Co-rotating scroll compressor

Abstract

The present disclosure proposes a co-rotation scroll compressor including a housing, and a first scroll plate, a second scroll plate and a transmission shaft rotatably disposed within the housing, the first scroll plate being configured to rotate about a first rotation axis and including a first scroll body protruding in an axial direction and a first gear ring arranged in a circumferential direction; a second scroll plate configured to rotate about a second rotation axis and including a second scroll body protruding in an axial direction and a second gear ring arranged in a circumferential direction, the second scroll body meshing with the first scroll body, and the second rotation axis and the first rotation axis being parallel to each other and offset from each other; and the transmission shaft is provided with a first gear and a second gear which are fixed on the transmission shaft and are coaxial, the first gear is meshed with the first gear ring, the second gear is meshed with the second gear ring, and the tooth number ratio of the first gear ring to the first gear is equal to the tooth number ratio of the second gear ring to the second gear.

Description

Technical Field

[0001] The present disclosure relates to the technical field of compressors, and more particularly, to a co-rotating scroll compressor. Background Art

[0002] Scroll compressors are widely used in the air-conditioning field due to many advantages such as high volumetric efficiency, low vibration, and low noise. The improvements of existing scroll compressors mainly focus on increasing the suction volume and improving the volumetric efficiency, and usually adopt a single moving scroll disk and a single stationary scroll disk, and compress the medium through the revolution of the moving scroll disk relative to the stationary scroll disk. However, the following problems are brought about. First, the revolution of the moving scroll disk causes eccentric inertia of the moving scroll disk, and the eccentric inertia causes the scroll body of the moving scroll disk to collide with the scroll body of the stationary scroll disk, thereby reducing the reliability of the scroll body and shortening its service life; Second, in order to overcome the eccentric inertia of the moving scroll disk, an eccentric block needs to be provided on the eccentric shaft to compensate for the eccentric dynamic mass of the moving scroll, which not only increases the weight of the compressor, but also increases the energy consumption of the compressor, and makes the manufacturing and assembly of the compressor more complicated; Third, in order to suppress the self-rotation of the moving scroll disk so that the moving scroll disk can only revolve, that is, revolve and translate, an anti-self-rotation structure needs to be provided, which further increases the weight of the compressor and makes the manufacturing and assembly of the compressor more complicated.

[0003] Therefore, there is an urgent need in the art for a technical solution that can utilize the advantages of a scroll compressor and effectively overcome the disadvantages of existing scroll compressors. Summary of the Utility Model

[0004] To solve the above problems in the prior art, the present disclosure provides a co-rotating scroll compressor, which includes a housing and a first scroll disk, a second scroll disk, and a transmission shaft rotatably disposed in the housing. The first scroll disk is configured to rotate about a first rotation axis and includes a first scroll body protruding axially and a first tooth ring arranged circumferentially; the second scroll disk is configured to rotate about a second rotation axis and includes a second scroll body protruding axially and a second tooth ring arranged circumferentially, the second scroll body meshes with the first scroll body, and the second rotation axis is parallel to and offset from the first rotation axis; and the transmission shaft is provided with a first gear and a second gear fixed thereon and coaxial, the first gear meshes with the first tooth ring, the second gear meshes with the second tooth ring, and the tooth number ratio of the first tooth ring to the first gear is equal to the tooth number ratio of the second tooth ring to the second gear.

[0005] According to an alternative embodiment of the present disclosure, the co-rotating scroll compressor further includes a motor disposed within the housing, and a main shaft of the motor is coupled to the drive shaft to drive the drive shaft to rotate.

[0006] According to an alternative embodiment of the present disclosure, the co-rotating scroll compressor further includes a motor disposed within the housing, and a main shaft of the motor is coupled to the second scroll disk to drive the second scroll disk to rotate.

[0007] According to an alternative embodiment of the present disclosure, the first scroll disk is provided with a through hole that leads to the center of the first scroll body.

