CO-ROTATING SCROLL COMPRESSOR

Description

BACKGROUND

The present disclosure relates to the technical field of compressors, and more particularly to a co-rotating scroll compressor.

Scroll compressors are widely used in air conditioning due to their numerous advantages, including high volumetric efficiency, minimal vibration, and low noise. Improvements to existing scroll compressors primarily focus on increasing suction volume and enhancing volumetric efficiency. These compressors typically use a single orbiting scroll and a single fixed scroll, with the medium being compressed by the orbital motion of the orbiting scroll relative to the fixed scroll. However, this design presents several challenges. First, the orbital motion of the orbiting scroll generates eccentric inertia, causing the scroll body of the orbiting scroll to collide with that of the fixed scroll. This reduces the reliability of the scroll body and shortens its service life. Second, to counteract the eccentric inertia of the orbiting scroll, an eccentric block must be placed on the eccentric shaft to compensate for the eccentric dynamic mass. This not only increases the weight of the compressor but also raises energy consumption and complicates the manufacturing and assembly processes. Third, to suppress the self-rotation of the orbiting scroll, allowing it to only orbit in a translational motion, an anti-rotation structure must be implemented. This further adds to the weight of the compressor and complicates its manufacture and assembly.

Therefore, there is an urgent need in the art for a technical solution that leverages the advantages of scroll compressors while effectively addressing the shortcomings of existing scroll compressors.

SUMMARY

In order to address the problems in the prior art described above, the present disclosure provides a co-rotating scroll compressor, comprising: a housing; a motor mounted within the housing, the motor comprising a first rotor and a second rotor configured to rotate in opposite directions around a main axis; a proximal scroll plate and a distal scroll plate rotatably disposed within the housing and meshing with each other, wherein the proximal scroll plate is positioned between the motor and the distal scroll plate; a gear pair coupling the first rotor to the proximal scroll plate such that the proximal scroll plate is adapted to rotate around a secondary axis offset relative to the main axis, the gear ratio of the gear pair being equal to the rotational speed ratio of the first rotor to the second rotor; and a support cylinder connecting the second rotor to the distal scroll plate such that the distal scroll plate is adapted to rotate synchronously with the second rotor around the main axis.

The present disclosure may be embodied as a schematic example in the accompanying drawings. However, it should be noted that the accompanying drawings are merely schematic and that any change contemplated under the teachings of the present disclosure shall be considered to be included within the scope of the present disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

The accompanying drawings illustrate exemplary examples of the present disclosure. These accompanying drawings should not be construed as necessarily limiting the scope of the present disclosure, wherein:

FIG. 1 is a schematic cross-sectional view of a co-rotating scroll compressor according to one embodiment of the present disclosure;

FIGS. 2A-2C are schematic cross-sectional views of a proximal scroll body and a distal scroll body taken along line II-II in FIG. 1 at different rotational positions;

FIG. 3 is a schematic cross-sectional view of an outer bearing, an eccentric block, and an inner bearing taken along line III-III in FIG. 1;

FIG. 4 is a schematic perspective view of the distal scroll plate of FIG. 1; and

FIG. 5 is a schematic cross-sectional view of a co-rotating scroll compressor according to another embodiment of the present disclosure.

DETAILED DESCRIPTION

Further features and advantages of the present disclosure will become more apparent from the following description, which is made with reference to the accompanying drawings. Exemplary examples of the present disclosure are shown in the accompanying drawings, and the various accompanying drawings are not necessarily drawn in actual proportions. However, the present disclosure may be implemented in many different forms and should not be construed as necessarily limiting to the exemplary examples disclosed herein. Rather, these exemplary examples are merely provided for illustrative purposes of the present disclosure and for delivering the spirit and substance of the present disclosure to those skilled in the art.

