Motor compressor

Abstract

To provide a motor compressor capable of suppressing vibration and noise.SOLUTION: A compressor ECP has a housing 10, a rotation shaft 20, a compression part 30, an electric motor 50, a shaft support member 40 including a first bearing part 411 supporting the rotation shaft 20, and a second bearing part 17 supporting the rotation shaft 20 at a position different from the first bearing part 411. The housing 10 includes an inner housing 16 accommodating at least a part of the electric motor 50 and to which a stator 54 is fixed, a motor housing 12 accommodating the inner housing 16, and a discharge housing 14 fixed to the motor housing 12. In the inner housing 16 and the compression part 30, a part of an intermediate portion E3 is fixed to a fixing portion FP set to at least one of the motor housing 12 and the discharge housing 14, and is separated from other portions except the fixing portion FP in a radial direction DR of the rotation shaft 20.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present disclosure relates to an electric compressor. [Background technology]

[0002] Conventionally, an electric compressor has been disclosed in which a stator of an electric motor is fixed to an inner housing arranged inside a motor housing (see, for example, Patent Document 1). In the electric compressor of Patent Document 1, the inner housing and the compression section are fixed to a discharge housing with bolts, and the inner peripheral surface of the motor housing and the outer peripheral surface of the inner housing are spaced apart from each other. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2019-173658 A Summary of the Invention [Problem to be solved by the invention]

[0004] However, in the electric compressor described in Patent Document 1, the internal housing and the compression unit are fixed to the discharge housing at the axial end, and the stator and compression unit, which are heavy parts, are supported in a manner similar to that of a cantilever. In such a structure, the distance between the position where the internal housing and the compression unit are supported and the position where vibration occurs is large, so that vibrations of the electric motor and the compression unit are easily transmitted to the discharge housing, and noise is likely to occur. This fact was discovered after extensive research by the present inventors.

[0005] An object of the present disclosure is to provide an electric compressor capable of suppressing vibration and noise. [Means for solving the problem]

[0006] The invention described in claim 1 is An electric compressor, A housing (10); A rotating shaft (20) accommodated inside the housing; a compression section (30) that compresses a fluid by rotating a rotary shaft; an electric motor (50) having a rotor (52) that rotates integrally with a rotary shaft and a stator (54) that is fixed to a housing, and that drives a compression section; a shaft support member (40) including a first bearing portion (411) that rotatably supports a rotating shaft; a second bearing portion (17) that rotatably supports the rotating shaft relative to the housing at a position different from the first bearing portion, The housing is an inner housing (16) that accommodates at least a portion of the electric motor and to which the stator is fixed; a first outer housing (12) that houses the inner housing; a second outer housing (14) fixed to the first outer housing; When the portion of the inner housing and the compression portion that is located closest to one side in the axial direction of the rotating shaft is defined as a first end (E1), the portion that is located closest to the other side in the axial direction is defined as a second end (E2), and an intermediate portion (E3) that is located between the first end and the second end is defined as: A portion of the intermediate portion of the inner housing and the compression portion is fixed to a fixed portion (FP) set on at least one of the first outer housing and the second outer housing, and is spaced apart from other portions in the radial direction of the rotation axis except for the fixed portion.

[0007] In this way, by fixing a part of the middle part of the internal housing and the compression unit, the distance between the position supporting the internal housing and the compression unit and the position where vibration occurs can be made smaller than when the internal housing and the compression unit are fixed in a cantilever-like manner. This reduces the vibration of the electric motor and the compression unit and makes it difficult for it to be transmitted to each external housing, thereby suppressing noise. In this way, the electric compressor of the present disclosure can suppress vibration and noise.

[0008] In addition, the rotating shaft is supported by the first and second bearings, which allows the sliding area of ​​each bearing to be set small, making it easier to steadily supply lubricant to the entire sliding surface in low to high rotation ranges of the rotating shaft, ensuring reliability.

[0009] Note that the reference symbols in parentheses attached to each component indicate an example of the correspondence between the component and specific components described in the embodiments described below. [Brief description of the drawings]

[0010] [Figure 1] 1 is a schematic configuration diagram of a refrigeration cycle including an electric compressor according to a first embodiment. [Diagram 2] 1 is a schematic cross-sectional view of an electric compressor according to a first embodiment. [Diagram 3] FIG. 3 is a cross-sectional view taken along line III-III of FIG. [Figure 4] FIG. 4 is an explanatory diagram for explaining the flow of an assembly operation of each component part of the compressor. [Diagram 5] 10 is an explanatory diagram for explaining a process of assembling an inner housing to which the stator is fixed, to a shaft support member. FIG. [Figure 6] 10A to 10C are explanatory views for explaining a process of assembling an inner housing, a shaft support member, and a compression portion to a motor housing. [Figure 7] 11A to 11C are explanatory views for explaining a process of assembling the discharge housing to the motor housing. [Figure 8] FIG. 6 is a schematic cross-sectional view of an electric compressor according to a second embodiment. [Figure 9] 11 is a schematic diagram showing an end portion of a shaft support member on an inner housing side as viewed from the axial direction. FIG. [Figure 10] XX cross-sectional view of Figure 9. [Figure 11] FIG. 11 is a schematic cross-sectional view of an electric compressor according to a third embodiment. [Figure 12] 11 is a schematic diagram showing an end portion of a shaft support member on an inner housing side as viewed from the axial direction. FIG. [Figure 13] FIG. 13 is a cross-sectional view taken along line XIII-XIII of FIG. [Figure 14] FIG. 11 is a schematic cross-sectional view of an electric compressor according to a fourth embodiment. [Figure 15] FIG. 11 is a schematic cross-sectional view of an electric compressor according to a fifth embodiment. [Figure 16] FIG. 13 is a schematic cross-sectional view of an electric compressor according to a sixth embodiment. [Figure 17] FIG. 13 is a schematic cross-sectional view of an electric compressor according to a seventh embodiment. [Figure 18] 18 is a cross-sectional view taken along line XVIII-XVIII of FIG. 17. [Figure 19] FIG. 13 is a schematic cross-sectional view of an electric compressor according to an eighth embodiment. [Figure 20] FIG. 13 is a schematic cross-sectional view of an electric compressor according to a ninth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0011] Hereinafter, the embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, the same reference numerals are used for parts that are the same as or equivalent to those described in the preceding embodiments, and the description thereof may be omitted. In addition, in the embodiments, when only a part of the components is described, the components described in the preceding embodiments can be applied to the other parts of the components. In the following embodiments, each embodiment can be partially combined with each other, even if not specifically stated, as long as it does not cause any trouble in combination.

[0012] (First embodiment) The present embodiment will be described with reference to Figures 1 to 7. In the present embodiment, an example will be described in which an electric compressor (hereinafter referred to as a compressor ECP) ​​according to the present disclosure is applied to a refrigeration cycle device 1 constituting a vehicle air conditioner.

[0013] The refrigeration cycle device 1 constitutes a vapor compression type refrigeration cycle. As shown in FIG. 1, the refrigeration cycle device 1 includes a compressor ECP, a radiator CD, a pressure reducing device EXV, and an evaporator EV. The compressor ECP is a device that compresses and discharges a refrigerant, which is a fluid. The radiator CD is a heat exchanger that exchanges heat between the refrigerant discharged from the compressor ECP and the air blown from the first blower FAN1 to dissipate heat. The pressure reducing device EXV is a device that reduces the pressure of the refrigerant that has passed through the radiator CD and expands it. The evaporator EV is a heat exchanger that exchanges heat between the refrigerant depressurized by the pressure reducing device EXV and the air blown from the second blower FAN2 to evaporate it. The radiator CD may be configured to dissipate heat to a heat medium different from the air blown from the first blower FAN1. The same applies to the evaporator EV.

[0014] The refrigeration cycle device 1 employs a fluorocarbon-based refrigerant as the refrigerant. The refrigerant is mixed with lubricating oil that lubricates each sliding part inside the compressor ECP. A part of the lubricating oil circulates in the cycle together with the refrigerant. The refrigerant may be a refrigerant other than the fluorocarbon-based refrigerant (e.g., carbon dioxide, propane).

[0015] Hereinafter, the compressor ECP will be described in detail with reference to Fig. 2. Fig. 2 is an axial cross-sectional view showing a cross-section cut along the axis CL of the rotating shaft 20 of the compressor ECP. Note that the arrows indicating up and down in Fig. 2 indicate the vertical direction Dg in a state in which the compressor ECP is mounted on a vehicle. Also, in Fig. 2, the direction along the axis CL of the rotating shaft 20 is the axial direction Dax, and the direction perpendicular to the axis CL of the rotating shaft 20 is the radial direction Dr. These are the same in the drawings other than Fig. 2.

[0016] 2, the compressor ECP includes a housing 10, a rotating shaft 20, a compression unit 30, and an electric motor 50. The rotating shaft 20, the compression unit 30, and the electric motor 50 are accommodated inside the housing 10. The compressor ECP has a horizontally-mounted structure in which the axis CL of the rotating shaft 20 extends in a substantially horizontal direction, and the compression unit 30 and the electric motor 50 are arranged in a substantially horizontal direction and are installed in the vehicle.