[0008] According to an alternative embodiment of the present disclosure, the first scroll disk further includes a first disk body and a first ring body protruding axially from the first disk body. The first scroll body protrudes axially from the first disk body and is located radially inside the first ring body, and the first gear ring is disposed on the outer periphery of the first ring body.

[0009] According to an alternative embodiment of the present disclosure, the second scroll body abuts against the first disk body.

[0010] According to an alternative embodiment of the present disclosure, the meshing position of the first gear and the first gear ring is radially aligned with the meshing position of the first scroll body and the second scroll body.

[0011] According to an alternative embodiment of the present disclosure, the first scroll disk further includes a first disk body, the first scroll body protrudes axially from the first disk body, and the first gear ring is disposed on the outer periphery of the first disk body.

[0012] According to an alternative embodiment of the present disclosure, the second scroll body abuts against the first disk body.

[0013] According to an alternative embodiment of the present disclosure, the second scroll disk further includes a second disk body, the second scroll body protrudes axially from the second disk body, and the second gear ring is disposed on the outer periphery of the second disk body.

[0014] According to an alternative embodiment of the present disclosure, the first scroll body abuts against the second disk body.

[0015] According to an alternative embodiment of the present disclosure, the co-rotating scroll compressor includes a plurality of drive shafts that are evenly distributed circumferentially.

[0016] According to an alternative embodiment of the present disclosure, the first gear is a spur gear.

[0017] According to an alternative embodiment of the present disclosure, the first scroll disk is configured to rotate in a predetermined direction, and the first gear is a helical gear such that when the first scroll disk rotates in the predetermined direction, the force exerted by the first gear on the first gear ring has a component towards the second scroll disk.

[0018] According to an alternative embodiment of the present disclosure, the second gear is a spur gear.

[0019] According to an alternative embodiment of the present disclosure, the second scroll disk is configured to rotate in a predetermined direction, and the second gear is a helical gear such that when the second scroll disk rotates in the predetermined direction, the force exerted by the second gear on the second gear ring has a component towards the first scroll disk.

[0020] According to an alternative embodiment of the present disclosure, the transmission shaft is configured to rotate about a third axis of rotation, and the first axis of rotation, the second axis of rotation, and the third axis of rotation intersect a same radially oriented line, and the first axis of rotation is located between the second axis of rotation and the third axis of rotation.

[0021] The present disclosure may be embodied in the schematic embodiments in the drawings. However, it should be noted that the drawings are merely schematic, and any variations contemplated under the teachings of the present disclosure should be considered to be included within the scope of the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The drawings illustrate exemplary embodiments of the present disclosure. These drawings should not be construed as necessarily limiting the scope of the present disclosure, wherein:

[0023] Figure 1 is a schematic cross-sectional view of a co-rotating scroll compressor according to an embodiment of the present disclosure;

[0024] Figure 2 is Figure 1 a schematic cross-sectional view of a first scroll body and a second scroll body of the co-rotating scroll compressor shown in a first position;

[0025] Figure 3 is Figure 1 a schematic cross-sectional view of a first scroll body and a second scroll body of the co-rotating scroll compressor shown in a second position;

[0026] Figure 4 is Figure 1 a schematic cross-sectional view of a first scroll body and a second scroll body of the co-rotating scroll compressor shown in a third position;

[0027] Figure 5Schematic cross-sectional view of a co-rotating scroll compressor according to another embodiment of the present disclosure;

[0028] Figure 6 Schematic cross-sectional view of a co-rotating scroll compressor according to yet another embodiment of the present disclosure; and

[0029] Figure 7 Schematic perspective view of the first scroll disk of a co-rotating scroll compressor according to still another embodiment of the present disclosure. Detailed Embodiments

[0030] Further features and advantages of the present disclosure will become more apparent from the following description with reference to the accompanying drawings. Exemplary embodiments of the present disclosure are shown in the drawings, and the various drawings are not necessarily drawn to actual scale. However, the present disclosure can be implemented in many different forms and should not be construed as necessarily limited to the exemplary embodiments disclosed herein. Instead, these exemplary embodiments are provided only to illustrate the present disclosure and to convey the spirit and essence of the present disclosure to those skilled in the art.