The present disclosure aims to propose an improved co-rotating scroll compressor. Compared to traditional rotary scroll compressors, this co-rotating scroll compressor replaces the revolution of one scroll plate relative to another with the rotation of two scroll plates around two mutually offset axes in the process of working on the medium (e.g., coolants such as R744, R134A, R290, etc.). This avoids the eccentric inertia caused by the revolution of the scroll plates and thus reduces the lateral impact of the scroll bodies of the two scroll plates caused by eccentric inertia, thereby improving the reliability of the scroll bodies and extending their service life. In addition, the co-rotating scroll compressor according to the present disclosure does not need to set an eccentric block to overcome the eccentric inertia, thereby simplifying the overall structure of the compressor. Moreover, since the orbital translational motion is replaced by the self-rotation motion around their respective rotation axes with higher stability, the dynamic performance of the co-rotating scroll compressor is also significantly improved. In particular, in addition to the advantages mentioned above, in some specific embodiments, the co-rotating scroll compressor according to the present disclosure can also offer several benefits. These include reliably ensuring that the two scroll plates rotate in the same direction and at the same speed, as well as effectively suppressing the axial gap and radial offset between the two scroll plates.

Various optional but non-limiting embodiments of a co-rotating scroll compressor according to the present disclosure are described in detail below with reference to the accompanying drawings. It should be noted that, among the terms used herein to indicate the relative orientations of various components, “axial direction” refers to a direction coincident with or parallel to the axis of rotation, “radial direction” refers to a direction perpendicular to the axis of rotation, and “circumferential direction” refers to a direction around the axis of rotation. Unless otherwise expressly stated, these terms indicating relative orientations have their usual meanings in the art.

Referring to FIG. 1, a schematic cross-sectional view of a co-rotating scroll compressor according to an embodiment of the present disclosure is shown. As shown in FIG. 1, the co-rotating scroll compressor 10 comprises a housing 100 and a motor 200 mounted within the housing 100. The motor 200 comprises two rotors (i.e., a first rotor 210 and a second rotor 220) rotatably disposed within the housing 100 and a stator 230 fixedly disposed within the housing 100. Each of the first rotor 210 and the second rotor 220 is adapted to be coupled with a rotational magnetic field generated by the stator 230 to rotate around a main axis MA. In particular, the motor 200 may be a permanent magnet synchronous motor, wherein the stator 230 comprises a stator core 231 fixedly disposed within the housing 100 and a stator winding 232 attached to the stator core 231, the stator winding 232 being adapted to generate a rotating magnetic field rotating around the main axis MA after being energized by alternating current; the first rotor 210 comprises a rotor core 211 rotatably disposed within the housing 100 and a plurality of permanent magnets 212 attached to the rotor core 211. These permanent magnets 212 are distributed along the circumferential direction and are adapted to be coupled with the rotating magnetic field, thereby driving the rotor core 211 to rotate together around the main axis MA under the drive of the rotating magnetic field; similar to the first rotor 210, the second rotor 220 also comprises a rotor core 221 rotatably disposed within the housing 100 and a plurality of permanent magnets 222 attached to the rotor core 221. These permanent magnets 222 are distributed along the circumferential direction and are adapted to be coupled with the rotating magnetic field, thereby driving the rotor core 221 to rotate together around the main axis MA under the drive of the rotating magnetic field. In the above manner, electrical energy is converted into the kinetic energy of the two rotors. As can be seen from the foregoing, by adjusting the alternating current supplied to the stator winding 232, the rotating magnetic field produced by the stator winding 232 can be adjusted, thereby adjusting the rotational speed and/or direction of each rotor. Accordingly, the motor 200 may further comprise control devices such as an inverter (not shown), which may, for example, adjust the alternating current supplied to the stator winding 232 by pulse width modulation and thereby independently control the rotational speed and/or direction of the first rotor 210 and the second rotor 220. It is to be noted that although the specific configuration of the motor 200 is described above with a permanent magnet synchronous motor as an example, it is understood by those skilled in the art that the motor 200 can also be other types of motors, such as asynchronous motors. Therefore, the specific type of motor 200 cannot constitute a limitation on the protective scope of the present disclosure.

