Co-rotating scroll compressor

Abstract

The present disclosure proposes 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 about a main axis; a proximal scroll and a distal scroll rotatably disposed within the housing and meshing with each other, wherein the proximal scroll is located between the motor and the distal scroll; a gear pair coupling the first rotor with the proximal scroll, such that the proximal scroll is adapted to rotate about a secondary axis offset with respect to the main axis, a transmission ratio of the gear pair being equal to a rotational speed ratio of the first rotor to the second rotor; and a support cylinder connecting the second rotor with the distal scroll, such that the distal scroll is adapted to rotate about the main axis in synchronization with the second rotor.

Description

Technical Field

[0001] This disclosure relates to the field of compressor technology, and more specifically, to a co-rotating scroll compressor. Background Technology

[0002] Scroll compressors are widely used in the air conditioning industry due to their high volumetric efficiency, low vibration, and low noise. Current improvements to scroll compressors mainly focus on increasing suction capacity and improving volumetric efficiency, often employing a single moving scroll and a single stationary scroll, compressing the medium through the revolution of the moving scroll relative to the stationary scroll. However, this introduces the following problems. First, the revolution of the moving scroll causes it to have eccentric inertia, which leads to collisions between the scroll bodies of the moving and stationary scrolls, reducing their reliability and shortening their lifespan. Second, to overcome the eccentric inertia of the moving scroll, an eccentric block needs to be installed on the eccentric shaft to compensate for the eccentric dynamic mass of the moving scroll. This not only increases the weight of the compressor but also its energy consumption and makes the manufacturing and assembly of the compressor more complex. Third, to suppress the rotation of the moving scroll so that it can only revolve (i.e., revolve translation), an anti-rotation structure is needed, which further increases the weight of the compressor and makes its manufacturing and assembly more complex.

[0003] Therefore, there is an urgent need in this field for a technical solution that can both utilize the advantages of scroll compressors and effectively overcome the shortcomings of existing scroll compressors. Summary of the Invention

[0004] To address the problems in the prior art described above, this disclosure proposes a co-rotating scroll compressor, comprising: a housing; a motor mounted within the housing, the motor including a first rotor and a second rotor configured to rotate in opposite directions about a main axis; a proximal scroll and a distal scroll rotatably disposed within the housing and meshing with each other, wherein the proximal scroll is located between the motor and the distal scroll; a gear pair coupling the first rotor to the proximal scroll such that the proximal scroll is adapted to rotate about a secondary axis offset relative to the main axis, the gear ratio being equal to the speed ratio of the first rotor to the second rotor; and a support cylinder connecting the second rotor to the distal scroll such that the distal scroll is adapted to rotate synchronously with the second rotor about the main axis.

[0005] This disclosure may be embodied in the illustrative embodiments shown in the accompanying drawings. However, it should be noted that the drawings are merely illustrative, and any variations contemplated under the teachings of this disclosure should be considered to be included within the scope of this disclosure. Attached Figure Description

[0006] The accompanying drawings illustrate exemplary embodiments of this disclosure. These drawings should not be construed as necessarily limiting the scope of this disclosure, wherein:

[0007] Figure 1 This is a schematic cross-sectional view of a co-rotating scroll compressor according to one embodiment of the present disclosure;

[0008] Figure 2A-2C Along which are at different rotational positions Figure 1 A schematic cross-sectional view of the near-side and far-side vortex bodies taken from line II-II in the diagram;

[0009] Figure 3 It is along Figure 1 A schematic cross-sectional view of the outer bearing, eccentric block, and inner bearing taken from line III-III in the diagram;

[0010] Figure 4 yes Figure 1 A schematic three-dimensional view of the distal vortex disk in the image; and

[0011] Figure 5 This is a schematic cross-sectional view of a co-rotating scroll compressor according to another embodiment of the present disclosure. Detailed Implementation

[0012] Further features and advantages of this disclosure will become more apparent from the following description with reference to the accompanying drawings. Exemplary embodiments of this disclosure are shown in the drawings, and the drawings are not necessarily drawn to scale. However, this disclosure can be implemented in many different forms and should not be construed as necessarily limited to the exemplary embodiments shown herein. Rather, these exemplary embodiments are provided merely to illustrate this disclosure and to convey the spirit and essence of this disclosure to those skilled in the art.

