WO2024085064A1 - Compresseur électrique - Google Patents

Compresseur électrique Download PDF

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Publication number
WO2024085064A1
WO2024085064A1 PCT/JP2023/037048 JP2023037048W WO2024085064A1 WO 2024085064 A1 WO2024085064 A1 WO 2024085064A1 JP 2023037048 W JP2023037048 W JP 2023037048W WO 2024085064 A1 WO2024085064 A1 WO 2024085064A1
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WO
WIPO (PCT)
Prior art keywords
housing
fixed
stator
support member
axial direction
Prior art date
Application number
PCT/JP2023/037048
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English (en)
Japanese (ja)
Inventor
智貴 方田
恭弘 沖
正人 小村
陽平 櫛田
忠資 堀田
Original Assignee
株式会社デンソー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Publication of WO2024085064A1 publication Critical patent/WO2024085064A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/24—Casings; Enclosures; Supports specially adapted for suppression or reduction of noise or vibrations
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans

Definitions

  • This disclosure relates to an electric compressor.
  • the electric compressor is Housing and A rotating shaft accommodated inside the housing; a compression section that compresses the fluid by rotating a rotating shaft; an electric motor having a rotor that rotates integrally with a rotary shaft and a stator that is fixed to a housing and drives the compression unit; a shaft support member including a first bearing portion that rotatably supports a rotating shaft; a second bearing portion that rotatably supports the rotating shaft with respect to the housing at a position different from the first bearing portion,
  • the housing is an inner housing that accommodates at least a portion of the electric motor and to which the stator is fixed; a first outer housing that houses the inner housing; a second outer housing 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, a portion that is located closest to the other side in the axial direction is defined as a second end, and an intermediate portion that is located between the first end and the second end
  • the distance between the position supporting the internal housing and the compression section and the position where vibration occurs can be made smaller than when the internal housing and the compression section are fixed in a cantilever-like manner. This reduces the vibration of the electric motor and the compression section 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 is able to suppress vibration and noise.
  • the rotating shaft is supported by both the first and second bearings, making it possible to set the sliding area of each bearing small, which makes it easier to steadily supply lubricating oil to the entire sliding surface when the rotating shaft is in a low to high rotation range, ensuring reliability.
  • FIG. 1 is a schematic configuration diagram of a refrigeration cycle including an electric compressor according to a first embodiment.
  • FIG. 1 is a schematic cross-sectional view of an electric compressor according to a first embodiment.
  • FIG. 3 is a cross-sectional view taken along line III-III of FIG.
  • FIG. 4 is an explanatory diagram for explaining the flow of an assembly operation of each component part of the compressor.
  • 11 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. 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.
  • FIG. 11A to 11C are explanatory views for explaining a process of assembling the discharge housing to the motor housing.
  • FIG. 5 is a schematic cross-sectional view of an electric compressor according to a second embodiment.
  • 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. This is a cross-sectional view taken along the line XX in FIG.
  • FIG. 11 is a schematic cross-sectional view of an electric compressor according to a third embodiment.
  • 4 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. This is a cross-sectional view taken along line XIII-XIII of Figure 12.
  • FIG. 11 is a schematic cross-sectional view of an electric compressor according to a fourth embodiment.
  • FIG. 13 is a schematic cross-sectional view of an electric compressor according to a fifth embodiment.
  • FIG. 13 is a schematic cross-sectional view of an electric compressor according to a sixth embodiment.
  • FIG. 13 is a schematic cross-sectional view of an electric compressor according to a seventh embodiment. This is a cross-sectional view taken along line XVIII-XVIII of Figure 17.
  • FIG. 13 is a schematic cross-sectional view of an electric compressor according to an eighth embodiment.
  • FIG. 13 is a schematic cross-sectional view of an electric compressor according to a ninth embodiment.
  • 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, thereby dissipating 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 depressurized by the pressure reducing device EXV by exchanging heat with the air blown from the second blower FAN2.
  • 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.
  • the refrigeration cycle device 1 uses a fluorocarbon-based refrigerant as the refrigerant.
  • the refrigerant is mixed with a lubricating oil that lubricates the various sliding parts inside the compressor ECP. A portion of the lubricating oil circulates within the cycle together with the refrigerant.
  • the refrigerant may be a refrigerant other than a fluorocarbon-based refrigerant (e.g., carbon dioxide, propane).
  • 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 up and down arrows 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 as FIG. 2.
  • the compressor ECP includes a housing 10, a rotating shaft 20, a compression section 30, and an electric motor 50.
  • the rotating shaft 20, the compression section 30, and the electric motor 50 are housed 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 section 30 and the electric motor 50 are aligned in a substantially horizontal direction and installed in the vehicle.
  • the housing 10 comprises 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 external 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.
