Bidirectional rotary scroll-type compressor

Abstract

In a bidirectional rotary scroll-type compressor, a stator (17) is fixed to a protruding body (64). A drive scroll (30) is supported by the protruding body (64) so as to be rotatable about a drive axis (O1). Furthermore, a driven scroll (40) is supported by the protruding body (64) so as to be rotatable about a driven axis (O2). The protruding body (64) is attached to a housing (6) by means of an elastically deformable support body (70a). The support body (70a) has a cutout part (701). When the support body (70a) is viewed along the drive axis (O1) direction, the cutout part (701) is disposed in a state of avoiding a fluctuation range (FR) of a compressive load.

Description

Double-rotating scroll compressor

[0001] This invention relates to a reciprocating scroll compressor.

[0002] Patent Document 1 discloses a conventional double-rotation scroll compressor (hereinafter, as appropriate, simply referred to as "compressor"). This compressor comprises a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism. The housing has a scroll chamber in which the drive mechanism, the drive scroll, and the driven scroll are housed. Fluid is drawn into the scroll chamber from outside the housing. In the same document, the fluid is specifically a refrigerant.

[0003] The drive mechanism comprises a stator and a rotor. The stator is cylindrical in shape, with its outer circumference fixed to the housing. The rotor is positioned on the inner circumference side of the stator. The drive scroll has a cylindrical extension. The rotor is fixed to the outer surface of the extension. This allows the drive scroll to be rotationally driven around the drive axis by the rotation of the rotor. The drive scroll has a drive end plate extending in a direction intersecting the drive axis, and a drive spiral body projecting spirally from the drive end plate toward the driven scroll. The driven scroll is eccentric with respect to the drive scroll and can be rotationally driven around the driven axis by the drive scroll and the driven mechanism. The driven scroll has a driven end plate extending in a direction intersecting the drive axis, and a driven spiral body projecting spirally from the driven end plate toward the drive end plate. These drive scrolls and driven scrolls form a compression chamber for compressing fluid by rotationally driving and rotationally driving with the drive spiral body and driven spiral body facing each other.

[0004] Further, in this compressor, a protrusion is integrally provided on the housing. The protrusion is formed in a substantially cylindrical shape with a constant outer diameter, and extends into the scroll chamber along the drive axis direction toward the driving scroll and the driven scroll. The protrusion penetrates into the interior of the extending portion, and the protrusion rotatably supports the extending portion, and thus the driving scroll, via a bearing. Further, a fluid passage extending in the drive axis direction is formed inside the protrusion. The fluid passage communicates with the compression chamber at one end in the drive axis direction, and communicates with the outside of the housing at the other end in the drive axis direction.

[0005] In this compressor, fluid in the scroll chamber is sucked into the compression chamber and compressed in the compression chamber. Then, the fluid compressed in the compression chamber flows through the fluid passage and is discharged to the outside of the housing, that is, the outside of the compressor.

[0006] Japanese Unexamined Patent Publication No. Hei 2-227575

[0007] In a compressor, a compression load is generated when fluid is compressed in the compression chamber during operation. In the above conventional compressor, the driving scroll has an extending portion, and the extending portion is rotatably supported by the protrusion. Accordingly, in this compressor, the compression load generated during operation is transmitted from the extending portion to the protrusion. Further, since a rotor is fixed to the extending portion, vibration generated by the drive mechanism is also transmitted to the protrusion. When these compression loads and vibration generated by the drive mechanism are transmitted to the housing including the protrusion, the housing is likely to vibrate during operation of the compressor, which consequently impairs the quietness of the compressor.

[0008] Therefore, it is conceivable to provide a support body capable of supporting the protrusion while being elastically deformed between the extending portion and the protrusion, so as to suppress the transmission of compression load and vibration generated by the drive mechanism from the extending portion to the protrusion. Further, in this case, it is conceivable to form the support body in an annular shape so that the entire circumference of the protrusion can be covered between the extending portion and the protrusion.

[0009] However, if the support is annular, the only way to install it between the extended portion and the protruding body is to insert the support in the direction of the drive axis relative to either the extended portion or the protruding body. Therefore, when using an annularly formed support to suppress the transmission of vibration to the protruding body, not only does the installation of the support between the extended portion and the protruding body increase the number of work steps, but the method of attaching the support is also limited, leading to a decrease in the manufacturing efficiency of the compressor. As a result, there are concerns that the manufacturing cost of such compressors will skyrocket.

[0010] This invention has been made in view of the above-mentioned conventional circumstances, and aims to solve the problem of providing a dual-rotation scroll compressor that can suppress the soaring manufacturing costs and has excellent quietness.

[0011] The dual-rotation scroll compressor of the present invention comprises a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism, the housing having a scroll chamber in which the drive scroll, the driven scroll, and the drive mechanism are housed, the drive mechanism having a stator and a rotor rotationally driven by the stator, the drive scroll being rotationally driven around a drive axis by the drive mechanism, the driven scroll being rotationally driven around a driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, the drive scroll having a drive end plate extending in a direction intersecting the drive axis and a drive spiral body projecting spirally from the drive end plate toward the driven scroll, the driven scroll having a driven end plate extending in a direction intersecting the driven axis and a driven spiral body projecting spirally from the driven end plate toward the drive end plate, The drive scroll and the driven scroll are a double-rotation scroll compressor in which a compression chamber for compressing a fluid is formed by rotating the drive scroll and the driven scroll facing each other and rotating them toward each other, the stator is mounted inside the scroll chamber and a projection is provided extending toward the drive axis toward the drive scroll and the driven scroll, the drive scroll is rotatably supported by the projection around the drive axis, the driven scroll is rotatably supported by the projection around the driven axis, the housing has a holding portion extending toward the drive axis and located inside the projection, a support is provided between the projection and the holding portion in the radial direction of the housing that elastically deforms to support the projection, the support has a notch that separates one end and the other end in the circumferential direction of the support and is not in contact with the projection and the holding portion, and a virtual plane perpendicular to the drive axis is assumed,The midpoint between the center of the drive-side base circle forming the drive-side spiral body and the center of the driven-side base circle forming the driven-side spiral body in the virtual plane is defined as the point of application of the compressive load generated radially outward from the center side of the drive-side and driven-side scrolls due to the rotation of the drive-side and driven-side scrolls. The direction perpendicular to the virtual line connecting the first contact point where the outer surface of the drive-side spiral body and the inner surface of the driven-side spiral body contact at the outermost circumference in the virtual plane, and the second contact point where the inner surface of the drive-side spiral body and the outer surface of the driven-side spiral body contact at the outermost circumference is defined as the load direction of the compressive load. The range in which the load direction changes during one rotation of the drive-side and driven-side scrolls is defined as the fluctuation range. The notch is positioned to avoid the fluctuation range when viewed from the drive axis direction.

[0012] In the dual-rotation scroll compressor of the present invention, the stator is fixed to a projection located within the scroll chamber. As a result, vibrations generated in the drive mechanism during operation are inevitably transmitted to the projection. Furthermore, the drive scroll is supported on the projection so as to be rotatable around the drive axis, and the driven scroll is also supported so as to be rotatable around the driven axis. Therefore, the compressive load generated during operation is also inevitably transmitted to the projection.

[0013] In this compressor, a support is provided between the radially projecting body and the retaining part of the housing, and this support supports the projecting body while elastically deforming. Here, the support has a notch, which separates one end of the support in the circumferential direction from the other end. The notch is not in contact with the projecting body and the retaining part.

[0014] Due to the presence of such notches, the support in this compressor does not completely cover the projection. Therefore, when providing a projection between the projection and the retaining part in this compressor, the support can be attached to the projection or retaining part from the radial direction by utilizing the notches, in addition to inserting the support in the direction of the drive axis relative to the projection or retaining part. In this way, this compressor allows for a high degree of freedom in attaching the support, thereby minimizing the reduction in manufacturing efficiency caused by providing a support between the retaining part and the projection.

[0015] Incidentally, since the notch does not come into contact with the protruding body and the holding part, the support cannot support the protruding body at the notch. In this respect, in this compressor, both the drive scroll and the driven scroll rotate, and during operation, the drive scroll and the driven scroll rotate at the same angular velocity while being eccentric. For this reason, the direction in which the compression load acts during the operation of the compressor does not change significantly in the circumferential direction of the drive scroll and the driven scroll. In other words, in this compressor, the range in which the compression load acts during operation is limited to a predetermined range of variation in the circumferential direction of the drive scroll and the driven scroll.

[0016] Furthermore, in this compressor, when the support is viewed from the direction of the drive axis, the notch is positioned to avoid the range of variation. In other words, in this compressor, when the support is viewed from the direction of the drive axis, the notch and the range of variation do not overlap, so the fact that the notch does not come into contact with the protrusion and the holding part does not affect the support's ability to support the protrusion against the compressive load. Thus, in this compressor, the support effectively suppresses the transmission of the compressive load from the protrusion to the holding part and, consequently, to the housing. In addition, in this compressor, the support effectively suppresses the transmission of vibrations generated in the drive mechanism from the protrusion to the housing.

[0017] Therefore, the dual-rotation scroll compressor of the present invention can suppress the soaring manufacturing costs and is also excellent in terms of quietness.

[0018] In the compressor of the present invention, when the support is viewed from the direction of the drive axis, it is preferable that the notch is located on the opposite side of the point of action from the range of variation. In this case, the notch can be appropriately spaced away from the range of variation.

[0019] The support is preferably made of an elastically deformable metal plate and has radially protruding bumps. In this case, the support can suitably support the protruding body by the elastic deformation of the bumps.

[0020] In the compressor of the present invention, a state in which the resultant force of the inertial force due to vibration transmitted to the protruding body and the compressive load is less than or equal to a set value can be considered a first state. Furthermore, a state in which the resultant force of the inertial force and the compressive load transmitted to the protruding body is greater than the set value can be considered a second state. Preferably, the bump has a main bump that contacts the protruding body and the holding part in the first and second states, and a sub-bump that contacts only one of the protruding body and the holding part in the first state, and contacts both the protruding body and the holding part in the second state.

