compressor, the housing 6 is composed of a housing main body 60, the first housing cover 81, and a second housing cover 62 (see Fig. 1 ). Then, as in the compressor of embodiment 1, the housing main body 60, the first housing cover 81, and the second housing cover 62 are fixed in the direction of the drive axis O1, thereby forming a scroll chamber 65 in the housing 6.

[0142] 4, in this compressor, a protrusion 73 is provided inside the scroll chamber 65. Furthermore, in this compressor, the elastic body 67 is composed of a first elastic body 67c and a second elastic body 67b (see FIG. 1).

[0143] The first housing cover 81 shown in Figure 4 is made of an aluminum alloy. The first housing cover 81 is located at the rear end of the housing main body 60. The first housing cover 81 is generally disk-shaped and centered on the drive axis O1, extending in the radial direction of the housing 6. The first housing cover 81 has a front surface 81a facing forward and a rear surface 81b facing rearward and located on the opposite side of the front surface 81a. The first housing cover 81 may also be made of steel.

[0144] The first housing cover 81 is also formed with a plurality of fitting holes 810. A first connecting pin 811 is inserted into and fixed to each fitting hole 810. At this time, each first connecting pin 811 is fixed to each fitting hole 810 in a state where it protrudes forward from the front surface 81 a.

[0145] The first elastic body 67c is made of synthetic rubber. The first elastic body 67c is formed in a disk shape with a predetermined thickness in the direction of the drive axis O1. More specifically, the first elastic body 67c is formed in a disk shape with approximately the same diameter as a flange portion 733 of the protrusion 73 (described later). The first elastic body 67c is attached to the first housing cover 81 by inserting the first connecting pins 811, so that the first elastic body 67c abuts against the front surface 81a of the first housing cover 81. This allows the first housing cover 81 to hold the first elastic body 67c. The first elastic body 67c is disposed in the scroll chamber 65 and is positioned forward of the first housing cover 81. The material and thickness of the first elastic body 67c can be designed as appropriate.

[0146] The protrusion 73 is formed as a separate part from the first housing cover 81. The protrusion 73 is made of steel and has a solid cylindrical shape. The protrusion 73 is composed of a first radial portion 731, a second radial portion 732, and a flange portion 733. The first radial portion 731 forms the front portion of the protrusion 73. The first radial portion 731 has a configuration similar to that of the first radial portion 641 in the compressor of the first embodiment. As a result, the length of the outer diameter of the first radial portion 731 is formed to be a first length L1. Furthermore, a pin hole 4 is formed in the first radial portion 731.

[0147] The second diameter portion 732 is located rearward of the first diameter portion 731 and is integral with the first diameter portion 731. As a result, the second diameter portion 732 constitutes the central portion of the protrusion 73. The second diameter portion 732 has an outer diameter length of the second length L2. As a result, the second diameter portion 732 is formed to have a larger diameter than the first diameter portion 731. The flange portion 733 is located rearward of the second diameter portion 732 and is integral with the second diameter portion 732. As a result, the flange portion 733 constitutes the rear portion of the protrusion 73. The flange portion 733 is formed to have a larger diameter than the second diameter portion 732.

[0148] The protrusion 73 is positioned forward of the first elastic body 67c, causing the flange portion 733 and the first elastic body 67c to abut against each other in the direction of the drive axis O1. The protrusion 73 is attached to the first elastic body 67c by inserting a plurality of second connecting pins 734 through the flange portion 733 and the first elastic body 67c from the flange portion 733 side. The first elastic body 67c is spaced apart in the direction of the drive axis O1 so that the first connecting pins 811 and the second connecting pins 734 do not abut against each other. Thus, the protrusion 73 is attached to the first housing cover 81 via the first elastic body 67c. As a result, in this compressor, the first housing cover 81 supports the protrusion 73 via the first elastic body 67c.

