Bidirectional rotary scroll-type compressor

Abstract

This bidirectional rotary scroll-type compressor comprises a housing (6), a compression unit (3), and a drive mechanism (10). The housing (6) has a scroll chamber (65) in which the compression unit (3) and the drive mechanism (10) are accommodated. Provided within the scroll chamber (65) are: a first shaft support part (51) that is positioned on one side of the housing (6) in the axial direction (X1) and that rotatably supports the compression unit (3); and a second shaft support part (52) that is positioned on the other side of the first shaft support part (51) in the axial direction (X1) and that rotatably supports the compression unit (3). At least one of the first shaft support part (51) and the second shaft support part (52), when a fluid is not compressed, supports the compression unit (3) such that the compression unit (3) is inclined in a direction opposite from a first incline direction (Y1) with respect to the axial direction (X1).

Description

Dual-rotation scroll compressor

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

[0002] Patent Document 1 discloses a conventional dual-rotation scroll compressor (hereinafter simply referred to as "compressor" where appropriate). This compressor includes a housing, a compression unit, and a drive mechanism. The housing has a scroll chamber that accommodates the compression unit and the drive mechanism. Fluid is sucked into the scroll chamber from outside the housing. In this document, the fluid is specifically a refrigerant gas.

[0003] The compression unit is composed of a driving scroll that is rotationally driven around a driving shaft center by the driving mechanism, and a driven scroll that is eccentric with respect to the driving scroll and is rotationally driven around a driven shaft center by the driving scroll and a driven mechanism.

[0004] Furthermore, a first shaft support portion and a second shaft support portion are provided in the scroll chamber. The first shaft support portion is located on one axial side of the housing. The second shaft support portion is located on the other axial side of the housing relative to the first shaft support portion. That is, in the scroll chamber, the first shaft support portion and the second shaft support portion are arranged spaced apart from each other in the axial direction of the housing. The first shaft support portion rotatably supports the driving scroll on one axial side of the housing within the scroll chamber, and the second shaft support portion rotatably supports the driving scroll on one axial side of the housing within the scroll chamber. In the aforementioned document, the first shaft support portion and the second shaft support portion are specifically sliding bearings.

[0005] In this compressor, the driving scroll and the driven scroll form a compression chamber between them for compressing fluid. As the compression unit, that is, the driving scroll and the driven scroll, rotate within the scroll chamber, the fluid in the scroll chamber is sucked into the compression chamber and compressed therein. The fluid compressed in the compression chamber in this manner is discharged to the outside of the housing, that is, to the outside of the compressor.

[0006] Japanese Unexamined Patent Application Publication No. 2004-65292

[0007] In the conventional compressor described above, when a fluid is compressed, a tilting moment acts on the compression section, causing it to tilt in a first tilting direction relative to the axial direction of the housing due to the reaction force of the fluid being compressed in the compression chamber. Therefore, when a fluid is compressed, the compression section inevitably tries to rotate in a tilted position in the first tilting direction due to this tilting moment. To explain this using the first shaft support as an example, the first shaft support is subjected to a tilting moment in the opposite direction to the tilting moment acting on the compression section, due to the compression section trying to rotate in a tilted position in the first tilting direction as described above. Therefore, when a fluid is compressed, the first shaft support tilts in the opposite direction to the first tilting direction.

[0008] As a result, when the fluid is compressed, the first shaft support supports the compression section in an inclined position relative to the axial direction of the housing. Therefore, in this compressor, it becomes difficult for the first shaft support to adequately support the compression section, raising concerns about increased power loss during fluid compression.

[0009] Furthermore, because the first shaft support supports the compression section in an inclined position relative to the axial direction of the housing during fluid compression, there is a concern that the first shaft support may be prone to uneven wear in this compressor.

[0010] This invention has been made in view of the above-mentioned conventional circumstances, and aims to solve the problem of providing a double-rotation scroll compressor with excellent operating efficiency and durability.

[0011] The double-rotation scroll compressor of the present invention comprises a housing, a compression section, and a drive mechanism, the housing having a scroll chamber in which the compression section and the drive mechanism are housed, the compression section having a drive scroll rotated around a drive axis by the drive mechanism, and a driven scroll rotated around a driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, the drive scroll and the driven scroll forming a compression chamber for compressing fluid by the rotational drive and rotational drive, the scroll chamber being provided with a first shaft support located on one side in the axial direction of the housing and rotatably supporting the compression section, and a second shaft support located on the other side in the axial direction of the first shaft support and rotatably supporting the compression section, the compression section during fluid compression is subjected to a tilt moment that tilts it in a first tilting direction with respect to the axial direction due to the reaction force of the fluid compressed in the compression chamber, The first and second shaft supports the compression portion in the uncompressed state of the fluid, such that the compression portion is tilted in the same direction as the first tilting direction with respect to the axial direction.

[0012] In the double-rotation scroll compressor of the present invention, a tilting moment due to the reaction force of the fluid being compressed in the compression chamber acts on the compression section when the fluid is compressed, i.e., during operation. Therefore, when the fluid is compressed, the compression section tilts in a first tilting direction with respect to the axial direction of the housing. In this compressor, at least one of the first and second shaft supports supports the compression section such that it tilts in the opposite direction to the first tilting direction with respect to the axial direction when the fluid is not compressed.

[0013] Here, for example, if the first shaft support supports the compression section such that it tilts in the opposite direction to the first tilting direction with respect to the axial direction when the fluid is uncompressible, then in this compressor, when the compression section tilts in the first tilting direction when the fluid is compressed, the posture of the compression section, which is already tilted in the opposite direction to the first tilting direction when the fluid is uncompressible, will be corrected. As a result, the first shaft support can support the compression section in a posture that is approximately parallel to the axial direction of the housing when the fluid is compressed. Note that a posture that is approximately parallel to the axial direction of the housing includes not only a posture that is perfectly parallel to the axial direction of the housing, but also a posture that is slightly tilted with respect to the axial direction of the housing.

[0014] As a result, in this compressor, the first shaft support can suitably support the compression section when compressing the fluid, thereby reducing power loss during fluid compression. Furthermore, by supporting the compression section in a position substantially parallel to the axial direction of the housing when compressing the fluid, the compression section can rotate in a position substantially parallel to the axial direction of the housing when compressing the fluid.

[0015] Furthermore, when the fluid is compressed, the first support supports the compression section in a position approximately parallel to the axial direction of the housing, which reduces uneven wear on the first support. The same applies when the fluid is uncompressed and the second support supports the compression section in such a way that it is tilted in the opposite direction to the first tilting direction relative to the axial direction.

[0016] Therefore, the dual-rotation scroll compressor of the present invention offers excellent operating efficiency and durability.

[0017] In the compressor of the present invention, it is preferable that at least one of the first and second shaft supports the compression section in a position inclined in a first tilting direction with respect to the axial direction when the fluid is not compressed.

[0018] For example, if the first support shaft supports the compression section in a position tilted in the first tilting direction when the fluid is uncompressed, then when the fluid is compressed, the compression section tilting in the first tilting direction causes the first support shaft to tilt in the opposite direction to the first tilting direction. In this way, the first support shaft can be displaced to a position approximately parallel to the axial direction of the housing when the fluid is compressed.

[0019] As a result, when the fluid is compressed, the first support can support the compression section in a position substantially parallel to the axial direction of the housing, thus providing suitable support for the compression section. The same applies when the fluid is uncompressed and the second support supports the compression section in a position tilted in the first tilting direction.

[0020] A projection extending toward the compression section may be provided within the scroll chamber. The projection may be attached to the housing via an elastically deformable elastic body. Preferably, the first shaft support is provided on the projection and rotatably supports the drive scroll.

[0021] In this case, the first shaft support can be easily provided within the scroll chamber by the projection. Furthermore, the projection is attached to the housing via an elastically deformable elastic body. As a result, the elastic body can effectively suppress the transmission of vibrations generated in the compression section to the housing through the projection by its own elastic deformation. Therefore, in this compressor, vibration of the housing during fluid compression can be effectively suppressed.

[0022] Preferably, the elastic body tilts the protruding body in a first tilting direction with respect to the axial direction when the fluid is incompressible. In this case, when the fluid is incompressible, the protruding body tilts in the first tilting direction with respect to the axial direction of the housing, thereby allowing the first pivot support provided on the protruding body to be suitably tilted in the first tilting direction with respect to the axial direction of the housing when the fluid is incompressible. Furthermore, even if the first pivot support tilts in the opposite direction to the first tilting direction together with the protruding body when the fluid is compressed, when the fluid is incompressible, the elastic body elastically deforms, allowing the protruding body and the first pivot support to suitably return to a position tilted in the first tilting direction.

[0023] The housing may have an extension that is located inside the projection and holds the projection. The elastic body may also have a first elastic body and a second elastic body that are formed in an annular shape and are positioned between the projection and the extension in the radial direction of the housing. Preferably, the first elastic body and the second elastic body are positioned axially separated with their centers offset radially from each other.

[0024] In this case, the first elastic body and the second elastic body can suitably tilt the protruding body, and consequently the first pivot point, in the first tilting direction when the fluid is incompressible.

[0025] Furthermore, the housing may have an extension that is located inside the projection and holds the projection. The elastic body may be positioned between the projection and the extension in the radial direction of the housing. Preferably, the extension is inclined in a first tilting direction with respect to the axial direction. In this case, the shape of the extension can be used to suitably tilt the projection in the first tilting direction when the fluid is uncompressible.