[0021] In this case, in the first state, the support can elastically support the projection body because only the main bump elastically deforms between the projection body and the holding part. On the other hand, in the second state, that is, when the resultant force of the inertial force due to vibration and the compressive load transmitted to the projection body is larger than in the first state, the support can elastically support the projection body because the main bump and the sub-bump each elastically deform between the projection body and the holding part. Thus, in this compressor, the support can elastically support the projection body with two different spring constants depending on the magnitude of the resultant force of the inertial force due to vibration and the compressive load transmitted to the projection body. For this reason, in this compressor, the support can suitably support the projection body in both the first and second states.

[0022] Furthermore, in the compressor of the present invention, a state in which the resultant force of the inertial force due to vibration transmitted to the protruding body and the compressive load is less than or equal to a set value may be considered a first state. A state in which the resultant force of the inertial force and the compressive load transmitted to the protruding body is greater than the set value may be considered a second state. Moreover, the bump may include a first bump, a second bump arranged at a distance from the first bump in the circumferential direction of the protruding body relative to the first bump, and a third bump arranged between the first bump and the second bump in the circumferential direction of the protruding body and connected to the first bump and the second bump. The first bump may contact only the holding portion in the first and second states. The second bump may contact only the protruding body in the first and second states. Furthermore, it is preferable that the third bump is not in contact with the holding portion and the protruding body in the first state, but is in contact with both the holding portion and the protruding body in the second state.

[0023] In this case, in the first state, the support body can elastically support the protruding body because the first and second bumps elastically deform between the protruding body and the holding part. On the other hand, in the second state, in addition to the first and second bumps, the third bump also elastically deforms between the protruding body and the holding part, so that the support body can elastically support the protruding body. Thus, even in this compressor, the support body can elastically support the protruding body with two different spring constants depending on the magnitude of the resultant force of the inertial force due to vibration transmitted to the protruding body and the compressive load. For this reason, even in this compressor, the support body can suitably support the protruding body in both the first and second states.

[0024] The support may have a first elastic section set to a first spring constant and a second elastic section set to a second spring constant higher than the first spring constant. When the support is viewed from the direction of the drive axis, it is preferable that the second elastic section is positioned at least in a location that overlaps with the range of variation. In this case, the second elastic section can effectively suppress the transmission of compressive load to the protruding body and, consequently, to the housing.

[0025] The protruding body can be fixed to the stator by a fixing member. Preferably, the fixing member is positioned so as to overlap with the notch in the radial direction. In this case, relative rotation between the protruding body and the stator during operation can be effectively prevented. Furthermore, by positioning the fixing member so as to overlap with the notch in the radial direction, the fixing member can be easily installed.

[0026] Furthermore, it is preferable that the support is positioned in the notch and has a positioning portion for positioning the support relative to at least one of the protruding body and the holding portion. In this case, the support can be easily provided between the protruding body and the holding portion while maintaining the above-described positional relationship between the variable range and the notch. In addition, the positioning portion can effectively prevent the support from rotating between the protruding body and the holding portion.

[0027] The dual-rotation scroll compressor of the present invention can suppress the soaring manufacturing costs and also offers excellent quietness.

[0028] Figure 1 is a cross-sectional view of the compressor of Example 1. Figure 2 is an enlarged cross-sectional view of the main parts of the compressor of Example 1, showing the protruding body, holding part, and support body, etc. Figure 3 is a cross-sectional view of the compressor of Example 1, showing the section A-A in Figure 2. Figure 4 is a cross-sectional view of the compressor of Example 1, showing the section B-B in Figure 1. Figure 5 is a cross-sectional view of the compressor of Example 1, in the same direction as Figure 4, showing the state in which the drive scroll and driven scroll have rotated 180 degrees from the position shown in Figure 4. Figure 6 is a cross-sectional view of the compressor of Example 1, in the same direction as Figure 4, showing the state just before the drive scroll and driven scroll rotate 360 ​​degrees from the position shown in Figure 4. Figure 7 is a cross-sectional view of the compressor of Example 1, in the same direction as Figure 4, showing the range of variation in the load direction of the compression load. Figure 8 is a cross-sectional view of the compressor of Example 2, similar to Figure 3, showing the support body, etc. in the first state. Figure 9 is a cross-sectional view of the compressor of Example 2, similar to Figure 3, showing the support body, etc. in the second state. Figure 10 is a cross-sectional view of the compressor of Example 3, similar to Figure 3, showing the support and other components in the first state. Figure 11 is a cross-sectional view of the compressor of Example 3, similar to Figure 3, showing the support and other components in the second state.

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

[0030] As shown in Figure 1, the compressor of Embodiment 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.

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

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

[0033] The housing body 60 is cylindrical with 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).

[0034] The first housing cover 61 is located at the rear end of the housing body 60. The first housing cover 61 has a cover body portion 61a and a holding portion 61b. The cover body portion 61a is substantially disc-shaped with the drive shaft center O1 as its center and extends radially from the housing 6. The cover body portion 61a has a front surface 610a facing forward and a rear surface 610b located on the opposite side of the front surface 610a and facing rear.

[0035] The retaining portion 61b is integrally formed with the cover body portion 61a. The retaining portion 61b extends cylindrically forward from the front surface 610a of the cover body portion 61a in the direction of the drive axis O1. The retaining portion 61b consists of a base end portion 615 and a tip portion 616.

[0036] As shown in Figure 2, the base portion 615 constitutes the rear part of the holding portion 61b and is connected to the cover body portion 61a. The tip portion 616 constitutes the front part of the holding portion 61b. The tip portion 616 is connected to the base portion 615 and extends forward from the base portion 615. The tip portion 616 is formed in a cylindrical shape with a smaller diameter than the base portion 615. As shown in Figure 3, a first engagement groove 617 is formed in the tip portion 616. More specifically, the first engagement groove 617 is recessed in the radial direction of the housing 6 relative to the outer circumferential surface 616a of the tip portion 616.

[0037] As shown in Figure 2, a projection 64 is attached to the first housing cover 61. The projection 64 is made of steel. The projection 64 consists of a first diameter portion 64a and a second diameter portion 64b. The first diameter portion 64a constitutes the front portion of the projection 64. The first diameter portion 64a is formed to be smaller in diameter than the insertion hole 375, which will be described later. A pin hole 4 is formed in the first diameter portion 64a. The pin hole 4 extends through the interior of the first diameter portion 64a in the direction of the drive axis O1 and opens to the front end surface of the first diameter portion 64a.

[0038] Furthermore, a first radial ball bearing 51 is provided on the outer circumferential surface of the first diameter portion 64a. Alternatively, a sliding bearing may be provided on the outer circumferential surface of the first diameter portion 64a instead of the first radial ball bearing 51.

[0039] The second diameter portion 64b is integral with the first diameter portion 64a at its front end. As a result, the second diameter portion 64b constitutes the rear portion of the projection 64. The second diameter portion 64b is larger in diameter than the first diameter portion 64a and is formed in a bottomed cylindrical shape with an open rear end. Furthermore, the inner diameter of the second diameter portion 64b is larger in diameter than the outer diameter of the tip portion 616 of the holding portion 61b. As shown in Figure 3, a second engagement groove 642 is formed in the second diameter portion 64b. More specifically, the second engagement groove 642 is recessed in the radial direction of the housing 6 relative to the inner circumferential surface 641 of the second diameter portion 64b. Furthermore, a first keyway 64c is formed in the outer circumferential surface 643 of the second diameter portion 64b. The first keyway 64c is recessed in the radial direction of the housing 6 relative to the outer circumferential surface 643. Although detailed illustrations are omitted, the first keyway 64c extends from the front end to the rear end of the second diameter portion 64b toward the drive shaft center O1.

[0040] As shown in Figure 2, the projection 64 has the tip portion 616 of the holding portion 61b inserted into the interior of the second diameter portion 64b. The rear end of the second diameter portion 64b of the projection 64 abuts against the base end portion 615 of the holding portion 61b. Here, although not shown in the figure, the second diameter portion 64b and the base end portion 615 are connected by a connecting member. This prevents the projection 64 from rotating independently of the holding portion 61b, and consequently, the first housing cover 61.

[0041] Furthermore, a support 70a is provided between the radial projection 64 and the holding portion 61b of the housing 6, more specifically, between the second radial portion 64b and the tip portion 616 of the housing 6 in the radial direction.

[0042] The support 70a has a top foil 71 and a bump foil 73. The top foil 71 is made of a metal plate and extends in the direction of the drive axis O1. Also, as shown in Figure 3, the top foil 71 has a first notch 71a. Due to this first notch 71a, the top foil 71 does not have a cylindrical shape that goes all the way around in the circumferential direction. Specifically, when this compressor is viewed from the direction of the drive axis O1, the top foil 71 has an arc shape that extends in a roughly U-shape along the outer circumferential surface 616a of the tip portion 616. In other words, the first notch 71a separates one end and the other end of the top foil 71 in the circumferential direction. Also, a first engaging piece 711 is provided at the circumferential end of the top foil 71. The first engaging piece 711 is an example of a "positioning part" in the present invention. The first engaging piece 711 extends radially toward the tip portion 616 of the housing 6.

[0043] The bump foil 73 is formed from a metal plate. As shown in Figure 2, the bump foil 73 extends parallel to the top foil 71 in the direction of the drive axis O1. Also, as shown in Figure 3, the bump foil 73 has a second notch 73a. Due to this second notch 73a, the bump foil 73, like the top foil 71, does not have a cylindrical shape that goes all the way around in the circumferential direction. Specifically, when this compressor is viewed from the direction of the drive axis O1, the bump foil 73 has an arc shape that extends in a roughly U-shape along the inner circumferential surface 641 of the second diameter portion 64b. In other words, the second notch 73a separates one end and the other end of the bump foil 73 in the circumferential direction of the bump foil 73.

