Scroll compressor

Abstract

Provided is a scroll compressor capable of achieving high quietness over a long period of time and suppressing an increase in manufacturing costs. A compressor of the present invention comprises a housing 6, a first scroll 30, and a second scroll 40. The housing 6 has a scroll chamber 65 and a discharge part 69. Moreover, an elastic body 81 and a sealing part 83 are installed in the housing 6. The elastic body 81 is disposed in the scroll chamber 65 and supports the first scroll 30 while being elastically deformed. The sealing part 83 is formed separately from the elastic body 81 and seals between the scroll chamber 65 and the discharge part 69. The sealing part 83 has an annular shape. A compressed fluid flows radially inward of the sealing part 83 toward the discharge part 69. The elastic body 81 is disposed radially outward of the sealing part 83.

Description

Scroll-type compressor

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

[0002] Patent Document 1 discloses a conventional scroll-type compressor (hereinafter simply referred to as a compressor as appropriate). This compressor includes a housing, a drive mechanism, a first scroll, and a second scroll.

[0003] A high-low pressure separation plate is fixed inside the housing. The interior of the housing is partitioned into a scroll chamber and a discharge space by the high-low pressure separation plate. The scroll chamber accommodates the drive mechanism, the first scroll, and the second scroll. The discharge space communicates with the outside of the housing via a discharge pipe connected to the housing.

[0004] The drive mechanism includes a stator, a rotor rotated by the stator, and a shaft fixed to the rotor. A suction pipe is connected to the first scroll. The suction pipe penetrates the housing and extends to the outside of the housing. Further, a discharge muffler is attached to the first scroll. The second scroll is connected to the shaft. The second scroll forms a compression chamber that compresses fluid between the second scroll and the first scroll. In this document, the fluid is specifically refrigerant gas. The compression chamber communicates with the interior of the discharge muffler.

[0005] In this compressor, the discharge muffler is inserted through the high-low pressure separation plate. Further, an O-ring serving as an elastic body is provided between the discharge muffler and the high-low pressure separation plate. Accordingly, the elastic body elastically deforms between the discharge muffler and the high-low pressure separation plate while supporting the discharge muffler and consequently the first scroll. With the discharge muffler inserted through the high-low pressure separation plate in this manner, the discharge muffler faces the discharge space, and the compression chamber and the discharge space communicate with each other through the discharge muffler.

[0006] In this compressor, the second scroll rotates relative to the first scroll by a drive mechanism, compressing the fluid drawn into the compression chamber by the intake pipe. The fluid compressed in the compression chamber then flows through the inside of the discharge muffler as a high-temperature, high-pressure compressed fluid, reaching the discharge space. The compressed fluid in the discharge space is then discharged to the outside of the housing by the discharge pipe.

[0007] Furthermore, in this compressor, an elastic body elastically supports the first scroll between the discharge muffler and the high / low pressure separator plate, thereby suppressing the transmission of vibrations generated in the first and second scrolls during operation to the housing. Here, the elastic body faces the discharge space and the scroll chamber, respectively. As a result, the elastic body also functions as a sealing part that seals the space between the discharge space and the scroll chamber.

[0008] Japanese Patent Application Publication No. 6-241178

[0009] In the conventional compressor described above, the elastic body not only elastically supports the first scroll but also faces the discharge space and seals the space between the discharge space and the scroll chamber. As a result, the elastic body is directly affected by the high temperature and high pressure atmosphere of the discharge space, making it prone to changes in properties and a decrease in durability. Consequently, in this compressor, the elastic body cannot adequately support the first scroll, making it difficult to suppress the transmission of vibrations generated in the first and second scrolls during operation to the housing, which may impair quietness.

[0010] Therefore, it is conceivable to use an elastic body made of a material that is less susceptible to changes in properties or deterioration of durability even in the high-temperature, high-pressure environment of the discharge space; however, this would result in a significant increase in manufacturing costs.

[0011] This invention has been made in view of the above-mentioned conventional circumstances, and aims to solve the problem of providing a scroll-type compressor that exhibits high quietness over a long period of time and can suppress the soaring of manufacturing costs.

[0012] The scroll compressor of the present invention comprises a housing, a first scroll housed within the housing, and a second scroll housed within the housing and forming a compression chamber between itself and the first scroll for compressing fluid. The housing houses the first scroll and the second scroll and has a scroll chamber from which fluid is drawn in from outside the housing, and a discharge section for discharging the compressed fluid, which is the fluid compressed in the compression chamber, to the outside of the housing. The scroll chamber is provided with an elastic body that supports the first scroll while elastically deforming, and a sealing section that is annular in shape and separate from the elastic body, sealing the space between the scroll chamber and the discharge section. The compressed fluid flows towards the discharge section inside the sealing section in the radial direction of the housing, and the elastic body is positioned radially outward from the sealing section.

[0013] In the scroll compressor of the present invention, an elastic body provided in the scroll chamber supports the first scroll while undergoing elastic deformation. In this compressor, an annular sealing portion is provided in the scroll chamber, and this sealing portion is separate from the elastic body. In this compressor, the compressed fluid compressed in the compression chamber flows radially inside the sealing portion toward the discharge portion. Here, the sealing portion seals the space between the scroll chamber and the discharge portion, thereby preventing the compressed fluid flowing toward the discharge portion and the compressed fluid from the discharge portion from flowing into the scroll chamber.

[0014] Furthermore, although the discharge section becomes a high-temperature, high-pressure environment as the compressed fluid flows through it, in this compressor, the elastic body is located radially outside the sealing section. Therefore, the elastic body is less affected by the high-temperature, high-pressure environment in the discharge section.

[0015] Furthermore, as described above, since the sealing section seals the space between the scroll chamber and the discharge section, this compressor does not require an elastic body to seal the space between the scroll chamber and the discharge section. In this respect as well, the elastic body is less susceptible to the effects of the high-temperature, high-pressure atmosphere in the discharge section.

[0016] As a result, this compressor is less susceptible to changes in the properties of the elastic body or a decrease in durability due to the effects of high temperature and high pressure. Therefore, in this compressor, the elastic body can suitably support the first scroll over a long period of time. Furthermore, in this compressor, there is no need to use an elastic body made of a material that is excessively resistant to high temperature and high pressure environments.

[0017] Therefore, the scroll compressor of the present invention exhibits high quietness over a long period of time and can suppress increases in manufacturing costs.

[0018] In the compressor of the present invention, the first scroll can be rotationally driven around a drive axis by a drive mechanism. Preferably, the second scroll is rotationally driven around a driven axis by the first scroll and the driven mechanism, while being eccentric with respect to the first scroll. In this case, the compressor of the present invention can be a double-rotating scroll type compressor in which both the first scroll and the second scroll rotate.

[0019] The housing may have a main body portion in which a discharge section is formed, and a support member attached to the main body portion and positioned in the scroll chamber, which supports the first scroll around the drive axis. The elastic body and the sealing section may be provided on the main body portion or the support member and positioned between the main body portion and the support member. Preferably, the support member has a discharge passage formed therein, which is located radially inward from the elastic body and the sealing section, communicates with the discharge section, and through which compressed fluid flows toward the discharge section.

[0020] In this case, by providing the elastic body and the sealing member on the main body or the support member, the elastic body and the sealing member can be easily positioned between the main body and the support member. Furthermore, in this compressor, the elastic body can suitably support the first scroll through the support member, and the elastic body can suitably suppress the transmission of vibrations from the first scroll to the main body through the support member during operation.

[0021] Preferably, the elastic body includes at least one of a thrust elastic body disposed between the main body and the support member in the direction of the drive axis, and a radial elastic body disposed between the main body and the support member in the radial direction. In this case, at least one of the thrust elastic body and the radial elastic body can more effectively suppress the transmission of vibrations from the first scroll to the main body through the support member during operation.

[0022] Furthermore, in the compressor of the present invention, the first scroll can be rotationally driven around the drive axis by a drive mechanism. The housing may have a main body portion in which a discharge portion is formed, and a support member attached to the main body portion and arranged in the scroll chamber, which supports the first scroll around the drive axis. The elastic body may be provided on the main body portion or the support member and located radially between the main body portion and the support member. The sealing portion may have a first sealing portion and a second sealing portion that is further away from the first sealing portion in the drive axis direction toward the first scroll. The first sealing portion may be provided on the main body portion or the support member and located between the main body portion and the support member. The second sealing portion may be provided on the support member or the first scroll and located between the support member and the first scroll. Preferably, the support member also has a discharge passage formed therein that is located radially inward from the elastic body, the first sealing portion and the second sealing portion, communicates with the discharge portion, and through which compressed fluid flows toward the discharge portion.

[0023] In this case as well, the elastic body can suitably support the first scroll through the support member, and the elastic body can suitably suppress the transmission of vibrations from the first scroll to the main body through the support member during operation. Furthermore, in this compressor, the sealing section has a first sealing section and a second sealing section. As a result, in this compressor, the space between the scroll chamber and the discharge section can be suitably sealed by the first sealing section and the second sealing section.

[0024] In this compressor, the elastic body is positioned radially between the main body and the support member. Therefore, in this compressor, the first scroll and the support member move radially relative to the main body as the elastic body deforms between the main body and the support member.

[0025] In this compressor, the first sealing portion is provided on the main body or support member and is located between the main body and the support member, while the second sealing portion is provided on the support member or the first scroll and is located between the support member and the first scroll. Therefore, as described above, when the elastic body undergoes elastic deformation and the first scroll and support member move radially relative to the main body, the second sealing portion will also move radially together with the first scroll and support member. As a result, in this compressor, even when the elastic body undergoes elastic deformation, the radial positional relationship between the first scroll, the support member and the second sealing portion remains virtually unchanged. Thus, in this compressor, even when the elastic body undergoes elastic deformation, the space between the scroll chamber and the discharge portion can be sealed by the second sealing portion.

[0026] Furthermore, because the second sealing portion can move radially together with the first scroll and support member, even if the first scroll and support member move radially relative to the main body due to the elastic deformation of the elastic body, excessive load is unlikely to be applied to the second sealing portion. For this reason, the durability of the second sealing portion can also be increased in this compressor.

