Scroll compressor
By setting sealing grooves and sealing strips on the moving scroll of the scroll compressor, the problems of media leakage and wear caused by axial clearance are solved, achieving high volumetric efficiency and low wear while eliminating clearance.
Patent Information
- Application Number
- CN202410816675.7
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2024-06-24
- Publication Date
- 2025-12-26
AI Technical Summary
Existing scroll compressors suffer from axial clearance between the moving and stationary scrolls, leading to media leakage and wear, which affects volumetric efficiency. Existing back pressure technology further exacerbates wear and media consumption.
A sealing groove and sealing strip are set on the moving scroll. The sealing strip automatically closes and builds back pressure when there is axial clearance, eliminating the clearance. When there is no clearance, it isolates the back pressure to avoid unnecessary wear and media loss.
While eliminating axial clearance, it maintains high volumetric efficiency, avoids wear and media consumption, and achieves a balance between the moving and stationary scrolls.
Smart Images
Figure CN121205931A_ABST
Abstract
Description
Technical Field
[0001] This disclosure relates to the field of compressor technology, and more specifically, to a scroll compressor. Background Technology
[0002] Current improvements to scroll compressors primarily focus on increasing suction capacity and improving volumetric efficiency. Existing scroll compressors often use a moving scroll and a stationary scroll to compress the medium. This results in a pressure imbalance between the moving scroll on the working chamber side and the drive assembly side. This pressure imbalance leads to axial movement of the moving scroll, which not only increases noise and wear during operation but also creates an axial gap between the moving and stationary scrolls. This gap provides a path for the medium to leak from the high-pressure working chamber to the low-pressure working chamber, thus reducing the volumetric efficiency of the scroll compressor. To address this, existing technologies utilize high-pressure medium to create back pressure on the drive assembly side of the moving scroll to eliminate the axial gap. However, this back pressure exists even when there is no axial gap between the moving and stationary scrolls, unnecessarily increasing the contact pressure between them. This exacerbates wear and leads to unnecessary consumption of the high-pressure medium, further reducing volumetric efficiency.
[0003] Therefore, there is an urgent need in this field for a technical solution that can achieve a better balance between eliminating axial clearance and maintaining volumetric efficiency, or even both. Summary of the Invention
[0004] To address the problems in the prior art, this disclosure proposes an improved scroll compressor, comprising: a stationary scroll, the stationary scroll including a stationary scroll body and a stationary scroll body protruding from the stationary scroll body; and a moving scroll, the moving scroll including a moving scroll body and a moving scroll body protruding from the moving scroll body and cooperating with the stationary scroll body, the moving scroll body having a bottom surface away from the moving scroll body, and the moving scroll body having a top surface away from the moving scroll body; wherein the moving scroll is provided with a sealing groove recessed from the top surface and a through hole extending from the bottom wall of the sealing groove to the bottom surface, and further includes a sealing strip accommodated in the sealing groove, the inner end of the sealing strip defining an end gap and a bottom gap with the inner end wall and the bottom wall of the sealing groove, respectively.
[0005] This disclosure may be embodied in the illustrative embodiments shown in the accompanying drawings. However, it should be noted that the drawings are merely illustrative, and any variations contemplated under the teachings of this disclosure should be considered to be included within the scope of this disclosure. Attached Figure Description
[0006] The accompanying drawings illustrate exemplary embodiments of this disclosure. These drawings should not be construed as necessarily limiting the scope of this disclosure, wherein:
[0007] Figure 1 This is a schematic cross-sectional view of a scroll compressor according to one embodiment of the present disclosure;
[0008] Figure 2 yes Figure 1 A schematic top view of the moving scroll of a scroll compressor without a sealing strip;
[0009] Figure 3A It is along Figure 2 A schematic partial cross-sectional view of the moving vortex disk, taken from line AA in the diagram;
[0010] Figure 3B It is along Figure 2 A schematic cross-sectional view of the moving vortex disk taken from line BB in the diagram;
[0011] Figure 4 yes Figure 1 A schematic top view of the moving scroll of a scroll compressor with a sealing strip;
[0012] Figure 5A It is along Figure 4 A schematic partial cross-sectional view of the moving vortex disk, taken from line AA in the diagram;
[0013] Figure 5B It is along Figure 4 A schematic cross-sectional view of the moving vortex disk taken from line BB in the diagram;
[0014] Figure 6 This is a schematic top view of a scroll compressor with a sealing strip according to another embodiment of the present disclosure;
[0015] Figure 7 It is along Figure 6 A schematic partial cross-sectional view of the moving vortex disk, taken from line AA in the diagram;
[0016] Figure 8 This is a schematic top view of a scroll compressor without a sealing strip according to another embodiment of the present disclosure;
[0017] Figure 9 It is along with a sealing strip Figure 8 A schematic cross-sectional view of the moving vortex disk taken from line BB in the diagram;
[0018] Figure 10 This is a schematic top view of a scroll compressor without a sealing strip according to another embodiment of the present disclosure; and
[0019] Figure 11 It is along with a sealing strip Figure 10 A schematic cross-sectional view of the moving vortex disk taken from line BB in the diagram. Detailed Implementation
[0020] 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.