[0044] In the support body 70a, a notch 701 is formed by the first notch 71a and the second notch 73a. As a result, neither the top foil 71 nor the bump foil 73 is present in the notch 701. Due to this notch 701, the support body 70a does not have a full-circumferential cylindrical shape in the circumferential direction. In other words, when this compressor is viewed from the direction of the drive shaft center O1, the support body 70a has a shape extending in a substantially U-shape between the second diameter portion 64b and the distal end portion 616 in the radial direction of the housing 6, due to the shapes of the top foil 71 and the bump foil 73. In this way, the notch 701 spaces one end and the other end of the support body 70a in the circumferential direction apart from each other in the circumferential direction of the support body 70a. It should be noted that the size of the notch 701 in the circumferential direction of the support body 70a can be appropriately designed.

[0045] The bump foil 73 has bumps 73b. The bumps 73b are composed of six large-diameter bumps 731 and one small-diameter bump 732. Each large-diameter bump 731 is an example of the "first elastic portion" in the present invention, and the small-diameter bump 732 is an example of the "second elastic portion" in the present invention. Each large-diameter bump 731 and the small-diameter bump 732 respectively protrude in an arc shape from the second diameter portion 64b side toward the distal end portion 616 side in the radial direction of the housing 6. It should be noted that each large-diameter bump 731 and the small-diameter bump 732 may also protrude in an arc shape from the distal end portion 616 side toward the second diameter portion 64b side in the radial direction of the housing 6.

[0046] Here, each large-diameter bump 731 is set to a first spring constant. On the other hand, the small-diameter bump 732 is set to a second spring constant that is higher than the first spring constant. That is, each large-diameter bump 731 is formed in a shape protruding in an arc shape with a first radius of curvature so as to have the first spring constant. On the other hand, the small-diameter bump 732 is formed in a shape protruding in an arc shape with a second radius of curvature smaller than the first radius of curvature so as to have the second spring constant. Thus, the small-diameter bump 732 has a substantially semicircular arc shape with a smaller diameter than each large-diameter bump 731.

[0047] Furthermore, the bump foil 73 has a connecting portion 73c. The connecting portion 73c is positioned between each pair of adjacent large-diameter bumps 731, and between each large-diameter bump 731 and each small-diameter bump 732, respectively. Accordingly, the connecting portion 73c connects the adjacent large-diameter bumps 731 to each other at substantially equal intervals in the circumferential direction of the bump foil 73, and also connects the large-diameter bumps 731 and the small-diameter bumps 732 at substantially equal intervals in the circumferential direction of the bump foil 73. A second engagement piece 733 is provided at a circumferential end of the bump foil 73. The second engagement piece 733 is also an example of the "positioning portion" in the present invention. Note that the respective numbers of the large-diameter bumps 731 and the small-diameter bumps 732 can be designed as appropriate.

[0048] In the support body 70a, the first engagement piece 711 of the top foil 71 is engaged with the first engagement groove 617 of the tip portion 616. Accordingly, the top foil 71 is attached to the outer circumferential surface 616a of the tip portion 616. At this time, the first notch 71a is not in contact with the outer circumferential surface 616a. Furthermore, in the support body 70a, the second engagement piece 733 of the bump foil 73 is engaged with the second engagement groove 642 of the second diameter portion 64b. Accordingly, the bump foil 73 is attached to the inner circumferential surface 641 of the second diameter portion 64b. At this time, the second notch 73a is not in contact with the inner circumferential surface 641.

[0049] More specifically, by engaging the first engagement piece 711 with the first engagement groove 617, the top foil 71 is positioned such that the first notch 71a is located on the upper side of the compressor relative to an action point MP described later, and is attached to the outer circumferential surface 616a of the tip portion 616. Furthermore, by engaging the second engagement piece 733 with the second engagement groove 642, the bump foil 73 is positioned such that the second notch 73a is located on the upper side of the compressor relative to the action point MP described later, and the small-diameter bump 732 is located substantially directly below the action point MP, and is attached to the inner circumferential surface 641 of the second diameter portion 64b.

[0050] Thus, the support 70a is provided between the second diameter portion 64b and the tip portion 616 in the radial direction of the housing 6, with the notch portion 701 positioned above the compressor than the point of application MP. Since the first notch portion 71a is not in contact with the outer circumferential surface 616a of the tip portion 616, and the second notch portion 73a is not in contact with the inner circumferential surface 641 of the second diameter portion 64b, the notch portion 701 is not in contact with the outer circumferential surface 616a of the tip portion 616 and the inner circumferential surface 641 of the second diameter portion 64b. As a result, in the notch portion 701, the outer circumferential surface 616a of the tip portion 616 and the inner circumferential surface 641 of the second diameter portion 64b face each other in the radial direction of the housing 6.

[0051] Furthermore, in the support 70a, the bumps 73b, namely the large-diameter bump 731 and the small-diameter bump 732, are in contact with the top foil 71 and the inner circumferential surface 641 in the radial direction of the housing 6. In other words, in the support 70a, the bumps 73b are located below the notch 701 and are in contact with the top foil 71 and the inner circumferential surface 641. As a result, in the support 70a, the large-diameter bump 731 and the small-diameter bump 732 are able to maintain contact with the top foil 71, and consequently with the holding portion 61b via the top foil 71, while being able to elastically deform in the radial direction of the housing 6.

[0052] Thus, the top foil 71 is held on the outer circumferential surface 616a of the tip portion 616, and the bump foil 73 is held on the inner circumferential surface 641 of the second diameter portion 64b. As described above, the support 70a is provided between the second diameter portion 64b and the tip portion 616 in the radial direction of the housing 6. As a result, the projection 64 is attached to the first housing cover 61 via the support 70a. The holding portion 61b holds the projection 64 from the inside via the support 70a, thereby supporting the projection 64 on the first housing cover 61.

[0053] As shown in Figure 1, the second housing cover 62 is positioned in front of the housing body 60. The second housing cover 62 is substantially disc-shaped with the drive shaft center O1 as its center and extends radially across the housing 6. The second housing cover 62 has a front surface 62a facing forward and a rear surface 62b located opposite the front surface 62a and facing rear.

[0054] Furthermore, the second housing cover 62 has a support portion 66 and a discharge port 69 formed therein. The support portion 66 is integrally formed approximately in the center of the rear surface 62b and protrudes rearward from the rear surface 62b. The support portion 66 is formed in a cylindrical shape with the drive shaft center O1 as the center, and a second radial ball bearing 52, an elastic body 67, and a shaft sealing member 63 are provided inside.

[0055] The elastic body 67 is made of an elastically deformable resin such as synthetic rubber and is cylindrical in shape. The elastic body 67 is positioned between the support portion 66 and the second radial ball bearing 52, surrounding the second radial ball bearing 52 from the outside and holding the second radial ball bearing 52 within the support portion 66. The elastic body 67 may be made of a metal or the like with lower rigidity than the second housing cover 62. The thickness of the elastic body 67 can be designed as appropriate. Furthermore, a sliding bearing may be provided inside the support portion 66 instead of the second radial ball bearing 52.

[0056] The shaft seal member 63 is positioned inside the support portion 66, forward of the second radial ball bearing 52 and the elastic body 67. The shaft seal member 63 is formed in an annular shape.

[0057] The discharge port 69 penetrates the second housing cover 62 in the direction of the drive shaft center O1 and communicates with the inside of the support portion 66. The discharge port 69 is also connected to a condenser (not shown) through piping (not shown).

[0058] In the housing 6, the front surface 610a of the first housing cover 61 is in contact with the rear end of the housing body 60, and the rear surface 62b of the second housing cover 62 is in contact with the front end of the housing body 60. The housing body 60, the first housing cover 61, and the second housing cover 62 are fixed together in the direction of the drive axis O1 by a plurality of bolts (not shown).

[0059] 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.

[0060] 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.

[0061] 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.

[0062] 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 centered on the drive axis O1. As shown in Figure 3, a second keyway 17c is formed on the inner circumferential surface 170 of the stator core 17a. The second keyway 17c is recessed in the radial direction of the housing 6 relative to the inner circumferential surface 170. Although not shown in detail, the second keyway 17c extends from the front end to the rear end of the stator core 17a toward the drive axis O1.

[0063] As shown in Figure 2, the winding 17b is wound around the stator core 17a. This forms a first coil end 171 and a second coil end 172. 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.

[0064] In the stator 17, the stator core 17a is inserted through the outer circumferential surface 643 of the second diameter portion 64b. In this case, the stator core 17a has a second keyway 17c facing the first keyway 64c in the radial direction of the housing 6. The stator core 17a is then fixed to the second diameter portion 64b, and consequently to the protruding body 64, by fitting a key block 81 into these first keyway 64c and second keyway 17c from the drive shaft center O1. The key block 81 is an example of a "fixing member" in the present invention. In other words, the stator 17 and the protruding body 64 are fixed together by a key coupling.

[0065] Here, with the protruding body 64 and the stator core 17a fixed, the key block 81 is positioned so as to overlap the notch 701 of the support 70a in the radial direction of the housing 6. In other words, the first key groove 64c is formed on the outer circumferential surface 643 of the second radial portion 64b at a position where it overlaps the notch 701 with the radial direction of the housing 6.

[0066] Although not shown in the figures, the inner circumferential surface 170 of the stator core 17a has multiple slits that extend in the direction of the drive axis O1. As a result, the slits form a gap between the stator core 17a and the outer circumferential surface 643 of the second diameter portion 64b when the stator core 17a is fixed to the second diameter portion 64b.

[0067] The rotor 11 shown in Figure 2 is cylindrical around the drive axis O1. Although detailed illustrations are omitted, the rotor 11 is composed of multiple permanent magnets corresponding to the stator 17 and laminated steel plates that fix each permanent magnet. The rotor 11 is also formed to be larger in diameter than the stator core 17a. As a result, the rotor 11 covers the stator core 17a from the outside within the scroll chamber 65 and is rotationally driven by the stator 17. Furthermore, the rotor 11 has multiple first bolt holes 11a. Each first bolt hole 11a penetrates the rotor 11 in the direction of the drive axis O1.

