WO2024185233A1 - Co-rotating scroll compressor - Google Patents

Abstract

On one side in the direction of a drive axis (R1) in a driving scroll (30), a bearing cover body (36) with a higher strength than a driving end plate (31) is fixed to an end surface (311) on an opposite side of the driving end plate (31) from a compression chamber (55), and, on the other side in the direction of the drive axis (R1) in the driving scroll (30), a restricting part (811) is mounted on a driving peripheral wall (32). The bearing cover body (36) integrally has a supported part (38). A driving mechanism (10) has a rotor (11) that is disposed on an outer peripheral surface of the driving scroll (30) while surrounding the driving scroll (30) from the outer peripheral side. The rotor (11) is restricted, by the bearing cover body (36), from moving toward the one side in the direction of the drive axis (R1), and is restricted, by the restricting part (811), from moving toward the other side in the direction of the drive axis.

Description

Double-rotating scroll compressor

The present invention relates to a double-rotating scroll compressor.

Patent Document 1 discloses a conventional double-rotating scroll compressor. This double-rotating scroll compressor includes a drive mechanism, a drive scroll, a driven mechanism, a driven scroll, and a housing.

The drive scroll is rotated around the drive axis by the drive mechanism. The driven scroll is rotated around the driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll.

The drive scroll has a drive end plate, a drive peripheral wall, and a drive scroll. The drive end plate extends in a direction intersecting the drive axis. The drive peripheral wall protrudes in a cylindrical shape from the drive end plate toward the driven scroll. The drive scroll protrudes in a spiral shape from the drive end plate toward the driven scroll within the drive peripheral wall.

The driven scroll has a driven end plate and a driven scroll. The driven end plate extends in a direction intersecting the driven axis. The driven scroll protrudes in a spiral shape from the driven end plate toward the driving scroll.

The driving scroll and the driven scroll face each other to form a compression chamber, and the volume of the compression chamber is changed by the rotational driving and the rotational driven.

The driving end plate and the driven end plate are integrally formed with a supported portion on the rear side of the compression chamber, which is rotatably supported on the housing via a bearing.

The drive mechanism is cylindrical and has a rotor that surrounds the drive scroll from the outer periphery and is fixed to the drive scroll.

JP 2002-310073 A

In the above-mentioned conventional double-rotating scroll compressor, it is necessary to prevent the rotor from slipping out of the drive scroll in the direction of the drive shaft center. In this case, if an attempt is made to prevent the rotor from slipping out using bolts, for example, the formation of bolt holes reduces the strength of the rotor, which may reduce the durability of the rotor.

On the other hand, from the viewpoint of weight reduction, the drive scroll may be made of an aluminum alloy, for example. In this case, there is a risk that the supported part, which is integrally formed with the drive end plate and rotatably supported by the bearing, will not be strong enough to withstand the bearing load.

The present invention was made in consideration of the above-mentioned conventional situation, and the problem to be solved is to provide a double-rotating scroll compressor in which the supported part, which is rotatably supported by the bearing, can withstand the bearing load, and in which the rotor can be prevented from coming off the driving scroll without reducing the durability of the rotor.

The double-rotating scroll compressor of the present invention comprises a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism,
The driving scroll is rotated about a drive axis by the driving mechanism,
The driven scroll is rotated around a driven axis by the driving scroll and the driven mechanism while being eccentric with respect to the driving scroll,
The drive scroll has a drive end plate extending in a direction intersecting the drive axis, a drive peripheral wall protruding in a cylindrical shape from the drive end plate toward the driven scroll, and a drive scroll body protruding in a spiral shape from the drive end plate toward the driven scroll within the drive peripheral wall,
The driven scroll has a driven end plate extending in a direction intersecting the driven axis, and a driven scroll protruding in a spiral shape from the driven end plate toward the driving scroll,
The drive scroll and the driven scroll form a compression chamber by opposing each other, and the volume of the compression chamber is changed by the rotation drive and the rotation driven.
A bearing cover body having a higher strength than the drive end plate is fixed to an end surface of the drive end plate opposite to the compression chamber on one side of the drive scroll in the drive axial direction, and a restricting portion is provided on the drive peripheral wall on the other side of the drive scroll in the drive axial direction,
the bearing cover body has a supported portion integrally therewith that is rotatably supported on the housing via a bearing,
The drive mechanism has a cylindrical rotor that surrounds the drive scroll from the outer circumferential side and is disposed on the outer circumferential surface of the drive scroll,
The rotor is characterized in that its movement toward the one side in the direction of the drive shaft is restricted by the bearing cover body, and its movement toward the other side in the direction of the drive shaft is restricted by the restricting portion.

