Electric compressor

Abstract

To provide an electric compressor capable of suppressing liquid compression in a compression part, while suppressing a physique in an axial direction of a rotary shaft.SOLUTION: A compressor ECP includes a housing 10, a compression part 30 for compressing a refrigerant, and an electric motor 50 for driving the compression part 30. The housing 10 includes: an internal housing 16 in which a stator 54 of the electric motor 50 is fixed; a motor housing 12 which stores the internal housing 16, and in which a suction port 127 for a refrigerant is formed; and a discharge housing 14 fixed to the motor housing 12. In the motor housing 12 and the internal housing 16, at least a part of a portion overlapped in a radial direction Dr of a rotary shaft 20 is separated. The compressor ECP has a structure in which the refrigerant which has flowed in the inside of the motor housing 12 from the suction port 127 flows in a gap space 164 formed between the internal housing 16 and the motor housing 12 and then sucked into the compression part 30.SELECTED DRAWING: Figure 6

Description

[Technical Field]

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

[0002] Conventionally, there has been known a device that integrates a compressor and a gas-liquid separation means to save space (see, for example, Patent Document 1). Patent Document 1 discloses a device that suppresses liquid compression in the compressor by arranging the compressor body and an electric motor in a lower space within a sealed case and providing a refrigerant storage chamber that stores liquid refrigerant in an upper space within the sealed case. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 5-256275 Summary of the Invention [Problem to be solved by the invention]

[0004] However, in Patent Document 1, the compressor body, electric motor, and refrigerant chamber are arranged in the axial direction of the rotating shaft, which results in a large axial size. A large axial size of an electric compressor is undesirable because it can lead to reduced mountability, etc. This fact was discovered after extensive research by the present inventors.

[0005] An object of the present disclosure is to provide an electric compressor that can suppress liquid compression in a compression section while reducing the axial size of a rotating shaft. [Means for solving the problem]

[0006] An electric compressor applied to a vapor compression refrigeration cycle (1), a housing (10); a rotating shaft (20) accommodated inside the housing; a compression section (30) that compresses a refrigerant by rotation of a 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; The housing is an inner housing (16) that accommodates at least a portion of the electric motor and to which the stator is fixed; an outer housing (12) that accommodates the inner housing and has a refrigerant intake port (127) formed therein; a discharge housing (14) through which the refrigerant compressed by the compression section is discharged and which is fixed to the external housing; The outer housing and the inner housing are separated at least in part of the overlapping portion in the radial direction of the rotary shaft, and the refrigerant that flows into the outer housing from the suction port flows through a clearance space (164) formed between the inner housing and the outer housing and is then sucked into the compression section. At least a portion of the compression section is disposed outside the inner housing. The rotary shaft is fixed to the outer housing via a shaft support member (40) that supports the rotary shaft. The shaft support member is disposed between the electric motor and the compression section, and is configured to be able to guide the refrigerant that has flowed into the inner housing to a refrigerant suction passage (38) of the compression section.

[0007] With this structure, the gap formed between the outer housing and the inner housing in the radial direction of the rotating shaft can function as a liquid reservoir space for storing liquid refrigerant. Therefore, with the electric compressor of the present disclosure, it is possible to suppress liquid compression in the compression section while keeping the axial size small.

[0008] The reference symbols in parentheses attached to each component indicate an example of the correspondence between the component and the specific components described in the embodiments described below. [Brief explanation of the drawings]

[0009] [Figure 1] 1 is a schematic configuration diagram of a refrigeration cycle including an electric compressor according to a first embodiment. [Figure 2]1 is a schematic cross-sectional view of an electric compressor according to a first embodiment. [Figure 3] FIG. 3 is a cross-sectional view taken along the line III-III in FIG. 2. [Figure 4] FIG. 4 is a cross-sectional view taken along line IV-IV of FIG. 2. [Figure 5] FIG. 3 is an enlarged view of a portion V in FIG. 2. [Figure 6] FIG. 2 is an explanatory diagram for explaining the operation of the electric compressor according to the first embodiment. [Figure 7] 5 is an explanatory diagram for explaining how a refrigerant flows as it is sucked into the inside of the housing from the suction port. FIG. [Figure 8] 3 is an explanatory diagram for explaining how a refrigerant flows in a V portion of FIG. 2. FIG. [Figure 9] FIG. 5 is a schematic cross-sectional view of an electric compressor according to a second embodiment. [Figure 10] FIG. 10 is an explanatory diagram for explaining the operation of the electric compressor according to the second embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0010] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, parts that are the same as or equivalent to those described in the preceding embodiments will be given the same reference numerals, and their description may be omitted. Furthermore, in the embodiments, when only some of the components are described, the components described in the preceding embodiments can be applied to the remaining components. The following embodiments can be partially combined with each other, even if not specifically stated, as long as there is no particular problem with the combination.

[0011] (First embodiment) This embodiment will be described with reference to Figures 1 to 8. In this embodiment, an example will be described in which an electric compressor (hereinafter referred to as compressor ECP) ​​according to the present disclosure is applied to a refrigeration cycle device 1 that constitutes a vehicle air conditioner.

[0012] The refrigeration cycle apparatus 1 forms a vapor compression refrigeration cycle. As shown in FIG. 1, the refrigeration cycle apparatus 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 fluid. The radiator CD is a heat exchanger that exchanges heat between the refrigerant discharged from the compressor ECP and air blown from the first fan FAN1, thereby radiating 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 evaporates the refrigerant decompressed by the pressure-reducing device EXV by exchanging heat with air blown from the second fan FAN2. Note that the radiator CD may be configured to radiate heat to a heat medium different from the air blown from the first fan FAN1. The same applies to the evaporator EV.

[0013] The refrigeration cycle device 1 uses a fluorocarbon-based refrigerant as the refrigerant. The refrigerant is mixed with lubricating oil that lubricates the sliding parts inside the compressor ECP. A portion of the lubricating oil circulates within the cycle together with the refrigerant. Note that the refrigerant may be a refrigerant other than a fluorocarbon-based refrigerant (for example, carbon dioxide).

[0014] The refrigeration cycle device 1 of this embodiment configures an accumulator-less cycle in which no accumulator is installed in the path from the refrigerant outlet of the evaporator EV to the refrigerant inlet of the compressor ECP. The accumulator is a liquid storage device that separates the refrigerant into gas and liquid and temporarily stores the liquid refrigerant.

[0015] The compressor ECP will be described in detail below 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 when 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 other drawings as well.

[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 a 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 cylindrical shape with a bottom that is open on one side in the axial direction Dax of the rotary 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 cylindrically from the outer peripheral portion of the first bottom wall portion 121. The motor housing 12 is configured such that the first bottom wall portion 121 and the first outer peripheral wall portion 122 are molded as a seamless, one-piece product. In this embodiment, the motor housing 12 constitutes the "outer housing."