[0027] Furthermore, in this case, it is preferable that the first sealing portion has a larger diameter than the second sealing portion. This makes it possible to increase the biasing force exerted by the first sealing portion toward the first scroll in the drive axis direction compared to the biasing force exerted by the second sealing portion toward the main body in the drive axis direction. As a result, in this compressor, the support member is less likely to be pressed strongly against the main body in the drive axis direction, and therefore, the transmission of vibrations from the support member to the main body during operation can be effectively suppressed.

[0028] Furthermore, it is preferable that the second sealing portion has a larger diameter than the first sealing portion. This allows the biasing force exerted by the second sealing portion toward the main body in the drive axis direction to be greater than the biasing force exerted by the first sealing portion toward the first scroll in the drive axis direction. As a result, in this compressor, for example, when a bearing that rotatably supports the support member is provided between the first scroll and the support member in the radial direction, thrust loads are less likely to act on the bearing. This increases the durability of the bearing. In addition, in this case, it becomes easier to select the type of bearing that can rotatably support the support member, thus increasing the degree of design freedom.

[0029] Furthermore, in the compressor of the present invention, a bearing may be provided between the first scroll and the support member in the radial direction. The elastic body may have a radial elastic body disposed between the main body and the support member in the radial direction. The radial elastic body may be located radially outward from the bearing. Preferably, the radial elastic body and the bearing overlap radially in at least a portion of their respective parts.

[0030] In this case, the support member can suitably support the first scroll around the drive axis via the bearing. Furthermore, since the radial elastic body and the bearing overlap in the radial direction at least in part, the radial elastic body can suitably support the radial load acting on the bearing in this compressor. As a result, the support member can be stably supported by the radial elastic body in this compressor.

[0031] Furthermore, in the compressor of the present invention, a bearing may be provided between the first scroll and the support member in the radial direction. The elastic body may have a radial elastic body disposed between the main body and the support member in the radial direction. The radial elastic body may have a first radial elastic body and a second radial elastic body located radially outward from the bearing. The first radial elastic body and the second radial elastic body may be spaced apart in the direction of the drive axis. It is also preferable that the bearing is located between the first radial elastic body and the second radial elastic body in the direction of the drive axis.

[0032] In this case as well, the support member can suitably support the first scroll around the drive axis via the bearing. Furthermore, since the radial elastic body has a first radial elastic body and a second radial elastic body, the radial load acting on the bearing can be suitably supported by the first radial elastic body and the second radial elastic body. As a result, in this compressor, the support member can be stably supported by the first radial elastic body and the second radial elastic body.

[0033] Furthermore, in these cases, it is preferable that the elastic body includes a thrust elastic body positioned between the main body and the support member in the direction of the drive axis. This allows the radial elastic body and the thrust elastic body to more effectively suppress the transmission of vibrations from the support member to the main body in this compressor.

[0034] The scroll compressor of the present invention exhibits high quietness over long periods of time and can suppress increases in manufacturing costs.

[0035] Figure 1 is a cross-sectional view of the compressor of Example 1. Figure 2 is an enlarged cross-sectional view of the main parts of the compressor of Example 1, showing protruding parts, etc. Figure 3 is an enlarged cross-sectional view of the main parts of the compressor of Example 1, showing support members, etc. Figure 4 is an enlarged cross-sectional view of the main parts of the compressor of Example 2, similar to Figure 3, showing support members, etc. Figure 5 is an enlarged cross-sectional view of the compressor of Example 3, similar to Figure 3, showing support members, etc.

[0036] The following describes three embodiments of the present invention with reference to the drawings. Specifically, the compressors of embodiments 1 to 3 are double-rotation scroll compressors. The compressors of embodiments 1 to 3 are mounted on a vehicle (not shown) and constitute the vehicle's air conditioning system.

[0037] (Example 1) As shown in Figure 1, the compressor of Example 1 comprises a housing 6, an electric motor 10, a drive scroll 30, a driven scroll 40, and a driven mechanism 20. The electric motor 10 is an example of a "drive mechanism" in the present invention. The drive scroll 30 is an example of a "first scroll" in the present invention. The driven scroll 40 is an example of a "second scroll" in the present invention.

[0038] 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.

[0039] As shown in Figure 1, the housing 6 is composed of a housing body 60, a first housing cover 61, and a second housing cover 62. These housing body 60, first housing cover 61, and second housing cover 62 are made of aluminum alloy. However, the housing body 60, first housing cover 61, and second housing cover 62 may also be made of steel or the like.

[0040] The housing body 60 is cylindrical with a drive shaft center O1 at its center, and has openings at its front and rear ends. The drive shaft center O1 is parallel to the front-rear direction. The housing body 60 also has an intake port 68. The intake port 68 extends radially from the housing body 60. The intake port 68 is connected to an evaporator (not shown) through piping (not shown).

[0041] The first housing cover 61 is located at the rear end of the housing body 60. The first housing cover 61 is substantially disc-shaped with the drive shaft center O1 as its center and extends radially from the housing 6. The first housing cover 61 has a front surface 61a that faces forward and a rear surface 61b that is located opposite the front surface 61a and faces rear.

[0042] Furthermore, the first housing cover 61 has a retaining portion 611. As shown in Figure 2, the retaining portion 611 is integrally formed with the first housing cover 61. The retaining portion 611 protrudes cylindrically forward from the center of the front surface 61a in the direction of the drive axis O1.

[0043] A one-side elastic body 70 is attached to the holding portion 611. The one-side elastic body 70 is formed of synthetic rubber and is elastically deformable. The one-side elastic body 70 has a cylindrical shape, extends in the direction of the drive axis O1, and has substantially the same length as the holding portion 611. The one-side elastic body 70 is attached to the outer peripheral surface of the holding portion 611 by inserting the holding portion 611 into the inner part thereof. Accordingly, the one-side elastic body 70 covers the holding portion 611 from the outer side. Note that the material and thickness of the one-side elastic body 70 can be designed as appropriate.

[0044] Further, a projecting body 64 is provided in the housing 6. The projecting body 64, including the holding portion 611, is formed as a separate component from the first housing cover 61. The projecting body 64 is made of steel. The projecting body 64 is composed of a first diameter portion 641 and a second diameter portion 642. The first diameter portion 641 constitutes a front part of the projecting body 64. The first diameter portion 641 is formed to have a smaller diameter than a first insertion hole 375 which will be described later. A pin hole 4 is formed in the first diameter portion 641. The pin hole 4 extends inside the first diameter portion 641 in the direction of the drive axis O1, and opens at the front end surface of the first diameter portion 641.

[0045] Further, a first radial ball bearing 51 is provided on the outer peripheral surface of the first diameter portion 641. Note that a sliding bearing may be provided on the outer peripheral surface of the first diameter portion 641 instead of the first radial ball bearing 51.

[0046] The second diameter portion 642 is integrated with the first diameter portion 641 at a front end thereof. Accordingly, the second diameter portion 642 constitutes a rear part of the projecting body 64. The second diameter portion 642 is formed in a bottomed cylindrical shape with an opening at a rear side thereof. An outer diameter of the second diameter portion 642 is formed to be larger than that of the first diameter portion 641. Further, an inner diameter of the second diameter portion 642 is larger than that of the holding portion 611, and is formed to be slightly smaller than an outer diameter of the one-side elastic body 70.

[0047] The protrusion 64 accommodates the holding portion 611 and the one-side elastic body 70 inside the second diameter portion 642. Accordingly, the holding portion 611 is disposed inside the second diameter portion 642. Further, as described above, since the inner diameter of the second diameter portion 642 is smaller than the outer diameter of the one-side elastic body 70, the one-side elastic body 70 is disposed between the holding portion 611 and the second diameter portion 642 while being elastically deformed in the radial direction of the housing 6.

[0048] Thus, the protrusion 64 is attached to the first housing cover 61 via the one-side elastic body 70. Then, the first housing cover 61 supports the protrusion 64 by the holding portion 611 holding the protrusion 64 from the inner side via the one-side elastic body 70.

[0049] As shown in FIG. 3, the second housing cover 62 is disposed in front of the housing main body 60. The second housing cover 62 includes a cover main body portion 62a and a bearing spacer 72. The cover main body portion 62a is an example of the "main body portion" in the present invention. The bearing spacer 72 is an example of the "support member" in the present invention.

[0050] The cover main body portion 62a has a substantially disc shape centered on the drive axis O1, and extends in the radial direction of the housing 6. The cover main 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 housing cover 62 is formed with a support portion 66, a communication recess 620, and a discharge communication port 69. The discharge communication port 69 is an example of the "discharge portion" in the present invention. 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 centered on the drive axis O1, and has an outer peripheral surface 661 and an inner peripheral surface 662.

[0052] The communication recess 620 is located inside the support portion 66 in the radial direction of the housing 6. The communication recess 620 is formed by being recessed in a columnar shape centered on the drive axis O1 with respect to the rear surface 622. Accordingly, the communication recess 620 communicates with the inside of the support portion 66.

[0053] The discharge port 69 penetrates the second housing cover 62 in the direction of the drive axis O1 and communicates with the communication recess 620. In this way, the discharge port 69 communicates with the support portion 66 through the communication recess 620. The discharge port 69 is also connected to a condenser (not shown) through piping (not shown).

[0054] The bearing spacer 72 is made of metal. The bearing spacer 72 has a first wall portion 72a, a second wall portion 72b, a first extension portion 72c, and a second extension portion 72d. The first wall portion 72a is located in the front part of the bearing spacer 72 and extends radially in the direction of 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 is positioned so that the front surface 720a of the first wall portion 72a faces the rear surface 622 of the cover body portion 62a. 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 centered on the drive shaft center O1. The bearing spacer 72 may also be made of resin. Furthermore, the formation of the retaining groove 721 on the first wall portion 72a may be omitted.