[0031] The present disclosure aims to provide an improved co-rotating scroll compressor. Compared with traditional orbiting scroll compressors, in this co-rotating scroll compressor, the work process on the medium (e.g., coolants such as R744, R134A, R290, etc.) is replaced from the revolution of one scroll disk relative to another scroll disk to the rotation of two scroll disks around their respective rotation axes. Thereby, the eccentric inertia caused by the revolution of the scroll disks can be avoided, and thus the lateral impact of the scroll bodies of the two scroll disks caused by the eccentric inertia can be reduced, 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 require an eccentric block to overcome the eccentric inertia, thereby simplifying the overall structure of the compressor. And since the orbiting translation is replaced by the rotation 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 above advantages, in some specific embodiments, the co-rotating scroll compressor according to the present disclosure can also have many advantages such as reliably ensuring the same-direction and same-speed rotation of the two scroll disks, effectively suppressing the axial clearance and radial offset of the two scroll disks.

[0032] The following describes in detail various optional but non-limiting embodiments of the co-rotating scroll compressor according to the present disclosure with reference to the respective drawings. It should be noted that in the terms used herein to indicate the relative orientation of the various components, "axial" refers to the direction coinciding with or parallel to the rotation axis, "radial" refers to the direction perpendicular to the rotation axis, and "circumferential" refers to the direction around the rotation axis. Unless otherwise clearly stated, these terms indicating relative orientation have their usual meanings in the art.

[0033] Reference Figure 1 , which shows a schematic cross-sectional view of a co-rotating scroll compressor according to an embodiment of the present disclosure. As Figure 1 shown, the co-rotating scroll compressor 10 includes a housing 110 and a first scroll disk 210 and a second scroll disk 220 rotatably disposed in the housing 110. Specifically, the first scroll disk 210 is configured to rotate about a first rotational axis RA1 and includes a first scroll body 211 protruding in the axial direction and a first gear ring 212 disposed around the first rotational axis RA1. Wherein, the first scroll body 211 has a spiral or scroll shape when viewed in the axial direction and extends from the outer periphery or perimeter of the first scroll disk 210 towards the center along the scroll direction, and the first gear ring 212 may be disposed on the outer periphery or perimeter of the first scroll disk 210, and in particular, the first rotational axis RA1 may be defined by a first scroll disk bearing 310 fixed within the housing 110 and for rotatably supporting the first scroll disk 210. The second scroll disk 220 is configured to rotate about a second rotational axis RA2 and includes a second scroll body 221 protruding in the axial direction and a second gear ring 222 disposed around the second rotational axis RA2. Wherein, the second scroll body 221 also has a spiral or scroll shape when viewed in the axial direction and extends from the outer periphery or perimeter of the second scroll disk 220 towards its center along the scroll direction, and the second gear ring 222 may be disposed on the outer periphery or perimeter of the second scroll disk 220, and the second rotational axis RA2 is parallel to the first rotational axis RA1 and offset relative to each other. In particular, the second rotational axis RA2 may be defined by a second scroll disk bearing 320 fixed within the housing 110 and for rotatably supporting the second scroll disk 220. Additionally, as Figure 1 shown, the first scroll disk 210 and the second scroll disk 220 are positioned such that the side surface of the first scroll body 211 engages with the side surface of the second scroll body 221 so that the first scroll body 211 and the second scroll body 221 cooperate or mesh with each other to define 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 the volume of each compression chamber decreases as it approaches the center of the two scroll bodies.