[0017] The housing 10 includes a motor housing 12, a discharge housing 14, and an inner housing 16. The motor housing 12, the discharge housing 14, and the inner housing 16 are made of a metal material. The motor housing 12 and the discharge housing 14 are outer housings that form the outer shell of the compressor ECP. The motor housing 12 and the discharge housing 14 are made of, for example, aluminum or an aluminum alloy.

[0018] The motor housing 12 accommodates the inner housing 16. The motor housing 12 has a bottomed cylindrical shape that is open on one side in the axial direction Dax of the rotating shaft 20. Specifically, the motor housing 12 has a plate-shaped first bottom wall portion 121 and a first outer peripheral wall portion 122 that extends in a cylindrical shape from an outer peripheral portion of the first bottom wall portion 121. The motor housing 12 is configured as a seamless, integrally molded product in which the first bottom wall portion 121 and the first outer peripheral wall portion 122 are integrated. In this embodiment, the motor housing 12 constitutes a "first outer housing."

[0019] The motor housing 12 has a stepped shape in which a step surface 123 is formed on the inner portion of the first outer circumferential wall portion 122. The step surface 123 intersects with the axial direction Dax. The step surface 123 in this embodiment extends along the radial direction Dr of the rotating shaft 20.

[0020] The step surface 123 is a surface that connects a first housing portion 124, which has a smaller inner diameter at the inner portion of the motor housing 12, to a second housing portion 125, which has a larger inner diameter than the first housing portion 124. The first housing portion 124 is a portion that continues to the first bottom wall portion 121. The inner housing 16 is housed inside the first housing portion 124. The shaft support member 40 and a part of the compression portion 30 are housed inside the second housing portion 125.

[0021] Although not shown, an airtight terminal to which electrical wiring and the like of the electric motor 50 is connected is provided on the first bottom wall portion 121 of the motor housing 12. The electric motor 50 is electrically connected to an inverter (not shown) via the airtight terminal.

[0022] A refrigerant suction port is formed in the motor housing 12. The refrigerant outlet side of the evaporator EV is connected to this suction port. Therefore, the space in the housing 10 in which the electric motor 50 is disposed has a low-pressure and low-temperature atmosphere. This allows the electric motor 50 to be cooled, thereby improving the efficiency and reliability of the electric motor 50.

[0023] The discharge housing 14 forms a space into which the refrigerant compressed in the compression section 30 is discharged. The discharge housing 14 has a bottomed cylindrical shape that opens on the other side in the axial direction Dax of the rotating shaft 20. Specifically, the discharge housing 14 has a plate-shaped second bottom wall portion 141 and a second outer peripheral wall portion 142 that extends in a cylindrical shape from the outer peripheral portion of the second bottom wall portion 141. The discharge housing 14 is configured as a seamless integral molded product of the second bottom wall portion 141 and the second outer peripheral wall portion 142. In this embodiment, the discharge housing 14 configures a "second outer housing."

[0024] The discharge housing 14 is fixed to the motor housing 12 by fastening bolts 15 in a state in which an opening edge on the other side of the axial direction Dax of the discharge housing 14 is abutted against an opening edge on one side of the motor housing 12 in the axial direction Dax. The motor housing 12 and the discharge housing 14 form a pressure vessel. An atmosphere consisting of low-pressure, low-temperature refrigerant inside the motor housing 12 and an atmosphere consisting of high-pressure, high-temperature refrigerant discharged from the compression section 30 are separated by a sealing member (not shown).

[0025] Although not shown, a refrigerant discharge port is formed in the discharge housing 14. The refrigerant inlet side of the radiator CD is connected to this discharge port. An oil separator that separates the lubricating oil in the refrigerant is installed in the discharge port. Therefore, the lubricating oil in the refrigerant discharged from the compression section 30 is stored inside the discharge housing 14.

[0026] The rotating shaft 20 is accommodated inside the housing 10. Specifically, the rotating shaft 20 is disposed inside the motor housing 12 such that the axis CL of the rotating shaft 20 coincides with the central axis of the first outer peripheral wall portion 122 of the motor housing 12.

[0027] The rotating shaft 20 is provided at one end in the axial direction Dax with an eccentric shaft portion 21 that is eccentric from the axis CL of the rotating shaft 20. The eccentric shaft portion 21 is formed integrally with the main body of the rotating shaft 20. The eccentric shaft portion 21 is supported by an eccentric bearing portion 344 provided on a first boss portion 343 of the orbiting scroll 34, which will be described later.

[0028] The rotating shaft 20 is provided with an enlarged diameter portion 22, the outer diameter of which is enlarged, adjacent to the eccentric shaft portion 21. The enlarged diameter portion 22 is provided with a balance weight 23 for suppressing eccentric rotation of the rotating shaft 20.

[0029] An oil supply passage 24 is formed inside the rotating shaft 20, which supplies lubricating oil to the eccentric bearing 344, a first bearing 411 described later, a second bearing 17, etc. The oil supply passage 24 communicates with the inside of the discharge housing 14 via an oil supply path (not shown) formed in the fixed scroll 32 and the orbiting scroll 34. The lubricating oil stored inside the discharge housing 14 is supplied to the eccentric bearing 344, a first bearing 411 described later, a second bearing 17, etc. via the oil supply path and the oil supply passage 24.

[0030] The compression section 30 is configured as a scroll-type compression mechanism. The compression section 30 has a fixed scroll 32, an orbiting scroll 34, and a discharge plate 36. The orbiting scroll 34, the fixed scroll 32, and the discharge plate 36 are arranged in this order in the axial direction Dax. The fixed scroll 32, the orbiting scroll 34, and the discharge plate 36 are made of steel material, aluminum alloy, or the like.

[0031] The fixed scroll 32 has a fixed base plate portion 321 formed in a disk shape, and a spiral-shaped fixed teeth portion 322 protruding from the fixed base plate portion 321 toward the orbiting scroll 34 on the other side in the axial direction Dax.

[0032] The orbiting scroll 34 has an orbiting base portion 341 formed in a disk shape, and a spiral orbiting tooth portion 342 protruding from the orbiting base portion 341 toward the fixed scroll 32 on one side in the axial direction Dax.

[0033] The orbiting scroll 34 is provided with a cylindrical first boss portion 343 on the opposite side of the orbiting base plate portion 341 from the orbiting teeth portion 342. An eccentric bearing portion 344 is provided inside the first boss portion 343. The eccentric bearing portion 344 is made of a plain bearing. The eccentric bearing portion 344 may be made of a bearing other than a plain bearing.

[0034] An Oldham ring 35 is connected to the orbiting scroll 34. The Oldham ring 35 constitutes a rotation prevention mechanism that prevents the orbiting scroll 34 from rotating on its axis. When the rotating shaft 20 rotates, the orbiting scroll 34 performs an orbital motion (i.e., an orbital motion) around the axis CL of the rotating shaft 20 as the center of revolution. Note that the rotation prevention mechanism may be constituted by something other than the Oldham ring 35.

[0035] Between the fixed scroll 32 and the orbiting scroll 34, the fixed teeth 322 and the orbiting teeth 342 mesh with each other and come into contact at multiple points, forming multiple crescent-shaped working chambers 31. As the orbiting scroll 34 orbits, the working chambers 31 move from the outer periphery to the center while decreasing in volume. Although not shown, refrigerant sucked from a refrigerant suction port formed on the outer periphery of the fixed scroll 32 is supplied to the working chambers 31. The refrigerant in the working chambers 31 is compressed as the volume of the working chambers 31 decreases. For convenience, in FIG. 2 and other figures, only one of the multiple working chambers 31 is indicated by a reference number.

[0036] A discharge hole 323 for discharging the refrigerant compressed in the working chamber 31 is formed in the center of the fixed base plate part 321. A reed valve (not shown) serving as a check valve for preventing backflow of the refrigerant into the working chamber 31 and a stopper 324 for regulating the maximum opening degree of the reed valve are provided on one end face of the fixed base plate part 321 in the axial direction Dax. The reed valve and the stopper 324 are fastened and fixed to the fixed base plate part 321 by a bolt 325.

[0037] The discharge plate 36 is disposed adjacent to the fixed scroll 32. Between the discharge plate 36 and the fixed scroll 32, a muffler chamber 361 is formed for reducing discharge pulsation of the refrigerant discharged from the discharge hole 323. The discharge plate 36 is formed in a cup shape. Although not shown, an outlet port for discharging the refrigerant in the muffler chamber 361 is formed at the bottom of the discharge plate 36. Note that the discharge plate 36 is not an essential component of the compression section 30.

[0038] The fixed scroll 32 and the discharge plate 36 have substantially the same outer diameter. The fixed scroll 32 and the discharge plate 36 have outer diameters that are larger than the inner diameter of the first housing portion 124 of the motor housing 12 and smaller than the inner diameter of the second housing portion 125.

[0039] The compression portion 30 configured in this manner is fixed to the stepped surface 123 of the motor housing 12 by a mounting bolt 37 via the shaft support member 40. The stepped surface 123 of the motor housing 12 constitutes a fixing portion FP to which the compression portion 30 is fixed.

[0040] The shaft support member 40 includes a first bearing portion 411 that rotatably supports the rotating shaft 20. The shaft support member 40 is disposed between the compression section 30 and the electric motor 50. A space is formed between the shaft support member 40 and the fixed scroll 32 to accommodate the orbiting scroll 34, the Oldham ring 35, a part of the rotating shaft 20, etc. The shaft support member 40 is made of a steel material, an aluminum alloy, etc.