In the double-rotating scroll compressor of the present invention, a bearing cover body is fixed to the end face of the drive end plate opposite the compression chamber on one side of the drive scroll in the drive axial direction, and a regulating portion is provided on the drive peripheral wall on the other side of the drive scroll in the drive axial direction. The rotor arranged on the outer peripheral surface of the drive scroll is regulated in its movement toward one side in the drive axial direction by the bearing cover body, and in its movement toward the other side in the drive axial direction by the regulating portion. Therefore, the bearing cover body and the regulating portion can prevent the rotor from slipping out of the drive scroll in the drive axial direction.

In this case, the strength of the rotor is not reduced by the formation of bolt holes, etc., and the durability of the rotor is not reduced.

In addition, in both rotary scroll compressors, the supported part, which is rotatably supported on the housing via a bearing, is provided on the bearing cover body, and this bearing cover body has a higher strength than the driving end plate. Therefore, the supported part can withstand the bearing load.

Therefore, with the double-rotating scroll compressor of the present invention, the supported part that is rotatably supported by the bearing can withstand the bearing load, and the rotor can be prevented from coming off the driving scroll without reducing the durability of the rotor.

The drive scroll preferably has a rotor housing portion provided on the drive end plate and the drive peripheral wall, with the rotor disposed on its outer peripheral surface, and a peripheral wall shoulder portion provided on the drive peripheral wall, with an outer diameter larger than that of the rotor housing portion. It is also preferable that the shoulder end face of the peripheral wall shoulder portion facing one side in the drive shaft direction constitutes the regulating portion.

In this case, the rotor placed in the rotor accommodating section is restricted from moving to one side in the direction of the drive shaft by the bearing cover body, and is restricted from moving to the other side in the direction of the drive shaft by the shoulder end face of the peripheral wall shoulder.

The bearing cover body is preferably made of a magnetic material, and an intermediate member made of a non-magnetic material is interposed between the bearing cover body and the rotor.

In this case, even if the bearing cover is made of a low-cost magnetic material, the intermediate member can prevent magnetic flux leakage through the bearing cover.

The bearing cover is preferably made of a non-magnetic material.

In this case, it is possible to prevent magnetic flux leakage through the bearing cover body.

It is preferable that the end face of the drive end plate opposite the compression chamber and the opposing face of the bearing cover body that faces this end face are in surface contact.

In this case, it is advantageous to fix the bearing cover body in the correct position relative to the drive end plate, and to ensure coaxiality between the drive shaft center and the supported part.

　With the double-rotating scroll compressor of the present invention, the supported part that is rotatably supported by the bearing can withstand the bearing load, and the rotor can be prevented from coming off the driving scroll without reducing the durability of the rotor.

FIG. 1 is a cross-sectional view of a double-rotating scroll compressor according to a first embodiment of the present invention. FIG. 2 relates to the double-rotating scroll compressor of the first embodiment and is a cross-sectional view taken along line AA of FIG. FIG. 3 is a cross-sectional view of a double-rotating scroll compressor according to a second embodiment.

Below, examples 1 and 2 of the present invention will be described with reference to the drawings.

Example 1
As shown in Fig. 1, the double-rotating scroll compressor (hereinafter simply referred to as the compressor) of the first embodiment includes a housing 60, an electric motor 10, a driving scroll 30, a driven scroll 40, and a driven mechanism 20. The electric motor 10 is an example of the "driving mechanism" in the present invention. This compressor is mounted on a vehicle (not shown) and constitutes an air conditioner for the vehicle.

In this embodiment, the front-to-rear direction of the compressor is defined by the solid arrow shown in FIG. 1. Note that the front-to-rear direction is an example for ease of explanation, and the compressor can change its own position as appropriate depending on the vehicle in which it is installed.

The housing 60 is composed of a housing body 61 and a cover 65. The housing body 61 is a bottomed cylindrical member having an outer peripheral wall 62 and a bottom wall 63. The outer peripheral wall 62 is cylindrical with its center at the drive axis R1, and has an inner peripheral surface 62B. The drive axis R1 is parallel to the front-rear direction. In the following description, the front refers to one side in the direction of the drive axis R1, and the rear refers to the other side in the direction of the drive axis R1.