[0149] In this compressor, the stator core 17a is fixed to the second radial portion 732. Furthermore, the inner cylindrical portion 37b of the cover body 37 is rotatably supported around the drive axis O1 relative to the first radial portion 731 via the first radial ball bearing 51. The driven scroll 40 is rotatably supported around the driven axis O2 relative to the first radial portion 731. As a result, in this compressor as well, the cover body 37 and the driven scroll 40 are rotatably supported by the protruding body 73 forward of the stator core 17a. Other configurations of this compressor are similar to those of the compressor of Example 1.

[0150] In this compressor, torque fluctuations transmitted from the stator core 17a to the protruding body 73 and torque fluctuations transmitted from the driving scroll 30 and the driven scroll 40 to the protruding body 73 are offset at the protruding body 73. The protruding body 73 is a separate component from the first housing cover 81, and is attached to the first housing cover 81 with the first elastic body 67c interposed therebetween. Therefore, in this compressor, torque fluctuations acting on the protruding body 73, and in turn, moments acting on the protruding body 73, are suitably absorbed by the first elastic body 67c as the first elastic body 67c elastically deforms between the protruding body 73 and the first housing cover 81. As a result, in this compressor, moments acting on the protruding body 73 are less likely to be transmitted to the first housing cover 81, and the housing 6 is less likely to vibrate. Other functions of this compressor are similar to those of the compressor of the first embodiment.

[0151] 5, in a compressor of the fourth embodiment, a protrusion 74 is provided in the scroll chamber 65 instead of the protrusion 73 in the compressor of the third embodiment. In addition, in this compressor, the elastic body 67 is composed of a first elastic body 67d and a second elastic body 67b (see FIG. 1).

[0152] As shown in FIG. 5 , the first elastic body 67d is made of synthetic rubber. The first elastic body 67d is composed of a large diameter portion 671 and a small diameter portion 672. The large diameter portion 671 is formed in a disk shape having a predetermined thickness in the direction of the drive axis O1. More specifically, the large diameter portion 671 is formed in a disk shape having approximately the same diameter as a flange portion 743 of the protrusion 74, which will be described later. The small diameter portion 672 is formed integrally with the large diameter portion 671. The small diameter portion 672 is formed to have a smaller diameter than the large diameter portion 671 and extends cylindrically forward from the large diameter portion 671 in the direction of the drive axis O1.

[0153] The first elastic body 67d is attached to the first housing cover 81 in a state of contact with the front surface 81a of the first housing cover 81 by inserting each of the first connecting pins 811 into the large diameter portion 671. In this way, the first housing cover 81 holds the first elastic body 67d. The first elastic body 67d is disposed in the scroll chamber 65 in a state of being located forward of the first housing cover 81. Note that the material of the first elastic body 67d, as well as the plate thickness of the large diameter portion 671 and the length of the small diameter portion 672 in the direction of the drive axis O1, can be designed as appropriate.

[0154] The protrusion 74 is formed as a separate part from the first housing cover 81. The protrusion 74 is made of steel. The protrusion 74 is composed of a first radial portion 741, a second radial portion 742, and a flange portion 743. The first radial portion 741 constitutes the front portion of the protrusion 74. The first radial portion 741 has a configuration similar to that of the first radial portion 641 in the compressor of the first embodiment. As a result, the length of the outer diameter of the first radial portion 741 is formed to be a first length L1. In addition, a pin hole 4 is formed in the first radial portion 741.

[0155] The second diameter portion 742 is formed in a cylindrical shape with a bottom that is open at the rear. The second diameter portion 742 has an outer diameter length of a second length L2. As a result, the second diameter portion 742 is formed with a larger diameter than the first diameter portion 741. The inner diameter of the second diameter portion 742 is also slightly smaller than the outer diameter of the small diameter portion 672 of the first elastic body 67d.

[0156] The flange portion 743 is located rearward of the second diameter portion 742 and is integral with the second diameter portion 742. As a result, the flange portion 743 forms the rear portion of the protrusion 74. The flange portion 743 is formed in an annular shape with a diameter larger than that of the second diameter portion 742. The inner diameter of the flange portion 743 is the same as the inner diameter of the second diameter portion 742. Therefore, the inner diameter of the flange portion 743 is also slightly smaller than the outer diameter of the small diameter portion 672 of the first elastic body 67d.