[0026] A retaining member may be attached to the housing, positioned within the scroll chamber on the other axial side of the first pivot. The second pivot can be provided on the retaining member to rotatably support the drive scroll. Preferably, when the fluid is uncompressed, the retaining member is inclined with respect to the axial direction so that the second pivot can support the drive scroll in a position substantially parallel to the axial direction when the fluid is compressed.

[0027] In this case, the second shaft support can be easily provided within the scroll chamber by the retaining member. Furthermore, when the fluid is uncompressed, the retaining member tilts with respect to the axial direction of the housing, so the second shaft support provided on the retaining member also tilts with respect to the axial direction of the housing when the fluid is uncompressed. In this compressor, the retaining member is pre-tilted with respect to the axial direction when the fluid is uncompressed so that the second shaft support can support the drive scroll in a position substantially parallel to the axial direction when the fluid is compressed. As a result, in this compressor, the second shaft support can suitably support the drive scroll when the fluid is compressed. The specific direction in which the protective member tilts when the fluid is uncompressed can be determined based on the positional relationship between the support center of the second shaft support and the tilt center of the retaining member.

[0028] The dual-rotation scroll compressor of the present invention offers excellent operating efficiency and durability.

[0029] Figure 1 is a cross-sectional view of the compressor of Example 1 during fluid compression. Figure 2 is an enlarged cross-sectional view of the main part of the compressor of Example 1 when the fluid is uncompressed. Figure 3 is an enlarged cross-sectional view of the main part of the compressor of Example 1 when the fluid is uncompressed. Figure 4 is a schematic cross-sectional view of a comparative example compressor showing the tilt moment acting on the compression section, the first shaft support, and the second shaft support when the fluid is compressed. Figure 5 is an enlarged cross-sectional view of the main part of the compressor of Example 2 when the fluid is uncompressed, similar to Figure 2.

[0030] The following describes two embodiments of the present invention with reference to the drawings. The compressors in embodiments 1 and 2 are mounted on a vehicle (not shown) and constitute the vehicle's air conditioning system.

[0031] As shown in Figure 1, the compressor of this embodiment comprises a housing 6, an electric motor 10, and a scroll compression section 3. The electric motor 10 is an example of a "drive mechanism" in the present invention. The scroll compression section 3 is an example of a "compression section" in the present invention.

[0032] In this embodiment, the front-rear and up-down directions of the compressor are defined by the solid arrows shown in Figure 1. The front-rear and up-down directions are orthogonal to each other. Then, in Figures 2 and onward, the front-rear and up-down directions of the compressor are defined in correspondence with Figure 1. Note that these front-rear and up-down directions are examples for the sake of explanation, and the compressor can change its own orientation as appropriate depending on the vehicle on which it is mounted.

[0033] As shown in Figures 1 to 3, the housing 6 is composed of a housing body 60, a first housing cover 61, and a second housing cover 62. These housing body 60, first housing cover 61, and second housing cover 62 are made of aluminum alloy. However, the housing body 60, first housing cover 61, and second housing cover 62 may also be made of steel or the like.

[0034] The housing body 60 is formed in a cylindrical shape that extends linearly in the axial direction X1. The housing body 60 has openings at one end in the axial direction X1 and at the other end in the axial direction X1.

[0035] In this embodiment, the axial direction X1 is parallel to the front-rear direction of the compressor. The axial direction X1 of the housing body 60 corresponds to the axial direction X1 of the housing 6. One side of the axial direction X1 corresponds to the "rear side of the compressor," and the other side of the axial direction X1 corresponds to the "front side of the compressor." In other words, in this invention, "one side in the axial direction" corresponds to the "rear side of the compressor," and "the other side in the axial direction" corresponds to the "front side of the compressor." Thus, in this embodiment, "axial direction X1" and "front-rear direction" are synonymous, "one side of the axial direction X1" and "rear side" are synonymous, and "the other side of the axial direction X1" and "front side" are synonymous. Based on these, the housing body 60 can be described as "formed in a cylindrical shape that extends linearly in the front-rear direction, with openings at the front and rear ends." Furthermore, as described above, the compressor of this embodiment can change its orientation as appropriate depending on the vehicle on which it is mounted, so depending on the orientation of the compressor, the axial direction X1 of the housing 6 may be parallel to the vertical direction.

[0036] A suction port 68 is formed in the housing body 60. The suction port 68 extends radially in the housing body 60, that is, radially in the housing 6. The suction port 68 is connected to an evaporator (not shown) through piping (not shown).

[0037] As shown in Figure 2, the first housing cover 61 is located at the rear end of the housing body 60. The first housing cover 61 has a first cover body portion 61a and an extension portion 61b. The first cover body portion 61a extends in a substantially disc shape in the radial direction of the housing 6. The first cover body portion 61a has a front surface 610a facing forward and a rear surface 610b located on the opposite side of the front surface 610a and facing rear.

[0038] The extension portion 61b is integrally formed with the first cover body portion 61a. The extension portion 61b extends cylindrically forward from the front surface 610a of the first cover body portion 61a in the axial direction X1 of the housing 6. Here, the extension portion 61b extends parallel to the axial direction X1 of the housing 6.

[0039] Retaining grooves 611 and 612 are formed in the extension portion 61b. These retaining grooves 611 and 612 are recessed in the outer circumferential surface 616 of the extension portion 61b and form an annular shape that encircles the outer circumferential surface 616. The retaining grooves 611 and 612 are arranged in the order of retaining groove 611, then retaining groove 612, from the rear side to the front side of the extension portion 61b.

[0040] Here, the retaining grooves 611 and 612 are recessed in the outer circumferential surface 616 with their centers offset radially from the central axis (not shown) of the extension portion 61b. Furthermore, each retaining groove 611 and retaining groove 612 are recessed in the outer circumferential surface 616 with their centers offset radially from each other. That is, the retaining groove 611 is recessed in the outer circumferential surface 616 with its center offset downwards with respect to the central axis of the extension portion 61b. On the other hand, the retaining groove 612 is recessed in the outer circumferential surface 616 with its center offset upwards with respect to the central axis of the extension portion 61b and the center of the retaining groove 611.

[0041] Furthermore, a one-sided elastic body 70 is attached to the extension portion 61b. The one-sided elastic body 70 is an example of an "elastic body" in the present invention. The one-sided elastic body 70 is composed of a first elastic body 70a and a second elastic body 70b. These first and second elastic bodies 70a and 70b are made of an elastically deformable resin such as synthetic rubber. These first and second elastic bodies 70a and 70b are formed in an annular shape having the same form. The one-sided elastic body 70 may be made of a metal or the like with lower rigidity than the first housing cover 61.

[0042] The first elastic body 70a is attached to the extension portion 61b by being housed in the retaining groove 611. On the other hand, the second elastic body 70b is attached to the extension portion 61b by being housed in the retaining groove 612. Here, since the retaining groove 611 and the retaining groove 612 have the shapes described above, the first elastic body 70a and the second elastic body 70b are arranged axially separated with their centers offset from each other in the radial direction of the housing 6. Specifically, the first elastic body 70a is housed in the retaining groove 611 such that the portion below the center of the extension portion 61b protrudes radially from the housing 6 more than the portion above the center of the extension portion 61b. On the other hand, the second elastic body 70b is housed in the retaining groove 612 such that the portion above the center of the extension portion 61b protrudes radially from the housing 6 more than the portion below the center of the extension portion 61b.

[0043] A protruding body 64 is attached to the first housing cover 61. The protruding body 64 is made of steel. The protruding body 64 consists of a first diameter portion 64a and a second diameter portion 64b. The first diameter portion 64a constitutes the front portion of the protruding body 64. A pin hole 4 is formed in the first diameter portion 64a. The pin hole 4 extends in the front-rear direction inside the first diameter portion 64a and opens to the front end surface of the first diameter portion 64a.

[0044] The second diameter portion 64b is integrated with the first diameter portion 64a at a front end thereof. Thus, the second diameter portion 64b constitutes a rear portion of the protruding body 64. The second diameter portion 64b has a larger diameter than the first diameter portion 64a and is formed in a bottomed cylindrical shape with an open rear end. Here, the inner diameter of the second diameter portion 64b is larger than the outer diameter of the extending portion 61b, and is smaller than the outer diameter of the one-side elastic body 70, that is, smaller than the outer diameters of the first and second elastic bodies 70a and 70b.

[0045] In the protruding body 64, the extending portion 61b and the one-side elastic body 70 are inserted into the second diameter portion 64b. Thus, the extending portion 61b is disposed inside the second diameter portion 64b. Further, as described above, since the inner diameter of the second diameter portion 64b is smaller than the outer diameter of the one-side elastic body 70, the one-side elastic body 70, that is, the first and second elastic bodies 70a and 70b are each elastically deformed in the radial direction of the housing 6, and are disposed between the extending portion 61b and the second diameter portion 64b.

[0046] In this way, the protruding body 64 is attached to the first housing cover 61 via the one-side elastic body 70. The extending portion 61b holds the protruding body 64 from an inner side via the one-side elastic body 70. Thus, the first housing cover 61 supports the protruding body 64.

[0047] Further, in the protruding body 64, a first radial ball bearing 51 is provided on the first diameter portion 64a. The first radial ball bearing 51 is an example of the "first shaft support portion" in the present invention. The first radial ball bearing 51 includes a first inner ring 51a and a first outer ring 51b. The first radial ball bearing 51 is provided on the first diameter portion 64a by inserting the first inner ring 51a through the first diameter portion 64a. More specifically, the first radial ball bearing 51 is provided on the first diameter portion 64a by interference-fitting the first inner ring 51a onto the outer peripheral surface of the first diameter portion 64a. Note that a slide bearing may be provided on the outer peripheral surface of the first diameter portion 64a instead of the first radial ball bearing 51.