[0055] The second wall portion 72b is integral with the first wall portion 72a and extends cylindrically backward from the first wall portion 72a in the direction of the drive axis O1. Here, the outer diameters of the first wall portion 72a and the second wall portion 72b are formed to be approximately the same as the inner diameter of the support portion 66. More precisely, the outer diameters of the first wall portion 72a and the second wall portion 72b are formed to be slightly smaller than the inner diameter of the support portion 66.

[0056] A retaining groove 722 is formed in the second wall portion 72b. The retaining groove 722 is recessed in the outer circumferential surface of the second wall portion 72b. The retaining groove 722 has an annular shape centered on the drive shaft center O1. Note that the formation of the retaining groove 722 in the second wall portion 72b may be omitted.

[0057] The first extension portion 72c is integral with the first wall portion 72a and protrudes forward from the front surface 720a of the first wall portion 72a in the direction of the drive axis O1. More specifically, the first extension portion 72c protrudes forward from the front surface 720a in the direction of the drive axis O1 toward the connecting recess 620. Furthermore, the length of the first extension portion 72c in the direction of the drive axis O1 is approximately the same as the depth of the connecting recess 620. The outer diameter of the first extension portion 72c is formed to be smaller than the inner diameter of the connecting recess 620. As a result, the first extension portion 72c is housed in the connecting recess 620.

[0058] The second extension portion 72d is integral with the first wall portion 72a and protrudes rearward in the direction of the drive axis O1 from the rear surface 720b of the first wall portion 72a, which is inward of the second wall portion 72b. As a result, the second extension portion 72d is spaced radially away from the second wall portion 72b in the housing 6. Also, the second extension portion 72d has a smaller diameter than the second wall portion 72b. Furthermore, the second extension portion 72d extends further rearward than the second wall portion 72b. The outer diameter of the second extension portion 72d is formed to be approximately the same as the inner diameter of the second insertion hole 39d of the case 39, which will be described later. More precisely, the outer diameter of the second extension portion 72d is formed to be slightly smaller than the inner diameter of the second insertion hole 39d. A retaining groove 723 is recessed in the outer circumferential surface of the second extension portion 72d. The retaining groove 723 has an annular shape centered on the drive shaft center O1.

[0059] Furthermore, the bearing spacer 72 has a discharge passage 724, and is also provided with an elastic body 81 on the other side, a first sealing member 83, and a second sealing member 84. The first sealing member 83 is an example of the "first sealing part" in the present invention, and the second sealing member 84 is an example of the "second sealing part" in the present invention. The elastic body 81 on the other side is an example of the "elastic body" in the present invention. These elastic body 81 on the other side, the first sealing member 83, and the second sealing member 84 are each formed as separate parts.

[0060] The discharge passage 724 is formed to have a smaller diameter than the retaining grooves 721 to 723, and in the bearing spacer 72, it is positioned radially inward of the housing 6 than the retaining grooves 721 to 723. The discharge passage 724 extends in a cylindrical shape centered on the drive axis O1, and penetrates the first extension portion 72c, the first wall portion 72a, and the second extension portion 72d in the direction of the drive axis O1. As a result, the front end of the discharge passage 724 opens into the first extension portion 72c, and the rear end of the discharge passage 724 opens into the second extension portion 72d. The diameter of the discharge passage 724 is formed to be approximately the same as the diameter of the opening at the rear surface 622 of the cover body portion 62a in the discharge communication port 69.

[0061] The other elastic body 81 is composed of a thrust elastic body 81a and a radial elastic body 81b. The thrust elastic body 81a and the radial elastic body 81b are made of an elastically deformable resin such as synthetic rubber. The thrust elastic body 81a and the radial elastic body 81b are formed in an annular shape.

[0062] The thrust elastic body 81a is housed in the retaining groove 721. As a result, the thrust elastic body 81a is provided on the first wall portion 72a. On the other hand, the radial elastic body 81b is housed in the retaining groove 722. As a result, the radial elastic body 81b is provided on the second wall portion 72b. Although detailed illustration is omitted, the thrust elastic body 81a is housed in the retaining groove 721 with a projection slightly forward of the front surface 720a of the first wall portion 72a. The radial elastic body 81b is housed in the retaining groove 722 with a projection slightly radially outward of the housing 6 from the outer circumferential surface of the second wall portion 72b.

[0063] The first sealing member 83 is made of a resin such as PTFE (polytetrafluoroethylene) and is elastically deformable. Furthermore, the first sealing member 83 has higher heat resistance than the thrust elastic body 81a and the radial elastic body 81b, i.e., the other elastic body 81. The first sealing member 83 is formed in an annular shape. The first sealing member 83 is attached to the first extension 72c by inserting the first extension 72c through its own interior.

[0064] The second sealing member 84, like the first sealing member 83, is made of a resin such as PTFE (polytetrafluoroethylene) and is elastically deformable. As a result, the second sealing member 84 also has higher heat resistance than the other elastic body 81. The second sealing member 84 is formed in an annular shape. The second sealing member 84 is housed in the retaining groove 723. As a result, the second sealing member 84 is provided on the second extension 72d.

[0065] Here, the length of the outer diameter of the first sealing member 83 is a first length L1. The outer diameter of the first sealing member 83 is slightly larger than the inner diameter of the connecting recess 620. On the other hand, the length of the outer diameter of the second sealing member 84 is a second length L2. This second length L2 is shorter than the first length L1 mentioned above. As a result, the first sealing member 83 has a larger diameter than the second sealing member 84.

[0066] Furthermore, the outer diameter of the second sealing member 84 is slightly larger than the outer diameter of the second extension 72d, and also slightly larger than the inner diameter of the second insertion hole 39d. For this reason, the second sealing member 84 is housed in the retaining groove 723 with its outer diameter protruding slightly from the outer circumferential surface of the second extension 72d.

[0067] Furthermore, since the thrust elastic body 81a and the radial elastic body 81b are housed in the retaining grooves 721 and 722 respectively, and the first sealing member 83 and the second sealing member 84 are provided on the first extension portion 72c and the second extension portion 72d respectively, in the bearing spacer 72, the first sealing member 83 and the second sealing member 84 surround the discharge passage 724 from the radial outside of the housing 6. The thrust elastic body 81a and the radial elastic body 81b, that is, the other elastic body 81, are located radially outside the first sealing member 83, i.e., radially outside the housing 6, compared to the first sealing member 83 and the second sealing member 84.

[0068] The bearing spacer 72 is attached to the cover body 62a by being positioned within the support portion 66. In this case, the thrust elastic body 81a of the bearing spacer 72 is positioned between the rear surface 622 of the cover body 62a and the first wall portion 72a while elastically deforming in the direction of the drive axis O1. The radial elastic body 81b is positioned between the inner circumferential surface 662 of the support portion 66 and the second wall portion 72b while elastically deforming in the radial direction of the housing 6.

[0069] Furthermore, in the bearing spacer 72, the first extension portion 72c is located within the communication recess 620, and therefore the first sealing member 83 provided on the first extension portion 72c is also located within the communication recess 620. More specifically, the first sealing member 83 is positioned between the inner circumferential surface of the communication recess 620 and the outer circumferential surface of the first extension portion 72c, while elastically deforming in the radial direction of the housing 6. Within the communication recess 620, the first sealing member 83 is in contact with the rear surface 622 of the cover body portion 62a in its axial direction, i.e., in the direction of the drive axis O1, and is in contact with the front surface 720a of the first wall portion 72a in the rear direction of the drive axis O1. Note that the first sealing member 83 may not be in contact with the front surface 720a as long as it is in contact with the rear surface 622 in the direction of the drive axis O1. Conversely, the first sealing member 83 may not be in contact with the rear surface 622 as long as it is in contact with the front surface 720a in the direction of the drive axis O1.

[0070] As the bearing spacer 72 is attached to the cover body 62a in this manner, the rear end of the discharge port 69 and the front end of the discharge passage 724 are connected, and the discharge port 69 and the discharge passage 724 are in communication in the direction of the drive axis O1. The thrust elastic body 81a and the radial elastic body 81b are located radially outward of the housing 6 relative to the discharge port 69 and the discharge passage 724, compared to the first sealing member 83 and the second sealing member 84.

[0071] As shown in Figure 1, in the housing 6, the front surface 61a 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 together in the direction of the drive axis O1 by a plurality of bolts (not shown).

[0072] Thus, in the housing 6, the housing body 60 is sandwiched in the front-rear direction by the first housing cover 61 and the second housing cover 62, and the front and rear ends of the housing body 60 are closed by the first housing cover 61 and the second housing cover 62, respectively. As a result, a scroll chamber 65 is formed inside the housing body 60 in the housing 6. The scroll chamber 65 is in communication with the intake port 68. Therefore, refrigerant is drawn into the scroll chamber 65 from outside the housing 6 through the intake port 68. The refrigerant is an example of a "fluid" in this invention.

[0073] 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.

[0074] Furthermore, in the bearing spacer 72, the other elastic body 81, the first sealing member 83, and the second sealing member 84 are each arranged within the scroll chamber 65. The first sealing member 83 is positioned between the cover body 62a and the bearing spacer 72 in the direction of the drive axis O1, and seals the space between the scroll chamber 65 and the discharge communication port 69.

[0075] Furthermore, within the scroll chamber 65, a second radial ball bearing 52 is provided on the second extension 72d of the bearing spacer 72. The second radial ball bearing 52 is an example of a "bearing" in the present invention. More specifically, the second radial ball bearing 52 is provided on the outer circumferential surface of the second extension 72d. As a result, the second radial ball bearing 52 is positioned between the second extension 72d and the second wall 72b in the radial direction of the housing 6. Note that a sliding bearing or the like may be provided on the outer circumferential surface of the second extension 72d instead of the second radial ball bearing 52.

[0076] 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.

[0077] As shown in Figure 2, the electric motor 10 is composed of a stator 17 and a rotor 11. The stator 17 has a stator core 17a and windings 17b. The stator core 17a is formed in a cylindrical shape with the drive axis O1 as the center. The windings 17b are wound around the stator core 17a. As a result, the windings 17b form a first coil end 171 and a second coil end 172.