[0068] 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.

[0069] 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.

[0070] 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.

[0071] 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. As shown in Figures 4 to 7, the drive spiral body 33 protrudes outward in a spiral shape from its own center.

[0072] As shown in Figure 1, the drive circumferential wall 35 is formed in a cylindrical shape that extends 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 figure, 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.

[0073] 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.

[0074] 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.

[0075] 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.

[0076] Furthermore, multiple rings 22 are attached to the wall portion 37a at the location between the recess 373 and the intake port 374. Although detailed illustrations are omitted, each ring 22 is arranged at equal intervals in the circumferential direction of the recess 373 when facing forward, and surrounds the recess 373 from the outside. In this embodiment, there are six rings 22. Figures 1 and 2 illustrate one of the six rings 22.

[0077] As shown in Figure 2, the inner cylindrical portion 37b is formed inward from the stator 17 in the radial direction of the cover body 37 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 64a of the protruding body 64 and is formed to be approximately the same as the outer diameter of the first radial ball bearing 51.

[0078] 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.

[0079] Furthermore, an insertion hole 375 is formed in the cover body 37 at the location that is inside the connection portion 37c. The insertion hole 375 extends in the direction of the drive shaft center O1 and connects the inner cylindrical portion 37b and the recess 373.

[0080] 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.

[0081] 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.

[0082] 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.

[0083] 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.

[0084] 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.

[0085] 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 39d is formed on the front wall 39b. The boss 39d is integrally formed in the center of the front wall 39b and protrudes forward from the front wall 39b in the direction of the drive axis O1. The outer diameter of the boss 39d is formed to be substantially the same as the inner diameter of the second radial ball bearing 52 and the inner diameter of the shaft sealing member 63. A discharge passage 390 is also formed on the boss 39d. The discharge passage 390 penetrates the boss 39d in the direction of the drive axis O1.

[0086] 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. Figure 1 shows one of these multiple third bolt holes 39e.

[0087] 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 the second bolts 34b are 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.

[0088] In this way, by fixing the case 39 to the drive peripheral wall 35, a discharge chamber 14 is formed inside the outer peripheral wall 39a, between the front wall 39b of the case 39 and the drive end plate 31. The discharge chamber 14 is in communication with the discharge port 32 and also with the discharge passage 390.

[0089] 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.

[0090] 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.

[0091] 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 faces the rear of the driven end plate 41, and consequently the first diameter portion 64a of the protruding body 64.

[0092] 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.

[0093] 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.

[0094] 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.

[0095] 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. As shown in Figures 4 to 7, the driven spiral body 43 protrudes outward in a spiral shape from its own center.

[0096] In this compressor, the driven scroll 40 is housed within the drive scroll 30, more specifically, in the drive scroll 30, at a location between the drive spiral body 33 and the drive peripheral wall 35 and the cover body 37. The drive spiral body 33 and the driven spiral body 43 are meshed together. As a result, the drive spiral body 33 and the driven spiral body 43 face each other and form a compression chamber 12. In this compressor, two compression chambers 12 are formed by the drive spiral body 33 and the driven spiral body 43 (see Figures 4 to 7).

[0097] Furthermore, as shown in Figure 1, an intake 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 intake section 30a. The intake 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 intake section 30a is also in communication with the intake port 374. As a result, the intake section 30a is in communication with the housing section 38 through the intake port 374.

[0098] 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.

[0099] 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.

[0100] 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 64a 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 64a is inserted into the insertion hole 375.

[0101] Here, since the cover body 37 is rotatably supported on the first diameter portion 64a, 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.

[0102] As described above, the first diameter portion 64a constitutes the front part of the projection 64, and the second diameter portion 64b constitutes the rear part of the projection 64. The stator core 17a is fixed to the outer circumferential surface of the second diameter portion 64b. Therefore, the inner cylindrical portion 37b is rotatably supported on the first diameter portion 64a 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.

[0103] Furthermore, in the cover body 37, the inner cylindrical portion 37b faces the second radial portion 64b 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 spaced apart in the radial direction of the housing 6.

[0104] 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.

[0105] Furthermore, in this compressor, when the cover body 37 is rotatably supported by the protruding body 64, the first diameter portion 64a, 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 diameter portion 64a, 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.

[0106] Furthermore, as shown in Figure 1, in the drive scroll 30, the boss 39d of the case 39 is inserted through the second radial ball bearing 52 and the shaft sealing member 63. As a result, the boss 39d is rotatably supported around the drive axis O1 by the support portion 66 via the second radial ball bearing 52 and the elastic body 67. In this way, the drive scroll 30 is positioned within the scroll chamber 65 and is rotatably supported around the drive axis O1 by both the protruding body 64 and the support portion 66 in the housing 6.

[0107] Furthermore, with the case 39 supported by the support portion 66, the discharge passage 390 faces the discharge port 69 from the rear. As a result, the discharge chamber 14 and the discharge port 69 are in communication through the discharge passage 390. The shaft sealing member 63 seals the space between the discharge passage 390 and the discharge port 69 and the scroll chamber 65.

[0108] On the other hand, in the driven scroll 40, the driven pin 55 of the driven shaft portion 16 is inserted into the pin hole 4. As a result, the driven scroll 40 is positioned in front of the protruding body 64 and is rotatably supported around the driven axis O2 relative to the first diameter portion 64a. Furthermore, by being rotatably supported by the first diameter portion 64a in this way, the driven scroll 40 is also rotatably supported by 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 by the protruding body 64 on the compression chamber 12 side of the stator core 17a. Moreover, by inserting the driven pin 55 into the pin hole 4, the driven scroll 40 is rotatably supported around the driven axis O2 by the first diameter portion 64a in the radial direction of the housing 6, inside the inner cylindrical portion 37b. Thus, unlike the drive scroll 30, the driven scroll 40 is supported by the housing 6 solely by the protruding body 64 so as to be rotatable around the driven axis O2.

[0109] Furthermore, in this compressor, the stator core 17a, the first radial ball bearing 51, and the bush 53 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 O1.

[0110] 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.

[0111] 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.

[0112] 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.

[0113] 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-pressure refrigerant, thus compressed to the discharge pressure, is discharged from the discharge port 32 into the discharge chamber 14, and further discharged to the outside of the compressor via the discharge passage 390 and the discharge connecting port 69. In this compressor, the space between the discharge passage 390 and the discharge connecting port 69 and the scroll chamber 65 is sealed by the shaft sealing member 63, preventing the refrigerant flowing from the discharge passage 390 to the discharge connecting port 69 from flowing into the scroll chamber 65.

[0114] In this compressor, the stator core 17a is fixed to the second diameter portion 64b of the protruding body 64. During operation, the electric motor 10 experiences torque fluctuations due to the compression of the refrigerant in the compression chamber 12. As a result, vibrations caused by these torque fluctuations of the electric motor 10 are inevitably transmitted from the stator core 17a to the protruding body 64.

[0115] Furthermore, in this compressor, the inner cylindrical portion 37b of the cover body 37 is rotatably supported on the first diameter portion 64a of the protruding body 64. In addition, the driven scroll 40 is also rotatably supported on the first diameter portion 64a. When the compressor is in operation, a compressive load is generated as the refrigerant is compressed. Therefore, the compressive load is inevitably transmitted to the protruding body 64 through the driving scroll 30 and the driven scroll 40.

[0116] In this compressor, a support 70a is provided between the radial projection 64 and the holding portion 61b of the housing 6, more specifically, between the inner circumferential surface 641 of the second radial portion 64b of the housing 6 and the outer circumferential surface 616a of the tip portion 616. The support 70a elastically supports the projection 64 by elastically deforming in the radial direction of the housing 6 while the bumps 73b, i.e., the large-diameter bump 731 and the small-diameter bump 732, are in contact with the holding portion 61b and the projection 64, respectively.

[0117] As a result, in this compressor, the support 70a effectively suppresses the transmission of the compressive load transmitted from the drive scroll 30 and the driven scroll 40 from the protruding body 64 to the holding part 61b and, consequently, to the housing 6. Furthermore, in this compressor, the support also effectively suppresses the transmission of vibrations generated by the electric motor 10 from the protruding body 64 to the housing 6.

[0118] In this compressor, since the support 70a has a notch 701, the support 70a is not cylindrical in shape that covers the entire holding portion 61b in the circumferential direction. In other words, the notch 701 separates one end and the other end of the support 70a in the circumferential direction. Furthermore, the notch 701 is not in contact with the inner circumferential surface 641 of the second diameter portion 64b and the outer circumferential surface 616a of the tip portion 616. In other words, the notch 701 is not in contact with the protruding body 64 and the holding portion 61b.

[0119] By having such a notch 701, in this compressor, when providing a support 70a between the inner circumferential surface 641 of the second diameter portion 64b and the outer circumferential surface 616a of the tip portion 616, it is possible not only to insert the support 70a into the second diameter portion 64b or the tip portion 616 in the direction of the drive axis O1, but also to attach the support 70a to the second diameter portion 64b or the tip portion 616 from the radial direction of the housing 6 by utilizing the notch 701. In this way, this compressor allows for a high degree of freedom in attaching the support 70a, and thus the decrease in manufacturing efficiency caused by providing a support 70a between the inner circumferential surface 641 of the second diameter portion 64b and the outer circumferential surface 616a of the tip portion 616 can be suppressed as much as possible.

[0120] Incidentally, as mentioned above, the notch 701 does not come into contact with the protruding body 64 and the holding portion 61b, so the support 70a cannot elastically support the protruding body 64 at the notch 701. In this respect, since both the drive scroll 30 and the driven scroll 40 rotate in this compressor, the direction in which the compressive load acts when the compressor is operating does not change significantly in the circumferential direction of the drive scroll 30 and the driven scroll 40. The direction in which the compressive load acts when the compressor is operating will be explained in detail below with reference to Figures 4 to 7.