[0048] Here, as described above, the first elastic body 70a and the second elastic body 70b are arranged on the extending portion 61b with their centers shifted from each other in the radial direction of the housing 6. Accordingly, the protruding body 64 is attached to the first housing cover 61 while being inclined in the first tilting direction Y1 with respect to the extending portion 61b. The first tilting direction Y1 is a direction that inclines toward the upper side of the compressor as going from the rear side to the front side of the compressor. That is, when the refrigerant is not compressed, that is, when the compressor is not in operation, the protruding body 64 attached to the first housing cover 64 assumes an attitude inclined upward toward the upper side of the compressor as going from the rear side to the front side of the compressor. The refrigerant is an example of the "fluid" in the present invention.

[0049] And since the protruding body 64 is inclined in the first tilting direction Y1 when the refrigerant is not compressed as described above, the first radial ball bearing 51 provided on the first diameter portion 64a also assumes an attitude inclined in the first tilting direction Y1 when the refrigerant is not compressed.

[0050] As shown in FIG. 3, the second housing cover 62 is arranged in front of the housing body 60. The second housing cover 62 has a second cover body portion 62a. The second cover body portion 62a extends in a substantially disc shape in the radial direction of the housing 6. The second cover body portion 62a has a front surface 621 facing forward, and a rear surface 622 located on the opposite side of the front surface 621 and facing rearward.

[0051] Further, the second cover body portion 62a is formed with a support portion 66 and a discharge communication port 69. The support portion 66 is integrally formed substantially at the center of the rear surface 622, and protrudes rearward from the rear surface 622. The support portion 66 is formed in a cylindrical shape extending parallel to the axial direction X1 of the housing 6, and has an outer peripheral surface 661 and an inner peripheral surface 662.

[0052] The discharge communication port 69 penetrates the second cover body portion 62a in the axial direction X1 of the housing 6, and communicates with the inside of the support portion 66. Further, the discharge communication port 69 is connected to a condenser (not shown) through a pipe (not shown).

[0053] Furthermore, the second cover body portion 62a is provided with a first sealing member 63. The first sealing member 63 is made of a resin such as PTFE (polytetrafluoroethylene) and is elastically deformable. The first sealing member 63 is also formed in an annular shape. The first sealing member 63 is positioned in the second cover body portion 62a at a location where the support portion 66 and the discharge communication port 69 are in communication. The first sealing member 63 is attached to the second cover body portion 62a with a part of itself protruding into the support portion 66. As a result, the first sealing member 63 surrounds the discharge communication port 69 from the outside within the support portion 66.

[0054] Furthermore, a bearing spacer 72 is attached to the second cover body portion 62a. The bearing spacer 72 is an example of a "holding member" in the present invention.

[0055] The bearing spacer 72 is made of metal. The bearing spacer 72 has a first wall portion 72a, a second wall portion 72b, and a bearing holding portion 72c. The first wall portion 72a is located in the front part of the bearing spacer 72 and extends radially in the housing 6. The first wall portion 72a has a front surface 720a facing forward and a rear surface 720b located on the opposite side of the front surface 720a and facing rear. The bearing spacer 72 may also be made of resin.

[0056] Furthermore, a retaining groove 721 is formed in the first wall portion 72a. The retaining groove 721 is recessed from the front surface 720a of the first wall portion 72a toward the rear. The retaining groove 721 has an annular shape that surrounds the first sealing member 63 and the discharge passage 724, which will be described later, from the outside.

[0057] The second wall portion 72b is integral with the first wall portion 72a and extends cylindrically from the first wall portion 72a toward the rear. Here, the outer diameters of the first wall portion 72a and the second wall portion 72b are formed to be smaller than the inner diameter of the support portion 66.

[0058] Retaining grooves 722 and 723 are formed in the second wall portion 72b. These retaining grooves 722 and 723 are recessed into the outer circumferential surface of the second wall portion 72b and form an annular shape that encircles the outer circumferential surface of the second wall portion 72b. The retaining grooves 722 and 723 are arranged in the order of retaining groove 722, then retaining groove 723, from the rear side to the front side of the bearing spacer 72.

[0059] Here, the retaining grooves 722 and 723 are recessed into the outer circumferential surface of the second wall portion 72b, with their centers offset radially from the central axis of the bearing spacer 72 (not shown) in the housing 6. Furthermore, each retaining groove 722 and retaining groove 723 are recessed into the outer circumferential surface of the second wall portion 72b, with their centers offset radially from each other in the housing 6. That is, the retaining groove 722 is recessed into the outer circumferential surface of the second wall portion 72b with its center offset upward relative to the central axis of the bearing spacer 72. On the other hand, the retaining groove 723 is recessed into the outer circumferential surface of the second wall portion 72b with its center offset downward relative to the central axis of the bearing spacer 72 and the center of the retaining groove 722.

[0060] The bearing retaining portion 72c is integral with the first wall portion 72a and protrudes linearly backward from the rear surface 720b of the first wall portion 72a, inside of the second wall portion 72b. As a result, the bearing retaining portion 72c is spaced radially away from the second wall portion 72b in the housing 6. Furthermore, the bearing retaining portion 72c extends further backward than the second wall portion 72b. In addition, the bearing retaining portion 72c is formed to have a smaller diameter than the second wall portion 72b. Specifically, the outer diameter of the bearing retaining portion 72c is formed to be smaller than the inner diameter of the insertion hole 39d of the case 39, which will be described later. A second sealing member 74 is provided on the bearing retaining portion 72c. The second sealing member 74 is also formed of a resin such as PTFE and is elastically deformable. The second sealing member 74 is formed in an annular shape that encircles the outer circumferential surface of the bearing retaining portion 72c.

[0061] Furthermore, a discharge passage 724 is formed in the bearing spacer 72. The discharge passage 724 is cylindrical in shape and extends in the axial direction X1 of the housing 6, penetrating the first wall portion 72a and the bearing holding portion 72c in the axial direction X1 of the housing 6. As a result, the front end of the discharge passage 724 opens to the front surface 720a of the first wall portion 72a, and the rear end of the discharge passage 724 opens to the rear end surface of the bearing holding portion 72c.

[0062] Furthermore, the bearing spacer 72 is provided with an elastic body 81 on the other side. The elastic body 81 on the other side is composed of a third elastic body 81a, a fourth elastic body 81b, and a fifth elastic body 81c. These third to fifth elastic bodies 81a to 81c are made of an elastically deformable resin such as synthetic rubber. The third elastic body 81a and the fourth elastic body 81b are formed in the same annular shape. The elastic body 81 on the other side may be made of a metal or the like with lower rigidity than the bearing spacer 72.

[0063] The third elastic body 81a is attached to the second wall portion 72b by being housed in the retaining groove 722. The fourth elastic body 81b is attached to the second wall portion 72b by being housed in the retaining groove 723. Here, since the retaining grooves 722 and 723 have the shapes described above, the third elastic body 81a and the fourth elastic body 81b are positioned with their centers offset from each other in the radial direction of the housing 6. Specifically, the third elastic body 81a is housed in the retaining groove 722 such that the portion above the center of the bearing spacer 72 protrudes radially from the housing 6 more than the portion below the center of the bearing spacer 72. On the other hand, the fourth elastic body 81b is housed in the retaining groove 723 such that the portion below the center of the bearing spacer 72 protrudes radially from the housing 6 more than the portion above the center of the bearing spacer 72.

[0064] The fifth elastic body 81c is formed in an annular shape with a smaller diameter than the third elastic body 81a and the fourth elastic body 81b. The fifth elastic body 81c is attached to the first wall portion 72a by being housed in the retaining groove 721.

[0065] The bearing spacer 72 is attached to the second cover body 62a by being positioned within the support portion 66. In this case, the third and fourth elastic bodies 81a and 81b of the bearing spacer 72 are positioned between the inner circumferential surface 662 of the support portion 66 and the second wall portion 72b, while being elastically deformed in the radial direction of the housing 6. On the other hand, the fifth elastic body 81c is positioned between the rear surface 622 of the second cover body 62a and the first wall portion 72a, while being elastically deformed in the axial direction X1 of the housing 6. In addition, in the bearing spacer 72, the front surface 720a of the first wall portion 72a abuts against the first sealing member 63 around the discharge passage 724.

[0066] In the bearing spacer 72, a second radial ball bearing 52 is provided in the bearing retaining portion 72c. The second radial ball bearing 52 is an example of the "second shaft support" in the present invention. The second radial ball bearing 52 has a second inner ring 52a and a second outer ring 52b. The second radial ball bearing 52 is provided in the bearing retaining portion 72c by inserting the second inner ring 52a into the bearing retaining portion 72c. More specifically, the second radial ball bearing 52 is provided in the bearing retaining portion 72c by interlocking the second inner ring 52a with the outer circumferential surface of the bearing retaining portion 72c. Alternatively, a sliding bearing may be provided on the outer circumferential surface of the bearing retaining portion 72c instead of the second radial ball bearing 52.

[0067] Here, as described above, the third elastic body 81a and the fourth elastic body 81b are positioned on the second wall portion 72b with their centers offset from each other in the radial direction of the housing 6. As a result, the bearing spacer 72 is attached to the second cover body portion 62a within the support portion 66 in a state inclined in the first tilting direction Y1. In other words, when the refrigerant is not compressed, the bearing spacer 72 attached to the second cover body portion 62a is in a position that is tilted upwards towards the top of the compressor as it moves from the rear side of the compressor to the front side.

