Electric compressor

Abstract

The present invention provides an electric compressor that can effectively prevent inverter damage due to heat and can also reduce manufacturing costs. [Solution] The electric compressor of the present invention comprises a housing 6, a compression mechanism 2, an electric motor 10, and an inverter 3. A housing chamber 65 is formed inside the housing 6. The electric motor 10 has a stator 17 and a rotor 11. The inverter 3 is fixed to the housing 6 and is located outside the housing chamber 65. The housing has a partition wall 61 and a support 64. The support 64 is located inside the housing chamber 65. The support 64 supports the stator 17. The support 64 is formed separately from the partition wall 61 and is supported by the partition wall 61.

Description

Technical Field

[0007] ,

[0001] The present invention relates to an electric compressor.

Background Art

[0002] Patent Document 1 discloses a conventional electric compressor. This electric compressor includes a housing, a compression mechanism, and an electric motor. Inside the housing, a housing chamber is formed into which fluid is inhaled from the outside of the housing, and the compression mechanism and the electric motor are accommodated.

[0003] Further, a support is integrally provided on the housing. The support is located inside the housing chamber and extends axially toward the compression mechanism. A discharge passage is formed inside the support. The discharge passage communicates with the outside of the housing.

[0004] The compression mechanism has a driving scroll and a driven scroll. The driving scroll and the driven scroll form a compression chamber for compressing fluid. The compression chamber communicates with the discharge passage. Further, the driving scroll has a cover body. The driving scroll is rotatably supported by the support via the cover body.

[0005] The electric motor has a stator and a rotor. The stator is fixed to the housing. The rotor is disposed inside the stator and is rotationally driven by the stator. The rotor is fixed to the cover body.

[0006] In this electric compressor, when the electric motor is rotationally driven, the compression mechanism is operated. Thereby, in the compression mechanism, fluid is compressed in the compression chamber. Then, the fluid compressed in the compression chamber is discharged to the outside of the housing by flowing through the discharge passage.

Prior Art Documents

Patent Documents

[0007]

Patent Document 1

[0008] In this type of electric compressor, an inverter is provided to control the operation of the electric motor. The inverter is typically fixed to the housing and located outside the chamber.

[0009] In the conventional electric compressor described above, the support body is integrally formed with the housing, and the rotor is fixed to the cover body supported by this support body. Therefore, the heat from the rotor, which becomes hot during operation, is transferred from the cover body to the support body, and then this heat is transferred from the support body to the housing. In addition, the heat from the stator, which is fixed to the housing, is also transferred to the housing. As a result, the housing of this electric compressor tends to become hot during operation. Therefore, if an inverter is fixed to the housing of this electric compressor, the inverter is susceptible to the effects of the high temperature of the housing and is prone to thermal damage.

[0010] Therefore, it is conceivable to use heat-resistant components in the inverter, but in this case, the manufacturing cost of the inverter, and consequently the electric compressor, would skyrocket.

[0011] This invention has been made in view of the above-mentioned conventional circumstances, and aims to solve the problem of providing an electric compressor that can suitably prevent damage to the inverter due to heat and can also reduce manufacturing costs. [Means for solving the problem]

[0012] The electric compressor of the present invention comprises a housing, a compression mechanism for compressing a fluid, an electric motor for operating the compression mechanism, and an inverter for controlling the operation of the electric motor. Inside the housing, a chamber is formed into which fluid is drawn in from outside the housing, and which houses the compression mechanism and the electric motor. The electric motor comprises a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator. The inverter is an electric compressor fixed to the housing and located outside the housing chamber, The housing has a partition wall separating the housing chamber from the outside of the housing chamber, and a support located inside the housing chamber that supports the stator. The support is characterized in that it is formed separately from the partition wall and is supported by the partition wall.

[0013] In the electric compressor of the present invention, the inverter is fixed to the housing and located outside the housing chamber. The housing also has a partition wall and a support, which is located inside the housing chamber. The stator is supported by the support. Therefore, heat from the stator during operation is inevitably transferred to the support.

[0014] In this electric compressor, the support structure is formed separately from the partition wall and is supported by the partition wall. As a result, even if the support structure becomes hot, heat from the support structure is less likely to be transferred to the partition wall compared to a case where the support structure is formed integrally with the partition wall. Consequently, in this electric compressor, heat from the support structure is less likely to be transferred to the inverter located outside the housing chamber.

[0015] Furthermore, because heat from the support is not easily transferred to the inverter in this way, this electric compressor does not require the use of excessively heat-resistant components in the inverter.

[0016] Therefore, the electric compressor of the present invention can effectively prevent damage to the inverter due to heat, and can also achieve lower manufacturing costs.

[0017] The thermal conductivity of the support is preferably lower than that of the partition wall. In this case, the heat from the stator during operation is less likely to be transferred to the support, and as a result, the support is less likely to become hot.

[0018] Preferably, a fluid passage is formed inside the support, through which the fluid in the containment chamber can flow. This allows the support to be effectively cooled by the fluid flowing through the fluid passage.

[0019] Furthermore, in this case, it is preferable that the fluid is drawn into the compression mechanism through the fluid passage. This allows the fluid to flow suitably through the fluid passage toward the compression mechanism, thereby more effectively cooling the support structure. As a result, this compressor can more effectively suppress heat transfer to the inverter through the support wall.

[0020] The support can be supported by the partition wall via an insulating material that suppresses heat transfer from the support to the partition wall. Preferably, the insulating material has lower rigidity than the housing. In this case, the insulating material not only makes it difficult for heat from the support to be transferred to the partition wall, but also effectively suppresses the transmission of vibrations from the support to the partition wall.

[0021] The stator can be supported by a support via an insulating member that suppresses heat transfer from the stator to the support. Preferably, the insulating member has lower rigidity than the housing. In this case, the insulating member not only makes it difficult for heat from the stator to be transferred to the support, but also effectively suppresses the transmission of vibrations from the electric motor to the support and, consequently, to the housing.

[0022] The housing may have a housing body. The housing body may be formed in a bottomed cylindrical shape having a bottom wall extending radially from the housing and a circumferential wall that is connected to the bottom wall and extends cylindrically from the bottom wall in the axial direction of the housing. Preferably, the partition wall is fixed to the circumferential wall on the side opposite to the bottom wall in the axial direction.

[0023] In this case, by fixing the partition wall to the peripheral wall, a housing chamber can be suitably formed within the housing body.

[0024] The compression mechanism may include a driving scroll, a driven scroll, and a driven mechanism. The driving scroll can be rotationally driven around a driving axis by an electric motor. The driven scroll can be rotationally driven by the driving scroll and the driven mechanism around a driven axis while being eccentric with respect to the driving scroll. And it is preferable that the driving scroll and the driven scroll form a compression chamber for compressing fluid by rotational driving and rotational following.

[0025] In this case, while suppressing the complication of the configuration of the compression mechanism, the compression mechanism can suitably compress the fluid.

[0026] The partition wall may have a first surface facing the inside of the housing chamber and a second surface located on the opposite side of the first surface and facing the outside of the housing. And it is preferable that the inverter is fixed to the second surface.

[0027] In this case, the inverter can be suitably fixed to the partition wall. Also, in this electric compressor, since the heat of the support hardly transfers to the partition wall as described above, even if the inverter is fixed to the second surface of the partition wall, the heat of the support hardly transfers to this inverter.

Advantages of the Invention

[0028] The electric compressor of the present invention can suitably prevent damage to the inverter due to heat and can achieve a reduction in manufacturing cost.

Brief Description of the Drawings

[0029] [Figure 1] FIG. 1 is a cross-sectional view of the electric compressor of Example 1. [Figure 2] FIG. 2 is a cross-sectional view of the electric compressor of Example 2.

Modes for Carrying Out the Invention

[0030] Examples 1 and 2, which embody the present invention, will be described below with reference to the drawings. The electric compressors of Examples 1 and 2 are mounted on a vehicle (not shown) and constitute the vehicle's air conditioning system.

[0031] (Example 1) As shown in Figure 1, the electric compressor of Embodiment 1 comprises a housing 6, an electric motor 10, a compression mechanism 2, and an inverter 3.

[0032] In this embodiment, the front-rear direction of the electric compressor is defined by the solid arrow shown in Figure 1. Similarly, the front-rear direction of the electric compressor in Embodiment 2 is defined by the solid arrow shown in Figure 2. This front-rear direction is an example of the "axial direction" in the present invention. Note that this front-rear direction is just an example for the sake of explanation, and the electric compressor can appropriately change its own orientation depending on the vehicle on which it is mounted.

[0033] As shown in Figure 1, the housing 6 is composed of a housing body 60, a support 64, a partition wall 61, and an inverter cover 62.

[0034] The housing body 60 is made of aluminum alloy. The housing body 60 has a first outer peripheral wall 60a and a first bottom wall 60b. The first outer peripheral wall 60a is an example of a "peripheral wall" in the present invention, and the first bottom wall 60b is an example of a "bottom wall" in the present invention. The first outer peripheral wall 60a is cylindrical in shape with the drive axis O1 as the center. The drive axis O1 is parallel to the front-rear direction.

[0035] An intake port 71 is formed in the first outer peripheral wall 60a. The intake port 71 extends radially from the housing body 60. The intake port 71 is connected to an evaporator (not shown) through piping (not shown).