[0021] This disclosure aims to provide a scroll compressor with a novel design. Through this novel design, during operation, when an axial clearance occurs between the moving and stationary scrolls, the working chamber and the back pressure chamber are automatically connected. This allows the high-pressure medium in the working chamber to enter the back pressure chamber, thereby generating back pressure in the back pressure chamber to help eliminate the axial clearance. This reliably prevents axial leakage of the medium (e.g., refrigerant) due to the axial clearance. Specifically, through this novel design, during operation, when there is no axial clearance between the moving and stationary scrolls, the working chamber and the back pressure chamber are also automatically isolated. This prevents the generation of undesirable back pressure in the back pressure chamber, thus avoiding increased contact pressure between the moving and stationary scrolls due to undesirable back pressure, which would exacerbate wear on both, and also prevents a reduction in the volumetric efficiency of the scroll compressor due to the loss of high-pressure medium. More specifically, through the novel design of this scroll compressor, a certain level of back pressure can be maintained in the working chamber during operation. This back pressure helps prevent axial clearance between the moving and stationary scrolls, while ensuring that the back pressure is not large enough to significantly exacerbate wear on the moving and stationary scrolls or reduce the volumetric efficiency of the scroll compressor. In other words, the scroll compressor according to this disclosure can automatically eliminate axial clearance between the moving and stationary scrolls during operation, while simultaneously considering wear on the moving and stationary scrolls and the volumetric efficiency of the scroll compressor, and also preventing axial clearance from forming between the moving and stationary scrolls.
[0022] Various alternative, but non-limiting, embodiments of the scroll compressor according to this disclosure are described in detail below with reference to the accompanying drawings. However, it should be noted that, as used in this disclosure, the terms "axial direction," "radial direction," "circumferential direction," etc., have their usual meanings in the art. Specifically, the axial direction can be a direction parallel to or coincident with the axis of rotation of the main shaft of the scroll compressor; that is, the axial direction can be defined by the axis of rotation of the main shaft. The radial direction can be any direction perpendicular to the axial direction; and the circumferential direction can be any direction surrounding the axial direction.
[0023] 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 generally includes a housing 100 and a stationary scroll 200, a moving scroll 300, a motor 400, and a transmission assembly 500 housed in the housing 100.
[0024] A stationary scroll 200 is fixedly disposed within the housing 100 and includes a stationary scroll body 210 and a stationary scroll body 220 protruding from the stationary scroll body 210 along an axial direction XX', wherein the stationary scroll body 220 extends from the center of the stationary scroll body 210 toward the periphery of the stationary scroll body 210 along an involute or in an involute shape. A moving scroll 300 is movably disposed within the housing 100 and includes a moving scroll body 310 and a moving scroll body 320 protruding from the moving scroll body 310 along an axial direction XX', wherein the moving scroll body 320 extends from the center of the moving scroll body 310 toward the periphery of the moving scroll body 310 along an involute or in an involute shape. The stationary volute 220 of the stationary volute 200 and the moving volute 320 of the moving volute 300 are arranged facing each other, such that the stationary volute 220 is oriented to protrude from the stationary volute 210 toward the moving volute 310, while the moving volute 320 is oriented to protrude from the moving volute 310 toward the stationary volute 210. Furthermore, the sidewalls of the stationary volute 220 and the moving volute 320 can engage with each other, thereby defining a plurality of working chambers distributed along an involute curve between them.