[0157] The protrusion 74 has the small diameter portion 672 of the first elastic body 67d inserted into the flange portion 743 and the second diameter portion 742. Because the inner diameters of the flange portion 743 and the second diameter portion 742 are slightly smaller than the outer diameter of the small diameter portion 672, the small diameter portion 672 is inserted into the flange portion 743 and the second diameter portion 742 while being slightly reduced in diameter due to elastic deformation. The protrusion 74 also abuts the flange portion 743 and the large diameter portion 671 of the first elastic body 67d in the direction of the drive axis O1. Thus, the protrusion 74 is attached to the first housing cover 81 via the first elastic body 67d. As a result, in this compressor, the first housing cover 81 supports the protrusion 74 via the first elastic body 67d. The first elastic body 67d holds the protrusion 74 from inside the protrusion 74 using the small diameter portion 672.

[0158] In this compressor, the stator core 17a is fixed to the outer peripheral surface of the second radial portion 742. Furthermore, the inner cylindrical portion 37b of the cover body 37 is rotatably supported around the drive axis O1 relative to the first radial portion 741 via the first radial ball bearing 51. The driven scroll 40 is rotatably supported around the driven axis O2 relative to the first radial portion 741. As a result, in this compressor as well, the cover body 37 and the driven scroll 40 are rotatably supported by the protruding body 74 forward of the stator core 17a. The other configurations of this compressor are similar to those of the compressor of Example 3.

[0159] In this compressor, torque fluctuations transmitted from the stator core 17a to the protruding body 74 and torque fluctuations transmitted from the driving scroll 30 and the driven scroll 40 to the protruding body 74 cancel each other out at the protruding body 74. Furthermore, the protruding body 74 is a separate component from the first housing cover 81, and the protruding body 74 is attached to the first housing cover 81 with the first elastic body 67d interposed therebetween. Therefore, in this compressor, torque fluctuations acting on the protruding body 74, and therefore moments acting on the protruding body 74, are suitably absorbed by the first elastic body 67d as the first elastic body 67d elastically deforms between the protruding body 74 and the first housing cover 81. As a result, in this compressor, moments acting on the protruding body 74 are less likely to be transmitted to the first housing cover 81, and the housing 6 is less likely to vibrate.

[0160] Furthermore, in this compressor, the small diameter portion 672 of the first elastic body 67d is inserted into the flange portion 743 and the second diameter portion 742 while being reduced in diameter by elastic deformation. As a result, in this compressor, it is not necessary to attach the protrusion 74 to the first elastic body 67d using multiple second connecting pins 734 as in the compressor of Example 3. Furthermore, in this compressor, the first elastic body 67d holds the protrusion 74 from inside the protrusion 74 by the small diameter portion 672 inserted into the flange portion 743 and the second diameter portion 742, so that the first housing cover 81 can suitably support the protrusion 74 via the first elastic body 67d. Other functions of this compressor are similar to those of the compressor of Example 1.

[0161] Fifth Embodiment As shown in Fig. 6 , in a compressor according to a fifth embodiment, the housing 6 has a first housing cover 83. The first housing cover 83 is also an example of the "first wall" of the present invention. As a result, in this compressor, the housing 6 is composed of a housing main body 60, the first housing cover 83, and the second housing cover 62 (see Fig. 1 ). The housing main body 60, the first housing cover 83, and the second housing cover 62 are fixed in the direction of the drive axis O1, thereby forming a scroll chamber 65 within the housing 6.

[0162] 6, in this compressor, a protrusion 75 is provided inside the scroll chamber 65. Furthermore, in this compressor, the elastic body 67 is composed of a first elastic body 67e and a second elastic body 67b (see FIG. 1).

[0163] The first housing cover 83 shown in Figure 6 is made of an aluminum alloy. The first housing cover 83 is located at the rear end of the housing main body 60. The first housing cover 83 is generally disk-shaped and centered on the drive axis O1, extending in the radial direction of the housing 6. The first housing cover 83 has a front surface 83a facing forward and a rear surface 83b facing rearward and located on the opposite side of the front surface 83a. The first housing cover 83 may also be made of steel.