Continuing to refer to FIG. 1, the co-rotating scroll compressor 10 further comprises two scroll plates rotatably disposed within the housing 100 and spaced apart from the motor 200 along the axial direction, i.e., a proximal scroll plate 300 closer to the motor 200 and a distal scroll plate 400 farther from the motor 200, i.e., the proximal scroll plate 300 is positioned between the motor 200 and the distal scroll plate 400 in the axial direction. As shown in FIG. 1, the proximal scroll plate 300 is coupled to the first rotor 210 by a gear pair 500. The gear pair 500 comprises a drive gear 510 and a driven gear 520 that mesh with each other, wherein the drive gear 510 is oriented along the main axis MA and coupled to the first rotor 210 so that the drive gear 510 can rotate synchronously with the first rotor 210 (i.e., at the same rotational speed and in the same direction) around the main MA. The driven gear 520 is oriented along a secondary axis SA that is parallel to the main axis MA and offset relative to the main axis MA and coupled to the proximal scroll plate 300 so that the driven gear 520 can rotate synchronously with the proximal scroll plate 300 around the secondary axis SA. It is worth noting that the gear pair 500 not only transmits the rotational motion of the first rotor 210 to the proximal scroll plate 300 at a certain drive ratio, but also causes the rotational direction (i.e., the direction of rotation) of the proximal scroll plate 300 to be opposite to the rotational direction of the first rotor 210. As shown in FIG. 1, the scroll compressor 10 further comprises a support cylinder 600 coupling the distal scroll plate 400 to the second rotor 220. The support cylinder 600 is connected to the distal scroll plate 400 at one end and to the second rotor 220 at the other end to enable the distal scroll plate 400 to rotate around the main axis MA synchronously with the second rotor 220.

Further, by configuring the first rotor 210 and the second rotor 220 such that the rotational direction of the first rotor 210 is opposite to the rotational direction of the second rotor 220 and the ratio of the rotational speed of the first rotor 210 to the rotational speed of the second rotor 220 is equal to the drive ratio of the gear pair 500 (i.e., the ratio of the rotational speed of the drive gear 510 to the rotational speed of the driven gear 520), e.g., the rotational speed of the first rotor 210 is the same as the rotational speed of the second rotor 220 and the drive ratio of the gear pair 500 is 1, the proximal scroll plate 300 and the distal scroll plate 400 can rotate around the secondary axis SA and the main MA respectively in the same direction and at the same rotational speed, thereby moving and compressing the medium between the proximal scroll plate 300 and the distal scroll plate 400 towards their center. Specifically, as shown in FIG. 1, the proximal scroll plate 300 comprises a proximal scroll body 310 protruding along the axial direction. The proximal scroll body 310 is spiral or scroll-shaped when viewed along the axial direction and extends from the outer periphery or surrounding area of the proximal scroll plate 300 toward the center along the scroll direction. The distal scroll plate 400 comprises a distal scroll body 410 protruding along the axial direction. The distal scroll body 410 is also spiral or scroll-shaped when viewed along the axial direction and extends from the outer periphery or surrounding area of the distal scroll plate 400 toward its center along the scroll direction. In addition, the proximal scroll plate 300 and the distal scroll plate 400 are positioned such that a side surface of the proximal scroll body 310 and a side surface of the distal scroll body 410 engage with each other, so that the proximal scroll body 310 and the distal scroll body 410 cooperate or mesh, thereby defining a plurality of compression chambers between the two scroll bodies as described in more detail below. These compression chambers are arranged along the scroll direction and isolated from each other, and among these compression chambers, the compression chambers closer to the center of the two scroll bodies have smaller volumes. As the proximal scroll plate 300 rotates around the secondary axis SA and the distal scroll plate 400 rotates around the main axis MA at the same speed and in the same direction, each compression chamber moves along the scroll direction toward the center of the two scroll bodies while its volume gradually decreases, which causes the medium in each compression chamber to be pushed toward the center of the two scroll bodies and gradually compressed, thereby causing the pressure of the medium to gradually increase and reach a maximum when the medium moves to the center of the two scroll bodies and achieving a compression process of the medium. Of course, in the embodiment shown in FIG. 1, to discharge the compressed medium at the center of the two scroll bodies, the distal scroll plate 400 is further provided with an exhaust hole 401. The exhaust hole 401 extends through the distal scroll plate 400 and leads to the center of the distal scroll body 410, thereby allowing the compressed medium at the center of the two scroll bodies to be discharge through the exhaust hole 401.