  • the motor housing 12 accommodates the internal housing 16.
  • the motor housing 12 is a cylindrical shape with a bottom that is open on one side in the axial direction Dax of the rotating shaft 20.
  • 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 the outer peripheral portion of the first bottom wall portion 121.
  • the motor housing 12 is configured as a seamless, one-piece molded product with the first bottom wall portion 121 and the first outer peripheral wall portion 122. In this embodiment, the motor housing 12 constitutes the "first outer housing.”
  • the motor housing 12 has a stepped shape with a step surface 123 formed on the inner portion of the first outer wall portion 122.
  • the step surface 123 intersects with the axial direction Dax.
  • the step surface 123 extends along the radial direction Dr of the rotating shaft 20.
  • the step surface 123 is a surface that connects a first housing portion 124, which has a smaller inner diameter in 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 is connected 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 part of the compression portion 30 are housed inside the second housing portion 125.
  • the first bottom wall portion 121 of the motor housing 12 is provided with an airtight terminal to which the electrical wiring of the electric motor 50 is connected.
  • the electric motor 50 is electrically connected to an inverter (not shown) via the airtight terminal.
  • the motor housing 12 is formed with a refrigerant suction port.
  • 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, low-temperature atmosphere. This allows the electric motor 50 to be cooled, improving the efficiency and reliability of the electric motor 50.
  • the discharge housing 14 forms a space into which the refrigerant compressed in the compression section 30 is discharged.
  • the discharge housing 14 is a cylindrical shape with a bottom that is open on the other side in the axial direction Dax of the rotating shaft 20.
  • 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. In this embodiment, the discharge housing 14 constitutes the "second outer housing.”
  • the discharge housing 14 is fixed to the motor housing 12 by fastening bolts 15 with the opening edge on the other side of the axial direction Dax of the discharge housing 14 butting against the opening edge on one side of the axial direction Dax of the motor housing 12.
  • 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 and the atmosphere consisting of high-pressure, high-temperature refrigerant discharged from the compression section 30 are separated by a sealing member (not shown).
  • the discharge housing 14 has a refrigerant discharge port formed therein.
  • 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 at the discharge port. Therefore, the lubricating oil in the refrigerant discharged from the compression section 30 is stored inside the discharge housing 14.
  • 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 coincides with the central axis of the first outer peripheral wall portion 122 of the motor housing 12.
  • the rotating shaft 20 has an eccentric shaft portion 21 at one end in the axial direction Dax, which is eccentric from the axis CL of the rotating shaft 20.
  • the eccentric shaft portion 21 is integral 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.
  • the rotating shaft 20 has an enlarged diameter section 22 adjacent to the eccentric shaft section 21, the outer diameter of which is enlarged.
  • This enlarged diameter section 22 is provided with a balance weight 23 to suppress eccentric rotation of the rotating shaft 20.
  • An oil supply passage 24 is formed inside the rotating shaft 20 to supply lubricating oil to the eccentric bearing portion 344, the first bearing portion 411 described later, the second bearing portion 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 portion 344, the first bearing portion 411 described later, the second bearing portion 17, etc. via the oil supply path and the oil supply passage 24.
  • 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, etc.
  • the fixed scroll 32 has a fixed base portion 321 formed in a disk shape and a spiral-shaped fixed tooth portion 322 that protrudes from the fixed base portion 321 toward the rotating scroll 34 on the other side in the axial direction Dax.
  • the orbiting scroll 34 has a rotating base portion 341 formed in a disk shape and a spiral-shaped orbiting tooth portion 342 that protrudes from the orbiting base portion 341 toward the fixed scroll 32 on one side in the axial direction Dax.
  • the orbiting scroll 34 has a cylindrical first boss portion 343 on the side of the orbiting base portion 341 opposite 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. Note that the eccentric bearing portion 344 may be made of a bearing other than a plain bearing.
  • An Oldham ring 35 is also 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.
  • the orbiting scroll 34 performs an orbital motion (i.e., an orbital motion) around the axis center CL of the rotating shaft 20.
  • the rotation prevention mechanism may be composed of something other than the Oldham ring 35.
  • 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.
  • the working chambers 31 move from the outer periphery to the center while decreasing in volume.
  • refrigerant is sucked from a refrigerant suction port formed on the outer periphery of the fixed scroll 32 and 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.
  • FIG. 2 and other figures only one of the multiple working chambers 31 is labeled with a reference number.
  • a discharge hole 323 is formed in the center of the fixed base plate part 321 to discharge the refrigerant compressed in the working chamber 31.
  • a reed valve (not shown) that serves as a check valve to prevent backflow of the refrigerant into the working chamber 31, and a stopper 324 that regulates 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 stopper 324 are fastened and fixed to the fixed base plate part 321 by bolts 325.