[0034] Continue to refer to Figure 1, the co-rotating scroll compressor 10 further includes a drive shaft 400 which is rotatably disposed in the housing 110 and is provided with a first gear 410 and a second gear 420. Among them, the first gear 410 and the second gear 420 are coaxially arranged and are both fixed on the drive shaft 400, so that the drive shaft 400, the first gear 410 and the second gear 420 are configured to rotate around the third rotation axis RA3 at the same rotational speed and in the same direction. Among them, the third rotation axis RA3 is parallel to and offset from each of the first rotation axis RA1 and the second rotation axis RA2. In particular, the third rotation axis RA3 can be defined by two drive shaft bearings 340 fixed in the housing 110 and used for rotatably supporting the drive shaft 400, and these two drive shaft bearings 340 are located at both ends of the drive shaft 400. In addition, as Figure 1 shown, the first gear 410 meshes with the first tooth ring 212 of the first scroll disk 210, the second gear 420 meshes with the second tooth ring 222 of the second scroll disk 220, and the tooth number ratio of the first tooth ring 212 to the first gear 410 (i.e., the number of teeth of the first tooth ring 212 / the number of teeth of the first gear 410) is equal to the tooth number ratio of the second tooth ring 222 to the second gear 420 (i.e., the number of teeth of the second tooth ring 222 / the number of teeth of the second gear 420). In this configuration, the drive shaft 400 can ensure that the first scroll disk 210 and the second scroll disk 220 rotate around their respective rotation axes at the same rotational speed and in the same direction through the first gear 410 and the second gear 420, so that each compression chamber defined between the first scroll body 211 and the second scroll body 221 can move towards the centers of the two scroll bodies as the two scroll disks rotate and the chamber volume gradually becomes smaller, thereby completing the compression process of the medium, as described in more detail below.

[0035] As the first scroll disk 210 rotates around the first rotation axis RA1 and the second scroll disk 220 rotates around the second rotation axis RA2 at the same rotational speed and in the same direction, each compression chamber will move along the scroll direction towards the centers of the two scroll bodies while its volume gradually decreases, and this causes the medium in each compression chamber to be pushed towards the centers of the two scroll bodies while being gradually compressed, resulting in a gradual increase in the pressure of the medium and reaching the maximum when the medium moves to the centers of the two scroll bodies, thereby realizing the compression process of the medium. Of course, in Figure 1 the illustrated embodiment, in order to discharge the compressed medium at the centers of the two scroll bodies, the first scroll disk 210 is provided with a through hole H1 which extends through the first scroll disk 210 and leads to the center of the first scroll body 211, whereby the medium at the centers of the two scroll bodies can be discharged through the through hole H1.

[0036] To make the above compression process more intuitive, the following description is made with reference to the cross-sectional views of the first scroll 211 and the second scroll 221. Refer to Figures 2-4 , which shows schematic cross-sectional views of the first scroll 211 and the second scroll 221 at different rotational positions. As Figures 2-4 shown, the first scroll 211 and the second scroll 221 define two sets of compression chambers symmetrically arranged about the centers of the two scrolls between each other. Among them, each set of compression chambers includes a first compression chamber 231, a second compression chamber 232, and a third compression chamber 233 that are arranged from the outside to the inside along the scroll direction and are isolated from each other. When the two scrolls are in Figure 2 the first position shown, the first compression chamber 231 is open to allow the medium to be compressed to enter the first compression chamber 231, while the second compression chamber 232 and the third compression chamber 233 that already contain the medium are closed. When the two scrolls move from Figure 2 the first position shown reach Figure 3 the second position shown through their respective rotations, the first compression chamber 231 moves towards the centers of the two scrolls and begins to close, the second compression chamber 232 moves towards the centers of the two scrolls and its volume decreases, and the third compression chamber 233 reaches the centers of the two scrolls and its volume decreases, so that the medium in each compression chamber is pushed towards the centers of the two scrolls and is compressed. When the two scrolls further move from Figure 3 the second position shown reach Figure 4 the third position shown through their respective rotations, the first compression chamber 231 further moves towards the centers of the two scrolls and is completely closed, the second compression chamber 232 further moves towards the centers of the two scrolls and its volume further decreases, and the third compression chamber 233 remains at the centers of the two scrolls but its volume further decreases, so that the medium in each compression chamber is further pushed towards the centers of the two scrolls and is further compressed. When the two scrolls further move from Figure 4 the third position shown return to Figure 2 the first position shown through their respective rotations, the third compression chamber 233 disappears, thereby discharging the compressed medium, the second compression chamber 232 becomes the new third compression chamber 233, the first compression chamber 231 becomes the new second compression chamber 232, and a new first compression chamber 231 is generated, thus ending the previous compression process and starting a new compression process. As the two scroll disks rotate, the above compression process is repeatedly executed, so that the two scrolls can continuously suck in, move, compress, and discharge the medium.