[0078] The first coil end 171 protrudes cylindrically forward from the stator core 17a in the direction of the drive axis O1. The second coil end 172 is located on the opposite side of the stator core 17a from the first coil end 171. The second coil end 172 protrudes cylindrically backward from the stator core 17a in the direction of the drive axis O1.

[0079] In the stator 17, the stator core 17a is fitted onto the outer circumferential surface of the second diameter portion 642. In this way, the stator core 17a is fixed to the outer circumferential surface of the second diameter portion 642, and consequently to the outer circumferential surface of the protruding body 64. Although not shown in the figures, multiple slits extending in the direction of the drive axis O1 are formed on the inner circumferential surface of the stator core 17a. As a result, the slits form a gap between the stator core 17a and the outer circumferential surface of the second diameter portion 642 while the stator core 17a is fixed to the second diameter portion 642.

[0080] The rotor 11 is cylindrical around the drive axis O1. Although detailed illustrations are omitted, the rotor 11 is composed of multiple permanent magnets corresponding to the stator 17 and laminated steel plates that fix each permanent magnet. The rotor 11 is also formed to be larger in diameter than the stator core 17a. As a result, the rotor 11 covers the stator core 17a from the outside within the scroll chamber 65. Furthermore, the rotor 11 has multiple first bolt holes 11a. Each first bolt hole 11a penetrates the rotor 11 in the direction of the drive axis O1.

[0081] As shown in Figure 1, the drive scroll 30 is housed in the scroll chamber 65. The drive scroll 30 is made of aluminum alloy. The drive scroll 30 includes a drive end plate 31, a drive spiral body 33, a drive peripheral wall 35, a cover body 37, and a case 39.

[0082] The drive end plate 31 extends in a substantially disc shape perpendicular to the drive axis O1 and the driven axis O2. The driven axis O2 extends parallel to the drive axis O1 while being eccentric with respect to the drive axis O1. In other words, the driven axis O2 is also parallel in the front-rear direction. The drive end plate 31 has a first front surface 311 facing forward and a first rear surface 312 located on the opposite side of the first front surface 311 and facing rear.

[0083] Furthermore, a discharge port 32 is formed in the drive end plate 31. The discharge port 32 penetrates the drive end plate 31 in the direction of the drive axis O1. In addition, a discharge reed valve 57 and a retainer 58 are fixed to the first front surface 311 of the drive end plate 31 by fixing bolts 59. As a result, the discharge reed valve 57 can open and close the discharge port 32. The retainer 58 can adjust the opening degree of the discharge reed valve 57.

[0084] The drive spiral body 33 is integral with the drive end plate 31 and protrudes from the first rear surface 312 toward the rear, i.e., toward the driven scroll 40, parallel to the drive axis O1 and the driven axis O2. Although detailed illustration is omitted, the drive spiral body 33 has the center of the drive end plate 31 as its spiral center and protrudes outward from the spiral center in a spiral shape.

[0085] The drive circumferential wall 35 is formed in a cylindrical shape, extending parallel to the drive axis O1 and the driven axis O2, with the drive axis O1 as its center. The front end of the drive circumferential wall 35 is integral with the outer peripheral edge of the drive end plate 31. As a result, the drive circumferential wall 35 surrounds the drive spiral body 33 from the outside and protrudes cylindrically toward the rear from the first rear surface 312. Although not shown in the figures, the outer peripheral end of the spiral in the drive spiral body 33 is connected to the inner peripheral surface of the drive circumferential wall 35.

[0086] As shown in Figure 2, the cover body 37 has a wall portion 37a, an inner cylindrical portion 37b, a connecting portion 37c, and an outer cylindrical portion 37d. The wall portion 37a extends in a substantially plate-like shape in the radial direction of the cover body 37. The wall portion 37a has a second front surface 371 facing forward and a second rear surface 372 located on the opposite side of the second front surface 371 and facing rear.

[0087] 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.

[0088] The intake port 374 is located radially outside the cover body 37, i.e., radially outside the housing 6, relative to the recess 373. The intake port 374 penetrates the wall portion 37a in the front-rear direction, with its front end opening to the second front surface 371 and its rear end opening to the second rear surface 372.

[0089] Furthermore, in the wall portion 37a, multiple rings 22 are attached between the recess 373 and the intake port 374. Although detailed illustrations are omitted, each ring 22 is arranged at equal intervals in the circumferential direction of the recess 373 when facing forward, and surrounds the recess 373 from the outside. In this embodiment, there are six rings 22. Figures 1 and 2 illustrate one of the six rings 22.

[0090] As shown in Figure 2, the inner cylindrical portion 37b is formed radially inward of the cover body 37 beyond the stator 17 and extends cylindrically toward the rear in the direction of the drive axis O1. The inner diameter of the inner cylindrical portion 37b is larger than the first diameter portion 641 of the protruding body 64 and is formed to be approximately the same as the outer diameter of the first radial ball bearing 51.

[0091] The connecting portion 37c is located between the wall portion 37a and the inner cylindrical portion 37b, and is integral with the wall portion 37a and the inner cylindrical portion 37b. The connecting portion 37c expands in diameter from the inner cylindrical portion 37b toward the wall portion 37a in the direction of the drive axis O1, connecting the wall portion 37a and the inner cylindrical portion 37b. As a result, the outer circumferential surface of the inner cylindrical portion 37b and the second rear surface 372 of the wall portion 37a are continuous through the connecting portion 37c.

[0092] Furthermore, a first through-hole 375 is formed inside the connecting portion 37c of the cover body 37. The first through-hole 375 extends in the direction of the drive shaft center O1 and connects the inner cylindrical portion 37b and the recess 373.

[0093] The outer cylindrical portion 37d is integral with the wall portion 37a at its outer peripheral edge. As a result, the outer cylindrical portion 37d is connected to the wall portion 37a and extends cylindrically backward from the wall portion 37a in the direction of the drive axis O1. The outer diameter of the outer cylindrical portion 37d is formed to be approximately the same as the outer diameter of the drive peripheral wall 35 and the outer diameter of the rotor 11.

[0094] Furthermore, the inner diameter of the outer cylindrical portion 37d is formed to be larger than that of the inner cylindrical portion 37b and the connecting portion 37c. As a result, in the cover body 37, the inner cylindrical portion 37b and the connecting portion 37c are positioned on the inner circumference side of the outer cylindrical portion 37d, spaced radially away from the outer cylindrical portion 37d of the cover body 37. In this way, the cover body 37 has a housing portion 38 formed by the wall portion 37a, the inner cylindrical portion 37b, the connecting portion 37c, and the outer cylindrical portion 37d. The housing portion 38 is a bottomed annular shape that opens at the rear. The housing portion 38 is in communication with the intake port 374.

[0095] Furthermore, multiple second bolt holes 376 are formed in the outer cylindrical portion 37d. Each second bolt hole 376 penetrates the outer cylindrical portion 37d in the direction of the drive axis O1. Although not shown in the figures, the number of second bolt holes 376 is equal to the number of first bolt holes 11a formed in the rotor 11. In Figures 1 and 2, one of the multiple first bolt holes 11a and one of the second bolt holes 376 are shown.

[0096] As shown in Figure 1, the cover body 37 has the front end of the outer cylindrical portion 37d in contact with the rear end of the drive peripheral wall 35. The cover body 37 also has the rotor 11 in contact with the rear end of the outer cylindrical portion 37d. In this state, the first bolts 34a are inserted from the rotor 11 side into each of the first bolt holes 11a and each of the second bolt holes 376, respectively, and the first bolts 34a are screwed into the drive peripheral wall 35. In this way, the cover body 37 is sandwiched between the drive peripheral wall 35 and the rotor 11 and fixed to the drive peripheral wall 35 and the rotor 11. As a result, the drive scroll 30 is integrated with the rotor 11.

[0097] Case 39 is a bottomed cylindrical member having an outer peripheral wall 39a and a front wall 39b. The outer peripheral wall 39a is cylindrical with the drive axis O1 as its center. Here, the outer diameter of the outer peripheral wall 39a is formed to be approximately the same as the outer diameter of the drive peripheral wall 35.

[0098] As shown in Figure 3, the front wall 39b is located at the front end of the case 39. The front wall 39b extends in a substantially disc shape perpendicular to the drive axis O1 and the driven axis O2. The front wall 39b is connected to the front end of the outer peripheral wall 39a. A boss 39c is 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 in the direction of the drive axis O1. The outer diameter of the boss 39c is larger than the outer diameter of the second extension portion 72d 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 extension portion 72d and is substantially the same as the outer diameter of the second radial ball bearing 52.

[0099] Furthermore, a second through-hole 39d is formed in the front wall 39b at the location inside the boss 39c. The second through-hole 39d penetrates the front wall 39b in the direction of the drive axis O1. The inner diameter of the second through-hole 39d is larger than the outer diameter of the second extension 72d of the bearing spacer 72, while being slightly smaller than the outer diameter of the second sealing member 84.

[0100] Furthermore, third bolt holes 39e are formed in the outer periphery wall 39a and the front wall 39b. The third bolt holes 39e penetrate the outer periphery wall 39a and the front wall 39b in the direction of the drive axis O1. Although not shown in the figures, multiple third bolt holes 39e are formed in the outer periphery wall 39a and the front wall 39b. Figures 1 and 3 show one of these multiple third bolt holes 39e.

[0101] 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.

[0102] As the case 39 is fixed to the drive peripheral wall 35 in this manner, a discharge chamber 14 is formed inside the peripheral wall 39a, between the front wall 39b of the case 39 and the drive end plate 31. The discharge chamber 14 communicates with the discharge port 32 and also with the second insertion hole 39d.

[0103] 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.

[0104] The driven end plate 41 extends in a substantially disc shape perpendicular to the drive axis O1 and the driven axis O2. The driven end plate 41 has a third front surface 411 facing forward and a third rear surface 412 located on the opposite side of the third front surface 411 and facing rear.