[0036] The first bottom wall 60b is located at the front end of the housing body 60. The first bottom wall 60b extends in a substantially circular, flat shape perpendicular to the drive axis O1. The outer edge of the first bottom wall 60b is connected to the front end of the first outer wall 60a. These first outer wall 60a and first bottom wall 60b give the housing body 60 a bottomed cylindrical shape with an opening at the rear.

[0037] The first bottom wall 60b has a front surface 601 facing forward and a rear surface 602 located opposite the front surface 601 and facing rear. A first support portion 66 and a discharge port 72 are formed in the first bottom wall 60b. The first support portion 66 is integrally formed approximately in the center of the rear surface 602 and protrudes rearward from the rear surface 602. The first support portion 66 is formed in a cylindrical shape centered on the drive shaft O1 and is provided with a radial ball bearing 52 and a shaft sealing member 63 inside. A sliding bearing may be provided inside the first support portion 66 instead of the radial ball bearing 52.

[0038] The shaft seal member 63 is positioned inside the first support portion 66, forward of the radial ball bearing 52. The shaft seal member 63 is formed in an annular shape.

[0039] The discharge port 72 penetrates the first bottom wall 60b in the direction of the drive shaft center O1 and communicates with the inside of the first support portion 66. The discharge port 72 is also connected to a condenser (not shown) through piping (not shown).

[0040] The bulkhead 61 is made of aluminum alloy. The bulkhead 61 is formed separately from the housing body 60 and is located behind the housing body 60. The bulkhead 61 has a substantially disc shape centered on the drive shaft center O1. Furthermore, the bulkhead 61 is formed to have substantially the same diameter as the first outer peripheral wall 60a of the housing body 60.

[0041] The partition wall 61 has a first surface 61a facing forward and a second surface 61b located opposite the first surface 61a and facing rear. A mounting recess 61c is also formed in the partition wall 61. The mounting recess 61c is recessed in a substantially cylindrical shape extending rearward from the first surface 61a. Here, the mounting recess 61c is formed with a larger diameter than the first diameter portion 64a of the support 64, which will be described later.

[0042] Furthermore, a first heat insulating body 91 is provided within the mounting recess 61c. The first heat insulating body 91 is an example of a "heat insulating body" in the present invention. The first heat insulating body 91 is made of a resin such as synthetic rubber that has heat insulating properties and elasticity. The first heat insulating body 91 is formed in the shape of a bottomed cylinder with an open front.

[0043] The support 64 is formed separately from the housing body 60 and the partition wall 61. The support 64 is made of steel. The support 64 has a first diameter portion 64a and a second diameter portion 64b. These first diameter portion 64a and second diameter portion 64b are formed integrally. The support 64 may also be made of an aluminum alloy.

[0044] The first diameter portion 64a is located behind the second diameter portion 64b and constitutes the rear part of the support 64. The first diameter portion 64a has a bottomed cylindrical shape due to the formation of a second fluid passage 642, which will be described later, inside it. A second heat insulating body 92 is also provided in the first diameter portion 64a. The second heat insulating body 92 is an example of a "heat insulating member" in the present invention. Similar to the first heat insulating body 91, the second heat insulating body 92 is also made of a resin such as synthetic rubber that has heat insulating properties and elasticity. The second heat insulating body 92 is formed in a cylindrical shape that extends in the direction of the drive shaft center O1 and is attached to the outer circumferential surface of the first diameter portion 64a. Note that the first heat insulating body 91 and the second heat insulating body 92 may be made of different materials.

[0045] The second diameter portion 64b is formed in a substantially cylindrical shape, extending forward from the front end of the first diameter portion 64a in the direction of the drive axis O1. As a result, the second diameter portion 64b constitutes the front part of the support 64. Furthermore, the second diameter portion 64b is formed to have a smaller diameter than the first diameter portion 64a.

[0046] A pin hole 55a is formed in the second diameter portion 64b. The pin hole 55a opens to the front end face of the second diameter portion 64b and extends rearward in the direction of the drive axis O1 within the interior of the second diameter portion 64b. Here, the pin hole 55a does not penetrate the second diameter portion 64b in the direction of the drive axis O. For this reason, the pin hole 55a does not communicate with the second fluid passage 642, which will be described later. However, the pin hole 55a may communicate with the second fluid passage 642 by penetrating the second diameter portion 64b in the direction of the drive axis O.

[0047] Furthermore, a fluid passage 64c is formed in the support 64. The fluid passage 64c is composed of a first fluid passage 641, a second fluid passage 642, and a third fluid passage 643. The first fluid passage 641 extends radially from the first diameter portion 64a of the support 64. One end of the first fluid passage 641 opens to the outer circumferential surface of the first diameter portion 64a.

[0048] The second fluid passage 642 is formed in the first diameter portion 64a. The second fluid passage 642 is recessed from the rear end of the first diameter portion 64a toward the front. As a result, the second fluid passage 642 communicates with the other end of the first fluid passage 641.

[0049] The third fluid passage 643 is formed in the first diameter portion 64a. The third fluid passage 643 extends from the first diameter portion 64a in the direction of the drive axis O. As a result, the front end of the third fluid passage 643 is on the outer circumference side of the second diameter portion 64b and opens to the front end surface of the first diameter portion 64a, and the rear end communicates with the second fluid passage 642. In this way, the first fluid passage 641 and the third fluid passage 643 are in communication through the second fluid passage 642.

[0050] The support 64 has its rear portion of the first diameter 64a inserted into the interior of the first insulator 91, and consequently into the mounting recess 61c. In this state, the support 64 is fastened from the second surface 61b side of the partition wall 61 by bolts (not shown). Thus, the support 64 is supported by the partition wall 61 via the first insulator 91. Furthermore, with the support 64 supported by the partition wall 61 in this manner, the rear end of the second fluid passage 642 in the support 64 is closed by the first insulator 91 and the partition wall 61.

[0051] The inverter cover 62 is made of aluminum alloy. The inverter cover 62 has a second outer peripheral wall 62a and a second bottom wall 62b. The second outer peripheral wall 62a is cylindrical with the drive shaft center O1 as the center. The second outer peripheral wall 62a is formed to be approximately the same diameter as the first outer peripheral wall 60a and the partition wall 61.

[0052] The second bottom wall 62b is located at the rear end of the inverter cover 62. The second bottom wall 62b extends in a substantially circular, flat shape perpendicular to the drive shaft center O1. The outer edge of the second bottom wall 62b is connected to the rear end of the second outer wall 62a. These second outer wall 62a and second bottom wall 62b give the inverter cover 62 a bottomed cylindrical shape with an open front. Although not shown in the figures, a connector portion is also formed on the inverter cover 62.

[0053] In the housing 6, the first surface 61a of the partition wall 61 is in contact with the rear end of the first outer peripheral wall 60a. Also, the front end of the second outer peripheral wall 62a is in contact with the second surface 61b of the partition wall 61. In this state, the housing body 60, the partition wall 61, and the inverter cover 62 are fixed together in the direction of the drive axis O1 by multiple bolts (not shown) from the inverter cover 62 side. In this way, the housing body 60, the partition wall 61, and the inverter cover 62 are integrated into one unit in the housing 6.

[0054] Furthermore, in the housing 6, the rear of the housing body 60 is closed by a partition wall 61, thereby forming a scroll chamber 65 within the housing body 60. The scroll chamber 65 is an example of a "container chamber" in the present invention. The scroll chamber 65 is in communication with an intake port 71. As a result, refrigerant is drawn into the scroll chamber 65 from outside the housing 6 through the intake port 71. The refrigerant is an example of a "fluid" in the present invention.

[0055] Furthermore, in the housing 6, the front of the inverter cover 62 is closed off by a partition wall 61, thereby forming an inverter chamber 620 inside the inverter cover 62. The inverter chamber 620 is located outside the scroll chamber 65. The inverter chamber 620 and the scroll chamber 65 are separated by the partition wall 61.

[0056] Furthermore, the support 64 is located within the scroll chamber 65 by being supported by the partition wall 61. The support 64 protrudes forward from the partition wall 61 toward the compression mechanism 2. In addition, the first fluid passage 641 of the fluid passage 64c of the support 64 faces into the scroll chamber 65. As a result, the fluid passage 64c is in communication with the scroll chamber 65.

[0057] As mentioned above, the support 64 is made of steel, and the partition wall 61 is made of aluminum alloy. Therefore, the thermal conductivity of the support 64 is lower than that of the partition wall 61.

[0058] Furthermore, the housing 6 is composed of a housing body 60, a support 64, a partition wall 61, and an inverter cover 62. The housing body 60, partition wall 61, and inverter cover 62 are made of aluminum alloy, while the support 64 is made of steel. On the other hand, the first insulator 91 and the second insulator 92 are both made of synthetic rubber. For this reason, the first insulator 91 and the second insulator 92, including the support 64, have lower rigidity than the housing 6.

[0059] The electric motor 10 is housed in a scroll chamber 65. The electric motor 10 consists 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. The windings 17b are wound around the stator core 17a. As a result, the windings 17b form a first coil end 171 and a second coil end 172.

[0060] In the stator 17, the second insulator 92 is inserted into the interior of the stator core 17a and supported on the outer circumferential surface of the first diameter portion 64a. In this way, the stator core 17a, and by extension the stator 17, is supported on the support 64 via the second insulator 92. Although not shown in the figures, multiple slits extending in the direction of the drive axis O1 are formed on the inner circumferential surface of the stator core 17a. As a result, the slits form gaps between themselves and the second insulator 92.