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

[0020] The stepped surface 123 is set between a first housing portion 124 having a smaller inner diameter in the inner portion of the motor housing 12, and a second housing portion 125 having an inner diameter larger than that of the first housing portion 124. Specifically, a protruding portion 126 is provided between the first housing portion 124 and the second housing portion 125, protruding toward the rotating shaft 20. The facing surface of the protruding portion 126 that faces the shaft support member 40 constitutes the stepped surface 123.

[0021] 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.

[0022] Although not shown, an airtight terminal to which electrical wiring and the like of the electric motor 50 are 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.

[0023] A refrigerant suction port 127 is formed in the motor housing 12. The refrigerant outlet side of the evaporator EV is connected to this suction port 127. Therefore, the space in the housing 10 in which the electric motor 50 is disposed is a low-pressure, low-temperature atmosphere. This allows the electric motor 50 to be cooled, thereby improving the efficiency and reliability of the electric motor 50.

[0024] In this embodiment, the suction port 127 is formed in a position of the motor housing 12 that does not face the inner housing 16. Specifically, the suction port 127 is provided above the axis CL of the rotating shaft 20 in the motor housing 12 in the vertical direction Dg. The refrigerant drawn in through the suction port 127 flows through a gap space 164 between the motor housing 12 and the inner housing 16.

[0025] As described above, the refrigeration cycle apparatus 1 of this embodiment is configured as an accumulator-less cycle. Therefore, depending on the load condition of the refrigeration cycle apparatus 1, the refrigerant may not completely evaporate in the evaporator EV, and a two-phase refrigerant including a liquid refrigerant may flow into the gap space 164 through the suction port 127.

[0026] 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 cylindrical shape with a bottom that is open 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, one-piece molded product, with the second bottom wall portion 141 and the second outer peripheral wall portion 142.

[0027] The discharge housing 14 is fixed to the motor housing 12 with fastening bolts 15, with the opening edge on the other side of the discharge housing 14 in the axial direction Dax abutting against the 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. The atmosphere consisting of low-pressure, low-temperature refrigerant inside the motor housing 12 is separated from the atmosphere consisting of high-pressure, high-temperature refrigerant discharged from the compression section 30 by a sealing member (not shown).

[0028] 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 from the refrigerant is installed at the discharge port. Therefore, the lubricating oil in the refrigerant discharged from the compression section 30 is stored inside the discharge housing 14.

[0029] The rotating shaft 20 is accommodated inside the housing 10. Specifically, the rotating shaft 20 is disposed inside the motor housing 12 so 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.

[0030] 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.

[0031] 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.

[0032] An oil supply passage 24 is formed inside the rotating shaft 20 to supply lubricating oil to the eccentric bearing 344, a first bearing 411 (described later), a second bearing 17, etc. The oil supply passage 24 is connected to 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.

[0033] The compression unit 30 is configured as a scroll-type compression mechanism. The compression unit 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, aluminum alloy, or the like.

[0034] The fixed scroll 32 has a fixed base plate portion 321 formed in a disk shape, and a spiral fixed tooth portion 322 protruding from the fixed base plate portion 321 toward the orbiting scroll 34 on the other side in the axial direction Dax.

[0035] The orbiting scroll 34 has an orbiting base plate portion 341 formed in a disk shape, and a spiral orbiting tooth portion 342 protruding from the orbiting base plate portion 341 toward the fixed scroll 32 on one side in the axial direction Dax.

[0036] The orbiting scroll 34 has a cylindrical first boss portion 343 provided on the orbiting base plate portion 341 on the side opposite to the orbiting tooth portion 342. An eccentric bearing portion 344 is provided inside the first boss portion 343. The eccentric bearing portion 344 is made up of a plain bearing. Note that the eccentric bearing portion 344 may be made up of a bearing other than a plain bearing.

[0037] 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 rotary shaft 20 rotates, the orbiting scroll 34 performs an orbital motion (i.e., an orbital motion) around the axis CL of the rotary shaft 20 as the center of revolution. Note that the rotation prevention mechanism may be configured with something other than the Oldham ring 35.

[0038] 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 locations, thereby forming multiple crescent-shaped working chambers 31. As the orbiting scroll 34 orbits, the working chambers 31 move from the outer periphery toward the center while decreasing in volume. For convenience, only one of the multiple working chambers 31 is labeled in Figure 2 and other figures.

[0039] The working chamber 31 is supplied with refrigerant drawn from a refrigerant suction passage 38 formed adjacent to the compression section 30. In this embodiment, the refrigerant suction passage 38 is formed on the outer periphery of the fixed scroll 32 and the orbiting scroll 34. The refrigerant supplied from the refrigerant suction passage 38 to the working chamber 31 is compressed as the volume of the working chamber 31 decreases.

[0040] A discharge hole 323 is formed in the center of the fixed base plate portion 321 to discharge the refrigerant compressed in the working chamber 31. A reed valve (not shown) serving as a check valve to prevent backflow of the refrigerant into the working chamber 31, and a stopper 324 to regulate the maximum opening degree of the reed valve are provided on one end face of the fixed base plate portion 321 in the axial direction Dax. The reed valve and the stopper 324 are fastened and fixed to the fixed base plate portion 321 by bolts 325.

[0041] The discharge plate 36 is disposed adjacent to the fixed scroll 32. A muffler chamber 361 is formed between the discharge plate 36 and the fixed scroll 32 to reduce 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 from 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.

[0042] 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 substantially the same outer diameter as the inner diameter of the second housing portion 125.

[0043] The compression section 30 configured in this manner is fixed to the stepped surface 123 of the motor housing 12 by a mounting bolt (not shown) via the shaft support member 40. The stepped surface 123 of the motor housing 12 forms a fixing portion for fixing the compression section 30.

[0044] 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 portion of the rotating shaft 20, etc. The shaft support member 40 is made of a steel material, an aluminum alloy, etc.

[0045] 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 smallest, a large diameter portion 42 where the outer diameter is 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 formed.

[0046] The shaft support member 40 has a first bearing portion 411 formed on the inner circumferential 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 with a resin layer or the like coated on its inner circumferential surface. The first bearing portion 411 may be made of the same material as the shaft support member 40 and may be made integral with the shaft support member 40. The first bearing portion 411 may also be made of a bearing other than a plain bearing.

[0047] 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.

[0048] The outer diameter of the large diameter portion 42 of the shaft support member 40 is set to be approximately 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.