[0105] A receiving recess 15 is formed in the driven end plate 41. The receiving recess 15 is located in the center of the driven end plate 41. The receiving recess 15 is recessed in a cylindrical shape from the third rear surface 412 of the driven end plate 41 toward the front, with the driven axis O2 as the center. As a result, the receiving recess 15 opens toward the rear of the driven end plate 41, and consequently toward the first diameter portion 641 of the protruding body 64.

[0106] As shown in Figure 2, a driven shaft portion 16 and a sliding bearing 13 are provided within the housing recess 15. The driven shaft portion 16 has a bush 53 and a driven pin 55. The bush 53 is housed within the housing recess 15 via the sliding bearing 13. 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, i.e., the driven axis O2. 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 and 2 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 parallel to the drive axis O1 and the driven axis O2. The driven spiral body 43 has the center of the driven end plate 41 as its spiral center and extends outward from the spiral center.

[0110] In this compressor, a driven scroll 40 is housed within the drive scroll 30, more specifically, between the drive end plate 31 and the drive peripheral wall 35 and the cover body 37. The drive spiral body 33 and the driven spiral body 43 are meshed together. As a result, the drive spiral body 33 and the driven spiral body 43 face each other to form a compression chamber 12.

[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. As a result, the suction section 30a is in communication with the housing section 38 through the suction port 374.

[0112] Furthermore, by housing the driven scroll 40 within the driven scroll 30, the second front surface 371 of the wall portion 37a and the third rear surface 412 of the driven end plate 41 face each other in the direction of the drive axis O1. Each pivot pin 21 is positioned within each ring 22. In this way, the driven scroll 30 and the driven scroll 40 are assembled in the front-rear direction, and the driven scroll 30 and the driven scroll 40 constitute the scroll compression section 100. More precisely, after the driven spiral body 33 and the driven spiral body 43 are meshed and each pivot pin 21 is inserted into each ring 22, the cover body 37 of the driven scroll 30 is fixed to the drive peripheral wall 35 and the rotor 11.

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

[0114] As shown in Figure 2, the drive scroll 30 is positioned in front of the stator core 17a within the scroll chamber 65. In the drive scroll 30, the inner cylindrical portion 37b of the cover body 37 is inserted into the inner circumference of the first coil end 171. In this state, the first radial ball bearing 51 is inserted into the inner cylindrical portion 37b. As a result, the inner cylindrical portion 37b, and thus the cover body 37, is rotatably supported around the drive axis O1 with respect to the first diameter portion 641 of the protruding body 64 via the first radial ball bearing 51. The housing portion 38 is in communication with the scroll chamber 65. The front portion of the first diameter portion 641 is inserted into the first insertion hole 375.

[0115] Here, since the cover body 37 is rotatably supported on the first diameter portion 641, in this compressor, the compression chamber 12, including the stator core 17a, is located forward of the electric motor 10 in the direction of the drive axis O1. More specifically, the compression chamber 12 is located forward of the electric motor 10 in the direction of the drive axis O1, with the cover body 37 and the driven end plate 41 in between.

[0116] As described above, the first diameter portion 641 constitutes the front part of the projection 64, and the second diameter portion 642 constitutes the rear part of the projection 64. The stator core 17a is fixed to the outer circumferential surface of the second diameter portion 642. Therefore, the inner cylindrical portion 37b is rotatably supported on the first diameter portion 641 via the first radial ball bearing 51, so that the cover body 37 is rotatably supported on the projection 64 in front of the stator core 17a. In other words, the cover body 37 is supported on the projection 64 closer to the compression chamber 12 than the stator core 17a.

[0117] Furthermore, in the cover body 37, the inner cylindrical portion 37b faces the second diameter portion 642 in the direction of the drive axis O1. Here, with the cover body 37 rotatably supported by the protruding body 64, the inner cylindrical portion 37b and the first coil end 171 are separated in the radial direction of the housing 6.

[0118] Furthermore, because the cover body 37 is rotatably supported on the protruding body 64 in this manner, the wall portion 37a of the cover body 37 faces the first coil end 171 from the front. In addition, the outer cylindrical portion 37d of the cover body 37 is located outside the first coil end 171 in the radial direction of the cover body 37. At this time, the outer cylindrical portion 37d and the first coil end 171 are separated in the radial direction of the housing 6. In other words, because the cover body 37 is rotatably supported on the protruding body 64, the first coil end 171 is housed within the housing portion 38.

[0119] Furthermore, in this compressor, when the cover body 37 is rotatably supported by the protruding body 64, the first radial portion 641, the first radial ball bearing 51, the inner cylindrical portion 37b, the first coil end 171, and the outer cylindrical portion 37d are arranged in this order from the drive shaft center O1 side outward in the radial direction of the housing 6. These first radial portion 641, the first radial ball bearing 51, the inner cylindrical portion 37b, the first coil end 171, and the outer cylindrical portion 37d are arranged overlapping in the radial direction of the housing 6.

[0120] Furthermore, as shown in Figure 3, in the drive scroll 30, the boss 39c of the case 39 is inserted inside the second wall portion 72b of the bearing spacer 72. In this state, the second radial ball bearing 52 is inserted inside the boss 39c. As a result, the boss 39c is rotatably supported by the second extension portion 72d of the bearing spacer 72 via the second radial ball bearing 52. The portion of the second extension portion 72d that is rearward of the second radial ball bearing 52 is inserted into the second insertion hole 39d of the boss 39c. In this way, the bearing spacer 72 rotatably supports the case 39, and by extension the drive scroll 30, around the drive axis O1.

[0121] The thrust elastic body 81a and the radial elastic body 81b, and by extension the other elastic body 81, support the drive scroll 30 while undergoing elastic deformation between the cover body 62a and the bearing spacer 72. In other words, the other elastic body 81 elastically supports the drive scroll 30 via the bearing spacer 72.

[0122] Furthermore, because the second radial ball bearing 52 is inserted inside the boss 39c, the radial elastic body 81b and the second radial ball bearing 52 overlap in the radial direction of the housing 6. More specifically, the entire radial elastic body 81b overlaps with the second radial ball bearing 52 and the housing 6 in the radial direction. In other words, in the bearing spacer 72, a retaining groove 722 is formed in the second wall portion 72b such that the radial elastic body 81b is positioned to overlap with the second radial ball bearing 52 and the housing 6 in the radial direction.

[0123] Thus, the drive scroll 30 is positioned within the scroll chamber 65 and is rotatably supported by the housing 6 by both the protruding body 64 and the support portion 66, so as to be about the drive axis O1.

[0124] Furthermore, in the bearing spacer 72, the second extension portion 72d is inserted into the second insertion hole 39d, so that the discharge passage 724 is in communication with the second insertion hole 39d in the direction of the drive axis O1. 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 84 is positioned inside the second insertion hole 39d as the second extension portion 72d is inserted into the second insertion hole 39d. In this case, since the outer diameter of the second sealing member 84 is larger than the inner diameter of the second insertion hole 39d, the second sealing member 84 is elastically deformed radially of the housing 6 between the outer circumferential surface of the second extension portion 72d and the inner circumferential surface of the second insertion hole 39d. As a result, the second sealing member 84 is positioned between the second extension portion 72d and the second insertion hole 39d, and consequently between the bearing spacer 72 and the drive scroll 30. In this way, the second sealing member 84 seals the space between the second extension 72d and the second insertion hole 39d.

[0125] On the other hand, as shown in Figure 2, in the driven scroll 40, the driven pin 55 of the driven shaft portion 16 is inserted into the pin hole 4. As a result, the driven scroll 40 is positioned in front of the protruding body 64 and is rotatably supported around the driven axis O2 with respect to the first diameter portion 641. Furthermore, by being rotatably supported on the first diameter portion 641 in this way, the driven scroll 40 is also rotatably supported on the protruding body 64 in front of the stator core 17a. In other words, the driven scroll 40 is rotatably supported around the driven axis O2 on the compression chamber 12 side of the stator core 17a by the protruding body 64. Moreover, with the driven pin 55 inserted into the pin hole 4, the driven scroll 40 is rotatably supported around the driven axis O2 on the first diameter portion 641 in the radial direction of the housing 6, inside the inner cylindrical portion 37b. Unlike the drive scroll 30, the driven scroll 40 is supported by the housing 6 solely by the protruding body 64, allowing it to rotate around the driven axis O2.

[0126] Furthermore, in this compressor, the stator core 17a, the first radial ball bearing 51, and the bush 53 of the driven shaft portion 16 are arranged in this order from the first housing cover 61 side toward the compression chamber 12 side in the direction of the drive shaft center O1.

[0127] In this compressor configured as described above, as shown by the dashed arrows in Figures 1 and 2, low-temperature, low-pressure refrigerant that has passed through the evaporator is drawn into the scroll chamber 65 from the intake port 68. When the electric motor 10 operates and the rotor 11 rotates, the rotation of the rotor 11 is transmitted to the drive scroll 30, causing the drive scroll 30 to rotate around the drive axis O1 within the scroll chamber 65. In other words, the drive scroll 30 and the rotor 11 rotate together as a single unit. At this time, in the driven mechanism 20, each orbital pin 21 slides against the inner circumferential surface of each ring 22, causing each ring 22 to rotate relatively around the center of each orbital pin 21. In this way, the driven mechanism 20 transmits the torque of the drive scroll 30 to the driven scroll 40.

[0128] As a result, the driven scroll 40 is rotated by the drive scroll 30 and the driven mechanism 20 around the driven axis O2. At this time, the driven mechanism 20 restricts the driven scroll 40 from rotating on its own axis. This causes the driven scroll 40 to revolve relative to the drive scroll 30 around the driven axis O2. Then, as the drive volute 33 and the driven volute 43 rotate within the intake section 30a, the drive volute 33 and the driven volute 43 change the volume of the compression chamber 12.

[0129] 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.

[0130] 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. Compressed refrigerant is an example of a "compressible fluid" in this invention.