In order to make the above compression process more intuitive, the following description will be made with reference to the cross-sectional view of the proximal scroll body 310 and the distal scroll body 410. Referring to FIGS. 2A-2C, schematic cross-sectional views of the proximal scroll body 310 and the distal scroll bodies 410 taken along line II-II in FIG. 1 at different rotational positions are shown. As shown in FIGS. 2A-2C, the proximal scroll body 310 and the distal scroll body 410 define two groups of compression chambers arranged symmetrically about the center of the two scroll bodies between each other, wherein each group of compression chambers comprises a first compression chamber C1, a second compression chamber C2, and a third compression chamber C3 arranged from outside to inside along the scroll direction and isolated from each other. When the two scroll bodies are in the first position shown in FIG. 2A, the first compression chamber C1 is open to allow the medium to be compressed to enter the first compression chamber C1, while the second compression chamber C2 and the third compression chamber C3 that have already accommodated the medium are closed. When the two scroll bodies rotate respectively from the first position shown in FIG. 2A to the second position shown in FIG. 2B, the first compression chamber C1 moves toward the center of the two scroll bodies and begins to close, the second compression chamber C2 moves toward the center of the two scroll bodies and decreases in volume, and the third compression chamber C3 reaches the center of the two scroll bodies and decreases in volume, so that the medium in each compression chamber is pushed toward the center of the two scroll bodies and compressed. When the two scroll bodies further rotate respectively from the second position shown in FIG. 2B to the third position shown in FIG. 2C, the first compression chamber C1 moves further toward the center of the two scroll bodies and completely closes, the second compression chamber C2 moves further toward the center of the two scroll bodies and decreases in volume, and the third compression chamber C3 remains at the center of the two scroll bodies while its volume decreases further, so that the medium in each compression chamber is pushed further toward the center of the two scroll bodies and further compressed. As the two scroll bodies further rotate respectively from the third position shown in FIG. 2C back to the first position shown in FIG. 2A, the third compression chamber C3 disappears, thereby discharging the compressed medium. The second compression chamber C2 becomes the new third compression chamber C3, and the first compression chamber C1 becomes the new second compression chamber C2. A new first compression chamber C1 is generated, thereby ending the previous compression process and starting a new one. As the two scroll plates rotate, the above compression process is repeated, allowing the two scroll bodies to continuously suction, move, compress, and discharge the medium.

Under the above configuration, the compression process is achieved by the two scroll plates rotating at the same speed and in the same direction around two mutually offset axes, rather than through the orbital motion (also known as translational motion) of either scroll plate. Therefore, neither scroll plate generates eccentric inertia due to orbital motion, which prevents the two scroll bodies from colliding with each other due to eccentric inertia, thereby extending the service life of the scroll bodies and improving their reliability. Furthermore, there is no need to provide an eccentric block to overcome eccentric inertia, nor is there a need to provide an anti-rotation structure to suppress the self-rotation of the scroll plates. This simplifies the overall structure of the compressor and improves its reliability. Furthermore, since the orbital motion is replaced by a more stable rotational motion, the dynamic performance of the compressor is significantly improved.