[0049] A refrigerant introduction passage 45 that introduces refrigerant from inside the inner housing 16 to the compression section 30 is provided between the shaft support member 40 and the motor housing 12. This refrigerant introduction passage 45 is provided at least below the axis CL of the rotating shaft 20. The refrigerant introduction passage 45 is a passage that connects the inside of the inner housing 16 with the refrigerant suction passage 38. In this embodiment, one refrigerant introduction passage 45 is provided below the axis CL of the rotating shaft 20. Note that multiple refrigerant introduction passages 45 may be formed between the shaft support member 40 and the motor housing 12. Note that the refrigerant introduction passage 45 may be provided, for example, to penetrate the shaft support member 40.

[0050] The shaft support member 40 configured in this manner is fixed to the motor housing 12 together with the compression portion 30 by mounting bolts (not shown).

[0051] 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 arranged on the other side of the shaft support member 40 in the axial direction Dax. The electric motor 50 drives the compression unit 30 and has a rotor 52 that rotates integrally with the rotary 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 arranged inside the stator 54.

[0052] 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 imbalance in the eccentric rotation of the orbiting scroll 34 and the like.

[0053] 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.

[0054] The inner housing 16 is accommodated inside the motor housing 12. The 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 (e.g., iron) as the stator 54.

[0055] 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. Electromagnetic steel sheets are generally used for the stator core 541. Taking these factors into consideration, the material constituting the inner housing 16 should have a linear expansion coefficient of 20×10 -6 Materials below [ / ℃] are desirable.

[0056] By reducing the difference in the linear expansion coefficients between the stator 54 and the inner housing 16, it is possible to set the interference appropriately in the expected temperature range. Note that, for example, if a metal material with a high linear expansion coefficient, such as aluminum, is used as the constituent material of the inner housing 16, the difference in the linear expansion coefficient between the stator 54 and the inner housing 16 will be large. Therefore, if an interference that ensures sufficient tension in the high temperature range is set and a low ambient temperature range is assumed, the interference will increase. This increases distortion of the stator core 541 and reduces the efficiency of the electric motor 50. Conversely, if the interference is set so that the effect of distortion is small at low ambient temperatures, the tension will decrease and the fixation of the stator 54 may become unstable at high ambient temperatures.

[0057] The inner housing 16 has a generally cup-shaped configuration. The inner housing 16 has a cylindrical tubular portion 161 to which the stator 54 is fixed, and a flange portion 162 that protrudes from one end 161a of the tubular portion 161, which is closer to the compression portion 30, in a direction away from the rotary shaft 20. The inner housing 16 also includes a support portion 163 that extends from the other end 161b, which is located opposite the one end 161a, toward the rotary shaft 20 and supports the second bearing portion 17. The tubular portion 161, the flange portion 162, and the support portion 163 are formed as an integrally molded product. In this embodiment, the support portion 163 forms a "bottom portion" of the inner housing 16. Note that the tubular portion 161, the flange portion 162, and the support portion 163 may be partially formed as separate parts.

[0058] The support portion 163 has an annular bottom portion 163a connected to the other end portion 161b of the cylindrical portion 161 and a cylindrical second boss portion 163b provided in the center 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 portion of the second boss portion 163b overlaps with the stator 54 in the radial direction Dr. A second bearing portion 17 is formed on the inner periphery of the second boss portion 163b. The second bearing portion 17 is configured as a plain bearing. The second bearing portion 17 is configured from a cylindrical steel member with a resin layer or the like coated on its inner periphery. The second bearing portion 17 may be configured as an integral part of the shaft support member 40 and made of the same material as the inner housing 16. The second bearing portion 17 may also be configured as a bearing other than a plain bearing.

[0059] 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.

[0060] The entire flange portion 162 of the inner housing 16 faces the shaft support member 40 in the axial direction Dax. The flange portion 162 is fixed to the shaft support member 40 by fixing bolts (not shown).

[0061] An inside-outside communicating part 165 that penetrates the inside and outside of the inner housing 16 is formed in the inner housing 16. As a result, the refrigerant that is sucked from the suction port 127 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 part 165.

[0062] The inside-outside communicating portion 165 in this embodiment is provided above the axis CL of the rotating shaft 20 in the vertical direction Dg. Specifically, the inside-outside communicating portion 165 is provided in each of the cylindrical portion 161 and the bottom portion 163a constituting the bottom surface portion of the inner housing 16. That is, the inside-outside communicating portion 165 has a cylindrical side communicating portion 165a provided in the cylindrical portion 161 and a bottom side communicating portion 165b provided in the bottom portion 163a.

[0063] The tube-side communication portion 165a is provided in a position close to the shaft support member 40 in a portion of the tube portion 161 above the axis CL of the rotating shaft 20. The gas refrigerant present in the gap space 164 passes through the tube-side communication portion 165a and flows into the inner housing 16. The refrigerant that has passed through the tube-side communication portion 165a flows along the surface of the shaft support member 40 and is then introduced into the refrigerant introduction passage 65.

[0064] The bottom-side communication portion 165b is provided at a portion of the bottom portion 163a above the axis CL of the rotating shaft 20. The gas refrigerant present in the gap space 164 passes through the bottom-side communication portion 165b and flows into the inner housing 16. The refrigerant that has passed through the bottom-side communication portion 165b flows through the gap between the rotor 52 and the stator 54, and is then introduced into the refrigerant inlet passage 65.

[0065] Meanwhile, the inside of the inner housing 16 and the gap space 164 between the motor housing 12 and the inner housing 16 are partitioned by the tubular 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 in communication with each other. In other words, the inner housing 16 does not have an inside-outside communication portion 165 below the axis CL in the vertical direction Dg.

[0066] Here, in the compressor ECP of this embodiment, the wiring electrically connecting the stator 54 and the airtight terminal is drawn from the stator 54 to the airtight terminal via the internal / external communication part 165. In this way, by using the internal / external communication part 165 as a lead-out path for the wiring, etc., the structure of the compressor ECP can be simplified and costs can be reduced.

[0067] The inner housing 16, the shaft support member 40, and the compression unit 30 are arranged in this order in the axial direction Dax. The inner housing 16 and the compression unit 30 are fixed to a stepped surface 123 of the motor housing 12 by mounting bolts (not shown) at a portion between the stator 54, which is a heavy component, and the compression unit 30.

[0068] Specifically, as shown in FIG. 3, the inner housing 16 is fixed to the stepped surface 123 of the motor housing 12 in a state where the portion excluding the flange portion 162 is spaced apart from the first housing portion .

[0069] Furthermore, the axial length Dax of the inner housing 16 is smaller than the axial length Dax from the stepped surface 123 to the first bottom wall portion 121 of the motor housing 12. As a result, a gap is formed between the support portion 163 of the inner housing 16 and the motor housing 12.