[0061] The rotor 11 is cylindrical around the drive axis O1. Although detailed illustrations are omitted, the rotor 11 is composed of multiple permanent magnets corresponding to the stator 17 and laminated steel plates that fix each permanent magnet. The rotor 11 is also formed to be larger in diameter than the stator core 17a. As a result, the rotor 11 covers the stator core 17a from the outside within the scroll chamber 65. Furthermore, the rotor 11 has multiple first bolt holes 11a. Each first bolt hole 11a penetrates the rotor 11 in the direction of the drive axis O1.

[0062] The compression mechanism 2 is housed within the scroll chamber 65. The compression mechanism 2 includes a drive scroll 30, a driven scroll 40, and a driven mechanism 20.

[0063] 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 first cover body 37, and a first case 39.

[0064] 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.

[0065] 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.

[0066] The drive spiral body 33 is integral with the drive end plate 31 and protrudes from the first rear surface 312 toward the rear, i.e., toward the driven scroll 40, parallel to the drive axis O1 and the driven axis O2. Although detailed illustration is omitted, the drive spiral body 33 has the center of the drive end plate 31 as its spiral center and protrudes outward from the spiral center.

[0067] The drive circumferential wall 35 is formed in a cylindrical shape, extending parallel to the drive axis O1 and the driven axis O2, with the drive axis O1 as its center. The front end of the drive circumferential wall 35 is integral with the outer peripheral edge of the drive end plate 31. As a result, the drive circumferential wall 35 surrounds the drive vortex body 33 from the outside and protrudes cylindrically toward the rear from the first rear surface 312. Although not shown in the figures, the outer peripheral end of the vortex in the drive vortex body 33 is connected to the inner peripheral surface of the drive circumferential wall 35.

[0068] The first cover body 37 has a wall portion 37a, an inner cylindrical portion 37b, and an outer cylindrical portion 37c. The wall portion 37a extends in a substantially plate-like shape in the radial direction of the drive scroll 30. 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.

[0069] Furthermore, 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 toward the rear from the second front surface 371.

[0070] The intake port 374 is located radially outward from the recess 373 of the drive scroll 30. The intake port 374 penetrates the wall portion 37a in the direction of the drive axis O. As a result, the front end of the intake port 374 opens to the second front surface 371, and the rear end opens to the second rear surface 372. In this electric compressor, the intake port 374 is formed only in the wall portion 37a. Furthermore, there is only one intake port 374 formed in the wall portion 37a. Note that multiple intake ports 374 may be formed in the wall portion 37a.

[0071] Furthermore, in the wall portion 37a, multiple rings 22 are attached to the area between the recess 373 and the intake port 374. Although detailed illustration is 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. Figure 1 shows one of the six rings 22.

[0072] The inner cylindrical portion 37b is located in the radial direction of the drive scroll 30, inside the stator 17, and extends cylindrically backward in the direction of the drive axis O1 from the second rear surface 372 of the wall portion 37a. The inner cylindrical portion 37b is formed to have a larger diameter than the second diameter portion 64b of the support 64, and a smaller diameter than the first diameter portion 64a.

[0073] Furthermore, the first cover body 37 has an insertion hole 375. The insertion hole 375 is formed to be approximately the same diameter as the second diameter portion 64b of the support body 64 and constitutes the inner circumferential surface of the inner cylindrical portion 37b. The insertion hole 375 extends in the direction of the drive axis O1 and communicates with the recess 373.

[0074] Furthermore, a first sliding bearing 51 is provided in the through hole 375. Alternatively, instead of the first sliding bearing 51, a coating layer or plating layer that provides sliding properties may be provided on the inner circumferential surface of the through hole 375 or on the outer circumferential surface of the second diameter portion 64b of the support 64. Alternatively, a radial ball bearing may be provided in the through hole 375 instead of the first sliding bearing 51.

[0075] The outer cylindrical portion 37c is integral with the wall portion 37a at its outer peripheral edge. As a result, the outer cylindrical portion 37c is connected to the wall portion 37a and extends cylindrically backward from the wall portion 37a in the direction of the drive axis O1. The outer diameter of the outer cylindrical portion 37c is formed to be approximately the same as the outer diameter of the drive peripheral wall 35 and the outer diameter of the rotor 11.

[0076] Furthermore, the inner diameter of the outer cylindrical portion 37c is formed to be larger than that of the inner cylindrical portion 37b. As a result, in the first cover body 37, the inner cylindrical portion 37b is positioned on the inner circumference side of the outer cylindrical portion 37c, separated from the outer cylindrical portion 37c in the radial direction of the drive scroll 30. In this way, the coil end housing portion 38 is formed in the first cover body 37 by the wall portion 37a, the inner cylindrical portion 37b, and the outer cylindrical portion 37c. The coil end housing portion 38 has a bottomed annular shape that opens at the rear.

[0077] The intake port 374 formed in the wall portion 37a is located in the radial direction of the drive scroll 30, outside the inner cylindrical portion 37b and inside the outer cylindrical portion 37c. Thus, the intake port 374 communicates with the coil end housing portion 38 at a point between the inner cylindrical portion 37b and the outer cylindrical portion 37c.

[0078] Furthermore, the first cover body 37 has a plurality of second bolt holes 376 formed therein. Each second bolt hole 376 penetrates the wall portion 37a in the direction of the drive axis O1. Although not shown in the figure, the number of second bolt holes 376 is equal to the number of first bolt holes 11a formed in the rotor 11. In Figure 1, one of the plurality of first bolt holes 11a and one of the second bolt holes 376 are shown.

[0079] The first cover body 37 has its front end of the outer cylindrical portion 37c in contact with the rear end of the drive peripheral wall 35. The rotor 11 is also in contact with the rear end of the outer cylindrical portion 37c of the first cover body 37. In this state, the first bolts 34a are inserted from the rotor 11 side through the first bolt holes 11a and the second bolt holes 376 in that order, and the first bolts 34a are screwed into the drive peripheral wall 35. In this way, the first cover body 37 is fixed to the drive peripheral wall 35 and the rotor 11, while being sandwiched in the front-rear direction between the drive peripheral wall 35 and the rotor 11. As a result, the drive scroll 30 is integrated with the rotor 11.

[0080] The first case 39 has 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.

[0081] The front wall 39b is located at the front end of the first case 39. The front wall 39b extends in a substantially disc shape perpendicular to the drive axis O1 and the driven axis O2. The outer edge of the front wall 39b is connected to the front end of the outer wall 39a. These outer wall 39a and front wall 39b give the first case 39 a bottomed cylindrical shape with an opening at the rear.

[0082] Furthermore, a first boss 39c is formed on the front wall 39b. The first boss 39c is integrally formed in the center of the front wall 39b and protrudes forward from the front wall 39b in the direction of the drive axis O1. The outer diameter of the first boss 39c is formed to be approximately the same as the inner diameter of the radial ball bearing 52 and the inner diameter of the shaft sealing member 63. In addition, a discharge passage 390 is formed on the first boss 39c. The discharge passage 390 penetrates the first boss 39c in the direction of the drive axis O1.

[0083] Furthermore, a third bolt hole 39d is formed in the first case 39. The third bolt hole 39d penetrates the outer periphery wall 39a and the front wall 39b in the direction of the drive axis O1. Although not shown in the figure, multiple third bolt holes 39d are formed in the outer periphery wall 39a and the front wall 39b. Figure 1 shows one of these multiple third bolt holes 39d.

[0084] The first case 39 has its rear end of the outer peripheral wall 39a in contact with the front end of the drive peripheral wall 35. In this state, the second bolts 34b are inserted through each of the third bolt holes 39d, and the second bolts 34b are screwed into the drive peripheral wall 35. In this way, the first case 39 is fixed to the drive peripheral wall 35 in the drive scroll 30.

[0085] Then, by fixing the first case 39 to the drive peripheral wall 35, a discharge chamber 14 is formed inside the first case 39. The discharge chamber 14 is in communication with the discharge port 32 and also with the discharge passage 390.

[0086] The driven scroll 40 is also made of aluminum alloy. The driven scroll 40 has a driven end plate 41 and a driven spiral body 43.

[0087] 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.

[0088] 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 second diameter portion 64b of the support 64.

[0089] A driven shaft portion 16 is 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 a second sliding bearing 13.

[0090] 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. As a result, the driven pin 55 protrudes rearward from the bush 53, and consequently from the driven end plate 41.

[0091] 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. Figure 1 illustrates one of the six pivot pins 21.

[0092] 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.

[0093] The driven spiral body 43 is integral with the driven end plate 41 and extends forward from the third front surface 411 of the driven end plate 41 parallel to the drive axis O1 and the driven axis O2. The driven spiral body 43 has the center of the driven end plate 41 as its spiral center and extends outward from the spiral center.

[0094] In this electric 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 first cover body 37. The drive spiral body 33 and the driven spiral body 43 are then meshed together. As a result, the drive spiral body 33 and the driven spiral body 43 face each other to form a compression chamber 12.