[0037] Under the above configuration, the compression process is achieved by two scroll disks rotating around their respective rotation axes at the same rotational speed and in the same direction, rather than by the revolution (also known as translation) of any one scroll disk. Therefore, no scroll disk will generate eccentric inertia due to revolution, which avoids the mutual collision of the two scroll bodies due to eccentric inertia, thereby prolonging the service life of the scroll bodies and improving their reliability. Moreover, there is no need to set eccentric blocks to overcome eccentric inertia, nor is there a need to set anti-rotation structures to suppress the self-rotation of the scroll disks. This simplifies the overall structure of the compressor and improves its reliability. Additionally, since the revolution motion is replaced by a more stable rotational motion, the dynamic performance of the compressor is also significantly improved. Further, since the transmission shaft 400 can effectively ensure that the two scroll disks rotate around their respective rotation axes at the same rotational speed and in the same direction, the above compression process can be carried out in a more reliable and stable manner, which further improves the reliability of the compressor.

[0038] Return to Figure 1 , the co-rotating scroll compressor 10 further includes a motor 500 disposed within the housing 110. The motor 500 includes a stator 510 fixed within the housing 110, a main shaft 520 rotatably disposed within the housing 110 and radially inside the stator 510, and a rotor 530 fixed to the main shaft 520. Among them, the stator 510 is configured to generate a rotating magnetic field after being energized, and the rotor 530 is configured to be coupled to the rotating magnetic field generated by the stator 510 through magnetic flux, so as to drive the main shaft 520 to rotate together under the drive of the rotating magnetic field. In particular, the main shaft 520 can be rotatably supported by two main shaft bearings 350 fixed within the housing 110, and these two main shaft bearings 350 are positioned at both ends of the main shaft 520. Additionally, as Figure 1As shown, the main shaft 520 is configured to rotate about a second rotation axis RA2 and is coupled to the second scroll disk 220 on a side opposite to the second scroll body 221 (e.g., via a keyway) so as to drive the second scroll disk 220 to rotate about the second rotation axis RA2. In this configuration, after being powered on, the motor 500 drives the second scroll disk 220 to rotate about the second rotation axis RA2 via the main shaft 520. The second scroll disk 220 drives the transmission shaft 400 to rotate about a third rotation axis RA3 via the second gear ring 222 and the second gear 420, and the transmission shaft 400 drives the first scroll disk 210 to rotate about a first rotation axis RA1 via the first gear 410 and the first gear ring 212, thereby completing the above compression process. Of course, the above embodiments are merely exemplary. In embodiments not shown, the co-rotating scroll compressor 10 may not include the motor 500 and instead may be driven by an external motor. The main shaft 520 may also not be coupled to any of the scroll disks but instead may be coupled to the transmission shaft 400 so as to drive the two scroll disks to rotate about their respective rotation axes via the transmission shaft 400. Therefore, any coupling manner of the motor 500 with the two scroll disks and the transmission shaft 400 falls within the protection scope of the present disclosure.