[0070] A separation plate 18 is disposed between the support portion 163 of the inner housing 16 and the first bottom wall portion 121 of the motor housing 12. This separation plate 18 causes the refrigerant introduced into the gap space 164 from the suction port 127 to collide with the separation plate 18, promoting separation of the refrigerant into gas and liquid phases. The separation plate 18 is disposed below the axis CL of the rotating shaft 20 in the vertical direction Dg so as not to impede the flow of gas refrigerant to the interior-exterior communication portion 165.

[0071] Specifically, the separation plate 18 is made of punched metal with a large number of holes formed therein that penetrate from the front to the back. The shape of the holes is not particularly limited and may be, for example, round holes, slit holes, or the like. A plurality of separation plates 18 may be arranged in a line in the vertical direction Dg. Furthermore, the separation plate 18 may be fixed to either the motor housing 12 or the inner housing 16. However, it is desirable to arrange the separation plate 18 at a distance from either the motor housing 12 or the inner housing 16 so that the separation plate 18 does not become a vibration transmission element.

[0072] Furthermore, a protrusion 166 that protrudes toward the rotating shaft 20 is provided on the first outer peripheral wall portion 122 of the motor housing 12 so as to extend in the axial direction Dax of the rotating shaft 20. The protrusion 166 may be configured integrally with the motor housing 12, or may be configured separately and attached to the motor housing 12.

[0073] 3 and 4, the protrusion 166 is provided in a portion of the first outer peripheral wall portion 122 that faces the inner housing 16. The protrusion 166 may be provided over the entire portion that faces the inner housing 16 in the axial direction Dax, or may be provided over a portion thereof.

[0074] The protrusion 166 has a protruding height Lh set so as not to come into contact with the internal housing 16. The protrusion 166 is formed at a position that is approximately the same height as the rotation shaft 20 in the vertical direction Dg. The position at which the protrusion 166 is provided is not limited to the position shown in Figures 3 and 4, but it is desirable that the protrusion 166 be provided below the suction port 127 in the vertical direction Dg. It is also desirable that the protrusion 166 be provided at a position equivalent to or above the separation plate 18 in the vertical direction Dg.

[0075] Furthermore, inside the housing 10, there is provided a communication passage 19 that connects a gap space 164 formed between the motor housing 12 and the inner housing 16 to the refrigerant introduction passage 45. The communication passage 19 is a throttle passage having a smaller cross-sectional area than the refrigerant introduction passage 45.

[0076] Specifically, as shown in FIG. 5, the communicating flow path 19 includes a first through hole 191 provided in the protrusion 126 provided on the motor housing 12 and a second through hole 192 provided in the flange portion 162 of the inner housing 16.

[0077] The first through hole 191 is formed on the base side of the protrusion 126. The second through hole 192 is formed on the tip side of the flange portion 162 so as to overlap with the first through hole 191 in the axial direction Dax.

[0078] The size of each of the first through hole 191 and the second through hole 192 is smaller than the flow path cross-sectional area of ​​the refrigerant introduction flow path 45. Specifically, the hole diameter φ1 of the first through hole 191 is larger than the hole diameter φ2 of the second through hole 192 and is smaller than the flow path height FH of the refrigerant introduction flow path 45. The hole diameter φ1 of the first through hole 191 may be equal to or smaller than the hole diameter φ2 of the second through hole 192.

[0079] Next, the operation of the compressor ECP will be described with reference to Figures 6 to 8. When power is supplied from an inverter (not shown) to the stator 54 of the electric motor 50, the rotor 52 and the rotary shaft 20 rotate, 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 through the suction port 127.

[0080] Specifically, as shown by arrow FR1 in Figures 6 and 7, the refrigerant flows into the gap space 164 formed between the motor housing 12 and the inner housing 16, and then is introduced into the inside of the inner housing 16 through the internal / external communication part 165.

[0081] The internal / external communicating portion 165 is formed above the axial center CL of the rotating shaft 20 in the internal housing 16. The gas refrigerant, which has a low specific gravity, is introduced into the inside of the internal housing 16 through the internal / external communicating portion 165, while the liquid refrigerant, which has a high specific gravity, is stored in the gap space 164, as shown in Fig. 7. In particular, the separation plate 18 is disposed in the gap space 164, so that the gas and liquid refrigerant can be appropriately separated.

[0082] Here, when the liquid refrigerant stored in the gap space 164 is heated by the heat generated by the compression section 30 and the electric motor 50 performing their work, it may gasify and be introduced into the inside of the inner housing 16 through the internal / external communication section 165.

[0083] The refrigerant introduced into the inner housing 16 passes through gaps between various components of the electric motor 50 and a refrigerant inlet passage 45 provided between the motor housing 12 and the shaft support member 40. The refrigerant passing through the refrigerant inlet passage 45 flows into the refrigerant suction passage 38 formed on the outer periphery of the fixed scroll 32, as indicated by arrow FR2 in FIG. 6 , and is then drawn into the working chamber 31 through the refrigerant suction passage 38. 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 compressed refrigerant in the working chamber 31 is discharged from the discharge hole 323 of the fixed scroll 32 into the muffler chamber 361, as indicated by arrow FR3 in FIG. 6 . The refrigerant discharged into the muffler chamber 361 flows into the discharge housing 14 through an outlet provided in the discharge plate 36 and is then discharged from a discharge port provided in the discharge housing 14 as discharge refrigerant for the compressor ECP. At this time, the lubricating oil contained in the discharged refrigerant is separated by an oil separator provided at the discharge port and falls under its own weight to accumulate in the lower part of discharge housing 14. The lubricating oil is then supplied to each sliding part inside housing 12 via oil supply path 24 and the like due to the pressure difference of the refrigerant inside housing 10. Some of the lubricating oil supplied to the sliding parts flows into gap space 164. Unlike the refrigerant, the lubricating oil does not vaporize, so it temporarily accumulates in a liquid state in the lower part of gap space 164, but is then led to refrigerant introduction path 45 via communication path 19, which communicates gap space 164 with refrigerant introduction path 45.

[0084] Here, the communication flow path 19 is a throttled flow path with a smaller flow path cross-sectional area than the refrigerant inlet flow path 45. Therefore, the gas refrigerant flowing through the inner housing 16 passes through the refrigerant inlet flow path 45, which has a smaller pressure loss than the communication flow path 19, and easily flows to the refrigerant suction flow path 38. At this time, the refrigerant flow from the refrigerant inlet flow path 45 to the refrigerant suction flow path 38 causes the liquid refrigerant containing the lubricating oil stored in the gap space 164 to be sucked into the refrigerant suction flow path 38, as shown in FIG. 8 .

[0085] In the compressor ECP of the present embodiment described above, the motor housing 12 and the inner housing 16 are separated from each other at portions that overlap in the radial direction Dr of the rotating shaft 20. The refrigerant that flows into the motor housing 12 from the suction port 127 flows through a gap space 164 formed between the inner housing 16 and the motor housing 12, and is then drawn into the compression section 30.