According to an optional embodiment of the present disclosure, as shown in FIG. 1, as the proximal scroll plate 300 is positioned between the motor 200 and the distal scroll plate 400, the support cylinder 600 is configured to transmit the rotational motion of the second rotor 220 across the proximal scroll plate 300 to the distal scroll plate 400, such that the proximal scroll plate 300 is positioned radially inside of the support cylinder 600 such that the support cylinder 600 surrounds the proximal scroll plate 300 radially outside of the proximal scroll plate 300. As shown in FIG. 1, the co-rotating scroll compressor 10 further comprises an outer bearing 710, an eccentric block 720, and an inner bearing 730 disposed within the support cylinder 600, wherein the outer bearing 710 is mounted on the support cylinder 600 and supports the eccentric block 720, the eccentric block 720 supports the inner bearing 730, and the inner bearing 730 supports the proximal scroll plate 300, and wherein the outer bearing 710 is arranged around the main axis MA to allow the support cylinder 600 to rotate relative to the eccentric block 720 around the main axis MA, while the inner bearing 730 is arranged around the secondary axis SA to allow the proximal scroll plate 300 to rotate relative to the eccentric block 720 around the secondary axis SA, i.e., the outer bearing 710 and the inner bearing 730 are nested together eccentrically through the eccentric block 720. Specifically, referring to FIG. 3, which shows a schematic cross-sectional view of the outer bearing, the eccentric block, and the inner bearing taken along line III-III in FIG. 1, the outer ring 711 of the outer bearing 710 is fixed to the support cylinder 600, while its inner ring 712 is fixed to the eccentric block 720. The eccentric block 720 is generally disc-shaped and has an eccentric hole 721 that is eccentric relative to its outer periphery. The inner bearing 730 is accommodated in the eccentric hole 721, and its outer ring 731 is fixed to the eccentric block 720, while its inner ring 732 is fixed to the proximal scroll plate 300. In this configuration, during operation, due to the presence of the outer bearing 710, the support cylinder 600 may rotate relative to the eccentric block 720 and support the eccentric block 720, while due to the presence of the inner bearing 730, the eccentric block 720 allows the proximal scroll plate 300 to rotate and supports the proximal scroll plate 300. Additionally, the inner ring 712 of the outer bearing 710 and the outer ring 731 of the inner bearing 730 can remain stationary together with the eccentric block 720. In other words, the support cylinder 600 can support the proximal scroll 300 through two bearings nested together in an eccentric manner, thereby achieving reliable positioning of the proximal scroll plate 300. In particular, the co-rotating scroll compressor 10 further comprises a distal bearing 740 mounted within the housing 100. The distal bearing 740 is arranged around the main axis MA and used to support the distal scroll plate 400 to allow the distal scroll plate 400 to rotate around the main axis MA. Specifically, the outer ring 741 of the distal bearing 740 is fixed to the housing 100, while its inner ring 742 is fixed to the distal scroll plate 400 to enable the housing 100 to support the distal scroll plate 400 and allow the distal scroll plate 400 to rotate, thereby achieving reliable positioning of the distal scroll plate 400.

According to an optional embodiment of the present disclosure, as shown in FIG. 1, the housing 100 comprises a housing body 110 defining an interior chamber and an isolation plate 120 disposed within the housing body 110. The isolation plate 120 divides the interior chamber into an intake chamber 111 for receiving a medium to be compressed and an exhaust chamber 112 for receiving the compressed medium. In particular, the housing body 110 is further provided with an inlet 113 in fluid communication with the intake chamber 111 and an outlet 114 in fluid communication with the exhaust chamber 112 so that the medium to be compressed from the outside can be supplied to the intake chamber 111 through the inlet 113, while the compressed medium in the exhaust chamber 112 can be supplied to the outside through the outlet 114. In particular, the distal bearing 740 (more specifically, its outer ring 741) is mounted on the isolation plate 120 and components that perform work on the medium, such as the motor 200, the proximal scroll plate 300, and the distal scroll plate 400, are housed in the intake chamber 111 so as to compress the medium in the intake chamber 111 and then discharge it into the exhaust chamber 112.

To this end, the isolation plate 120 is provided with a through hole 121. The through hole 121 extends through the isolation plate 120, the distal scroll plate 400 comprises a post 402 protruding along the axial direction and oriented along the main axis MA, i.e., the post 402 is oriented such that its axis coincides with the main axis MA, and the exhaust hole 401 extends through the post 402. As shown in FIG. 1, the post 402 is inserted into the through hole 121 of the isolation plate 120 such that the exhaust hole 401 is in fluid communication with the exhaust chamber 112, thereby allowing the compressed medium to be discharged from the center of the two scroll bodies through the exhaust hole 401 into the exhaust chamber 112. In particular, the co-rotating scroll compressor 10 further comprises a sealing ring 801 disposed in the through hole 121 of the isolation plate 120. The sealing ring 801 surrounds the post 402 of the distal scroll plate 400 and is clamped or pressed between the post 402 and a side wall of the through hole 121. In this configuration, the sealing ring 801 can provide a seal between the post 402 and the side wall of the through hole 121, thereby preventing the compressed medium in the exhaust chamber 112 from leaking through the gap between the post 402 and the side wall of the through hole 121 into the intake chamber 111 and helping to maintain the volumetric efficiency of the co-rotating scroll compressor 10. Optionally, the sealing ring 801 is made of a wear-resistant elastomer material such as nitrile rubber or polyurethane rubber, which can provide sealing performance while resisting wear caused by the rotation of the post 402.