The bottom wall 63 is located at the rear end of the housing body 61. The bottom wall 63 extends in a generally circular flat plate shape perpendicular to the drive axis R1. The outer peripheral edge of the bottom wall 63 is connected to the rear end of the outer peripheral wall 62. A cylindrical second shaft support portion 64 is provided in a protruding manner at the center of the inner surface of the bottom wall 63, protruding forward with the driven axis R2 as its center. The driven axis R2 extends parallel to the drive axis R1 while being eccentric with respect to the drive axis R1. The inner ring of the bearing 71 is fitted onto the second shaft support portion 64.

In addition, an inverter case with a connector portion is connected to the rear of the housing main body 61. An inverter circuit having a circuit board and switching elements, etc. is housed inside the inverter case. The inverter circuit is electrically connected to the vehicle's battery through the connector, and is also electrically connected to the stator 17 (described below) through an airtight passage provided in the bottom wall 63. As a result, the inverter circuit supplies power to the stator 17 while converting the direct current supplied from the battery into alternating current. Note that illustrations of the airtight passage, connector portion, inverter case, inverter circuit, and battery are omitted.

The cover 65 is disposed in front of the housing body 61. The cover 65 extends in a generally circular flat plate shape perpendicular to the drive axis R1. The cover 65 is fastened to the outer peripheral wall 62 of the housing body 61 by bolts (not shown) with its outer peripheral edge abutting the front end of the outer peripheral wall 62 of the housing body 61. In this way, the cover 65 blocks the housing body 61 from the front. In this way, a suction chamber 61A is formed within the housing body 61.

A cylindrical first support portion 66 is provided in a protruding manner on the center of the inner surface of the cover 65, with the center on the drive shaft center R1. The outer ring of a needle bearing 72 is fitted into the first support portion 66. The needle bearing 72 is an example of a "bearing" in the present invention.

The cover 65 is formed with an intake port 65A and a discharge port 65B. The intake port 65A is located between the outer peripheral edge of the cover 65 and the first bearing portion 66, and penetrates the cover 65 in a direction parallel to the drive shaft center R1. The intake port 65A connects the intake chamber 61A to the outside of the compressor. A pipe is connected to the intake port 65A. As a result, low-temperature, low-pressure refrigerant gas that has passed through the evaporator is sucked into the intake chamber 61A through the pipe.

The discharge port 65B penetrates the cover 65 in a direction parallel to the drive shaft R1 so as to open into the first bearing portion 66 at the center of the cover 65. A pipe (not shown) is connected to the discharge port 65B, and the discharge port 65B allows the refrigerant gas discharged to the discharge portion 38B (described later) to flow toward the condenser. The pipes, evaporator, and condenser are not shown in the illustration.

The electric motor 10 is housed in the suction chamber 61A. As a result, the suction chamber 61A also serves as a motor chamber that houses the electric motor 10. The electric motor 10 is composed of a stator 17 and a rotor 11.

The stator 17 is cylindrical and centered on the drive shaft R1, and has windings 18. The stator 17 is fixed to the housing body 61, and thus to the housing 60, by fitting into the inner circumferential surface 62B of the outer circumferential wall 62 of the housing body 61.

The rotor 11 is cylindrical around the drive shaft R1 and is disposed within the stator 17. The center O of the rotor 11 coincides with the drive shaft R1. The rotor 11 has a front surface 111 and a rear surface 112 located opposite the front surface 111. Although not shown in detail, the rotor 11 is composed of a plurality of permanent magnets 12 corresponding to the stator 17 and laminated steel plates that secure each permanent magnet 12. As shown in FIG. 2, the plurality of permanent magnets 12 are disposed at equal intervals in the circumferential direction of the drive scroll 30.

The drive scroll 30 has a drive end plate 31, a drive peripheral wall 32, and a drive scroll 33. The drive end plate 31, the drive peripheral wall 32, and the drive scroll 33 are integrally formed. The drive scroll 30 is made of a non-magnetic material. Specifically, the drive scroll 30 is made of an aluminum alloy.

The driving end plate 31 extends in a generally circular plate shape perpendicular to the driving axis R1. The driving end plate 31 has a front surface 311 and a rear surface 312 located opposite the front surface 311. The front surface 311 corresponds to the "end surface of the driving end plate opposite the compression chamber" in this invention.

