Scroll compressor

Abstract

This disclosure discloses a scroll compressor comprising: an electric motor including a stator and a rotor spaced apart axially; a first scroll including a first disc body, a first scroll body projecting axially from the first disc body, a sidewall, and a plurality of cylindrical pins projecting axially from the sidewall, the sidewall surrounding the first scroll body and having a plurality of radially extending through openings; and a second scroll including a second disc body and a second scroll body projecting axially from the second disc body, the second disc body having a plurality of axially extending circular holes, wherein the rotor is fixed to the first disc body on the side opposite to the sidewall to drive the first scroll to rotate about a first axis, the first scroll body meshing with the second scroll body, and each cylindrical pin inserted into a circular hole and having a radial dimension smaller than that of the circular hole to drive the second scroll to rotate about a second axis parallel to and offset from the first axis.

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 this eccentric inertia, an eccentric block is needed on the eccentric shaft to compensate for the eccentric dynamic mass of the moving scroll. This not only increases the compressor's weight and energy consumption but also complicates its manufacturing and assembly. Third, to suppress the rotation of the moving scroll and ensure it only revolves (i.e., translational revolution), an anti-rotation structure is required, further increasing the compressor's weight and complicating its manufacturing and assembly. Although some existing technologies use two scrolls rotating around their respective axes to compress the medium, the drive and transmission mechanisms between the two scrolls negatively impact the intake volume, even resulting in lower volumetric efficiency than traditional revolution-type scroll compressors.

[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. Utility Model Content

[0004] To address the problems in the prior art, this disclosure proposes an improved co-rotating scroll compressor, comprising: a motor including a stator and a rotor spaced apart axially; a first scroll including a first disc body, a first scroll body projecting axially from the first disc body, a sidewall, and a plurality of cylindrical pins projecting axially from the sidewall, the sidewall surrounding the first scroll body and having a plurality of radially extending through openings; and a second scroll including a second disc body and a second scroll body projecting axially from the second disc body, the second disc body having a plurality of axially extending circular holes, wherein the rotor is fixed to the first disc body on the side opposite to the sidewall to drive the first scroll to rotate about a first axis, the first scroll body meshing with the second scroll body, and each cylindrical pin inserted into a circular hole and having a radial dimension smaller than that of the circular hole to drive the second scroll to rotate about a second axis parallel to and offset from the first axis.

[0005] According to an alternative embodiment of this disclosure, the sidewall has an end axially away from the first disc body, the plurality of cylindrical pins are disposed on the end, and each opening extends axially from the first disc body to the end.

[0006] According to an optional embodiment of this disclosure, the first vortex disk further includes a first support shaft that protrudes axially from the first disk body on the side opposite to the first vortex body and the sidewall, the first support shaft being supported by a first bearing.

[0007] According to an optional embodiment of this disclosure, the second vortex further includes a second support shaft that protrudes axially from the second disk body on the side opposite to the second vortex body, the second support shaft being supported by a second bearing.

[0008] According to an alternative embodiment of this disclosure, the scroll compressor further includes: a cage comprising a retaining sleeve and an outer flange projecting radially outward from the retaining sleeve, the retaining sleeve being arranged to surround the second support shaft, and each cylindrical pin extending through the second disc and connecting to the outer flange; and a bearing assembly disposed in the retaining sleeve, comprising an outer bearing and an inner bearing arranged eccentrically relative to each other, the outer ring of the outer bearing being fixed to the retaining sleeve, the inner ring of the inner bearing being fixed to the second support shaft, and the outer ring of the inner bearing being fixed to the inner ring of the outer bearing.

[0009] According to an alternative embodiment of this disclosure, the outer flange protrudes outward from the end of the retaining cylinder near the second disc body; and / or, the bearing assembly further includes an eccentric block for fixing the outer ring of the inner bearing to the inner ring of the outer bearing; and / or, the outer bearing is an eccentric bearing with an eccentric hole in its inner ring, and the inner bearing is disposed in the eccentric hole.

[0010] According to an optional embodiment of the present disclosure, the bearing assembly and the second disc are axially spaced apart to define a back pressure chamber between them, the first vortex body and the second vortex body define a central chamber at the center, and the second vortex disc is provided with a pressure accumulator hole communicating the central chamber and the back pressure chamber.

[0011] According to an optional embodiment of this disclosure, the second scroll plate is provided with an exhaust port extending axially through the second support shaft and leading to the central chamber, and the accumulator hole extends radially through the second support shaft to communicate the exhaust port with the back pressure chamber; or, the accumulator hole extends axially through the second plate body to communicate the central chamber with the back pressure chamber.

