JP2024127087A - Electric Compressor - Google Patents

Abstract

To provide a motor-driven compressor capable of exerting a vibration-proof function properly.SOLUTION: A compressor 1 includes an outside housing, a rotary shaft 20, a compression part 30, an electric motor 50, and a vibration-proof member 60. The vibration-proof member 60 includes a plurality of spring parts 611, 612 formed into a plate-like shape or a rod-like shape. The outside housing and an inside structure body ST are connected with each other via the plurality of spring parts 611, 612 in a state where an inner surface of the outside housing and an outer surface of the inside structure body ST are separated in the radial direction Dr of the rotary shaft 20. The plurality of spring parts 611, 612 are connected to a first fixing part FP1 in which one end side of the spring parts 611, 612 is set on the inner surface of the outside housing. Also, the plurality of spring parts 611, 612 are connected to a second fixing part FP2 which is set at a position in which the other end side of the spring parts 611, 612 is not overlapped with the first fixing part FP1 in the axial direction Dax of the rotary shaft 20 out of the inside structure body ST.SELECTED DRAWING: Figure 1

Description

This disclosure relates to an electric compressor.

Conventionally, there is known an electric compressor equipped with a suspension mechanism that supports an internal structure consisting of a compression element and an electric element inside a sealed container by a pair of upper and lower suspension springs and a discharge pipe (see, for example, Patent Document 1).

Japanese Unexamined Patent Publication No. 4-1497

The inventors have investigated a vibration-proofing structure that prevents vibrations from the internal structure from being transmitted to the external housing by sandwiching elastic rubber between the external housing, which is the outer shell of the electric compressor, and the internal structure to prevent them from coming into direct contact with each other, and by bending the rubber in the axial direction of the rotating shaft.

However, when elastic rubber is sandwiched between the external housing and the internal structure and deflected in the axial direction of the rotating shaft, as in the above vibration-proof structure, it is difficult to set the spring constant of the elastic rubber to the desired state, making it difficult to properly demonstrate the vibration-proofing function. This was discovered after extensive research by the inventors.

The objective of this disclosure is to provide an electric compressor that can adequately perform vibration isolation functions.

The invention described in claim 1 is
An electric compressor,
An outer housing (12, 14) that constitutes an outer shell;
A rotating shaft (20) housed inside an outer housing;
A compression section (30) that compresses a fluid by rotating a rotating shaft;
An electric motor (50) for driving the compression section;
a vibration-proof member (60) that is interposed between an internal structure (ST) including a compression unit and an electric motor and the external housing inside the external housing to suppress transmission of vibration;
The vibration-proof member includes a plurality of spring portions (611, 612, 623, 633) formed in a plate or rod shape,
the outer housing and the inner structure are connected to each other via a plurality of spring portions in a state in which an inner surface of the outer housing and an outer surface of the inner structure are spaced apart from each other in a radial direction of the rotation shaft;
The multiple spring portions have one end connected to a first fixed portion (FP1) set on the inner surface of the external housing, and the other end connected to a second fixed portion (FP2) set in a position within the internal structure that does not overlap with the first fixed portion in the axial direction of the rotation shaft.

In this way, if the inner surface of the external housing and the outer surface of the internal structure are connected via multiple spring parts while being spaced apart in the radial direction of the rotating shaft, the vibration of the internal structure is damped by the spring parts, making it difficult for the vibration of the internal structure to be transmitted to the external housing. As a result, the transmission of vibration from the external housing to the surrounding air, i.e., the radiation of noise, can be suppressed.

In particular, in the electric compressor of the present disclosure, the second fixed portion of the internal structure is provided at a position that does not overlap with the first fixed portion of the external housing in the axial direction of the rotating shaft. In this manner, when the multiple spring portions are connected to the first fixed portion and the second fixed portion, the multiple spring portions are not sandwiched between the inner surface of the external housing and the outer surface of the internal structure in the axial direction of the rotating shaft and do not bend, so the spring constants of the multiple spring portions can be set arbitrarily. Therefore, with the electric compressor of the present disclosure, the vibration-proofing function can be properly exerted and the transmission of vibration to the outside can be suppressed.

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.

1 is a schematic axial cross-sectional view of an electric compressor according to a first embodiment. FIG. This is a cross-sectional view of FIG. FIG. 4 is a schematic cross-sectional view of a spring portion of the vibration-proof spring. 13 is a cross-sectional view showing a modified example of the spring portion of the vibration-proof spring. FIG. FIG. 2 is an explanatory diagram for explaining noise characteristics of an electric compressor. FIG. 6 is a schematic radial cross-sectional view of an electric compressor according to a second embodiment. FIG. 11 is a schematic axial cross-sectional view of an electric compressor according to a third embodiment. FIG. 8 is an enlarged view of a portion VIII of FIG. 7 . 11 is an explanatory diagram for explaining displacement of a joint pipe when an internal structure vibrates. FIG. FIG. 11 is a schematic axial cross-sectional view of an electric compressor according to a fourth embodiment. 11 is a cross-sectional view taken along the line XI-XI of FIG. FIG. 11 is an enlarged view of a portion XII in FIG. FIG. 13 is a schematic axial cross-sectional view of an electric compressor according to a fifth embodiment. FIG. 14 is an enlarged view of a portion XIV of FIG. 13.

Embodiments of the present disclosure will be described below with reference to the drawings. In the following embodiments, parts that are the same as or equivalent to those described in the preceding embodiments may be given the same reference numerals, and their description may be omitted. In addition, in the embodiments where only some of the components are described, the components described in the preceding embodiments may be applied to the other parts of the components. The following embodiments may be partially combined with each other, as long as the combination does not cause any problems, even if not specifically stated.

First Embodiment
The present embodiment will be described with reference to Figures 1 to 5. In the present embodiment, an example will be described in which an electric compressor according to the present disclosure (hereinafter, referred to as compressor 1) is applied to a refrigeration cycle device constituting a vehicle air conditioner.

The refrigeration cycle device constitutes a vapor compression type refrigeration cycle. In addition to the compressor 1, the refrigeration cycle device is equipped with a radiator that dissipates heat from the refrigerant, a pressure reducing device that reduces the pressure of the refrigerant that has passed through the radiator, and an evaporator that evaporates the refrigerant that has been reduced in pressure by the pressure reducing device. The refrigerant is mixed with lubricating oil that lubricates each sliding part inside the compressor 1.