A discharge valve chamber 34 is formed in the front surface 311 of the drive end plate 31. The discharge valve chamber 34 is formed by a recess in which the front surface 311 is partially recessed toward the compression chamber 55 described below. The discharge valve chamber 34 has an inner shape that roughly corresponds to the outer shape of the discharge valve mechanism 56 described below so that it can accommodate the discharge valve mechanism 56. In addition, a discharge port 35 is formed near the center of the drive end plate 31, penetrating the drive end plate 31 in the front-rear direction. The discharge port 35 connects the compression chamber 55 and the discharge valve chamber 34.

A discharge valve mechanism 56 is disposed within the discharge valve chamber 34. The discharge valve mechanism 56 has a discharge reed valve 57, a retainer 58, and a fixing bolt 59. The discharge reed valve 57 and the retainer 58 are fixed to the bottom surface of the discharge valve chamber 34 by the fixing bolt 59. The discharge reed valve 57 is capable of opening and closing the discharge port 35. In addition, the retainer 58 is capable of adjusting the opening degree of the discharge reed valve 57.

The drive spiral 33 is located inside the drive peripheral wall 32. The drive spiral 33 extends rearward from the rear surface 312 of the drive end plate 31 in parallel with the drive axis R1. The drive spiral 33 is formed based on an involute curve and is spiral-shaped around the drive axis R1. As shown in Figure 2, when viewed from the rear, the drive spiral 33 is formed to be wound counterclockwise around the drive axis R1 from the center of the spiral. The outer peripheral end of the drive spiral 33 is connected to the drive peripheral wall 32. Note that in Figure 2, the discharge port 35, which would normally be visible from the rear, is omitted from the illustration.

The driving peripheral wall 32 extends rearward from the outer periphery of the driving end plate 31, i.e., parallel to the driving axis R1, toward the driven scroll 40. The driving peripheral wall 32 is substantially cylindrical with the driving axis R1 at its center.

A bearing cover body 36 is fixed to the front surface 311 of the driving end plate 31 at the front side of the driving scroll 30. The bearing cover body 36 is made of a magnetic material. Specifically, the bearing cover body 36 is made of an iron-based alloy that is stronger than the driving scroll 30.

The bearing cover body 36 has a cover portion 37 and a first boss 38 that is integrally formed with the cover portion 37. The first boss 38 is an example of the "supported portion" in the present invention.

The cover portion 37 extends perpendicular to the drive shaft center R1 and has a generally circular plate shape. A through hole 37B is formed in the center of the cover portion 37.

The first boss 38 protrudes forward from the inner peripheral edge of the cover portion 37, i.e., from the center of the cover portion 37. The first boss 38 extends cylindrically in the direction of the drive axis R1, centered on the drive axis R1. The cylindrical internal space of the first boss 38 forms the discharge portion 38B. In this compressor, the discharge chamber is formed by the discharge valve chamber 34 and the discharge portion 38B.

The cover portion 37 of the bearing cover body 36 and the driving end plate 31 of the driving scroll 30 are fastened by a number of bolts 50 extending parallel to the driving axis R1. When fastened by the bolts 50, the front surface 311 of the driving end plate 31 is in surface contact with the rear surface 371 of the cover portion 37, which faces the front surface 311 in the front-rear direction. The rear surface 371 of the cover portion 37 corresponds to the "facing surface" in this invention.

The driven scroll 40 has a driven end plate 41 and a driven scroll 42. The driven end plate 41 and the driven scroll 42 are integrally formed. The driven scroll 40 is made of a non-magnetic material. Specifically, the driven scroll 40 is made of an aluminum alloy.

The driven end plate 41 extends in a generally circular plate shape perpendicular to the driven axis R2. The driven end plate 41 has a front surface 411 and a rear surface 412 located opposite the front surface 411. A second boss 43 is formed in the center of the rear surface 412, protruding toward the bottom wall 63. The second boss 43 is cylindrical and centered on the driven axis R2.

The driven end plate 41 is formed with an intake port 44. The intake port 44 penetrates the driven end plate 41 in the direction of the driven axis R2, i.e., in the front-rear direction, at a position that is on the outer periphery of the second boss 43.

The driven spiral body 42 extends forward from the front surface 411 of the driven end plate 41 in parallel with the driven axis R2. The driven spiral body 42 is formed based on an involute curve and has a spiral shape around the driven axis R2. More specifically, as shown in FIG. 2, when viewed from the rear, the driven spiral body 42 is formed in a counterclockwise spiral around the driven axis R2 from the center of the spiral.