[0095] Furthermore, a suction section 30a is formed between the drive peripheral wall 35 and the driven scroll 40. In other words, the drive spiral body 33 and the driven spiral body 43 are located within the suction section 30a. The suction section 30a is separated from the scroll chamber 65 by the drive peripheral wall 35 and the first cover body 37, and is also separated from the discharge chamber 14 by the drive end plate 31. The suction section 30a is also in communication with the suction port 374.

[0096] Furthermore, by housing the driven scroll 40 within the driven scroll 30, each orbital pin 21 enters each ring 22. In this way, the driven scroll 30 and the driven scroll 40 are assembled in the front-rear direction, and the driven scroll 30 and the driven scroll 40 constitute the scroll compression section 100. More precisely, after the driven spiral body 33 and the driven spiral body 43 are meshed and each orbital pin 21 enters each ring 22, the first cover body 37 of the driven scroll 30 is fixed to the drive peripheral wall 35 and the rotor 11.

[0097] Furthermore, when the drive scroll 30 and the driven scroll 40 are assembled, the housing recess 15 of the driven end plate 41 and the driven shaft portion 16 face the recess 373 of the first cover body 37. As a result, the bush passage 53a communicates with the recess 373 at its rear end. The recess 373 can then communicate with the suction portion 30a through the gap between the driven end plate 41 and the first cover body 37, and through the gaps between each swivel pin 21 and each ring 22.

[0098] The drive scroll 30 is positioned in front of the stator 17 within the scroll chamber 65. In the drive scroll 30, the inner cylindrical portion 37b of the first cover body 37 is inserted into the inner circumference of the first coil end 171. In this state, the second diameter portion 64b of the support body 64 is inserted into the insertion hole 375, thereby inserting the second diameter portion 64b into the first sliding bearing 51. In this way, the first cover body 37 is rotatably supported on the second diameter portion 64b via the first sliding bearing 51. The coil end housing portion 38 is in communication with the scroll chamber 65.

[0099] Furthermore, since the first cover body 37 is rotatably supported on the second diameter portion 64b, the first coil end 171 is housed within the coil end housing portion 38. As a result, within the coil end housing portion 38, the first coil end 171 is covered from the front by the wall portion 37a and covered from the radially inner side of the drive scroll 30 by the inner cylindrical portion 37b. The first coil end 171 is also covered from the radially outer side of the drive scroll 30 by the outer cylindrical portion 37c within the coil end housing portion 38.

[0100] Furthermore, as described above, the first cover body 37 is rotatably supported on the second diameter portion 64b via the first sliding bearing 51, so that the third fluid passage 643 faces the coil end housing portion 38 in the direction of the drive axis O at a point radially inward of the drive scroll 30 from the first coil end 171. As a result, in this electric compressor, the coil end housing portion 38 and the scroll chamber 65 are also in communication via the fluid passage 64c.

[0101] Furthermore, in the drive scroll 30, the first boss 39c of the first case 39 is inserted through the radial ball bearing 52 and the shaft sealing member 63. As a result, the first case 39 is rotatably supported by the first support portion 66 via the radial ball bearing 52. Thus, the drive scroll 30 is positioned within the scroll chamber 65 and is rotatably supported by both the support body 64 and the first support portion 66 in the housing 6 around the drive axis O1.

[0102] 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 55a. As a result, the driven scroll 40 is positioned within the scroll chamber 65 and is rotatably supported around the driven axis O2 with respect to the second diameter portion 64b of the support 64. In other words, unlike the drive scroll 30, the driven scroll 40 is rotatably supported around the driven axis O2 in the housing 6 by the support 64 alone.

[0103] The inverter 3 consists of a circuit board 3a and switching elements 3b provided on the circuit board 3a. The inverter 3 is fixed to the second surface 61b of the bulkhead 61 by bolts (not shown) on the circuit board 3a. As a result, the inverter 3 is housed in the inverter chamber 620. In other words, the inverter 3 is located outside the scroll chamber 65. The inverter 3 is electrically connected to the vehicle's battery (not shown) through a connector provided on the inverter cover 62. The inverter 3 is also electrically connected to the stator 17 through an airtight passage (not shown) provided in the bulkhead 61. As a result, the inverter 3 converts the DC current supplied from the battery into AC current and supplies power to the stator 17.

[0104] In this electric compressor configured as described above, as shown by the dashed arrow in Figure 1, low-temperature, low-pressure refrigerant that has passed through the evaporator is drawn into the scroll chamber 65 from the intake port 71. The inverter 3 supplies power to the stator 17 and controls the operation of the electric motor 10, causing the rotor 11 to rotate. This rotation of the rotor 11 is transmitted to the drive scroll 30, causing the drive scroll 30 to rotate around the drive axis O1 in the compression mechanism 2. In other words, the drive scroll 30 and the rotor 11 rotate together. At this time, in the driven mechanism 20, each orbital pin 21 slides against the inner 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.

[0105] As a result, in the compression mechanism 2, the driven scroll 40 is rotated by the drive scroll 30 and the driven mechanism 20 around the driven axis O2. At this time, the driven mechanism 20 restricts the driven scroll 40 from rotating relative to the drive scroll 30. This causes the driven scroll 40 to revolve relative to the drive scroll 30 around the driven axis O2. Then, as the drive volute body 33 and the driven volute body 43 rotate within the intake section 30a, the drive volute body 33 and the driven volute body 43 change the volume of the compression chamber 12.

[0106] The refrigerant drawn into the scroll chamber 65 flows between the rotor 11 and the stator 17 to the coil end housing 38, and is drawn into the compression chamber 12 through the intake port 374 and the intake section 30a. Alternatively, the refrigerant drawn into the scroll chamber 65 can also reach the coil end housing 38 by flowing through slits formed in the stator core 17a, and is drawn into the compression chamber 12 through the intake port 374 and the intake section 30a.

[0107] Furthermore, in this electric compressor, a portion of the refrigerant drawn into the scroll chamber 65 also reaches the coil end housing 38 by flowing through the first fluid passage 641, the second fluid passage 642, and the third fluid passage 643. Therefore, in this electric compressor, the refrigerant in the scroll chamber 65 is also drawn into the compression chamber 12 by flowing in the order of fluid passage 64c, coil end housing 38, suction port 374, and suction section 30a. In other words, in this electric compressor, the refrigerant in the scroll chamber 65 is also drawn into the compression chamber 12, and consequently into the compression mechanism 2, via fluid passage 64c. Here, the refrigerant drawn into the scroll chamber 65 contains lubricating oil. Therefore, the lubricating oil contained in the refrigerant is also drawn into the compression chamber 12 along with the refrigerant.

[0108] 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. At this time, along with the high-pressure refrigerant, some of the lubricating oil in the compression chamber 12 is also discharged from the discharge port 32 into the discharge chamber 14.

[0109] Furthermore, since the drive scroll 30 rotates around the drive axis O1, the centrifugal force of the rotating drive scroll 30 acts on the refrigerant discharged into the discharge chamber 14. As a result, the lubricating oil contained in the refrigerant is separated from the refrigerant by centrifugal force. The refrigerant in the discharge chamber 14 is then discharged to the outside of the electric compressor through the discharge port 72 via the discharge passage 390.

[0110] In this electric compressor, the support 64 is located inside the scroll chamber 65, and the inverter 3 is located inside the inverter chamber 620, that is, outside the scroll chamber 65. Therefore, in this electric compressor, the inverter 3 is not fixed to the support 64.

[0111] Incidentally, when the electric motor 10 operates, the stator 17 and rotor 11 generate heat. The stator 17 is supported by the first diameter portion 64a of the support 64. Therefore, the heat from the stator 17 during operation is inevitably transferred to the support 64.

[0112] In this respect, in this electric compressor, the support 64 is formed separately from the partition wall 61 and is supported by the partition wall 61. As a result, in this electric compressor, even if the support 64 becomes hot due to the heat of the stator 17, the heat from the support 64 is less likely to be transferred to the partition wall 61 compared to when the support 64 is integrally formed with the partition wall 61. Consequently, in this electric compressor, the heat from the support 64 is less likely to be transferred to the inverter 3, which is fixed to the second surface 61b of the partition wall 61 and housed in the inverter chamber 620.

[0113] Furthermore, because heat from the support 64 is not easily transferred to the inverter 3 in this way, this electric compressor does not require the use of semiconductors or other materials with excessively high heat resistance in the inverter 3.

[0114] Therefore, the electric compressor of Example 1 can effectively prevent damage to the inverter 3 due to heat, and can also achieve lower manufacturing costs.

[0115] In particular, in this electric compressor, the support 64 is made of steel and has lower thermal conductivity than the aluminum alloy partition wall 61. The support 64 is supported by the partition wall 61 via the first insulator 91. Furthermore, the stator 17 is supported by the support 64 via the second insulator 92.

[0116] For these reasons, in this electric compressor, the second insulator 92 makes it difficult for heat from the stator 17 to be transferred to the support 64, thereby suppressing the heat generation of the support 64 as much as possible. In addition, the material of the support 64 itself and the first insulator 91 also make it difficult for heat from the support 64 to be transferred to the partition wall 61. In these respects as well, in this electric compressor, heat from the support 64 is difficult to transfer to the inverter 3.

[0117] Furthermore, the first insulator 91 and the second insulator 92 have lower rigidity and elasticity than the housing 6. Therefore, in this electric compressor, the first insulator 91 and the second insulator 92 absorb vibrations generated in the compression mechanism 2 and the electric motor 10 during operation, making it difficult for these vibrations to be transmitted to the support 64, and also making it difficult for these vibrations to be transmitted from the support 64 to the partition wall 61.