The compressor 1 will now be described in detail with reference to FIG. 1. FIG. 1 is a cross-sectional view of the compressor 1 cut along the axis CL of the rotating shaft 20. Note that the up and down arrows in FIG. 1 indicate the vertical direction Dg when the compressor 1 is mounted on a vehicle. Also, in FIG. 1, 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 figures besides FIG. 1.

As shown in FIG. 1, the compressor 1 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 1 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 arranged in a substantially horizontal direction and are 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 metal materials. The motor housing 12 and the discharge housing 14 are housings that form the outer shell of the compressor 1. The motor housing 12 and the discharge housing 14 are made of, for example, aluminum or an aluminum alloy. In this embodiment, the motor housing 12 and the discharge housing 14 form the "external housing." Hereinafter, the motor housing 12 and the discharge housing 14 may be collectively referred to as the external housing.

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. Specifically, the motor housing 12 has a plate-shaped first bottom wall portion 121, a first outer peripheral wall portion 122 that extends cylindrically from the outer peripheral portion of the first bottom wall portion 121, and a flange portion 123. The motor housing 12 is configured as a seamless, one-piece molded product in which the first bottom wall portion 121, the first outer peripheral wall portion 122, and the flange portion 123 are molded.

The flange portion 123 is formed at the end of the opening side of the motor housing 12. The flange portion 123 protrudes in the radial direction Dr of the rotating shaft 20 so as to move away from the axis CL of the rotating shaft 20.

Although not shown, 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.

Although not shown, the motor housing 12 is formed with a refrigerant suction port. The refrigerant outlet side of the evaporator is connected to this suction port. 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, improving the efficiency and reliability of the electric motor 50.

The discharge housing 14, together with the motor housing 12, forms an accommodation space that accommodates the compression section 30 and the electric motor 50. The discharge housing 14 is a bottomed cylindrical shape that opens on the other side in the axial direction Dax of the rotating shaft 20. Specifically, the discharge housing 14 has a plate-shaped second bottom wall portion 141 and a second outer peripheral wall portion 142 that extends cylindrically 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.

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 abutting against the flange portion 123 of the motor housing 12. The motor housing 12 and the discharge housing 14 form a pressure vessel. Although not shown, a gasket is arranged between the motor housing 12 and the discharge housing 14 to prevent refrigerant from leaking to the outside.

The discharge housing 14 is provided with a discharge section 144 having an external discharge hole 143 for discharging the refrigerant to the outside of the external housing at a portion overlapping with a discharge section 363 (described later) in the axial direction Dax of the rotating shaft 20. Specifically, the discharge section 144 is provided in the approximate center of the second bottom wall section 141. The discharge section 144 protrudes from the second bottom wall section 141 toward the compression section 30. The external discharge hole 143 is formed as a through hole penetrating the second bottom wall section 141 and the discharge section 144.

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 to suppress eccentric rotation of the rotating shaft 20.

Although not shown, an oil supply passage is formed inside the rotating shaft 20 to supply lubricating oil to the eccentric bearing portion 344, the first bearing portion 411 described below, the second bearing portion 17, etc. This oil supply passage is supplied with lubricating oil via an oil supply path (not shown) formed in the fixed scroll 32 and the orbiting scroll 34.

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 plate portion formed in a disk shape and a spiral-shaped fixed tooth portion protruding from the fixed base plate portion toward the orbiting scroll 34 on the other side in the axial direction Dax.

The orbiting scroll 34 has a disk-shaped orbiting base portion and a spiral orbiting tooth portion that protrudes from the orbiting base portion 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 plate opposite the orbiting teeth portion. An eccentric bearing portion 344 is provided inside the first boss portion 343. The eccentric bearing portion 344 is made of a plain bearing. The eccentric bearing portion 344 may be made of a bearing other than a plain bearing.

A rotation prevention pin 35 is connected to the orbiting scroll 34. The rotation prevention pin 35 constitutes a rotation prevention mechanism that prevents the orbiting scroll 34 from rotating on its axis. When the rotating shaft 20 rotates, the orbiting scroll 34 performs an orbital motion (i.e., an orbital motion) around the axis center CL of the rotating shaft 20. The rotation prevention mechanism may be composed of something other than the rotation prevention pin 35 (for example, an Oldham ring).

Between the fixed scroll 32 and the orbiting scroll 34, the fixed teeth and the orbiting teeth mesh and come into contact at multiple points, forming multiple crescent-shaped working chambers 31. As the orbiting scroll 34 orbits, the working chambers 31 move from the outer periphery to the center while decreasing in volume. Although not shown, the working chambers 31 are supplied with refrigerant sucked from a refrigerant suction port 320 formed on the outer periphery of the fixed scroll 32. The refrigerant in the working chambers 31 is compressed as the volume of the working chambers 31 decreases. For convenience, in FIG. 1 and other figures, only one of the multiple working chambers 31 is labeled with a reference number.

A refrigerant outlet hole 323 is formed in the center of the fixed base plate portion, which serves as an outlet for 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 portion in the axial direction Dax. The reed valve and stopper 324 are fastened and fixed to the fixed base plate portion 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 flowing out from the refrigerant outlet hole 323. The discharge plate 36 is formed in a cup shape.

The discharge plate 36 constitutes the "compression side end" of the compression section 30, located on the opposite side to the electric motor 50 in the axial direction Dax of the rotating shaft 20. The discharge plate 36 is provided with a discharge section 363 having a discharge hole 362 that discharges the compressed refrigerant. The discharge section 363 is provided at a portion of the discharge plate 36 that faces the discharge section 144 in the axial direction Dax of the rotating shaft 20 so that the discharge hole 362 and the external discharge hole 143 are in communication. The discharge section 363 protrudes toward the discharge section 144.

The lead-out portion 144 and the discharge portion 363 are connected via a seal member 38. The seal member 38 is composed of a seal ring 381 disposed in a portion of the discharge portion 363 facing the lead-out portion 144. Specifically, the seal ring 381 is an O-ring disposed in a circular groove portion 364 formed to surround the discharge hole 362 in a portion of the discharge portion 363 facing the lead-out portion 144. The seal ring 381 may be an O-ring disposed in a circular groove formed to surround the external lead-out hole 143 in a portion of the discharge portion 144 facing the discharge portion 363.