[0041] The shaft support member 40 has a cylindrical shape. The outer diameter and inner diameter of the shaft support member 40 are gradually reduced from one side to the other side in the axial direction Dax. Specifically, the shaft support member 40 has a small diameter portion 41 where the inner diameter is the smallest, a large diameter portion 42 where the outer diameter is the largest, and a connecting portion 43 that connects the small diameter portion 41 and the large diameter portion 42. The small diameter portion 41, the large diameter portion 42, and the connecting portion 43 are integrally configured.

[0042] The shaft support member 40 has a first bearing portion 411 formed on the inner peripheral side of the small diameter portion 41. The first bearing portion 411 is made of a plain bearing. The first bearing portion 411 is made of a cylindrical steel member and a resin layer or the like coated on its inner peripheral surface. The first bearing portion 411 may be made of the same material as the shaft support member 40 and may be integrally formed with the shaft support member 40. The first bearing portion 411 may be made of a bearing other than a plain bearing.

[0043] A thrust plate 44 formed in an annular shape is disposed between the shaft support member 40 and the orbiting scroll 34. The thrust plate 44 allows the orbiting scroll 34 to slide relative to the shaft support member 40.

[0044] The outer diameter of the large diameter portion 42 of the shaft support member 40 is set to be substantially the same as the dimensions of the fixed scroll 32 and the discharge plate 36. The outer diameter of the large diameter portion 42 of the shaft support member 40 is larger than the inner diameter of the first housing portion 124 of the motor housing 12 and smaller than the inner diameter of the second housing portion 125.

[0045] Although not shown, the shaft support member 40 is provided with a refrigerant introduction passage that introduces a refrigerant from the inside of the inner housing 16, which will be described later, to the compression section 30. This refrigerant introduction passage is provided at least below the axis CL of the shaft support member 40.

[0046] The shaft support member 40 configured in this manner is fixed to the motor housing 12 together with the compression portion 30 by a mounting bolt 37. A fixing portion FP of the shaft support member 40 for fixing the shaft support member 40 to the motor housing 12 will be described later.

[0047] Although not shown, a communication passage is provided inside the housing 10 to connect the gap space 164 formed between the motor housing 12 and the inner housing 16 to the refrigerant introduction passage. This allows the lubricating oil that has accumulated in the gap space 164 to be guided to the refrigerant introduction passage via the communication passage.

[0048] The electric motor 50 is configured as an inverter-driven DC motor that is driven by power supplied from an inverter (not shown). It is disposed on the other side of the shaft support member 40 in the axial direction Dax. The electric motor 50 drives the compression section 30, and has a rotor 52 that rotates integrally with the rotating shaft 20, and a stator 54 that is fixed to the housing 10. The electric motor 50 is configured as an inner rotor motor in which the rotor 52 is disposed inside the stator 54.

[0049] The rotor 52 is a cylindrical member to which the rotating shaft 20 is fixed by press-fitting or the like. A permanent magnet (not shown) is disposed inside the rotor 52. In addition, balance weights 521 and 522 are attached to the side surface of the rotor 52 to offset the imbalance of the eccentric rotation of the orbiting scroll 34 and the like.

[0050] The stator 54 has a stator core 541 made of a metallic magnetic material, and a coil 542 wound around the stator core 541. When power is supplied to the stator 54 from an inverter (not shown), the stator 54 generates a rotating magnetic field that rotates the rotor 52. The stator 54 is fixed to the cylindrical portion 161 of the inner housing 16 by shrink fitting or press fitting.

[0051] The inner housing 16 is accommodated inside the motor housing 12. A stator 54 is fixed to the inner housing 16. The inner housing 16 is made of the same type of metal material as the stator 54. When the stator 54 is made of a steel material, the inner housing 16 is made of the same type of steel material as the stator 54 (e.g., iron).

[0052] Here, the operating environment range of the on-vehicle compressor ECP is assumed to be -40 to 100°C, taking into consideration the low outside air temperature and heat generated by the main motor and engine. The stator core 541 is generally made of electromagnetic steel sheet. Taking these factors into consideration, the material constituting the inner housing 16 should have a linear expansion coefficient of 20×10 -6 Materials with a temperature of 0.1°C or less are preferable.

[0053] If the difference in linear expansion coefficient between the stator 54 and the internal housing 16 is reduced, the tightening margin can be set appropriately in the expected temperature range. For example, when a metal material with a large linear expansion coefficient such as aluminum is used as the material for the internal housing 16, the difference in linear expansion coefficient with the stator 54 becomes large. Therefore, when a tightening margin that can secure the tension force in the high temperature range is set, assuming a low outside air temperature range, the tightening margin increases. As a result, the distortion of the stator core 541 increases, and the efficiency of the electric motor 50 decreases. Conversely, if the tightening margin is set so that the effect of the distortion is small at low outside air temperatures, the tension force decreases at high outside air temperatures, and the fixing of the stator 54 may become unstable.

[0054] The internal housing 16 has a generally cup-shaped configuration. The internal housing 16 has a cylindrical tube portion 161 to which the stator 54 is fixed, and a flange portion 162 that protrudes in a direction away from the rotating shaft 20 from one end portion 161a of the tube portion 161 that is closer to the compression portion 30. The internal housing 16 also includes a support portion 163 that extends from the other end portion 161b located opposite to the one end portion 161a so as to approach the rotating shaft 20 and supports the second bearing portion 17. The tube portion 161, the flange portion 162, and the support portion 163 are configured as an integrally molded product.

[0055] The support portion 163 has an annular bottom portion 163a connected to the other end portion 161b of the tube portion 161, and a cylindrical second boss portion 163b provided at the center portion of the bottom portion 163a. ​​The second boss portion 163b protrudes from the other side to one side in the axial direction Dax so that a part of the second boss portion 163b overlaps with the stator 54 in the radial direction Dr. The second bearing portion 17 is formed on the inner periphery side of the second boss portion 163b. The second bearing portion 17 is made of a plain bearing. The second bearing portion 17 is made of a cylindrical steel member and a resin layer or the like coated on the inner periphery of the member. The second bearing portion 17 may be made of the same material as the inner housing 16 and may be integral with the shaft support member 40. The second bearing portion 17 may be made of a bearing other than a plain bearing.

[0056] The outer diameter of the cylindrical portion 161 of the inner housing 16 is smaller than the inner diameter of the first housing portion 124 of the motor housing 12. The outer diameter of the flange portion 162 of the inner housing 16 is larger than the inner diameter of the first housing portion 124 of the motor housing 12 and smaller than the inner diameter of the second housing portion 125.

[0057] The inner housing 16 has a flange portion 162 which faces a stator facing surface 421 which faces the stator 54 of the shaft support member 40 in the axial direction Dax. The flange portion 162 is fixed to the stator facing surface 421 by a fixing bolt 18.

[0058] Specifically, the stator facing surface 421 is formed with a plurality of female threaded holes into which the fixing bolts 18 can be screwed. The flange portion 162 is formed with a plurality of insertion holes SH, through which the fixing bolts 18 are inserted, in a manner corresponding to the female threaded holes. The inner housing 16 is fixed to the shaft support member 40 by the fixing bolts 18 passing through the insertion holes SH of the flange portion 162 and being screwed into the female threaded holes of the stator facing surface 421.

[0059] Although not shown, the inner housing 16 has an inside-outside communicating portion penetrating the inside and outside above the axis CL of the rotating shaft 20 in the vertical direction Dg. The inside of the inner housing 16 and a gap space 164 between the motor housing 12 and the inner housing 16 are partitioned by the cylindrical portion 161 and the bottom portion 163a below the axis CL in the vertical direction Dg so that the inside and outside of the inner housing 16 are not communicated with each other. As a result, the refrigerant sucked from the suction port of the motor housing 12 into the gap space 164 between the motor housing 12 and the inner housing 16 is supplied to the inside of the inner housing 16 via the inside-outside communicating portion.

[0060] The inner housing 16, the shaft support member 40, and the compression section 30 are arranged in this order in the axial direction Dax. The portion of the inner housing 16 and the compression section 30 located closest to one side of the axial direction Dax is defined as the first end E1, the portion located closest to the other side of the axial direction Dax is defined as the second end E2, and the portion located between the first end E1 and the second end E2 is defined as the intermediate portion E3. At this time, the inner housing 16 and the compression section 30 have a part of the intermediate portion E3 fixed to a fixing portion FP set in the motor housing 12, and are separated from other portions in the radial direction Dr except for the fixing portion FP. Note that the intermediate portion E3 does not include the first end E1 and the second end E2.

[0061] The inner housing 16 and the compression unit 30 are fixed to the fixing part FP at a portion between the stator 54, which is a heavy part, and the compression unit 30. The end face of the stator 54 that faces the stator facing surface 421 in the axial direction Dax is defined as a core end face 543. In this case, it is preferable that the inner housing 16 and the compression unit 30 are fixed to the fixing part FP at a portion of the motor housing 12 that is in a range from the stator facing surface 421 to the core end face 543. The core end face 543 is the end face of the stator core 541 that faces the stator facing surface 421 in the axial direction Dax.