[0039] Continue to refer to Figure 1, the first scroll disk 210 further includes a generally disk-shaped first disk body 213 and a generally cylindrical first ring body 214 that projects axially from the first disk body 213 along the outer periphery or perimeter of the first disk body 213. Among them, the first scroll body 211 projects from the first disk body 213 and is radially inside the first ring body 214, such that the first ring body 214 surrounds the first scroll body 211, and the first gear ring 212 is arranged on the outer periphery or perimeter of the first ring body 214. The second scroll disk 220 further includes a generally disk-shaped second disk body 223. Among them, the second scroll body 221 projects axially from the second disk body 223, and the second gear ring 222 is arranged on the outer periphery or perimeter of the second disk body 223. In this configuration, since the first gear ring 212 is arranged on the outer periphery or perimeter of the first ring body 214, rather than on the outer periphery or perimeter of the first disk body 213, the position of the first gear ring 212 and the position of the first gear 410 meshing with the first gear ring 212 are no longer restricted by the position of the first disk body 213. Thus, the first gear ring 212 and the first gear 410 can be positioned such that the meshing position of the first gear ring 212 and the first gear 410 can be aligned or centered in the radial direction with the meshing position of the first scroll body 211 and the second scroll body 221. That is to say, the meshing position of the first gear ring 212 and the first gear 410 and the meshing position of the first scroll body 211 and the second scroll body 221 are at the same level in the axial direction. Further, the first scroll disk 210, the second scroll disk 220, and the transmission shaft 400 can be positioned such that the first rotation axis RA1, the second rotation axis RA2, and the third rotation axis RA3 are intersected by or intersect with the same line oriented along the radial direction, and the first rotation axis RA1 is located between the second rotation axis RA2 and the third rotation axis RA3. In this configuration, the first scroll disk 210 will be clamped between the second scroll disk 220 and the transmission shaft 400 in the radial direction. Thus, when the first gear ring 212 meshes with the first gear 410, the radial component force F (as shown by the arrow in Figure 1 ) applied to the involute side when the first scroll body 211 meshes with the second scroll body 221 and points to the centers of the first scroll body 211 and the second scroll body 221. Thus, the overturning of the first scroll body 211 and the second scroll body 221 can be reduced, thereby reducing the tangential leakage of the medium. In addition, as shown in Figure 1 , the first scroll body 211 abuts against the second disk body 223, and the second scroll body 221 abuts against the first disk body 213, thereby eliminating the axial clearance between the first scroll disk 210 and the second scroll disk 220 that may cause the axial leakage of the medium in each compression chamber, thus ensuring the working efficiency of the compressor.

[0040] Refer to Figure 5, which shows a schematic cross-sectional view of a co-rotating scroll compressor according to another embodiment of the present disclosure. Figure 5 The illustrated embodiment and Figure 1 The main difference between the illustrated embodiment is that the first scroll disk 210 does not include the first ring body 214, and the first toothed ring 212 is arranged on the outer periphery or perimeter of the first disk body 213. In this configuration, the first toothed ring 212 and the first gear 410, and the second toothed ring 222 and the second gear 420 can be arranged adjacent to two transmission shaft bearings 340 at both ends of the transmission shaft 400 respectively, which enables the two transmission shaft bearings 340 to more effectively suppress the radial displacement of the first toothed ring 212 and the first gear 410, and the second toothed ring 222 and the second gear 420. Thereby, it can be ensured that the first toothed ring 212 and the first gear 410, and the second toothed ring 222 and the second gear 420 can all be reliably meshed together, which more reliably ensures the smooth operation of the compressor and further improves its dynamic performance.