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 smaller than the inner diameter of the motor housing 12.

In the compression section 30 configured in this manner, the fixed scroll 32 and discharge plate 36 are fixed to the shaft support member 40 and the inner housing 16 (described below) by a number of mounting bolts 37.

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 rotation prevention pin 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. Specifically, the shaft support member 40 has a small diameter portion 41 where the inner diameter is the smallest, a large diameter portion 42 where the outer diameter is the largest, and a connecting portion 43 that connects the small diameter portion 41 and the large diameter portion 42. The small diameter portion 41, the large diameter portion 42, and the connecting portion 43 are integrally configured.

The shaft support member 40 has a first bearing portion 411 formed on the inner periphery side of the small diameter portion 41. The first bearing portion 411 is made of a plain bearing. The first bearing portion 411 is made of a cylindrical steel member and a resin layer 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 smaller than the inner diameter of the motor housing 12.

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. In addition, 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 and the like.

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.

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 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 steel material as the stator 54 (e.g., iron).

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

The support portion 163 has a bottom portion 163a in an annular shape connected to the other end 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 sliding 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 sliding bearing.

The outer diameter of the fastening portion 162 of the internal housing 16 is set to be approximately the same as the outer diameter of the fixed scroll 32, discharge plate 36, shaft support member 40, etc. Specifically, the entire fastening portion 162 of the internal housing 16 faces the shaft support member 40 in the axial direction Dax. The fastening portion 162 is fixed to the compression portion 30 and shaft support member 40 by the mounting bolts 37.

The compression section 30, the shaft support member 40, and the electric motor 50 fixed to the internal housing 16 are arranged in this order in the axial direction Dax. The compression section 30, the shaft support member 40, the electric motor 50, and the internal housing 16 are fixed to each other by mounting bolts 37. In this embodiment, the compression section 30, the shaft support member 40, the electric motor 50, and the internal housing 16 constitute the "internal structure ST."

The discharge plate 36, which is located on the opposite side of the electric motor 50 in the compression section 30, is connected to the external housing via a vibration-isolating member 60, with its outer surface of the internal structure ST spaced apart from the inner surface of the external housing in the radial direction Dr of the rotating shaft 20. Specifically, the internal structure ST is connected to the flange portion 123 of the motor housing 12 via the vibration-isolating member 60, with the portions of the discharge plate 36 other than the discharge portion 363 spaced apart from the external housing.

The vibration-proof member 60 is not connected to the electric motor 50 side of the internal structure ST, but is connected to the compression section 30 side of the internal structure ST, so that the internal structure ST is supported in a cantilevered manner.

Specifically, as shown in FIG. 2, the vibration-proof member 60 includes four vibration-proof springs 61A, 61B, 61C, and 61D. The four vibration-proof springs 61A, 61B, 61C, and 61D are arranged at equal intervals in the circumferential direction Drt of the rotating shaft 20. In this example, the vibration-proof member 60 is arranged such that the vibration-proof springs 61A and 61C are symmetrically arranged about the axis CL of the rotating shaft 20, and the vibration-proof springs 61B and 61D are symmetrically arranged about the axis CL of the rotating shaft 20.

The four anti-vibration springs 61A, 61B, 61C, and 61D are composed of leaf springs made of spring steel such as SWP and SUS301CSP. The four anti-vibration springs 61A, 61B, 61C, and 61D in this embodiment have the same shape, size, and material. For this reason, hereinafter, the four anti-vibration springs 61A, 61B, 61C, and 61D may be simply referred to as "anti-vibration springs 61."

The anti-vibration spring 61 is generally U-shaped. The anti-vibration spring 61 has a pair of spring portions 611, 612 formed in a plate shape, and a spring connection portion 613 that connects the pair of spring portions 611, 612. The anti-vibration spring 61 is configured as an integral molded product in which the pair of spring portions 611, 612 and the spring connection portion 613 are integrated.

One end of the pair of spring parts 611, 612 is connected to a first fixed part FP1 set on the inner surface of the external housing, and the other end is connected to a second fixed part FP2 set on the internal structure ST. In this embodiment, each of the pair of spring parts 611, 612 has one end fixed to the first fixed part FP1 with a bolt BT1, and the other end fixed to the second fixed part FP2 with a bolt BT2.

The first and second fixed parts FP1 and FP2 are set at positions where they do not overlap in the axial direction Dax of the rotating shaft 20 so that the pair of spring parts 611, 612 are not deflected by the fastening force acting in the axial direction Dax of the rotating shaft 20 when the external housing is fastened. Specifically, the first fixed part FP1 is set on the end face of the flange part 123 of the motor housing 12 that faces the discharge housing 14. The second fixed part FP2 is set on the end face of the discharge plate 36 that is positioned closer to the axis CL of the rotating shaft 20 than the flange part 123 in the radial direction Dr of the rotating shaft 20, that faces the discharge housing 14. In this example, the second fixed part FP2 is set on the discharge plate 36 so as to be on the same plane as the first fixed part FP1.

The first fixing portion FP1 is provided at eight locations on the flange portion 123. The second fixing portion FP2 is provided at eight locations on the discharge plate 36. The multiple second fixing portions FP2 are arranged at regular intervals in the circumferential direction Drt of the rotating shaft 20 so as to be symmetrical about the axis CL of the rotating shaft 20.

For example, the external housing and the internal structure ST are divided into three regions AR1, AR2, and AR3 evenly in the circumferential direction Drt of the rotating shaft 20. At least one first fixed portion FP1 and at least one second fixed portion FP2 are set for each of the three regions AR1, AR2, and AR3. This arrangement suppresses variation in the spring characteristics, including the spring constant, in the circumferential direction Drt of the rotating shaft 20.

As shown in FIG. 3, the pair of spring parts 611, 612 are made of leaf springs with a rectangular cross section. In this example, the pair of spring parts 611, 612 are set to a thickness of, for example, about 2 to 4 mm so as to obtain the desired spring constant. Note that the pair of spring parts 611, 612 are not limited to leaf springs. The pair of spring parts 611, 612 may be made of rod springs with a circular cross section, for example, as shown in FIG. 4.