The driven mechanism 20 is composed of four rotation prevention pins 21 and four rings 22. The number of rotation prevention pins 21 and rings 22 can be appropriately designed as long as there are three or more of each. Also, in FIG. 1, two of each rotation prevention pin 21 and ring 22 are illustrated. The driving scroll 30 and the driven scroll 40 form a compression chamber 55 by opposing the driving scroll 33 and the driven scroll 42 to each other.

Each rotation prevention pin 21 is fixed to the rear surface of a peripheral wall shoulder portion 81 of the driving scroll 30, which will be described later. Each ring 22 is fixed to the front surface 411 of the driven end plate 41 so as to face each rotation prevention pin 21.

In the compressor of this embodiment 1, a rotor accommodating section 80 is provided on the outer peripheral surfaces of the driving end plate 31 and the driving peripheral wall 32. The rotor accommodating section 80 extends rearward from the front surface 311 of the driving end plate 31 to the driving peripheral wall 32. The outer peripheral surface of the rotor accommodating section 80 has a cylindrical shape corresponding to the inner peripheral surface of the rotor 11. The rotor 11 is disposed on the outer peripheral surface of the rotor accommodating section 80. The outer diameter of the rotor accommodating section 80 is slightly smaller than the inner diameter of the rotor 11. In other words, the rotor 11 and the rotor accommodating section 80 are fitted together by a clearance fit. In this way, the rotor 11 is disposed on the outer peripheral surface of the driving scroll 30 while surrounding the driving scroll 30 from the outer peripheral side.

Also, an annular peripheral wall shoulder 81 is provided on the outer peripheral surface of the rear end of the driving peripheral wall 32. The peripheral wall shoulder 81 is provided rearward of the rotor accommodating portion 80 and continuous with the rotor accommodating portion 80. The outer diameter of the peripheral wall shoulder 81 is larger than the outer diameter of the rotor accommodating portion 80. Specifically, the outer diameter of the peripheral wall shoulder 81 is larger than the outer diameter of the rotor accommodating portion 80 by the radial thickness of the rotor 11. The front surface of the peripheral wall shoulder 81, i.e., the shoulder end surface 811 facing forward of the peripheral wall shoulder 81, abuts against the rear surface 112 of the rotor 11. The shoulder end surface 811 is an example of a "regulating portion" in the present invention.

As shown in FIG. 2, the driving scroll 30 has a first region S and a second region other than the first region S on the outer peripheral surface in the circumferential direction of the driving scroll 30. The first region S includes the outer peripheral end of the driving scroll 33 and a connection portion 82 with the driving peripheral wall 32. The first region S also includes a part of the driving peripheral wall 32. The second region includes the driving peripheral wall 32 other than the driving peripheral wall 32 in the first region S.

The driving peripheral wall 32 in the first region S has a thick portion 85 in which a first inner surface 83 facing radially inward of the driving scroll 30 is located radially inward relative to a second inner surface 84 facing radially inward of the driving peripheral wall 32 in the second region.

In addition, the first inner surface 83 of the driving peripheral wall 32 in the first region S is formed along an involute curve that is an extension of the involute curve drawn by the inner surface 331 of the driving scroll 33. In other words, the involute curve that is an extension of the involute curve drawn by the inner surface 331 of the driving scroll 33 coincides with the involute curve drawn by the first inner surface 83 of the driving peripheral wall 32 in the first region S. This involute curve extends throughout the entire first region S, but the end of the involute curve does not extend to the second region.

A recess 87 is formed on the outer surface 86 of the drive scroll 30 facing radially outward in the first region S. A protrusion 114 that engages with the recess 87 is formed on the opposing inner surface 113 of the rotor 11 that faces radially opposite the outer surface 86 of the drive scroll 30.

The recess 87 and the protrusion 114 extend in the front-rear direction with a constant, roughly rectangular cross-sectional shape. The recess 87 and the protrusion 114 extend in the front-rear direction from the position of the front surface 311 of the driving end plate 31 to the position of the shoulder end surface 811 of the peripheral wall shoulder 81. The recess 87 and the protrusion 114 are also arranged opposite one permanent magnet 12 in the radial direction of the driving scroll 30. In other words, the recess 87 and the protrusion 114 are arranged to avoid the gap between adjacent permanent magnets 12.