[0131] In this way, the compressed refrigerant discharged into the discharge chamber 14 flows from the second insertion hole 39d through the discharge passage 724 of the bearing spacer 72 toward the discharge port 69. In other words, the compressed refrigerant flows inside the first sealing member 83 and the second sealing member 84 toward the discharge port 69. In this way, the compressed refrigerant that has reached the discharge port 69 via the discharge passage 724 flows through the piping connected to the discharge port 69 and is discharged to the outside of the compressor.

[0132] In this compressor, the other elastic body 81 is composed of a thrust elastic body 81a and a radial elastic body 81b, and these thrust elastic body 81a and radial elastic body 81b elastically support the drive scroll 30 via a bearing spacer 72. In this compressor, the first sealing member 83 is located between the cover body 62a and the bearing spacer 72 in the direction of the drive axis O1, and seals the space between the scroll chamber 65 and the discharge port 69, thereby preventing compressed refrigerant that has reached the discharge port 69 from flowing into the scroll chamber 65. In addition, in this compressor, the second sealing member 84 seals the space between the second extension 72d and the second insertion hole 39d, thereby preventing compressed refrigerant flowing through the second insertion hole 39d from flowing into the scroll chamber 65.

[0133] As described above, the compressed refrigerant that reaches the discharge port 69 via the discharge passage 724 is at high temperature and high pressure, so the discharge passage 724 and the discharge port 69 are in a high-temperature, high-pressure atmosphere. In the other elastic body 81, the thrust elastic body 81a is positioned in the scroll chamber 65 between the rear surface 622 of the cover body 62a and the first wall portion 72a, and the radial elastic body 81b is positioned in the scroll chamber 65 between the inner circumferential surface 662 of the support portion 66 and the second wall portion 72b. As a result, the thrust elastic body 81a and the radial elastic body 81b, i.e., the other elastic body 81, are located radially outside the housing 6 within the scroll chamber 65 compared to the first sealing member 83 and the second sealing member 84. In other words, in this compressor, the other elastic body 81 is located radially further away from the discharge passage 724 and the discharge port 69 than the first sealing member 83 and the second sealing member 84. As a result, in this compressor, the other elastic body 81 is less susceptible to the effects of the high-temperature, high-pressure atmosphere in the discharge passage 724 and the discharge connecting port 69.

[0134] Furthermore, in this compressor, since the first sealing member 83 and the second sealing member 84 seal the space between the scroll chamber 65 and the discharge port 69, there is no need for the other elastic body 81 to seal the space between the scroll chamber 65 and the discharge port 69. Moreover, in this compressor, the space between the second extension 72d and the second insertion hole 39d is sealed by the second sealing member 84. In these respects as well, in this compressor, the other elastic body 81 is less susceptible to the effects of the high-temperature, high-pressure atmosphere in the discharge passage 724 and the discharge port 69.

[0135] As a result, this compressor is less susceptible to changes in the properties and deterioration of the durability of the other elastic body 81 due to the effects of high temperature and high pressure. Therefore, in this compressor, the other elastic body 81 can suitably support the drive scroll 30 over a long period of time via the bearing spacer 72. As a result, although the drive scroll 30 inevitably vibrates in conjunction with the compression of the refrigerant during operation, the elastic deformation of the other elastic body 81 can suitably suppress the transmission of this vibration of the drive scroll 30 from the bearing spacer 72 to the second housing cover 62. In this way, this compressor can suitably suppress vibration of the second housing cover 62, and consequently the housing 6, during operation. Furthermore, this compressor does not require the other elastic body 81 to be made of a material that is excessively resistant to high temperature and high pressure environments.

[0136] Therefore, the compressor of Example 1 can exhibit high quietness over a long period of time and suppress increases in manufacturing costs.

[0137] Furthermore, in this compressor, although the first sealing member 83 and the second sealing member 84 are inevitably susceptible to the effects of high-temperature, high-pressure compressed fluid, the first sealing member 83 and the second sealing member 84 have higher heat resistance than the other elastic body 81. For this reason, in this compressor, the first sealing member 83 and the second sealing member 84 are less likely to experience changes in properties or a decrease in durability.

[0138] Furthermore, in this compressor, the other elastic body 81 is composed of a thrust elastic body 81a and a radial elastic body 81b. Therefore, compared to, for example, a case where the other elastic body 81 is composed of only a thrust elastic body 81a, in this compressor, the thrust elastic body 81a not only elastically supports the bearing spacer 72 in the direction of the drive axis O1, but the radial elastic body 81b can also elastically support the bearing spacer 72 in the radial direction of the housing 6. As a result, in this compressor, it is possible to effectively suppress the transmission of vibrations generated in the drive scroll 30 during operation from the bearing spacer 72 to the housing 6.

[0139] Furthermore, in this compressor, the thrust elastic body 81a, the radial elastic body 81b, the first sealing member 83, and the second sealing member 84 are attached to the bearing spacer 72, and the bearing spacer 72 is positioned within the support portion 66. As a result, in this compressor, the thrust elastic body 81a can be easily positioned between the cover body portion 62a and the bearing spacer 72, more specifically between the rear surface 622 of the cover body portion 62a and the first wall portion 72a, and the radial elastic body 81b can be easily positioned between the inner circumferential surface 662 of the support portion 66 and the second wall portion 72b. Moreover, in this compressor, the first sealing member 83 can also be easily positioned between the inner circumferential surface of the connecting recess 620 and the first extension portion 72c.

[0140] Incidentally, in this compressor, when it is in operation, the radial elastic body 81b undergoes elastic deformation between the support portion 66 and the second wall portion 72b, causing the drive scroll 30 and the bearing spacer 72 to move radially in the housing 6 relative to the cover body portion 62a.

[0141] In this compressor, the second sealing member 84 is housed in a retaining groove 723 formed in the second extension 72d, thereby attaching the second sealing member 84 to the bearing spacer 72. With the second sealing member 84 attached to the bearing spacer 72 in this manner, it is positioned between the second extension 72d and the second insertion hole 39d. Therefore, in this compressor, as described above, when the radial elastic body 81b undergoes elastic deformation and the drive scroll 30 and bearing spacer 72 move radially in the housing 6 relative to the cover body 62a, the second sealing member 84 also moves radially in the housing 6 together with the drive scroll 30 and bearing spacer 72. As a result, in this compressor, even when the radial elastic body 81b undergoes elastic deformation, the radial positional relationship between the drive scroll 30, the bearing spacer 72, and the second sealing member 84 in the housing 6 remains virtually unchanged. Thus, in this compressor, even if the radial elastic body 81b undergoes elastic deformation, the second sealing member 84 can suitably seal the space between the scroll chamber 65 and the discharge port 69.

[0142] Furthermore, since the second sealing member 84 can move radially in the housing 6 together with the drive scroll 30 and the bearing spacer 72, in this compressor, even if the drive scroll 30 and the bearing spacer 72 move radially in the housing 6 relative to the cover body 62a due to the elastic deformation of the radial elastic body 81b, excessive load is less likely to act on the second sealing member 84. For this reason, in this compressor, the second sealing member 84 is less likely to deform due to loads caused by the elastic deformation of the radial elastic body 81b. In this respect as well, the durability of the second sealing member 84 is high in this compressor.

[0143] Furthermore, in this compressor, the first sealing member 83 is positioned between the inner circumferential surface of the contact recess 620 and the outer circumferential surface of the first extension 72c, and is in contact with the cover body 62a and the bearing spacer 72. As a result, the first sealing member 83 biases the bearing spacer 72 toward the rear in the direction of the drive axis O1, that is, toward the drive scroll 30. On the other hand, the second sealing member 84 is housed in the retaining groove 723 and is in contact with the second extension 72d and the second insertion hole 39d. As a result, the second sealing member 84 biases the bearing spacer 72 toward the front in the direction of the drive axis O1, that is, toward the cover body 62a. In this compressor, the first sealing member 83 has a larger diameter than the second sealing member 84. Therefore, in this compressor, the biasing force exerted by the first sealing member 83 towards the drive scroll 30 is greater than the biasing force exerted by the second sealing member 84 towards the cover body 62a.

[0144] As a result, in this compressor, the bearing spacer 72 is less likely to be pressed strongly against the cover body 62a, and therefore vibrations transmitted from the bearing spacer 72 to the cover body 62a and, consequently, to the housing 6 during operation are effectively suppressed. In this respect as well, this compressor is quieter.

[0145] Furthermore, in this compressor, the radial elastic body 81b and the second radial ball bearing 52 are arranged to overlap in the radial direction of the housing 6. Therefore, in this compressor, the radial elastic body 81b can suitably support the radial load acting on the second radial ball bearing 52. As a result, in this compressor, the bearing spacer 72 can be stably supported by the radial elastic body 81b, making it less likely for the bearing spacer 72, including the cover body 62a, to tilt relative to the second housing cover 62 during operation. In addition, in this compressor, the bearing spacer 72 can be made smaller in the direction of the drive axis O1 compared to the case where the radial elastic body 81b and the second radial ball bearing 52 are arranged to be spaced apart in the direction of the drive axis O1. As a result, in this compressor, while achieving the above-mentioned effects, miniaturization in the direction of the drive axis O1 is also realized.

[0146] Furthermore, in this compressor, torque fluctuations occur in the electric motor 10 due to the compression of the refrigerant in the compression chamber 12 during operation. Here, in this compressor, since the stator core 17a is fixed to the second diameter portion 642 of the protruding body 64, vibrations caused by the torque fluctuations of the electric motor 10 are inevitably transmitted from the stator core 17a to the protruding body 64. Moreover, in this compressor, the drive scroll 30 and the driven scroll 40 are each rotatably supported on the first diameter portion 641. Therefore, during operation, vibrations of the drive scroll 30 and the driven scroll 40 due to the compression of the refrigerant in the compression chamber 12 are also inevitably transmitted to the protruding body 64.

[0147] In this compressor, a one-sided elastic body 70 is provided between the second diameter portion 642 and the holding portion 611. Therefore, vibrations transmitted from the electric motor 10, drive scroll 30, and driven scroll 40 to the protruding body 64 are effectively suppressed from being transmitted to the first housing cover 61 by the elastic deformation of the one-sided elastic body 70. In this respect as well, this compressor effectively suppresses vibrations of the housing 6 during operation, thus exhibiting high quietness.