  • 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 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 is formed at the bottom of the discharge plate 36 to discharge the refrigerant from the muffler chamber 361. Note that the discharge plate 36 is not a required component of the compression section 30.
  • the fixed scroll 32 and the discharge plate 36 have approximately 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.
  • the compression section 30 thus configured is fixed to the step surface 123 of the motor housing 12 by the mounting bolt 37 via the shaft support member 40.
  • the step surface 123 of the motor housing 12 constitutes the fixing portion FP that fixes the compression section 30.
  • 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. Between the shaft support member 40 and the fixed scroll 32, a space is formed 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 steel material, aluminum alloy, etc.
  • 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.
  • 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.
  • the shaft support member 40 has a first bearing portion 411 formed on the inner periphery 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 coated on its inner periphery.
  • 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.
  • a circular thrust plate 44 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.
  • 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.
  • the shaft support member 40 is provided with a refrigerant introduction passage that introduces refrigerant from the inside of the inner housing 16 (described later) to the compression section 30.
  • This refrigerant introduction passage is provided at least below the axis center CL of the shaft support member 40.
  • the shaft support member 40 configured in this manner is fixed to the motor housing 12 together with the compression section 30 by the mounting bolts 37.
  • the fixing portion FP of the shaft support member 40 that fixes the shaft support member 40 to the motor housing 12 will be described later.
  • 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.
  • 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 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 arranged inside the stator 54.
  • 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.
  • balance weights 521 and 522 are attached to the side of the rotor 52 to offset the imbalance of the eccentric rotation of the orbiting scroll 34, etc.
  • the stator 54 has a stator core 541 made of a metallic magnetic material and a coil 542 wound around the stator core 541.
  • the stator 54 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.
  • 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.
  • the inner housing 16 is made of the same type of steel material as the stator 54 (e.g., iron).
  • the operating environment range of the on-vehicle compressor ECP is assumed to be -40 to 100°C, taking into consideration everything from low outside temperatures to heat generated by the main motor and engine.
  • Electromagnetic steel sheets are generally used for the stator core 541. Taking these factors into consideration, it is desirable for the constituent material of the inner housing 16 to have a linear expansion coefficient of 20 ⁇ 10 -6 [/°C] or less.
  • the clamping margin can be set appropriately in the expected temperature range. For example, if a metal material with a large linear expansion coefficient, such as aluminum, is used as the constituent material of the internal housing 16, the difference in the linear expansion coefficient with the stator 54 will be large. Therefore, when a clamping margin that can ensure tension in the high temperature range is set, assuming a low outside air range, the clamping margin increases. This increases the distortion of the stator core 541 and reduces the efficiency of the electric motor 50. Conversely, if the clamping margin is set so that the effect of distortion is small at low outside air temperatures, there is a risk that the tension will decrease and the fixation of the stator 54 will become unstable at high outside air temperatures.
  • the internal housing 16 has a generally cup shape.
  • 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 the one end portion 161a toward 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 a single molded product.
  • the support portion 163 has a circular bottom portion 163a connected to the other end portion 161b of the tube portion 161, and a cylindrical second boss portion 163b provided in 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 peripheral side of the second boss portion 163b.
  • the second bearing portion 17 is composed of a plain bearing.
  • the second bearing portion 17 is composed of a cylindrical steel member and a resin layer coated on its inner peripheral surface.
  • the second bearing portion 17 may be composed 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 composed of a bearing other than a plain bearing.
  • 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.
  • the entire flange portion 162 of the internal housing 16 faces the 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 the fixing bolts 18.
  • the stator facing surface 421 has a plurality of female threaded holes into which the fixing bolts 18 can be screwed.
  • the flange portion 162 has a plurality of insertion holes SH through which the fixing bolts 18 are inserted, corresponding to the female threaded holes.
  • the internal 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.
  • the inner housing 16 has an inside-outside communication part that penetrates 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 the gap space 164 between the motor housing 12 and the inner housing 16 are partitioned by the tube part 161 and the bottom part 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.
  • 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 communication part.
  • the internal housing 16, shaft support member 40, and compression section 30 are arranged in this order in the axial direction Dax.
  • the portion of the internal housing 16 and 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
  • the portion located between the first end E1 and the second end E2 is defined as the intermediate portion E3.
  • the internal housing 16 and compression section 30 have a part of the intermediate portion E3 fixed to a fixed portion FP set on the motor housing 12, and are separated from other portions in the radial direction Dr except for the fixed portion FP. Note that the intermediate portion E3 does not include the first end E1 or the second end E2.
  • the internal housing 16 and the compression section 30 are fixed to the fixed part FP at the portion between the stator 54, which is a heavy part, and the compression section 30.