[0164] An attachment recess 83c is formed in the first housing cover 83. The attachment recess 83c is recessed in a cylindrical shape extending from the front surface 83a to the rear surface 83b and centered on the drive axis O1.

[0165] The first elastic body 67e is made of synthetic rubber and has a cylindrical shape extending in the direction of the drive shaft center O1. More specifically, the first elastic body 67e has the same diameter as the small diameter portion 672 of the first elastic body 67d in the compressor of the fourth embodiment.

[0166] The rear portion of the first elastic body 67e is inserted into the mounting recess 83c. The inner diameter of the mounting recess 83c is slightly smaller than the outer diameter of the first elastic body 67e. Therefore, the first elastic body 67e is inserted into the mounting recess 83c with its rear portion slightly reduced in diameter due to elastic deformation. As a result, the first elastic body 67e is attached to the first housing cover 83 in a state where it protrudes from the mounting recess 83c into the scroll chamber 65. In other words, the first housing cover 83 holds the first elastic body 67e in a state where it protrudes from the mounting recess 83c into the scroll chamber 65. The material of the first elastic body 67e can be designed as appropriate.

[0167] The protrusion 75 is formed as a separate part from the first housing cover 83. The protrusion 75 is made of steel. The protrusion 75 is composed of a first radial portion 751, a second radial portion 752, and a flange portion 753. The first radial portion 751 has a configuration similar to that of the first radial portion 741 in the compressor of Example 4. The second radial portion 752 has a configuration similar to that of the second radial portion 742 in the compressor of Example 4, except that it is formed longer in the direction of the drive axis O1 than the second radial portion 742 in the compressor of Example 4. The flange portion 753 has a configuration similar to that of the flange portion 743 in the compressor of Example 4. As a result, the inner diameters of the second radial portion 752 and the flange portion 753 are slightly smaller than the outer diameter of the first elastic body 67e.

[0168] The first elastic body 67e of the protrusion 75 is inserted into the flange portion 753 and the second diameter portion 752. At this time, the first elastic body 67e is inserted into the flange portion 753 and the second diameter portion 752 while being slightly reduced in diameter due to elastic deformation. Thus, the protrusion 75 is attached to the first housing cover 83 with the first elastic body 67e interposed therebetween. As a result, in this compressor, the first housing cover 83 supports the protrusion 75 via the first elastic body 67e. Furthermore, with the protrusion 75 attached to the first housing cover 83, the flange portion 753 is spaced from the front surface 83a of the first housing cover 83. Therefore, the protrusion 75 and the first housing cover 83 do not abut against each other. Furthermore, the first elastic body 67e holds the protrusion 75 from inside the protrusion 75.

[0169] In this compressor, the stator core 17a is fixed to the outer peripheral surface of the second radial portion 752. Furthermore, the inner cylindrical portion 37b of the cover body 37 is rotatably supported around the drive axis O1 relative to the first radial portion 751 via the first radial ball bearing 51. The driven scroll 40 is rotatably supported around the driven axis O2 relative to the first radial portion 751. As a result, in this compressor as well, the cover body 37 and the driven scroll 40 are rotatably supported by the protruding body 75 forward of the stator core 17a. The other configurations of this compressor are similar to those of the compressor of Example 1.

[0170] In this compressor, torque fluctuations transmitted from the stator core 17a to the protruding body 75 and torque fluctuations transmitted from the driving scroll 30 and the driven scroll 40 to the protruding body 75 cancel each other out at the protruding body 75. Furthermore, the protruding body 75 is a separate component from the first housing cover 83, and the protruding body 75 is attached to the first housing cover 83 with the first elastic body 67e interposed therebetween. Therefore, in this compressor, torque fluctuations acting on the protruding body 75, and ultimately moments acting on the protruding body 75, are suitably absorbed by the first elastic body 67e as the first elastic body 67e elastically deforms. As a result, in this compressor, moments acting on the protruding body 75 are less likely to be transmitted to the first housing cover 83, and the housing 6 is less likely to vibrate.