[0148] (Example 2) As shown in Figure 4, in the compressor of Example 2, a communication recess 623 is formed in the second housing cover 62. The communication recess 623 is located inside the support portion 66 in the radial direction of the housing 6. The communication recess 623 is formed by recessing the rear surface 622 in a cylindrical shape centered on the drive shaft O1, and communicates with the inside of the support portion 66. Here, the communication recess 623 has a smaller diameter than the communication recess 620 in the compressor of Example 1.

[0149] Furthermore, in this compressor, a first sealing member 83a is provided between the cover body 62a and the bearing spacer 72. The first sealing member 83a is also made of a resin such as PTFE and has an annular shape. The length of the outer diameter of the first sealing member 83a is a third length L3. As a result, the outer diameter of the first sealing member 83a is slightly larger than the inner diameter of the contact recess 623. Here, the third length L3 is shorter than the second length L2, which is the length of the outer diameter of the second sealing member 84. As a result, in this compressor, the second sealing member 84 has a larger diameter than the first sealing member 83a.

[0150] The first sealing member 83a is attached to the first extension portion 72c by inserting the first extension portion 72c through its interior. The first sealing member 83a is located within the communication recess 623 while attached to the first extension portion 72c. At this time, the first sealing member 83a is positioned between the inner circumferential surface of the communication recess 623 and the outer circumferential surface of the first extension portion 72c, while elastically deforming in the radial direction of the housing 6. The first sealing member 83a is in contact with the rear surface 622 of the cover body portion 62a in front of the drive axis O1 direction, and in contact with the front surface 720a of the first wall portion 72a in rear of the drive axis O1 direction. As a result, the first sealing member 83a is positioned between the cover body portion 62a and the bearing spacer 72 in the drive axis O1 direction, sealing the space between the scroll chamber 65 and the discharge communication port 69. Furthermore, the first sealing member 83a may not be in contact with the front surface 720a as long as it is in contact with the rear surface 622 in the direction of the drive axis O1. Conversely, the first sealing member 83a may not be in contact with the rear surface 622 as long as it is in contact with the front surface 720a in the direction of the drive axis O1.

[0151] Furthermore, because the first sealing member 83a is located within the connecting recess 623, in this compressor as well, the thrust elastic body 81a and the radial elastic body 81b, i.e., the other elastic body 81, are located radially outward from the housing 6 than the first sealing member 83a. 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.

[0152] In this compressor, the space between the scroll chamber 65 and the discharge port 69 can be sealed by the first sealing member 83a and the second sealing member 84. In this compressor, the second sealing member 84 has a larger diameter than the first sealing member 83a. Therefore, in this compressor, the biasing force exerted by the second sealing member 84 on the bearing spacer 72 toward the cover body 62a is greater than the biasing force exerted by the first sealing member 83a on the bearing spacer 72 toward the drive scroll 30. As a result, thrust loads are less likely to act on the second radial ball bearing 52 during operation, thus increasing the durability of the second radial ball bearing 52. Furthermore, because thrust loads are less likely to act on the second radial ball bearing 52, which is the "bearing" in this invention, it is easier to use other bearings such as sliding bearings and needle bearings, which are unfavorable to thrust loads, as the "bearing" in this invention, thus increasing the design flexibility.

[0153] Furthermore, the biasing force exerted by the second sealing member 84 toward the cover body 62a is greater than the biasing force exerted by the first sealing member 83a toward the drive scroll 30, so that in this compressor, the first sealing member 83a can suitably contact the cover body 62a and the bearing spacer 72 in the direction of the drive axis O1. As a result, in this compressor, the first sealing member 83a can suitably seal the space between the scroll chamber 65 and the discharge port 69. Other functions of this compressor are the same as those of the compressor in Embodiment 1.

[0154] (Example 3) As shown in Figure 5, in the compressor of Example 3, the bearing spacer 72 is provided with the other elastic body 82. The other elastic body 82 is also an example of an "elastic body" in the present invention. The other elastic body 82 is formed separately from the first sealing member 83 and the second sealing member 84.

[0155] Furthermore, in this compressor, retaining grooves 725 to 727 are formed in the bearing spacer 72. Retaining groove 725 is recessed from the front surface 720a of the first wall portion 72a toward the rear. Retaining grooves 726 and 727 are recessed on the outer circumferential surface of the second wall portion 72b. Also, retaining grooves 726 and 727 are spaced apart in the direction of the drive axis O1. Note that the formation of retaining grooves 725 to 727 on the bearing spacer 72 may be omitted.

[0156] The other elastic body 82 is composed of a thrust elastic body 82a, a first radial elastic body 82b, and a second radial elastic body 82c. These thrust elastic body 82a, first radial elastic body 82b, and second radial elastic body 82c are also formed from an elastically deformable resin such as synthetic rubber and have an annular shape.

[0157] The thrust elastic body 82a is provided on the first wall portion 72a by being housed in the retaining groove 725. In this case, the thrust elastic body 82a is housed in the retaining groove 725 with a slight forward protrusion from the front surface 720a of the first wall portion 72a. The first radial elastic body 82b and the second radial elastic body 82c are provided on the second wall portion 72b by being housed in the retaining groove 726 and retaining groove 727, respectively. The first radial elastic body 82b and the second radial elastic body 82c are also housed in the retaining grooves 726 and 727 with a slight outward protrusion from the outer circumferential surface of the second wall portion 72b in the radial direction of the housing 6. Here, since the retaining groove 726 and the retaining groove 727 are spaced apart in the direction of the drive axis O1, the first radial elastic body 82b and the second radial elastic body 82c are provided on the second wall portion 72b with a spaced apart in the direction of the drive axis O1.

[0158] The thrust elastic body 82a is positioned between the rear surface 622 of the cover body 62a and the first wall portion 72a, while elastically deforming in the direction of the drive axis O1, due to the bearing spacer 72 being placed within the support portion 66. The first radial elastic body 82b and the second radial elastic body 82c are positioned between the inner circumferential surface 662 of the support portion 66 and the second wall portion 72b, while elastically deforming in the radial direction of the housing 6, due to the bearing spacer 72 being placed within the support portion 66. In this compressor as well, the thrust elastic body 82a, the first radial elastic body 82b, and the second radial elastic body 82c are located radially outward of the housing 6 compared to the first sealing member 83 and the second sealing member 84.

[0159] Furthermore, in this compressor, a second radial ball bearing 54 is inserted through the boss 39c of the case 39. The second radial ball bearing 54 is also an example of a "bearing" in the present invention. As a result, the boss 39c is rotatably supported by the second extension 72d of the bearing spacer 72 via the second radial ball bearing 54. Here, the second radial ball bearing 54 is located between the first radial elastic body 82b and the second radial elastic body 82c in the direction of the drive axis O1. As a result, in this compressor, the first radial elastic body 82b and the second radial elastic body 82c and the second radial ball bearing 54 do not overlap in the radial direction of the housing 6. Note that a sliding bearing or the like may be provided instead of the second radial ball bearing 54. The other configurations in this compressor are the same as those of the compressor in Embodiment 1.

[0160] In this compressor, the other elastic body 82, namely the thrust elastic body 82a, the first radial elastic body 82b, and the second radial elastic body 82c, elastically support the drive scroll 30 via the bearing spacer 72. In this case, the drive scroll 30 can be suitably supported in the radial direction of the housing 6 by both the first radial elastic body 82b and the second radial elastic body 82c.

[0161] In this compressor, the first radial elastic body 82b and the second radial elastic body 82c are arranged spaced apart in the direction of the drive axis O1, and the second radial ball bearing 54 is located between the first radial elastic body 82b and the second radial elastic body 82c in the direction of the drive axis O1. As a result, in this compressor, the first radial elastic body 82b and the second radial elastic body 82c can suitably support the radial load acting on the second radial ball bearing 52, and the bearing spacer 72 can be stably supported by the first radial elastic body 82b and the second radial elastic body 82c. Thus, in this compressor as well, the bearing spacer 72 is less likely to tilt relative to the second housing cover 62 during operation.

[0162] Furthermore, in this compressor, it is possible to prevent the load transmitted from the drive scroll 30 to the bearing spacer 72 via the second radial ball bearing 54 from being biased towards one of the first radial elastic body 82b and the second radial elastic body 82c. Therefore, in this compressor, both the first radial elastic body 82b and the second radial elastic body 82c can be suitably elastically deformed in the radial direction of the housing 6. As a result, in this compressor, vibration of the second housing cover 62 and, consequently, the housing 6 during operation can be more suitably suppressed. Other functions of this compressor are the same as those of the compressor in Embodiment 1.

[0163] Although the present invention has been described above in reference to Examples 1 to 3, it goes without saying that the present invention is not limited to Examples 1 to 3, and can be applied with appropriate modifications without departing from its spirit.

[0164] For example, in the compressor of Example 1, the drive scroll 30 is designated as the "first scroll" in the present invention, and the driven scroll 40 is designated as the "second scroll" in the present invention, so that the refrigerant is compressed by the rotation of both the drive scroll 30 and the driven scroll 40. However, the invention is not limited to this, and the "first scroll" in the present invention may be configured to be fixed in the housing 6 so as not to rotate. The same applies to the compressors of Examples 2 and 3.

[0165] Furthermore, in the compressor of Example 1, the other elastic body 81 may consist of only one of the thrust elastic body 81a and the radial elastic body 81b. The same applies to the compressors of Examples 2 and 3.

[0166] Furthermore, in the compressor of Embodiment 1, the boss 39c of the case 39 may be inserted into the discharge passage 724 of the bearing spacer 72, and the second radial ball bearing 52 may be positioned between the inner circumferential surface of the discharge passage 724 and the outer circumferential surface of the boss 39c. The same applies to the compressors of Embodiments 2 and 3.

[0167] Furthermore, in the compressor of Example 1, either the first sealing member 83 or the second sealing member 84 may be omitted. The same applies to the compressors of Examples 2 and 3.

