Scroll compressor

Abstract

This disclosure discloses a scroll compressor comprising: a housing defining an internal chamber; an isolation plate fixed to the housing and dividing the internal chamber into an intake chamber and an exhaust chamber; a first scroll and a second scroll housed in the intake chamber, the first scroll being configured to rotate about a first axis and including a first scroll body, the second scroll being configured to rotate about a second axis parallel to and offset relative to the first axis and including a second scroll body, the first scroll body and the second scroll body defining a central chamber at their center; an exhaust cover housed in the exhaust chamber, fixed to the isolation plate to define a buffer chamber, and having an exhaust port communicating with the exhaust chamber; and a reed valve mounted on the exhaust cover, configured to open and close the exhaust port, wherein the second scroll has an exhaust orifice communicating with the central chamber, the exhaust orifice extending through the isolation plate and leading to the buffer chamber.

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. This reduces the reliability of the scroll bodies and shortens their service life. 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 and ensure that it only revolves around its axis (i.e., translational revolution), an anti-rotation structure is required. This further increases the weight of the compressor and makes its manufacturing and assembly more complex. Although some existing technologies employ co-rotation techniques where two scrolls rotate around their respective axes to compress the medium, the rotating scrolls exacerbate the wear of the reed valve, reducing its sealing performance. This can prevent the scroll compressor from stably outputting the medium at the desired pressure.

[0003] Therefore, there is an urgent need in this field for a technical solution that can both utilize the advantages of co-rotating scroll compressors and effectively avoid accelerated wear of reed valves. Utility Model Content

[0004] To address the problems in the prior art, this disclosure proposes an improved co-rotating scroll compressor, comprising: a housing defining an internal chamber; a partition plate fixed to the housing and dividing the internal chamber into an intake chamber and an exhaust chamber; a first scroll and a second scroll housed in the intake chamber, the first scroll being configured to rotate about a first axis and including a first scroll body, the second scroll being configured to rotate about a second axis parallel to and offset relative to the first axis and including a second scroll body, the first scroll body and the second scroll body defining a central chamber at their center; an exhaust cover housed in the exhaust chamber, fixed to the partition plate to define a buffer chamber, and having an exhaust port communicating between the buffer chamber and the exhaust chamber; and a reed valve mounted on the exhaust cover, configured to open and close the exhaust port, wherein the second scroll has an exhaust orifice communicating with the central chamber, the exhaust orifice extending through the partition plate and leading to the buffer chamber.

[0005] According to an alternative embodiment of this disclosure, the exhaust cover includes a top and a side portion projecting from the top, the exhaust port is disposed in the top, the reed valve is mounted on the top, and the side portion is fixed to the partition plate to space the reed valve from the second scroll plate.

[0006] According to an alternative embodiment of this disclosure, the exhaust cover has an inner surface for defining the buffer chamber, and includes a layer of sound-absorbing material coated on the inner surface and / or has a plurality of grooves recessed from the inner surface.

[0007] According to an alternative embodiment of this disclosure, the scroll compressor further includes a limiter mounted on the exhaust cover, the limiter being configured to limit the deformation range of the reed valve.

[0008] According to an alternative embodiment of this disclosure, the scroll compressor further includes a motor housed in the intake chamber, the motor including a stator and a rotor spaced apart along the axial direction, the rotor being fixed to the first scroll on the side opposite to the second scroll to drive the first scroll to rotate about the first axis.

[0009] According to an optional embodiment of this disclosure, the first volute further includes a plurality of cylindrical pins protruding along the axial direction and having a plurality of openings extending radially through it, and the second volute also has a plurality of circular holes extending along the axial direction, wherein each cylindrical pin is inserted into a circular hole and has a radial dimension smaller than that of the circular hole, so as to drive the second volute to rotate about the second axis.