An end ring 51 is disposed in front of the rotor 11 in the rotor housing portion 80. The end ring 51 is an example of an "intermediate member" in the present invention. The end ring 51 is made of a non-magnetic material. Specifically, the end ring 51 is made of an aluminum alloy. The end ring 51 is interposed between the bearing cover body 36 and the rotor 11, and is sandwiched between the rear surface 371 of the cover portion 37 and the front surface 111 of the rotor 11.

In the compressor configured as described above, an inverter circuit (not shown) supplies power to the stator 17 while controlling the operation of the electric motor 10, thereby operating the electric motor 10. This causes the rotor 11 to rotate, and the driving scroll 30 is driven to rotate around the driving axis R1 within the suction chamber 61A. In other words, the driving scroll 30, which is integrally formed with the rotor 11, is driven to rotate. At this time, in the driven mechanism 20, each rotation prevention pin 21 slides against the inner circumferential surface of each ring 22, causing each ring 22 to rotate relatively around the center of each rotation prevention pin 21. In this way, the driven mechanism 20 transmits the torque of the driving scroll 30 to the driven scroll 40.

As a result, the driven scroll 40 is rotated around the driven axis R2 by the driving scroll 30 and the driven mechanism 20. At this time, the driven mechanism 20 restricts the driven scroll 40 from rotating on its own axis. As a result, the driving scroll 30 and the driven scroll 40 revolve around the driving axis R1 relative to the driving scroll 30 due to the rotational drive and the rotational follower, thereby changing the volume of the compression chamber 55.

As a result, the refrigerant in the suction chamber 61A is drawn into the compression chamber 55 through the suction port 44 and compressed in the compression chamber 55. The refrigerant compressed to the discharge pressure in the compression chamber 55 is then discharged from the discharge port 35 into the discharge valve chamber 34, passes through the discharge section 38B, and is discharged from the discharge connection port 65B into the condenser. In this way, air conditioning is performed by the vehicle air conditioning system.

Here, in this compressor, the bearing cover body 36 is fixed to the front surface 311 of the driving end plate 31 at the front side of the driving scroll 30, and a peripheral wall shoulder 81 is provided on the driving peripheral wall 32 at the rear side of the driving scroll 30. The rotor 11 arranged in the rotor accommodating section 80 of the driving scroll 30 is restricted in its forward movement by the cover portion 37 of the bearing cover body 36, and restricted in its rearward movement by the shoulder end face 811 of the peripheral wall shoulder 81. Therefore, the bearing cover body 36 and the peripheral wall shoulder 81 can prevent the rotor 11 from slipping out of the driving scroll 30 in the forward/rearward direction.

In this case, since no bolt holes or the like are formed in the rotor 11 to prevent it from coming loose, the strength of the rotor 11 is not reduced, and the durability of the rotor 11 is not reduced either.

The first boss 38, which receives the bearing load from the needle bearing 72, is integrally formed with the bearing cover body 36, and this bearing cover body 36 has a higher strength than the driving end plate 31. Therefore, the first boss 38 can withstand the bearing load from the needle bearing 72.

Therefore, according to the compressor of the embodiment, the first boss 38 rotatably supported by the needle bearing 72 can withstand the bearing load, and the rotor 11 can be prevented from coming loose from the driving scroll 30 without reducing the durability of the rotor 11.

In addition, in this compressor, end rings 51 made of a non-magnetic material are interposed between the rotor 11 and the bearing cover body 36. Therefore, the end rings 51 can suppress magnetic flux leakage. As a result, the bearing cover body 36 can be made of an iron-based alloy, which is cost-effective.

Furthermore, in this compressor, the front surface 311 of the drive end plate 31 is in surface contact with the rear surface 371 of the cover portion 37, which faces the front surface 311 in the front-rear direction. This makes it easier to fix the bearing cover body 36 to the drive end plate 31 in the correct position, which is advantageous in ensuring coaxiality between the drive axis R1 and the first boss 38.

In addition, in this compressor, a recess 87 formed on the outer surface 86 of the drive scroll 30 engages with a protrusion 114 formed on the opposing inner surface 113 of the rotor 11. This ensures good torque transmission from the rotor 11 to the drive scroll 30 through the engagement of the recesses and protrusions.