[0025] The motor 400 includes a stator 410 fixedly disposed in the housing 100 and a rotor 420 rotatably disposed in the housing 100. The rotor 420 can rotate about the axial direction XX' under the drive of the rotating magnetic field generated after the stator 410 is energized. The transmission assembly 500 includes a main shaft 510, a transition shaft 520, and an eccentric shaft 530 connecting the transition shaft 520 to the main shaft 510. The main shaft 510 can be non-rotatably connected to the rotor 420, for example by welding, bolts, keyways, etc., so that the main shaft 510 can rotate together with the rotor 420 about the axial direction XX'. The transition shaft 520 is connected to the moving scroll 300, for example, via a bearing 610. The moving scroll 300 may have a bearing seat 380 on the side of the moving scroll body 310 opposite to the moving scroll body 320. The bearing 610 can be received in the bearing seat 380, and the transition shaft 520 can be inserted into the bearing 610. Furthermore, the eccentric shaft 530 can be inserted into the main shaft 510 in a fixed and eccentric manner relative to the main shaft 510, and also inserted into the adapter shaft 520 in a rotatable and eccentric manner relative to the adapter shaft 520, so that the adapter shaft 520 is connected to the main shaft 510 in an eccentric and rotatable manner relative to the main shaft 510. In this configuration, the rotation of the main shaft 510 about the axial direction XX' is converted into the revolution of the adapter shaft 520 about the axial direction XX', and the revolution of the adapter shaft 520 about the axial direction XX' is further converted into the revolution of the moving scroll 300 about the axial direction XX'. Of course, in order to suppress the rotational tendency of the moving scroll 300, the scroll compressor 10 may also include an anti-rotation structure acting on the moving scroll 300 to ensure that the moving scroll 300 revolves or translates about the axial direction XX' without rotating on its own axis.
[0026] In the above configuration, the motor 400 can drive the main shaft 510 to rotate after being powered on. The main shaft 510 can then drive the moving scroll 300 to revolve via the eccentric shaft 530, the adapter shaft 520, and the bearing 610. As the moving scroll 300 revolves, each of the multiple working chambers confined between the sidewalls of the stationary scroll 220 and the moving scroll 320 will move along an involute from the periphery of the stationary scroll 220 and the moving scroll 320 toward their center. The working chamber that moves to the center of the stationary scroll 220 and the moving scroll 320 will disappear, and a new working chamber will be generated on the periphery of the stationary scroll 220 and the moving scroll 320. The volume of each working chamber will gradually decrease as the above movement occurs. Therefore, during the operation of the scroll compressor 10, the medium (e.g., air, nitrogen, or refrigerant such as R22 or HFC) can enter the working chamber from the periphery of the stationary scroll 220 and the moving scroll 320, then be transported and compressed by the working chamber toward the center of the two, and finally discharged from the working chamber at the center of the two (e.g., through the exhaust port 211 provided in the stationary scroll 210). As the moving scroll 300 continuously revolves, the medium can be continuously transported, compressed, and discharged in the above manner.
[0027] As mentioned earlier, the pressure in each working chamber distributed along the involute curve is different. Specifically, the pressure in the working chamber closer to the center of the stationary scroll 220 and the moving scroll 320 is higher, and vice versa. To prevent the medium in the high-pressure working chamber from leaking into the low-pressure working chamber through the axial gap between the stationary scroll 200 and the moving scroll 300 (this leakage can be called axial leakage), it is necessary to maintain contact between the moving scroll 320 and the stationary scroll 210 to eliminate the axial gap between them, and to ensure contact between the stationary scroll 220 and the moving scroll 310 to eliminate the axial gap between them. In fact, since the height of the stationary scroll 220 is the same as the height of the moving scroll 320, the above two axial gaps are generated simultaneously and can be eliminated simultaneously. Therefore, for the sake of simplicity, the above two axial gaps are collectively referred to as the axial gap between the stationary scroll 200 and the moving scroll 300. However, the pressure in each working chamber tends to push the stationary scroll 200 and the moving scroll 300 away from each other, thereby creating an axial clearance between them. Therefore, this disclosure proposes the following technical solution to eliminate the axial clearance between the stationary scroll 200 and the moving scroll 300.