[0121] Figures 4 to 7 are diagrams that assume a plane perpendicular to the drive axis O1 and the driven axis O2. In Figures 4 to 7, the drive scroll 30 and the driven scroll 40 are schematically shown, showing only the portion of the drive spiral 33 and the driven spiral 43 that substantially contribute to the formation of the compression chamber 12. In Figures 3 to 7, the drive-side base circle (base circle of the involute curve) 330 that forms the outer surface 33a and inner surface 33b of the drive spiral 33, and the driven-side base circle (base circle of the involute curve) 430 that forms the outer surface 43a and inner surface 43b of the driven spiral 43. The centers of the drive-side base circle 330 and the driven-side base circle 430 are offset by a predetermined amount in a direction perpendicular to the drive axis O1.

[0122] Figure 4 shows the drive scroll 30 and driven scroll 40 at the moment when the two compression chambers 12 are closed on the outermost side, that is, when each compression chamber 12 is closed. When each compression chamber 12 is closed, the outer surface 33a of the drive spiral body 33 and the inner surface 43b of the driven spiral body 43 are in contact at a first contact point P1 on the outermost side, and the inner surface 33b of the drive spiral body 33 and the outer surface 43a of the driven spiral body 43 are in contact at a second contact point P2 on the outermost side.

[0123] Here, we define a virtual line VL connecting the first contact point P1 and the second contact point P2. The length of the virtual line VL can be considered as the length of the radial width of the entire two compression chambers 12. The surface that includes this virtual line VL and extends in the direction of the drive axis O1 is defined as the pressure-receiving surface of the compressive load. Furthermore, the midpoint between the center of the drive-side base circle 330 and the center of the driven-side base circle 430 is defined as the point of application MP of the compressive load. This point of application MP can be considered as the center of the entire two compression chambers 12.

[0124] Furthermore, the direction perpendicular to the imaginary line VL in the plane perpendicular to the drive axis O1 and the driven axis O2 is defined as the load direction (direction of action) LD of the compressive load.

[0125] The first contact point P1 described above is located on one tangent line (not shown) that is tangent to both the driving base circle 330 and the driven base circle 430. The second contact point P2 is located on the other tangent line (not shown) that is tangent to both the driving base circle 330 and the driven base circle 430. These tangent lines extend parallel to the imaginary line VL.

[0126] Figure 5 shows the state after the drive scroll 30 and driven scroll 40 have rotated approximately 180 degrees from the closed position. Figure 6 shows the state just before the drive scroll 30 and driven scroll 40 have rotated 360 degrees from the closed position.

[0127] As shown in Figures 4 to 6, as the rotation of the drive scroll 30 and the driven scroll 40 progresses, the first contact P1 and the second contact P2 are displaced toward the inner circumference. Accordingly, the length of the imaginary line VL, that is, the length of the radial width of the entire two compression chambers 12, also gradually decreases.

[0128] Here, the drive axis O1 of the drive scroll 30 and the driven axis O2 of the driven scroll 40 are eccentric by a predetermined amount. As the drive scroll 30 and the driven scroll 40 rotate, the first contact P1 and the second contact P2 move, and therefore the load direction LD of the compressive load also changes. In Figure 7, the range in which the load direction LD changes during one rotation of the drive scroll 30 and the driven scroll 40 is defined as the variation range FR.

[0129] In Figures 4, 6, and 7, a hypothetical straight line L1 is defined that extends vertically in the direction of the compressor while being perpendicular to the drive axis O1, and the angle of the load direction LD with respect to this straight line L1 is defined as the load angle θ. As a result, when the compressor is closed, as shown in Figure 4, the load angle θ is the minimum load angle θmin. On the other hand, when the compressor is closed, as shown in Figure 6, just before it rotates 360 degrees, the load angle θ is the maximum load angle θmax.

[0130] As shown in Figure 7, the variation range FR of the load direction LD is the angular range of the difference between the minimum load angle θmin and the maximum load angle θmax at the load angle θ. Thus, in this compressor, during operation, the compression load acts downward from the point of application MP to the compressor, and the compression load fluctuates in the circumferential direction of the drive scroll 30 and the driven scroll 40 within the variation range FR during one rotation of the drive scroll 30 and the driven scroll 40. In other words, in this compressor, the compression load does not fluctuate beyond the variation range FR in the circumferential direction of the drive scroll 30 and the driven scroll 40.

[0131] As shown in Figure 3, in this compressor, when the support 70a, which is provided between the inner circumferential surface 641 of the second diameter portion 64b and the outer circumferential surface 616a of the tip portion 616, is viewed from the direction of the drive axis O1, the notch 701 is positioned to avoid the range of variation FR of the compressive load. More specifically, the notch 701 is positioned on the opposite side of the point of application MP from the range of variation FR, that is, the notch 701 is positioned above the point of application MP. Thus, in this compressor, when the support 70a is viewed from the direction of the drive axis O1, the notch 701 and the range of variation FR do not overlap, so the fact that the notch 701 is not in contact with the protruding body 64 and the holding portion 61b does not affect the support 70a's support of the protruding body 64 against the compressive load. As a result, even though the support 70a has a notch 701, the support 70a effectively suppresses the transmission of the compressive load and vibrations generated by the electric motor 10 from the protruding body 64 to the housing 6, as described above.

[0132] Therefore, the compressor of Example 1 can suppress the soaring manufacturing costs and is also excellent in terms of quietness.

[0133] In particular, in this compressor, the bumps 73b of the support body 70a are composed of six large-diameter bumps 731 and one small-diameter bump 732. When the support body 70a is viewed from the direction of the drive axis O1, the small-diameter bump 732 is located almost directly below the point of application MP and overlaps with the range of compression load fluctuation FR. For this reason, it is more important to suppress the transmission of the compression load from the protruding body 64 to the housing 6 with respect to the small-diameter bump 732. In this regard, the small-diameter bump 732 is set to a second spring constant and is less elastically deformable than the large-diameter bump 731 which is set to a first spring constant. As a result, the small-diameter bump 732 does not undergo unnecessarily large elastic deformation due to the compression load, and therefore the small-diameter bump 732 can effectively suppress the transmission of the compression load from the protruding body 64 to the housing 6.

[0134] Furthermore, in this compressor, the key block 81 that fixes the protruding body 64 and the stator core 17a is positioned in the radial direction of the housing 6 so as to overlap with the notch 701. Therefore, in this compressor, when fixing the protruding body 64 and the stator core 17a with the key block 81, the key block 81 can be fitted into the first key groove 64c and the second key groove 17c in areas where the support 70a is not present. As a result, the key block 81 can be easily fitted into the first key groove 64c and the second key groove 17c, making it possible to easily fix the protruding body 64 and the stator core 17a with the key block 81. In addition, in this compressor, the load when fitting the key block 81 into the first key groove 64c and the second key groove 17c is less likely to act on the top foil 71 and bump foil 73 of the support 70a.

[0135] Furthermore, in this compressor, the support body 70a is attached to the outer circumferential surface 616a of the tip portion 616 by engaging the first engaging piece 711 of the top foil 71 with the first engaging groove 617 of the tip portion 616. In addition, the bump foil 73 is attached to the inner circumferential surface 641 of the second diameter portion 64b by engaging the second engaging piece 733 of the bump foil 73 with the second engaging groove 642 of the second diameter portion 64b. These first engaging pieces 711 and 733 are located in the notch portion 701 and engage with the first engaging groove 617 and the second engaging groove 642, respectively. As a result, in this compressor, the support body 70a can be easily provided between the protruding body 64 and the holding portion 61b while the notch portion 701 is located above the point of action MP and the small diameter bump 732 is located almost directly below the point of action MP.

[0136] Furthermore, since the first engaging piece 711 of the top foil 71 is engaged with the first engaging groove 617 and the second engaging piece 733 of the bump foil 73 is engaged with the second engaging groove 642, this compressor can effectively prevent the support 70a from rotating between the protruding body 64 and the holding portion 61b.

[0137] Furthermore, in this compressor, since the notch 701 is located above the point of action MP, the top foil 71 and the bump foil 73 are located below the notch 701. Therefore, in this compressor, each bump 73b of the bump foil 73 can suitably contact the top foil 71 even due to gravity acting on the compressor. In this way, the support 70a can suitably maintain the state in which each bump 73b and the top foil 71 are in contact, so that each bump 73b can suitably undergo elastic deformation.

[0138] As shown in Figure 8, in the compressor of Embodiment 2, a support 70b is provided between the second radial portion 64b and the tip portion 616 in the radial direction of the housing 6. The support 70b has a top foil 71 and a bump foil 75.

[0139] The bump foil 75 is formed from a metal plate. Although detailed illustrations are omitted, the bump foil 75, like the bump foil 73 in the compressor of Embodiment 1, extends parallel to the top foil 71 in the direction of the drive axis O1. Furthermore, as shown in Figure 8, the bump foil 75 has a second notch 75a. Due to this second notch 75a, the bump foil 75, like the top foil 71, does not have a cylindrical shape that goes all the way around in the circumferential direction. As a result, like the bump foil 73 in the compressor of Embodiment 1, the bump foil 75 also has an arc shape that extends in a roughly U-shape along the inner circumferential surface 641 of the second diameter portion 64b when the compressor is viewed from the direction of the drive axis O1. In other words, the second notch 75a separates one end and the other end of the bump foil 75 in the circumferential direction of the bump foil 75.

[0140] In the support 70b, a notch 702 is formed by the second notch 75a and the first notch 71a of the top foil 71. As a result, the top foil 71 and bump foil 75 are not present in the notch 702. Furthermore, due to this notch 702, the support 70b does not have a cylindrical shape that goes all the way around in the circumferential direction. In other words, when this compressor is viewed from the direction of the drive axis O1, the support 70b has a shape that extends in a roughly U shape between the second radial portion 64b and the tip portion 616 in the radial direction of the housing 6, due to the shapes of the top foil 71 and bump foil 75. In this way, the notch 702 separates one end and the other end of the support 70b in the circumferential direction of the support 70b. The size of the notch 702 in the circumferential direction of the support 70b can be designed as appropriate.