And because the torque transmission force from the rotor 11 to the driving scroll 30 is not secured by pressing the rotor 11 and the driving scroll 30 together, the driving scroll 30 is not deformed due to the press-fitting. Also, because the recess 87 is provided in the thick portion 85 of the driving peripheral wall 32, the strength of the driving peripheral wall 32 is not significantly reduced due to the formation of the recess 87. As a result, deformation of the driving scroll 30 can be effectively suppressed.

Furthermore, the recesses 87 and the protrusions 114 are arranged to avoid the gaps between adjacent permanent magnets 12. This makes it possible to suppress disturbance of the magnetic field lines caused by the formation of the recesses 87 and the protrusions 114.

Example 2
As shown in Fig. 3, in the compressor of the second embodiment, a bearing cover body 36A is used instead of the bearing cover body 36 in the compressor of the first embodiment. This bearing cover body 36A is made of a non-magnetic material. Specifically, the bearing cover body 36A is made of an iron-based alloy as a non-magnetic steel having a higher strength than the driving scroll 30. This bearing cover body 36A has a cover portion 37A and a first boss 38A, similar to the bearing cover body 36 in the compressor of the first embodiment.

No end ring is interposed between the rotor 11 and the bearing cover body 36A. In other words, the front surface 111 of the rotor 11 abuts against the rear surface 371 of the cover portion 37A of the bearing cover body 36A.

As a result, this compressor can prevent magnetic flux leakage through the bearing cover body 36A while omitting the end rings. As a result, the number of parts can be reduced compared to the compressor of Example 1.

The rest of the configuration and operation of this compressor is the same as that of the compressor in Example 1, and the same components are given the same reference numerals and detailed explanations of the configurations are omitted.

　Although the present invention has been described above with reference to Examples 1 and 2, it goes without saying that the present invention is not limited to the above Examples 1 and 2, and can be modified as appropriate without departing from the spirit of the present invention.

For example, in the compressors of Examples 1 and 2, a peripheral wall shoulder is formed on the driving peripheral wall, and the end face of the shoulder constitutes the regulating portion. However, this is not limited to this, and the regulating portion may be constituted by attaching a circlip or the like made of a non-magnetic material to the driving peripheral wall.

In the compressors of Examples 1 and 2, a gasket may be interposed between the front surface 311 of the drive end plate 31 and the rear surface 371 of the cover portion 37.

In the compressors of Examples 1 and 2, a predetermined torque transmission force is ensured from the rotor 11 to the driving scroll 30 by the engagement of the recessed portion 87 and the protruding portion 114, but the present invention is not limited to this. For example, the predetermined torque transmission force may be ensured by press-fitting the rotor 11 and the driving scroll 30 or by using bolts, pins, or keys.

In the compressors of Examples 1 and 2, the driven mechanism 20 is composed of a rotation prevention pin 21 and a ring 22. However, this is not limited to this, and the driven mechanism 20 may be composed of a pin-ring-pin system in which two pins slide against the inner peripheral surface of one free ring, a pin-pin system in which the outer peripheral surfaces of two pins slide against each other, a system using an Oldham joint, etc.

(Appendix 1)
The scroll includes a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism,
The driving scroll is rotated about a drive axis by the driving mechanism,
The driven scroll is rotated around a driven axis by the driving scroll and the driven mechanism while being eccentric with respect to the driving scroll,
The drive scroll has a drive end plate extending in a direction intersecting the drive axis, a drive peripheral wall protruding in a cylindrical shape from the drive end plate toward the driven scroll, and a drive scroll body protruding in a spiral shape from the drive end plate toward the driven scroll within the drive peripheral wall,
The driven scroll has a driven end plate extending in a direction intersecting the driven axis, and a driven scroll protruding in a spiral shape from the driven end plate toward the driving scroll,
The drive scroll and the driven scroll form a compression chamber by opposing each other, and the volume of the compression chamber is changed by the rotation drive and the rotation driven.
A bearing cover body having a higher strength than the drive end plate is fixed to an end surface of the drive end plate opposite to the compression chamber on one side of the drive scroll in the drive axial direction, and a restricting portion is provided on the drive peripheral wall on the other side of the drive scroll in the drive axial direction,
the bearing cover body has a supported portion integrally therewith that is rotatably supported on the housing via a bearing,
The drive mechanism has a cylindrical rotor that surrounds the drive scroll from the outer circumferential side and is disposed on the outer circumferential surface of the drive scroll,
a bearing cover body that restricts movement of the rotor toward the one side in the direction of the drive shaft, and a restricting portion that restricts movement of the rotor toward the other side in the direction of the drive shaft.