[0012] According to an optional embodiment of this disclosure, the first vortex body and the second vortex body further define a plurality of other compression chambers located radially outside the central chamber, and the second vortex disk is provided with a pressure relief hole communicating the back pressure chamber with one of the plurality of other compression chambers.

[0013] According to an alternative embodiment of this disclosure, the pressure relief hole extends axially through the second disc to communicate the back pressure chamber with one of the plurality of other compression chambers.

[0014] According to an optional embodiment of this disclosure, the scroll compressor further includes an outer sealing ring clamped between the outer flange and the second disc; and / or, the retainer further includes an inner flange projecting radially inward from the retaining cylinder, and the scroll compressor further includes an annular boss for retaining the second bearing and an inner sealing ring clamped between the inner flange and the annular boss.

[0015] 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

[0016] The accompanying drawings illustrate exemplary embodiments of this disclosure. These drawings should not be construed as necessarily limiting the scope of this disclosure, wherein:

[0017] Figure 1 This is a schematic cross-sectional view of a scroll compressor according to one embodiment of the present disclosure;

[0018] Figure 2 yes Figure 1 A schematic perspective view of the first scroll plate of the scroll compressor shown;

[0019] Figure 3 yes Figure 1 A schematic perspective view of the second scroll plate of the scroll compressor shown;

[0020] Figure 4 It is along Figure 1 A schematic cross-sectional view of the first and second vortex bodies intercepted by line IV-IV in the diagram;

[0021] Figure 5 yes Figure 1 A schematic perspective view of the cage of the scroll compressor shown;

[0022] Figure 6 yes Figure 1 A schematic perspective view of the bearing assembly of the scroll compressor shown.

[0023] Figure 7 yes Figure 6 A schematic front view of the bearing assembly shown; and

[0024] Figure 8 This is a schematic cross-sectional view of a scroll compressor according to another embodiment of the present disclosure. Detailed Implementation

[0025] 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.

[0026] This disclosure aims to propose a novel co-rotating scroll compressor. Co-rotation refers to the fact that, compared to a conventional revolution-type scroll compressor, the scroll compressor of this disclosure replaces the revolution of one scroll relative to another with the rotation of the two scrolls around two mutually offset axes in the process of working with the medium (e.g., coolants such as R744, R134A, R290, etc.). This avoids eccentric inertia caused by the revolution of the scrolls, and thus prevents the scroll bodies of the two scrolls from laterally impacting each other due to eccentric inertia, thereby improving the reliability of the scroll bodies and extending their service life. Furthermore, since eccentric inertia is overcome, the scroll compressor of this disclosure does not require an eccentric block, thereby 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 scroll compressor of this disclosure is also significantly improved. In particular, in addition to the advantages mentioned above, the novel design of the scroll compressor according to this disclosure also gives it one or more of the following advantages: allowing coolant to enter the compression chamber more smoothly, positioning the two scrolls more reliably, eliminating the axial clearance between the two scrolls, and improving the lubrication of the scroll bodies and bearing assemblies of the two scrolls, etc.

[0027] Various alternative, but non-limiting, embodiments of the co-rotating scroll compressor according to this disclosure are described in detail below with reference to the accompanying drawings. 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 any axis of rotation, "radial direction" refers to a direction perpendicular to any axis of rotation, and "circumferential direction" refers to a direction about any axis of rotation; unless otherwise explicitly stated, these terms indicating relative orientation have their usual meaning in the art.

[0028] refer to Figure 1 A schematic cross-sectional view of a scroll compressor according to one embodiment of the present disclosure is shown. Figure 1 As shown, the scroll compressor 10 includes a housing 100 and a motor 200 mounted in the housing 100. The motor 200 includes a stator 210 fixed to the housing 100 and a rotor 220 spaced apart from the stator 210 in an axial direction. That is, the motor 200 is configured as an axial flux motor such that the stator 210 and the rotor 220 are coupled to each other by magnetic flux located between them in the axial direction.