[0013] This disclosure aims to provide an improved co-rotating scroll compressor. Compared to conventional revolution-type scroll compressors, this co-rotating scroll compressor replaces the revolution of one scroll relative to another in the work process on the medium (e.g., coolants such as R744, R134A, R290, etc.) with the rotation of the two scrolls around two mutually offset axes. This avoids eccentric inertia caused by the revolution of the scrolls, and thus reduces lateral impacts on the scroll bodies caused by eccentric inertia, thereby improving the reliability of the scroll bodies and extending their service life. Furthermore, the co-rotating scroll compressor according to this disclosure does not require an eccentric block to overcome eccentric inertia, thus simplifying the overall structure of the compressor. And because the revolutionary translational motion is replaced by the more stable rotational motion around their respective axes, 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 this disclosure also has many advantages such as reliably ensuring that the two scroll discs rotate in the same direction and at the same speed, and effectively suppressing the axial clearance and radial offset of the two scroll discs.

[0014] The following describes in detail, with reference to the accompanying drawings, various alternative but non-limiting embodiments of the co-rotating scroll compressor according to the present disclosure. It should be noted that, as used herein, in the terminology indicating the relative orientation of the various components, "axial direction" refers to a direction coinciding 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 about the axis of rotation; unless otherwise explicitly stated, these terms indicating relative orientation have their usual meaning in the art.

[0015] refer to Figure 1 A schematic cross-sectional view of a co-rotating scroll compressor according to one embodiment of the present disclosure is shown. Figure 1As shown, the co-rotating scroll compressor 10 includes a housing 100 and a motor 200 mounted within the housing 100. The motor 200 includes 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 couple with a rotating magnetic field generated by the stator 230, thereby rotating about a main axis MA. Specifically, the motor 200 may be a permanent magnet synchronous motor, wherein the stator 230 includes a stator core 231 fixedly disposed within the housing 100 and stator windings 232 attached to the stator core 231, the stator windings 232 being adapted to generate a rotating magnetic field rotating about the main axis MA when an alternating current is applied; the first rotor 210 includes 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 being circumferentially oriented... The rotor core 211 is distributed and adapted to couple with the rotating magnetic field, thereby driving the rotor core 211 to rotate around the main axis MA under the drive of the rotating magnetic field. Similar to the first rotor 210, the second rotor 220 also includes 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 circumferentially and adapted to couple with the rotating magnetic field, thereby driving the rotor core 221 to rotate around the main axis MA under the drive of the rotating magnetic field. In this way, electrical energy is converted into the kinetic energy of the two rotors, and as mentioned above, by adjusting the alternating current supplied to the stator winding 232, the rotating magnetic field generated by the stator winding 232 can be adjusted, thereby adjusting the speed and / or direction of each rotor. Therefore, the motor 200 may also include control devices such as an inverter (not shown), which, for example, can adjust the alternating current supplied to the stator winding 232 via pulse width modulation, thereby independently controlling the speed and / or direction of the first rotor 210 and the second rotor 220. It should be noted that although the specific configuration of the motor 200 has been described above using a permanent magnet synchronous motor as an example, those skilled in the art will understand that the motor 200 can also be other types of motors such as asynchronous motors; therefore, the specific type of the motor 200 does not constitute a limitation on the scope of this disclosure.

[0016] Continue to refer to Figure 1 The co-rotating scroll compressor 10 also includes two scrolls rotatably disposed within the housing 100 and spaced axially from the motor 200, namely, a proximal scroll 300 closer to the motor 200 and a distal scroll 400 farther from the motor 200. In other words, the proximal scroll 300 is located axially between the motor 200 and the distal scroll 400. Figure 1As shown, the proximal scroll 300 is coupled to the first rotor 210 via a gear pair 500, which includes a driving gear 510 and a driven gear 520 meshing with each other. The driving gear 510 is oriented along the main axis MA and coupled to the first rotor 210 so that it can rotate synchronously with the first rotor 210 (i.e., at the same speed and in the same direction) around the main axis MA. The driven gear 520 is oriented along a secondary axis SA parallel to and offset relative to the main axis MA and coupled to the proximal scroll 300 so that it can rotate synchronously with the proximal scroll 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 300 at a certain transmission ratio, but also ensures that the direction of rotation of the proximal scroll 300 is opposite to that of the first rotor 210. Figure 1 As shown, the scroll compressor 10 also includes a support cylinder 600 that couples the distal scroll 400 to the second rotor 220. The support cylinder 600 is connected to the distal scroll 400 at one end and to the second rotor 220 at the other end, so that the distal scroll 400 can rotate synchronously with the second rotor 220 around the main axis MA.