[0062] In this embodiment, the stepped surface 123 of the motor housing 12 constitutes a fixing portion FP that fixes the inner housing 16 and the compression portion 30. The inner housing 16, the shaft support member 40, and the compression portion 30 are fixed to the motor housing 12 by a mounting bolt 37.

[0063] Specifically, the fixed scroll 32 and the discharge plate 36 have insertion holes SH1, through which the mounting bolts 37 are inserted, formed in the outer peripheral portions of the fixed scroll 32 and the discharge plate 36 that overlap the stepped surface 123 in the axial direction Dax. The fixed scroll 32 and the discharge plate 36 are fixed to the stepped surface 123 of the motor housing 12 via the shaft support member 40 in a state spaced apart from the second housing portion 125.

[0064] Further, the shaft support member 40 has an insertion hole SH2 through which the mounting bolt 37 is inserted, formed in a large diameter portion 42 that overlaps with the step surface 123 in the axial direction Dax. The shaft support member 40 is fixed to the step surface 123 of the motor housing 12 via the flange portion 162 of the inner housing 16 in a state separated from the second housing portion 125. In this embodiment, the stator facing surface 421 and the flange portion 162 are in contact with each other over substantially the entire portions that overlap with the step surface 123 in the axial direction Dax.

[0065] Furthermore, the inner housing 16 has a flange portion 162 that overlaps with the step surface 123 in the axial direction Dax, and an insertion hole SH3 through which the mounting bolt 37 is inserted is formed in the flange portion 162. The inner housing 16 is fixed to the step surface 123 of the motor housing 12 with a portion of the inner housing 16 other than the flange portion 162 separated from the first housing portion 124, as shown in Fig. 3. In this embodiment, substantially the entire portion of the flange portion 162 that overlaps with the step surface 123 in the axial direction Dax is in contact with the step surface 123.

[0066] Here, the length of the inner housing 16 in the axial direction Dax is smaller than the length of the axial direction Dax from the step surface 123 to the first bottom wall portion 121 in the motor housing 12. As a result, in the inner housing 16, a gap is formed between the support portion 163 and the motor housing 12.

[0067] Next, the flow of an assembly operation for each component part of the compressor ECP will be described with reference to Figures 4 to 7. In Figures 5 to 7, in order to avoid complicating the drawings, some of the reference numerals corresponding to the components are omitted.

[0068] 4, the assembly work of the compressor ECP includes assembly steps such as a preparation step, a first assembly step, a second assembly step, and a third assembly step. In the assembly work, first, in the preparation step of step S10, the components of the compressor ECP, that is, the housing 10, the compression section 30, the shaft support member 40, and the electric motor 50, are prepared. In this preparation step, for example, the inner housing 16 with the stator 54 fixed thereto is prepared.

[0069] In the subsequent first assembly step of step S20, the inner housing 16 is fixed to the shaft support member 40. Specifically, in the first assembly step, as shown in Fig. 5, the fixing bolt 18 is passed through the insertion hole SH of the flange portion 162 from the other side to one side in the axial direction Dax and screwed into the female screw hole of the shaft support member 40. In this first assembly step, when the inner housing 16 is fixed to the shaft support member 40, the axis of the first bearing portion 411 and the axis of the second bearing portion 17 are made to coincide with each other. Note that, although only one fixing bolt 18 is shown in Fig. 5, the inner housing 16 is actually fixed to the shaft support member 40 by a plurality of fixing bolts 18.

[0070] In the second assembly step of step S30, the inner housing 16, the shaft support member 40, and the compression section 30 are fixed to the motor housing 12. Specifically, in the second assembly step, as shown in FIG. 6, the mounting bolt 37 is passed through the insertion holes SH1, SH2, and SH3 of the inner housing 16, the shaft support member 40, and the compression section 30 from one side to the other side in the axial direction Dax, and screwed into the female screw hole of the step surface 123. At this time, the inner housing 16, the shaft support member 40, and the compression section 30 are fixed to the step surface 123 so that the inner housing 16, the shaft support member 40, and the compression section 30 are separated from other parts of the motor housing 12 and the discharge housing 14 except for the fixed part FP. Note that although only one mounting bolt 37 is shown in FIG. 6, the inner housing 16, the shaft support member 40, and the compression section 30 are actually fixed to the motor housing 12 by a plurality of mounting bolts 37.

[0071] In the subsequent third assembly step of step S40, the discharge housing 14 is fixed to the motor housing 12. Specifically, in the third assembly step, as shown in Fig. 7, the fastening bolt 15 is passed through an insertion hole SH4 formed in the discharge housing 14 from one side to the other side in the axial direction Dax, and screwed into a female threaded hole formed in the open end surface 126 of the motor housing 12. Note that although only one fastening bolt 15 is shown in Fig. 7, in reality, the discharge housing 14 is fixed to the motor housing 12 by a plurality of fastening bolts 15.

[0072] Next, the operation of the compressor ECP will be described. When power is supplied to the stator 54 of the electric motor 50 from an inverter (not shown), the compressor ECP rotates the rotor 52 and the rotary shaft 20, and the orbiting scroll 34 revolves around the rotary shaft 20. This drives the compression section 30, and the low-temperature, low-pressure refrigerant that has passed through the evaporator EV is sucked into the housing 10 from the suction port.

[0073] Specifically, the refrigerant flows into a gap space 164 formed between the motor housing 12 and the inner housing 16, and is then introduced into the inside of the inner housing 16 via the interior-exterior communicating part. The interior-exterior communicating part is formed above the axis CL of the rotating shaft 20 in the inner housing 16. The refrigerant is introduced into the inside of the inner housing 16 as a gas refrigerant having a low specific gravity via the interior-exterior communicating part, while liquid refrigerant having a high specific gravity is stored in the gap space 164.

[0074] The refrigerant introduced into the inner housing 16 passes through the gaps between various components of the electric motor 50 and the refrigerant suction passage provided in the shaft support member 40, and is then sucked into the working chamber 31 through the refrigerant suction port formed on the outer periphery of the fixed scroll 32. The refrigerant supplied to the working chamber 31 is compressed as the volume of the working chamber 31 decreases. When the pressure in the working chamber 31 reaches the valve opening pressure of the reed valve, the refrigerant compressed in the working chamber 31 is discharged from the discharge hole 323 of the fixed scroll 32 to the muffler chamber 361. The refrigerant discharged to the muffler chamber 361 flows into the inside of the discharge housing 14 from the outlet provided in the discharge plate 36, and is then discharged from the discharge port provided in the discharge housing 14 as discharge refrigerant for the compressor ECP. At this time, the lubricating oil contained in the discharge refrigerant is separated by the oil separator provided in the discharge port, and falls by its own weight to be stored on the lower side of the discharge housing 14. The lubricating oil is supplied to each sliding part inside the housing 12 via the oil supply passage 24 etc. due to the pressure difference of the refrigerant inside the housing 10. A part of the lubricating oil supplied to the sliding parts flows into the gap space 164, and is guided to the refrigerant introduction passage via a communication flow passage that communicates the gap space 164 with the refrigerant introduction passage.

[0075] Here, in the electric motor 50, vibration occurs in the stator 54 due to an electromagnetic force generated by the interaction between the magnetic field of the permanent magnet provided in the rotor 52 and the current flowing through the coil 542 provided in the stator 54. This vibration of the stator 54 is not transmitted directly to the motor housing 12, but is transmitted from the fixed part FP to the motor housing 12 via the inner housing 16.

[0076] Furthermore, the compression section 30 compresses the low-temperature, low-pressure refrigerant in the working chamber 31, and discharges it as a high-temperature, high-pressure refrigerant. The specifications of this compression section 30 are determined so that there is as little imbalance as possible with respect to the axis CL of the rotating shaft 20, but in the actual finished product, it is difficult to perfectly align the centers of gravity and eliminate the imbalance, and there may be variation. Such variation causes imbalance with respect to the axis CL of the rotating shaft 20, which generates vibration.

[0077] Furthermore, the compression section 30 compresses the refrigerant as the volume of the working chamber 31 decreases. At that time, the contact points of the tooth sides of the fixed scroll 32 and the orbiting scroll 34 that form the working chamber 31 do not move smoothly but move slightly intermittently due to variations in the accuracy of the spirals of the scrolls 32 and 34, causing vibrations.

[0078] Taking these factors into consideration, in the compressor ECP of this embodiment, the inner housing 16 and a part of the intermediate portion E3 in the compression section 30 are fixed to a fixing portion FP set in the motor housing 12.

[0079] This allows the distance between the position supporting the inner housing 16 and the compression section 30 and the position where vibration occurs to be smaller than when the inner housing 16 and the compression section 30 are fixed in a cantilever-like manner. This reduces the vibration of the electric motor 50 and the compression section 30 and makes it difficult for it to be transmitted to the motor housing 12, thereby suppressing noise.

[0080] Furthermore, in the compressor ECP, the inner housing 16 and a part of the intermediate portion E3 in the compression portion 30 are separated from other portions except for the fixed portion FP in the radial direction Dr of the rotating shaft 20. In this manner, if there is a gap between the inner housing 16 and the compression portion 30 and the motor housing 12 and the discharge housing 14, the vibration of the stator 54 and the compression portion 30 is suppressed from being directly transmitted to the motor housing 12 and the discharge housing 14. Therefore, the compressor ECP of this embodiment can suppress vibration and noise.