[0029] refer to Figure 2 , which shows Figure 1 A schematic perspective view of the first scroll plate of a scroll compressor. (See diagram.) Figure 1 and Figure 2 As shown, the scroll compressor 10 also includes a first scroll 300 rotatably disposed within the housing 100. The first scroll 300 includes a first disk body 310 and first scroll bodies 320 and a first support shaft 330 protruding from both sides of the first disk body 310. Specifically, the first scroll bodies 320 and the first support shaft 330 are located on opposite sides of the first disk body 310 along the axial direction and protrude from the first disk body 310 respectively along the axial direction. When viewed along the axial direction, the first scroll body 320 has a spiral or vortex shape; that is, the first scroll body 320 extends along an involute from an end near the center of the base circle to an end away from the center of the base circle. Furthermore, the first support shaft 330 is generally cylindrical and rotatably supported by a first bearing 410 fixed to the housing 100. The first bearing 410 can be held, for example, by an annular boss fixed to the housing 100. Specifically, the outer ring of the first bearing 410 is fixed to the housing 100, while its inner ring is fitted and fixed to the first support shaft 330, and the first bearing 410 positions the first support shaft 330 such that the first scroll 300 can rotate around the first axis X1.

[0030] refer to Figure 3 , which shows Figure 1 A schematic perspective view of the second scroll plate of a scroll compressor. (See diagram.) Figure 1 and Figure 3As shown, the scroll compressor 10 also includes a second scroll 500 rotatably disposed within the housing 100. The second scroll 500 includes a second disk body 510 and second scroll bodies 520 and a second support shaft 530 protruding from both sides of the second disk body 510. Specifically, the second scroll body 520 and the second support shaft 530 are located on opposite sides of the second disk body 510 along the axial direction and protrude from the second disk body 510 respectively along the axial direction. When viewed along the axial direction, the second scroll body 520 has a spiral or vortex shape; that is, the second scroll body 520 extends along an involute from an end near the center of the base circle to an end away from the center of the base circle. Furthermore, the second support shaft 530 is generally cylindrical and rotatably supported by a second bearing 420 fixed to the housing 100. The second bearing 420 can be held, for example, by an annular boss fixed to the housing 100. Specifically, the outer ring of the second bearing 420 is fixed to the housing 100, while its inner ring is fitted and fixed to the second support shaft 530. The second bearing 420 positions the second support shaft 530 such that the second scroll 500 can rotate about a second axis X2, wherein the second axis X2 is parallel to the first axis X1 and offset radially relative to the first axis X1. That is, the first scroll 300 and the second scroll 500 are configured to rotate about two axes that are parallel and offset relative to each other. Furthermore, the first scroll 300 and the second scroll 500 are oriented oppositely to each other in the axial direction, such that the first support shaft 330 and the second support shaft 530 are oriented away from each other, while the first scroll body 320 and the second scroll body 520 are oriented towards each other. In this configuration, the first scroll body 320 and the second scroll body 520 can mesh together as described in more detail below, thereby defining a plurality of compression chambers.

[0031] refer to Figure 4 , which shows along Figure 1 A schematic cross-sectional view of the first and second vortex bodies intercepted by line IV-IV in the diagram. (See diagram below.) Figure 1 and Figure 4As shown, the first vortex body 320 and the second vortex body 520 define a plurality of compression chambers between each other. The plurality of compression chambers include a central chamber C1 located at the center of the two vortex bodies, two intermediate chambers C2 located outside the central chamber C1 and symmetrically arranged about the center of the two vortex bodies, and two outer chambers C3 located outside the two intermediate chambers C2 and symmetrically arranged about the center of the two vortex bodies. The intermediate chambers C2 and the outer chambers C3 can be collectively referred to as other compression chambers. The first vortex body 320 and the second vortex body 520 isolate the above-mentioned compression chambers from each other, and the volume of the above-mentioned compression chambers decreases as they approach the center of the two vortex bodies. When the first vortex 300 and the second vortex 500 rotate around their respective axes, the two outer chambers C3 can receive the medium from the radially outer side and then move toward the position of the two intermediate chambers C2 until they become two new intermediate chambers C2; the two intermediate chambers C2 can move toward the position of the central chamber C1 until they merge into a new central chamber C1; and the central chamber C1 can contract until it disappears, thereby discharging the medium. This realizes the process of moving and compressing the medium from the outside to the inside of the two vortex bodies. As the first vortex 300 and the second vortex 500 rotate around their respective axes, the above compression process is repeated so that the two vortex bodies can continuously draw in, move, compress and discharge the medium.

