An eccentric sleeve and a scroll compressor

Abstract

This invention discloses an eccentric sleeve and a scroll compressor. The eccentric sleeve includes a shaft portion and an edge portion. The edge portion includes a front end edge and a rear end edge disposed radially on the shaft portion. The edge portion is formed by the front end edge extending around the edge of the shaft portion towards the rear end edge. The front end edge and / or the rear end edge are at least partially tangential. By implementing this invention, the front end edge and rear end edge are designed with tangential structures. When the eccentric sleeve rotates, the tangential structures of the front end edge and rear end edge cause them to be tangential to the refrigerant oil. The small contact area between the front end edge and the refrigerant oil greatly reduces the agitation of the refrigerant oil, reduces the generation of eddies, lowers the compressor's power consumption, and thus improves the compressor's energy efficiency.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more particularly to an eccentric sleeve and scroll compressor. Background Technology

[0002] A scroll compressor is a positive displacement compressor. During the relative movement of the moving and stationary discs, the gas is gradually compressed. The compressed high-pressure gas, mixed with lubricating oil, enters the high-pressure buffer zone through the exhaust port of the stationary disc, then passes through an oil-gas separator before being discharged from the exhaust port. Current scroll compressors suffer from at least the following problems during operation: First, the movement of the moving disc in a scroll compressor is eccentric. During compressor operation, a structure is needed to counteract the eccentric force. The common method is to add an eccentric sleeve structure along with a balance block to balance the shaft system. The eccentric sleeve is located below the moving disc bearing and connected to the crankshaft. However, during compressor operation, due to the presence of refrigerant oil and refrigerant in the environment of the eccentric sleeve, oil churning inevitably occurs, generating eddies, increasing compressor power consumption, and reducing compressor efficiency. Secondly, during the operation of a scroll compressor, gas compression is primarily generated by the relative motion of the moving and stationary discs. Due to the high gas pressure within the discs, they are driven apart. If the gap between the discs becomes too large, leakage will occur at the tooth tips, reducing the compressor's cooling capacity and thus its efficiency. In this case, a back pressure chamber is needed to assist the discs in compressing the gas. Currently, the common practice is to draw gas from the exhaust chamber into the back of the moving disc, forming a back pressure chamber. As the exhaust pressure increases, the pressure in the back pressure chamber also increases, ensuring proper engagement of the discs. However, the back pressure chamber oil circuit has a complex structure and involves numerous seals, many of which are made of rubber, resulting in unstable long-term reliability and requiring high assembly precision. Furthermore, returning the oil to the oil passage also reduces the compressor's cooling capacity, further decreasing its efficiency. Summary of the Invention

[0003] The embodiments of the present invention provide an eccentric sleeve and a scroll compressor, which aim to solve the problem of oil churning phenomenon in existing scroll compressors.

[0004] The present invention provides an eccentric sleeve, including a shaft portion and an edge portion, the edge portion including a front end edge and a rear end edge disposed radially on the shaft portion, the edge portion being formed by the front end edge extending around the edge of the shaft portion toward the rear end edge; wherein, the front end edge and / or the rear end edge are at least partially sectional in structure.

[0005] In the eccentric sleeve provided by the present invention, both the front edge and the rear edge extend radially along the shaft portion.

[0006] In the eccentric sleeve provided by the present invention, the front end edge and the rear end edge are at different heights in the axial direction of the shaft.

[0007] In the eccentric sleeve provided by the present invention, the edge portion further includes an outer edge connecting the front edge and the rear edge, the front edge, the rear edge and the outer edge together form a back pressure surface, and at least a portion of the back pressure surface is higher than the front edge in the axial direction of the shaft portion.

[0008] In the eccentric sleeve provided by the present invention, the back pressure surface gradually rises from the front edge to the rear edge in a spiral upward shape.

[0009] In the eccentric sleeve provided by the present invention, the counterweight portion forms a pressure-increasing surface axially toward the shaft portion, and the pressure-increasing surface gradually rises toward the rear end edge and connects with the rear end edge.

[0010] In the eccentric sleeve provided by the present invention, the width of the counterweight portion is smaller than the width of the rear end edge.

[0011] In the eccentric sleeve provided by the present invention, a limiting hole is provided on the back pressure surface; and / or, a pressure discharge hole is provided on the back pressure surface.

[0012] In the eccentric sleeve provided by the present invention, the shaft portion includes a cylindrical body and an annular platform formed protruding outward around the cylindrical body, the edge portion is formed along a portion of the annular platform, and the portion of the annular platform adjacent to the front edge and the rear edge is provided with an air outlet.

[0013] The present invention also provides a scroll compressor, including the eccentric sleeve described above.