[0081] In addition, the rotating shaft 20 has a double-supported structure in which it is supported by the first bearing portion 411 and the second bearing portion 17. This allows the sliding area of ​​each of the bearing portions 411, 17 to be set small, making it easier to stably supply lubricating oil to the entire sliding surface under conditions ranging from low to high rotation speeds of the rotating shaft 20, thereby ensuring reliability.

[0082] Moreover, the compressor ECP of this embodiment has the following features.

[0083] (1) The inner housing 16 and the compression unit 30 are fixed to the fixing part FP at a portion in the axial direction Dax ranging from the stator facing surface 421 to the core end surface 543. This means that the compression unit 30 and the inner housing 16 are fixed to the motor housing 12 between the center of gravity of the stator 54, which is a heavy part, and the center of gravity of the compression unit 30. This makes it possible to reduce the distance between the position supporting the inner housing 16 and the compression unit 30 and the center of gravity of the stator 54 and the compression unit 30, respectively, and therefore makes it possible to reduce vibration of the stator 54 and the compression unit 30.

[0084] Although not shown, the first bottom wall portion 121 of the motor housing 12 is provided with an airtight terminal (i.e., a sealed terminal) for supplying power from the inverter to the stator 54 of the electric motor 50. Also, the discharge housing 14 is provided with an oil separator at the refrigerant discharge port. In this way, the motor housing 12 and the discharge housing 14 are connected in part to components constituting the interface of the compression section 30 and the electric motor 50, but gaps are generated in other areas. Therefore, the transmission of vibration from the stator 54 and the compression section 30 is sufficiently suppressed. The airtight terminal may be formed in, for example, the first housing portion 124 of the first outer peripheral wall portion 122, instead of the first bottom wall portion 121 of the motor housing 12.

[0085] (2) The inner housing 16 has a cylindrical tube portion 161 to which the stator 54 is fixed, and a flange portion 162 extending from one end 161a of the tube portion 161 close to the compression portion 30 in a direction away from the rotating shaft 20. The inner housing 16 includes a support portion 163 that extends from the other end 161b located opposite to the one end 161a of the tube portion 161 toward the rotating shaft 20 and supports the second bearing portion 17. A step surface 123 that intersects with the axial direction Dax is formed on the inner peripheral side of the motor housing 12 at a portion facing the inner housing 16, and the flange portion 162, the shaft support member 40, and the compression portion 30 are fixed to the step surface 123 with mounting bolts 37.

[0086] If the inner housing 16 is simply a cylinder with both ends open, when the stator 54 vibrates, the inner housing 16 also vibrates in response to the vibration, which may cause slight deformation. Such deformation is undesirable because it increases the vibration transmitted from the inner housing 16 to the motor housing 12. The same applies when the inner housing 16 is configured to partially support the stator 54 with a plurality of plate-shaped support pieces.

[0087] In contrast, in the compressor ECP of the present embodiment, the inner housing 16 is substantially cup-shaped, having a tubular portion 161, a support portion 163, and a flange portion 162. This makes it easier to ensure rigidity compared to a compressor simply having a cylindrical shape, and makes it possible to suppress deformation of the inner housing 16 due to vibration of the stator 54.

[0088] In addition, since the support portion 163 is formed integrally with the cylindrical portion 161 of the inner housing 16, it is possible to increase the rigidity of the support portion 163 and further suppress deformation due to the load received by the second bearing portion 17 from the rotating shaft 20. This makes it possible to reduce the amount of imbalance of the axis CL of the rotating shaft 20.

[0089] In addition, the inner housing 16, the shaft support member 40, and the compression section 30 are fixed to the stepped surface 123 of the motor housing 12. This makes it possible to reduce the contact area between the inner housing 16 and the compression section 30 and the motor housing 12 and the discharge housing 14, compared to a case in which the stator 54 and the compression section 30 are fixed to the inner circumferential surfaces of the motor housing 12 and the discharge housing 14. This makes it difficult for vibrations of the stator 54 and the compression section 30 to be transmitted to the motor housing 12 and the discharge housing 14, so that sound and vibrations emitted to the outside of the motor housing 12 and the discharge housing 14 can be suppressed.

[0090] (3) The second bearing portion 17 is supported relative to the inner housing 16. The inner housing 16 has a flange portion 162 fixed to the shaft support member 40 by a fixing bolt 18.

[0091] According to this, when the shaft support member 40 and the inner housing 16 are fixed, the axis of the first bearing portion 411 and the axis of the second bearing portion 17 can be adjusted to be coaxial. For example, even if a slight deformation occurs in the inner housing 16 when the stator 54 is fixed to the inner housing 16 by shrink fitting or press fitting, the axis of the first bearing portion 411 and the axis of the second bearing portion 17 can be adjusted later to be coaxial. In this way, the gap between the stator 54 and the rotor 52 can be made uniform to reduce bias in magnetic flux and to reduce imbalance due to whirling of the rotating shaft 20, so that vibration can be sufficiently suppressed.

[0092] Also, the relative inclination between each of the bearings 411, 17 and the rotating shaft 20 can be reduced, ensuring reliability. Furthermore, the axis of each of the bearings 411, 17 can be realized by a simple and highly rigid structure such as the fixing bolt 18, allowing for weight reduction and a simplified shape.

[0093] Furthermore, with this configuration, there is no need to provide a female screw for fixing the second bearing portion 17 to the inner housing 16. This allows the inner housing 16 to be lighter in weight and have a simpler shape.

[0094] (4) The inner housing 16 is made of the same metal material as the stator 54. This makes it possible to prevent the fixed state between the inner housing 16 and the stator 54 from becoming unstable due to the difference in linear expansion coefficient between the inner housing 16 and the stator 54. For example, when the stator 54 is fitted and fixed to the inner circumferential surface of the inner housing 16, the interference can be appropriately set.

[0095] Here, the term "same kind of metallic material" refers to metallic materials that have the same most abundant element in their chemical composition. Note that the term "same kind of metallic material" includes not only metallic materials that have the exact same chemical composition, but also metallic materials that have the same designation in standards.

[0096] (5) When the stator 54 is fixed to the motor housing 12 and the discharge housing 14 that constitute the outer housing by shrink fitting, the interference of the shrink fitting needs to be set large in consideration of deformation due to pressure inside the housing 10.

[0097] In contrast, if the stator 54 is fixed to the inner housing 16 as in this embodiment, the motor housing 12 and the discharge housing 14 can be simplified. Furthermore, if the stator 54 is fixed to the inner housing 16, restrictions on the shapes of the motor housing 12 and the discharge housing 14 can be reduced. This makes it possible to connect multiple elemental parts, such as a pressure adjustment valve, a refrigerant path, a water path, a heat exchanger, etc., to the motor housing 12 and the discharge housing 14.

[0098] Here, since the pressure from the inside of the motor housing 12 acts on both the inner and outer circumferential surfaces of the cylindrical portion 161 of the inner housing 16, the pressure acting on the cylindrical portion 161 is offset. This makes it difficult for the cylindrical portion 161 to deform due to the pressure from the inside of the motor housing 12. This makes it possible to reduce the interference associated with shrink-fitting or press-fitting the stator 54 into the cylindrical portion 161 of the inner housing 16.

[0099] (Modification of the first embodiment) In the above-described first embodiment, the space in the housing 10 in which the electric motor 50 is disposed is in a low-pressure, low-temperature atmosphere, but the compressor ECP is not limited to this. For example, the compressor ECP may be configured such that the refrigerant discharged from the compression section 30 is introduced into the space in the housing 10 in which the electric motor 50 is disposed, and the space is in a high-pressure, high-temperature atmosphere. This also applies to the following embodiments.

[0100] Second embodiment Next, a second embodiment will be described with reference to Figures 8 to 10. In this embodiment, differences from the first embodiment will be mainly described.

[0101] As shown in FIG. 8, the shaft support member 40 and the flange portion 162 of this embodiment have a contact portion CP1 in contact with each other and a non-contact portion NP1 spaced a predetermined distance apart at a portion where the shaft support member 40 and the flange portion 162 overlap with the step surface 123 in the axial direction Dax.

[0102] 9 and 10, the non-contact portion NP1 is provided on the stator-facing surface 421 of the shaft support member 40, and is formed by a recess 422 recessed in a direction away from the step surface 123. Note that Fig. 9 is a diagram showing one end face of the shaft support member 40 in the axial direction Dax, but for convenience, the female thread portion into which the fixing bolt 18 is screwed is omitted.

[0103] The contact portion CP1 is provided on the stator facing surface 421 of the shaft support member 40, and is formed by a cylindrical protrusion 423 protruding in a direction approaching the step surface 123. The protrusion 423 constituting the contact portion CP1 is set around the insertion hole SH2 through which the mounting bolt 37 is inserted. In other words, the contact portion CP1 is set at a portion overlapping the head of the mounting bolt 37 in the axial direction Dax. Note that a groove depth T1, which is the length from the opening to the bottom of the recess 422, is approximately the same size as the protruding height of the protrusion 423.