The pair of spring portions 611 and 612 are connected to each other via a spring connecting portion 613 .
The pair of spring portions 611, 612 are connected via a spring connection portion 613, thereby defining the positional relationship between them. Therefore, the spring connection portion 613 functions as a position defining portion that defines the positions of the pair of spring portions 611, 612. The spring connection portion 613 is sized to overlap with the flange portion 123 in the axial direction Dax of the rotating shaft 20 so as not to interfere with the internal structure ST.

Here, Figure 5 shows the noise characteristics of the compressor 1. The compressor 1 mounted on a vehicle is normally used in the frequency band of 10 to 180 Hz, and noise caused by vibrations in this frequency band tends to be noticeable inside the vehicle cabin. Furthermore, for the compressor 1 mounted on a vehicle, vibrations occurring in the frequency band of 800 Hz or higher tend to be noticeable outside the vehicle cabin.

In consideration of these, the spring constant of the anti-vibration spring 61 of the compressor 1 of this embodiment is set so as to resonate in a frequency band that avoids the frequency bands of 10 to 180 [Hz] and 800 [Hz] or higher. It is desirable that the spring constant of the anti-vibration spring 61 is set so that the resonant frequency is in the frequency band of 300 to 500 [Hz]. For example, when the weight of the compressor 1 is 10 kg, the spring constant of the anti-vibration spring 61 is set to 35.5 to 98.7 [kN/mm] so that the resonant frequency is in the frequency band of 300 to 500 [Hz]. By setting the spring constant of the anti-vibration spring 61 in such a range, it is possible to obtain the effect of suppressing vibration at high frequencies while avoiding resonance with the primary vibration of the compressor 1.

The inventors have also considered a vibration-proof structure that suppresses the transmission of vibrations from the internal structure ST to the external housing by sandwiching elastic rubber between the external housing and the internal structure ST to prevent them from coming into direct contact with each other and bending it in the axial direction Dax of the rotating shaft 20. However, in the vibration-proof structure considered, it was actually difficult to set the spring constant of the elastic rubber to 35.5 to 98.7 [kN/mm], making it difficult to properly demonstrate the vibration-proofing function.

In contrast, the vibration-proof member 60 of the present invention is structured so that the vibration-proof spring 61 is sandwiched between the inner surface of the external housing and the outer surface of the internal structure ST in the axial direction Dax of the rotating shaft 20 and does not bend, and the spring constant of the vibration-proof spring 61 can be set arbitrarily.

Next, the operation of the compressor 1 will be described. When power is supplied to the stator 54 of the electric motor 50 from an inverter (not shown), the rotor 52 and the rotating shaft 20 rotate, and the orbiting scroll 34 revolves around the rotating shaft 20. This drives the compression section 30, and the low-temperature, low-pressure refrigerant that has passed through the evaporator is sucked into the inside of the housing 10 through the suction port.

Specifically, the refrigerant flows into the gap space 164 formed between the motor housing 12 and the inner housing 16, and is then sucked into the working chamber 31 through the refrigerant suction port 320 formed on the outer periphery of the fixed scroll 32. The refrigerant supplied to the working chamber 31 is compressed as the volume of the working chamber 31 decreases. When the pressure in the working chamber 31 reaches the valve opening pressure of the reed valve, the refrigerant compressed in the working chamber 31 is discharged from the refrigerant outlet hole 323 of the fixed scroll 32 to the muffler chamber 361. The refrigerant discharged to the muffler chamber 361 is discharged to the outside of the compressor 1 through the discharge hole 362 provided in the discharge plate 36 and the external discharge hole 143 provided in the discharge housing 14.

Here, the electric motor 50 vibrates the stator 54 due to the electromagnetic force generated by the interaction between the magnetic field of the permanent magnet provided in the rotor 52 and the current flowing through the coil 542 provided in the stator 54. The compression section 30 compresses the low-temperature, low-pressure refrigerant in the working chamber 31, and discharges it as a high-temperature, high-pressure refrigerant. The specifications of this compression section 30 are determined so that there is as little imbalance as possible with respect to the axis CL of the rotating shaft 20, but in the actual finished product, it is difficult to completely align the centers of gravity and eliminate the imbalance, and there may be variation. Due to such variation, imbalance occurs with respect to the axis CL of the rotating shaft 20, causing vibration. Furthermore, the compression section 30 compresses the refrigerant as the volume of the working chamber 31 decreases. At that time, the contact points of the tooth sides of the fixed scroll 32 and the orbiting scroll 34 that form the working chamber 31 do not move smoothly but move slightly intermittently due to the variation in the accuracy of the spirals of each scroll 32, 34, causing vibration.

In this way, the internal structure ST vibrates when the compressor 1 is in operation. If such vibrations are transmitted to the external housing consisting of the motor housing 12 and the discharge housing 14, the noise and vibrations radiated to the outside will become large.

In contrast, the compressor 1 of this embodiment connects the internal structure ST and the motor housing 12 via a vibration-isolating member 60. Therefore, the vibration-isolating member 60 can prevent the vibrations generated by the compression section 30 and the electric motor 50 from being transmitted to the external housing. As a result, it is possible to ensure quietness by suppressing the transmission of vibrations from the external housing to the surrounding air, i.e., the radiation of noise.

In addition, the vibration-proof spring 61 constituting the vibration-proof member 60 is provided in a position where the second fixed part FP2, which is the connection part with the internal structure ST, does not overlap with the first fixed part FP1, which is the connection part with the external housing, in the axial direction Dax of the rotating shaft 20. As a result, when the spring parts 611, 612 constituting the vibration-proof spring 61 are connected to the first fixed part FP1 and the second fixed part FP2, the spring parts 611, 612 are not sandwiched between the inner surface of the external housing and the outer surface of the internal structure ST in the axial direction Dax of the rotating shaft 20 and do not bend. Therefore, in the structure of the present proposal, there are no restrictions on setting the spring constant, and the spring constants of the spring parts 611, 612 can be set arbitrarily.

Therefore, according to the compressor 1 of this embodiment, the spring constant of the vibration-proof spring 61 can be set to a desired value, so that the vibration-proof function can be properly exerted and the transmission of vibration to the outside can be suppressed.

The compressor 1 of this embodiment also has the following features:

(1) At least one first fixed portion FP1 and one second fixed portion FP2 are set for each of three regions AR1, AR2, and AR3 that divide the external housing and internal structure ST evenly in the circumferential direction Drt of the rotating shaft 20. As a result, the external housing and internal structure ST are connected via spring portions 611 and 612 in the three regions AR1, AR2, and AR3 in the circumferential direction Drt of the rotating shaft 20, and the variation in the spring constants of the spring portions 611 and 612 can be suppressed. This makes it possible to suppress the vibration of the internal structure ST from being transmitted to the external housing.