[0171] Furthermore, in this compressor, the first elastic body 67e is inserted into the mounting recess 83c, the flange portion 743, and the second diameter portion 742 while contracting in diameter due to elastic deformation. As a result, in this compressor, it is not necessary to attach the first elastic body 67e to the protruding body 75 and the first housing cover 83 using multiple first and second connecting pins 811, 734, as in the compressor of the third embodiment. Furthermore, in this compressor, the first elastic body 67e is inserted into the flange portion 753 and the second diameter portion 752, so that the first elastic body 67e holds the protruding body 75 from inside the protruding body 75. This allows the first housing cover 83 to suitably support the protruding body 75 via the first elastic body 67e. Other functions of this compressor are similar to those of the compressor of the first embodiment.

[0172] Although the present invention has been described above in accordance with Examples 1 to 5, it goes without saying that the present invention is not limited to the above Examples 1 to 5, and can be appropriately modified and applied within the scope of the spirit of the present invention.

[0173] For example, in the compressor of Example 1, the first housing cover 61 has the retaining portion 611, but this is not limiting, and the retaining portion 611 may be omitted, and the second diameter portion 642 of the protrusion 64 may be connected to the first housing cover 61. The same applies to the compressor of Example 2.

[0174] Furthermore, in the compressor of Example 1, the holding portion 611 is formed integrally with the first housing cover 61. However, this is not limiting, and the holding portion 611 and the first housing cover 61 may be formed separately, and the holding portion 611 may be fixed to the first housing cover 61. In this case, it is easy to form the holding portion 611 and the first housing cover 61 from different materials. The same applies to the compressor of Example 2.

[0175] In the compressor of Example 1, the first radial portion 641 and the second radial portion 642 of the protrusion 64 are integrally formed. However, this is not limiting, and the first radial portion 641 and the second radial portion 642 may be formed separately, and the first radial portion 641 may be fixed to the second radial portion 642. The same applies to the compressors of Examples 2 to 5.

[0176] In the compressors of Examples 1 and 2, the housing 6 is configured by a housing main body 60, a first housing cover 61, and a second housing cover 62. However, the present invention is not limited to this, and the housing 6 may have other configurations as long as it has the "peripheral wall," "first wall," and "second wall" of the present invention. The same applies to the compressors of Examples 3 to 5.

[0177] Furthermore, the first elastic body 67a and the second elastic body 67b may be omitted in the compressor of the first embodiment, and the same applies to the second elastic body 67b in the compressor of the second embodiment.

[0178] In the compressor of the second embodiment, an elastic body may be provided between the front end surface 612 a of the holding portion 612 and the rear end surface 713 of the protrusion 71 .

[0179] Furthermore, in the compressor of Example 3, the stator core 17a is fixed to the second radial portion 732 of the protrusion 73, more specifically, to the outer peripheral surface of the second radial portion 732. However, this is not limiting, and the stator core 17a may be disposed on the outer peripheral surface of the second radial portion 732 and fixed to the flange portion 733 by pins, bolts, or the like. Similarly, in the compressor of Example 4, the stator core 17a may be disposed on the outer peripheral surface of the second radial portion 742 and fixed to the flange portion 743 by pins, bolts, or the like. Similarly, in the compressor of Example 5, the stator core 17a may be disposed on the outer peripheral surface of the second radial portion 752 and fixed to the flange portion 753 by pins, bolts, or the like.

[0180] In addition, in the compressors of Examples 1 to 5, the outer cylindrical portion 37d may be omitted from the cover body 37, and the rotor 11 may be formed to extend in the direction of the drive axis O1 so that the rotor 11 is connected to the wall portion 37a.

[0181] In the compressors of the first to fifth embodiments, a return passage may be formed to return the lubricating oil contained in the refrigerant discharged to the discharge chamber 14 to the first radial ball bearing 51 and the like for lubrication.

[0182] In the compressors of the first to fifth embodiments, a suction passage that connects the scroll chamber 65 and the suction section 30a may be formed in the driving peripheral wall 35 or the like, separate from the suction port 374.