[0141] The bump foil 75 has a bump 75b and a connecting portion 75c. The bump 75b is composed of three main bumps 751 and four sub-bumps 752. Each main bump 751 and each sub-bump 752 protrudes in an arc shape from the second diameter portion 64b side toward the tip portion 616 side in the radial direction of the housing 6. Each main bump 751 protrudes more toward the tip portion 616 side than each sub-bump 752. The number of main bumps 751 and sub-bumps 752 can be designed as appropriate. The number of main bumps 751 may be greater than the number of sub-bumps 752, or the number of main bumps 751 and the number of sub-bumps 752 may be equal. Furthermore, each main bump 751 and each sub-bump 752 may protrude in an arc shape from the tip portion 616 side toward the second diameter portion 64b side in the radial direction of the housing 6.

[0142] In this compressor, the first state is defined as a condition where the resultant force of the inertial force due to vibration transmitted from the electric motor 10 to the protruding body 64 (hereinafter simply referred to as the inertial force) and the compressive load transmitted from the drive scroll 30 and the driven scroll 40 to the protruding body 64 is less than or equal to a set value. Here, the first state also includes the case where the compressor has stopped operating and the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is zero. On the other hand, the second state is defined as a condition where the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is greater than the set value.

[0143] Furthermore, in the bump foil 75, each main bump 751 is in contact with the top foil 71 in both the case when the compressor is in the first state (see Figure 8) and the case when the compressor is in the second state (see Figure 9). In other words, each main bump 751 is always in contact with the tip portion 616, and consequently the holding portion 61b, via the top foil 71, regardless of whether it is in the first or second state. On the other hand, as shown in Figure 8, in the bump foil 75, each sub-bump 752 is separated from the top foil 71 in the radial direction of the housing 6 when the compressor is in the first state, and is not in contact with the top foil 71. Thus, each sub-bump 752 is not in contact with the holding portion 61b in the first state.

[0144] Furthermore, each main bump 751 is formed in an arc shape with a smaller radius of curvature than each sub-bump 752. As a result, in this compressor, each sub-bump 752 is set to a first spring constant, and each main bump 751 is set to a second spring constant that is greater than the first spring constant. Thus, in this compressor, each main bump 751 is the "second elastic part" in the present invention, and each sub-bump 752 is the "first elastic part" in the present invention.

[0145] The connecting portion 75c is located between the main bump 751 and the sub-bump 752, and between the sub-bumps 752 themselves. As a result, the connecting portion 75c connects the main bump 751 and the sub-bump 752 at approximately equal intervals in the circumferential direction of the bump foil 75, and also connects the sub-bumps 752 themselves at approximately equal intervals in the circumferential direction of the bump foil 75. In addition, a second engaging piece 753 is provided at the circumferential end of the bump foil 75. The second engaging piece 753 is also an example of a "positioning portion" in the present invention.

[0146] In the support 70b, the second engaging piece 753 of the bump foil 75 is engaged with the second engaging groove 642 of the second diameter portion 64b. As a result, the bump foil 75 is attached to the inner circumferential surface 641 of the second diameter portion 64b. At this time, the second notch portion 75a is not in contact with the inner circumferential surface 641. On the other hand, as the bump foil 75 is attached to the inner circumferential surface 641 in this way, each main bump 751, each sub-bump 752 and each connecting portion 75c are in contact with the inner circumferential surface 641, i.e., the protruding body 64.

[0147] Thus, each main bump 751 is in contact with the projection 64 and the retaining portion 61b in both the first and second states. On the other hand, each sub-bump 752 is in contact with the projection 64 in the first state, but as described above, it is not in contact with the retaining portion 61b.

[0148] Furthermore, the bump foil 75 is positioned such that one of the three main bumps 751 is located almost directly below the point of action MP, and is attached to the inner circumferential surface 641 of the second diameter portion 64b.

[0149] In this compressor, the support 70b is provided between the second diameter portion 64b and the tip portion 616 in the radial direction of the housing 6, with the notch 702 positioned above the compressor relative to the point of action MP. The notch 702 is not in contact with the outer circumferential surface 616a of the tip portion 616 and the inner circumferential surface 641 of the second diameter portion 64b. As a result, similar to the notch 701 in the compressor of Embodiment 1, the outer circumferential surface 616a of the tip portion 616 and the inner circumferential surface 641 of the second diameter portion 64b face each other in the radial direction of the housing 6 in the notch 702 as well. Thus, by providing the support 70b between the second diameter portion 64b and the tip portion 616 in the radial direction of the housing 6, the projection 64 is attached to the first housing cover 61 via the support 70b. The holding portion 61b supports the protruding body 64 from the inside via the support body 70b, thereby supporting the protruding body 64 with the first housing cover 61.

[0150] Furthermore, in the support 70b, the notch 702 overlaps with the key block 81 in the radial direction of the housing 6. The other components of this compressor are the same as those of the compressor in Embodiment 1, and the same reference numerals are used for the same components, and a detailed explanation of the components is omitted.

[0151] In this compressor, since the support 70b has a notch 702, the degree of freedom in mounting the support 70b can be increased by utilizing this notch 702. Also, similar to the compressor in Embodiment 1, in this compressor as well, when the support 70b provided between the protruding body 64 and the holding part 61b is viewed from the direction of the drive axis O1, the notch 702 is positioned to avoid the range of compression load fluctuation FR. As a result, in this compressor as well, the support 70b can suitably suppress the transmission of the resultant force of the inertial force and compression load transmitted to the protruding body 64 from the protruding body 64 to the housing 6.

[0152] In this first state, only the main bumps 751 of the bump foil 75 are in contact with the inner circumferential surface 641 and the top foil 71, and consequently with the protruding body 64 and the holding portion 61b. Therefore, in this compressor, when the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is less than or equal to a set value, the housing 6 can be elastically deformed radially while maintaining the state in which only the main bumps 751 are in contact with the protruding body 64 and the holding portion 61b. In other words, in this compressor, when the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is less than or equal to a set value, the sub-bumps 752 of the bump foil 75 do not elastically deform radially in the housing 6 on the support 70b.

[0153] On the other hand, in the second state, where the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is greater than the set value, as shown in Figure 9, the protruding body 64 attempts to move significantly in the radial direction of the housing 6 relative to the retaining portion 61b due to the resultant force of the inertial force and compressive load transmitted to it. Therefore, in the second state, compared to the first state, each main bump 751 undergoes a large elastic deformation in the radial direction of the housing 6 while maintaining contact with the protruding body 64 and the retaining portion 61b. As a result, in the second state, in addition to each main bump 751, each sub-bump 752 also comes into contact with the top foil 71. In other words, in the second state, the sub-bump 752 elastically deforms in the radial direction of the housing 6 while in contact with the inner circumferential surface 641 and the top foil 71, and consequently with the protruding body 64 and the retaining portion 61b.

[0154] Thus, in the second state, that is, when the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is greater than the set value, the support body 70b elastically deforms radially of the housing 6 while maintaining a state in which both the main bumps 751 and the sub-bumps 752 are in contact with the protruding body 64 and the holding portion 61b, respectively. As a result of the elastic deformation of each main bump 751 and the sub-bumps 752 radially of the housing 6, the overall spring constant of the support body 70b becomes larger compared to the case where only the main bumps 751 elastically deform radially of the housing 6. In other words, in this compressor, the spring constant of the support body 70b changes in two stages between the first state and the second state. Thus, in this compressor, in either the first or second state, the support body 70b can suitably suppress the transmission of the resultant force of the inertial force and compressive load transmitted to the protruding body 64 from the protruding body 64 to the housing 6. Other functions of this compressor are the same as those of the compressor in Example 1.

[0155] As shown in Figure 10, in the compressor of Embodiment 3, a support 70c is provided between the second radial portion 64b and the tip portion 616 in the radial direction of the housing 6. The support 70c has a top foil 71 and a bump foil 77.

[0156] The bump foil 77 is formed from a metal plate. Although detailed illustrations are omitted, the bump foil 77, like the bump foil 73 in the compressor of Embodiment 1, extends parallel to the top foil 71 in the direction of the drive axis O1. Also, as shown in Figure 10, the bump foil 77 has a second notch 77a. Due to this second notch 77a, the bump foil 77 is not a cylindrical shape that goes all the way around in the circumferential direction. In other words, when the compressor is viewed from the direction of the drive axis O1, the bump foil 77 has an arc shape that extends in a roughly U-shape along the inner circumferential surface 641 of the second diameter portion 64b. That is, the second notch 77a separates one end and the other end of the bump foil 77 in the circumferential direction.

[0157] In the support 70c, a notch 703 is formed by the second notch 77a and the first notch 71a of the top foil 71. As a result, the top foil 71 and bump foil 77 are not present in the notch 703. Furthermore, due to this notch 703, the support 70c does not have a cylindrical shape that goes all the way around in the circumferential direction. In other words, when this compressor is viewed from the direction of the drive axis O1, the support 70c has a shape that extends in a roughly U shape between the second radial portion 64b and the tip portion 616 in the radial direction of the housing 6. In this way, the notch 703 separates one end and the other end of the support 70c in the circumferential direction of the support 70c. The size of the notch 703 in the circumferential direction of the support 70c can be designed as appropriate.

[0158] The bump foil 77 has bumps 77b and second engaging pieces 77c. The second engaging pieces 77c are also an example of a "positioning part" in the present invention. The bump 77b is composed of three first bumps 771, two second bumps 772, and four third bumps 773. The second engaging pieces 77c are provided at the circumferential end of the bump foil 75. The number of each of the first to third bumps 771 to 773 can be designed as appropriate.