[0086] In this structure, the gap formed between the motor housing 12 and the inner housing 16 in the radial direction Dr of the rotating shaft 20 can function as a liquid reservoir space for storing liquid refrigerant. Therefore, compared to a structure in which the space accommodating the electric motor 50 and the liquid reservoir space are aligned in the axial direction Dax, it is possible to suppress liquid compression in the compression section 30 while keeping the size in the axial direction Dax small.

[0087] However, if the internal housing 16 and the compression section 30 are fixed to the discharge housing 14 in a cantilever-like manner, the distance between the position supporting the internal housing 16 and the compression section 30 and the position where vibration occurs becomes larger, and the amplitude of the vibration becomes larger.

[0088] In particular, when the space accommodating the electric motor 50 and the liquid reservoir space are aligned in the axial direction Dax, the amplitude of vibration increases. In this case, the amplitude of vibration of piping and other components connected to external devices of the compressor ECP also increases, which may increase noise and damage to the connections. Furthermore, when the space accommodating the electric motor 50 and the liquid reservoir space are aligned in the axial direction Dax, the wiring connecting the stator 54 and the airtight terminal must be routed to avoid the area that forms the liquid reservoir space, which complicates the structure of the compressor ECP.

[0089] In contrast to these, in the compressor ECP of this embodiment, a portion located midway between the inner housing 16 and the compression unit 30 is fixed to the stepped surface 123 of the motor housing 12. This makes it possible to reduce the distance between the position where the inner housing 16 and the compression unit 30 are supported and the position where vibrations occur, compared to when the inner housing 16 and the compression unit 30 are fixed in a cantilever-like manner. In particular, in the compressor ECP of this embodiment, the liquid reservoir space is formed outside the electric motor 50 in the radial direction Dr. This reduces vibrations of the electric motor 50 and the compression unit 30 and makes them less likely to be transmitted to the motor housing 12, thereby suppressing noise.

[0090] Moreover, the compressor ECP of this embodiment has the following features. (1) The inner housing 16 is provided with an inside-outside communicating portion 165 that communicates the inside and outside of the inner housing 16. The refrigerant that flows into the inside of the motor housing 12 from the suction port 127 flows through the clearance space 164, and then is introduced into the inside of the inner housing 16 via the inside-outside communicating portion 165 and is sucked into the compression section 30. This allows liquid refrigerant, which has a high specific gravity, to be stored in the clearance space 164, while gas refrigerant, which has a low specific gravity, to flow from the inside of the inner housing 16 toward the compression section 30 via the inside-outside communicating portion 165.

[0091] (2) Specifically, the inner housing 16 includes a cylindrical tube portion 161 to which the stator 54 is fixed, and a support portion 163 extending from an end portion 161b of the tube portion 161 located opposite to an end portion 161a closer to the compression portion 30, toward the rotating shaft 20. An inside-outside communication portion 165 that communicates the inside and outside of the inner housing 16 is provided in at least one of the tube portion 161 and the support portion 163, at a location located above the axis CL of the rotating shaft 20 in the vertical direction Dg.

[0092] This allows the liquid refrigerant with a high specific gravity to be stored in the lower part of the gap space 164, while the gas refrigerant with a low specific gravity can flow from the inside of the inner housing 16 toward the compression section 30 via the internal / external communication section 165.

[0093] In particular, the inside-outside communicating portion 165 of this embodiment has a tube-side communicating portion 165a provided in the tube portion 161 of the inner housing 16 and a bottom-side communicating portion 165b provided in the bottom portion 163a. ​​By changing the ratio of the opening areas of the tube-side communicating portion 165a and the bottom-side communicating portion 165b, it is possible to adjust the cooling effect of the refrigerant on the electric motor 50.

[0094] For example, if the heat resistance grade of the electric motor 50 is low, by providing only the bottom-side communication portion 165b in the inner housing 16, the cooling effect of the electric motor 50 by the refrigerant can be improved.

[0095] On the other hand, if the heat resistance grade of the electric motor 50 is high, providing only the cylinder side communicating portion 165a in the inner housing 16 can prevent foreign matter from entering the electric motor 50. Even in this case, the electric motor 50 can be cooled by heat conduction via the inner housing 16.

[0096] (3) The inside of the inner housing 16 and the gap space 164 are partitioned by the cylindrical portion 161 and the support portion 163 below the axis CL of the rotating shaft 20 in the vertical direction Dg so that the inside and outside of the inner housing 16 are not in communication with each other. This makes it possible to prevent the liquid refrigerant that has accumulated on the lower side of the gap space 164 from flowing into the inside of the inner housing 16.

[0097] (4) The housing 10 is provided inside with the refrigerant suction passage 38, the refrigerant introduction passage 45, and the communication passage 19. This allows the lubricating oil in the clearance space 164 to be guided to the compression section 30 side via the communication passage 19, thereby preventing the lubricating oil from accumulating in the clearance space 164.

[0098] (5) The communication passage 19 is a throttled passage having a smaller cross-sectional area than the refrigerant introduction passage 45. This prevents the liquid refrigerant from flowing into the compression section 30, while properly directing the lubricating oil in the clearance space 164 to the compression section 30. As a result, abnormal wear and seizure of the sliding parts of the compression section 30 can be prevented.

[0099] (6) The refrigerant inlet passage 45 is provided below the axis CL of the rotating shaft 20 in the vertical direction Dg. With this configuration, the flow of the refrigerant through the refrigerant inlet passage 45 can draw the lubricating oil on the lower side of the housing 10 into the compression section 30.

[0100] (7) Separator plate 18 is disposed in gap space 164 to promote separation of the refrigerant into gas and liquid by causing the refrigerant introduced into gap space 164 from suction port 127 to collide with it. This allows the refrigerant to collide with separator plate 18 in gap space 164, thereby promoting separation of the refrigerant into gas and liquid.

[0101] Here, when the rotor 52 of the electric motor 50 rotates as shown by the solid arrow in FIG. 7, a swirling flow of the refrigerant occurs inside the housing 10 in the direction of rotation of the rotor 52 as shown by the dotted arrow in FIG. 7, and the liquid refrigerant may be stirred up upward.

[0102] In contrast, if the separation plate 18 is disposed in the gap space 164, the liquid refrigerant accumulated on the lower side of the gap space 164 can be prevented from being swirled upward by the swirling flow of the refrigerant.

[0103] (8) The motor housing 12 is provided with a protrusion 166 that protrudes toward the rotating shaft 20 and extends in the axial direction Dax of the rotating shaft 20. This also prevents the liquid refrigerant that has accumulated in the lower part of the clearance space 164 from being swirled upward by the swirling flow of the refrigerant.