[0014] In the scroll compressor provided by the present invention, the scroll compressor includes a crankshaft connected to a shaft portion, and an intake channel penetrating both ends of the crankshaft is provided on the crankshaft along its axial direction.

[0015] In the scroll compressor provided by the present invention, the scroll compressor includes a bracket and a moving plate. The moving plate is installed on the top surface of the bracket. An eccentric sleeve is disposed inside the bracket. A back pressure cavity is formed between the eccentric sleeve and the moving plate inside the bracket. The air intake channel is connected to the back pressure cavity.

[0016] This invention provides an eccentric sleeve and a scroll compressor. The eccentric sleeve includes a shaft portion and an edge portion. The edge portion is disposed along the edge of the shaft portion. The front and rear ends of the edge portion have a front edge and a rear edge. The front edge and the rear edge have a tangential structure. Thus, when the eccentric sleeve rotates, it is precisely because of the tangential structure of the front edge and the rear edge that the front edge and the rear edge are tangential to the refrigeration oil. The contact area between the front edge and the rear edge and the refrigeration oil is small, which greatly reduces the agitation of the refrigeration oil, reduces the generation of eddies, reduces the power consumption of the compressor, and thus improves the energy efficiency of the compressor. Attached Figure Description

[0017] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a three-dimensional schematic diagram of the eccentric sleeve according to an embodiment of the present invention;

[0019] Figure 2 This is a top view of the eccentric sleeve according to an embodiment of the present invention;

[0020] Figure 3 This is a bottom view of the eccentric sleeve according to an embodiment of the present invention;

[0021] Figure 4 This is a side view of the eccentric sleeve according to an embodiment of the present invention;

[0022] Figure 5 This is an exploded schematic diagram of a scroll compressor according to an embodiment of the present invention;

[0023] Figure 6 This is a cross-sectional schematic diagram of a scroll compressor according to an embodiment of the present invention;

[0024] Figure 7 This is a schematic diagram of the gas flow direction of the scroll compressor according to an embodiment of the present invention;

[0025] Figure 8 This is a three-dimensional schematic diagram of a scroll compressor according to an embodiment of the present invention;

[0026] Figure 9 This is a bottom view schematic diagram of the scroll compressor according to an embodiment of the present invention;

[0027] Figure caption:

[0028] 1. Eccentric sleeve; 11. Shaft; 111. Cylinder; 1111. Pin hole; 112. Annular platform; 113. Air outlet; 12. Edge; 121. Front edge; 122. Rear edge; 123. Outer edge; 124. Back pressure surface; 1241. Limiting hole; 1242. Pressure discharge hole; 13. Counterweight; 131. Pressure boosting surface; 2. Crankshaft; 21. First pin; 22. Second pin; 23. Intake channel; 3. Bracket; 31. Back pressure chamber; 4. Moving disc; 5. First bearing; 6. Second bearing; 7. First seal; 8. Second seal. Detailed Implementation

[0029] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0030] The directional terms used in this invention, such as "up," "down," "front," "back," "left," "right," "inner," "outer," and "side," are merely for reference to the accompanying drawings. Therefore, the directional terms used are for illustrating and understanding this invention, and not for limiting it. Furthermore, in the drawings, structures that are similar or identical are indicated by the same reference numerals.

[0031] This invention provides an eccentric sleeve 1 and a scroll compressor, which solves the problems of oil churning and tooth tip leakage in existing scroll compressors. By designing the front edge 121 and rear edge 122 of the edge 12 as a slit structure and designing the edge 12 as a spiral structure, the oil churning of the eccentric sleeve 1 is reduced, power consumption is reduced, and back pressure is provided for the moving plate 4, ensuring a tight connection between the moving and stationary plates, avoiding tooth tip leakage, and improving the reliability of the compressor.

[0032] To solve the aforementioned problems of oil stirring and tooth tip leakage, the technical solution of this invention is as follows:

[0033] The existing scroll compressor's eccentric sleeve 1 has an oil-facing surface and an oil-returning surface, both of which are vertical planar structures. Therefore, when the eccentric sleeve 1 rotates, the oil-facing surface pushes the refrigerant oil towards the oil-returning surface, generating eddies as the eccentric sleeve 1 rotates. The specific solution proposed in this application is to design the front edge 121 and rear edge 122 of the edge 12 as tangential structures. When the eccentric sleeve 1 rotates, the front edge 121 and rear edge 122 are tangential to the refrigerant oil, instead of pushing it towards the refrigerant oil as in the existing oil-facing and oil-returning surfaces. This tangential structure significantly reduces the contact area with the refrigerant oil compared to a planar structure, minimizing the generation of eddies, thereby reducing compressor power consumption and improving compressor energy efficiency.