(2) The compression section 30 is provided with a discharge section 363 having a discharge hole 362 for discharging the compressed fluid at the compression side end located on the opposite side to the electric motor 50 in the axial direction Dax of the rotating shaft 20. The external housing is provided with an outlet section 144 having an external outlet hole 143 for discharging the refrigerant to the outside of the external housing at a portion overlapping the discharge section 363 in the axial direction Dax of the rotating shaft 20. The discharge section 363 and the outlet section 144 are connected to the axial direction Dax of the rotating shaft 20 via a seal member 38.

In this way, if the discharge section 363 of the compression section 30 and the outlet section 144 of the external housing are connected via the seal member 38, the refrigerant compressed in the compression section 30 is prevented from leaking into the gap between the external housing and the internal structure ST. In addition, if the discharge section 363 and the outlet section 144 are connected via the seal member 38, the vibration of the internal structure ST is prevented from being transmitted to the external housing via the connection portion of the discharge section 363 and the outlet section 144.

(3) The second fixing portion FP2 is set on the discharge plate 36 that constitutes the compression side end portion. This results in a structure in which the spring portions 611 and 612 are connected to the compression side end portion, and the relative displacement between the discharge portion 363 and the outlet portion 144 due to vibration of the internal structure ST is suppressed. This prevents the fluid compressed in the compression portion 30 from leaking into the gap between the external housing and the internal structure ST.

(4) The seal member 38 includes a seal ring 381 disposed in the opposing portion of one of the discharge section 363 and the lead-out section 144 that faces the other. In this way, if the discharge section 363 of the compression section 30 and the lead-out section 144 of the external housing are connected via the seal ring 381, the fluid compressed in the compression section 30 is prevented from leaking into the gap between the external housing and the internal structure ST.

It is desirable that the wire diameter of the O-ring of the seal ring 381, together with the spring constant of the vibration-proof spring 61, be selected so that the deflection of the O-ring is the recommended value (e.g., 8 to 30%) even if relative displacement occurs between the outlet portion 144 and the discharge portion 363.

(Modification of the first embodiment)
The anti-vibration spring 61 in the first embodiment is exemplified as a pair of spring portions 611, 612 connected by a spring connection portion 613, but is not limited to this. The anti-vibration spring 61 may be configured such that the pair of spring portions 611, 612 and the spring connection portion 613 are separate bodies. Furthermore, the anti-vibration spring 61 may omit the spring connection portion 613. This also applies to the subsequent embodiments.

Second Embodiment
Next, a second embodiment will be described with reference to Fig. 6. In this embodiment, differences from the compressor 1 described in the first embodiment will be mainly described.

As shown in FIG. 6, the vibration-proof member 60 of this embodiment includes three vibration-proof springs 61A, 61B, and 61C. The three vibration-proof springs 61A, 61B, and 61C are arranged at equal intervals in the circumferential direction Drt of the rotating shaft 20. The vibration-proof springs 61A, 61B, and 61C of this example have the same shape and material as those described in the first embodiment.

The vibration-proof spring 61 has a pair of plate-shaped spring portions 611, 612 and a spring connection portion 613 that connects the pair of spring portions 611, 612. One end of each of the spring portions 611, 612 is connected to a first fixed portion FP1 of the external housing, and the other end is connected to a second fixed portion FP2 of the internal structure ST.

Six first fixing parts FP1 are provided on the flange portion 123. Six second fixing parts FP2 are provided on the discharge plate 36. The second fixing parts FP2 are arranged at a predetermined interval so as to be symmetrical about the axis CL of the rotating shaft 20. At least one first fixing part FP1 and one second fixing part FP2 are provided for each of three regions AR1, AR2, and AR3 that divide the external housing and the internal structure ST evenly in the circumferential direction Drt of the rotating shaft 20. This arrangement suppresses variation in the spring characteristics, including the spring constant, in the circumferential direction Drt of the rotating shaft 20.

Otherwise, it is the same as the first embodiment. The compressor 1 of this embodiment can obtain the same effects as the first embodiment, which are achieved from a common configuration or an equivalent configuration to the first embodiment.

(Modification of the second embodiment)
Although the vibration-isolating member 60 in the second embodiment is exemplified as being configured with three vibration-isolating springs 61, the present invention is not limited to this. The vibration-isolating member 60 may be configured with five or more vibration-isolating springs 61. Furthermore, the vibration-isolating member 60 may be configured with a plurality of vibration-isolating springs 61 as an integrated part.

Third Embodiment
Next, a third embodiment will be described with reference to Figures 7 to 9. In this embodiment, differences from the compressor 1 described in the first embodiment will be mainly described.

As shown in Figures 7 and 8, the seal member 38 includes a joint pipe 382, a first seal ring 383, a second seal ring 384, a first backup ring 385, and a second backup ring 386, instead of the seal ring 381 described in the first embodiment.

The joint pipe 382 is a cylindrical pipe that is inserted into both the discharge hole 362 and the external discharge hole 143. A flow path hole 382a is formed on the inside of the joint pipe 382, which serves as a flow path for the refrigerant discharged from the compression section 30.

The outer diameter of the joint pipe 382 is large enough to form a gap between the discharge hole 362 and the external discharge hole 143. Specifically, the outer diameter of the joint pipe 382 at the portion inserted into the discharge hole 362 is smaller than the inner diameter of the discharge hole 362, and the outer diameter of the portion inserted into the external discharge hole 143 is smaller than the inner diameter of the external discharge hole 143.

In this embodiment, the joint pipe 382 has a first insertion portion 382b that is inserted into the discharge hole 362, a second insertion portion 382c that is inserted into the external discharge hole 143, and an intermediate portion 382d that connects the first insertion portion 382b and the second insertion portion 382c.

The intermediate portion 382d is a portion that straddles both the discharge hole 362 and the external discharge hole 143. The outer diameter of the intermediate portion 382d is larger than the outer diameter of the first insertion portion 382b and the outer diameter of the second insertion portion 382c.