[0032] In order to drive the first scroll plate 300 and the second scroll plate 500 to rotate around their respective axes to achieve the above compression process, as follows: Figure 1 As shown, the motor 200 is positioned within the housing 100 such that its axis of rotation coincides with the first axis X1, and the rotor 220 of the motor 200 is fixed to the first disk 310 on the side opposite to the first scroll body 320 (that is, on the side where the first support shaft 330 is provided), so that the first scroll 300 is located axially between the motor 200 and the second scroll 500, and the rotor 220 is capable of driving the first scroll 300 to rotate about the first axis X1 after the motor 200 (e.g., the stator winding of the stator 210) is energized. Further, as Figures 1-3As shown, the first vortex disk 300 also includes a sidewall 340 protruding from one side of the first disk body 310. The sidewall 340 is located on the same side as the first vortex body 320 and protrudes from the first disk body 310 in the axial direction. The sidewall 340 also surrounds (or encloses or encircles) the first vortex body 320 in the circumferential direction. This makes the sidewall 340 oriented toward the second vortex disk 500 after the first vortex disk 300 and the second vortex disk 500 are assembled, and the first vortex body 320 and the second vortex body 520 are both located radially inside the sidewall 340. Additionally, the first scroll 300 includes a plurality of cylindrical pins 350 fixed to the end 341 of the sidewall 340 (i.e., the end of the sidewall 340 axially away from the first disk body 310) and distributed circumferentially. Each cylindrical pin 350 may be cylindrical and protrude axially from the end 341 of the sidewall 340. The second disk body 510 of the second scroll 500 also has a plurality of circular holes 511 distributed circumferentially, each circular hole 511 may be circular and extend axially. Furthermore, each cylindrical pin 350 is inserted into one of the plurality of circular holes 511, that is, each circular hole 511 is for insertion of one of the plurality of cylindrical pins 350, and the radial dimension (e.g., diameter or radius) of the circular hole 511 is larger than the radial dimension (e.g., diameter or radius) of the cylindrical pin 350. In this configuration, when the first scroll 300 rotates about the first axis X1 driven by the rotor 220 of the motor 200, since each cylindrical pin 350 of the first scroll 300 is inserted into the corresponding circular hole 511 of the second scroll 500, the first scroll 300 can transmit motion to the second scroll 500 through the cylindrical pins 350 to drive the second scroll 500 to rotate. Furthermore, since the radial dimension of the circular hole 511 is larger than the radial dimension of the cylindrical pin 350, each cylindrical pin 350 can move radially within the corresponding circular hole 511 while rotating about the first axis X1, thereby enabling the second scroll 500 to rotate about a second axis X2 offset relative to the first axis X1. Therefore, by means of the pin-ring structure composed of the cylindrical pins 350 and the circular holes 511, the above configuration enables two scrolls to be driven to rotate about two mutually offset axes by a single motor 200, thereby achieving the compression process described above.

[0033] It is worth mentioning that, such as Figure 2 As shown, since the rotor 220 of the motor 200 is disposed on the side of the first disc 310 opposite to the side wall 340, in other words, since the rotor 220 is spaced apart from the side wall 340 along the axial direction rather than disposed on the side wall 340, the side wall 340 may be provided with one or more radially extending through it for the medium to flow through. Figure 2Five openings 342 are shown. In this configuration, the fact that the rotor 220 is spaced axially from the sidewall 340 allows for the provision of openings 342 on the sidewall 340 for media flow. These openings allow the media to flow smoothly through the sidewall 340 to the radially outer sides of the two scroll bodies, thereby increasing the flow rate of the media through the sidewall 340 and thus improving the operating efficiency of the scroll compressor 10. Specifically, each opening 342 extends not only radially through the sidewall 340 but also axially from the first disc 310 to the end 341 of the sidewall 340, so that each opening 342 completely separates two adjacent portions of the sidewall 340. This configuration increases the flow area of ​​the openings 342, further increasing the flow rate of the media through the sidewall 340 and further improving the operating efficiency of the scroll compressor 10. In addition, in order to suppress mutual wear between the two scrolls and extend the service life of the two scrolls, the first scroll 300 may have a wear-resistant coating applied to the first scroll body 320 (optionally and the first disk body 310), and the second scroll 500 may have a wear-resistant coating applied to the second scroll body 520 (optionally and the second disk body 510).