[0159] Each first bump 771 is curved in the radial direction of the housing 6 so as to extend from the second diameter portion 64b side toward the tip portion 616 side. Each second bump 772 is positioned spaced apart from each first bump 771 in the radial direction of the bump foil 77, that is, in the circumferential direction of the protruding body 64. Each second bump 772 is curved in the radial direction of the housing 6 so as to extend from the tip portion 616 side toward the second diameter portion 64b side. Thus, each second bump 772 is curved in the radial direction of the housing 6 toward the opposite side from each first bump 771. Each third bump 773 is positioned between the first bump 771 and the second bump 772 in the circumferential direction of the protruding body 64. Each third bump 773 is connected to the first bump 771 and the second bump 772 while curving toward the second diameter portion 64b side and the tip portion 616 side, respectively, in the radial direction of the housing 6.

[0160] In the support 70c, the second engaging piece 77c of the bump foil 77 is engaged with the second engaging groove 642 of the second diameter portion 64b. This attaches the bump foil 77 to the inner circumferential surface 641 of the second diameter portion 64b. At this time, the bump foil 77 is positioned so that one of the first bumps 771 is located approximately directly below the point of application MP, and is attached to the inner circumferential surface 641 of the second diameter portion 64b. Also, similar to the compressor in Embodiment 2, in this compressor as well, the state in which the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is less than or equal to a set value is considered the first state (see Figure 10), and the state in which the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is greater than the set value is considered the second state (see Figure 11).

[0161] Here, in the bump foil 77, each first bump 771 is in contact only with the top foil 71, regardless of whether the compressor is in the first or second state. On the other hand, each second bump 772 is in contact only with the inner circumferential surface 641 of the second diameter portion 64b, regardless of whether the compressor is in the first or second state. And each third bump 773 is not in contact with either the inner circumferential surface 641 or the top foil 71 when the compressor is in the first state (see Figure 10). Thus, in the bump foil 77, each first bump 771 is always in contact only with the tip portion 616, and consequently with the holding portion 61b, via the top foil 71, regardless of whether the compressor is in the first or second state. And each second bump 772 is always in contact only with the protruding body 64, regardless of whether the compressor is in the first or second state.

[0162] In this compressor as well, the support 70c is provided between the second diameter portion 64b and the tip portion 616 in the radial direction of the housing 6, with the notch portion 703 positioned above the compressor above the point of action MP. The notch portion 703 is not in contact with the outer circumferential surface 616a of the tip portion 616 and the inner circumferential surface 641 of the second diameter portion 64b. As a result, at the notch portion 703, the outer circumferential surface 616a of the tip portion 616 and the inner circumferential surface 641 of the second diameter portion 64b face each other in the radial direction of the housing 6. In this way, by providing the support 70c between the second diameter portion 64b and the tip portion 616 in the radial direction of the housing 6, the projection 64 is attached to the first housing cover 61 via the support 70c. The holding portion 61b supports the projection 64 by holding it from the inside via the support 70c, thereby supporting the projection 64 on the first housing cover 61.

[0163] Furthermore, in the support 70c, the notch 703 overlaps with the key block 81 in the radial direction of the housing 6. The other configurations of this compressor are the same as those of the compressor in Embodiment 1.

[0164] Similar to the compressors in Examples 1 and 2, this compressor also allows for greater flexibility in mounting the support 70c by utilizing the notch 703 of the support 70c. Furthermore, in this compressor as well, the notch 703 is positioned to avoid the range of compression load fluctuation FR, so the support 70c effectively suppresses the transmission of the resultant force of the inertial force and compression load transmitted to the protruding body 64 from the protruding body 64 to the housing 6.

[0165] In this compressor, in the first state, each first bump 771 of the bump foil 75 is in contact with the holding portion 61b, and each second bump 772 is in contact with the protruding body 64. Therefore, when the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is less than the set value, each first bump 771 can elastically deform in the radial direction of the housing 6 while maintaining contact with the holding portion 61b, and each second bump 772 can elastically deform in the radial direction of the housing 6 while maintaining contact with the protruding body 64. Thus, when the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is less than or equal to the set value, in the support 70c, each first bump 771 and each second bump 772 elastically deforms in the radial direction of the housing 6, but each third bump 773 does not elastically deform in the radial direction of the housing 6. In other words, in the first state, the support 70c elastically supports the protrusion 64 as each first bump 771 and each second bump 772 elastically deforms in the radial direction of the housing 6.

[0166] On the other hand, in the second state, when the resultant force of the inertial force and compressive load transmitted to the protruding body 64 is greater than the set value, as shown in Figure 11, the protruding body 64 attempts to move significantly in the radial direction of the housing 6 relative to the holding portion 61b due to the resultant force of the inertial force and compressive load transmitted to it. For this reason, in the second state, compared to the first state, each first bump 771 undergoes a large elastic deformation in the radial direction of the housing 6 while maintaining contact with the holding portion 61b. Similarly, each second bump 772 undergoes a large elastic deformation in the radial direction of the housing 6 while maintaining contact with the protruding body 64. As a result, in the second state, each third bump 773 comes into contact with the inner circumferential surface 641 and the top foil 71, respectively. In other words, in the second state, each third bump 773 comes into contact with the protruding body 64 and the holding portion 61b.

[0167] Thus, in the second state, the support 70c elastically deforms radially of the housing 6 while each third bump 773 maintains contact with the protrusion 64 and the holding portion 61b. In this way, in the second state, that is, when the resultant force of the inertial force and compressive load transmitted to the protrusion 64 is greater than the set value, each third bump 773, in addition to each first bump 771 and each second bump 772, also elastically deforms radially of the housing 6, thereby elastically supporting the protrusion 64 with the support 70c. In this way, in this compressor, the overall spring constant of the support 70c is larger when each of the first to third bumps 771 to 773 elastically deforms radially of the housing 6 compared to when only each of the first bumps 771 and each second bump 772 elastically deforms radially of the housing 6. In other words, in this compressor as well, the spring constant of the support 70c changes in two stages between the first state and the second state. As a result, in this compressor, in either the first or second state, the support 70c can suitably suppress the transmission of the resultant force of the inertial force and compressive load transmitted to the protruding body 64 from the protruding body 64 to the housing 6. Other functions of this compressor are the same as those of the compressor in Example 1.

[0168] 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.

[0169] For example, in the compressor of Example 1, the support 70a has a top foil 71 and a bump foil 73 made of metal plate material. In other words, the support 70a is made of metal. However, it is not limited to this, and the support 70a may be made of resin as long as it has a notch 701. The same applies to the compressors of Examples 2 and 3.

[0170] Furthermore, in the compressor of Example 1, the top foil 71 may be omitted, and the support 70a may consist only of the bump foil 73. The same applies to the compressors of Examples 2 and 3.

[0171] Furthermore, in the compressor of Example 1, the radius of curvature of the small-diameter bump 732 is made smaller than that of the large-diameter bump 731, thereby making the small-diameter bump 732 the second spring constant. However, this is not the only way; the small-diameter bump 732 may also be made the second spring constant by forming it with a thicker wall than the large-diameter bump 731.

[0172] Furthermore, in the compressor of Example 1, when the support 70a is viewed from the direction of the drive axis O1, the notch 701 is located on the opposite side of the point of application MP with respect to the variation range FR of the compressive load. However, this is not the only option; the notch 701 may be located below the point of application MP, etc., as long as it avoids the variation range FR. The same applies to the compressors of Examples 2 and 3.

[0173] Furthermore, in the compressor of Example 1, the compression load acts downward from the point of application MP during operation. However, the compressor is not limited to this configuration, and the compression load may also act in the direction to the right or left of the paper, such as in Figure 4, from the point of application MP. Even in this case, the above-described effect can be achieved if the notch 701 is positioned to the right or left of the point of application MP when the support 70a is viewed from the direction of the drive axis O1. The same applies to the compressors of Examples 2 and 3.

[0174] Furthermore, in the compressor of Example 1, one of the seven bumps 73b is a small-diameter bump 732, that is, the "second elastic part" in the present invention. However, the number of small-diameter bumps 732 can be changed as appropriate. Also, the number of small-diameter bumps 732 may be greater than the number of large-diameter bumps 731.

[0175] Furthermore, in the compressor of Example 2, the state in which either the inertial force or the compressive load transmitted to the protruding body 64 is less than or equal to a set value may be defined as the first state, and the state in which either the inertial force or the compressive load transmitted to the protruding body 64 is greater than the set value may be defined as the second state. The same applies to the compressor of Example 3.

[0176] Furthermore, in the compressor of Example 2, the bump foil 75 may be formed such that one of the sub-bumps 752 overlaps with the fluctuation range FR when the support 70b is viewed from the direction of the drive axis O1. In this way, the main bump 751 may be designated as the "first elastic body" in the present invention, and the sub-bump 752 may be designated as the "second elastic body" in the present invention.

[0177] Furthermore, in the compressor of Embodiment 2, when the support 70b is viewed from the direction of the drive axis O1, only one main bump 751 that overlaps with the fluctuation range FR may be formed to have a second spring constant, while the other main bumps 751 and sub-bumps 752 may be formed to have a first spring constant.

[0178] Furthermore, in the compressor of Embodiment 3, when the support 70c is viewed from the direction of the drive axis O1, one of the first bumps 771 overlaps with the fluctuation range FR. For this reason, the spring constant of this first bump 771 may be higher than that of the other first to third bumps 771 to 773. Also, not limited to the first bump 771, the second bump 772 and the third bump 773 may be arranged to overlap with the fluctuation range FR. In this case as well, the spring constants of the second bump 772 and the third bump 773 may be higher than those of the other first to third bumps 771 to 773.

[0179] Furthermore, in the compressor of Example 1, the projection 64 and the stator core 17a are fixed by a key block 81. However, the method is not limited to this, and the projection 64 and the stator core 17a may also be fixed by fitting the second diameter portion 64b of the projection 64 into the inner circumferential surface 170 of the stator core 17a. The same applies to the compressors of Examples 2 and 3.