[0118] Furthermore, in this electric compressor, the rotor 11 covers the stator core 17a from the outside. In order to ensure the rotation of the rotor 11 within the scroll chamber 65, the first outer peripheral wall 60a of the housing body 60 and the rotor 11 are separated in the radial direction of the drive scroll 30. In other words, the first outer peripheral wall 60a and the rotor 11 are not in contact. Therefore, in this electric compressor, it is possible to effectively prevent heat from the rotor 11 from being transmitted to the inverter 3 through the housing body 60 and support 64.

[0119] Furthermore, in this electric compressor, a portion of the refrigerant can circulate inside the support 64 through a fluid passage 64c formed in the support 64. The refrigerant in the fluid passage 64c is then drawn into the compression chamber 12 by circulating in the order of the coil end housing 38, the suction port 374, and the suction port 30a. In this way, in this electric compressor, the refrigerant that has reached the fluid passage 64c from the scroll chamber 65 does not remain stagnant within the fluid passage 64c. As a result, this electric compressor is able to suitably cool the support 64 with the low-temperature refrigerant circulating through the fluid passage 64c toward the compression chamber 12. In this respect as well, in this electric compressor, heat from the support 64 is less likely to be transferred to the inverter 3.

[0120] Furthermore, in this electric compressor, the inverter 3 can be easily fixed to the housing 6 by fixing the circuit board 3a of the inverter 3 to the second surface 61b of the partition wall 61. Here, although the support 64 is supported on the opposite side of the circuit board 3a in the partition wall 61, as described above, in this electric compressor, heat from the support 64 is not easily transferred to the partition wall 61. Therefore, even if the circuit board 3a is fixed to the second surface 61b of the partition wall 61, heat from the support 64 is not easily transferred to the circuit board 3a, and consequently to the inverter 3.

[0121] Furthermore, in this electric compressor, the compression mechanism 2 includes a drive scroll 30, a driven scroll 40, and a driven mechanism 20. This makes it possible to suitably compress the refrigerant using the compression mechanism 2 while suppressing the complexity of the configuration of the compression mechanism 2.

[0122] (Example 2) As shown in Figure 2, the electric compressor of Embodiment 2 comprises a housing 6a, a compression mechanism 4, an electric motor 10, and an inverter 3.

[0123] The housing 6a is composed of a housing body 67, a partition wall 61, a shaft 68, and an inverter cover 62. The shaft 68 is an example of a "support" in the present invention.

[0124] The housing body 67 is made of aluminum alloy. The housing body 67 has a third outer peripheral wall 67a and a third bottom wall 67b. The third outer peripheral wall 67a is an example of a "peripheral wall" in the present invention, and the third bottom wall 67b is an example of a "bottom wall" in the present invention. The third outer peripheral wall 67a is cylindrical with a central axis X1 at its center. The central axis X1 is parallel to the front-rear direction.

[0125] An intake port 73 is formed in the third outer peripheral wall 67a. The intake port 73 extends radially from the housing body 67. Similar to the intake port 71 in the electric compressor of Embodiment 1, the intake port 73 is also connected to an evaporator (not shown) through piping (not shown).

[0126] The third bottom wall 67b is located at the front end of the housing body 67. The third bottom wall 67b extends in a substantially circular, flat shape perpendicular to the central axis X1. The outer edge of the third bottom wall 67b is connected to the front end of the third outer wall 67a. These third outer wall 67a and third bottom wall 67b give the housing body 67 a bottomed cylindrical shape with an opening at the rear.

[0127] The third bottom wall 67b has a front surface 671 facing forward and a rear surface 672 located opposite the front surface 671 and facing rear. The third bottom wall 67b also has a second support portion 69 and a discharge port 74 formed therein. The second support portion 69 is integrally formed approximately in the center of the rear surface 672 and protrudes rearward from the rear surface 672. The second support portion 69 is formed in a cylindrical shape with a central axis X1 as its center.

[0128] The discharge port 74 penetrates the third bottom wall 67b in the direction of the central axis X1 and communicates with the inside of the second support portion 69. Similar to the discharge port 72 in the electric compressor of Embodiment 1, the discharge port 74 is also connected to a condenser (not shown) through piping (not shown).

[0129] The shaft 68 is made of steel. The shaft 68 is formed separately from the housing body 67 and the partition wall 61. The shaft 68 has a main shaft portion 68a, a first eccentric shaft portion 68b, and a second eccentric shaft portion 68c. The main shaft portion 68a, the first eccentric shaft portion 68b, and the second eccentric shaft portion 68c are all cylindrical in shape with a circular cross-section perpendicular to the central axis X1. The shaft 68 may also be made of aluminum alloy.

[0130] The main shaft portion 68a has a first diameter portion 681, a second diameter portion 682, and a third diameter portion 683. These first diameter portion 681, second diameter portion 682, and third diameter portion 683 are formed integrally.

[0131] The first diameter portion 681 is located behind the second diameter portion 682 and constitutes the rear part of the shaft 68. The first diameter portion 681 has a bottomed cylindrical shape due to the formation of a second fluid passage 812, which will be described later, inside it. A second heat insulating body 92 is provided on the outer circumferential surface of the first diameter portion 681.

[0132] Furthermore, a fluid passage 68d is formed in the first diameter portion 681. The fluid passage 68d is composed of a first fluid passage 811, a second fluid passage 812, and a third fluid passage 813. The first fluid passage 811 extends radially along the shaft 68 from the first diameter portion 681. One end of the first fluid passage 811 opens onto the outer circumferential surface of the first diameter portion 681.

[0133] The second fluid passage 812 is recessed forward from the rear end of the first diameter portion 681. As a result, the second fluid passage 812 communicates with the other end of the first fluid passage 811. The third fluid passage 813 extends in the direction of the central axis X1. The front end of the third fluid passage 813 opens to the front end surface of the first diameter portion 681, and the rear end communicates with the second fluid passage 812. In this way, the first fluid passage 811 and the third fluid passage 813 communicate through the second fluid passage 812.

[0134] The second diameter portion 682 extends forward from the front end surface of the first diameter portion 681 in the direction of the central axis X1. The second diameter portion 682 is formed to be smaller in diameter than the first diameter portion 681. The third diameter portion 683 extends forward from the front end surface of the second diameter portion 682 in the direction of the central axis X1. Thus, the third diameter portion 683 constitutes the front part of the shaft 68. The third diameter portion 683 is formed to be smaller in diameter than the first diameter portion 681 and the second diameter portion 682.

[0135] The first eccentric shaft portion 68b and the second eccentric shaft portion 68c are each provided on the third diameter portion 683. More specifically, the first eccentric shaft portion 68b is positioned forward of the second eccentric shaft portion 68c. Here, the first eccentric shaft portion 68b and the second eccentric shaft portion 68c are separated by a distance in the direction of the central axis X1 that corresponds to the combined length of the first intermediate plate 152 and the second intermediate plate 162, which will be described later.

[0136] Both the first eccentric shaft portion 68b and the second eccentric shaft portion 68c have approximately the same outer diameter as the second diameter portion 682. The first eccentric axis Y1 of the first eccentric shaft portion 68b is eccentric with respect to the central axis X1. The second eccentric axis Y2 of the second eccentric shaft portion 68c is eccentric with respect to the central axis X1. Here, the amount of eccentricity of the first eccentric axis Y1 with respect to the central axis X1 is equal to the amount of eccentricity of the second eccentric axis Y2 with respect to the central axis X1. Furthermore, the first eccentric shaft portion 68b and the second eccentric shaft portion 68c are eccentric in opposite directions. As a result, for example, if the first eccentric shaft portion 68b is eccentric upward in the plane of Figure 2 with respect to the central axis X1, the second eccentric shaft portion 68c is eccentric downward in the plane of Figure 2, which is the opposite direction.

[0137] A cylindrical first roller 124 is positioned on the outer circumferential surface of the first eccentric shaft portion 68b. The first roller 124 is fitted to the outer circumferential surface of the first eccentric shaft portion 68b by clearance fitting. The first eccentric portion 126 is formed by the first eccentric shaft portion 68b and the first roller 124. The first eccentric portion 126 has a circular outer circumferential surface centered on the first eccentric axis Y1.

[0138] Meanwhile, a cylindrical second roller 125 is positioned on the outer circumferential surface of the second eccentric shaft portion 68c. The second roller 125 is fitted to the outer circumferential surface of the second eccentric shaft portion 68c by clearance fitting. The second eccentric portion 127 is formed by the second eccentric shaft portion 68c and the second roller 125. The second eccentric portion 127 has a circular outer circumferential surface centered on the second eccentric axis Y2.

[0139] Furthermore, a shaft discharge passage 175 is formed in the third diameter portion 683. One end of the shaft discharge passage 175 opens to the front end surface of the third diameter portion 683, that is, to the front end surface of the shaft 68, and the other end opens to the outer circumferential surface of the third diameter portion 683 at a point forward of the first eccentric shaft portion 68b.