[0028] refer to Figures 2-3B ,in, Figure 2 It shows Figure 1 The diagram shows a schematic top view of a scroll compressor without a sealing strip, showing the moving scroll. Figure 3A It shows along Figure 2A schematic partial cross-sectional view of the moving vortex disk, taken from line AA in the diagram, and Figure 3B It shows along Figure 2 A schematic cross-sectional view of the moving vortex disk taken from line BB. (See diagram below.) Figures 1-3B As shown, the moving vortex body 320 has an inner end portion 321 near the center of the moving disk body 310 and an outer end portion 322 near the periphery of the moving disk body 310, and extends from the inner end portion 321 to the outer end portion 322 along an involute or in the form of an involute. Additionally, the moving scroll 320 also has a top surface 323 extending axially away from the moving disk 310 and intended to contact the stationary disk 210. The moving scroll 300 also has a sealing groove 330 recessed from the top surface 323 of the moving scroll 320. This sealing groove 330 has an inner end wall 331 near the inner end portion 321 of the moving scroll 320 (i.e., near the center of the moving disk 310) and an outer end wall 332 near the outer end portion 322 of the moving scroll 320 (i.e., near the periphery of the moving disk 310), or is defined between the inner end wall 331 and the outer end wall 332, and extends along an involute or in the form of an involute from the inner end wall 331 to the outer end wall 332. Of course, as... Figure 2 As shown, the sealing groove 330 does not necessarily extend along the entire length of the moving vortex body 320 from the inner end 321 to the outer end 322. That is, the inner end wall 331 may be spaced apart from the inner end 321, and the outer end wall 332 may be spaced apart from the outer end 322.
[0029] like Figure 2 and Figure 3A As shown, the sealing groove 330 is recessed from the top surface 323 along the axial direction XX' and terminates at the bottom wall 333. A portion of the bottom wall 333 of the sealing groove 330 is further recessed near the inner end wall 331, thereby forming an auxiliary groove 340 near the inner end wall 331. That is, the auxiliary groove 340 can be constituted by a locally deepened portion of the sealing groove 330, or can be considered as a locally deepened portion of the sealing groove 330, which has a greater depth relative to the rest of the sealing groove 330. This depth can be the distance between the bottom wall of the locally deepened portion measured along the axial direction XX' or between the bottom wall 333 of the sealing groove 330 and the top surface 323. Specifically, as... Figure 2 and Figure 3A As shown, the auxiliary groove 340 is arranged adjacent to the inner end wall 331 of the sealing groove 330, such that the auxiliary groove 340 is partially defined by the inner end wall 331. Of course, this is merely illustrative; in embodiments not shown, the auxiliary groove 340 may also be spaced apart from the inner end wall 331, such that a portion of the bottom wall 333 is located between the auxiliary groove 340 and the inner end wall 331.
[0030] like Figure 2 and Figure 3B As shown, the moving disk body 310 has a bottom surface 311 on the side opposite to the moving vortex body 320 (this side can be simply referred to as the rear side of the moving disk body 310 or the moving vortex 300), which is away from the moving vortex body 320. That is, the bottom surface 311 faces away from the moving vortex body 320, i.e., it is opposite to the moving vortex body 320. The moving scroll 300 also has a through hole 350 extending from the bottom wall 333 of the sealing groove 330 of the moving scroll 320 through the moving scroll 320 and the moving disk body 310 to the bottom surface 311 of the moving disk body 310. That is, the through hole 350 opens at one end to the sealing groove 330 or has an opening on the bottom wall 333 of the sealing groove 330, and at the other end opens to the rear side of the moving disk body 310 or has an opening on the bottom surface 311 of the moving disk body 310, so that the through hole 350 can provide fluid communication between the sealing groove 330 and the rear side of the moving scroll 300. Specifically, as... Figure 2 As shown, the through hole 350 is spaced apart from the auxiliary groove 340, meaning that the through hole 350 leads to the bottom wall 333 of the sealing groove 330, rather than a locally deepened portion of the sealing groove 330. Specifically, as... Figure 3B As shown, the through-hole 350 extends along a straight path from the bottom wall 333 of the sealing groove 330 to the bottom surface 311 of the moving disc body 310, thereby reducing the pressure loss of the high-pressure medium in the through-hole 350 and thus helping to efficiently establish back pressure. Of course, this is only illustrative, and in embodiments not shown, the through-hole 350 may also extend along a bent, curved, or other shaped path.