[0034] refer to Figure 5 , which shows Figure 1 A schematic perspective view of the cage of a scroll compressor is shown. Figure 1 and Figure 5 As shown, the scroll compressor 10 also includes a retainer 600 disposed within the housing 100. The retainer 600 is located on the side of the second scroll 500's second disc body 510 where the second support shaft 530 is located (i.e., the side opposite to the first scroll 300), such that the second scroll 500 is axially positioned between the first scroll 300 and the retainer 600. The retainer 600 includes a generally cylindrical retaining cylinder 610 and an outer flange 620 projecting radially outward from the retaining cylinder 610. The outer flange 620 can, for example, project radially outward from the end of the retaining cylinder 610 near the second disc body 510. Figure 1As shown, the retaining sleeve 610 of the retainer 600 is arranged radially outside the second support shaft 530 of the second scroll 500, while the outer flange 620 is connected to each cylindrical pin 350 of the first scroll 300. That is, each cylindrical pin 350 is connected to the outer flange 620 after extending through a corresponding circular hole 511 of the second scroll 500 (i.e., extending through the second disk body 510). In this configuration, the first scroll 300 can transmit power not only to the second scroll 500 via the pin ring structure described above, but also to the outer flange 620 via the individual cylindrical pins 350, allowing the retainer 600 to rotate together with the first scroll 300 about the first axis X1. Further, refer to... Figure 6 and Figure 7 ,in, Figure 6 It shows Figure 1 A schematic perspective view of the bearing assembly of the scroll compressor is shown, and Figure 7 It shows Figure 6 A schematic front view of the bearing assembly shown. (As shown) Figure 1 , Figure 6 and Figure 7 As shown, the scroll compressor 10 also includes a bearing assembly 700 disposed within the retaining sleeve 610 of the retainer 600. The bearing assembly 700 is located radially inner to the retaining sleeve 610 and radially outer to the second support shaft 530 of the second scroll 500, such that the bearing assembly 700 is radially positioned between the retaining sleeve 610 and the second support shaft 530. The bearing assembly 700 includes an outer bearing 710 and an inner bearing 720 located radially inner to the outer bearing 710. Specifically, the outer ring of the outer bearing 710 is fixed to the support sleeve 610, and the inner ring of the inner bearing 720 is fitted onto and fixed to the second support shaft 530, and the inner ring of the outer bearing 710 and the outer ring of the inner bearing 720 are fixed together.

[0035] In the above configuration, the outer ring of the outer bearing 710 can rotate together with the cage 600 around the first axis X1, while the inner ring of the inner bearing 720 can rotate together with the second scroll 500 around the second axis X2. Therefore, the inner bearing 720 is eccentrically arranged relative to the outer bearing 710. Furthermore, since the inner ring of the outer bearing 710 and the outer ring of the inner bearing 720 are fixed together, the above-mentioned eccentric arrangement causes the inner ring of the outer bearing 710 and the outer ring of the inner bearing 720 to be unable to rotate relative to either the first axis X1 or the second axis X2. This allows the inner ring of the outer bearing 710 and the outer ring of the inner bearing 720 to remain fixed when the second scroll 500 and the cage 600 rotate around their respective axes. This allows the second scroll 500 and the cage 600 to support each other during rotation by means of the fixed inner ring of the outer bearing 710 and the outer ring of the inner bearing 720. Therefore, with the aid of the aforementioned bearing assembly 700, the second scroll 500 and the cage 600 can support each other even when rotating about two mutually offset axes. This allows the first scroll 300 to be supported by a first bearing 410 and an outer bearing 710 spaced apart along the axial direction, and the second scroll 500 to be supported by a second bearing 420 and an inner bearing 720 spaced apart along the axial direction. Since each scroll is supported by two bearings spaced apart along the axial direction, the dynamic stability of each scroll is significantly improved. This not only improves the reliability and dynamic performance of the scroll compressor 10, but also allows each scroll to rotate at a higher speed, thereby helping to improve the operating efficiency of the scroll compressor 10.

[0036] Furthermore, such as Figure 1 , Figure 6 and Figure 7As shown, the bearing assembly 700 also includes an eccentric block 730 disposed between the inner ring of the outer bearing 710 and the outer ring of the inner bearing 720, and fixing the two together. Specifically, the eccentric block 730 is generally disk-shaped and has an eccentric hole 731 eccentric to its outer periphery. The eccentric block 730 is disposed in the inner ring of the outer bearing 710, while the inner bearing 720 is disposed in the eccentric hole 731. The eccentric block 730 is connected to the inner ring of the outer bearing 710 on the radially outer side and to the outer ring of the inner bearing 720 on the radially inner side, so that the inner ring of the outer bearing 710 and the outer ring of the inner bearing 720 are fixed together by the eccentric block 730. Therefore, by means of the eccentric block 730, the outer bearing 710 and the inner bearing 720 can be nested together in an eccentric manner. Of course, the above embodiments are merely exemplary. In embodiments not shown, the outer bearing 710 can be an eccentric bearing. Specifically, the inner ring of the outer bearing 710 has an eccentric hole that is eccentric relative to its axis of rotation (i.e., the first axis X1), and the inner bearing 720 can be disposed in this eccentric hole, with its outer ring fixed to the inner ring of the outer bearing 710. In this configuration, the outer ring of the inner bearing 720 can be directly connected to the inner ring of the outer bearing 710, eliminating the need for connection via the eccentric block 730. Therefore, this configuration eliminates the necessity of the eccentric block 730, simplifying the construction of the bearing assembly 700.