[0104] (9) The compressor ECP of this embodiment has a double-supported structure in which the rotating shaft 20 is supported by the first bearing 411 and the second bearing 17. This allows the sliding area of ​​each of the bearings 411, 17 to be set short, making it easier to stably supply lubricating oil to the entire sliding surface in conditions ranging from low rotation speed to high rotation speed of the rotating shaft 20, thereby ensuring reliability.

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

[0106] (10) If the inner housing 16 is simply cylindrical with both ends open, when the stator 54 vibrates, the inner housing 16 may vibrate in response to the vibration, resulting in slight deformation. Such deformation is undesirable because it increases the vibration transmitted from the inner housing 16 to the motor housing 12. This also applies when the inner housing 16 is configured to partially support the stator 54 with multiple plate-shaped support pieces.

[0107] In contrast, in the compressor ECP of this embodiment, the inner housing 16 is substantially cup-shaped and has a cylindrical portion 161, a support portion 163, and a flange portion 162. This makes it easier to ensure rigidity compared to a compressor having a simple cylindrical shape, and makes it possible to suppress deformation of the inner housing 16 due to vibration of the stator 54.

[0108] Furthermore, since the support portion 163 is formed integrally with the cylindrical portion 161 of the inner housing 16, the rigidity of the support portion 163 is increased, and deformation due to the load received by the second bearing portion 17 from the rotating shaft 20 can be further suppressed. This makes it possible to reduce the amount of imbalance of the axis CL of the rotating shaft 20.

[0109] (11) The compressor ECP is configured to fix the inner housing 16, the shaft support member 40, and the compression unit 30 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 unit 30 and the motor housing 12 and the discharge housing 14 compared to when the stator 54 and the compression unit 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 unit 30 to be transmitted to the motor housing 12 and the discharge housing 14, thereby suppressing noise and vibrations radiating to the outside of the motor housing 12 and the discharge housing 14.

[0110] (12) The inner housing 16 is made of the same metal material as the stator 54. This prevents the fixed state between the inner housing 16 and the stator 54 from becoming unstable due to the difference in the 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 set appropriately.

[0111] Here, "same type of metallic material" means metallic materials that have the same most abundant element in their chemical composition. Note that the term "same type of metallic material" does not only refer to metallic materials that have the exact same chemical composition, but also includes those that have the same designation in standards.

[0112] (13) When the stator 54 is fixed to the motor housing 12 and the discharge housing 14 that constitute the outer housing by shrink fitting, it is necessary to set the shrink fitting interference large, taking into account deformation due to pressure inside the housing 10.

[0113] 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 components, such as a pressure adjustment valve, a refrigerant path, a water path, and a heat exchanger, to the motor housing 12 and the discharge housing 14.

[0114] Here, since the pressure from inside 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 canceled out. This makes it difficult for the cylindrical portion 161 to deform due to the pressure from inside the motor housing 12. This makes it possible to reduce the interference that accompanies shrink-fitting or press-fitting of the stator 54 into the cylindrical portion 161 of the inner housing 16.

[0115] (Second embodiment) Next, a second embodiment will be described with reference to Figures 9 and 10. In this embodiment, differences from the first embodiment will be mainly described.

[0116] 9, the motor housing 12 of this embodiment does not have the stepped surface 123 described in the first embodiment, and the inner diameter of the first outer peripheral wall portion 122 is generally constant. Furthermore, 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 together by fastening bolts 15 with their opening edges abutting against the shaft support member 40.

[0117] The outer diameter of the large diameter portion 42 of the shaft support member 40 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 insertion holes SH, through which fastening bolts 15 are inserted, at portions 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 bolts 15 while being sandwiched between the motor housing 12 and the discharge housing 14.

[0118] A refrigerant introduction passage 45 is provided in the shaft support member 40. The refrigerant introduction passage 45 is a passage that guides refrigerant from the inside of the inner housing 16 to the compression section 30. The refrigerant introduction passage 45 is provided so as to obliquely penetrate the shaft support member 40. Specifically, the opening of the refrigerant introduction passage 45 on the inner housing 16 side is positioned more inward in the radial direction Dr than the opening on the compression section 30 side.

[0119] In addition, a communication flow path 46 that connects the gap space 164 and the refrigerant introduction flow path 45 is formed in the shaft support member 40. The communication flow path 46 extends along the axial direction Dax so as to intersect with the refrigerant introduction flow path 45. The communication flow path 46 is a throttle flow path with a smaller flow path cross-sectional area than the refrigerant introduction flow path 45.

[0120] The inner housing 16 does not have the flange portion 162 described in the first embodiment. The outer diameter of the inner housing 16 is the same size as 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.

[0121] 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 threading mounting bolts 37 into female threaded holes provided in the cylindrical portion 161. In this embodiment, the inner housing 16 and the compression portion 30 are fixed to the motor housing 12 and the discharge housing 14 via the shaft support member 40.

[0122] The motor housing 12 also has an intake port 127 at a location facing the inner housing 16. Specifically, the intake port 127 is provided at a side surface of the first outer peripheral wall portion 122 of the motor housing 12 that faces the inner housing 16. Instead, the separation plate 18 is not disposed in the clearance space 164. As a result, the clearance formed between the first bottom wall portion 121 of the motor housing 12 and the support portion 163 of the inner housing 16 is smaller than in the first embodiment. This contributes to a reduction in the size of the compressor ECP in the axial direction Dax.

[0123] Next, the operation of the compressor ECP will be described with reference to Fig. 10. When power is supplied to the stator 54 of the electric motor 50 and the rotor 52 and the rotary shaft 20 rotate, the compressor ECP draws the refrigerant that has passed through the evaporator EV into the housing 10 through the suction port 127.

[0124] Specifically, as shown by arrow FR1 in Fig. 10 , the refrigerant is introduced from suction port 127 into gap space 164 formed between motor housing 12 and inner housing 16, and then collides with inner housing 16 to separate gas and liquid. The refrigerant is then introduced into the inside of inner housing 16 via interior-exterior communicating part 165. The gas refrigerant, which has a low specific gravity, is introduced into the inside of inner housing 16 via interior-exterior communicating part 165, while the liquid refrigerant, which has a high specific gravity, is stored in gap space 164.

[0125] The refrigerant introduced into the inner housing 16 passes through gaps between various components of the electric motor 50 and a refrigerant inlet passage 45 provided between the motor housing 12 and the shaft support member 40. The refrigerant passing through the refrigerant inlet passage 45 flows into the refrigerant suction passage 38 formed on the outer periphery of the fixed scroll 32, as indicated by arrow FR2 in FIG. 10 . At this time, the refrigerant flowing from the refrigerant inlet passage 45 to the refrigerant suction passage 38 draws the liquid refrigerant containing lubricating oil stored in the clearance space 164 into the refrigerant suction passage 38 via the communication passage 46.