[0140] The shaft 68 has its rear portion of the first diameter section 681 inserted into the interior of the first insulator 91, and consequently into the mounting recess 61c of the partition wall 61. In this state, the shaft 68 is fastened from the second surface 61b side of the partition wall 61 by bolts (not shown). Thus, the shaft 68 is supported by the partition wall 61 via the first insulator 91. Furthermore, because the shaft 68 is supported by the partition wall 61, the rear end of the second fluid passage 812 is closed off by the first insulator 91 and the partition wall 61.

[0141] Furthermore, the front portion of the third diameter section 683 of the shaft 68 is fitted into the second support section 69. In this way, the shaft 68 is also supported by the third bottom wall 67b and, consequently, by the housing body 67. As a result of the shaft 68 being supported by the third bottom wall 67b, the internal discharge passage 175 of the shaft is connected to the discharge port 74.

[0142] In the housing 6a, the first surface 61a of the partition wall 61 is in contact with the rear end of the third outer peripheral wall 67a. In this state, the housing body 67, the partition wall 61, and the inverter cover 62 are fixed together in the direction of the central axis X1 by multiple bolts (not shown) from the inverter cover 62 side. In this way, the housing body 67, the partition wall 61, and the inverter cover 62 are integrated into one unit in the housing 6a.

[0143] Furthermore, in housing 6a, the rear of the housing body 67 is closed off by a partition wall 61, thereby forming a storage chamber 18 inside the housing body 67. The storage chamber 18 is in communication with the intake port 73. As a result, refrigerant is drawn into the storage chamber 18 from outside the housing 6a through the intake port 73.

[0144] The shaft 68 is positioned within the housing chamber 18, supported by the bulkhead 61 and the housing body 67. The bulkhead 61 is located between the housing chamber 18 and the inverter chamber 620, thereby separating the two.

[0145] The electric motor 10 is located inside the housing chamber 18. The stator 17 is supported on the outer surface of the first diameter portion 681 with the second insulator 92 inserted inside the stator core 17a. In this way, the stator core 17a, and by extension the stator 17, is supported on the shaft 68 via the second insulator 92.

[0146] The compression mechanism 4 is housed in the containment chamber 18. The compression mechanism 4 includes a first cylinder 131, a second cylinder 132, a first vane 133, a second vane 134, a second case 135, and a second cover body 136.

[0147] The first cylinder 131 comprises a first cylinder body 151, a first intermediate plate 152, and a first side plate 153. The first cylinder body 151 is positioned on the outer circumference of the first eccentric portion 126 so as to cover it. The first cylinder body 151 is substantially cylindrical and has an inner circumferential surface 151a with a circular cross-section centered on the central axis X1. This inner circumferential surface 151a and the outer circumferential surface of the first eccentric portion 126 are in contact at one point in the circumferential direction. Thus, a first working chamber (not shown) is formed between the inner circumferential surface 151a of the first cylinder body 151 and the outer circumferential surface of the first eccentric portion 126.

[0148] The first cylinder body 151 has a first vane housing hole 155 formed therein. Although detailed illustration is omitted, the first vane housing hole 155 extends radially outward from the inner circumferential surface 151a of the first cylinder body 151 and opens onto the outer circumferential surface of the first cylinder body 151. Furthermore, the first vane housing hole 155 penetrates the first cylinder body 151 in the direction of the central axis X1.

[0149] A first closing plate 156 is fixed to the first vane housing hole 155. A first spring 157 is also positioned inside the first vane housing hole 155, biasing the first vane 133 radially inward toward the first cylinder body 151. One end of the first spring 157 is fixed to the first closing plate 156, and the other end of the first spring 157 is in contact with the first vane 133.

[0150] The first vane 133 is rectangular and flat, and is slidably housed in the first vane housing hole 155. The first vane 133 is biased by the first spring 157 and is always in contact with the outer surface of the first eccentric shaft portion 68b. As a result, the first working chamber is divided into a first intake chamber (not shown) for drawing in refrigerant and a first compression chamber (not shown) for compressing refrigerant.

[0151] The first intermediate plate 152 is positioned on the outer circumference of the third diameter portion 683, which is located between the first eccentric shaft portion 68b and the second eccentric shaft portion 68c, at the rear of the first cylinder body 151. The front surface of the first intermediate plate 152 is in contact with the rear surface of the first cylinder body 151. The first intermediate plate 152 is substantially disc-shaped, and a first through hole 152a is formed in the center of the first intermediate plate 152, through which the first eccentric shaft portion 68b can be inserted.

[0152] The first side plate 153 is positioned in front of the first cylinder body 151, on the outer circumference side of the third diameter portion 683. The rear surface of the first side plate 153 is in contact with the front surface of the first cylinder body 151. The first side plate 153 is substantially disc-shaped, and a second through hole 153a is formed in the center of the first side plate 153 through which the third diameter portion 683 can be inserted.

[0153] A first discharge port 158 ​​is formed in the first side plate 153. The first discharge port 158 ​​penetrates the first side plate 153 in the direction of the central axis X1 and connects the first compression chamber and the first discharge chamber 137, which will be described later. A first discharge valve mechanism 159 is fixed to the front surface of the first side plate 153. The first discharge valve mechanism 159 includes a discharge reed valve, a retainer, and fixing bolts for fixing the discharge reed valve and retainer to the first side plate 153.

[0154] The second case 135 is positioned in front of the first cylinder 131, on the outer circumference side of the third diameter portion 683. The second case 135 has a cylindrical outer case wall 135a, a substantially disc-shaped front case wall 135b, and a second boss 135c.

[0155] In the second case 135, the front end of the outer peripheral wall 135a of the case is connected to the outer peripheral edge of the front wall 135b of the case. Also, the rear end of the outer peripheral wall 135a of the case is in contact with the front surface of the first side plate 153. As a result, the first discharge chamber 137 is formed inside the second case 135.

[0156] The second boss 135c is integrally formed with the case front wall 135b and protrudes forward from the case front wall 135b. A third through hole 135d is formed inside the second boss 135c. The second boss 135c is rotatably supported by the third diameter portion 683, which is inserted into the third through hole 135d.

[0157] The second cylinder 132 comprises a second cylinder body 161, a second intermediate plate 162, and a second side plate 163. The second cylinder body 161 is positioned on the outer circumference of the second eccentric shaft portion 68c so as to cover the second eccentric shaft portion 68c. Similar to the first cylinder body 151, the second cylinder body 161 is substantially cylindrical and has an inner circumferential surface 161a with a circular cross-section centered on the central axis X1. This inner circumferential surface 161a and the outer circumferential surface of the second eccentric shaft portion 68c are in contact at one point in the circumferential direction. In this way, a second working chamber (not shown) is formed between the inner circumferential surface 161a of the second cylinder body 161 and the outer circumferential surface of the second eccentric shaft portion 68c.

[0158] The second cylinder body 161 has a second vane housing hole 165 formed therein. Although detailed illustration is omitted, the second vane housing hole 165 extends radially outward from the inner circumferential surface 161a of the second cylinder body 161 and opens onto the outer circumferential surface of the second cylinder body 161. Furthermore, the second vane housing hole 165 penetrates the second cylinder body 161 in the direction of the central axis X1.

[0159] A second closing plate 166 is fixed to the second vane housing hole 165. A second spring 167 is also positioned inside the second vane housing hole 165, biasing the second vane 134 radially inward toward the second cylinder body 161. One end of the second spring 167 is fixed to the second closing plate 166, and the other end of the second spring 167 is in contact with the second vane 134.

[0160] The second vane 134 is rectangular and flat, and is slidably housed in the second vane housing hole 165. The second vane 134 is biased by the second spring 167 and is always in contact with the outer surface of the second eccentric shaft portion 68c. As a result, the second working chamber is divided into a second intake chamber (not shown) for drawing in refrigerant and a second compression chamber (not shown) for compressing refrigerant.

[0161] The second intermediate plate 162 is positioned on the outer circumference of the third diameter portion 683, which is located between the first eccentric shaft portion 68b and the second eccentric shaft portion 68c, in front of the second cylinder body 161. The rear surface of the second intermediate plate 162 is in contact with the front surface of the second cylinder body 161. The second intermediate plate 162 is substantially disc-shaped, and a fourth insertion hole 162a is formed in the center of the second intermediate plate 162, through which the first eccentric shaft portion 68b can be inserted.

[0162] The second side plate 163 is positioned at the rear of the second cylinder body 161, on the outer circumference side of the second diameter portion 682. The front surface of the second side plate 163 is in contact with the rear surface of the second cylinder body 161. The second side plate 163 is substantially disc-shaped, and a fifth insertion hole 163a is formed in the center of the second side plate 163 through which the second diameter portion 682 can be inserted.

[0163] A second discharge port 168 is formed in the second side plate 163. The second discharge port 168 penetrates the second side plate 163 in the direction of the central axis X1 and connects the second compression chamber and the second discharge chamber 138, which will be described later. A second discharge valve mechanism 169 is fixed to the rear surface of the second side plate 163. The second discharge valve mechanism 169, like the first discharge valve mechanism 159, has a discharge reed valve, a retainer, and fixing bolts that fix the discharge reed valve and retainer to the second side plate 163.

[0164] The second cover body 136 has a cylindrical portion 136a and a vertical wall portion 136b. The cylindrical portion 136a extends cylindrically in the direction of the central axis X1. The outer diameter of the cylindrical portion 136a is formed to be approximately the same as the outer diameter of the rotor 11. The vertical wall portion 136b is located inside the cylindrical portion 136a. The vertical wall portion 136b extends radially to the second cover body 136. The outer peripheral edge of the vertical wall portion 136b is connected to the inner peripheral surface of the cylindrical portion 136a. A sixth insertion hole 136c is formed in the center of the vertical wall portion 136b. The second cover body 136 is rotatably supported by the second diameter portion 682 by inserting the second diameter portion 682 into the sixth insertion hole 136c.