[0183] The present specification also includes the following inventions: (Supplementary Note 1) A double-rotary scroll compressor comprising a housing, a driving scroll, a driven scroll, a driving mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the driving scroll, the driven scroll, and the driving mechanism are housed, the driving mechanism has a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator, the stator has a stator core supported by the housing, the driving scroll is rotationally driven about a drive axis by the driving mechanism, and the driven scroll is rotationally driven by the driving scroll and the driven mechanism about a driven axis while being eccentric with respect to the driving scroll, the driving scroll and the driven scroll form a compression chamber that compresses a fluid by the rotational driving and the rotational driven, and within the scroll chamber is provided a protrusion that is fixed to the stator core and extends in the drive axis direction toward the driving scroll and the driven scroll, and the driving scroll has a cover body that is rotationally driven by the rotor, the cover body is rotatably supported about the drive axis by the protruding body on the compression chamber side of the stator core in the direction of the drive axis, and the driven scroll is rotatably supported about the driven axis by the protruding body on the compression chamber side of the stator core in the direction of the drive axis. (Supplementary Note 2) A double-rotary scroll compressor according to Supplementary Note 1, wherein the housing has a first wall extending in a radial direction of the housing, a peripheral wall connected to an outer periphery of the first wall and extending cylindrically from the first wall in the drive axis direction, and a second wall extending in the radial direction and connected to the peripheral wall on the opposite side of the drive axis direction from the first wall, the first wall supports the protrusion, the drive scroll has a supported member located on the opposite side of the drive axis direction from the cover body with the compression chamber in between, the cover body is supported by the protrusion via a first bearing so as to be rotatable about the drive axis, and the supported member is supported by the second wall via a second bearing so as to be rotatable about the drive axis.(Supplementary Note 3) The double-rotary scroll compressor according to Supplementary Note 2, wherein the first wall has a retaining portion extending into the scroll chamber in the drive shaft direction, and the protrusion is fitted with the retaining portion. (Supplementary Note 4) The double-rotary scroll compressor according to Supplementary Note 2, wherein an elastically deformable first elastic body is provided between the protrusion and the first wall. (Supplementary Note 5) The double-rotary scroll compressor according to any one of Supplements 2 to 4, wherein an elastically deformable second elastic body is provided between the second bearing and the second wall. (Supplementary Note 6) A double-rotary scroll compressor comprising a housing, a driving scroll, a driven scroll, a driving mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the driving scroll, the driven scroll, and the driving mechanism are housed, the driving mechanism has a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator, the stator has a stator core supported by the housing, the driving scroll is rotationally driven about the drive axis by the drive mechanism, and the driven scroll is rotationally driven by the drive scroll and the driven mechanism about the driven axis while being eccentric with respect to the drive scroll, the driving scroll and the driven scroll form a compression chamber that compresses a fluid by the rotational driving and the rotational driven, and within the scroll chamber is provided a protrusion that is fixed to the stator core and extends in the drive axis direction toward the driving scroll and the driven scroll, the driving scroll has a cover body that is rotationally driven by the rotor, and the cover body is supported by the protrusion so as to be rotatable about the drive axis, The driven scroll is supported by the protruding body so as to be rotatable about the driven axis, and the protruding body is attached to the housing via an elastic body that is elastically deformable.(Appendix 7) A double-rotating scroll compressor according to appendix 6, wherein the housing has a first wall extending in a radial direction of the housing, a peripheral wall connected to an outer periphery of the first wall and extending cylindrically from the first wall in the drive axis direction, and a second wall extending in the radial direction and connected to the peripheral wall on the opposite side of the drive axis direction from the first wall, the first wall has the protrusion attached to it and holds the elastic body, the drive scroll has a supported body located on the opposite side of the drive axis direction from the cover body with the compression chamber in between, the cover body is supported by the protrusion via a first bearing so as to be rotatable about the drive axis, and the supported body is supported by the second wall via a second bearing so as to be rotatable about the drive axis. (Supplementary Note 8) The double-rotary scroll compressor according to Supplementary Note 7, wherein the first wall has a retaining portion extending into the scroll chamber in the drive shaft direction, the protruding body fits with the retaining portion while allowing the elastic body and the retaining portion to enter inside, and the elastic body is provided between the retaining portion and the protruding body in the radial direction and is sandwiched between the retaining portion and the protruding body in the radial direction. (Supplementary Note 9) The double-rotary scroll compressor according to Supplementary Note 8, wherein the elastic body has a first elastic body provided between the protruding body and the first wall, and a second elastic body provided between the second bearing and the second wall. (Supplementary Note 10) The double-rotary scroll compressor according to Supplementary Note 4, wherein at least a portion of the first elastic body overlaps with the stator core in the radial direction. (Supplementary Note 11) The double-rotary scroll compressor according to Supplementary Note 8, wherein at least a portion of the elastic body overlaps with the stator core in the radial direction. (Supplementary Note 12) The double-rotary scroll compressor according to any one of Supplementary Notes 1 to 11, wherein the protrusion has a first diameter portion where the cover body is rotatably supported about the drive axis via the first bearing and the driven scroll is rotatably supported about the driven axis, and a second diameter portion where the stator core is disposed on an outer peripheral surface and has a diameter larger than that of the first diameter portion, and the first diameter portion is located closer to the compression chamber than the second diameter portion in the direction of the drive axis.(Supplementary Note 13) The double-rotary scroll compressor according to claim 12, wherein the driven scroll is supported on the first radial portion radially inward of the cover body so as to be rotatable about the driven axis. (Supplementary Note 14) The double-rotary scroll compressor according to Supplementary Note 12 or 13, wherein the driven scroll has a driven shaft portion supported on the first radial portion, and the stator core, the first bearing, and the driven shaft portion are arranged in this order from the first wall side toward the compression chamber side in the drive axis direction.