According to an optional embodiment of the present disclosure, as shown in FIG. 1, the proximal scroll plate 300 further comprises a proximal plate body 320 that is generally disc-shaped and oriented transversely to the secondary axis SA, wherein the proximal scroll body 310 protrudes from the proximal plate body 320 along the axial direction. Further, referring to FIG. 4, which shows a schematic perspective view of the distal scroll plate of FIG. 1, the distal scroll plate 400 further comprises a distal plate body 420 that is generally disc-shaped and oriented transversely to the main axis MA and a distal ring body 430 that is generally cylindrical and protrudes axially from the distal plate body 420 and extends circumferentially, wherein the distal scroll body 410 also protrudes axially from the distal plate body 420 but is located radially inside of the distal ring body 430, such that the distal ring body 430 surrounds the distal scroll body 410 radially outside of the distal scroll body 410. As shown in FIG. 1, the distal scroll body 410 abuts the proximal plate body 320 and the proximal scroll body 310 abuts the distal plate body 420, thereby eliminating the axial gap between the distal scroll plate 400 and the proximal scroll plate 300 that could lead to axial leakage of the medium in each compression chamber, thus ensuring the volumetric efficiency of the compressor. In particular, the distal ring body 430 defines a contact area CA on its outer periphery or circumference for connection with the support cylinder 600, the contact area CA extending circumferentially (specifically, extending through the entire circumference) and having a non-zero axial height H1. In this configuration, since the contact area CA is defined on the outer periphery or circumference of the distal ring body 430 rather than on the outer periphery or circumference of the distal plate body 420, the axial height H1 of the contact area CA is not limited by the thickness of the distal plate body 420. This allows the contact area CA to have a larger axial height H1, which enables the support cylinder 600 to reliably maintain the radial position of the distal scroll plate 400 and reliably maintain the radial position of the proximal scroll plate 300 through the distal scroll plate 400. This reduces the overturning of the distal scroll body 410 and the proximal scroll body 310, thereby reducing tangential leakage of the medium and ensuring the volumetric efficiency of the compressor. More particularly, the height range of the axial height H2 of the engagement area EA of the proximal scroll body 310 and the distal scroll body 410 is located in the height range of the axial height H1 of the contact area CA; that is, the axial height H1 of the contact area CA is greater than and crosses the axial height H2 of the engagement area EA, thereby enabling the support cylinder 600 to more reliably maintain the radial position of the proximal scroll plate 300 and the distal scroll plate 400.