The first seal ring 383 is disposed between the joint pipe 382 and the discharge hole 362. The first seal ring 383 is an O-ring disposed in the first groove 362a formed in the portion of the discharge hole 362 facing the first insertion portion 382b. The first groove 362a is a portion in which the inner diameter is enlarged at the opening portion of the discharge hole 362 into which the first insertion portion 382b is inserted. A first backup ring 385 is disposed in the first groove 362a to prevent the first seal ring 383 from protruding into the gap between the joint pipe 382 and the discharge hole 362. The first backup ring 385 is disposed between the first seal ring 383 and the middle portion 382d.

The second seal ring 384 is disposed between the joint pipe 382 and the external outlet hole 143. The second seal ring 384 is an O-ring disposed in the second groove portion 143a formed in the portion facing the second insertion portion 382c in the external outlet hole 143. The second groove portion 143a is a portion in which the inner diameter is enlarged at the opening portion in the external outlet hole 143 into which the second insertion portion 382c is inserted. A second backup ring 386 is disposed in the second groove portion 143a to prevent the second seal ring 384 from protruding into the gap between the joint pipe 382 and the external outlet hole 143. The second backup ring 386 is disposed between the second seal ring 384 and the middle portion 382d.

The joint pipe 382 is set so that the clearance between the discharge hole 362 and the external outlet hole 143 is greater than the maximum relative displacement ΔDP between the discharge section 363 and the outlet section 144 due to vibration of the internal structure ST.

Figure 8 shows a state in which the middle part 382d of the joint pipe 382 is coaxial with the center of the discharge hole 362 and the center of the external lead-out hole 143. Figure 9 shows a state in which the relative displacement between the discharge part 363 and the lead-out part 144 due to the vibration of the internal structure ST is at its maximum. The maximum clearance Cmax between the middle part 382d and the discharge hole 362 and the external lead-out hole 143 in Figure 8 is set to be larger than the maximum relative displacement ΔDP between the discharge part 363 and the lead-out part 144 due to the vibration of the internal structure ST. Note that the above "maximum relative displacement ΔDP" can be calculated based on the displacement of the internal structure ST assumed from the equation of motion of the vibration system to which the internal structure ST is connected by the vibration-proof spring 61, for example.

Otherwise, it is the same as the first embodiment. The compressor 1 of this embodiment can obtain the same effects as the first embodiment, which are achieved from a common configuration or an equivalent configuration to the first embodiment.

The compressor 1 of this embodiment also has the following features:

(1) The seal member 38 includes a joint pipe 382 inserted through both the discharge hole 362 and the external discharge hole 143. The seal member 38 also includes a first seal ring 383 disposed between the joint pipe 382 and the discharge hole 362, and a second seal ring 384 disposed between the joint pipe 382 and the external discharge hole 143. In this way, if the discharge section 363 and the discharge section 144 are connected via the joint pipe 382, the first seal ring 383, and the second seal ring 384, the refrigerant compressed in the compression section 30 is prevented from leaking into the gap between the external housing and the internal structure ST.

(2) In this embodiment, the outer diameter of the joint pipe 382 at the portion inserted into the discharge hole 362 is smaller than the inner diameter of the discharge hole 362, and the outer diameter of the portion inserted into the external discharge hole 143 is smaller than the inner diameter of the external discharge hole 143. The seal member 38 includes a first backup ring 385 that prevents the first seal ring 383 from protruding into the gap between the discharge hole 362 and the joint pipe 382. The seal member 38 also includes a second backup ring 386 that prevents the second seal ring 384 from protruding into the gap between the external discharge hole 143 and the joint pipe 382. This prevents the seal function from being deteriorated due to deformation of the first seal ring 383 and the second seal ring 384 by the high-pressure refrigerant, thereby preventing the refrigerant compressed in the compression section 30 from leaking into the gap between the external housing and the internal structure ST.

(3) The joint pipe 382 is set so that the clearance between the discharge hole 362 and the external discharge hole 143 is greater than the maximum relative displacement ΔDP between the discharge section 363 and the discharge section 144 due to vibration of the internal structure ST. As a result, even if the relative displacement between the discharge section 363 and the discharge section 144 increases due to vibration of the internal structure ST, the displacement of the joint pipe 382 is suppressed. This makes it possible to appropriately suppress leakage of the refrigerant compressed in the compression section 30 into the gap between the external housing and the internal structure ST.

(Modification of the third embodiment)
As in the third embodiment, the seal member 38 preferably includes a first back-up ring 385 and a second back-up ring 386, but does not have to be so.

It is also desirable that the joint pipe 382 be set so that the clearance between the discharge hole 362 and the external outlet hole 143 is greater than the maximum relative displacement amount ΔDP between the discharge portion 363 and the outlet portion 144, but this is not necessary.

Fourth Embodiment
Next, a fourth embodiment will be described with reference to Figures 10 to 12. In this embodiment, the differences from the compressor 1 described in the first embodiment will be mainly described.

As shown in FIG. 10, the flange portion 123 is omitted from the motor housing 12 of this embodiment. The first outer peripheral wall portion 122 of the motor housing 12 has an outer diameter and an inner diameter that are approximately equal to those of the second outer peripheral wall portion 142 of the discharge housing 14. Since the flange portion 123 of the motor housing 12 is omitted from the outer housing of this embodiment, the size of the outer housing in the radial direction Dr of the rotating shaft 20 is smaller than that described in the first embodiment.

As shown in FIG. 11, the vibration-proof member 60 of this embodiment is configured as an integral part with the gasket GKT used in the external housing, instead of a single vibration-proof spring 61. The vibration-proof member 60 is configured of a ring-shaped plate member 62. The plate member 62 has an outer diameter that is approximately equal to the outer diameter of the first outer peripheral wall portion 122 of the motor housing 12 and the second outer peripheral wall portion 142 of the discharge housing 14.

The plate member 62 is fixed by being clamped between the motor housing 12 and the discharge housing 14 at its outer periphery, and is fixed to the end face of the discharge plate 36 that faces the discharge housing 14 at its inner periphery.

The plate member 62 is thicker than the gaskets typically used in external housings. The plate member 62 has a thickness of, for example, about 0.5 to 1.0 mm. Note that gaskets typically used in external housings have a thickness of about 0.25 mm. As a result, the plate member 62 is configured so that the intermediate portion between the outer periphery and inner periphery functions as a spring.