[0037] Back Figure 1The housing 100 defines an internal chamber, and the scroll compressor 10 further includes an isolation plate 800 disposed in the internal chamber and fixed to the housing 100. The isolation plate 800 divides the internal chamber into an intake chamber 110 for receiving the medium to be compressed and an exhaust chamber 120 for collecting the compressed medium. Various components, such as the motor 200, the first scroll 300, the second scroll 500, the cage 600, and the bearing assembly 700, are housed within the intake chamber 110. Specifically, the second bearing 420 is held by an annular boss fixed to the isolation plate 800. That is, the isolation plate 800 not only separates the intake chamber 110 from the exhaust chamber 120 but also supports the second support shaft 530 of the second scroll 500. In particular, the housing 100 also has an inlet 130 in fluid communication with the intake chamber 110 and an outlet 140 in fluid communication with the exhaust chamber 120. As described above, the meshing first vortex body 320 and second vortex body 520 can draw in the medium from the radially outer side and discharge the medium through the central chamber C1 as they rotate about their respective axes. Therefore, in order to discharge the medium from the central chamber C1 into the exhaust chamber 120, the second vortex 500 is also provided with an exhaust port 531 extending longitudinally through the second support shaft 530 and leading to the central chamber C1 (i.e., in fluid communication with the central chamber C1), and the second support shaft 530 is arranged to extend through the partition plate 800 such that the exhaust port 531 leads to the exhaust chamber 120 on the side opposite to the central chamber C1. In this configuration, the medium to be compressed from the outside can be supplied to the intake chamber 110 through the inlet 130, and then drawn in from the radial outside by the first vortex body 320 and the second vortex body 520, compressed and moved towards the center of the two until it reaches the central chamber C1. The medium in the central chamber C1 can be discharged to the exhaust chamber 120 through the exhaust port 531. Finally, the medium in the exhaust chamber 120 can be discharged through the outlet 140. This realizes the working process of receiving low-pressure medium from the outside, compressing it into high-pressure medium and finally providing high-pressure medium to the outside.

[0038] refer to Figure 8 The illustration shows a schematic cross-sectional view of a scroll compressor according to another embodiment of the present disclosure. Figure 8 The implementation methods shown are the same as Figure 1 The embodiments shown are largely the same, with the main difference being that the second scroll plate 500 and the bearing assembly 700 have different configurations. Specifically, as... Figure 8As shown, the bearing assembly 700 is spaced axially from the second disc body 510 of the second scroll 500, such that the bearing assembly 700 and the second disc body 510 define a back pressure chamber CB between them. The back pressure chamber CB is located axially between the bearing assembly 700 and the second disc body 510 and is surrounded circumferentially by the retaining sleeve 610 of the retainer 600. Additionally, the second scroll 500 is provided with a pressure accumulator 532 extending radially through the second support shaft 530 to fluidly communicate the exhaust port 531 with the back pressure chamber CB. In this configuration, since the exhaust port 531 fluidly connects the central chamber C1 to the exhaust chamber 120, and the accumulator port 532 fluidly connects the exhaust port 531 to the back pressure chamber CB, the exhaust port 531 can not only discharge the high-pressure medium in the central chamber C1 to the exhaust chamber 120, but also discharge the high-pressure medium to the back pressure chamber CB through the accumulator port 532. This allows pressure to be established in the back pressure chamber CB by means of the high-pressure medium, which can act on the second disc 510, thereby pushing the second scroll 500 toward the first scroll 300. This ensures that the first scroll 300 and the second scroll 500 remain in contact, thus eliminating the axial clearance between them. This helps prevent leakage of the medium in each compression chamber (especially the central chamber C1) through the gap between the first scroll 300 and the second scroll 500, thereby improving the volumetric efficiency of the scroll compressor 10. Furthermore, it is worth mentioning that since the medium often contains lubricating oil, the accumulator hole 532 can not only supply high-pressure medium to the back pressure chamber CB, but also supply lubricating oil to the back pressure chamber CB. The lubricating oil entering the back pressure chamber CB can improve the lubrication of components such as the second scroll plate 500, the cage 600, and the bearing assembly 700, thereby delaying their wear and extending their service life. Of course, the above embodiments are merely exemplary. In embodiments not shown, the accumulator hole 532 may also be configured to extend axially through the second disc body 510 to fluidly communicate the back pressure chamber CB with the central chamber C1, instead of extending radially through the second support shaft 530.