[0184] The present invention can be used in vehicle air conditioning systems and the like.

[0185] DESCRIPTION OF SYMBOLS 6...Housing 10...Electric motor (drive mechanism) 11...Rotor 12...Compression chamber 16...Driven shaft portion 17...Stator 17a...Stator core 20...Driven mechanism 30...Drive scroll 31...Drive end plate 33...Driven scroll body 35...Driven peripheral wall 37...Cover body 39d...Boss (supported body) 40...Driven scroll 41...Driven end plate 43...Driven scroll body 51...First radial ball bearing (first bearing) 52...Second radial ball bearing (second bearing) 60...Housing body (peripheral wall) 61, 81, 83...First housing cover (first wall) 62...Second housing cover (second wall) 64, 71, 73, 74, 75...Protrusion 65...Scroll chamber 67...Elastic body 67a, 67c, 67d, 67e...First elastic body 67b...Second elastic body 611, 612...Holding portion 641, 711, 731, 741, 751...First radial portion 642, 712, 732, 742, 752...Second radial portion O1...Drive shaft center O2...Driver shaft center

Claims

1. A double-rotary scroll compressor comprising a housing, a driving scroll, a driven scroll, a driving mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the driving scroll, the driven scroll, and the driving mechanism are housed, the driving mechanism has a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator, the stator has a stator core supported by the housing, the driving scroll is rotationally driven about the drive axis by the driving mechanism, and the driven scroll is rotationally driven by the driving scroll and the driven mechanism about the driven axis while being eccentric with respect to the driving scroll, the driving scroll and the driven scroll form a compression chamber that compresses a fluid by the rotational driving and the rotational driven, and within the scroll chamber is provided a protrusion that is fixed to the stator core and extends in the drive axis direction toward the driving scroll and the driven scroll, and the driving scroll has a cover body that is rotationally driven by the rotor, the cover body is rotatably supported about the drive axis by the protruding body on the compression chamber side of the stator core in the direction of the drive axis, and the driven scroll is rotatably supported about the driven axis by the protruding body on the compression chamber side of the stator core in the direction of the drive axis.