[0017] Furthermore, by configuring the first rotor 210 and the second rotor 220 such that the direction of rotation of the first rotor 210 is opposite to that 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 transmission ratio of the gear pair 500 (i.e., the ratio of the rotational speed of the driving gear 510 to the rotational speed of the driven gear 520), for example, the rotational speed of the first rotor 210 is the same as that of the second rotor 220 and the transmission ratio of the gear pair 500 is 1, the proximal scroll 300 and the distal scroll 400 can rotate around the secondary axis SA and the main axis MA respectively with the same direction of rotation and the same rotational speed, thereby moving and compressing the medium between the proximal scroll 300 and the distal scroll 400 toward their center. Specifically, as Figure 1As shown, the proximal vortex disk 300 includes a proximal vortex body 310 projecting along the axial direction. This proximal vortex body 310 is spiral or vortex-shaped when viewed along the axial direction and extends from the outer periphery or periphery of the proximal vortex disk 300 towards its center along the vortex direction. The distal vortex disk 400 includes a distal vortex body 410 projecting along the axial direction. This distal vortex body 410 is also spiral or vortex-shaped when viewed along the axial direction and extends from the outer periphery or periphery of the distal vortex disk 400 towards its center along the vortex direction. Furthermore, the proximal vortex 300 and the distal vortex 400 are positioned such that the side surfaces of the proximal vortex 310 and the distal vortex 410 engage with each other, thereby cooperating or meshing the proximal vortex 310 and the distal vortex 410 to define a plurality of compression chambers between the two vortices, as described in more detail below. These compression chambers are arranged along the vortex direction and isolated from each other, and the volume of the compression chambers closer to the center of the two vortices is smaller. As the proximal vortex 300 rotates about the secondary axis SA and the distal vortex 400 rotates about the main axis MA at the same speed and direction, each compression chamber moves along the vortex direction toward the center of the two vortices while its volume gradually decreases. This causes the medium in each compression chamber to be pushed toward the center of the two vortices and gradually compressed, resulting in a gradual increase in the pressure of the medium, which reaches its maximum when the medium moves to the center of the two vortices, thus realizing the compression process of the medium. Of course, in Figure 1 In the embodiment shown, in order to discharge the compressed medium at the center of the two vortex bodies, the distal vortex disk 400 is also provided with an exhaust port 401, which extends through the distal vortex disk 400 and leads to the center of the distal vortex body 410, thereby allowing the compressed medium at the center of the two vortex bodies to be discharged through the exhaust port 401.

[0018] To make the compression process more intuitive, the following explanation refers to cross-sectional views of the near-side vortex 310 and the far-side vortex 410. Figure 2A-2C The figure shows the traverse along at different rotational positions. Figure 1 A schematic cross-sectional view of the near-side vortex 310 and the far-side vortex 410, taken from line II-II. (See diagram below.) Figure 2A-2C As shown, the proximal vortex 310 and the distal vortex 410 define two sets of compression chambers arranged symmetrically about the center of the two vortices. Each set of compression chambers includes a first compression chamber C1, a second compression chamber C2, and a third compression chamber C3 arranged from the outside to the inside along the vortex direction and isolated from each other. When the two vortices are in... Figure 2AIn the first position shown, the first compression chamber C1 is open to allow the medium to be compressed to enter, while the second and third compression chambers C2 and C3, which already contain the medium, are closed. When the two vortex bodies move from... Figure 2A The first position shown is reached through their respective rotations. Figure 2B In the second position shown, the first compression chamber C1 moves toward the center of the two vortexes and begins to close; the second compression chamber C2 moves toward the center of the two vortexes and its volume decreases; the third compression chamber C3 reaches the center of the two vortexes and its volume decreases, so that the medium in each compression chamber is pushed toward the center of the two vortexes and compressed. When the two vortexes further move from... Figure 2B The second position shown is reached through their respective rotations. Figure 2C In the third position shown, the first compression chamber C1 moves further toward the center of the two vortexes and closes completely; the second compression chamber C2 moves further toward the center of the two vortexes and its volume decreases further; the third compression chamber C3 remains at the center of the two vortexes and its volume decreases further, so that the medium in each compression chamber is further pushed toward the center of the two vortexes and further compressed. When the two vortexes further move from... Figure 2C The third position shown returns to its original position through its respective rotation. Figure 2A In the first position shown, the third compression chamber C3 disappears, thereby discharging the compressed medium. The second compression chamber C2 becomes the new third compression chamber C3, the first compression chamber C1 becomes the new second compression chamber C2, and a new first compression chamber C1 is generated, thus ending the previous compression process and starting a new one. As the two scrolls rotate, the above compression process is repeated so that the two scrolls can continuously draw in, move, compress, and discharge the medium.