[0039] Furthermore, such as Figure 8As shown, the second scroll 500 also has a pressure relief hole 512 extending axially through the second scroll body 510. This pressure relief hole 512 connects to the back pressure chamber CB on one side and to one of several other compression chambers (e.g., intermediate chamber C2 or outer chamber C3) other than the central chamber C1 on the other side. In other words, the pressure relief hole 512 is configured to provide fluid communication between the back pressure chamber CB and one of several other compression chambers located radially outside the central chamber C1. In this configuration, the pressure relief hole 512 can discharge the high-pressure medium in the back pressure chamber CB to a compression chamber other than the central chamber C1, thereby reducing the pressure in the back pressure chamber CB. Therefore, in the above configuration, on the one hand, the pressure in the back pressure chamber CB can be increased through the pressure accumulator 532, and on the other hand, the pressure in the back pressure chamber CB can be reduced through the pressure relief hole 512, thereby enabling the pressure in the back pressure chamber CB to achieve dynamic equilibrium and remain stable. Therefore, the above configuration helps reduce pressure fluctuations in the back pressure chamber CB, thereby preventing the first scroll 300 and the second scroll 500 from axially wobbling or even colliding due to pressure fluctuations in the back pressure chamber CB. This not only helps improve the NVH performance of the scroll compressor 10, but also extends the service life of the first scroll 300 and the second scroll 500 and improves the reliability of the scroll compressor 10. In addition, it is worth mentioning that since the medium often contains lubricating oil, the pressure relief hole 512 can not only discharge high-pressure medium into the compression chamber, but also discharge lubricating oil into the compression chamber. The lubricating oil entering the compression chamber can improve the lubrication of the first scroll body 320 and the second scroll body 520, thereby delaying their wear and extending their service life.

[0040] Furthermore, such as Figure 8As shown, the scroll compressor 10 also includes an outer sealing ring 910 sandwiched between the second disc body 510 of the second scroll 500 and the outer flange 620 of the cage 600. This outer sealing ring 910 is arranged radially outward of the back pressure chamber CB along its entire circumference. In this configuration, the outer sealing ring 910 prevents leakage of the high-pressure medium in the back pressure chamber CB through the gap between the second disc body 510 and the outer flange 620, thereby ensuring efficient pressure build-up in the back pressure chamber CB to reliably eliminate the axial clearance between the first scroll 300 and the second scroll 500. Specifically, the outer sealing ring 910 is also located radially inward of the aforementioned plurality of circular holes 511 to prevent leakage of the high-pressure medium in the back pressure chamber CB through the circular holes 511. Specifically, the cage 600 also includes an inner flange 630 projecting radially inward from the retaining cylinder 610. This inner flange 630 can, for example, project radially inward from the end of the retaining cylinder 610 away from the second disc 510; that is, the inner flange 630 can be spaced apart from the outer flange 620 in the axial direction. Furthermore, the second bearing 420 is held by an annular boss 810 projecting from the partition plate 800, and the scroll compressor 10 also includes an inner sealing ring 920 sandwiched between the annular boss 810 and the inner flange 630. This inner sealing ring 920 is arranged radially outward around the second bearing 420 along its entire circumference. In this configuration, the high-pressure medium in the back pressure chamber CB can be prevented from leaking through the gap between the inner flange 630 and the annular boss 810 by means of the inner sealing ring 920. Therefore, the leakage path of the back pressure chamber CB can be almost completely blocked by the cooperation of the outer sealing ring 910 and the inner sealing ring 920. Thus, it can more reliably ensure that pressure is built up efficiently in the back pressure chamber CB, thereby more reliably eliminating the axial gap between the first scroll 300 and the second scroll 500.