[0068] Furthermore, because the bearing spacer 72 is tilted in the first tilting direction Y1 when the refrigerant is uncompressed, the second radial ball bearing 52 provided in the bearing holding portion 72c is also tilted in the first tilting direction Y1 when the refrigerant is uncompressed. In addition, because the bearing spacer 72 is tilted in the first tilting direction Y1, the fifth elastic body 81c that is in contact with the rear surface 622 of the second cover body portion 62a is in a state where, when the refrigerant is uncompressed, the part below the center of the bearing spacer 72 is elastically deformed more than the part above the center of the bearing spacer 72.

[0069] Here, the protruding body 64 and the bearing spacer 72, and consequently the first radial ball bearing 51 provided on the protruding body 64 and the second radial ball bearing 52 provided on the bearing spacer 72, do not necessarily have to be inclined at the same angle as each other, as long as they are inclined in the first tilting direction Y1 when the refrigerant is uncompressed.

[0070] As shown in Figure 1, in the housing 6, the front surface 610a of the first housing cover 61 is in contact with the rear end of the housing body 60, and the rear surface 622 of the second housing cover 62 is in contact with the front end of the housing body 60. The housing body 60, the first housing cover 61, and the second housing cover 62 are fixed in the front-rear direction by a plurality of bolts (not shown).

[0071] Thus, in the housing 6, the housing body 60 is sandwiched in the front-rear direction by the first housing cover 61 and the second housing cover 62, and the front and rear ends of the housing body 60 are closed by the first housing cover 61 and the second housing cover 62, respectively. As a result, a scroll chamber 65 is formed inside the housing body 60 in the housing 6. The scroll chamber 65 is in communication with the intake port 68. Therefore, refrigerant is drawn into the scroll chamber 65 from outside the housing 6 through the intake port 68.

[0072] Furthermore, as described above, the projection 64 is attached to the first housing cover 61, so the projection 64 is positioned within the scroll chamber 65. Within the scroll chamber 65, the projection 64 protrudes forward from the first housing cover 61 toward the drive scroll 30 and the driven scroll 40. Similarly, the bearing spacer 72 attached to the second cover body 62a is also positioned within the scroll chamber 65. Within the scroll chamber 65, the bearing spacer 72 is positioned further forward than the projection 64. As a result, the second radial ball bearing 52 provided on the bearing spacer 72 is positioned further forward within the scroll chamber 65 than the first radial ball bearing 51 provided on the projection 64.

[0073] The electric motor 10 is housed within the scroll chamber 65. Thus, the scroll chamber 65 also serves as the motor chamber housing the electric motor 10.

[0074] As shown in Figure 2, the electric motor 10 is composed of a stator 17 and a rotor 11. The stator 17 has a stator core 17a and windings 17b. The stator core 17a is formed in a cylindrical shape that extends in the axial direction X1 of the housing 6. The windings 17b are wound around the stator core 17a. As a result, the windings 17b form a first coil end 171 and a second coil end 172.

[0075] The first coil end 171 protrudes forward in a cylindrical shape from the stator core 17a. 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 backward in a cylindrical shape from the stator core 17a.

[0076] In the stator 17, the stator core 17a is fitted onto the outer circumferential surface of the second diameter portion 64b. In other words, the stator core 17a is tightly fitted to the outer circumferential surface of the second diameter portion 64b. In this way, the stator core 17a is fixed to the outer circumferential surface of the second diameter portion 64b, and consequently to the outer circumferential surface of the protruding body 64. Although not shown in the figures, multiple slits extending in the front-rear direction are formed on the inner circumferential surface of the stator core 17a. As a result, the slits form a gap between the stator core 17a and the outer circumferential surface of the second diameter portion 64b while the stator core 17a is fixed to the second diameter portion 64b.

[0077] As described above, the protruding body 64 is tilted in the first tilting direction Y1 when the refrigerant is uncompressed. Therefore, the stator 17 is also tilted in the first tilting direction Y1 when the refrigerant is uncompressed.

[0078] The rotor 11 is formed in a cylindrical shape that extends in the axial direction X1 of the housing 6. Although detailed illustrations are omitted, the rotor 11 is composed of a plurality of permanent magnets corresponding to the stator 17 and laminated steel plates that fix each permanent magnet. The rotor 11 is also formed to be larger in diameter than the stator core 17a. As a result, the rotor 11 covers the stator core 17a from the outside within the scroll chamber 65. Furthermore, the rotor 11 has a plurality of first bolt holes 11a. Each first bolt hole 11a penetrates the rotor 11 in the axial direction X1 of the housing 6.

[0079] As shown in Figure 1, the scroll compression unit 3 is housed within the scroll chamber 65. The scroll compression unit 3 comprises a drive scroll 30, a driven scroll 40, and a driven mechanism 20.

[0080] The drive scroll 30 is made of aluminum alloy. The drive scroll 30 includes a drive end plate 31, a drive spiral body 33, a drive peripheral wall 35, a cover body 37, and a case 39.

[0081] The drive end plate 31 is formed in a substantially disc shape that extends radially from the housing 6. The drive end plate 31 has a first front surface 311 that faces forward and a first rear surface 312 that is located on the opposite side of the first front surface 311 and faces rear.

[0082] Furthermore, a discharge port 32 is formed in the drive end plate 31. The discharge port 32 penetrates the drive end plate 31 in the front-rear direction. In addition, a discharge reed valve 57 and a retainer 58 are fixed to the first front surface 311 of the drive end plate 31 by fixing bolts 59. As a result, the discharge reed valve 57 can open and close the discharge port 32. The retainer 58 can adjust the opening degree of the discharge reed valve 57.

[0083] The drive spiral body 33 is integral with the drive end plate 31 and extends from the first rear surface 312 toward the rear, i.e., toward the driven scroll 40, in the axial direction X1 of the housing 6. Although detailed illustration is omitted, the drive spiral body 33 has the center of the drive end plate 31 as its spiral center and extends outward from the spiral center.

[0084] The drive circumferential wall 35 is formed in a cylindrical shape, having the same diameter as the drive end plate 31 and extending in the axial direction X1 of the housing 6. The front end of the drive circumferential wall 35 is integral with the drive end plate 31. As a result, the drive circumferential wall 35 surrounds the drive vortex body 33 from the outside and extends cylindrically toward the rear from the first rear surface 312. Although not shown in the figures, the outer circumferential end of the vortex in the drive vortex body 33 is connected to the inner circumferential surface of the drive circumferential wall 35.

[0085] As shown in Figure 2, the cover body 37 has a wall portion 37a, an inner cylindrical portion 37b, and an outer cylindrical portion 37c. The wall portion 37a is formed in a substantially disc shape that extends radially from the housing 6. The wall portion 37a has a second front surface 371 that faces forward and a second rear surface 372 that is located on the opposite side of the second front surface 371 and faces rear.

[0086] A recess 373 and an intake port 374 are formed in the wall portion 37a. The recess 373 is located approximately in the center of the second front surface 371 and is recessed from the second front surface 371 toward the rear.

[0087] The intake port 374 is positioned radially outward from the recess 373 of the housing 6. The intake port 374 penetrates the wall portion 37a in the front-rear direction. As a result, the front end of the intake port 374 opens to the second front surface 371, and the rear end opens to the second rear surface 372. Multiple intake ports 374 may be formed in the wall portion 37a.

[0088] Furthermore, multiple rings 22 are attached to the wall portion 37a at the location between the recess 373 and the intake port 374. Although detailed illustrations are omitted, each ring 22 is arranged at equal intervals in the circumferential direction of the recess 373 when facing forward, and surrounds the recess 373 from the outside. In this embodiment, there are six rings 22. Figures 1, 2, and 5 illustrate one of the six rings 22.

[0089] As shown in Figure 2, the inner cylindrical portion 37b is located in the radial direction of the housing 6, inside the stator 17, and extends cylindrically backward from the second rear surface 372 of the wall portion 37a. The inner cylindrical portion 37b is in communication with the recess 373. The inner diameter of the inner cylindrical portion 37b is larger than the outer diameter of the first radial ball bearing 51 of the protruding body 64. The outer diameter of the inner cylindrical portion 37b is smaller than the outer diameter of the second diameter portion 64b.

[0090] The outer cylindrical portion 37c is connected to the wall portion 37a and extends cylindrically from the wall portion 37a toward the rear. The outer diameter of the outer cylindrical portion 37c is formed to be approximately the same as the outer diameter of the wall portion 37a, the outer diameter of the drive peripheral wall 35, and the outer diameter of the rotor 11.

[0091] Furthermore, the inner diameter of the outer cylindrical portion 37c is formed to be larger than the outer diameter of the inner cylindrical portion 37b. As a result, in the cover body 37, the inner cylindrical portion 37b is positioned on the inner circumference side of the outer cylindrical portion 37c, separated from the outer cylindrical portion 37c in the radial direction of the housing 6. In this way, the cover body 37 has a housing portion 38 formed by the wall portion 37a, the inner cylindrical portion 37b, and the outer cylindrical portion 37c. The housing portion 38 has a bottomed annular shape that opens at the rear.

[0092] The intake port 374 formed in the wall portion 37a is located in the radial direction of the housing 6, outside the inner cylindrical portion 37b and inside the outer cylindrical portion 37c. Thus, the intake port 374 communicates with the housing portion 38 at a point between the inner cylindrical portion 37b and the outer cylindrical portion 37c.