[0019] In the above configuration, the compression process is achieved by two scrolls rotating around two mutually offset axes at the same speed and in the same direction, rather than by the revolution (also known as translation) of either scroll. Therefore, neither scroll will generate eccentric inertia due to revolution, which avoids the two scrolls colliding with each other due to eccentric inertia. This extends the service life of the scrolls and improves their reliability. Furthermore, there is no need to set up eccentric blocks to overcome eccentric inertia, nor is there a need to set up anti-rotation structures to suppress the rotation of the scrolls. This simplifies the overall structure of the compressor and improves its reliability. Moreover, since the revolution motion is replaced by the more stable rotation motion, the dynamic performance of the compressor is also significantly improved.

[0020] According to one alternative embodiment of this disclosure, such as Figure 1As shown, since the proximal scroll 300 is located between the motor 200 and the distal scroll 400, the support cylinder 600 is configured to transmit the rotational motion of the second rotor 220 to the distal scroll 400 across the proximal scroll 300. This causes the proximal scroll 300 to be located radially inside the support cylinder 600, such that the support cylinder 600 surrounds the proximal scroll 300 radially outside the proximal scroll 300. Figure 1 As shown, the co-rotating scroll compressor 10 also includes an outer bearing 710, an eccentric block 720, and an inner bearing 730 disposed within a support cylinder 600. 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 300. 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 300 to rotate relative to the eccentric block 720 around the secondary axis SA. In other words, the outer bearing 710 and the inner bearing 730 are eccentrically nested together via the eccentric block 720. Specifically, refer to... Figure 3 , which shows along Figure 1The schematic cross-sectional view of the outer bearing, eccentric block, and inner bearing taken from line III-III shows that 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 disk-shaped and has an eccentric hole 721 that is eccentric to its outer circumference. 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 near-side scroll 300. In this configuration, during operation, the support cylinder 600 can rotate relative to and support the eccentric block 720 due to the presence of the outer bearing 710, while the eccentric block 720 allows the proximal scroll 300 to rotate and supports it due to the presence of the inner bearing 730. Furthermore, 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 eccentrically, thereby achieving reliable positioning of the proximal scroll 300. Specifically, the co-rotating scroll compressor 10 also includes a distal bearing 740 mounted within the housing 100, which is arranged around the main axis MA and supports the distal scroll 400 to allow it 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 400, so that the housing 100 can support the distal scroll 400 and allow the distal scroll 400 to rotate, thereby achieving reliable positioning of the distal scroll 400.

[0021] According to one alternative embodiment of this disclosure, such as Figure 1As shown, the housing 100 includes a housing body 110 defining an internal cavity and a partition plate 120 disposed within the housing body 110. The partition plate 120 divides the internal cavity into an intake chamber 111 for receiving a medium to be compressed and an exhaust chamber 112 for receiving a compressed medium. Specifically, the housing body 110 also has 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 a medium to be compressed from the outside can be supplied to the intake chamber 111 through the inlet 113, and a compressed medium in the exhaust chamber 112 can be supplied to the outside through the outlet 114. Specifically, 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 300, and the distal scroll 400, are housed in the intake chamber 111 to compress the medium in the intake chamber 111 and then discharge it into the exhaust chamber 112. For this purpose, the isolation plate 120 is provided with a through-hole 121 extending through the isolation plate 120. The distal scroll 400 includes a strut 402 projecting axially and oriented along the main axis MA, that is, the strut 402 is oriented such that its axis coincides with the main axis MA, and an exhaust port 401 extends through the strut 402. Figure 1 As shown, the support column 402 is inserted into the through-hole 121 of the partition plate 120, so that the exhaust port 401 is in fluid communication with the exhaust chamber 112, thereby allowing the compressed medium to be discharged from the center of the two scrolls through the exhaust port 401 into the exhaust chamber 112. Specifically, the co-rotating scroll compressor 10 also includes a sealing ring 801 disposed in the through-hole 121 of the partition plate 120, which surrounds the support column 402 of the distal scroll 400 and is clamped or pressed between the support column 402 and the sidewall of the through-hole 121. In this configuration, the sealing ring 801 can provide a seal between the support column 402 and the sidewall of the through-hole 121, thereby preventing the compressed medium in the exhaust chamber 112 from leaking into the intake chamber 111 through the gap between the support column 402 and the sidewall of the through-hole 121, thus helping to maintain the volumetric efficiency of the co-rotating scroll compressor 10. Alternatively, the sealing ring 801 may be made of a wear-resistant elastomer material such as nitrile rubber or polyurethane rubber, thereby providing sealing performance while resisting wear caused by the rotation of the support 402.