[0104] The rest is the same as in the first embodiment. The compressor ECP of the present embodiment can obtain the same effects as in the first embodiment, which are achieved by a common configuration with the first embodiment or an equivalent configuration.

[0105] The compressor ECP of this embodiment has the following features.

[0106] (1) In this embodiment, the shaft support member 40 and the flange portion 162 have a contact portion CP1 and a non-contact portion NP1 that are in contact with each other. The contact portion CP1 is provided around a portion of the shaft support member 40 and the flange portion 162 through which the mounting bolt 37 is inserted. This reduces the contact area between the shaft support member 40 and the motor housing 12 via the flange portion 162, making it difficult for vibrations of the compression portion 30 to be transmitted to the motor housing 12. As a result, sound and vibrations radiated to the outside from the motor housing 12 and the discharge housing 14 can be suppressed.

[0107] (Modification of the second embodiment) In the second embodiment, the recessed portion 422 and the protruding portion 423 are provided on the stator facing surface 421 of the shaft support member 40, but the present invention is not limited to this and they may be formed in a portion of the flange portion 162 that faces the shaft support member 40. In addition, the contact portion CP1 may be realized by, for example, a metal washer or the like disposed between the stator facing surface 421 of the shaft support member 40 and the flange portion 162. The same applies to the following embodiments.

[0108] Third embodiment Next, a third embodiment will be described with reference to Figures 11 to 13. In this embodiment, differences from the second embodiment will be mainly described.

[0109] As shown in Fig. 11 and Fig. 12, the non-contact portion NP1 is provided with an elastically deformable elastic member EM1 in a compressed state in the axial direction Dax. The elastic member EM1 is made of, for example, a rubber material. In Fig. 12, the elastic member EM1 is hatched with dots to clarify the position of the elastic member EM1.

[0110] 13, the elastic member EM1 has a thickness T2 greater than the groove depth T1 at the non-contact portion NP1.

[0111] The rest is the same as in the second embodiment. The compressor ECP of this embodiment can obtain the same effects as in the second embodiment, which are achieved by a common configuration with the second embodiment or an equivalent configuration.

[0112] The compressor ECP of this embodiment has the following features.

[0113] (1) In the non-contact portion NP1, an elastically deformable elastic member EM1 is disposed in a state compressed in the axial direction Dax. In this manner, if the elastic member EM1 is disposed between the flange portion 162 and the shaft support member 40, vibration between the flange portion 162 and the shaft support member 40 is damped by the elastic member EM1.

[0114] This makes it difficult for vibrations of the electric motor 50 and the compression section 30 to be transmitted to the motor housing 12, etc., thereby making it possible to suppress noise and vibrations radiated to the outside from the motor housing 12, etc. For example, a high-order vibration mode called a local vibration or the like may occur on the surface of the compression section 30, but this vibration can be reduced by the elastic member EM1.

[0115] Furthermore, in the compressor ECP of this embodiment, the mounting bolts 37 also function as part of the vibration-isolating members. This makes it possible to reduce the number of bolts used in the compressor ECP as a whole. This contributes to reducing the number of parts of the compressor ECP and reducing costs.

[0116] (Modification of the third embodiment) In the third embodiment, the elastic member EM1 is made of a rubber material, but the elastic member EM1 may be made of a material other than a rubber material. In the third embodiment, the elastic member EM1 is disposed over the entire non-contact portion NP1, but the present invention is not limited to this, and the elastic member EM1 may be disposed in only a part of the non-contact portion NP1.

[0117] (Fourth embodiment) Next, a fourth embodiment will be described with reference to Fig. 14. In this embodiment, differences from the second and third embodiments will be mainly described.

[0118] As shown in FIG. 14, the step surface 123 and the flange portion 162 of the motor housing 12 in this embodiment have a contact portion CP2 that contacts with each other in the axial direction Dax, and a non-contact portion NP2 that is spaced apart from each other with a predetermined gap therebetween.

[0119] The convex portion constituting the contact portion CP2 is provided on the stepped surface 123 of the motor housing 12. Specifically, the contact portion CP2 is set around a portion of the stepped surface 123 through which the mounting bolt 37 is inserted.

[0120] In addition, the elastically deformable elastic member EM2 is disposed in the non-contact portion NP2 in a state of being compressed in the axial direction Dax. The elastic member EM1 is made of, for example, a rubber material. Although not shown, the thickness of the elastic member EM1 is greater than the groove depth in the non-contact portion NP2. As a result, the elastic member EM1 is compressed by receiving the axial force of the mounting bolt 37.

[0121] The rest is the same as in the third embodiment. The compressor ECP of the present embodiment can obtain the effects achieved by the configuration common to the second and third embodiments or the equivalent configuration, similarly to the second and third embodiments.

[0122] Moreover, the compressor ECP of this embodiment has the following features.

[0123] (1) Step surface 123 and flange portion 162 have contact portion CP2 and non-contact portion NP2. Contact portion CP2 is provided around the portion of step surface 123 and flange portion 162 through which mounting bolt 37 is inserted. This reduces the contact area between motor housing 12 and flange portion 162 and makes it difficult for vibrations of stator 54 and compression portion 30 to be transmitted to motor housing 12, etc., thereby suppressing sound and vibrations radiated to the outside from motor housing 12, etc.

[0124] (2) In addition, since the elastically deformable elastic member EM2 is disposed in the non-contact portion NP2, the elastic member EM2 damps vibrations between the motor housing 12 and the flange portion 162. This also makes it difficult for vibrations of the electric motor 50 and the compression portion 30 to be transmitted to the motor housing 12, etc.

[0125] (Modification of the fourth embodiment) In the fourth embodiment, the convex portion constituting the contact portion CP2 is provided on the stepped surface 123 of the motor housing 12, but the present invention is not limited to this and may be formed on a portion of the flange portion 162 facing the stepped surface 123. In addition, the contact portion CP2 may be realized by, for example, a metal washer or the like disposed between the stepped surface 123 and the flange portion 162. The same applies to the subsequent embodiments.

[0126] In the fourth embodiment, the elastic member EM2 is made of a rubber material, but the elastic member EM2 may be made of a material other than a rubber material. The elastic member EM2 may be disposed over the entire area of ​​the non-contact portion NP1, or may be disposed over a part of the non-contact portion NP1. In the fourth embodiment, the elastic member EM2 is not an essential component and may be omitted.

[0127] Fifth embodiment Next, a fifth embodiment will be described with reference to Fig. 15. In this embodiment, differences from the first embodiment will be mainly described.

[0128] 15, the motor housing 12 of this embodiment does not have the step surface 123 described in the first embodiment, and the inner diameter of the first outer peripheral wall portion 122 is approximately constant. Also, the discharge housing 14 has a second outer peripheral wall portion 142 extending to the other side in the axial direction Dax so that the fixed scroll 32 and the discharge plate 36 are housed therein. The motor housing 12 and the discharge housing 14 of this embodiment are fixed by fastening bolts 15 with their opening edges abutting against the shaft support member 40.

[0129] The shaft support member 40 has an outer diameter of a large diameter portion 42 that is approximately the same as the outer diameter of the motor housing 12 and the outer diameter of the discharge housing 14. The large diameter portion 42 is provided with an insertion hole SH4 through which the fastening bolt 15 is inserted at a portion facing the opening edges of the motor housing 12 and the discharge housing 14 in the axial direction Dax. The shaft support member 40 is fixed to the motor housing 12 and the discharge housing 14 by the fastening bolt 15 while being sandwiched between the motor housing 12 and the discharge housing 14.

[0130] The inner housing 16 does not include the flange portion 162 described in the first embodiment. The outer diameter of the inner housing 16 is equal to the outer diameter of the compression section 30. The inner housing 16 has a cylindrical portion 161 whose thickness in the radial direction Dr is greater than that described in the first embodiment. The inner housing 16 has a plurality of female screw holes formed on the opening edge of the cylindrical portion 161, into which the mounting bolts 37 can be screwed.

[0131] The inner housing 16, together with the fixed scroll 32 and the discharge plate 36, is fixed to the large diameter portion 42 of the shaft support member 40 by screwing the mounting bolts 37 into female threaded holes provided in the cylindrical portion 161. The inner housing 16 and the compression portion 30 of this embodiment are fixed to the motor housing 12 and the discharge housing 14 via the shaft support member 40. In this embodiment, the opening edges of the motor housing 12 and the discharge housing 14 form the fixing portion FP.

[0132] The rest is the same as in the first embodiment. The compressor ECP of the present embodiment can obtain the same effects as in the first embodiment, which are achieved by a common configuration with the first embodiment or an equivalent configuration.

[0133] Moreover, the compressor ECP of this embodiment has the following features.

[0134] (1) The compressor ECP can be configured to be smaller in size than the compressor described in the first embodiment because the outer diameter of the inner housing 16 and the outer diameter of the compression section 30 can be made the same size.

[0135] In addition, since the inner housing 16 and the compression section 30 are attached to the opening edges of the motor housing 12 and the discharge housing 14 via the shaft support member 40, it is possible to reduce the effects of vibration of the inner housing 16 and the compression section 30. As a result, it is possible to reduce vibration and noise of the compressor ECP.

[0136] Sixth embodiment Next, a sixth embodiment will be described with reference to Fig. 16. In this embodiment, differences from the fifth embodiment will be mainly described.