[0010] According to an alternative embodiment of this disclosure, the second scroll further includes a second support shaft projecting axially on the side opposite to the second scroll body, the exhaust port extending through the second support shaft, and the second support shaft being arranged to pass through the partition plate and spaced apart from the reed valve.

[0011] 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 circular hole 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.

[0012] According to an optional embodiment of this disclosure, 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.

[0013] According to an optional embodiment of this disclosure, the first scroll further includes a first support shaft protruding axially on the side opposite to the first scroll body, and the scroll compressor further includes a first bearing fixed to the housing and supporting the first support shaft, and a second bearing fixed to the isolation plate and supporting the second support shaft.

[0014] 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

[0015] The accompanying drawings illustrate exemplary embodiments of this disclosure. These drawings should not be construed as necessarily limiting the scope of this disclosure, wherein:

[0016] Figure 1 This is a schematic cross-sectional view of a scroll compressor according to one embodiment of the present disclosure;

[0017] Figure 2 yes Figure 1 A schematic perspective view of the first scroll plate of the scroll compressor shown;

[0018] Figure 3 yes Figure 1 A schematic perspective view of the second scroll plate of the scroll compressor shown;

[0019] 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;

[0020] Figure 5 yes Figure 1 A schematic perspective view of the cage of the scroll compressor shown;

[0021] Figure 6 yes Figure 1 A schematic perspective view of the bearing assembly of the scroll compressor shown.

[0022] Figure 7 yes Figure 6 A schematic front view of the bearing assembly shown;

[0023] Figure 8 This is a schematic cross-sectional view of a scroll compressor according to another embodiment of the present disclosure; and

[0024] Figure 9 This is a schematic cross-sectional view of a scroll compressor according to yet 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 within the housing 100. The motor 200 includes a stator 210 fixed to the housing 100 and a rotor 220 configured to rotate under the drive of a rotating magnetic field generated by the stator 210.

[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 2As 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 a first scroll body 320 and a first support shaft 330 protruding from (i.e., supported by) both sides of the first disk body 310. Specifically, the first scroll body 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, which 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 a second scroll body 520 and a second support shaft 530 protruding from (i.e., supported by) 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, which 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 scroll plate 300 so that the rotor 220 can drive the first scroll plate 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] Specifically, the stator 210 of the motor 200 can be fixed to the housing 100, while the rotor 220 is spaced radially from the stator 210 and fixed to the sidewall 340 of the first scroll 300 radially outside the sidewall 340. That is, the motor 200 can be configured as a radial flux motor, such that the stator 210 and rotor 220 are coupled to each other by magnetic flux located between them in the radial direction. In this configuration, the medium can flow radially outside the two scroll bodies through the gap between the sidewall 340 of the first scroll 300 and the second disk body 510 of the second scroll 500. Of course, in the above embodiment, if the gap between the sidewall 340 and the second disk body 510 is small, the medium may experience a high pressure drop when flowing through this gap, which may adversely affect the operating efficiency of the scroll compressor 10. To solve this problem, such as... Figure 1 As shown, the stator 210 of the motor 200 can be fixed to the housing 100, while the rotor 220 is spaced apart from the stator 210 along the axial direction and 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). In other words, 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, and the first scroll 300 is located in the axial direction between the motor 200 and the second scroll 500. Furthermore, 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 2 Five 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.