[0093] Furthermore, multiple second bolt holes 376 are formed in the outer cylindrical portion 37c and the wall portion 37a. Each second bolt hole 376 penetrates the outer cylindrical portion 37c and the wall portion 37a in the front-rear direction. Although not shown in the figures, the number of second bolt holes 376 is equal to the number of first bolt holes 11a formed in the rotor 11. In Figures 1, 2, and 5, one of the multiple first bolt holes 11a and one of the second bolt holes 376 are shown.

[0094] As shown in Figure 1, the cover body 37 has its second front surface 371 of the wall portion 37a in contact with the rear end of the drive peripheral wall 35. The cover body 37 also has the rotor 11 in contact with the rear end of the outer cylindrical portion 37c. In this state, the first bolts 34a are inserted from the rotor 11 side through the first bolt holes 11a and the second bolt holes 376 in that order, and the first bolts 34a are screwed into the drive peripheral wall 35. In this way, the cover body 37 is fixed to the drive peripheral wall 35 and the rotor 11, while being sandwiched in the front-rear direction between the drive peripheral wall 35 and the rotor 11. As a result, the drive scroll 30 is integrated with the rotor 11.

[0095] The case 39 is a bottomed cylindrical member having an outer peripheral wall 39a and a front wall 39b. The outer peripheral wall 39a has a cylindrical shape extending in the axial direction X1 of the housing 6. The outer diameter of the outer peripheral wall 39a is formed to be approximately the same as the outer diameter of the drive peripheral wall 35.

[0096] As shown in Figure 3, the front wall 39b is located at the front end of the case 39. The front wall 39b is formed in a substantially disc shape that extends radially from the housing 6. The front wall 39b is connected to the front end of the outer peripheral wall 39a. A boss 39c is also formed on the front wall 39b. The boss 39c is integrally formed in the center of the front wall 39b and protrudes cylindrically forward from the front wall 39b. The outer diameter of the boss 39c is larger than the outer diameter of the bearing holding portion 72c of the bearing spacer 72, and smaller than the inner diameter of the second wall portion 72b. The inner diameter of the boss 39c is also larger than the outer diameter of the second radial ball bearing 52.

[0097] Furthermore, a through hole 39d is formed in the front wall 39b at the location on the inside of the boss 39c. The through hole 39d penetrates the front wall 39b in the front-rear direction.

[0098] Furthermore, third bolt holes 39e are formed in the outer perimeter wall 39a and the front wall 39b. The third bolt holes 39e penetrate the outer perimeter wall 39a and the front wall 39b in the front-rear direction. Although not shown in the figures, multiple third bolt holes 39e are formed in the outer perimeter wall 39a and the front wall 39b. Figures 1 and 3 show one of these multiple third bolt holes 39e.

[0099] As shown in Figure 1, the case 39 has its rear outer wall 39a in contact with the front end of the drive circumferential wall 35. In this state, the second bolts 34b are inserted through each of the third bolt holes 39e and screwed into the drive circumferential wall 35. In this way, the case 39 is fixed to the drive circumferential wall 35 in the drive scroll 30.

[0100] As the case 39 is fixed to the drive peripheral wall 35 in this manner, a discharge chamber 14 is formed inside the outer peripheral wall 39a, between the front wall 39b of the case 39 and the drive end plate 31. The discharge chamber 14 communicates with the discharge port 32 as well as the insertion hole 39d.

[0101] The driven scroll 40 is made of aluminum alloy. The driven scroll 40 has a driven end plate 41 and a driven spiral body 43.

[0102] The driven end plate 41 is formed in a substantially disc shape that extends radially from the housing 6. The driven end plate 41 has a third front surface 411 that faces forward and a third rear surface 412 that is located on the opposite side of the third front surface 411 and faces rear.

[0103] A receiving recess 15 is formed in the driven end plate 41. The receiving recess 15 is located in the center of the driven end plate 41. The receiving recess 15 is cylindrically recessed extending forward from the third rear surface 412 of the driven end plate 41. As a result, the receiving recess 15 faces the rear of the driven end plate 41, and consequently the first diameter portion 64a of the protruding body 64.

[0104] As shown in Figure 2, a driven shaft portion 16 and a third radial ball bearing 13 are provided within the housing recess 15. The third radial ball bearing 13 has a third inner ring 13a and a third outer ring 13b. The outer diameter of the third outer ring 13b, i.e., the outer diameter of the third radial ball bearing 13, is formed to be smaller than the inner diameter of the housing recess 15. As a result, the third radial ball bearing 13 is fitted into the housing recess 15 with a clearance.

[0105] The driven shaft portion 16 has a bush 53 and a driven pin 55. The bush 53 is positioned within the housing recess 15 and is press-fitted onto the third inner ring 13a of the third radial ball bearing 13. As a result, the bush 53 is fixed to the third radial ball bearing 13 and integrated with the third radial ball bearing 13.

[0106] The driven pin 55 is inserted through the bush 53. More specifically, the driven pin 55 is inserted through the bush 53 at a position eccentric to the center of the bush 53. As a result, the driven pin 55 protrudes rearward from the bush 53 and, consequently, from the driven end plate 41.

[0107] Furthermore, a pivot pin 21 is fixed to the driven end plate 41 at the location facing the ring 22. The pivot pin 21 protrudes rearward from the third rear surface 412. Six pivot pins 21 are fixed to the driven end plate 41, the same number as the rings 22. Figures 1, 2, and 5 illustrate one of the six pivot pins 21.

[0108] The driven mechanism 20 is then composed of these pivot pins 21 and rings 22. Here, the number of pivot pins 21 and rings 22 can be designed as appropriate, as long as there are three or more of each.

[0109] As shown in Figure 1, the driven spiral body 43 is integral with the driven end plate 41 and extends forward from the third front surface 411 of the driven end plate 41. The driven spiral body 43 extends outward in a spiral shape from the spiral center, with the center of the driven end plate 41 being the spiral center.

[0110] In this compressor, the driven scroll 40 is housed within the drive scroll 30, more specifically, in the drive scroll 30, at a location between the drive spiral body 33 and the drive peripheral wall 35 and the cover body 37. The drive spiral body 33 and the driven spiral body 43 are then meshed together. As a result, the drive spiral body 33 and the driven spiral body 43 face each other to form a compression chamber 12.

[0111] Furthermore, a suction section 30a is formed between the drive peripheral wall 35 and the driven scroll 40. In other words, the drive spiral body 33 and the driven spiral body 43 are located within the suction section 30a. The suction section 30a is separated from the scroll chamber 65 by the drive peripheral wall 35 and the cover body 37, and is also separated from the discharge chamber 14 by the drive end plate 31. The suction section 30a is also in communication with the suction port 374.

[0112] Furthermore, by housing the driven scroll 40 within the driven scroll 30, each orbital pin 21 is positioned within each ring 22. In this way, the drive scroll 30 and the driven scroll 40 are assembled in the front-rear direction to form the scroll compression section 3. More precisely, after the drive spiral body 33 and the driven spiral body 43 are meshed and each orbital pin 21 is inserted into each ring 22, the cover body 37 of the drive scroll 30 is fixed to the drive peripheral wall 35 and the rotor 11.

[0113] Furthermore, when the drive scroll 30 and the driven scroll 40 are assembled, the housing recess 15 of the driven end plate 41 and the driven shaft portion 16 face the recess 373 of the cover body 37.

[0114] The scroll compression section 3 is positioned in front of the stator 17 within the scroll chamber 65. As shown in Figure 2, in the scroll compression section 3, the inner cylindrical portion 37b of the cover body 37 is inserted into the inner circumference of the first coil end 171. In this state, the first diameter portion 64a of the protruding body 64 and the first radial ball bearing 51 are inserted into the inner cylindrical portion 37b.

[0115] As described above, the inner diameter of the inner cylinder portion 37b is formed to be larger than the outer diameter of the first radial ball bearing 51. As a result, in the first radial ball bearing 51, the first outer ring 51b is fitted into the inner cylinder portion 37b with a clearance. In this way, the drive scroll 30, and by extension the scroll compression portion 3, is rotatably supported by the first radial ball bearing 51. In other words, the first radial ball bearing 51 rotatably supports the scroll compression portion 3 while being mounted on the protruding body 64.

[0116] As described above, the protruding body 64 and the first radial ball bearing 51 provided on the first diameter portion 64a are inclined in the first tilting direction Y1 when the refrigerant is uncompressed. On the other hand, when inserting the first radial ball bearing 51 into the inner cylindrical portion 37b of the scroll compression section 3, it is inclined in the opposite direction to the first tilting direction Y1 with respect to the axial direction X1 of the housing 6. In other words, the scroll compression section 3 is inclined downwards toward the bottom of the compressor as it moves from the rear to the front. While maintaining this posture, the scroll compression section 3 is rotatably supported by the first radial ball bearing 51.

[0117] Furthermore, because the scroll compression section 3 is rotatably supported by the first radial ball bearing 51 in this manner, the housing section 38 is in communication with the scroll chamber 65. The first coil end 171 is housed within the housing section 38. As a result, within the housing section 38, the first coil end 171 is covered from the front by the wall section 37a and from the radially inner side of the drive scroll 30 by the inner cylindrical section 37b. The first coil end 171 is also covered from the radially outer side of the drive scroll 30 by the outer cylindrical section 37c within the housing section 38.