[0022] According to one alternative embodiment of this disclosure, such as Figure 1 As shown, the proximal vortex disk 300 also includes a generally disk-shaped proximal disk body 320 oriented transversely to the secondary axis SA, wherein the proximal vortex body 310 protrudes from the proximal disk body 320 along the axial direction. Additionally, refer to... Figure 4 , which shows Figure 1A schematic perspective view of the distal vortex disk 400, which further includes a generally disk-shaped distal disk body 420 oriented transversely to the principal axis MA, and a generally cylindrical distal annular body 430 protruding axially from the distal disk body 420 and extending circumferentially. A distal vortex body 410 also protrudes axially from the distal disk body 420 but is located radially inside the distal annular body 430, such that the distal annular body 430 surrounds the distal vortex body 410 radially outside the distal vortex body 410. Figure 1 As shown, the distal scroll 410 abuts against the proximal scroll 320, while the proximal scroll 310 abuts against the distal scroll 420, thereby eliminating the axial clearance between the distal scroll 400 and the proximal scroll 300 that could lead to axial leakage of the medium in each compression chamber, thus ensuring the volumetric efficiency of the compressor. Specifically, the distal annulus 430 defines a contact area CA on its outer periphery 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 confined to the outer periphery or periphery of the distal annulus 430, rather than to the outer periphery or periphery of the distal disc 420, the axial height H1 of the contact area CA is not limited by the thickness of the distal disc 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 400, and in turn, reliably maintain the radial position of the proximal scroll 300 through the distal scroll 400. This reduces the overturning of the distal scroll 410 and the proximal scroll 310, thereby reducing tangential leakage of the medium and ensuring the volumetric efficiency of the compressor. More specifically, the axial height H2 of the meshing area EA of the near-side vortex 310 and the far-side vortex 410 is within the axial height H1 of the contact area CA. In other words, the axial height H1 of the contact area CA is greater than and crosses the axial height H2 of the meshing area EA, thereby enabling the support cylinder 600 to more reliably maintain the radial position of the near-side vortex 300 and the far-side vortex 400.

[0023] According to one alternative embodiment of this disclosure, such as Figure 1As shown, the motor 200 also includes a main shaft 240, which is fixed to the housing 100 (more specifically, the housing body 110) and oriented along the main axis MA, that is, the main shaft 240 is oriented such that its axis coincides with the main axis MA. Furthermore, the stator 230 is fixed to the main shaft 240, that is, the stator 230 is fixedly supported on the main shaft 240, while the first rotor 210 is supported by a first bearing 251 mounted on the main shaft 240, so that the first rotor 210 is rotatably supported on the main shaft 240, and the second rotor 220 is supported by a second bearing 252 mounted on the main shaft 240, so that the second rotor 220 is rotatably supported on the main shaft 240. Furthermore, the first rotor 210 and the second rotor 220 are spaced apart from each other along the axial direction and located on opposite sides of the stator 230. Not only is the first rotor 210 located radially inside the support cylinder 600, but the stator 230 is also located radially inside the support cylinder 600, such that the support cylinder 600 surrounds the stator 230 radially outside the stator 230. In this configuration, the first rotor 210 and the second rotor 220 are coupled to the magnetic flux flowing axially generated by the stator 230 and are capable of rotating relative to the main shaft 240 under the drive of the rotating magnetic field. Therefore, in Figure 1 In the illustrated embodiment, the motor 200 is configured as an axial flux motor. Since axial flux motors have advantages such as small size and high power density, this configuration helps to improve the efficiency of the scroll compressor 10 while reducing its size. Furthermore, the driving gear 510 in the gear pair 500 is connected to the first rotor 210, while the driven gear 520 is connected to the proximal scroll 300. During operation, the first rotor 210 and the second rotor 220 rotate relative to the main shaft 240, respectively. The first rotor 210 drives the proximal scroll 300 to rotate around the secondary axis SA via the gear pair 500, while the second rotor 220 drives the distal scroll 400 to rotate around the main axis MA via the support cylinder 600, thereby completing the compression process described above.