[0031] Continue to refer to Figures 4-5B ,in, Figure 4 It shows Figure 1 The diagram shows a schematic top view of the moving scroll of a scroll compressor with a sealing strip. Figure 5A It shows along Figure 4 A schematic partial cross-sectional view of the moving vortex disk, taken from line AA in the diagram, and Figure 5B It shows along Figure 4 A schematic cross-sectional view of the moving vortex disk taken from line BB. (See diagram below.) Figure 1 and Figures 4-5B As shown, the moving scroll 300 also includes a sealing strip 360 housed in a sealing groove 330. The sealing strip 360 has an inner end portion 361 near the inner end wall 331 of the sealing groove 330 and an outer end portion 362 near the outer end wall 332 of the sealing groove 330, and is arranged to extend from the inner end portion 361 to the outer end portion 362 along an involute or in the form of an involute. Further, as... Figure 4 and Figure 5AAs shown, the inner end portion 361 of the sealing strip 360 is spaced apart from the inner end wall 331 of the sealing groove 330, thereby forming an end gap G1 between the inner end portion 361 and the inner end wall 331 of the sealing groove 330, leading to the top surface 323 of the moving vortex body 320. Furthermore, the inner end portion 361 of the sealing strip 360 is also spaced apart from the bottom wall 333 of the sealing groove 330, thereby forming a bottom gap G2 in fluid communication with the aforementioned end gap G1 between the inner end portion 361 and the bottom wall 333 (i.e., below the inner end portion 361). Specifically, as... Figure 2 and Figure 5B As shown, the opening of the through hole 350 on the bottom wall 333 is spaced apart from the bottom gap G2, so that the sealing strip 360 can contact the bottom wall 333 of the sealing groove 330 at the through hole 350, thereby covering the through hole 350 and closing the opening of the through hole 350 on the bottom wall 333. More specifically, as Figure 5B As shown, the sealing strip 360 and the sealing groove 330 are sized and shaped such that the sealing strip 360 completely fills the sealing groove 330 between the bottom gap G2 and the opening of the through hole 350 on the bottom wall 333, so that when the moving vortex body 320 contacts the fixed plate body 210, the sealing strip 360 can prevent the high-pressure medium from flowing from the bottom gap G2 to the through hole 350, thereby completely closing the opening of the through hole 350 on the bottom wall 333. More specifically, the sealing strip 360 can completely fill the sealing groove 330 between the bottom gap G2 and its outer end 362. In particular, as Figure 2 As shown, the length of the sealing groove 330 between the bottom gap G2 and the opening of the through hole 350 on the bottom wall 333 (e.g., measured along the involute) is less than 1 / 2, 1 / 5, or 1 / 10 of the total length of the sealing groove 330, so that the opening of the through hole 350 on the bottom wall 333, although spaced apart from the bottom gap G2, is still close to the bottom gap G2.
[0032] In this configuration, during operation of the scroll compressor 10, on the one hand, when an axial clearance is generated between the stationary scroll 200 and the moving scroll 300 (this axial clearance is generated, for example, due to the pressure exerted on the stationary scroll 200 and the moving scroll 300 by the medium in each working chamber), since the end gap G1 is positioned near the inner end 321 of the moving scroll 320, the high-pressure medium in the working chamber near the center of the moving scroll 320 can flow through the end gap G1 to the bottom gap G2, and then apply pressure to the lower part of the inner end 361 of the sealing strip 360. This pressure can then... The end 361 is raised, which causes an additional gap to be generated between the sealing strip 360 and the bottom wall 333 of the sealing groove 330. The high-pressure medium will flow into the additional gap and further raise the sealing strip 360, so that the additional gap gradually expands along the length of the sealing strip 360. The high-pressure medium can gradually flow to the bottom of the entire sealing strip 360, thereby raising the entire sealing strip 360 until the sealing strip 360 abuts against the stationary disc 210. The sealing strip 360 abutting against the stationary disc 210 can seal the axial gap between the stationary volute 200 and the moving volute 300, thereby preventing axial leakage. During the aforementioned process where the sealing strip 360 is gradually lifted from the bottom gap G2 by the high-pressure medium, when the additional gap reaches the through hole 350, the sealing strip 360, being lifted, cannot cover the through hole 350 and thus opens the through hole 350. This allows a portion of the high-pressure medium to flow through the through hole 350 to the rear side of the moving scroll 300, establishing back pressure on the rear side of the moving scroll 300. This back pressure pushes the moving scroll 300 toward the stationary scroll 200, thereby eliminating the axial gap between the stationary scroll 200 and the moving scroll 300. Therefore, the scroll compressor 10 according to this disclosure can automatically close and eliminate the axial gap after it is generated between the stationary scroll 200 and the moving scroll 300, thereby automatically preventing axial leakage. Furthermore, since the through-hole 350 is located before the outer end wall 332 of the sealing groove 330, especially when the through-hole 350 is close to the bottom gap G2, the aforementioned back pressure can be established before the entire sealing strip 360 is lifted. This allows the axial clearance to be eliminated before the entire sealing strip 360 is lifted, thus preventing the high-pressure medium from flowing under the entire sealing strip 360. Therefore, the scroll compressor 10 according to this disclosure can reduce the use of high-pressure medium in addition to automatically sealing and eliminating axial clearance, thereby maintaining high volumetric efficiency. On the other hand, when no axial clearance is generated between the stationary scroll 200 and the moving scroll 300, the sealing strip 360 can cover the through-hole 350, thereby preventing the high-pressure medium from leaking through the through-hole 350 to the rear side of the moving scroll 300. This also maintains high volumetric efficiency and avoids the establishment of undesirable back pressure on the rear side of the moving scroll 300, which would lead to accelerated wear of the stationary scroll 200 and the moving scroll 300.In short, the scroll compressor according to this disclosure can automatically close and eliminate axial clearance when it is generated while maintaining high volumetric efficiency, and can also maintain high volumetric efficiency and avoid accelerated wear of stationary and moving scrolls when no axial clearance is generated.