[0165] In the second cover body 136, the front end of the cylindrical portion 136a and the rear surface of the second side plate 163 are in contact. As a result, a second discharge chamber 138 is formed inside the second cover body 136.

[0166] In the compression mechanism 4, the first cylinder 131, the second cylinder 132, the first vane 133, the second vane 134, the second case 135, and the second cover body 136 are fastened together in the direction of the central axis X1 by a plurality of bolts (not shown). In this way, the first cylinder 131, the second cylinder 132, the first vane 133, the second vane 134, the second case 135, and the second cover body 136 are integrated into one unit.

[0167] Furthermore, in the second cover body 136, the rotor 11 is in contact with the rear end of the cylindrical portion 136a. In this state, the third bolts 34c are inserted through each of the first bolt holes 11a from the rotor 11 side, and the third bolts 34c are screwed into the cylindrical portion 136a. In this way, the rotor 11 is fixed to the second cover body 136, and by extension to the compression mechanism 4.

[0168] Furthermore, in the second cover body 136, the vertical wall portion 136b is located in front of the first coil end 171 and, consequently, the stator 17, while facing the stator 17 in the direction of the central axis X1.

[0169] Third to sixth sliding bearings 271 to 274 are provided between the compression mechanism 4 and the shaft 68. The third sliding bearing 271 is positioned between the third insertion hole 135d of the second case 135 and the third diameter portion 683 of the shaft 68. The fourth sliding bearing 272 is positioned between the second insertion hole 153a of the first side plate 153 and the third diameter portion 683. The fifth sliding bearing 273 is positioned between the fifth insertion hole 163a of the second side plate 163 and the second diameter portion 682 of the shaft 68. The sixth sliding bearing 274 is positioned between the sixth insertion hole 136c of the second cover body 136 and the second diameter portion 682.

[0170] Thus, in this electric compressor, the shaft 68 not only supports the stator 17, but also rotatably supports the compression mechanism 4 via the third to sixth sliding bearings 271 to 274. Similar to the electric compressor of Embodiment 1, a coating layer or plating layer may be provided in the third through-hole 135d, etc., instead of the third to sixth sliding bearings 271 to 274. Alternatively, radial ball bearings may be provided in the third through-hole 135d, etc., instead of the third to sixth sliding bearings 271 to 274.

[0171] Furthermore, the compression mechanism 4 has an intake passage 181 and a discharge passage 182. The intake passage 181 is formed across the first intermediate plate 152, the second intermediate plate 162, the second cylinder body 161, the second side plate 163, and the second cover body 136. The front end of the intake passage 181 branches in two directions within the second intermediate plate 162. As a result, the intake passage 181 communicates with the first intake chamber via the first intermediate plate 152, while also communicating with the second intake chamber via the second intermediate plate 162. The rear end of the intake passage 181 opens into the vertical wall portion 136b of the second cover body 136. In this way, the intake passage 181 connects the first and second intake chambers with the containment chamber 18.

[0172] The discharge passage 182 is formed across the first side plate 153, the first cylinder body 151, the first intermediate plate 152, the second intermediate plate 162, the second cylinder body 161, and the second side plate 163.

[0173] The discharge passage 182 penetrates the first side plate 153, the first cylinder body 151, the first intermediate plate 152, the second intermediate plate 162, the second cylinder body 161, and the second side plate 163 in the direction of the central axis X1. As a result, the discharge passage 182 opens at its front end to the first side plate 153 and at its rear end to the second side plate 163. In this way, the discharge passage 182 connects the first discharge chamber 137 and the second discharge chamber 138.

[0174] Although not shown in the figures, the compression mechanism 4 has a first supply passage that communicates with the first discharge chamber 137 and the first vane housing hole 155, and a second supply passage that communicates with the second discharge chamber 138 and the second vane housing hole 165. The other components of this electric compressor are the same as those of the electric compressor of Embodiment 1, and the same reference numerals are used for the same components, and a detailed explanation of the components is omitted.

[0175] In this electric compressor configured as described above, as shown by the dashed arrow in Figure 2, low-temperature, low-pressure refrigerant that has passed through the evaporator is drawn into the containment chamber 18 from the intake port 73. The refrigerant drawn into the containment chamber 18 in this way also contains lubricating oil. The inverter 3 supplies power to the stator 17 and controls the operation of the electric motor 10, causing the rotor 11 of the electric motor 10 to rotate around the central axis X1. As a result, the compression mechanism 4 also rotates around the central axis X1 along with the rotor 11.

[0176] The rotation of the compression mechanism 4 causes the first cylinder body 151 and the first vane 133, etc., and the second cylinder body 161 and the second vane 134, etc., to rotate together. The first cylinder body 151 and the first vane 133, etc., and the second cylinder body 161 and the second vane 134, etc., operate similarly. Therefore, the operation of the first cylinder body 151 and the first vane 133, etc., will be mainly explained below, and the operation of the second cylinder body 161 and the second vane 134, etc., will be omitted as appropriate.

[0177] Here, with each rotation of the compression mechanism 4, the first cylinder body 151 and the first vane 133, and the second cylinder body 161 and the second vane 134 are periodically displaced. In this electric compressor, the displacement period of the first cylinder body 151, etc., and the displacement period of the second cylinder body 161, etc., are offset by 180 degrees, which is half a cycle.

[0178] As the compression mechanism 4 rotates, the first cylinder body 151 rotates along the outer surface of the first eccentric portion 126 with the central axis X1 as the axis of rotation. The rotation of the first cylinder body 151 also causes the first vane 133 to rotate along the outer surface of the first eccentric portion 126. During this rotation, the first vane 133 is biased radially inward by the biasing force of the first spring 157, causing its tip to contact the outer surface of the first eccentric portion 126 as it moves back and forth relative to the first working chamber. This divides the first working chamber into a first intake chamber and a first compression chamber. In other words, in this electric compressor, the movement of the first vane 133 accompanying the rotation of the first cylinder body 151 changes the volume of both the first intake chamber and the first compression chamber.

[0179] As a result, as shown by the dashed arrows in Figure 2, the refrigerant in the containment chamber 18 flows between the rotor 11 and the stator 17 to reach the intake passage 181, and also flows through slits formed in the stator core 17a to reach the intake passage 181. Furthermore, the refrigerant in the containment chamber 18 also reaches the intake passage 181 by flowing through the first to third fluid passages 811 to 813, i.e., the fluid passage 68d. The refrigerant that reaches the intake passage 181 is then drawn into the first intake chamber by flowing through the intake passage 181.

[0180] The refrigerant drawn into the first intake chamber is then compressed in the first compression chamber, which it transitions to from the first intake chamber. The high-pressure refrigerant, thus compressed to the discharge pressure, is discharged from the first discharge port 158 ​​into the first discharge chamber 137.

[0181] Meanwhile, the reciprocating movement of the second vane 134 accompanying the rotation of the second cylinder body 161 causes a similar effect in the second working chamber. As a result, the refrigerant in the containment chamber 18 is also drawn into the second intake chamber by flowing through the intake passage 181. The refrigerant drawn into the second intake chamber is then compressed in the second compression chamber, to which it transitions, and discharged from the second discharge port 168 into the second discharge chamber 138.

[0182] The centrifugal force of the rotating compression mechanism 4 acts on the refrigerant discharged into the first discharge chamber 137 and the second discharge chamber 138, respectively. As a result, the lubricating oil contained in the refrigerant is separated from the refrigerant by centrifugal force, even in this electric compressor. This lubricating oil is then stored in the first discharge chamber 137 and the second discharge chamber 138.

[0183] Furthermore, the refrigerant discharged into the second discharge chamber 138 flows through the discharge passage 182 to reach the first discharge chamber 137. The refrigerant in the first discharge chamber 137 then flows through the shaft discharge passage 175 to reach the discharge port 74, and is discharged to the outside of the housing 6a.

[0184] In this electric compressor, the heat from the stator 17 during operation is inevitably transferred to the shaft 68. In addition, the frictional heat generated by the rotation of the compression mechanism 4, as well as the heat from the refrigerant that has become hot due to compression, are also inevitably transferred to the shaft 68.

[0185] In this electric compressor, the shaft 68 is formed separately from the partition wall 61 and is supported by the partition wall 61. As a result, similar to the electric compressor in Embodiment 1, even if the shaft 68 becomes hot, the heat from the shaft 68 is less likely to be transferred to the partition wall 61. Consequently, in this electric compressor as well, the heat from the shaft 68 is less likely to be transferred to the inverter 3 housed in the inverter chamber 620. Therefore, in this electric compressor as well, there is no need to use semiconductors or the like with excessively high heat resistance in the inverter 3.

[0186] Therefore, the electric compressor of Example 2 can effectively prevent damage to the inverter 3 due to heat, and can also achieve lower manufacturing costs.