[0024] It should be pointed out that, although in Figure 1 In the illustrated embodiment, motor 200 is configured as an axial flux motor, but this is merely exemplary, and motor 200 can also be configured as other types of motors. For example, refer to... Figure 5 A schematic cross-sectional view of a co-rotating scroll compressor according to another embodiment of the present disclosure is shown, due to Figure 5 The embodiments shown are the same as Figure 1 The implementation methods shown are largely the same, therefore the following text only addresses... Figure 5 The embodiments shown are the same as Figure 1 The differences between the illustrated embodiments will be described, while the similarities will not be repeated for the sake of brevity. For example... Figure 5As shown, 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 located radially inside the stator 230, and the first rotor 210 is located radially inside the second rotor 220. That is, the first rotor 210 is nested radially inside the second rotor 220, such that the second rotor 220 surrounds the first rotor 210 radially outside the first rotor 210. In addition, the first rotor 210 is also fixed to the main shaft 240, which is supported by a main bearing 254 mounted on the housing 100 (more specifically, the housing body 110), so that the main shaft 240 is rotatably disposed in the housing 100, and the second rotor 220 is supported by two second bearings 252 mounted on the main shaft 240 and spaced apart in the axial direction, so that the second rotor 220 is rotatably supported on the main shaft 240. Specifically, two second bearings 252 are located on opposite axial sides of the first rotor 210. In this configuration, the first rotor 210 and the second rotor 220 are coupled with a radially flowing magnetic flux generated by the stator 230, so that under the drive of the rotating magnetic field, the first rotor 210 rotates synchronously with the main shaft 240, while the second rotor 220 rotates relative to the main shaft 240. Therefore, in Figure 5 In the illustrated embodiment, the motor 200 is configured as a radial flux motor. Radial flux motors offer numerous advantages, including mature technology and low manufacturing costs, thus this configuration helps reduce the manufacturing cost of the scroll compressor 10. Furthermore, the driving gear 510 in the gear pair 500 is connected to the main shaft 240, while the driven gear 520 is connected to the proximal scroll 300. During operation, the main shaft 240 rotates synchronously with the first rotor 210 and drives the proximal scroll 300 to rotate around the secondary axis SA via the gear pair 500. The second rotor 220 rotates relative to the main shaft 240 and drives the distal scroll 400 to rotate around the main axis MA via the support cylinder 600, thereby completing the compression process described above.

[0025] The foregoing has described in detail, with reference to the accompanying drawings, optional but non-limiting embodiments of the co-rotating scroll compressor according to this disclosure. Modifications and additions to the technology and structure, as well as recombinations of features in the various embodiments, will be readily apparent to those skilled in the art without departing from the spirit and essence of this disclosure and should be considered within its scope. Therefore, such modifications and additions conceivable under the teachings of this disclosure should be considered part of this disclosure. The scope of this disclosure includes equivalent technologies known at the filing date of this disclosure and equivalent technologies not yet foreseen.

Claims

1. A co-rotating scroll compressor, comprising: Casing (100); A motor (200) is installed within the housing (100), the motor (200) comprising a first rotor (210) and a second rotor (220) configured to rotate about a main axis (MA) in opposite directions; A proximal volute (300) and a distal volute (400) are rotatably disposed within the housing (100) and mesh with each other, wherein the proximal volute (300) is located between the motor (200) and the distal volute (400); A gear pair (500) couples the first rotor (210) to the proximal volute (300) such that the proximal volute (300) is adapted to rotate about a secondary axis (SA) offset relative to the main axis (MA), the gear pair (500) having a transmission ratio equal to the speed ratio of the first rotor (210) to the second rotor (220); and A support cylinder (600) is used to connect the second rotor (220) to the distal vortex disk (400) so that the distal vortex disk (400) is adapted to rotate synchronously with the second rotor (200) around the main axis (MA).