[0180] Furthermore, this specification includes the following inventions: (Note 1) A housing comprising a drive scroll, a driven scroll, a drive mechanism and a driven mechanism, wherein the housing has a scroll chamber in which the drive scroll, the driven scroll and the drive mechanism are housed, the drive mechanism has a stator and a rotor that is rotationally driven by the stator, the drive scroll is rotationally driven around a drive axis by the drive mechanism, the driven scroll is rotationally driven around a driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, the drive scroll has a drive end plate extending in a direction intersecting the drive axis and a drive spiral body projecting spirally from the drive end plate toward the driven scroll, the driven scroll has a driven end plate extending in a direction intersecting the driven axis and a driven spiral body projecting spirally from the driven end plate toward the drive end plate, The drive scroll and the driven scroll are a double-rotation scroll compressor in which a compression chamber for compressing a fluid is formed by rotating the drive scroll and the driven scroll facing each other and rotating them toward each other, the stator is mounted inside the scroll chamber and a projection is provided extending toward the drive axis toward the drive scroll and the driven scroll, the drive scroll is rotatably supported by the projection around the drive axis, the driven scroll is rotatably supported by the projection around the driven axis, the housing has a holding portion extending toward the drive axis and located inside the projection, a support is provided between the projection and the holding portion in the radial direction of the housing that elastically deforms to support the projection, the support has a notch that separates one end and the other end in the circumferential direction of the support and is not in contact with the projection and the holding portion, and a virtual plane perpendicular to the drive axis is assumed,A dual-rotation scroll compressor characterized in that, when viewed from the drive axis direction, the notch is positioned to avoid the variation range, with respect to the midpoint between the center of the drive-side base circle forming the drive-side spiral body and the center of the driven-side base circle forming the driven-side spiral body in the virtual plane, and the direction perpendicular to the virtual line connecting the first contact point where the outer surface of the drive-side spiral body and the inner surface of the driven-side spiral body contact at the outermost circumference in the virtual plane, and the second contact point where the inner surface of the drive-side spiral body and the outer surface of the driven-side spiral body contact at the outermost circumference, and the range in which the load direction changes during one rotation of the drive-side scroll and the driven-side scroll being defined as the variation range. (Note 2) The double-rotating scroll compressor according to Note 1, wherein, when the support is viewed from the direction of the drive axis, the notch is located on the opposite side of the point of application with respect to the fluctuation range. (Note 3) The double-rotating scroll compressor according to Note 1 or 2, wherein the support is provided with bumps formed from elastically deformable metal plates and protruding in the radial direction. (Note 4) The state in which the resultant force of the inertial force and compressive load due to vibration transmitted to the protruding body is less than or equal to a set value is defined as the first state, and the state in which the resultant force of the inertial force and compressive load transmitted to the protruding body is greater than the set value is defined as the second state, and the bump has a main bump that contacts the protruding body and the holding part in the first and second states, and a sub-bump that contacts only one of the protruding body and the holding part in the first state, and contacts both the protruding body and the holding part in the second state. (Note 5) The state in which the resultant force of the inertial force and compressive load transmitted to the protruding body is less than or equal to the set value is considered the first state, and the state in which the resultant force of the inertial force and compressive load transmitted to the protruding body is greater than the set value is considered the second state.The double-rotating scroll compressor as described in Appendix 3, wherein the bump comprises a first bump, a second bump positioned spaced apart from the first bump in the circumferential direction of the projection, and a third bump positioned between the first and second bumps in the circumferential direction of the projection and connected to the first and second bumps, wherein the first bump contacts only the holding portion in the first and second states, the second bump contacts only the projection in the first and second states, and the third bump is not in contact with the holding portion and the projection in the first state, but contacts both the holding portion and the projection in the second state. (Note 6) The double-rotation scroll compressor according to any one of Notes 1 to 5, wherein the support body has a first elastic portion set to a first spring constant and a second elastic portion set to a second spring constant higher than the first spring constant, and when the support body is viewed from the direction of the drive axis, the second elastic portion is positioned to overlap with at least the fluctuation range. (Note 7) The double-rotation scroll compressor according to any one of Notes 1 to 6, wherein the stator is fixed to the protruding body by a fixing member, and the fixing member is positioned to overlap with the notch in the radial direction. (Note 8) The double-rotation scroll compressor according to any one of Notes 1 to 7, wherein the support body is positioned in the notch and has a positioning portion for positioning at least one of the protruding body and the holding portion and the support body.

[0181] This invention can be used in vehicle air conditioning systems and the like.

[0182] 6 Housing 10 Electric motor (drive mechanism) 11 Rotor 12 Compression chamber 17 Stator 20 Driven mechanism 30 Driven scroll 31 Driven end plate 33 Driven spiral body 33a Outer surface of driven spiral body 33b Inner surface of driven spiral body 40 Driven scroll 41 Driven end plate 43 Driven spiral body 43a Outer surface of driven spiral body 43b Inner surface of driven spiral body 61a Holding part 64 Projection 65 Scroll chamber 70a, 70b, 70c Support 73b, 75b, 77b Bump 81 Key block (fixing member) 330 Driven side base circle 430 Driven side base circle 701-703 Notch 711 First engaging piece (positioning part) 731 Large diameter bump (first elastic part) 732 Small diameter bump (second elastic part) 733, 753, 77c Second engaging piece (positioning part) 751 Main bump (second elastic part) 752 Sub-bump (first elastic part) 771 First bump 772 Second bump 773 Third bump FR Range of variation MP Point of application O1 Drive shaft center O2 Driven shaft center P1 First contact point P2 Second contact point VL Imaginary line

Claims

1. The device comprises a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism, wherein the housing has a scroll chamber in which the drive scroll, the driven scroll, and the drive mechanism are housed, the drive mechanism has a stator and a rotor that is rotationally driven by the stator, the drive scroll is rotationally driven around a drive axis by the drive mechanism, the driven scroll is rotationally driven around a driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, the drive scroll has a drive end plate extending in a direction intersecting the drive axis and a drive spiral body projecting spirally from the drive end plate toward the driven scroll, the driven scroll has a driven end plate extending in a direction intersecting the driven axis and a drive spiral body projecting spirally from the driven end plate toward the drive end plate, The drive scroll and the driven scroll are a double-rotation scroll compressor in which a compression chamber for compressing a fluid is formed by rotating the drive scroll and the driven scroll facing each other and rotating them toward each other, the stator is mounted inside the scroll chamber and a projection is provided extending toward the drive axis toward the drive scroll and the driven scroll, the drive scroll is rotatably supported by the projection around the drive axis, the driven scroll is rotatably supported by the projection around the driven axis, the housing has a holding portion extending toward the drive axis and located inside the projection, a support is provided between the projection and the holding portion in the radial direction of the housing that elastically deforms to support the projection, the support has a notch that separates one end and the other end in the circumferential direction of the support and is not in contact with the projection and the holding portion, and a virtual plane perpendicular to the drive axis is assumed, The midpoint between the center of the driving base circle forming the driving spiral body and the center of the driven base circle forming the driven spiral body in the virtual plane is defined as the point of application of the compressive load generated radially outward from the center side of the driving scroll and the driven scroll due to the rotation of the driving scroll and the driven scroll.In the aforementioned virtual plane, the direction perpendicular to the virtual line connecting the first contact point where the outer surface of the drive spiral and the inner surface of the driven spiral contact at their outermost periphery, and the second contact point where the inner surface of the drive spiral and the outer surface of the driven spiral contact at their outermost periphery, is defined as the load direction of the compression load, and the range in which the load direction changes during one rotation of the drive scroll and the driven scroll is defined as the variation range, so that when the support is viewed from the direction of the drive axis, the notch is positioned to avoid the variation range.

2. The double-rotating scroll compressor according to claim 1, wherein, when viewed from the direction of the drive axis, the notch is positioned on the opposite side of the point of action with respect to the range of variation.

3. The double-rotation scroll compressor according to claim 1 or 2, wherein the support is provided with bumps formed from an elastically deformable metal plate and projecting in the radial direction.

4. The state in which the resultant force of the inertial force and compressive load transmitted to the protruding body is less than or equal to a set value is defined as the first state, and the state in which the resultant force of the inertial force and compressive load transmitted to the protruding body is greater than the set value is defined as the second state, and the bump has a main bump that contacts the protruding body and the holding part in the first state and the second state, and a sub-bump that contacts only one of the protruding body and the holding part in the first state, and contacts both the protruding body and the holding part in the second state, as described in claim 3. A double-rotation scroll compressor.

5. The state in which the resultant force of the inertial force and compressive load due to vibration transmitted to the protruding body is less than or equal to a set value is defined as the first state, and the state in which the resultant force of the inertial force and compressive load transmitted to the protruding body is greater than the set value is defined as the second state, and the bump comprises a first bump, a second bump disposed at a distance from the first bump in the circumferential direction of the protruding body, and a third bump disposed between the first bump and the second bump in the circumferential direction of the protruding body and connected to the first bump and the second bump, wherein the first bump contacts only the holding portion in the first and second states, the second bump contacts only the protruding body in the first and second states, and the third bump is not in contact with the holding portion and the protruding body in the first state, but is in contact with both the holding portion and the protruding body in the second state, as described in claim 3.

6. The dual-rotation scroll compressor according to claim 1 or 2, wherein the support has a first elastic portion set to a first spring constant and a second elastic portion set to a second spring constant higher than the first spring constant, and when the support is viewed from the direction of the drive axis, the second elastic portion is positioned at least in a position that overlaps with the fluctuation range.

7. The stator is fixed to the protruding body by a fixing member, and the fixing member is positioned to overlap with the notch in the radial direction, according to claim 1 or 2.

8. The double-rotation scroll compressor according to claim 1 or 2, wherein the support is disposed in the notch and has a positioning portion for positioning at least one of the protruding body and the holding portion relative to the support.

Images