[0118] Furthermore, as shown in Figure 1, in the scroll compression section 3, the boss 39c of the case 39 is inserted inside the second wall portion 72b of the bearing spacer 72. At this time, as described above, the scroll compression section 3 is inclined in the direction opposite to the first tilting direction Y1. In this state, the boss 39c has the second radial ball bearing 52 inserted inside itself. Here, since the inner diameter of the boss 39c is formed to be larger than the outer diameter of the second radial ball bearing 52, the second outer ring 52b of the second radial ball bearing 52 is fitted with a clearance relative to the boss 39c. Also, the portion of the bearing holding portion 72c that is rearward of the second radial ball bearing 52 is inserted into the insertion hole 39d. In this way, the drive scroll 30, and by extension the scroll compression section 3, is rotatably supported by the second radial ball bearing 52. In other words, the second radial ball bearing 52 rotatably supports the scroll compression section 3 while being provided on the bearing spacer 72.

[0119] Thus, the drive scroll 30, and by extension the scroll compression section 3, is rotatably supported on its rear side by the first radial ball bearing 51 and on its front side by the second radial ball bearing 52. In other words, the scroll compression section 3 is rotatable within the scroll chamber 65 because it is rotatably supported in both the front-rear and rear directions by the first radial ball bearing 51 and the second radial ball bearing 52.

[0120] Furthermore, when the refrigerant is uncompressed, the scroll compression section 3 is inclined in the direction opposite to the first tilt direction Y1 with respect to the axial direction X1 of the housing 6, as described above. Also, since the rotor 11 is integrated with the drive scroll 30, when the scroll compression section 3 is in the above-described position, the rotor 11 is also inclined downwards toward the bottom of the compressor as it moves from the rear to the front when the refrigerant is uncompressed. Note that in Figure 2, for the sake of ease of explanation, the positions of the first radial ball bearing 51 and the scroll compression section 3 are exaggerated, as are the gaps between the first radial ball bearing 51 and the inner cylinder portion 37b in the radial direction of the housing 6. Similarly, in Figure 3, the positions of the second radial ball bearing 52 and the scroll compression section 3 are exaggerated, as are the gaps between the second radial ball bearing 52 and the boss 39c in the radial direction of the housing 6.

[0121] Furthermore, as shown in Figure 2, in the scroll compression section 3, the driven pin 55 of the driven shaft 16 is inserted into the pin hole 4. As a result, the driven scroll 40 is positioned in front of the projection 64 and is rotatably supported by the first diameter 64a. In this case, since the scroll compression section 3 is tilted in the opposite direction to the first tilt direction Y1 with respect to the axial direction X1 of the housing 6, the driven scroll 40 is tilted in the opposite direction to the first tilt direction Y1 with respect to the driven shaft 16 and the third radial ball bearing 13. Thus, in the scroll compression section 3, unlike the drive scroll 30, the driven scroll 40 is rotatably supported only by the projection 64.

[0122] Furthermore, by being rotatably supported on the first diameter portion 64a in this manner, the driven scroll 40 is rotatably supported on the protrusion 64 in front of the stator core 17a. In other words, the driven scroll 40 is rotatably supported on the protrusion 64 on the compression chamber 12 side of the stator core 17a.

[0123] Furthermore, as shown in Figure 3, in the bearing spacer 72, the bearing retaining portion 72c is inserted into the through hole 39d, thereby connecting the discharge passage 724 to the through hole 39d. As a result, the discharge passage 724 connects the discharge chamber 14 and the discharge communication port 69. Moreover, in the bearing spacer 72, the second sealing member 74 elastically deforms in the radial direction of the housing 6 between the outer circumferential surface of the bearing retaining portion 72c and the inner circumferential surface of the through hole 39d, sealing the space between the bearing retaining portion 72c and the through hole 39d.

[0124] In this compressor configured as described above, as shown by the dashed arrows in Figures 1 and 2, low-temperature, low-pressure refrigerant that has passed through the evaporator is drawn into the scroll chamber 65 from the intake port 68. When the electric motor 10 operates and the rotor 11 rotates, the scroll compression section 3 rotates within the scroll chamber 65. Specifically, in the scroll compression section 3, the rotation of the rotor 11 is transmitted to the drive scroll 30, causing the drive scroll 30 to rotate around the drive axis O1. In other words, the drive scroll 30 and the rotor 11 rotate together. At this time, in the driven mechanism 20, each orbital pin 21 slides against the inner circumferential surface of each ring 22, causing each ring 22 to rotate relatively around the center of each orbital pin 21. In this way, the driven mechanism 20 transmits the torque of the drive scroll 30 to the driven scroll 40.

[0125] As a result, in the scroll compression section 3, the driven scroll 40 is rotated by the drive scroll 30 and the driven mechanism 20 around the driven axis O2. At this time, the driven mechanism 20 restricts the driven scroll 40 from rotating on its own axis. As a result, the driven scroll 40 revolves relative to the drive scroll 30 around the driven axis O2. The driven axis O2 is parallel to the drive axis O1. Also, the driven axis O2 is eccentric with respect to the drive axis O1. Then, in the scroll compression section 3, the drive vortex 33 and the driven vortex 43 rotate within the suction section 30a, thereby changing the volume of the compression chamber 12.

[0126] Furthermore, the refrigerant drawn into the scroll chamber 65 flows between the rotor 11 and the stator 17, as shown by the dashed arrows in Figures 1 and 2, and reaches the housing section 38. The refrigerant drawn into the scroll chamber 65 also reaches the housing section 38 by flowing through slits formed in the stator core 17a. In addition, the refrigerant drawn into the scroll chamber 65 also reaches the housing section 38 by flowing through the gap between the slot (not shown) that houses the winding 17b formed in the stator core 17a and the winding 17b. In this way, the refrigerant in the housing section 38 is drawn into the compression chamber 12 from the intake port 374 through the intake section 30a.

[0127] The compression chamber 12 compresses the refrigerant by reducing its own volume while confining it within itself, through the rotational drive of the drive scroll 30 and the rotational movement of the driven scroll 40. The high-temperature, high-pressure refrigerant, thus compressed to the discharge pressure, is discharged as compressed refrigerant from the discharge port 32 into the discharge chamber 14, as shown by the dashed arrow in Figure 3.

[0128] In this way, the compressed refrigerant discharged into the discharge chamber 14 flows through the insertion hole 39d and into the discharge passage 724 of the bearing spacer 72 toward the discharge port 69. The compressed refrigerant that reaches the discharge port 69 then flows through the piping connected to the discharge port 69 and is discharged to the outside of the compressor.

[0129] Incidentally, in this compressor, when the refrigerant is compressed, that is, during operation, the scroll compression section 3 is subjected to the compressive reaction force of the refrigerant compressed in the compression chamber 12. In this respect, this compressor is capable of suitably supporting the scroll compression section 3, which is rotated by the first radial ball bearing 51 and the second radial ball bearing 52 when the refrigerant is compressed. This operation will be explained in detail based on a comparison with a comparative example.

[0130] In the comparative example compressor shown in Figure 4, when the refrigerant is uncompressed, the protruding body 64 and the bearing spacer 72 are positioned approximately parallel to the axial direction X1 of the housing 6. Therefore, the first radial ball bearing 51 provided on the protruding body 64 and the second radial ball bearing 52 provided on the bearing spacer 72 are positioned approximately parallel to the axial direction X1 of the housing 6. As a result, in the comparative example compressor, when the refrigerant is uncompressed, the first radial ball bearing 51 and the second radial ball bearing 52 support the scroll compression section 3 in a position approximately parallel to the axial direction X1 of the housing 6. Other configurations in the comparative example compressor are the same as those of the compressor in Example 1. Also, in Figure 4, for the sake of ease of explanation, the shape of the scroll compression section 3 and other components are simplified, and the driven mechanism 20 and other components are omitted from the illustration.

[0131] As described above, a compression reaction force acts on the scroll compression section 3 when the refrigerant is compressed, and a tilt moment M1 based on this compression reaction force acts on the scroll compression section 3. This tilt moment M1 attempts to tilt the scroll compression section 3 in the first tilt direction Y1 with respect to the axial direction X1 of the housing 6, with the support center C11 of the first radial ball bearing 51 as the center of tilt. Therefore, when the scroll compression section 3 is operating, it tilts in the first tilt direction Y1 due to this tilt moment M1. Note that as long as the scroll compression section 3 is tilted in the first tilt direction Y1, the angle of tilt at that time does not necessarily have to be the same as the angle of tilt of the scroll compression section 3 shown in Figure 4, etc.

[0132] Furthermore, when such a tilting moment M1 acts on the scroll compression section 3, a tilting moment M2 acting on the first radial ball bearing 51 and the protruding body 64 is exerted in the opposite direction to the tilting moment M1. Therefore, during operation, the protruding body 64 tilts around the tilting center C2 in the opposite direction to the first tilting direction Y1 due to this tilting moment M2.

[0133] Furthermore, a tilting moment M3 acts on the second radial ball bearing 52 and the bearing spacer 72. Therefore, during operation, the bearing spacer 72 tilts around the tilting center C3 due to this tilting moment M3. Here, since the bearing spacer 72 is supported on the inner circumferential surface 662 of the support portion 66 by the third elastic body 81a and the fourth elastic body 81b, the support centers of the third elastic body 81a and the fourth elastic body 81b become the tilting center C3 of the bearing spacer 72. The tilting center C3 of the bearing spacer 72 is located below the support center C12 of the second radial ball bearing 52 relative to the scroll compression portion 3, and in front of the support center C12. Therefore, the tilting moment M3 acting on the bearing spacer 72 is in the same direction as the tilting moment M2. As a result, during operation, the bearing spacer 72 tilts around the tilting center C3 in the opposite direction to the first tilting direction Y1.