[0126] The refrigerant that flows into the refrigerant suction passage 38 is drawn into the working chamber 31. The refrigerant supplied to the working chamber 31 is compressed as the volume of the working chamber 31 decreases. When the pressure inside 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 into the muffler chamber 361, as shown by arrow FR3 in Figure 10. The refrigerant discharged into the muffler chamber 361 flows into the discharge housing 14 from an outlet provided in the discharge plate 36, and is then discharged from a discharge port provided in the discharge housing 14 as discharge refrigerant for the compressor ECP.

[0127] The other points are the same as those of the first embodiment. The compressor ECP of this embodiment can obtain the same effects as those of the first embodiment that are achieved by a configuration common to or equivalent to that of the first embodiment.

[0128] Moreover, the compressor ECP of this embodiment has the following features.

[0129] (1) The motor housing 12 is provided with an intake port 127 at a location facing the inner housing 16. With this configuration, the refrigerant that passes through the intake port 127 can be caused to collide with the inner housing 16, thereby promoting gas-liquid separation of the refrigerant. This configuration can be easily achieved without the need for additional components.

[0130] (2) 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.

[0131] Furthermore, 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 vibrations of the inner housing 16 and the compression section 30. As a result, it is possible to reduce vibrations and noise of the compressor ECP.

[0132] (Modification of the second embodiment) In the compressor ECP of the second embodiment, the suction port 127 is provided in a side portion of the first outer peripheral wall portion 122 of the motor housing 12 that faces the inner housing 16, but this is not limiting. In the compressor ECP, the suction port 127 may be provided, for example, in a bottom portion of the first bottom wall portion 121 of the motor housing 12 that faces the inner housing 16. In this configuration, the refrigerant introduced into the motor housing 12 from the suction port 127 is caused to collide with the first bottom wall portion 121 of the inner housing 16, thereby efficiently separating the refrigerant into gas and liquid forms. As a result, liquid compression in the compressor ECP can be suppressed.

[0133] It is desirable that suction port 127 be provided in a position above the lower portion that forms the liquid storage space in first bottom wall portion 121, rather than in the lower portion. This configuration can prevent the refrigerant introduced into motor housing 12 from suction port 127 from disturbing the liquid level of the liquid refrigerant stored in the liquid storage space or causing the liquid refrigerant to be stirred up upward.

[0134] Here, suction port 127 may be formed in a portion of first bottom wall portion 121 or first outer peripheral wall portion 122 that forms a liquid storage space, but in this case, it is desirable that the refrigerant passing through suction port 127 be structured to be guided to the upper side inside motor housing 12. Such a structure can be achieved, for example, by connecting a pipe that protrudes upward to suction port 127. This also promotes gas-liquid separation of the refrigerant and suppresses liquid compression in compressor ECP.

[0135] (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 follows.

[0136] The inner housing 16 is not limited to being substantially cup-shaped, and may be, for example, cylindrical. Furthermore, the inner housing 16 is desirably made of the same metal material as the stator 54, but is not limited to this, and may be made of, for example, a different metal material from the stator 54. A portion of the inner housing 16 may be in contact with the motor housing 12 in the axial direction Dax.

[0137] As in the above-described embodiment, it is desirable to provide the communication flow path 19 inside the housing 10, but this is not limiting, and the communication flow path 19 may be omitted. Furthermore, the communication flow path 19 may be configured as a flow path having a flow path cross-sectional area approximately the same as that of the refrigerant introduction flow path 45.

[0138] As in the above-described embodiment, it is desirable that the refrigerant introduction passage 45 be located below the axis CL of the rotating shaft 20 in the vertical direction Dg, but this is not limited thereto and it may also be located above the axis CL of the rotating shaft 20.

[0139] As in the above embodiment, it is desirable that the separation plate 18 be disposed in the gap space 164, but this is not a limitation and the separation plate 18 may be omitted. Also, it is desirable that the motor housing 12 be provided with a protrusion 166, but this is not a limitation and the protrusion 166 may be omitted.

[0140] 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. Furthermore, the second bearing portion 17 may be provided on an element other than the inner housing 16. The compressor ECP may have a cantilever structure in which the rotating shaft 20 is supported by one of the first bearing portion 411 and the second bearing portion 17.

[0141] 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 configured as, for example, a piston type or a vane type. A portion of the compression section 30 may be in contact with the discharge housing 14 in the axial direction Dax.

[0142] In the above-described embodiment, the compressor ECP is described as being applied to a vehicle air conditioner. However, the present disclosure is not limited thereto. The compressor ECP can also be applied to other air conditioners, temperature control devices for various devices, and the like. Furthermore, the compressor ECP is not limited to a horizontally mounted configuration in which the compression section 30 and the electric motor 50 are arranged in a substantially horizontal direction. The various devices constituting the compressor ECP may be fixed by elements other than bolts. The compressor ECP of the present disclosure is not limited to an accumulator-less cycle, but can also be applied to an accumulator cycle. The refrigerant can be reliably separated into gas and liquid forms before being drawn into the compression section 30, thereby suppressing liquid compression in the compression section 30. Furthermore, if the refrigeration cycle apparatus 1 is configured to be set to a hot gas cycle in which high-temperature, high-pressure refrigerant discharged from the compressor ECP circulates, liquid refrigerant may be transiently supplied to the compressor ECP when switching to the hot gas cycle. In contrast, the compressor ECP of the present disclosure has a liquid reservoir space inside the compressor ECP, thereby suppressing liquid compression in the compression section 30 even when switching to the hot gas cycle. The refrigeration cycle device 1 has a cycle configuration in which heat is exchanged between the refrigerant and air in the evaporator EV, but is not limited to this. For example, the cycle may have a configuration in which a chiller is used instead of the evaporator EV to exchange heat between the refrigerant and water, etc.

[0143] In the above-described embodiments, it goes without saying that the elements constituting the embodiments are not necessarily essential unless they are specifically stated as essential or are clearly considered essential in principle.

[0144] 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 they are specifically stated as essential or are clearly limited to a specific number in principle.

[0145] In the above-described embodiments, when referring to the shapes, positional relationships, etc. of components, etc., the shapes, positional relationships, etc. are not limited to those unless otherwise specified or when they are fundamentally limited to specific shapes, positional relationships, etc.