2. A double-rotating scroll compressor according to claim 1, wherein the housing has a first wall extending radially of the housing, a peripheral wall connected to the outer periphery of the first wall and extending cylindrically from the first wall in the direction of the drive axis, and a second wall extending radially and connected to the peripheral wall on the opposite side of the drive axis from the first wall, the first wall supporting the protrusion, the drive scroll having a supported member located on the opposite side of the drive axis from the cover body across the compression chamber, the cover body being supported by the protrusion via a first bearing so as to be rotatable about the drive axis, and the supported member being supported by the second wall via a second bearing so as to be rotatable about the drive axis.

3. A double-rotating scroll compressor according to claim 2, wherein the first wall has a retaining portion extending into the scroll chamber in the direction of the drive shaft, and the protrusion is fitted into the retaining portion.

4. A double-rotating scroll compressor according to claim 2, wherein a first elastic body capable of elastic deformation is provided between said protrusion and said first wall.

5. A double-rotating scroll compressor according to claim 2 or 3, wherein an elastically deformable second elastic body is provided between said second bearing and said second wall.

6. A double-rotary scroll compressor comprising a housing, a driving scroll, a driven scroll, a driving mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the driving scroll, the driven scroll, and the driving mechanism are housed, the driving mechanism has a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator, the stator has a stator core supported by the housing, the driving scroll is rotationally driven about the drive axis by the driving mechanism, and the driven scroll is rotationally driven by the driving scroll and the driven mechanism about the driven axis while being eccentric with respect to the driving scroll, the driving scroll and the driven scroll form a compression chamber that compresses a fluid by the rotational driving and the rotational driven, wherein a protrusion is provided within the scroll chamber that is fixed to the stator core and extends in the direction of the drive axis toward the driving scroll and the driven scroll, the driving scroll has a cover body that is rotationally driven by the rotor, and the cover body is supported by the protrusion so as to be rotatable about the drive axis, The driven scroll is supported by the protruding body so as to be rotatable about the driven axis, and the protruding body is attached to the housing via an elastic body that is elastically deformable.

7. A double-rotating scroll compressor as set forth in claim 6, wherein the housing has a first wall extending radially of the housing, a peripheral wall connected to the outer periphery of the first wall and extending cylindrically from the first wall in the direction of the drive axis, and a second wall extending radially and connected to the peripheral wall on the opposite side of the drive axis from the first wall, the first wall having the protrusion attached thereto and holding the elastic body, the drive scroll having a supported body located on the opposite side of the drive axis from the cover body across the compression chamber, the cover body being supported by the protrusion via a first bearing so as to be rotatable about the drive axis, and the supported body being supported by the second wall via a second bearing so as to be rotatable about the drive axis.

8. A double-rotating scroll compressor as described in claim 7, wherein the first wall has a retaining portion that extends into the scroll chamber in the direction of the drive axis, the protrusion engages with the retaining portion while allowing the elastic body and the retaining portion to enter the interior, and the elastic body is provided between the retaining portion and the protrusion in the radial direction and is sandwiched between the retaining portion and the protrusion in the radial direction.

9. A double-rotating scroll compressor according to claim 7, wherein the elastic body comprises a first elastic body provided between the protrusion and the first wall, and a second elastic body provided between the second bearing and the second wall.

10. A double-rotating scroll compressor according to claim 4, wherein at least a portion of said first elastic body overlaps with said stator core in the radial direction.

11. A double-rotating scroll compressor according to claim 8, wherein at least a portion of said elastic body overlaps with said stator core in the radial direction.

12. A double-rotating scroll compressor as claimed in claim 2 or 7, wherein the protrusion has a first diameter portion where the cover body is rotatably supported about the drive axis via the first bearing and the driven scroll is rotatably supported about the driven axis, and a second diameter portion which is larger in diameter than the first diameter portion and on whose outer peripheral surface the stator core is disposed, and the first diameter portion is located closer to the compression chamber than the second diameter portion in the direction of the drive axis.

13. A double-rotating scroll compressor according to claim 12, wherein the driven scroll is supported rotatably about the driven axis at the first radial portion radially inward of the cover body.

14. A double-rotating scroll compressor as described in claim 13, wherein the driven scroll has a driven shaft portion supported by the first radial portion, and the stator core, the first bearing, and the driven shaft portion are arranged in this order in the drive shaft direction from the first wall side toward the compression chamber side.

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