[0134] As a result, in the comparative example compressor, when the refrigerant is compressed, the first radial ball bearing 51 and the second radial ball bearing 52 support the scroll compression section 3 in a position that is inclined with respect to the axial direction X1 of the housing 6. Consequently, in the comparative example compressor, the first radial ball bearing 51 and the second radial ball bearing 52 have difficulty adequately supporting the scroll compression section 3 when the refrigerant is compressed, resulting in increased power loss during refrigerant compression.

[0135] Furthermore, when the refrigerant is compressed, the first radial ball bearing 51 and the second radial ball bearing 52 support the scroll compression section 3 in an inclined position with respect to the axial direction X1 of the housing 6. As a result, in the comparative example compressor, the first radial ball bearing 51 and the second radial ball bearing 52 are prone to uneven wear.

[0136] In contrast, in the compressor of Embodiment 1, the projection 64 attached to the first housing cover 61 is tilted in the first tilting direction Y1 when the refrigerant is uncompressed. Similarly, the first radial ball bearing 51 provided on the projection 64 is also tilted in the first tilting direction Y1 when the refrigerant is uncompressed. Therefore, when the refrigerant is compressed, the projection 64 tilts around the tilting center C2 in the opposite direction to the first tilting direction Y1 due to the tilting moment M2, thereby correcting the position of the projection 64 which is already tilted in the first tilting direction Y1. Thus, as shown in Figure 1, when the refrigerant is compressed, the projection 64 can be displaced to a position approximately parallel to the axial direction X1 of the housing 6. Furthermore, as the projection 64 is displaced to a position approximately parallel to the axial direction X1 of the housing 6, the first radial ball bearing 51 provided on the projection 64 can also be displaced to a position approximately parallel to the axial direction X1 of the housing 6 when the refrigerant is compressed. Furthermore, when compressing the refrigerant, the orientation of the driven scroll 40 relative to the driven shaft portion 16 and the third radial ball bearing 13 within the housing recess 15 can also be similarly corrected.

[0137] Furthermore, the bearing spacer 72 attached to the second cover body 62a is also tilted in the first tilting direction Y1 when the refrigerant is uncompressed. Therefore, when the refrigerant is compressed, the bearing spacer 72 tilts around the tilting center C3 in the opposite direction to the first tilting direction Y1 due to the tilting moment M3, thereby correcting the position of the bearing spacer 72 which is already tilted in the first tilting direction Y1. In this way, when the refrigerant is compressed, the bearing spacer 72, and furthermore, the second radial ball bearing 52 provided on the bearing spacer 72, can be displaced to a position approximately parallel to the axial direction X1 of the housing 6.

[0138] Thus, in the compressor of Embodiment 1, the first radial ball bearing 51 and the second radial ball bearing 52 can support the scroll compression section 3 in a position substantially parallel to the axial direction X1 of the housing 6 when the refrigerant is compressed. As a result, the first radial ball bearing 51 and the second radial ball bearing 52 can suitably support the rotating scroll compression section 3 when the refrigerant is compressed, and therefore, power loss during refrigerant compression can be reduced in the compressor of Embodiment 1.

[0139] Furthermore, because the first radial ball bearing 51 and the second radial ball bearing 52 support the scroll compression section 3 in a position substantially parallel to the axial direction X1 of the housing 6 when the refrigerant is compressed, the scroll compression section 3 can rotate in a position substantially parallel to the axial direction X1 of the housing 6 when the refrigerant is compressed, even if the aforementioned tilting moment M1 acts on it. In other words, in the scroll compression section 3, the drive scroll 30 can be rotationally driven around a drive axis O1 substantially parallel to the axial direction X1 of the housing 6, and the driven scroll 40 can be rotationally driven around a driven axis O2 substantially parallel to the axial direction X1 of the housing 6.

[0140] Furthermore, when the refrigerant is compressed, the first radial ball bearing 51 and the second radial ball bearing 52 support the scroll compression section 3 in a position substantially parallel to the axial direction X1 of the housing 6. As a result, in the compressor of Embodiment 1, the first radial ball bearing 51 and the second radial ball bearing 52 are less prone to uneven wear.

[0141] Therefore, the compressor of Example 1 has excellent operating efficiency and durability.

[0142] In particular, in this compressor, the protruding body 64 is tilted in the first tilting direction Y1 when the refrigerant is uncompressed, due to the first and second elastic bodies 70a and 70b, and consequently the one-sided elastic body 70, provided between the second diameter portion 64b and the extension portion 61b of the protruding body 64. This makes it possible to easily tilt the protruding body 64, which is attached to the first housing cover 61, in the first tilting direction Y1 in this compressor. Furthermore, in this compressor, the one-sided elastic body 70 elastically deforms when the refrigerant is compressed, making it possible to suitably displace the protruding body 64 and the first radial ball bearing 51 to a position substantially parallel to the axial direction X1 of the housing 6. When the tilting moment M2 acting on the protruding body 64 decreases, including at the end of refrigerant compression, the one-sided elastic body 70 elastically deforms, making it possible to return the protruding body 64 to the position tilted in the first tilting direction Y1.

[0143] Similarly, in this compressor, the other elastic body 81 makes it possible to easily tilt the bearing spacer 72 to a position inclined in the first tilting direction Y1 when the refrigerant is uncompressed. Then, as the other elastic body 81 elastically deforms, it is possible to suitably displace the bearing spacer 72 and the second radial ball bearing 52 to a position substantially parallel to the axial direction X1 of the housing 6. Furthermore, when the tilting moment M3 acting on the bearing spacer 72 decreases, including at the end of refrigerant compression, the other elastic body 81 elastically deforms, making it possible to return the bearing spacer 72 to a position inclined in the first tilting direction Y1.

[0144] Furthermore, in this compressor, vibrations generated in the electric motor 10 and the scroll compression section 3 during operation are inevitably transmitted to the protruding body 64. In this respect, in this compressor, the elastic deformation of one elastic body 70 between the second diameter section 64b and the extension section 61b of the protruding body 64 effectively suppresses the transmission of vibrations transmitted from the electric motor 10 and the scroll compression section 3 to the protruding body 64 to the first housing cover 61. Moreover, in this compressor, the elastic deformation of the other elastic body 81 between the bearing spacer 72 and the support section 66 effectively suppresses the transmission of vibrations generated in the scroll compression section 3 to the second cover body section 62a through the bearing spacer 72. As a result, vibrations of the housing 6 during operation are effectively suppressed in this compressor.

[0145] As shown in Figure 5, in the compressor of Embodiment 2, the first housing cover 61 has an extension portion 61c. The extension portion 61c is integrally formed with the first cover body portion 61a and extends cylindrically from the front surface 610a of the first cover body portion 61a toward the scroll chamber 65. In this case, the extension portion 61c extends while inclined in the first tilting direction Y1 from the front surface 610a.

[0146] Furthermore, the extension portion 61c also has retaining grooves 611 and 612 formed therein, similar to the extension portion 61b, and the first elastic body 70a and the second elastic body 70b are housed in these retaining grooves 611 and 612, respectively. As a result, similar to the compressor in Embodiment 1, the first elastic body 70a and the second elastic body 70b are arranged in this compressor with their centers offset from each other in the radial direction of the housing 6. The other components of this compressor are the same as those of the compressor in Embodiment 1, and the same reference numerals are used for the same components, and a detailed explanation of the components is omitted.

[0147] In this compressor, in addition to the positional relationship between the first elastic body 70a and the second elastic body 70b in the extension portion 61c, the shape of the extension portion 61c that extends inclined in the first tilting direction Y1 also makes it possible to tilt the protruding body 64 in the first tilting direction Y1 when attached to the first housing cover 61. As a result, in this compressor, by adjusting the positional relationship between the first elastic body 70a and the second elastic body 70b in the extension portion 61c and the tilt angle of the extension portion 61c in the first tilting direction Y1, it is possible to suitably tilt the protruding body 64 in the first tilting direction Y1. Other functions of this compressor are the same as those of the compressor in Embodiment 1.

[0148] Although the present invention has been described above in reference to Examples 1 and 2, it goes without saying that the present invention is not limited to Examples 1 and 2, and can be applied with appropriate modifications without departing from its spirit.

[0149] For example, in the compressors of Examples 1 and 2, both the protruding body 64 and the bearing spacer 72 are tilted in the first tilting direction Y1 when the refrigerant is uncompressed, so that both the first radial ball bearing 51 and the second radial ball bearing 52 are tilted in the first tilting direction Y1 when the refrigerant is uncompressed. However, the configuration is not limited to this, and when the refrigerant is uncompressed, only one of the protruding body 64 and the bearing spacer 72 is tilted in the first tilting direction Y1, so that only one of the first radial ball bearing 51 and the second radial ball bearing 52 is tilted in the first tilting direction Y1 when the refrigerant is uncompressed.

[0150] Furthermore, when the refrigerant is uncompressed, only one of the protruding body 64 and the bearing spacer 72 may be tilted in the first tilting direction Y1, while the other of the protruding body 64 and the bearing spacer 72 may be in a position parallel to the axial direction X1 of the housing 6.

[0151] Furthermore, in the compressors of Examples 1 and 2, the first tilting direction Y1 is defined as the direction in which the compressor tilts upward as it moves from the rear to the front of the compressor, relative to the axial direction X1 of the housing 6. However, the first tilting direction Y1 is not limited to this, and may be any other direction as long as it is tilted relative to the axial direction X1 of the housing 6. Accordingly, when the refrigerant is not compressed, the scroll compression section 3 may be supported by the first radial ball bearing 51 and the second radial ball bearing 52 in a position in which it tilts upward as it moves from the rear to the front of the compressor.