  • the end face of the stator 54 that faces the stator facing surface 421 in the axial direction Dax is defined as 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.
  • the step surface 123 of the motor housing 12 constitutes the fixing portion FP that fixes the inner housing 16 and the compression section 30.
  • the inner housing 16, the shaft support member 40, and the compression section 30 are fixed to the motor housing 12 by the mounting bolts 37.
  • 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 portion where they overlap with the step surface 123 in the axial direction Dax.
  • the fixed scroll 32 and the discharge plate 36 are fixed to the step surface 123 of the motor housing 12 via the shaft support member 40, while separated from the second housing part 125.
  • the shaft support member 40 has a through 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 while separated from the second housing part 125.
  • the stator facing surface 421 and the flange portion 162 are in contact with each other over substantially the entire portion that overlaps with the step surface 123 in the axial direction Dax.
  • 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. As shown in FIG. 3, the inner housing 16 is fixed to the step surface 123 of the motor housing 12 with the portion other than the flange portion 162 spaced apart from the first housing part 124. 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.
  • the axial length Dax of the inner housing 16 is smaller than the axial length Dax from the step surface 123 to the first bottom wall portion 121 in 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.
  • 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.
  • 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.
  • the inner housing 16 with the stator 54 fixed thereto is prepared.
  • the internal housing 16 is fixed to the shaft support member 40.
  • 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 threaded hole of the shaft support member 40.
  • the axis of the first bearing portion 411 and the axis of the second bearing portion 17 are aligned. Note that although FIG. 5 shows only one fixing bolt 18, in reality, the internal housing 16 is fixed to the shaft support member 40 by multiple fixing bolts 18.
  • the inner housing 16, the shaft support member 40, and the compression section 30 are fixed to the motor housing 12.
  • 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 threaded hole of the step surface 123.
  • 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 the other parts of the motor housing 12 and the discharge housing 14 except for the fixed part FP.
  • the inner housing 16, the shaft support member 40, and the compression section 30 are actually fixed to the motor housing 12 by multiple mounting bolts 37.
  • the discharge housing 14 is fixed to the motor housing 12.
  • 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 face 126 of the motor housing 12.
  • FIG. 7 shows only one fastening bolt 15, in reality the discharge housing 14 is fixed to the motor housing 12 by multiple fastening bolts 15.
  • the refrigerant flows into the 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 internal/external communication part.
  • the internal/external communication part is formed above the axis CL of the rotating shaft 20 in the inner housing 16.
  • Gas refrigerant, which has a low specific gravity, is introduced into the inside of the inner housing 16 via the internal/external communication part, while liquid refrigerant, which has a high specific gravity, is stored in the gap space 164.
  • the refrigerant introduced into the inner housing 16 passes through the gaps between the 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.
  • 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 from the outlet provided in the discharge plate 36 to the inside of the discharge housing 14, and is then discharged from the discharge port provided in the discharge housing 14 as discharge refrigerant for the compressor ECP.
  • the lubricating oil contained in the discharge refrigerant is separated by the oil separator provided in the discharge port, and falls under its own weight to be stored on the lower side of the discharge housing 14.
  • the lubricating oil is then 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.
  • Some of the lubricating oil supplied to the sliding parts flows into the gap space 164, but is guided to the refrigerant introduction passage via a communication flow passage that connects the gap space 164 and the refrigerant introduction passage.
  • vibrations occur in the stator 54 due to electromagnetic forces 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 internal housing 16.
  • the compression section 30 compresses low-temperature, low-pressure refrigerant in the working chamber 31, and discharges it as 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 center of gravity and eliminate imbalance, and there may be variation. Such variation causes imbalance with respect to the axis CL of the rotating shaft 20, which generates vibration.
  • the compression section 30 also compresses the refrigerant as the volume of the working chamber 31 decreases. During this process, the contact points between the tooth sides of the fixed scroll 32 and orbiting scroll 34 that form the working chamber 31 do not move smoothly but move slightly and intermittently due to variations in the accuracy of the spirals of the scrolls 32 and 34, causing vibrations.
  • the compressor ECP of this embodiment has the inner housing 16 and a part of the intermediate portion E3 in the compression section 30 fixed to the fixed portion FP set in the motor housing 12.
  • the compressor ECP in the compressor ECP, a part of the intermediate portion E3 in the inner housing 16 and the compression section 30 is separated from other portions, except for the fixed portion FP, in the radial direction Dr of the rotating shaft 20. In this way, if there is a gap between the inner housing 16 and the compression section 30 and the motor housing 12 and the discharge housing 14, the vibrations of the stator 54 and the compression section 30 are prevented 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.
  • 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 short, making it easier to steadily supply lubricating oil to the entire sliding surface when the rotating shaft 20 is in a low to high rotation range, ensuring reliability.