[0034] refer to Figure 5 , which shows Figure 1A 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 1 As 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] refer to Figure 9 The illustration shows a schematic cross-sectional view of a scroll compressor according to yet another embodiment of the present disclosure. Figure 9 The implementation methods shown are the same as Figure 1 The embodiments shown are largely the same, with the main difference being that the scroll compressor 10 further includes an exhaust cover 820 disposed in the exhaust chamber 120. This exhaust cover 820 is fixed to the isolation plate 800, such that the exhaust cover 820 and the isolation plate 800 together define a buffer chamber CA, which is in fluid communication with the exhaust port 531 of the second scroll 500. That is, in Figure 9 In the embodiment shown, the vent 531 leads to the buffer chamber CA, rather than as... Figure 1In the illustrated embodiment, the high-pressure medium in the central chamber C1 is directly connected to the exhaust chamber 120, allowing it to be discharged into the buffer chamber CA via the exhaust port 531, rather than directly into the exhaust chamber 120. In this configuration, the buffer chamber CA reduces noise generated by the discharge of the high-pressure medium from the exhaust port 531, thereby improving the NVH performance of the scroll compressor 10. Furthermore, the exhaust cover 820 is provided with an extending exhaust port 821, which provides fluid communication between the buffer chamber CA and the exhaust chamber 120, allowing the high-pressure medium in the buffer chamber CA to be discharged into the exhaust chamber 120 via the exhaust port 821. Specifically, the scroll compressor 10 also includes a reed valve 830 mounted on the exhaust cover 820, which can open and close the exhaust port 821. More specifically, when the pressure difference between the buffer chamber CA and the exhaust chamber 120 reaches a threshold, the reed valve 830 undergoes elastic deformation, thereby opening the exhaust port 821 to allow the high-pressure medium in the buffer chamber CA to be discharged into the exhaust chamber 120. When the pressure difference between the buffer chamber CA and the exhaust chamber 120 is less than the threshold, the elastic restoring force causes the reed valve 830 to return to its original shape, thereby closing the exhaust port 821 to prevent the high-pressure medium in the buffer chamber CA from being discharged into the exhaust chamber 120. With this configuration, the high-pressure medium in the buffer chamber CA can be discharged into the exhaust chamber 120 only after it has reached a certain pressure, which helps the scroll compressor 10 output a high-pressure medium with the desired pressure and stable pressure. Furthermore, it is worth mentioning that the above configuration can also separate the reed valve 830 from the second support shaft 530 by means of the exhaust cover 820. This prevents the second support shaft 530 from wearing the reed valve 830 or causing the reed valve 830 to vibrate during rotation. This ensures that the reed valve 830 can reliably close the exhaust port 821 when the pressure difference between the buffer chamber CA and the exhaust chamber 120 is less than a threshold, thereby helping to build sufficient pressure in the buffer chamber CA before the reed valve 830 opens. Therefore, the above configuration helps to more reliably ensure that the scroll compressor 10 can output a high-pressure medium with the desired pressure and stable pressure.

[0042] Furthermore, such as Figure 9As shown, the exhaust cover 820 has a top 822 and a side 823 protruding axially from the top 822. An exhaust port 821 is disposed in the top 822, and a reed valve 830 is mounted on the top 822. The side 823 is fixed to an isolation plate 800, thereby axially separating the reed valve 830 from the isolation plate 800 and the second support shaft 530. Specifically, the exhaust port 821 is not aligned axially with the exhaust hole 531, but is offset radially relative to the exhaust hole 531. This configuration prevents the high-pressure medium discharged from the exhaust hole 531 from directly impacting the reed valve 830, thus preventing unnecessary vibration of the reed valve 830. This extends the service life of the reed valve 830 and helps prevent pressure fluctuations caused by the high-pressure medium discharged from the scroll compressor 10. Specifically, the exhaust cover 820 also has a layer of sound-absorbing material coated on its inner surface (i.e., the surface used to define the buffer chamber CA), and / or is provided with a plurality of recesses from its inner surface. In this configuration, the exhaust cover 820 can absorb noise generated by the discharge of high-pressure medium from the exhaust port 531 by means of the sound-absorbing material layer and / or the plurality of recesses, thereby further improving the NVH performance of the scroll compressor 10. Specifically, the scroll compressor 10 may also include a limiter 840 mounted on the exhaust cover 820 (more specifically, the top 822), a portion of which is suspended above the reed valve 830, such that the limiter 840 can limit the deformation range of the reed valve 830, in other words, limit the opening degree of the reed valve 830. In this configuration, the limiter 840 can limit the deformation range of the reed valve 830, thereby preventing damage to the reed valve 830 due to excessive deformation, thus improving the reliability of the reed valve 830 and extending its service life.