[0152] Furthermore, in the compressors of Examples 1 and 2, a bearing spacer with a different configuration from the bearing spacer 72 may be used, and a second radial ball bearing 52 may be provided in this bearing spacer. By using a bearing spacer with a different configuration from the bearing spacer 72, the support center of the bearing spacer when it is placed in the support portion 66, and consequently the tilting center of the bearing spacer, may be located behind the support center C12 of the second radial ball bearing 52 with respect to the scroll compression portion 3. In this case, the tilting moment M3 acting on the bearing spacer will be in the opposite direction to the tilting moment M2. Therefore, by tilting the bearing spacer in the opposite direction to the first tilting direction Y1 when the refrigerant is uncompressed, the same operation as the compressors of Examples 1 and 2 can be achieved.

[0153] Furthermore, in the compressors of Examples 1 and 2, the first inner ring 51a of the first radial ball bearing 51 may be gap-fitted into the first diameter portion 64a of the protruding body 64, and the first outer ring 51b of the first radial ball bearing 51 may be tightly fitted into the inner cylindrical portion 37b of the cover body 37. Alternatively, both the first inner ring 51a and the first outer ring 51b may be gap-fitted, or both the first inner ring 51a and the first outer ring 51b may be tightly fitted.

[0154] Furthermore, in the compressors of Examples 1 and 2, the second inner ring 52a of the second radial ball bearing 52 may be fitted with a gap fit to the outer circumferential surface of the bearing retaining portion 72c, and the second outer ring 52b of the second radial ball bearing 52 may be fitted with a pressure fit to the inner circumferential surface of the boss 39c. Alternatively, both the second inner ring 52a and the second outer ring 52b may be fitted with a gap fit, or both the second inner ring 52a and the second outer ring 52b may be fitted with a pressure fit.

[0155] Furthermore, in the compressors of Examples 1 and 2, the third inner ring 13a of the third radial ball bearing 13 may be fitted with a gap on the outer surface of the bush 53, and the third outer ring 13b of the third radial ball bearing 13 may be fitted with a pressure-fit on the inner surface of the housing recess 15. Alternatively, both the third inner ring 13a and the third outer ring 13b may be fitted with a gap, or both the third inner ring 13a and the third outer ring 13b may be fitted with a pressure-fit.

[0156] Furthermore, in the compressors of Examples 1 and 2, the protruding body 64 has a first diameter portion 64a and a second diameter portion 64b. However, it is not limited to this, and the protruding body 64 may be formed only of the first diameter portion 64a, or the protruding body 64 may be formed only of the second diameter portion 64b.

[0157] Furthermore, in the compressors of Examples 1 and 2, the stator 17 is fixed to the second diameter portion 64b, and the stator 17 is covered from the outside by the rotor 11. However, the invention is not limited to this, and the stator 17 may be fixed to the housing 6, and the rotor 11 may be fixed to the cover body 37 inside the stator 17.

[0158] Furthermore, in the compressors of Examples 1 and 2, one side elastic body 70 is composed of first and second elastic bodies 70a and 70b, and the other side elastic body 81 is composed of third to fifth elastic bodies 81a to 81c. However, the compressor is not limited to this configuration, and the one side elastic body 70 and the other side elastic body 81 may have other configurations. Also, the one side elastic body 70 or the other side elastic body 81 may be omitted.

[0159] Furthermore, in the compressor of Embodiment 2, the first elastic body 70a and the second elastic body 70b may be attached coaxially to the extension portion 61c, so that the protruding body 64 is tilted in the first tilting direction Y1 when the refrigerant is uncompressed, solely by the shape of the extension portion 61c.

[0160] Furthermore, this specification includes the following inventions: (Note 1) A double-rotation scroll compressor comprising a housing, a compression section and a drive mechanism, wherein the housing has a scroll chamber in which the compression section and the drive mechanism are housed, the compression section has a drive scroll that is rotationally driven around a drive axis by the drive mechanism and a driven scroll that is rotationally driven around a driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, the drive scroll and the driven scroll form a compression chamber that compresses a fluid by the rotational drive and the rotational drive, the scroll chamber is provided with a first shaft support located on one side in the axial direction of the housing and rotatably supporting the compression section, and a second shaft support located on the other side in the axial direction of the first shaft support and rotatably supporting the compression section, and when a fluid is compressed, a tilt moment acts on the compression section that tilts it in a first tilting direction with respect to the axial direction due to the reaction force of the fluid being compressed in the compression chamber. A double-rotation scroll compressor characterized in that, when the fluid is uncompressible, at least one of the first and second shaft supports the compression section such that the compression section is tilted in the opposite direction to the first tilting direction with respect to the axial direction. (Note 2) The double-rotation scroll compressor according to Note 1, wherein when the fluid is uncompressible, at least one of the first and second shaft supports the compression section in a position tilted in the first tilting direction with respect to the axial direction. (Note 3) The double-rotation scroll compressor according to Note 1 or 2, wherein a projection extending toward the compression section is provided in the scroll chamber, the projection is attached to the housing via an elastically deformable elastic body, and the first shaft support is provided on the projection to rotatably support the drive scroll. (Note 4) The double-rotation scroll compressor according to Note 3, wherein the elastic body tilts the projection in the first tilting direction with respect to the axial direction when the fluid is uncompressible.(Note 5) The double-rotation scroll compressor according to Note 4, wherein the housing has an extension located inside the projection and holding the projection, the elastic body is formed in an annular shape and has a first elastic body and a second elastic body disposed between the projection and the extension in the radial direction of the housing, and the first elastic body and the second elastic body are disposed at a distance from each other in the axial direction with their centers offset in the radial direction. (Note 6) The double-rotation scroll compressor according to any one of Notes 3 to 5, wherein the housing has an extension located inside the projection and holding the projection, the elastic body is disposed between the projection and the extension in the radial direction of the housing, and the extension is inclined in the first tilting direction with respect to the axial direction. (Note 7) The double-rotating scroll compressor according to any one of Notes 1 to 6, wherein a retaining member is attached to the housing and is located in the scroll chamber on the other side in the axial direction from the first shaft support, the second shaft support is provided on the retaining member and rotatably supports the drive scroll, the second shaft support is able to support the drive scroll in a position substantially parallel to the axial direction when the fluid is compressed, and the retaining member is inclined with respect to the axial direction when the fluid is uncompressed.

[0161] This invention can be used in vehicle air conditioning systems and the like.

[0162] 3 Scroll compression section (compression section) 6 Housing 10 Electric motor (drive mechanism) 12 Compression chamber 20 Driven mechanism 30 Driven scroll 40 Driven scroll 51 First radial ball bearing (first shaft support) 52 Second radial ball bearing (second shaft support) 61b Extension section 64 Projection 65 Scroll chamber 70 One-sided elastic body (elastic body) 70a First elastic body 70b Second elastic body 72 Bearing spacer (holding member) M1 Tilt moment O1 Drive shaft center O2 Driven shaft center X1 Axial direction Y1 First tilt direction

Claims

1. A double-rotation scroll compressor comprising a housing, a compression section, and a drive mechanism, wherein the housing has a scroll chamber in which the compression section and the drive mechanism are housed, the compression section has a drive scroll that is rotationally driven around a drive axis by the drive mechanism, and a driven scroll that is rotationally driven around a driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, the drive scroll and the driven scroll form a compression chamber that compresses a fluid by the rotational drive and the rotational drive, the scroll chamber is provided with a first shaft support located on one side in the axial direction of the housing and rotatably supporting the compression section, and a second shaft support located on the other side in the axial direction of the first shaft support and rotatably supporting the compression section, and when the fluid is compressed, a tilt moment acts on the compression section that tilts it in a first tilting direction with respect to the axial direction due to the reaction force of the fluid being compressed in the compression chamber. A double-rotating scroll compressor characterized in that, when the fluid is uncompressible, at least one of the first and second shaft supports the compression section such that the compression section is tilted in the opposite direction to the first tilting direction with respect to the axial direction.

2. The double-rotation scroll compressor according to claim 1, wherein at least one of the first and second shaft supports the compression section in a position inclined in the first tilting direction with respect to the axial direction when the fluid is uncompressible.

3. The double-rotating scroll compressor according to claim 1, wherein a projection is provided in the scroll chamber extending toward the compression section, the projection is attached to the housing via an elastically deformable elastic body, and the first shaft support is provided on the projection to rotatably support the drive scroll.

4. The double-rotation scroll compressor according to claim 3, wherein the elastic body tilts the protruding body in a first tilting direction with respect to the axial direction when the fluid is incompressible.

5. The double-rotating scroll compressor according to claim 4, wherein the housing has an extension located inside the projection and holding the projection, the elastic body has a first elastic body and a second elastic body formed in an annular shape and disposed between the projection and the extension in the radial direction of the housing, and the first elastic body and the second elastic body are disposed at an axial distance with their centers offset from each other in the radial direction.

6. The double-rotation scroll compressor according to any one of claims 3 to 5, wherein the housing has an extension located inside the projection and holding the projection, the elastic body is disposed between the projection and the extension in the radial direction of the housing, and the extension is inclined in the first tilting direction with respect to the axial direction.

7. The double-rotating scroll compressor according to claim 1, wherein a retaining member is attached to the housing and is located in the scroll chamber on the other side in the axial direction from the first shaft support, the second shaft support is provided on the retaining member and rotatably supports the drive scroll, the second shaft support is in a position substantially parallel to the axial direction when the fluid is compressed, and the retaining member is inclined with respect to the axial direction when the fluid is uncompressed.

Images