[0041] The optional but non-limiting embodiments of the scroll compressor according to this disclosure have been described in detail above with reference to the accompanying drawings. Modifications and additions to the technology and structure, as well as recombinations of features in the various embodiments, should be considered within the scope of this disclosure without departing from its spirit and essence. 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 scroll compressor, characterized in that, include: An electric motor (200) includes a stator (210) and a rotor (220) spaced apart along the axial direction; A first volute (300) includes a first disk body (310), a first volute body (320) protruding axially from the first disk body (310), a sidewall (340), and a plurality of cylindrical pins (350) protruding axially from the sidewall (340), the sidewall (340) surrounding the first volute body (320) and having a plurality of radially extending through openings (342); The second vortex (500) includes a second disk body (510) and a second vortex body (520) protruding axially from the second disk body (510). The second disk body (510) is provided with a plurality of axially extending circular holes (511). The rotor (220) is fixed to the first disc (310) on the side opposite to the sidewall (340) to drive the first volute (300) to rotate around the first axis (X1). The first volute (320) meshes with the second volute (520), and each cylindrical pin (350) is inserted into a circular hole (511) and has a radial dimension smaller than the circular hole (511) to drive the second volute (500) to rotate around a second axis (X2) that is parallel to and offset from the first axis (X1).

2. The scroll compressor according to claim 1, characterized in that, The sidewall (340) has an end (341) axially away from the first disc body (310), the plurality of cylindrical pins (350) are disposed on the end (341), and each opening (342) extends axially from the first disc body (310) to the end (341).

3. The scroll compressor according to claim 1, characterized in that, The first vortex (300) further includes a first support shaft (330) that protrudes axially from the first disk body (310) on the side opposite to the first vortex body (320) and the sidewall (340), the first support shaft (330) being supported by a first bearing (410).

4. The scroll compressor according to any one of claims 1-3, characterized in that, The second vortex (500) also includes a second support shaft (530) that protrudes axially from the second disk body (510) on the side opposite to the second vortex body (520), the second support shaft (530) being supported by a second bearing (420).

5. The scroll compressor according to claim 4, characterized in that, Also includes: A retainer (600) includes a retaining sleeve (610) and an outer flange (620) projecting radially outward from the retaining sleeve (610), the retaining sleeve (610) being arranged to surround the second support shaft (530), and each cylindrical pin (350) extending through the second disc (510) and connected to the outer flange (620); and A bearing assembly (700) disposed in the retaining sleeve (610) includes an outer bearing (710) and an inner bearing (720) arranged eccentrically relative to each other, the outer ring of the outer bearing (710) being fixed to the retaining sleeve (610), the inner ring of the inner bearing (720) being fixed to the second support shaft (530), and the outer ring of the inner bearing (720) being fixed to the inner ring of the outer bearing (710).

6. The scroll compressor according to claim 5, characterized in that, The outer flange (620) protrudes outward from the end of the retaining sleeve (610) near the second disc (510); and / or, the bearing assembly (700) further includes an eccentric block (730) for securing the outer ring of the inner bearing (720) to the inner ring of the outer bearing (710); and / or, the outer bearing (710) is an eccentric bearing with an eccentric bore in its inner ring, and the inner bearing (720) is disposed in the eccentric bore.

7. The scroll compressor according to claim 5, characterized in that, The bearing assembly (700) and the second disc (510) are axially spaced apart to define a back pressure chamber (CB) between them, the first vortex body (320) and the second vortex body (520) define a central chamber (C1) at the center, and the second vortex disc (500) is provided with a pressure accumulator (532) communicating the central chamber (C1) and the back pressure chamber (CB).

8. The scroll compressor according to claim 7, characterized in that, The second scroll plate (500) is provided with an exhaust port (531) extending axially through the second support shaft (530) and leading to the central chamber (C1), and the accumulator port (532) extends radially through the second support shaft (530) to communicate the exhaust port (531) with the back pressure chamber (CB); or, the accumulator port (532) extends axially through the second plate body (510) to communicate the central chamber (C1) with the back pressure chamber (CB).

9. The scroll compressor according to claim 7, characterized in that, The first vortex body (320) and the second vortex body (520) further define a plurality of other compression chambers located radially outside the central chamber (C1), and the second vortex disk (500) is provided with a pressure relief hole (512) communicating the back pressure chamber (CB) with one of the plurality of other compression chambers.

10. The scroll compressor according to claim 9, characterized in that, The pressure relief hole (512) extends axially through the second disc (510) to communicate the back pressure chamber (CB) with one of the plurality of other compression chambers.

11. The scroll compressor according to claim 7, characterized in that, It also includes an outer sealing ring (910) held between the outer flange (620) and the second disc (510); and / or, the retainer (600) also includes an inner flange (630) that projects radially inward from the retaining cylinder (610), and the scroll compressor also includes an annular boss (810) that holds the second bearing (420) and an inner sealing ring (920) held between the inner flange (630) and the annular boss (810).

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