(Appendix 2)
The drive scroll has a rotor accommodating portion provided on the drive end plate and the drive peripheral wall, the rotor being disposed on an outer peripheral surface of the rotor accommodating portion, and a peripheral wall shoulder provided on the drive peripheral wall, the peripheral wall shoulder having an outer diameter larger than that of the rotor accommodating portion,
2. The double-rotating scroll compressor according to claim 1, wherein a shoulder end surface of the peripheral wall shoulder facing the one side in the drive shaft direction constitutes the regulating portion.

(Appendix 3)
The bearing cover body is made of a magnetic material,
3. The double rotary scroll compressor according to claim 1, wherein an intermediate member made of a non-magnetic material is interposed between the bearing cover body and the rotor.

(Appendix 4)
3. The double rotary scroll compressor according to claim 1, wherein the bearing cover is made of a non-magnetic material.

(Appendix 5)
5. The double-rotating scroll compressor according to claim 1, wherein the end surface of the driving end plate and an opposing surface of the bearing cover body opposed to the end surface are in surface contact with each other.

The present invention can be used in vehicle air conditioning systems, etc.

10 Electric motor (drive mechanism)
11 rotor 20 driven mechanism 30 driving scroll 31 driving end plate 311 front surface (end surface)
32 Drive peripheral wall 33 Drive scroll 80 Rotor accommodating portion 36 Bearing cover body 37 Cover portion 371 Rear surface (opposing surface)
38 1st boss (supported part)
81 Surrounding wall shoulder 811 Shoulder end face (regulating part)
40: driven scroll 41: driven end plate 42: driven scroll body 51: end ring (intermediate member)
55 Compression chamber 60 Housing 72 Needle bearing
R1 Drive shaft center R2 Driven shaft center

Claims (5)

The scroll includes a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism,
The driving scroll is rotated about a drive axis by the driving mechanism,
The driven scroll is rotated around a driven axis by the driving scroll and the driven mechanism while being eccentric with respect to the driving scroll,
The drive scroll has a drive end plate extending in a direction intersecting the drive axis, a drive peripheral wall protruding in a cylindrical shape from the drive end plate toward the driven scroll, and a drive scroll body protruding in a spiral shape from the drive end plate toward the driven scroll within the drive peripheral wall,
The driven scroll has a driven end plate extending in a direction intersecting the driven axis, and a driven scroll protruding in a spiral shape from the driven end plate toward the driving scroll,
The drive scroll and the driven scroll form a compression chamber by opposing each other, and the volume of the compression chamber is changed by the rotation drive and the rotation driven.
A bearing cover body having a higher strength than the drive end plate is fixed to an end surface of the drive end plate opposite to the compression chamber on one side of the drive scroll in the drive axial direction, and a restricting portion is provided on the drive peripheral wall on the other side of the drive scroll in the drive axial direction,
the bearing cover body has a supported portion integrally therewith that is rotatably supported on the housing via a bearing,
The drive mechanism has a cylindrical rotor that surrounds the drive scroll from the outer circumferential side and is disposed on the outer circumferential surface of the drive scroll,
a bearing cover body that restricts movement of the rotor toward the one side in the direction of the drive shaft, and a restricting portion that restricts movement of the rotor toward the other side in the direction of the drive shaft. The drive scroll has a rotor accommodating portion provided on the drive end plate and the drive peripheral wall, the rotor being disposed on an outer peripheral surface of the rotor accommodating portion, and a peripheral wall shoulder provided on the drive peripheral wall, the peripheral wall shoulder having an outer diameter larger than that of the rotor accommodating portion,
2. The double-rotation scroll compressor according to claim 1, wherein a shoulder end face of the peripheral wall shoulder facing the one side in the drive shaft direction constitutes the restricting portion. The bearing cover body is made of a magnetic material,
3. A double-rotating scroll compressor according to claim 1, further comprising an intermediate member made of a non-magnetic material interposed between said bearing cover body and said rotor. The double-rotating scroll compressor according to claim 1 or 2, wherein the bearing cover body is made of a non-magnetic material. The double-rotating scroll compressor according to claim 1 or 2, wherein the end face of the drive end plate and the opposing surface of the bearing cover body that faces the end face are in surface contact.

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