[0137] 16, the motor housing 12 of this embodiment does not have a stepped surface 123, and the inner diameter of the first outer peripheral wall portion 122 is generally constant, as in the fifth embodiment. The fixed scroll 32 and the discharge plate 36 are housed inside the discharge housing 14. The motor housing 12 and the discharge housing 14 of this embodiment are fixed together by fastening bolts 15 with their opening edges abutting against the flange portion 162 and the shaft support member 40, respectively.

[0138] The large diameter portion 42 and the flange portion 162 of the shaft support member 40 have outer diameters that are approximately the same as the outer diameters of the motor housing 12 and the discharge housing 14. The large diameter portion 42 has an insertion hole SH4 through which the fastening bolt 15 is inserted at a portion facing the flange portion 162 and the opening edge of the discharge housing 14 in the axial direction Dax.

[0139] The shaft support member 40 and the inner housing 16 are fixed to the motor housing 12 and the discharge housing 14 by fastening bolts 15 with the large diameter portion 42 and the flange portion 162 sandwiched between the motor housing 12 and the discharge housing 14. In this embodiment, the opening edges of the motor housing 12 and the discharge housing 14 form the fixing portion FP.

[0140] The rest is the same as in the fifth embodiment. The compressor ECP of this embodiment can obtain the same effects as in the fifth embodiment, which are achieved by a common configuration with the fifth embodiment or an equivalent configuration.

[0141] Seventh embodiment Next, a seventh embodiment will be described with reference to Figures 17 and 18. In this embodiment, differences from the fifth embodiment will be mainly described.

[0142] 17, the motor housing 12 of this embodiment does not have a stepped surface 123, and the inner diameter of the first outer peripheral wall portion 122 is generally constant, as in the fifth embodiment. The discharge housing 14 accommodates the fixed scroll 32 and the discharge plate 36 inside. The motor housing 12 and the discharge housing 14 of this embodiment are fixed together by fastening bolts 15 with their opening edges abutting against the shaft support member 40.

[0143] The inner housing 16 includes a first cylindrical portion 165, a second cylindrical portion 166, and a support portion 167. The first cylindrical portion 165 and the second cylindrical portion 166 are formed of separate members. The second cylindrical portion 166 and the support portion 167 are integrally formed.

[0144] The first cylindrical portion 165 and the second cylindrical portion 166 are cylindrical members to which the stator 54 is fixed. The first cylindrical portion 165 and the second cylindrical portion 166 have substantially the same size in the radial direction Dr. The first cylindrical portion 165 is integrally formed with the large diameter portion 42 of the shaft support member 40. The first cylindrical portion 165 protrudes from the stator facing surface 421 of the shaft support member 40 toward the stator 54. The second cylindrical portion 166 is formed of a cylindrical collar.

[0145] The support portion 167 has a circular ring-shaped bottom portion 167a and a cylindrical second boss portion 167b provided at the center of the bottom portion 167a. The bottom portion 167a and the second boss portion 167b are configured as an integrally molded product.

[0146] The second cylindrical portion 166, the support portion 167, and the stator 54 are formed with insertion holes SH5 and SH6 through which bolts BT1 are inserted for fixing the inner housing 16 and the stator 54 to the shaft support member 40. The first cylindrical portion 165 is also formed with a plurality of female screw holes into which the bolts BT1 can be screwed.

[0147] 18, the stator 54 has a plurality of bulging portions 544 that bulge in a direction away from the rotating shaft 20 on the outer circumferential portion of a stator core 541. A plurality of insertion holes SH6 through which the bolts BT1 are inserted are formed in the bulging portions 544.

[0148] The stator 54 is fixed to the inner housing 16 by screwing the bolt BT1 into a female threaded hole provided in the first cylindrical portion 165 while the bolt BT1 is inserted through the second cylindrical portion 166, the support portion 167, and the insertion holes SH5 and SH6 of the stator 54. The first cylindrical portion 165 of the inner housing 16 is integrally formed with the shaft support member 40. Therefore, the inner housing 16 is fixed to the shaft support member 40.

[0149] In this manner, the inner housing 16 and the compression section 30 of this embodiment are fixed to the motor housing 12 and the discharge housing 14 via the shaft support member 40. In this embodiment, the opening edges of the motor housing 12 and the discharge housing 14 respectively form the fixing portion FP.

[0150] The rest is the same as in the fifth embodiment. The compressor ECP of this embodiment can obtain the same effects as in the fifth embodiment, which are achieved by a common configuration with the fifth embodiment or an equivalent configuration.

[0151] Moreover, the compressor ECP of this embodiment has the following features.

[0152] (1) In the compressor ECP of the present embodiment, the stator 54 is fixed to the inner housing 16 by the bolts BT1. Therefore, distortion of the stator 54 when the stator 54 is fixed to the inner housing 16 can be suppressed.

[0153] (2) Furthermore, when the stator 54, the shaft support member 40, and the inner housing 16 are fixed together with the bolt BT1, the axis of the first bearing portion 411 and the axis of the second bearing portion 17 can be adjusted to be coaxial with each other.

[0154] Eighth embodiment Next, an eighth embodiment will be described with reference to Fig. 19. In this embodiment, differences from the first embodiment will be mainly described.

[0155] 19, the motor housing 12 and the discharge housing 14 are fixed by fastening bolts 15 with their opening edges butted against each other. The motor housing 12 of this embodiment has a stepped surface 123 formed thereon, as in the first embodiment, and the fixed scroll 32 and the discharge plate 36 are fixed to the stepped surface 123 via the shaft support member 40.

[0156] As in the seventh embodiment, the inner housing 16 includes a first cylindrical portion 165, a second cylindrical portion 166, and a support portion 167 that are integral with the shaft support member 40. The first cylindrical portion 165, the second cylindrical portion 166, and the support portion 167 are each formed from a separate member.

[0157] The stator 54 is fixed to the inner housing 16 by the bolts BT1, similar to the seventh embodiment. Moreover, the inner housing 16 is fixed to the shaft support member 40, similar to the seventh embodiment.

[0158] The outer diameter of the large diameter portion 42 of the shaft support member 40 is set to be substantially the same as the dimensions of the fixed scroll 32 and the discharge plate 36. The shaft support member 40, together with the compression section 30, is fixed to the motor housing 12 by a mounting bolt 37.

[0159] In this embodiment, the inner housing 16 and the compression portion 30 are fixed to the stepped surface 123 of the motor housing 12 by the mounting bolt 37 via the shaft support member 40. In this embodiment, the stepped surface 123 of the motor housing 12 constitutes the fixing portion FP.

[0160] The rest is the same as in the first embodiment. The compressor ECP of the present embodiment can obtain the same effects as in the first embodiment, which are achieved by a common configuration with the first embodiment or an equivalent configuration.

[0161] Moreover, the compressor ECP of this embodiment has the following features.

[0162] (1) In the compressor ECP, the stator 54 is fixed to the inner housing 16 by the bolts BT1. Therefore, distortion of the stator 54 when the stator 54 is fixed to the inner housing 16 can be suppressed.

[0163] (2) Furthermore, when the stator 54, the shaft support member 40, and the inner housing 16 are fixed together with the bolt BT1, the axis of the first bearing portion 411 and the axis of the second bearing portion 17 can be adjusted to be coaxial with each other.

[0164] Ninth embodiment Next, a ninth embodiment will be described with reference to Fig. 20. In this embodiment, differences from the first embodiment will be mainly described.

[0165] 20, the support portion 163 is configured such that a portion connected to the cylindrical portion 161 and a portion supporting the second bearing portion 17 are separate bodies. Specifically, the support portion 163 has an annular first bottom portion 163a connected to the other end portion 161b of the cylindrical portion 161, a second bottom portion 163c fixed to the first bottom portion 163a by a bolt BT2, and a cylindrical second boss portion 163b formed integrally with the second bottom portion 163c. The second bearing portion 17 is formed on the inner peripheral side of the second boss portion 163b.

[0166] The rest is the same as in the first embodiment. The compressor ECP of the present embodiment can obtain the same effects as in the first embodiment, which are achieved by a common configuration with the first embodiment or an equivalent configuration.

[0167] Moreover, the compressor ECP of this embodiment has the following features.

[0168] (1) Since the inner housing 16 is integrally constructed with the tubular portion 161 and the flange portion 162, it is easier to ensure rigidity compared to a case having a simple cylindrical shape, and deformation of the inner housing 16 due to vibration of the stator 54 can be suppressed.

[0169] (2) Furthermore, in the compressor ECP of this embodiment, when the second bottom portion 163c is fixed to the first bottom portion 163a with the bolt BT2, the axis of the first bearing portion 411 and the axis of the second bearing portion 17 can be adjusted to be coaxial with each other.

[0170] (3) Furthermore, the second boss portion 163b on which the second bearing portion 17 is provided can be precisely machined using small parts. This contributes greatly to ensuring the accuracy of the second bearing portion 17.

[0171] (Other embodiments) Representative embodiments of the present disclosure have been described above, but the present disclosure is not limited to the above-described embodiments and can be modified in various ways, for example, as described below.

[0172] The internal housing 16 is not limited to being substantially cup-shaped, and may be, for example, cylindrical. The internal housing 16 is desirably made of the same metal material as the stator 54, but is not limited thereto, and may be, for example, made of a metal material different from that of the stator 54. A part of the internal housing 16 may be in contact with the motor housing 12 in the axial direction Dax.