[0034] In addition, the edge 12 is designed as a spiral structure, and the surface of the edge 12 is spirally upward. When the eccentric sleeve 1 rotates, the gas in the back pressure chamber 31 can be compressed by the edge 12 of the spiral structure, thereby providing back pressure. The back pressure is used to make the moving and stationary plates tightly connected, prevent tooth tip leakage, and improve the reliability of the compressor.

[0035] To better understand the above technical solutions, the following will provide a detailed explanation of the technical solutions in conjunction with the accompanying drawings and specific implementation methods.

[0036] Reference Figures 1-4 The present invention provides an eccentric sleeve 1. Figure 1 This is a perspective view of an eccentric sleeve 1 according to an embodiment of the present invention. The eccentric sleeve 1 includes a shaft portion 11 and a side portion 12. The side portion 12 includes a front edge 121 and a rear edge 122 disposed radially on the shaft portion 11. The side portion 12 is formed by the front edge 121 extending around the edge of the shaft portion 11 toward the rear edge 122. The front edge 121 and / or the rear edge 122 are at least partially sectional in structure.

[0037] Specifically, the shaft portion 11 is cylindrical in shape, and the edge portion 12 is arranged around a portion of the edge of the shaft portion 11, thus the edge portion 12 is not closed-loop and has a fan-shaped structure. The cylindrical shaft portion 11 and the fan-shaped edge portion 12 are eccentrically positioned, and the fan-shaped edge portion 12 is formed along the bottom edge of the cylindrical shaft portion 11. The two sides of the fan-shaped edge portion 12 are the front edge 121 and the rear edge 122. The front edge 121 and the rear edge 122 can be of equal or unequal width; in this embodiment, the width of the rear edge 122 is greater than the width of the front edge 121. The front edge 121 and / or the rear edge 122 are at least partially sectional, meaning only the front edge 121 or only the rear edge 122 may be sectional, or both may be sectional. Furthermore, the front edge 121 and the rear edge 122 may be partially or entirely sectional. Regardless of where the slicing structure is placed, its presence can reduce eddy current generation to some extent, and no limitation is made here. The slicing structure is similar to the blade of a cutting tool; the smaller the contact area with the object, the easier it is to cut the object. The same applies to the front edge 121 and rear edge 122 in this embodiment. When the eccentric sleeve 1 rotates, the contact area between the front edge 121 and rear edge 122 of the slicing structure and the refrigeration oil is very small, making it easy to break the refrigeration oil without pushing it to rotate and generating eddy currents like a planar structure. Therefore, the generation of eddy currents can be greatly reduced.

[0038] In this embodiment, the front edge 121 and the rear edge 122 are designed as a slit structure. When the eccentric sleeve 1 rotates, the front edge 121 and the rear edge 122 are tangential to the refrigeration oil. The contact area between the front edge 121 and the rear edge 122 and the refrigeration oil is small, which greatly reduces the agitation of the refrigeration oil, reduces the generation of eddies, reduces the power consumption of the compressor, and thus improves the energy efficiency of the compressor.

[0039] Reference Figure 2 and Figure 3In one embodiment, both the front edge 121 and the rear edge 122 extend radially along the shaft 11. Specifically, the front edge 121 is typically the portion facing the refrigeration oil when the eccentric sleeve 1 rotates, while the rear edge 122 is typically the portion facing away from the refrigeration oil. Both the front edge 121 and the rear edge 122 are truncated structures, with straight truncated edges that remain horizontal in cross-section and perpendicular to the axial direction of the shaft 11. Through this embodiment, structures capable of agitating the refrigeration oil are minimized on both sides of the fan-shaped edge 12. By designing the front edge 121 and the rear edge 122 as straight truncated edges, the contact area between this straight truncated structure and the refrigeration oil is minimized, thus maximizing the reduction of eddy current generation.

[0040] In other embodiments, the front edge 121 and the rear edge 122 may also be arc-shaped or have a wavy cut edge shape.

[0041] Reference Figure 4 In one embodiment, the front edge 121 and the rear edge 122 are at different heights in the axial direction of the shaft portion 11. Specifically, a back pressure cavity 31 is formed between the upper surface of the eccentric sleeve 1 and the back of the moving plate 4. In order to provide back pressure to the back pressure cavity 31, in this embodiment, the front edge 121 and the rear edge 122 are set on different horizontal planes, that is, the two are at different heights. In this embodiment, the height of the rear edge 122 is higher than that of the front edge 121, and the edge 12 is generally shaped with a lower front and a higher rear. Thus, the upper surface of the edge 12 is not a horizontal plane, and the distance between the edge 12 and the back of the moving plate 4 is not equal everywhere, but has undulations. As the eccentric sleeve 1 rotates, the higher part of the edge 12 will compress the space of the back pressure cavity 31, compress the gas in the back pressure cavity 31 to form back pressure, and provide back pressure to the back pressure cavity 31. In this way, the back pressure is used to make the moving and stationary plates tightly connected, preventing tooth tip leakage. The conventional oil circuit design is eliminated, which effectively improves the reliability of the compressor. It can provide back pressure during operation and prevent tooth tip leakage caused by the moving and stationary plates separating to both sides when the compressor is working.