[0043] 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: The shell (100) that defines the internal chamber; A partition plate (800) is fixed to the housing (100) and divides the internal chamber into an intake chamber (110) and an exhaust chamber (120); A first scroll plate (300) and a second scroll plate (500) are housed in the intake chamber (110). The first scroll plate (300) is configured to rotate about a first axis (X1) and includes a first scroll body (320). The second scroll plate (500) is configured to rotate about a second axis (X2) that is parallel to and offset relative to the first axis (X1) and includes a second scroll body (520). The first scroll body (320) and the second scroll body (520) define a central chamber (C1) at the center. An exhaust cover (820) housed in the exhaust chamber (120), fixed to the partition plate (800) to define a buffer chamber (CA), and provided with an exhaust port (821) communicating the buffer chamber (CA) with the exhaust chamber (120); and A reed valve (830) mounted on the exhaust cover (820) is configured to open and close the exhaust port (821). The second vortex (500) is provided with an exhaust port (531) communicating with the central chamber (C1), and the exhaust port (531) extends through the partition plate (800) and leads to the buffer chamber (CA).

2. The scroll compressor according to claim 1, characterized in that, The exhaust cover (820) includes a top (822) and a side (823) protruding from the top (822), the exhaust port (821) is disposed in the top (822), the reed valve (830) is mounted on the top (822), and the side (823) is fixed to the partition plate (800) to space the reed valve (830) from the second scroll plate (500).

3. The scroll compressor according to claim 1 or 2, characterized in that, The exhaust cap (820) has an inner surface for defining the buffer chamber (CA) and includes a layer of sound-absorbing material coated on the inner surface and / or has a plurality of grooves recessed from the inner surface.

4. The scroll compressor according to claim 1 or 2, characterized in that, It also includes a limiter (840) mounted on the exhaust cover (820), the limiter (840) being configured to limit the deformation range of the reed valve (830).

5. The scroll compressor according to claim 1 or 2, characterized in that, It also includes a motor (200) housed in the intake chamber (110), the motor (200) including a stator (210) and a rotor (220) spaced apart along the axial direction, the rotor (220) being fixed to the first scroll plate (300) on the side opposite to the second scroll plate (500) to drive the first scroll plate (300) to rotate about the first axis (X1).

6. The scroll compressor according to claim 5, characterized in that, The first scroll (300) further includes a plurality of cylindrical pins (350) protruding along the axial direction and having a plurality of openings (342) extending through it in the radial direction. The second scroll (500) also has a plurality of circular holes (511) extending along the axial direction, wherein each cylindrical pin (350) is inserted into a circular hole (511) and has a radial dimension smaller than that of the circular hole (511) to drive the second scroll (500) to rotate about the second axis (X2).

7. The scroll compressor according to claim 6, characterized in that, The second scroll (500) also includes a second support shaft (530) projecting axially on the side opposite to the second scroll body (520), the exhaust port (531) extending through the second support shaft (530), and the second support shaft (530) being arranged to pass through the partition plate (800) and spaced apart from the reed valve (830).

8. The scroll compressor according to claim 7, 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 circular hole (511) and connecting 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).

9. The scroll compressor according to claim 8, characterized in that, The bearing assembly (700) further includes an eccentric block (730) for fixing 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 hole in its inner ring, and the inner bearing (720) is disposed in the eccentric hole.

10. The scroll compressor according to claim 8, characterized in that, The first scroll (300) further includes a first support shaft (330) that protrudes axially on the side opposite to the first scroll body (320), and the scroll compressor further includes a first bearing (410) fixed to the housing (100) and supporting the first support shaft (330) and a second bearing (420) fixed to the isolation plate (800) and supporting the second support shaft (530).

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