[0033] In particular, such as Figure 4 and Figure 5A As shown, the inner end 361 of the sealing strip 360 is suspended above the auxiliary groove 340, such that a portion of the auxiliary groove 340 is located below the sealing strip 360, forming a bottom gap G2 in the auxiliary groove 340, while the other portion of the auxiliary groove 340 connects to the top surface 323 of the moving vortex body 320 through the end gap G1. That is, the sealing strip 360 only covers a portion of the auxiliary groove 340, forming the bottom gap G2, leaving the other portion of the auxiliary groove 340 uncovered, allowing the bottom gap G2 to fluidly communicate with the end gap G1 through this other portion. More specifically, as... Figure 4 and Figure 5A As shown, the auxiliary groove 340 is adjacent to the inner end wall 331 of the sealing groove 330. Therefore, as long as the inner end 361 of the sealing strip 360 is spaced apart from the inner end wall 331 of the sealing groove 330, an end gap G1 can be formed between the inner end 361 and the inner end wall 331, and a bottom gap G2 can be formed below the inner end 361. In this configuration, the bottom gap G2 can be formed simply by machining the auxiliary groove 340 at the inner end wall 331 of the sealing groove 330, without requiring special machining of the sealing strip 360, thereby reducing the configuration cost of the moving scroll 300.
[0034] Specifically, refer to Figure 6 and Figure 7 ,in, Figure 6 A schematic top view of a scroll compressor with a sealing strip according to another embodiment of the present disclosure is shown. Figure 7 It shows along Figure 6 A schematic partial cross-sectional view of the moving vortex disk, taken from line AA. (See diagram below.) Figure 6 and Figure 7 As shown, the sealing strip 360 thins at its inner end 361, meaning that the sealing strip 360 has a thinned portion at its inner end 361. The thickness of this thinned portion is less than the thickness of the rest of the sealing strip 360, so that the inner end 361 is spaced apart from the bottom wall 333 of the sealing groove 330, thereby forming a bottom gap G2 between the inner end 361 and the bottom wall 333. Therefore, Figure 6 and Figure 7 The implementation methods shown are the same as Figures 2-5BThe difference in the illustrated embodiment is that the bottom gap G2 is formed by the thinning portion of the sealing strip 360, rather than by the auxiliary groove 340. In this configuration, the bottom gap G2 can be formed simply by machining the thinning portion at the inner end 361 of the sealing strip 360, without requiring special machining of the bottom wall 333 of the sealing groove 330, thereby reducing the configuration cost of the moving scroll 300. Of course, in Figure 6 and Figure 7 In the embodiment shown, the auxiliary groove 340 may also be present so as to form a bottom gap G2 together with the thinned portion of the sealing strip 360.