2. The co-rotating scroll compressor according to claim 1 further includes an outer bearing (710) installed in the support cylinder (600), an eccentric block (720) supported by the outer bearing (710), and an inner bearing (730) installed in the eccentric block (720), wherein, The proximal scroll (300) is located inside the support cylinder (600) and is supported by the inner bearing (730).

3. The co-rotating scroll compressor according to claim 1 or 2, wherein, The housing (100) includes a housing body (110) defining an internal cavity and an isolation plate (120) disposed within the housing body (110), wherein the isolation plate (120) divides the internal cavity into an intake chamber (111) and an exhaust chamber (112), and the distal scroll plate (400) is supported by a distal bearing (740) mounted on the isolation plate (120).

4. The co-rotating scroll compressor according to claim 3, wherein, The distal vortex (400) includes an axially projecting strut (402) and an exhaust port (401) extending through the strut (402), wherein the partition plate (120) has a through hole (121) for insertion of the strut (402) so that the exhaust port (401) communicates with the exhaust chamber (112).

5. The co-rotating scroll compressor according to claim 4 further includes a sealing ring (801) disposed in the through hole (121), wherein, The sealing ring (801) surrounds the support (402) and is held between the support (402) and the sidewall of the through hole (121).

6. The co-rotating scroll compressor according to claim 3, wherein, The housing body (110) is provided with an inlet (113) communicating with the air intake chamber (111) and an outlet (114) communicating with the exhaust chamber (112).

7. The co-rotating scroll compressor according to claim 3, wherein, The motor (200), the near-side scroll (300), and the far-side scroll (400) are located within the intake chamber (111).

8. The co-rotating scroll compressor according to any one of claims 1-3, wherein, The proximal vortex disk (300) includes a proximal disk body (320) and a proximal vortex body (310) protruding axially from the proximal disk body (320), and the distal vortex disk (400) includes a distal disk body (420) and a distal vortex body (410) protruding axially from the distal disk body (420), wherein the proximal vortex body (310) meshes with the distal vortex body (410).

9. The co-rotating scroll compressor according to claim 8, wherein, The distal vortex (400) further includes a distal annulus (430) projecting axially from the distal disk body (420), wherein the distal annulus (430) surrounds the distal vortex body (410) and defines a contact area (CA) for connection with the support cylinder (600) on its outer periphery, the contact area (CA) extending circumferentially and having a non-zero axial height (H1).

10. The co-rotating scroll compressor according to claim 9, wherein, The contact area (CA) extends circumferentially through the entire circumference.

11. The co-rotating scroll compressor according to claim 9, wherein, The axial height (H1) of the contact area (CA) is greater than and spans the axial height of the meshing area (EA) between the proximal vortex (310) and the distal vortex (410).

12. The co-rotating scroll compressor according to claim 8, wherein, The proximal vortex (310) abuts against the distal disk (420), and the distal vortex (410) abuts against the proximal disk (320).

13. The co-rotating scroll compressor according to any one of claims 1-3, wherein, The motor (200) also includes a main shaft (240) fixed on the housing (100) and a stator (230) fixed on the main shaft (240), wherein the first rotor (210) and the second rotor (220) are located on opposite axial sides of the stator (230) and are respectively supported by bearings mounted on the main shaft (240).

14. The co-rotating scroll compressor according to claim 13, wherein, The gear pair (500) includes a driving gear (510) connected to the first rotor (210) and a driven gear (520) meshing with the driving gear (510) and connected to the proximal vortex (300).

15. The co-rotating scroll compressor according to any one of claims 1-3, wherein, The motor also includes a stator (230) fixed to the housing (100) and a main shaft (240) supported by bearings mounted on the housing (100), wherein the second rotor (220) is located radially inside the stator (230) and supported by bearings mounted on the main shaft (240), and the first rotor (210) is located radially inside the second rotor (220) and fixed to the main shaft (240).

16. The co-rotating scroll compressor according to claim 15, wherein, The second rotor (220) is supported by two bearings mounted on the main shaft (240) and located on both sides of the first rotor (210) in the axial direction.

17. The co-rotating scroll compressor according to claim 15, wherein, The gear pair (500) includes a drive gear (510) connected to the main shaft (240) and a driven gear (520) meshing with the drive gear (510) and connected to the proximal scroll (300).

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