[0146] (Aspects of the present disclosure) According to a first aspect of the present disclosure, The electric compressor is It is applied to the vapor compression refrigeration cycle (1), a housing (10); a rotating shaft (20) accommodated inside the housing; a compression section (30) that compresses a refrigerant 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; The housing includes: an inner housing (16) that accommodates at least a portion of the electric motor and to which the stator is fixed; an outer housing (12) that accommodates the inner housing and has a suction port (127) for a refrigerant; a discharge housing (14) through which the refrigerant compressed by the compression section is discharged and which is fixed to the external housing, The external housing and the internal housing are separated at least in part at the overlapping portion in the radial direction of the rotating shaft, and the refrigerant that flows into the inside of the external housing from the suction port flows through a gap space (164) formed between the internal housing and the external housing before being sucked into the compression section.

[0147] [Second perspective] The electric compressor according to the first aspect, wherein the inner housing is provided with an inside-outside communication part (165) that communicates the inside and outside of the inner housing, and the refrigerant that flows into the inside of the outer housing from the suction port flows through the gap space, and then is introduced into the inside of the inner housing via the inside-outside communication part and sucked into the compression part.

[0148] [Third Perspective] The rotating shaft is accommodated inside the housing in such a manner that the axis (CL) of the rotating shaft intersects with the vertical direction, the inner housing includes a cylindrical tube portion (161) to which the stator is fixed, and a bottom surface portion (163) extending from one end portion (161b) of the tube portion, the other end portion (161b) being located opposite to one end portion (161a) on a side closer to the compression portion, so as to approach the rotation shaft; The electric compressor according to a first aspect, wherein at least one of the cylindrical portion and the bottom surface portion is provided with an inside-outside communication portion (165) that communicates the inside and outside of the inner housing at a position located above the axis in the vertical direction.

[0149] [Fourth viewpoint] The electric compressor according to the second or third aspect, wherein the inside of the inner housing and the gap space are partitioned by the cylindrical portion and the bottom surface portion below the axis in the vertical direction so that the inside and outside of the inner housing do not communicate with each other.

[0150] [Fifth viewpoint] The electric compressor according to any one of the first to fourth aspects, wherein the housing is provided inside with a refrigerant suction passage (38) at a position adjacent to the compression section, which causes the compression section to draw in a refrigerant, a refrigerant introduction passage (45) which introduces a refrigerant from inside the inner housing to the refrigerant suction passage, and a communication passage (19, 46) which communicates the gap space with the refrigerant introduction passage below the axis in the vertical direction.

[0151] [Sixth viewpoint] The electric compressor according to a fifth aspect, wherein the communication passage is a throttle passage having a smaller cross-sectional area than the refrigerant introduction passage.

[0152] [Seventh viewpoint] The electric compressor according to a fifth or sixth aspect, wherein the refrigerant introduction channel is provided below the axis in the vertical direction.

[0153] [Eighth viewpoint] The electric compressor according to any one of the first to seventh aspects, wherein a separation plate (18) is arranged in the gap space to collide the refrigerant introduced into the gap space from the suction port, thereby promoting separation of the refrigerant into gas and liquid.

[0154] [Ninth viewpoint] The electric compressor according to any one of the first to eighth aspects, wherein the outer housing is provided with the suction port at a position facing the inner housing.

[0155] [10th viewpoint] The electric compressor according to any one of the first to ninth aspects, wherein the outer housing is provided with a protrusion (166) that protrudes in a direction approaching the rotary shaft and extends in the axial direction of the rotary shaft. [Explanation of symbols]

[0156] 10. Housing 12 Motor housing (outer housing) 14 Discharge housing 16 Inner housing 164 Interstitial Space 20 Rotation axis 30 Compression section 50 Electric motor 52 rotor 54 Stator

Claims

1. An electric compressor applied to a vapor compression refrigeration cycle (1), a housing (10); a rotating shaft (20) accommodated inside the housing; a compression section (30) that compresses a refrigerant by the 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; The housing includes: an inner housing (16) that accommodates at least a portion of the electric motor and to which the stator is fixed; an outer housing (12) that accommodates the inner housing and has a suction port (127) for a refrigerant; a discharge housing (14) through which the refrigerant compressed by the compression section is discharged and which is fixed to the external housing, The external housing and the internal housing are separated at least in part at the overlapping portions in the radial direction of the rotary shaft, and the refrigerant that flows into the inside of the external housing from the suction port flows through a gap space (164) formed between the internal housing and the external housing and is then sucked into the compression section, At least a portion of the compression unit is disposed outside the inner housing and is fixed to the outer housing via a shaft support member (40) that supports the rotation shaft, the shaft support member is disposed between the electric motor and the compression unit, and is configured to be able to guide the refrigerant that has flowed into the inner housing to a refrigerant suction passage (38) of the compression unit.

2. 2. The electric compressor according to claim 1, wherein the inner housing is provided with an inside-outside communication section (165) that communicates the inside and outside of the inner housing, and the refrigerant that flows into the inside of the outer housing from the suction port flows through the gap space (164), and then is introduced into the inside of the inner housing via the inside-outside communication section and sucked into the compression section.

3. The rotating shaft is accommodated inside the housing in such a position that an axis (CL) of the rotating shaft intersects with a vertical direction, The inner housing includes a cylindrical tube portion (161) to which the stator is fixed, and a bottom surface portion (163) extending from one end portion (161b) of the tube portion located opposite to one end portion (161a) close to the compression portion, so as to approach the rotation shaft, 2. The electric compressor according to claim 1, wherein at least one of the cylindrical portion and the bottom surface portion is provided with an inside-outside communication portion (165) that communicates the inside and outside of the inner housing, at a location located above the axis in the vertical direction.

4. 4. The electric compressor according to claim 3, wherein the inside of the inner housing and the gap space are partitioned by the cylindrical portion and the bottom surface portion below the axis in the vertical direction so that the inside and outside of the inner housing do not communicate with each other.

5. 5. The electric compressor according to claim 3, wherein the housing is provided inside with a refrigerant suction passage (38) at a position adjacent to the compression section for drawing refrigerant into the compression section, a refrigerant introduction passage (45) for guiding refrigerant from inside the inner housing to the refrigerant suction passage, and a communication passage (19, 46) below the axis in the vertical direction for communicating the gap space with the refrigerant introduction passage.

6. The electric compressor according to claim 5 , wherein the communication passage is a throttle passage having a smaller cross-sectional area than the refrigerant introduction passage.

7. The electric compressor according to claim 5 , wherein the refrigerant introduction channel is provided below the shaft center in the vertical direction.

8. 4. The electric compressor according to claim 1, wherein a separation plate (18) is disposed in the gap space to cause the refrigerant introduced into the gap space from the suction port to collide with the refrigerant, thereby promoting separation of the refrigerant into gas and liquid.

9. 4. The electric compressor according to claim 1, wherein the suction port is provided in the outer housing at a position facing the inner housing.

10. 4. The electric compressor according to claim 1, wherein the outer housing is provided with a protrusion (166) that protrudes toward the rotary shaft and extends in the axial direction of the rotary shaft.

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