  • the compressor ECP of this embodiment has the following features:
  • the internal housing 16 and the compression section 30 are fixed to the fixing part FP in the range from the stator facing surface 421 to the core end face 543 in the axial direction Dax.
  • This means that the compression section 30 and the internal 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 section 30.
  • 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.
  • 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 the components that constitute 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, for example, in the first housing portion 124 of the first outer peripheral wall portion 122, rather than in the first bottom wall portion 121 of the motor housing 12.
  • 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 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 periphery 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.
  • the internal housing 16 is simply a cylinder with both ends open, when the stator 54 vibrates, the internal housing 16 also vibrates in response to the vibration, which can cause slight deformation. This type of deformation is undesirable because it increases the vibration transmitted from the internal housing 16 to the motor housing 12. The same is true when the internal housing 16 is configured to partially support the stator 54 with multiple plate-shaped support pieces.
  • the compressor ECP of this embodiment has an internal housing 16 that is generally cup-shaped, with a tubular portion 161, a support portion 163, and a flange portion 162. This makes it easier to ensure rigidity compared to a simple cylindrical shape, and makes it possible to suppress deformation of the internal housing 16 due to vibration of the stator 54.
  • the support portion 163 is integrally formed with the cylindrical portion 161 of the inner housing 16, the rigidity of the support portion 163 can be increased, further suppressing deformation caused by the load received by the second bearing portion 17 from the rotating shaft 20. This makes it possible to reduce the amount of imbalance in the axis center CL of the rotating shaft 20.
  • the internal housing 16, shaft support member 40, and 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 internal housing 16 and compression section 30 and the motor housing 12 and discharge housing 14, compared to when the stator 54 and compression section 30 are fixed to the inner circumferential surfaces of the motor housing 12 and discharge housing 14. This makes it difficult for vibrations of the stator 54 and compression section 30 to be transmitted to the motor housing 12 and discharge housing 14, thereby suppressing sound and vibrations radiated to the outside of the motor housing 12 and discharge housing 14.
  • the second bearing portion 17 is supported by the inner housing 16.
  • the flange portion 162 of the inner housing 16 is fixed to the shaft support member 40 by the fixing bolt 18.
  • the axis of the first bearing portion 411 and the axis of the second bearing portion 17 can be adjusted to be coaxial.
  • the stator 54 is fixed to the internal housing 16 by shrink fitting or press fitting, even if a small deformation occurs in the internal housing 16, 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 magnetic flux bias and imbalance due to whirling of the rotating shaft 20 can be reduced, so vibration can be sufficiently suppressed.
  • each bearing 411, 17 can be reduced, ensuring reliability.
  • the axis of each bearing 411, 17 can be realized with a simple and highly rigid structure such as the fixing bolt 18, making it possible to reduce weight and simplify the shape.
  • 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 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 tightening margin can be set appropriately.
  • the same kind of metallic material means metallic materials that have the same most abundant element in their chemical composition.
  • the term “same kind 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.
  • 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.
  • 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, so 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 inside the motor housing 12. This makes it possible to reduce the tightening margin associated with shrink-fitting or press-fitting the stator 54 into the cylindrical portion 161 of the inner housing 16.
  • 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.
  • 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 in question is in a high-pressure, high-temperature atmosphere. This also applies to the following embodiments.
  • the shaft support member 40 and the flange portion 162 of this embodiment have a contact portion CP1 that contacts with each other and a non-contact portion NP1 that is separated by a predetermined distance at the portion where they overlap with the step surface 123 in the axial direction Dax.
  • 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.
  • Figure 9 shows 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 from the illustration.
  • 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 that protrudes in a direction approaching the step surface 123.
  • the protrusion 423 that constitutes 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 that overlaps with the head of the mounting bolt 37 in the axial direction Dax.
  • the 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.
  • the rest of the configuration is the same as in the first embodiment.
  • the compressor ECP of this embodiment can obtain the same effects as in the first embodiment, which are achieved from a common configuration or an equivalent configuration to the first embodiment.
  • the shaft support member 40 and the flange portion 162 have a contact portion CP1 and a non-contact portion NP1 that contact each other.
  • the contact portion CP1 is provided around the 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, the sound and vibrations radiated to the outside from the motor housing 12 and the discharge housing 14 can be suppressed.
  • the recess 422 and the protrusion 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.
  • 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.
  • an elastically deformable elastic member EM1 is disposed in the non-contact portion NP1 in a compressed state in the axial direction Dax.
  • the elastic member EM1 is made of, for example, a rubber material. Note that in Figure 12, the elastic member EM1 is hatched with dots to clarify the position of the elastic member EM1.