Specifically, as shown in FIG. 12, the plate member 62 includes a seal portion 621 that functions as a gasket GKT for the external housing, an attachment portion 622 that fixes the plate member 62 to the internal structure ST, and a plurality of spring portions 623 formed in a plate shape.

The seal portion 621 is an outer peripheral portion of the plate member 62 that is sandwiched between the motor housing 12 and the discharge housing 14. The seal portion 621 is sandwiched between the end face on the opening side of the first outer peripheral wall portion 122 and the end face on the opening side of the second outer peripheral wall portion 142.

The mounting portion 622 is an inner peripheral portion of the plate member 62 that is fixed to the discharge plate 36. The mounting portion 622 is fixed to the end face of the discharge plate 36 that faces the discharge housing 14 by a bolt BT. The outer peripheral side of the mounting portion 622 is connected to the inner peripheral side of the seal portion 621 by a number of spring portions 623.

The multiple spring portions 623 are intermediate portions that connect the seal portion 621 and the mounting portion 622. The multiple spring portions 623 are set radially at regular intervals in the circumferential direction Drt of the rotating shaft 20. Eight spring portions 623 are set in the plate member 62 of this embodiment. Note that the number of spring portions 623 is not limited to eight and can be set to any number.

The plate member 62 configured in this manner can be obtained by forming multiple arc-shaped through holes in the middle of a circular ring-shaped plate material. As with the vibration-proof spring 61 of the first embodiment, the spring constant of the plate member 62 is set so that it resonates in a frequency band that avoids the frequency bands of 10 to 180 Hz and 800 Hz or higher. It is desirable that the spring constant of the plate member 62 is set so that the resonant frequency is in the frequency band of 300 to 500 Hz. By setting the spring constant of the plate member 62 in this range, it is possible to obtain the effect of suppressing vibrations at high frequencies while avoiding resonance with the primary vibration of the compressor 1.

In this embodiment, the portions of the motor housing 12 and the discharge housing 14 that butt against each other form the first fixing portion FP1 to which the spring portion 623 is fixed in the external housing. Also, the portion of the discharge plate 36 that faces the discharge housing 14 forms the second fixing portion FP2 to which the spring portion 623 is fixed in the internal structure ST.

Otherwise, it is the same as the first embodiment. The compressor 1 of this embodiment can obtain the same effects as the first embodiment, which are achieved from a common configuration or an equivalent configuration to the first embodiment.

The compressor 1 of this embodiment also has the following features:

(1) The multiple spring portions 623 that make up the vibration-proof member 60 are configured as an integral part with the gasket GKT used in the external housing. In this way, by configuring the spring portions 623 and the gasket GKT as an integral part, it is possible to realize a vibration-proof structure in a simple manner with a reduced number of parts.

Fifth Embodiment
Next, a fifth embodiment will be described with reference to Fig. 13 and Fig. 14. In this embodiment, differences from the compressor 1 described in the fourth embodiment will be mainly described.

As shown in FIG. 13, the vibration-proof member 60 is configured as an integral part with the gaskets GKT1, GKT2 used in both the external housing and the internal structure ST. The vibration-proof member 60 is configured from a ring-shaped plate member 63. The plate member 63 has an outer diameter that is approximately equal to the outer diameter of the first outer peripheral wall portion 122 of the motor housing 12 and the second outer peripheral wall portion 142 of the discharge housing 14. The plate member 63 is thicker than gaskets that are normally used, similar to that described in the fourth embodiment.

The plate member 63 is fixed by being clamped at its outer periphery between the motor housing 12 and the discharge housing 14, and at its inner periphery between the discharge plate 36 and the fixed scroll 32.

As shown in FIG. 14, the plate member 63 includes a first seal portion 631 that functions as a gasket GKT1 for the external housing, a second seal portion 632 that functions as a gasket GKT2 for the internal structure ST, and a plurality of spring portions 633 formed in a plate shape.

The first seal portion 631 is an outer peripheral portion of the plate member 63 that is sandwiched between the motor housing 12 and the discharge housing 14. The first seal portion 631 is sandwiched between the end face on the opening side of the first outer peripheral wall portion 122 and the end face on the opening side of the second outer peripheral wall portion 142.

The second seal portion 632 is an inner peripheral portion that is sandwiched between the fixed scroll 32 and the discharge plate 36. The second seal portion 632 is sandwiched between the opposing end faces of the fixed scroll 32 and the discharge plate 36. The outer peripheral side of the second seal portion 632 is connected to the inner peripheral side of the first seal portion 631 by multiple spring portions 633.

The multiple spring portions 633 are intermediate portions that connect the first seal portion 631 and the second seal portion 632. The multiple spring portions 633 are set radially at regular intervals in the circumferential direction Drt of the rotating shaft 20. Eight spring portions 633 are set in the plate member 63 of this embodiment. Note that the number of spring portions 633 is not limited to eight, and can be set to any number.

The plate member 63 configured in this manner can be obtained by forming a plurality of arc-shaped through holes in the middle of a circular ring-shaped plate material. The plate member 63 has a spring constant set in the same manner as described in the fourth embodiment. In this embodiment, the portions of the motor housing 12 and the discharge housing 14 that are butted against each other form the first fixed portion FP1 to which the spring portion 633 is fixed in the external housing. The portions of the discharge plate 36 and the fixed scroll 32 that are butted against each other form the second fixed portion FP2 to which the spring portion 633 is fixed in the internal structure ST.

Otherwise, it is the same as the fourth embodiment. The compressor 1 of this embodiment can obtain the same effects as the first embodiment, which are achieved from a common configuration or an equivalent configuration to the fourth embodiment.

The compressor 1 of this embodiment also has the following features:

(1) The multiple spring portions 633 that make up the vibration-proof member 60 are configured as an integral part with the gaskets GKT1, GKT2 used in both the external housing and the internal structure ST. In this way, by configuring the spring portions 623 and the gaskets GKT1, GKT2 as an integral part, it is possible to realize a vibration-proof structure in a simple manner with a reduced number of parts.

(Modification of the fourth embodiment)
The vibration-isolating member 60 of the fourth embodiment is configured as an integral part with the gaskets GKT1 and GKT2 used in both the outer housing and the inner structure ST, but is not limited thereto. The vibration-isolating member 60 may be configured as an integral part with the gasket GKT2 used in the inner structure ST, for example.