[0168] Furthermore, in the compressor of Embodiment 1, the first sealing member 83 is attached to the bearing spacer 72 by being provided on the first extension portion 72c. However, the invention is not limited to this, and the first sealing member 83 may be pre-positioned in the communication recess 620 by being attached to the cover body portion 62a. The same applies to the compressors of Embodiments 2 and 3.

[0169] Furthermore, in the compressor of Embodiment 1, a retaining groove 723 is formed in the second extension portion 72d, and the second sealing member 84 is housed in this retaining groove 723, thereby attaching the second sealing member 84 to the bearing spacer 72. However, the method is not limited to this, and the second sealing member 84 may also be attached to the case 39, i.e., the drive scroll 30, by forming a retaining groove 723 on the inner circumferential surface of the second insertion hole 39d and providing the second sealing member 84 in the retaining groove 723. The same applies to the compressors of Embodiments 2 and 3.

[0170] Furthermore, in the compressor of Embodiment 1, the entire radial elastic body 81b overlaps with the second radial ball bearing 52 and the housing 6 in the radial direction. However, this is not limited to this configuration; a part of the radial elastic body 81b and a part of the second radial ball bearing 52 may overlap with the housing 6 in the radial direction. Alternatively, the radial elastic body 81b and the second radial ball bearing 52 may be arranged at a distance from each other in the direction of the drive axis O1 so that they do not overlap with the housing 6 in the radial direction. The same applies to the compressor of Embodiment 2.

[0171] Furthermore, in the compressor of Example 1, the discharge port 69 is defined as the "discharge section" in the present invention. However, the "discharge section" in the present invention may also have a passage connecting the discharge port 69 and the discharge passage 724, in addition to the discharge port 69. The same applies to the compressors of Examples 2 and 3.

[0172] Furthermore, in the compressor of Example 1, the one-sided elastic body 70 may be omitted. The same applies to the compressors of Examples 2 and 3.

[0173] Furthermore, this specification includes the following inventions: (Note 1) A scroll compressor comprising: a housing; a first scroll housed in the housing; and a second scroll housed in the housing and forming a compression chamber between itself and the first scroll for compressing fluid, wherein the housing houses the first scroll and the second scroll and has a scroll chamber from which fluid is drawn in from outside the housing, and a discharge section for discharging compressed fluid, which is the fluid compressed in the compression chamber, to the outside of the housing, wherein the scroll chamber is provided with an elastic body that supports the first scroll while elastically deforming, and a sealing section that is annular in shape and separate from the elastic body, and seals the space between the scroll chamber and the discharge section, wherein the compressed fluid flows toward the discharge section inside the sealing section in the radial direction of the housing, and the elastic body is positioned radially outward from the sealing section. (Note 2) The scroll compressor according to Note 1, wherein the first scroll is rotationally driven around a drive axis by a drive mechanism, and the second scroll is rotationally driven around a driven axis by the first scroll and the driven mechanism while being eccentric with respect to the first scroll. (Note 3) The scroll compressor according to Note 2, wherein the housing has a main body portion on which the discharge portion is formed, and a support member attached to the main body portion and arranged in the scroll chamber, and supporting the first scroll around the drive axis, the elastic body and the sealing portion are provided on the main body portion or the support member and are located between the main body portion and the support member, and the support member has a discharge passage formed therein which is located radially inward from the elastic body and the sealing portion and communicates with the discharge portion, and through which the compressed fluid flows toward the discharge portion. (Note 4) The scroll compressor according to Note 3, wherein the elastic body comprises at least one of a thrust elastic body disposed between the main body and the support member in the direction of the drive axis, and a radial elastic body disposed between the main body and the support member in the radial direction.(Note 5) The scroll compressor according to Note 1, wherein the first scroll is rotationally driven around a drive axis by a drive mechanism, the housing has a main body portion on which the discharge portion is formed, and a support member attached to the main body portion and arranged in the scroll chamber for supporting the first scroll around the drive axis, the elastic body is provided on the main body portion or the support member and is located between the main body portion and the support member in the radial direction, the sealing portion has a first sealing portion and a second sealing portion which is further away from the first sealing portion toward the first scroll in the drive axis direction, the first sealing portion is provided on the main body portion or the support member and is located between the main body portion and the support member, the second sealing portion is provided on the support member or the first scroll and is located between the support member and the first scroll, and the support member has a discharge passage formed therein which is located radially inward from the elastic body, the first sealing portion and the second sealing portion and communicates with the discharge portion, and through which the compressed fluid flows toward the discharge portion. (Note 6) The scroll compressor according to Note 5, wherein the first sealing portion has a larger diameter than the second sealing portion. (Note 7) The scroll compressor according to Note 5, wherein the second sealing portion has a larger diameter than the first sealing portion. (Note 8) The scroll compressor according to any one of Notes 5 to 7, wherein a bearing is provided between the first scroll and the support member in the radial direction, the elastic body has a radial elastic body disposed between the main body and the support member in the radial direction, the radial elastic body is located radially outward from the bearing, and the radial elastic body and the bearing overlap in the radial direction by at least a portion of each other.(Note 9) A scroll compressor according to any one of Notes 5 to 7, wherein a bearing is provided between the first scroll and the support member in the radial direction, the elastic body has a radial elastic body disposed between the main body and the support member in the radial direction, the radial elastic body has a first radial elastic body and a second radial elastic body located radially outward from the bearing, the first radial elastic body and the second radial elastic body are spaced apart in the direction of the drive axis, and the bearing is located between the first radial elastic body and the second radial elastic body in the direction of the drive axis. (Note 10) A scroll compressor according to Note 8 or 9, wherein the elastic body has a thrust elastic body disposed between the main body and the support member in the direction of the drive axis.

[0174] This invention can be used in vehicle air conditioning systems and the like.

[0175] 6…Housing 10…Electric motor (drive mechanism) 12…Compression chamber 20…Driven mechanism 30…Driven scroll (first scroll) 40…Driven scroll (second scroll) 52, 54…Second radial ball bearing (bearing) 62a…Cover body (body) 65…Scroll chamber 69…Discharge connection port (discharge section) 72…Bearing spacer (support member) 83, 83a…First sealing member (first sealing section, sealing section) 84…Second sealing member (second sealing section, sealing section) 81, 82…Other side elastic body (elastic body) 81a, 82a…Thrust elastic body 81b…Radial elastic body 82b…First radial elastic body 82c…Second radial elastic body 724…Discharge passage O1…Driven shaft center O2…Driven shaft center

Claims

1. A scroll compressor comprising: a housing; a first scroll housed within the housing; and a second scroll housed within the housing and forming a compression chamber between itself and the first scroll for compressing fluid, wherein the housing houses the first scroll and the second scroll and has a scroll chamber from which fluid is drawn in from outside the housing, and a discharge section for discharging compressed fluid, which is the fluid compressed in the compression chamber, to the outside of the housing, wherein the scroll chamber is provided with an elastic body that supports the first scroll while elastically deforming, and a sealing section that is annular in shape and separate from the elastic body, sealing the space between the scroll chamber and the discharge section, wherein the compressed fluid flows towards the discharge section inside the sealing section in the radial direction of the housing, and the elastic body is positioned radially outward from the sealing section.

2. The scroll compressor according to claim 1, wherein the first scroll is rotationally driven about a drive axis by a drive mechanism, and the second scroll is rotationally driven about a driven axis by the first scroll and the drive mechanism while being eccentric with respect to the first scroll.

3. The scroll compressor according to claim 2, wherein the housing comprises a main body portion on which the discharge portion is formed, and a support member attached to the main body portion and positioned in the scroll chamber, and supporting the first scroll around the drive axis, the elastic body and the sealing portion are provided on the main body portion or the support member and are located between the main body portion and the support member, and the support member has a discharge passage formed therein which is located radially inward from the elastic body and the sealing portion and communicates with the discharge portion, and through which the compressed fluid flows toward the discharge portion.

4. The scroll compressor according to claim 3, wherein the elastic body comprises at least one of a thrust elastic body disposed between the main body and the support member in the direction of the drive axis and a radial elastic body disposed between the main body and the support member in the radial direction.

5. The scroll compressor according to claim 1, wherein the first scroll is rotationally driven around a drive axis by a drive mechanism, the housing has a main body portion on which the discharge portion is formed, and a support member attached to the main body portion and positioned in the scroll chamber to support the first scroll around the drive axis, the elastic body is provided on the main body portion or the support member and is located between the main body portion and the support member in the radial direction, the sealing portion has a first sealing portion and a second sealing portion that is further away from the first sealing portion toward the first scroll in the drive axis direction, the first sealing portion is provided on the main body portion or the support member and is located between the main body portion and the support member, the second sealing portion is provided on the support member or the first scroll and is located between the support member and the first scroll, and the support member has a discharge passage formed therein that is located radially inward from the elastic body, the first sealing portion and the second sealing portion and communicates with the discharge portion, and through which the compressed fluid flows toward the discharge portion.

6. The scroll compressor according to claim 5, wherein the first sealing portion has a larger diameter than the second sealing portion.

7. The scroll compressor according to claim 5, wherein the second sealing portion has a larger diameter than the first sealing portion.

8. The scroll compressor according to claim 5, wherein a bearing is provided between the first scroll and the support member in the radial direction, the elastic body has a radial elastic body disposed between the main body and the support member in the radial direction, the radial elastic body is located radially outward from the bearing, and the radial elastic body and the bearing overlap in the radial direction by at least a portion.

9. The scroll compressor according to claim 5, wherein a bearing is provided between the first scroll and the support member in the radial direction, the elastic body has a radial elastic body disposed between the main body and the support member in the radial direction, the radial elastic body has a first radial elastic body and a second radial elastic body located radially outward from the bearing, the first radial elastic body and the second radial elastic body are spaced apart in the direction of the drive axis, and the bearing is located between the first radial elastic body and the second radial elastic body in the direction of the drive axis.

10. The scroll compressor according to claim 8 or 9, wherein the elastic body is a thrust elastic body disposed between the main body and the support member in the direction of the drive axis.

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