  • the thickness T2 of the elastic member EM1 is greater than the groove depth T1 at the non-contact portion NP1. As a result, the elastic member EM1 is compressed by the axial force of the mounting bolt 37.
  • the rest of the configuration 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 from a common configuration or an equivalent configuration to the second embodiment.
  • an elastically deformable elastic member EM1 is arranged in a state compressed in the axial direction Dax. In this way, if the elastic member EM1 is arranged between the flange portion 162 and the shaft support member 40, vibrations between the flange portion 162 and the shaft support member 40 are damped by the elastic member EM1.
  • vibrations of the electric motor 50 and compression section 30 are less likely to be transmitted to the motor housing 12, etc., so sound and vibrations radiated from the motor housing 12, etc. to the outside can be suppressed.
  • higher-order vibration modes called local vibrations can occur on the surface of the compression section 30, but these vibrations can be reduced by the elastic member EM1.
  • the mounting bolts 37 also serve as part of the vibration-proofing 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 in the compressor ECP and reducing costs.
  • 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.
  • 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.
  • the step surface 123 and the flange portion 162 of the motor housing 12 in this embodiment have a contact portion CP2 that contacts each other in the axial direction Dax, and a non-contact portion NP2 that is spaced a predetermined distance apart.
  • the protrusion that constitutes the contact portion CP2 is provided on the stepped surface 123 of the motor housing 12. Specifically, the contact portion CP2 is set around the portion of the stepped surface 123 through which the mounting bolt 37 is inserted.
  • an elastically deformable elastic member EM2 is arranged in the non-contact portion NP2 in a compressed state in the axial direction Dax.
  • the elastic member EM1 is made of, for example, a rubber material.
  • 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.
  • the rest of the configuration is the same as the third embodiment.
  • the compressor ECP of this embodiment can obtain the same effects as the second and third embodiments, which are achieved from a configuration common to or equivalent to the second and third embodiments.
  • the compressor ECP of this embodiment has the following features:
  • the step surface 123 and the flange portion 162 have a contact portion CP2 and a non-contact portion NP2.
  • the contact portion CP2 is provided around the portion of the step surface 123 and the flange portion 162 where the mounting bolt 37 is inserted. This reduces the contact area between the motor housing 12 and the flange portion 162, making it difficult for vibrations of the stator 54 and the compression portion 30 to be transmitted to the motor housing 12, etc., and thus suppresses sound and vibrations radiated to the outside from the motor housing 12, etc.
  • 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.
  • 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.
  • the elastic member EM2 is exemplified as being made of a rubber material, but the elastic member EM2 may be made of a material other than a rubber material. Furthermore, the elastic member EM2 may be disposed over the entire area of the non-contact portion NP1, or may be disposed over a portion of the non-contact portion NP1. Note that in the fourth embodiment, the elastic member EM2 is not an essential component and may be omitted.
  • 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.
  • 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 discharge plate 36 are housed inside.
  • the motor housing 12 and discharge housing 14 of this embodiment are fixed by fastening bolts 15 with their respective opening edges abutting against the shaft support member 40.
  • 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 has 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.
  • the internal housing 16 does not include the flange portion 162 described in the first embodiment.
  • the outer diameter of the internal housing 16 is the same size as the outer diameter of the compression section 30.
  • the internal housing 16 has a cylindrical portion 161 with a greater thickness in the radial direction Dr than that described in the first embodiment.
  • the internal housing 16 has multiple female threaded holes formed on the opening edge of the cylindrical portion 161, into which the mounting bolts 37 can be screwed.
  • the inner housing 16 is fixed to the large diameter portion 42 of the shaft support member 40 together with the fixed scroll 32 and the discharge plate 36 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 are fixed to the motor housing 12 and the discharge housing 14 via the shaft support member 40.
  • the opening edges of the motor housing 12 and the discharge housing 14 respectively form the fixing portion FP.
  • the rest of the configuration is the same as in the first embodiment.
  • the compressor ECP of this embodiment can obtain the same effects as in the first embodiment, which are achieved from a common configuration or an equivalent configuration to the first embodiment.
  • the compressor ECP of this embodiment has the following features:
  • the compressor ECP can be configured to be smaller than that 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.
  • 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, so the effects of vibrations of the inner housing 16 and the compression section 30 can be reduced. As a result, the compressor ECP can be made to have low vibrations and low noise.
  • 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 approximately constant.
  • the discharge housing 14 also houses the fixed scroll 32 and discharge plate 36 inside.
  • the motor housing 12 and discharge housing 14 of this embodiment are fixed by fastening bolts 15 with their respective opening edges abutting against the flange portion 162 and the shaft support member 40.
  • 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.
  • 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.
  • the opening edges of the motor housing 12 and the discharge housing 14 form the fixing portion FP.
  • the rest of the configuration is the same as the fifth embodiment.