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

As in the first embodiment, it is desirable that at least one spring portion 611, 612 is provided in each of three regions AR1, AR2, and AR3 that divide the outer housing and the inner structure ST evenly in the circumferential direction Drt of the rotating shaft 20, but this is not necessarily required. This is also true for embodiments other than the first embodiment.

As in the first and third embodiments, it is desirable that the discharge portion 363 and the outlet portion 144 are connected via a seal member 38, but this is not necessary. This is also true for embodiments other than the first and third embodiments.

As in the first embodiment, it is desirable for the spring portions 611 and 612 to have their ends fixed to the discharge plate 36 that constitutes the compression side end, but this is not limited thereto. The spring portions 611 and 612 may be fixed, for example, to the connection point between the compression portion 30 and the electric motor 50 in the internal structure ST, or may be fixed to the end of the internal structure ST on the electric motor 50 side.

In the above embodiment, an example was described in which the vibration-proof spring 61 constituting the vibration-proof member 60 is fixed to the external housing or the internal structure ST by the bolt BT, but this is not limited thereto and the vibration-proof spring 61 may be fixed by other fastening means. An example was given in which the first fixing portion FP1 and the second fixing portion FP2 are arranged at positions offset in the radial direction Dr of the rotating shaft 20, but this is not limited thereto. The first fixing portion FP1 and the second fixing portion FP2 may be arranged at positions offset in the circumferential direction Drt of the rotating shaft 20.

The internal housing 16 is not limited to being substantially cup-shaped, and may be, for example, cylindrical. The internal housing 16 is preferably made of the same metal material as the stator 54, but is not limited to this, and may be 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 first bearing portion 411 and the second bearing portion 17 may be configured as, for example, a rolling bearing instead of a sliding bearing. Also, the second bearing portion 17 may be provided on an element other than the inner housing 16.

The compression section 30 of the compressor 1 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 part of the compression section 30 may be in contact with the external housing in the axial direction Dax.

In the above embodiment, the space in the housing 10 where the electric motor 50 is disposed is exemplified as being in a low-pressure, low-temperature atmosphere, but the compressor 1 is not limited to this. For example, the compressor 1 may be configured such that the refrigerant discharged from the compression section 30 is introduced into the space in the housing 10 where the electric motor 50 is disposed, and the space is in a high-pressure, high-temperature atmosphere. In such a structure, it is desirable that the refrigerant suction section in the internal structure ST and the refrigerant introduction section in the external housing are connected via a sealing member 38 such as an O-ring or a connecting pipe.

In the above embodiment, the compressor 1 applied to a vehicle air conditioner has been described, but the present invention is not limited thereto, and the compressor 1 can also be applied to other air conditioners, temperature control devices for various devices, etc. Furthermore, the compressor 1 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.

It goes without saying that in the above-described embodiments, the elements constituting the embodiments are not necessarily essential, except in cases where they are specifically stated as essential or where they are clearly considered essential in principle.

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, except when it is expressly stated that they are essential or when they are clearly limited to a specific number in principle.

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

1. Compressor (electric compressor)
12 Motor housing (outer housing)
14 Discharge housing (outer housing)
30 Compression section 50 Electric motor 60 Vibration isolating member 611, 612 Spring section ST Internal structure

Claims (9)

An electric compressor,
An outer housing (12, 14) that constitutes an outer shell;
A rotating shaft (20) housed inside the outer housing;
A compression section (30) that compresses a fluid by rotating the rotating shaft;
an electric motor (50) for driving the compression section;
a vibration-proof member (60) that is interposed between an internal structure (ST) including the compression section and the electric motor and the external housing inside the external housing to suppress transmission of vibration;
The vibration-proof member includes a plurality of spring portions (611, 612, 623, 633) formed in a plate or rod shape,
the outer housing and the inner structure are connected to each other via the spring portions in a state in which an inner surface of the outer housing and an outer surface of the inner structure are spaced apart from each other in a radial direction of the rotation shaft,
The plurality of spring portions have one end sides connected to a first fixed portion (FP1) set on the inner surface of the external housing, and the other end sides of the spring portions connected to a second fixed portion (FP2) set in the internal structure at a position not overlapping with the first fixed portion in the axial direction of the rotating shaft. The electric compressor according to claim 1, wherein when the outer housing and the inner structure are divided into three regions (AR1, AR2, AR3) evenly in the circumferential direction of the rotating shaft, at least one of the first fixed portion and at least one of the second fixed portion are set for each of the three regions. the compression section is provided with a discharge section (363) having a discharge hole (362) for discharging compressed fluid at a compression side end (36) located on the opposite side to the electric motor in the axial direction of the rotary shaft,
The outer housing is provided with a lead-out portion (144) having an external lead-out hole (143) for leading a fluid to the outside of the outer housing at a portion overlapping with the discharge portion in the axial direction of the rotating shaft,
3. The electric compressor according to claim 1, wherein the discharge portion and the outlet portion are connected in an axial direction of the rotary shaft via a seal member. The electric compressor according to claim 3, wherein the second fixed portion is set at the compression side end portion. The electric compressor according to claim 3, wherein the seal member includes a seal ring (381) disposed in a portion of one of the discharge portion and the outlet portion that faces the other. The electric compressor according to claim 3, wherein the seal member includes a joint pipe (382) inserted through both the discharge hole and the external outlet hole, a first seal ring (383) disposed between the joint pipe and the discharge hole, and a second seal ring (384) disposed between the joint pipe and the external outlet hole. the outer diameter of the joint pipe at a portion inserted into the discharge hole is smaller than an inner diameter of the discharge hole, and the outer diameter of the joint pipe at a portion inserted into the external lead-out hole is smaller than an inner diameter of the external lead-out hole,
7. The electric compressor according to claim 6, wherein the sealing member includes a first backup ring (385) that suppresses protrusion of the first seal ring into a gap between the discharge hole and the joint pipe, and a second backup ring (386) that suppresses protrusion of the second seal ring into a gap between the external lead-out hole and the joint pipe. The electric compressor according to claim 7, wherein the joint pipe has a clearance between the discharge hole and the external outlet hole that is greater than the maximum relative displacement between the discharge section and the outlet section due to vibration of the internal structure. The electric compressor according to claim 1 or 2, wherein the spring portions (623, 633) are configured as an integral part with a gasket (GKT) used in at least one of the outer housing and the inner structure.

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