[0035] Specifically, refer to Figure 8 and Figure 9 ,in, Figure 8 A schematic top view of a scroll compressor without a sealing strip according to another embodiment of the present disclosure is shown. Figure 9 It shows the edge with a sealing strip Figure 8 A schematic cross-sectional view of the moving vortex disk taken from line BB in the diagram. Figure 8 and Figure 9 The implementation methods shown are the same as Figures 1-7 The difference in the illustrated embodiment is that the moving scroll 300 also has an auxiliary groove 370 recessed from the bottom wall 333 of the sealing groove 330. This auxiliary groove 370 extends from the bottom gap G2 (specifically, the auxiliary recess 340) along the sealing groove 330 toward the outer end wall 332 of the sealing groove 330. That is, the auxiliary groove 370 opens to the bottom gap G2 at one end and extends from this end along an involute or involute pattern in the bottom wall 333 of the sealing groove 330 toward the outer end wall 332 of the sealing groove 330. In this configuration, the high-pressure medium flowing through the end gap G1 to the bottom gap G2 can further flow into the auxiliary groove 370 and be rapidly guided by the auxiliary groove 370 to below the sealing strip 360, so that the high-pressure medium can apply pressure to the sealing strip 360 in the auxiliary groove 370, which helps to ensure the successful lifting of the sealing strip 360. Therefore, compared with... Figures 1-7 Compared to the configuration shown, Figure 8 and Figure 9 The configuration shown can more reliably ensure that the sealing strip 360 is lifted to close the axial gap when it is generated by the auxiliary groove 370. In particular, when the sealing strip 360 is bonded to the sealing groove 330 by lubricating oil, the auxiliary groove 370 can also reduce the contact area between the sealing strip 360 and the bottom wall 333, so as to reduce the resistance encountered when the sealing strip 360 is lifted.
[0036] In particular, such as Figure 8As shown, the auxiliary groove 370 extends from the bottom gap G2 to the outer end wall 332 of the sealing groove 330. In this configuration, the high-pressure medium can be guided through the auxiliary groove 370 to the underside of the entire sealing strip 360, thereby more reliably ensuring the lifting of the sealing strip 360. Specifically, as... Figure 8 and Figure 9 As shown, the sealing groove 330 also has two sidewalls 334 or is defined between two sidewalls 334, which are radially opposite each other and connected by an inner end wall 331 and an outer end wall 332. The moving scroll 300 is provided with two auxiliary grooves 370, each adjacent to a sidewall 334 so as to extend along that sidewall 334. In this configuration, the two auxiliary grooves 370 are arranged substantially symmetrically on both sides of the sealing strip 360, such that the high-pressure medium in the two auxiliary grooves 370 applies substantially the same pressure to the sealing strip 360, thereby only lifting the sealing strip 360 without causing it to twist. Specifically, as... Figure 8 As shown, the auxiliary groove 370 is spaced apart from the through hole 350 so that the through hole 350 only leads to the bottom wall 333 of the sealing groove 330, but not to the auxiliary groove 370. In this configuration, the sealing strip 360 can still prevent the high-pressure medium in the bottom gap G2 from flowing to the through hole 350 when the moving scroll body 320 contacts the fixed plate body 210, thereby maintaining the high volumetric efficiency of the scroll compressor 10.
[0037] Specifically, refer to Figure 10 and Figure 11 ,in, Figure 10 A schematic top view of a scroll compressor without a sealing strip according to another embodiment of the present disclosure is shown. Figure 11 It shows the edge with a sealing strip Figure 10 A schematic cross-sectional view of the moving vortex disk taken from line BB in the diagram. Figure 10 and Figure 11 The implementation methods shown are the same as Figure 8 and Figure 9The difference in the illustrated embodiment is that the through hole 350 intersects with the auxiliary groove 370, so that the through hole 350 leads to both the sealing groove 330 and the auxiliary groove 370. In other words, the through hole 350 has openings on both the bottom wall 333 of the sealing groove 330 and the bottom wall 371 of the auxiliary groove 370. In this configuration, since the sealing strip 360 can only cover the opening of the through hole 350 on the bottom wall 333 of the sealing groove 330 but cannot cover the opening of the through hole 350 on the bottom wall 371 of the auxiliary groove 370, even if the sealing strip 360 is not lifted, the high-pressure medium entering the bottom gap G1 can enter the through hole 350 through the opening of the through hole 350 on the bottom wall 371 of the auxiliary groove 370, thereby establishing a certain degree of back pressure on the rear side of the moving scroll 300. Therefore, the above configuration helps to maintain a certain degree of back pressure on the rear side of the moving scroll 300 to prevent the generation of axial clearance. Of course, since the through hole 350 only partially leads to the auxiliary groove 370, the back pressure established in the above manner is limited and will not cause significant aggravation of wear on the stationary scroll plate 200 and the moving scroll plate 300, nor will it cause a significant decrease in volumetric efficiency. In particular, when the moving scroll plate 300 is provided with two or more auxiliary grooves 370, the through hole 350 can intersect with any one or any number of auxiliary grooves 370.