[0041] Referring to Figure 6 , which shows a schematic cross-sectional view of a co-rotating scroll compressor according to yet another embodiment of the present disclosure. Figure 6 The illustrated embodiment and Figure 1 and Figure 5 The main difference between the illustrated embodiment is that in Figure 1 and Figure 5 In the illustrated embodiment, the co-rotating scroll compressor 10 only includes one transmission shaft 400, while in Figure 6In the illustrated embodiment, the co-rotating scroll compressor 10 may include two or more drive shafts 400 rotatably disposed within the housing 110. These drive shafts 400 may be evenly distributed about the first rotation axis RA1 or the second rotation axis RA2 (i.e., along the circumferential direction). Each of these drive shafts 400 is rotatably disposed within the housing 110 and is provided with a first gear 410 and a second gear 420 fixed thereto. Among them, the first gear ring 212 meshes with each first gear 410, and the tooth number ratio with each first gear 410 is the same. The second gear ring 222 meshes with each second gear 420, and the tooth number ratio with each second gear 420 is the same. And the tooth number ratio of the first gear ring 212 with each first gear 410 is equal to the tooth number ratio of the second gear ring 222 with each second gear 420. In this configuration, compared with a single drive shaft, multiple drive shafts can more reliably ensure that the two scroll disks rotate at the same rotational speed and in the same direction. And a single drive shaft may cause the two scroll disks to displace away from the drive shaft, while multiple drive shafts evenly distributed along the circumferential direction can effectively suppress such radial displacement of the two scroll disks, thereby ensuring that the two gear rings can reliably mesh with each gear. Therefore, the above configuration further improves the reliability and dynamic performance of the compressor.

[0042] In the embodiment described with reference to the accompanying drawings above, the first gear 410 is a spur gear, and the first gear ring 212 is a spur gear ring meshing therewith. The second gear 420 is a spur gear, and the second gear ring 222 is a spur gear ring meshing therewith. However, this is merely exemplary. For example, referring to Figure 7, which shows a schematic perspective view of a first scroll disk of a co-rotating scroll compressor according to yet another embodiment of the present disclosure, wherein the first tooth ring 212 is a helical tooth ring. In this embodiment, the first scroll disk 210 and the second scroll disk 220 are configured to rotate in a predetermined direction to compress a medium, and wherein the first gear 410 is a helical gear, the first tooth ring 212 is a helical tooth ring meshing therewith, and the inclination direction of the teeth of the first gear 410 is such that these teeth: when the first scroll disk 210 rotates in a predetermined direction, the force exerted by these teeth on the first tooth ring 212 has a component towards the second scroll disk 220; and / or, the second gear 420 is a helical gear, the second tooth ring 222 is a helical tooth ring meshing therewith, and the inclination direction of the teeth of the second gear 420 is such that these teeth: when the second scroll disk 220 rotates in a predetermined direction, the force exerted by these teeth on the second tooth ring 222 has a component towards the first scroll disk 210. In particular, the helix angles of the first tooth ring 212 and the second tooth ring 222 may both be right-handed, while the helix angles of the first gear 410 and the second gear 420 may both be left-handed. In this configuration, the first scroll disk 210 and the second scroll disk 220 can be pressed towards each other by the first gear 410 and / or the second gear 420, thereby avoiding an axial gap between the two that causes axial leakage of the medium, and thus more reliably ensuring the working efficiency of the compressor.

[0043] The optional but non-limiting embodiments of the co-rotating scroll compressor according to the present disclosure have been described in detail above with reference to the drawings. For those ordinary technicians in the art, modifications and supplements to the technology and structure and the recombination of the features in each embodiment should clearly be regarded as included within the scope of the present disclosure without departing from the spirit and essence of the present disclosure. Therefore, these modifications and supplements that can be envisioned under the teachings of the present disclosure should be regarded as part of the present disclosure. The scope of the present disclosure includes equivalent technologies known at the filing date of the present disclosure and equivalent technologies not yet foreseen.

Claims

1. A co-rotating scroll compressor, characterized in that, Comprising a housing (110), a first scroll disk (210), a second scroll disk (220) and a transmission shaft (400) rotatably arranged within the housing (110), wherein the first scroll disk (210) is configured to rotate about a first rotation axis (RA1), and includes a first scroll body (211) protruding axially and a first gear ring (212) arranged circumferentially; wherein the second scroll disk (220) is configured to rotate about a second rotation axis (RA2), and includes a second scroll body (221) protruding axially and a second gear ring (222) arranged circumferentially, the second scroll body (221) meshes with the first scroll body (211), and the second rotation axis (RA2) is parallel and offset from the first rotation axis (RA1); and wherein the transmission shaft (400) is provided with a first gear (410) and a second gear (420) fixed thereon and coaxial, the first gear (410) meshes with the first gear ring (212), the second gear (420) meshes with the second gear ring (222), and the tooth number ratio of the first gear ring (212) to the first gear (410) is equal to the tooth number ratio of the second gear ring (222) to the second gear (420).