According to an optional embodiment of the present disclosure, as shown in FIG. 1, the motor 200 further comprises a spindle 240, wherein the spindle 240 is fixed on the housing 100 (more specifically, the housing body 110) and oriented along the main axis MA, i.e., the spindle 240 is oriented such that its axis coincides with the main axis MA. Additionally, the stator 230 is fixed on the spindle 240, i.e., the stator 230 is fixedly supported on the spindle 240, while the first rotor 210 is supported by a first bearing 251 mounted on the spindle 240 such that the first rotor 210 is rotatably supported on the spindle 240 and the second rotor 220 is supported by a second bearing 252 mounted on the spindle 240 such that the second rotor 220 is rotatably supported on the spindle 240. In addition, the first rotor 210 and the second rotor 220 are spaced apart from each other along the axial direction and located on opposite axial sides of the stator 230. Not only is the first rotor 210 positioned radially inside of the support cylinder 600, but the stator 230 is also positioned radially inside of the support cylinder 600 such that the support cylinder 600 surrounds the stator 230 radially outside of the stator 230. In this configuration, the first rotor 210 and the second rotor 220 are configured to be coupled to the magnetic flux flowing in the axial direction generated by the stator 230 and are able to rotate relative to the spindle 240 under the drive of the rotating magnetic field. Therefore, in the embodiment shown in FIG. 1, the motor 200 is configured as an axial flux motor. Since axial flux motors have many advantages such as small size and high power density, the above configuration helps to improve the working efficiency of the scroll compressor 10 while reducing its size. In addition, the drive gear 510 of the gear pair 500 is connected to the first rotor 210, while the driven gear 520 is connected to the proximal scroll plate 300. During operation, the first rotor 210 and the second rotor 220 rotate relative to the spindle 240, and the first rotor 210 drives the rotation of the proximal scroll plate 300 around the secondary axis SA through the gear pair 500, while the second rotor 220 drives the rotation of the distal scroll plate 400 around the main axis MA through the support cylinder 600, thereby completing the above-described compression process.

It is to be noted that although the motor 200 is configured as an axial flux motor in the embodiment shown in FIG. 1, this is merely exemplary, and the motor 200 may also be configured as other types of motors.

For example, referring to FIG. 5, a schematic cross-sectional view of a co-rotating scroll compressor according to another embodiment of the present disclosure is shown. Since the embodiment shown in FIG. 5 is essentially the same as the embodiment shown in FIG. 1, only the differences between the embodiment shown in FIG. 5 and the embodiment shown in FIG. 1 are described below. For the sake of brevity, the similarities between the two will not be repeated. As shown in FIG. 5, the motor 200 is configured as a radial flux motor. Specifically, the stator 230 is fixed to the housing 100 (more specifically, the housing body 110), the second rotor 220 is positioned radially inside of the stator 230, and the first rotor 210 is positioned radially inside of the second rotor 220, i.e., the first rotor 210 is nested radially inside of the second rotor 220 such that the second rotor 220 surrounds the first rotor 210 radially outside of the first rotor 210. Additionally, the first rotor 210 is further fixed on the spindle 240, while the spindle 240 is supported by a main bearing 254 mounted on the housing 100 (more specifically, the housing body 110) such that the spindle 240 is rotatably disposed in the housing 100 and the second rotor 220 is supported by two second bearings 252 mounted on the spindle 240 and spaced apart in the axial direction, so that the second rotor 220 is rotatably supported on the spindle 240. In particular, the two second bearings 252 are positioned on opposite axial sides of the first rotor 210. In this configuration, the first rotor 210 and the second rotor 220 are configured to be coupled to the magnetic flux flowing radially generated by the stator 230, so that the first rotor 210 rotates synchronously with the spindle 240 under the drive of the rotating magnetic field, while the second rotor 220 rotates relative to the spindle 240. Therefore, in the embodiment shown in FIG. 5, the motor 200 is configured to be a radial flux motor. As radial flux motors have many advantages such as mature technology and low manufacturing cost, the above configuration helps to reduce the manufacturing cost of the scroll compressor 10. In addition, the drive gear 510 of the gear pair 500 is connected to the spindle 240, while the driven gear 520 is connected to the proximal scroll plate 300. During operation, the spindle 240 rotates synchronously with the first rotor 210 and drives the proximal scroll plate 300 rotate around the secondary axis SA through the gear pair 500, while the second rotor 220 rotates relative to the spindle 240 and drives the distal scroll plate 400 to rotate around the main axis MA through the support cylinder 600, thereby completing the above-described compression process.

The above optional but non-limiting examples of a co-rotating scroll compressor according to the present disclosure are described in detail above with reference the accompanying drawings. For those skilled in the art, without departing from the spirit and substance of the present disclosure, modifications and additions to techniques and structures and recombination of features in various examples shall clearly be considered to be included within the scope of the present disclosure. As a result, these modifications and supplements that may be conceived under the guidance of the present disclosure shall be considered as a part of the present disclosure. The scope of the present disclosure includes known equivalent technologies and equivalent technologies not yet foreseen as of the filing date of this disclosure.