  • the compressor ECP of this embodiment can obtain the same effects as the fifth embodiment, which are achieved from a common configuration or an equivalent configuration.
  • 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 approximately constant.
  • the discharge housing 14 also houses the fixed scroll 32 and discharge plate 36 inside.
  • the motor housing 12 and discharge housing 14 of this embodiment are fixed by fastening bolts 15 with their respective opening edges abutting against the shaft support member 40.
  • the internal 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 from separate members.
  • the second cylindrical portion 166 and the support portion 167 are formed integrally.
  • 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 approximately 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.
  • the support portion 167 has a circular ring-shaped bottom portion 167a and a cylindrical second boss portion 167b provided in the center of the bottom portion 167a.
  • the bottom portion 167a and the second boss portion 167b are configured as a single molded part.
  • the second cylindrical portion 166, the support portion 167, and the stator 54 are formed with insertion holes SH5 and SH6 through which the bolts BT1 are inserted to fix the internal housing 16 and the stator 54 to the shaft support member 40.
  • the first cylindrical portion 165 is also formed with multiple female threaded holes into which the bolts BT1 can be screwed.
  • the stator 54 has multiple bulging portions 544 that bulge in a direction away from the rotating shaft 20 on the outer periphery of the stator core 541.
  • Multiple insertion holes SH6 through which the bolts BT1 are inserted are formed in the bulging portions 544.
  • the stator 54 is fixed to the internal 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 internal housing 16 is integrally formed with the shaft support member 40. Therefore, the internal housing 16 is fixed to the shaft support member 40.
  • 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.
  • the opening edges of the motor housing 12 and the discharge housing 14 respectively form the fixing portion FP.
  • the rest of the configuration is the same as the fifth embodiment.
  • the compressor ECP of this embodiment can obtain the same effects as the fifth embodiment, which are achieved from a common configuration or an equivalent configuration.
  • the compressor ECP of this embodiment has the following features:
  • stator 54 is fixed to the inner housing 16 by the bolt BT1, so that distortion of the stator 54 can be suppressed when the stator 54 is fixed to the inner housing 16.
  • 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.
  • the internal 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, as in the seventh embodiment.
  • the first cylindrical portion 165, the second cylindrical portion 166, and the support portion 167 are each formed from separate members.
  • the stator 54 is fixed to the inner housing 16 by the bolt BT1, as in the seventh embodiment.
  • the inner housing 16 is also fixed to the shaft support member 40, as in the seventh embodiment.
  • the outer diameter of the large diameter portion 42 of the shaft support member 40 is set to approximately the same dimensions as 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 mounting bolts 37.
  • the inner housing 16 and the compression section 30 are fixed to the step surface 123 of the motor housing 12 by the mounting bolt 37 via the shaft support member 40.
  • the step surface 123 of the motor housing 12 constitutes the fixing part FP.
  • the rest of the configuration is the same as in the first embodiment.
  • the compressor ECP of this embodiment can obtain the same effects as in the first embodiment, which are achieved from a common configuration or an equivalent configuration to the first embodiment.
  • the compressor ECP of this embodiment has the following features:
  • the compressor ECP fixes the stator 54 to the inner housing 16 with the bolts BT1, which prevents distortion of the stator 54 when fixing the stator 54 to the inner housing 16.
  • the support portion 163 is configured with a portion connected to the cylindrical portion 161 and a portion supporting the second bearing portion 17 as separate bodies.
  • the support portion 163 has a circular ring-shaped 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 configured integrally with the second bottom portion 163c.
  • the second bearing portion 17 is formed on the inner periphery side of the second boss portion 163b.
  • the rest of the configuration is the same as in the first embodiment.
  • the compressor ECP of this embodiment can obtain the same effects as in the first embodiment, which are achieved from a common configuration or an equivalent configuration to the first embodiment.
  • the compressor ECP of this embodiment has the following features:
  • the inner housing 16 is constructed such that the tube portion 161 and the flange portion 162 are integrally formed, which makes it easier to ensure rigidity compared to a simple cylindrical shape, and makes it possible to suppress deformation of the inner housing 16 due to vibration of the stator 54.
  • 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 precision of the second bearing portion 17.
  • the internal housing 16 is not limited to being generally cup-shaped, and may be, for example, cylindrical. Furthermore, the internal housing 16 is desirably made of the same metal material as the stator 54, but is not limited to this, and may be, for example, made of a different metal material than the stator 54. A portion of the internal housing 16 may be in contact with the motor housing 12 in the axial direction Dax.
  • the various devices constituting the compressor ECP may be fixed by elements other than bolts.
  • 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.
  • 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.
  • the second bearing portion 17 may be provided on an element other than the inner housing 16.
  • 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, but may be, 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.