2. The co-rotating scroll compressor according to claim 1, wherein, Further comprising a motor (500) arranged within the housing (110), the main shaft (520) of the motor (500) being coupled to the transmission shaft (400) to drive the transmission shaft (400) to rotate.

3. The co-rotating scroll compressor according to claim 1, wherein, Further comprising a motor (500) arranged within the housing (110), the main shaft (520) of the motor (500) being coupled to the second scroll disk (22,0) to drive the second scroll disk (220) to rotate.

4. The co-rotating scroll compressor according to claim 3, wherein, The first scroll disk (210) is provided with a through hole (H1) leading to the center of the first scroll body (211).

5. The co-rotating scroll compressor according to any one of claims 1-4, characterized in that, The first scroll disk (210) further includes a first disk body (213) and a first ring body (214) protruding axially from the first disk body (213), the first scroll body (211) protrudes axially from the first disk body (213) and is located radially inside the first ring body (214), and the first gear ring (212) is arranged on the outer periphery of the first ring body (214).

6. The co-rotating scroll compressor according to claim 5, wherein, The second scroll body (221) abuts against the first disk body (213).

7. The co-rotating scroll compressor according to claim 5, wherein, The meshing position of the first gear (410) and the first gear ring (212) is radially aligned with the meshing position of the first scroll body (211) and the second scroll body (221).

8. The co-rotating scroll compressor according to any one of claims 1-4, characterized in that, The first scroll disk (210) further includes a first disk body (213), the first scroll body (211) protrudes axially from the first disk body (213), and the first gear ring (212) is arranged on the outer periphery of the first disk body (213).

9. The co-rotating scroll compressor according to claim 8, wherein, The second scroll body (221) abuts against the first disk body (213).

10. The co-rotating scroll compressor according to any one of claims 1-4, characterized in that, The second scroll disk (220) further includes a second disk body (223), the second scroll body (221) axially projects from the second disk body (223), and the second gear ring (222) is disposed on the outer periphery of the second disk body (223).

11. The co-rotating scroll compressor according to claim 10, characterized in that, The first scroll body (211) abuts against the second disk body (223).

12. The co-rotating scroll compressor according to any one of claims 1-4, characterized in that, It includes a plurality of transmission shafts (400) evenly distributed in the circumferential direction.

13. The co-rotating scroll compressor according to any one of claims 1-4, characterized in that, The first gear (410) is a spur gear.

14. The co-rotating scroll compressor according to any one of claims 1-4, characterized in that, The first scroll disk (210) is configured to rotate in a predetermined direction, and the first gear (410) is a helical gear, so that when the first scroll disk (210) rotates in the predetermined direction, the force applied by the first gear (410) to the first gear ring (212) has a component towards the second scroll disk (220).

15. The co-rotating scroll compressor according to any one of claims 1-4, characterized in that, The second gear (420) is a spur gear.

16. The co-rotating scroll compressor according to any one of claims 1-4, characterized in that, The second scroll disk (220) is configured to rotate in a predetermined direction, and the second gear (420) is a helical gear, so that when the second scroll disk (220) rotates in the predetermined direction, the force applied by the second gear (420) to the second gear ring (222) has a component towards the first scroll disk (210).

17. The co-rotating scroll compressor according to any one of claims 1-4, characterized in that, The transmission shaft (400) is configured to rotate about a third rotation axis (RA3), the first rotation axis (RA1), the second rotation axis (RA2) and the third rotation axis (RA3) intersect with the same radially oriented straight line, and the first rotation axis (RA1) is located between the second rotation axis (RA2) and the third rotation axis (RA3).

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