[0038] Specifically, returning Figure 1 A back pressure chamber 710 is formed on the rear side of the moving disc body 310. This back pressure chamber 710 is in fluid communication with the through hole 350, that is, the through hole 350 leads to the back pressure chamber 710 at the bottom surface 311 of the moving disc body 310. More specifically, the end of the adapter shaft 520 is spaced apart from the bottom surface 311 of the stationary disc body 310, so that the back pressure chamber 710 is defined in the bearing housing 380 by the inner surface of the bearing 610, the bottom surface 311 of the stationary disc body 310, and the end of the adapter shaft 520. In this configuration, the back pressure chamber 710 has a small volume, so a small amount of high-pressure medium is sufficient to establish enough back pressure in the back pressure chamber 710. This reduces the amount of high-pressure medium used to establish back pressure, thereby helping to maintain the high volumetric efficiency of the scroll compressor 10. Furthermore, the back pressure chamber 710 is largely closed, which prevents the high-pressure medium from leaking out of the back pressure chamber 710, thus helping to maintain the back pressure in the back pressure chamber 710.
[0039] 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, comprising: A stationary vortex disk (200), the stationary vortex disk (200) comprising a stationary disk body (210) and a stationary vortex body (220) protruding from the stationary disk body (210); and A moving scroll (300) includes a moving scroll body (310) and a moving scroll body (320) protruding from the moving scroll body (310) and cooperating with the stationary scroll body (220). The moving scroll body (310) has a bottom surface (311) away from the moving scroll body (320), and the moving scroll body (320) has a top surface (323) away from the moving scroll body (310). The moving scroll (300) is provided with a sealing groove (330) recessed from the top surface (323) and a through hole (350) extending from the bottom wall (333) of the sealing groove (330) to the bottom surface (311). It also includes a sealing strip (360) housed in the sealing groove (330). The inner end (361) of the sealing strip (360) defines an end gap (G1) and a bottom gap (G2) with the inner end wall (331) and the bottom wall (333) of the sealing groove (330), respectively.
2. The scroll compressor according to claim 1, wherein, The through hole (350) is spaced apart from the bottom gap (G2) and the end gap (G1).
3. The scroll compressor according to claim 2, wherein, The sealing strip (360) completely fills the space in the sealing groove (330) except for the end gap (G1) and the bottom gap (G2), and covers the through hole (350).
4. The scroll compressor according to any one of claims 1-3, wherein, The sealing groove (330) also includes an auxiliary groove (340) recessed from the bottom wall (333) for forming the bottom gap (G2).
5. The scroll compressor according to claim 4, wherein, The auxiliary groove (340) is adjacent to the inner end wall (331) such that the auxiliary groove (340) is partially defined by the inner end wall (331); or, the auxiliary groove (340) is spaced apart from the inner end wall (331).
6. The scroll compressor according to any one of claims 1-5, wherein, The sealing strip (360) thins at the inner end (361) to form the bottom gap (G2).
7. The scroll compressor according to any one of claims 1-6, wherein, The moving scroll (300) is also provided with an auxiliary groove (370) recessed from the bottom wall (333), and the auxiliary groove (370) is connected to the bottom gap (G2).
8. The scroll compressor according to claim 7, wherein, The auxiliary groove (370) extends from the bottom gap (G2) to the outer end wall (332) of the sealing groove (330).
9. The scroll compressor according to claim 7 or 8, wherein, The through hole (350) is spaced apart from the auxiliary groove (370); or the through hole (350) intersects with the auxiliary groove (370).
10. The scroll compressor according to any one of claims 7-9, wherein, The sealing groove (330) has two sidewalls (334) opposite to each other, and the moving scroll (300) is provided with two auxiliary grooves (370), each auxiliary groove (370) being adjacent to a sidewall (334) and extending along the sidewall (334).
11. The scroll compressor according to any one of claims 1-10, wherein, The scroll compressor (10) is provided with a back pressure chamber (710) which communicates with the through hole (350) and is partially defined by the bottom surface (311).
12. The scroll compressor according to claim 11, wherein, The moving scroll (300) has a bearing housing (380) for accommodating the bearing on the bottom surface (311), and the back pressure chamber (710) is located in the bearing housing (380).