  • the compressor ECP is described as being applied to a vehicle air conditioner, but the present invention is not limited to this, and the compressor ECP can also be applied to other air conditioners, temperature control devices for various devices, etc. Furthermore, the compressor ECP is not limited to a horizontally mounted structure in which the compression section 30 and the electric motor 50 are arranged in a substantially horizontal direction.
  • the electric compressor is 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 (411) 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 (
  • 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) facing 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 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.
  • 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,
  • 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).
  • 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.
  • 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,
  • CP2 contact portion
  • NP2 non-contact portion
  • 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).

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  • Compressor (AREA)

Abstract

L'invention concerne un compresseur électrique (ECP) qui comprend : un boîtier (10) ; un arbre rotatif (20) ; une partie de compression (30) ; un moteur électrique (50) ; un élément de support d'arbre (40) comprenant une première partie de palier (411) ; et une seconde partie de palier (17). Le boîtier comprend : un boîtier interne (16) ; un premier boîtier externe (12) recevant le boîtier interne ; et un second boîtier externe (14) fixé au premier boîtier externe. Du boîtier interne et de la partie de compression, une partie située le plus proche d'un côté dans une direction axiale de l'arbre rotatif est définie comme une première extrémité (E1), une partie située le plus proche de l'autre côté dans la direction axiale est définie comme une seconde extrémité (E2), et une partie intermédiaire (E3) est située entre la première extrémité et la seconde extrémité. Pour l'heure, du boîtier interne et de la partie de compression, une partie de la partie intermédiaire est fixée à une partie fixe (FP) définie dans le premier boîtier externe et/ou le second boîtier externe, et est espacée d'autres parties, à l'exclusion de la partie fixe, dans une direction radiale de l'arbre rotatif.
PCT/JP2023/037048 2022-10-21 2023-10-12 Compresseur électrique WO2024085064A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022169160A JP2024061302A (ja) 2022-10-21 2022-10-21 電動圧縮機
JP2022-169160 2022-10-21

Publications (1)

Publication Number Publication Date
WO2024085064A1 true WO2024085064A1 (fr) 2024-04-25

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Application Number Title Priority Date Filing Date
PCT/JP2023/037048 WO2024085064A1 (fr) 2022-10-21 2023-10-12 Compresseur électrique

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Country Link
JP (1) JP2024061302A (fr)
WO (1) WO2024085064A1 (fr)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5222205U (fr) * 1975-08-05 1977-02-17
JPS58165272U (ja) * 1982-04-30 1983-11-02 三菱重工業株式会社 アキュムレータ内蔵型密閉ロータリ圧縮機
JPH03202693A (ja) * 1989-06-22 1991-09-04 Mitsubishi Electric Corp 密閉型電動圧縮機及びその組立用治具
JPH041497A (ja) * 1990-04-17 1992-01-06 Mitsubishi Electric Corp 中吊り式横置形回転圧縮機
JP2002227767A (ja) * 2001-01-30 2002-08-14 Mitsubishi Electric Corp 密閉型圧縮機
JP2005248844A (ja) * 2004-03-04 2005-09-15 Mitsubishi Electric Corp 密閉型圧縮機
JP2007100544A (ja) * 2005-09-30 2007-04-19 Sanyo Electric Co Ltd 電動要素を収納した圧縮機
JP2008002420A (ja) * 2006-06-26 2008-01-10 Matsushita Electric Ind Co Ltd 流体機械
JP2022060787A (ja) * 2020-10-05 2022-04-15 三菱重工サーマルシステムズ株式会社 電動圧縮機

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5222205U (fr) * 1975-08-05 1977-02-17
JPS58165272U (ja) * 1982-04-30 1983-11-02 三菱重工業株式会社 アキュムレータ内蔵型密閉ロータリ圧縮機
JPH03202693A (ja) * 1989-06-22 1991-09-04 Mitsubishi Electric Corp 密閉型電動圧縮機及びその組立用治具
JPH041497A (ja) * 1990-04-17 1992-01-06 Mitsubishi Electric Corp 中吊り式横置形回転圧縮機
JP2002227767A (ja) * 2001-01-30 2002-08-14 Mitsubishi Electric Corp 密閉型圧縮機
JP2005248844A (ja) * 2004-03-04 2005-09-15 Mitsubishi Electric Corp 密閉型圧縮機
JP2007100544A (ja) * 2005-09-30 2007-04-19 Sanyo Electric Co Ltd 電動要素を収納した圧縮機
JP2008002420A (ja) * 2006-06-26 2008-01-10 Matsushita Electric Ind Co Ltd 流体機械
JP2022060787A (ja) * 2020-10-05 2022-04-15 三菱重工サーマルシステムズ株式会社 電動圧縮機

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