[0173] The various devices constituting the compressor ECP may be fixed by elements other than bolts. For example, the flange portion 162, the shaft support member 40, and the compression portion 30 may be fixed to the step surface 123 of the motor housing 12 by elements other than the mounting bolts 37. Also, the flange portion 162 of the inner housing 16 is fixed to the shaft support member 40 by elements other than the fixing bolts 18. The first bearing portion 411 and the second bearing portion 17 may be configured as, for example, a rolling bearing instead of a sliding bearing. In addition, the second bearing portion 17 may be provided on an element other than the inner housing 16.

[0174] The compression section 30 of the compressor ECP is not limited to a scroll type having a fixed scroll 32 and an orbiting scroll 34, and may be, for example, a piston type or a vane type. A part of the compression section 30 may be in contact with the discharge housing 14 in the axial direction Dax.

[0175] In the above embodiment, the compressor ECP applied to a vehicle air conditioner has been described, but the present invention is not limited thereto, and the compressor ECP can also be applied to other air conditioners, temperature control devices for various devices, etc. In addition, the compressor ECP is not limited to a horizontally mounted structure in which the compression unit 30 and the electric motor 50 are arranged in a substantially horizontal direction.

[0176] In the above-described embodiments, it goes without saying that the elements constituting the embodiments are not necessarily essential, except in cases where it is particularly expressly stated that they are essential or where they are clearly considered to be essential in principle.

[0177] In the above-described embodiments, when numerical values ​​such as the number, values, amounts, ranges, etc. of components of the embodiments are mentioned, they are not limited to the specific numbers unless expressly stated as required or clearly limited to a specific number in principle.

[0178] In the above-described embodiments, when referring to the shapes, positional relationships, etc. of components, etc., there is no limitation to those shapes, positional relationships, etc., unless specifically stated or in principle limited to a specific shape, positional relationship, etc.

[0179] (In view of the present disclosure) According to a first aspect of the present disclosure, The electric compressor is A housing (10); A rotating shaft (20) accommodated inside the housing; a compression section (30) that compresses a fluid by rotation of the rotary shaft; an electric motor (50) having a rotor (52) that rotates integrally with the rotary shaft and a stator (54) that is fixed to the housing, and that drives the compression section; a shaft support member (40) including a first bearing portion (411) that rotatably supports the rotating shaft; a second bearing portion (17) that rotatably supports the rotating shaft relative to the housing at a position different from the first bearing portion, The housing includes: an inner housing (16) that accommodates at least a portion of the electric motor and to which the stator is fixed; a first outer housing (12) that houses the inner housing; a second outer housing (14) fixed to the first outer housing; When a portion of the inner housing and the compression portion that is located closest to one side in the axial direction of the rotating shaft is defined as a first end (E1), a portion of the inner housing and the compression portion that is located closest to the other side in the axial direction is defined as a second end (E2), and an intermediate portion (E3) that is located between the first end and the second end is defined as: The inner housing and the compression section have a portion of the intermediate portion fixed to a fixed portion (FP) set on at least one of the first outer housing and the second outer housing, and are spaced apart from other portions in the radial direction of the rotation axis except for the fixed portion.

[0180] [Second viewpoint] the shaft support member is disposed between the compression unit and the electric motor in the axial direction, and has a stator facing surface (421) of the shaft support member that faces the stator in the axial direction, The stator has a core end surface (543) that faces the stator facing surface at a predetermined interval in the axial direction, The electric compressor according to a first aspect, wherein a portion of the inner housing and the compression portion in the axial direction ranging from the stator facing surface to the core end surface is fixed to the fixing portion.

[0181] [Third Perspective] the inner housing includes a cylindrical tube portion (161) to which the stator is fixed, a flange portion (162) extending from one end (161a) of the tube portion close to the compression portion in a direction away from the rotation shaft, and a support portion (163) extending from the other end (161b) located opposite to the one end toward the rotation shaft and supporting the second bearing portion, The electric compressor according to the first or second aspect, wherein a stepped surface (123) intersecting the axial direction is formed on an inner circumferential side of the first outer housing at a portion facing the inner housing, and the flange portion, the shaft support member, and the compression portion are fixed to the stepped surface with mounting bolts (37).

[0182] [Fourth viewpoint] the shaft support member and the flange portion have a contact portion (CP1) in contact with each other and a non-contact portion (NP1) spaced apart from each other at a predetermined interval at a portion where the shaft support member and the flange portion overlap with the step surface in the axial direction, The electric compressor according to a third aspect, wherein the contact portion is provided around a portion of the shaft support member and the flange portion through which the mounting bolt is inserted.

[0183] [Fifth viewpoint] the step surface and the flange portion have a contact portion (CP2) that contacts with each other in the axial direction and a non-contact portion (NP2) that is spaced apart from each other by a predetermined distance, The electric compressor according to a third aspect, wherein the contact portion is provided around the stepped surface and a portion of the flange portion through which the mounting bolt is inserted.

[0184] [Sixth viewpoint] The electric compressor according to the fourth or fifth aspect, wherein elastic members (EM1, EM2) that are elastically deformable are arranged in the non-contact portion in a state compressed in the axial direction.

[0185] [Seventh viewpoint] the second bearing portion is supported relative to the inner housing, The electric compressor according to any one of the first to sixth aspects, wherein the flange portion of the inner housing is fixed to the shaft support member by a fixing bolt (18).

[0186] [Eighth viewpoint] The electric compressor according to any one of the first to seventh aspects, wherein the inner housing is made of the same metal material as the stator. [Explanation of symbols]

[0187] 10. Housing 12 Motor housing (first outer housing) 14 Discharge housing (second outer housing) 16 Inner housing 17 Second bearing part 20 Rotational Axis 30 Compression section 37 1st bearing part 50 Electric motor FP fixation site

Claims

1. An electric compressor, A housing (10); A rotating shaft (20) accommodated inside the housing; A compression section (30) that compresses a fluid by rotating the rotating shaft; an electric motor (50) having a rotor (52) that rotates integrally with the rotary shaft and a stator (54) that is fixed to the housing, and that drives the compression section; a shaft support member (40) including a first bearing portion (37) that rotatably supports the rotating shaft; a second bearing portion (17) that rotatably supports the rotating shaft with respect to the housing at a position different from the first bearing portion, The housing includes: an inner housing (16) that accommodates at least a portion of the electric motor and to which the stator is fixed; a first outer housing (12) that accommodates the inner housing; a second outer housing (14) secured to the first outer housing; When a portion of the inner housing and the compression portion that is located closest to one side in the axial direction of the rotating shaft is defined as a first end (E1), a portion of the inner housing and the compression portion that is located closest to the other side in the axial direction is defined as a second end (E2), and an intermediate portion (E3) that is located between the first end and the second end is defined as: an electric compressor, wherein a portion of the intermediate portion of the inner housing and the compression portion is fixed to a fixed portion (FP) set on at least one of the first outer housing and the second outer housing, and is spaced apart from other portions in the radial direction of the rotating shaft except for the fixed portion.

2. The shaft support member is disposed between the compression section and the electric motor in the axial direction, and has a stator facing surface (421) of the shaft support member that faces the stator in the axial direction, The stator has a core end surface (543) that faces the stator facing surface at a predetermined interval in the axial direction, The electric compressor according to claim 1 , wherein a portion of the inner housing and the compression portion that is in a range from the stator facing surface to the core end surface in the axial direction is fixed to the fixing portion.

3. The internal housing includes a cylindrical tube portion (161) to which the stator is fixed, a flange portion (162) extending from one end (161a) of the tube portion close to the compression portion in a direction away from the rotation shaft, and a support portion (163) extending from the other end (161b) located opposite to the one end toward the rotation shaft and supporting the second bearing portion, 2. The electric compressor according to claim 1, wherein a stepped surface (123) intersecting the axial direction is formed on an inner circumferential side of the first outer housing at a portion facing the inner housing, and the flange portion, the shaft support member, and the compression portion are fixed to the stepped surface with mounting bolts (37).

4. The shaft support member and the flange portion have a contact portion (CP1) in contact with each other and a non-contact portion (NP1) spaced apart from each other at a predetermined interval at a portion where the shaft support member and the flange portion overlap with the step surface in the axial direction, The electric compressor according to claim 3 , wherein the contact portion is provided around a portion of the shaft support member and the flange portion through which the mounting bolt is inserted.

5. The step surface and the flange portion have a contact portion (CP2) that contacts with each other in the axial direction and a non-contact portion (NP2) that is spaced apart from each other by a predetermined distance, The electric compressor according to claim 3 , wherein the contact portion is provided around the stepped surface and a portion of the flange portion through which the mounting bolt is inserted.

6. 6. The electric compressor according to claim 4, wherein elastic members (EM1, EM2) that are elastically deformable are arranged in the non-contact portion in a state compressed in the axial direction.

7. the second bearing portion is supported relative to the inner housing, 3. The electric compressor according to claim 1, wherein the inner housing is fixed to the shaft support member by a fixing bolt (18).

8. The electric compressor according to claim 1 or 2, wherein the inner housing is made of the same metal material as the stator.

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