[0187] Furthermore, in this electric compressor, a portion of the refrigerant in the containment chamber 18 is also drawn into the first and second intake chambers from the intake passage 181 by flowing through the first to third fluid passages 811 to 813. In other words, in this electric compressor, the refrigerant in the containment chamber 18 is also drawn into the first and second compression chambers, and consequently the compression mechanism 4, via the fluid passage 68d. Therefore, in this electric compressor, the refrigerant that has reached the fluid passage 68d from the containment chamber 18 does not remain stagnant in the fluid passage 68d. As a result, in this electric compressor, the shaft 68 can be suitably cooled by the low-temperature refrigerant flowing through the fluid passage 68d toward the first and second compression chambers. In this respect as well, in this electric compressor, heat from the shaft 68 is less likely to be transferred to the inverter 3.

[0188] Furthermore, in this electric compressor, a portion of the lubricating oil stored in the first discharge chamber 137 is supplied to the first vane housing hole 155 through the first supply passage. Similarly, a portion of the lubricating oil stored in the second discharge chamber 138 is supplied to the second vane housing hole 165 through the second supply passage. As a result, the first vane housing hole 155 and the second vane housing hole 165 become high pressure in the electric compressor. Therefore, the pressure of the lubricating oil supplied to the first vane housing hole 155 and the second vane housing hole 165 respectively makes it possible to bring the tip of the first vane 133 into suitable contact with the outer circumferential surface of the first eccentric portion 126, and also makes it possible to bring the tip of the second vane 134 into suitable contact with the outer circumferential surface of the second eccentric portion 127. As a result, this electric compressor can effectively prevent refrigerant leakage from the first compression chamber to the first suction chamber, and also effectively prevent refrigerant leakage from the second compression chamber to the second suction chamber.

[0189] Furthermore, the lubricating oil in the first vane housing hole 155 flows through the gap between the first cylinder body 151 and the first side plate 153, etc. Similarly, the lubricating oil in the second vane housing hole 165 flows through the gap between the second cylinder body 161 and the second side plate 163, etc. In this way, the compression mechanism 4, including the first and second cylinders 131 and 132 and the first and second vanes 133 and 134, can be suitably lubricated with lubricating oil in this electric compressor.

[0190] Furthermore, in this electric compressor, the lubricating oil stored in the first discharge chamber 137 is capable of suitably lubricating the space between the third sliding bearing 271 and the fourth sliding bearing 272 and the third diameter portion 683 of the shaft 68. In this electric compressor, the lubricating oil stored in the second discharge chamber 138 is capable of suitably lubricating the space between the fifth sliding bearing 273 and the sixth sliding bearing 274 and the second diameter portion 682 of the shaft 68. Other functions of this electric compressor are the same as those of the electric compressor in Example 1.

[0191] Although the present invention has been described above in reference to Examples 1 and 2, it goes without saying that the present invention is not limited to Examples 1 and 2, and can be applied with appropriate modifications without departing from its spirit.

[0192] For example, in the electric compressor of Example 1, a compression mechanism with a different configuration from compression mechanism 2 may be adopted. Similarly, in the electric compressor of Example 2, a compression mechanism with a different configuration from compression mechanism 4 may be adopted.

[0193] Furthermore, in the electric compressor of Example 1, the first insulator 91 or the second insulator 92 may be omitted, or both the first insulator 91 and the second insulator 92 may be omitted. The same applies to the electric compressor of Example 2.

[0194] Furthermore, in the electric compressor of Embodiment 1, the inverter 3 may be fixed to the first outer peripheral wall 60a or the first bottom wall 60b of the housing body 60. Similarly, in the electric compressor of Embodiment 2, the inverter 3 may be fixed to the third outer peripheral wall 67a or the third bottom wall 67b of the housing body 67.

[0195] Furthermore, this specification includes the following inventions. (Note 1) The device comprises a housing, a compression mechanism for compressing a fluid, an electric motor for operating the compression mechanism, and an inverter for controlling the operation of the electric motor. Inside the housing, a chamber is formed into which fluid is drawn in from outside the housing, and which houses the compression mechanism and the electric motor. The electric motor comprises a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator. The inverter is an electric compressor fixed to the housing and located outside the housing chamber, The housing has a partition wall separating the housing chamber from the outside of the housing chamber, and a support located inside the housing chamber that supports the stator. An electric compressor characterized in that the support body is formed separately from the partition wall and is supported by the partition wall. (Note 2) The electric compressor according to Appendix 1, wherein the thermal conductivity of the support is smaller than the thermal conductivity of the partition wall. (Note 3) The electric compressor according to Appendix 1 or 2, wherein a fluid passage is formed inside the support body through which the fluid in the containment chamber can flow. (Note 4) An electric compressor as described in Appendix 3, wherein fluid is drawn into the compression mechanism via the fluid passage. (Note 5) The support is supported by the partition wall via an insulating material that suppresses heat transfer from the support to the partition wall. The aforementioned insulator is less rigid than the housing, and is an electric compressor according to any one of the appendices 1 to 4. (Note 6) The stator is supported by the support via an insulating member that suppresses heat transfer from the stator to the support, The aforementioned heat insulating member is an electric compressor according to any one of the appendices 1 to 5, wherein the heat insulating member has lower rigidity than the housing. (Note 7) The housing has a housing body, The housing body is formed in a bottomed cylindrical shape having a bottom wall extending radially to the housing and a peripheral wall that is connected to the bottom wall and extends cylindrically from the bottom wall in the axial direction of the housing. The electric compressor according to any one of the appendices 1 to 6, wherein the partition wall is fixed to the circumferential wall on the side opposite to the bottom wall in the axial direction. (Note 8) The compression mechanism comprises a drive scroll, a driven scroll, and a driven mechanism. The drive scroll is rotationally driven around the drive shaft by the electric motor. The driven scroll is rotated and driven by the driven scroll and the driven mechanism around its driven axis, while being eccentric with respect to the driven scroll. An electric compressor according to any one of the appendices 1 to 7, wherein the drive scroll and the driven scroll form a compression chamber for compressing a fluid by the rotational drive and the rotational drive. (Note 9) The partition wall has a first surface facing the interior of the housing and a second surface located on the opposite side of the first surface and facing the exterior of the housing. The inverter is an electric compressor as described in any one of the appendices 1 to 8, fixed to the second surface. [Industrial applicability]

[0196] This invention can be used in vehicle air conditioning systems and the like. [Explanation of symbols]

[0197] 2, 4... Compression mechanism 3…Inverter 6, 6a… Housing 10… Electric motor 11…Rota 12... Compression chamber 17…Status 18... Confinement Chamber 20…Following mechanism 30…Drive Scroll 40...Driven Scroll 60, 67... Housing body 60a...First perimeter wall (perimeter wall) 60b…1st bottom wall (bottom wall) 61...Bulkhead 61a…First page 61b…Second side 64...Support 64c, 68d...Fluid passage 65...Scroll Room (Containment Room) 67a...Third peripheral wall (peripheral wall) 67b...Third bottom wall (bottom wall) 68... Shaft (support) 91...First insulator (insulator) 92...Second insulation layer (insulating material) O1...Drive shaft center O2…driven shaft center

Claims

1. The device comprises a housing, a compression mechanism for compressing a fluid, an electric motor for operating the compression mechanism, and an inverter for controlling the operation of the electric motor. Inside the housing, a chamber is formed into which fluid is drawn in from outside the housing, and which houses the compression mechanism and the electric motor. The electric motor comprises a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator. The inverter is an electric compressor fixed to the housing and located outside the housing chamber, The housing has a partition wall separating the housing chamber from the outside of the housing chamber, and a support located inside the housing chamber that supports the stator. An electric compressor characterized in that the support body is formed separately from the partition wall and is supported by the partition wall.

2. The electric compressor according to claim 1, wherein the thermal conductivity of the support is smaller than the thermal conductivity of the partition wall.

3. The electric compressor according to claim 1 or 2, wherein a fluid passage is formed inside the support body through which the fluid in the containment chamber can flow.

4. The electric compressor according to claim 3, wherein a fluid is drawn into the compression mechanism through the fluid passage.

5. The support is supported by the partition wall via an insulating material that suppresses heat transfer from the support to the partition wall. The electric compressor according to claim 1 or 2, wherein the heat insulating body has lower rigidity than the housing.

6. The stator is supported by the support via an insulating member that suppresses heat transfer from the stator to the support, The electric compressor according to claim 1 or 2, wherein the heat insulating member has lower rigidity than the housing.

7. The housing has a housing body, The housing body is formed in a bottomed cylindrical shape having a bottom wall extending radially to the housing and a peripheral wall that is connected to the bottom wall and extends cylindrically from the bottom wall in the axial direction of the housing. The electric compressor according to claim 1 or 2, wherein the partition wall is fixed to the circumferential wall on the side opposite to the bottom wall in the axial direction.

8. The compression mechanism comprises a drive scroll, a driven scroll, and a driven mechanism. The drive scroll is rotationally driven around the drive shaft by the electric motor. The driven scroll is rotated and driven by the driven scroll and the driven mechanism around its driven axis, while being eccentric with respect to the driven scroll. The electric compressor according to claim 1 or 2, wherein the drive scroll and the driven scroll form a compression chamber that compresses a fluid by the rotational drive and the rotational drive.

9. The partition wall has a first surface facing the interior of the housing and a second surface located on the opposite side of the first surface and facing the exterior of the housing. The electric compressor according to claim 1 or 2, wherein the inverter is fixed to the second surface.

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