[0042] Continue to refer to Figure 1In one embodiment, the edge portion 12 further includes an outer edge 123 connecting the front end edge 121 and the rear end edge 122. The front end edge 121, the rear end edge 122, and the outer edge 123 together form a back pressure surface 124. At least a portion of the back pressure surface 124 is higher than the front end edge 121 in the axial direction of the shaft portion 11. Specifically, the outer arc-shaped edge of the fan-shaped edge portion 12 is the outer edge 123. The outer edge 123 and the two sides of the fan-shaped edge portion 12 define the back pressure surface 124, that is, the shape of the back pressure surface 124 is also fan-shaped. To provide back pressure to the back pressure chamber 31, this embodiment designs the back pressure surface 124 such that at least a portion is higher than the front edge 121. This means a portion of the back pressure surface 124 is relatively closer to the back of the moving plate 4. It is understood that the structure of the back pressure surface 124 being at least partially higher than the front edge 121 can take many forms, such as an inclined surface or inclined blocks, etc., and is not limited here. As the eccentric sleeve 1 rotates, the higher portion of the back pressure surface 124 compresses the space of the back pressure chamber 31, compressing the gas in the back pressure chamber 31 to form back pressure. This back pressure provides back pressure to the back pressure chamber 31, thereby using the back pressure to tightly connect the moving and stationary plates, preventing tooth tip leakage. This eliminates the need for a conventional oil circuit design, effectively improving the compressor's reliability. During operation, it can provide back pressure to prevent tooth tip leakage caused by the moving and stationary plates separating to both sides during compressor operation.

[0043] Reference Figure 1 and Figure 4 This embodiment provides a preferred implementation where the back pressure surface 124 gradually rises spirally from the front edge 121 to the rear edge 122. Specifically, the back pressure surface 124 has a smooth and flat surface, and the thickness of the edge 12 gradually increases along the axial direction of the shaft 11, so that the back pressure surface 124 starts from the front edge 121 and meanders upward along the edge of the shaft 11 until it reaches its highest point at the rear edge 122, thus forming a spiral upward structure. As the eccentric sleeve 1 rotates, this spiral upward structure compresses the space of the back pressure cavity 31, compressing the gas in the back pressure cavity 31 to form back pressure, providing back pressure to the back pressure cavity 31. This back pressure is used to tightly connect the moving and stationary discs, preventing tooth tip leakage, eliminating the need for conventional oil circuit design, effectively improving the reliability of the compressor, and providing back pressure during operation to prevent tooth tip leakage caused by the moving and stationary discs separating to both sides during compressor operation.

[0044] Continue to refer to Figure 1In one embodiment, the eccentric sleeve 1 further includes a counterweight 13, which extends along the outer edge 123 and is formed on the back pressure surface 124. Specifically, the function of the eccentric sleeve 1 is to counteract the eccentric force of the moving disk 4 and balance the shaft system. Therefore, a counterweight 13 needs to be provided on the eccentric sleeve 1 to provide corresponding weight. Specifically, the counterweight 13 is set on the back pressure surface 124. When the eccentric sleeve 1 and the moving disk 4 make eccentric movements, the counterweight 13 provides a certain force so that the eccentric sleeve 1 can counteract the eccentric force of the moving disk 4 when rotating, thereby balancing the shaft system.

[0045] Continue to refer to Figure 1 In this embodiment, the counterweight 13 forms a pressure-increasing surface 131 axially toward the shaft 11. The pressure-increasing surface 131 gradually rises toward the rear end edge 122 and connects to the rear end edge 122. To further increase the back pressure, a pressure-increasing surface 131 is provided on the counterweight 13. The pressure-increasing surface 131 is the upper surface of the counterweight 13. The structure of the pressure-increasing surface 131 is similar to that of the back pressure surface 124, both being spirally upward. One end of the pressure-increasing surface 131 connects to the back pressure surface 124, and the other end connects to the rear end edge 122. The pressure-increasing surface 131 starts from the back pressure surface 124 and meanders upward along the outer edge 123 until it reaches its highest point at the rear end edge 122. Thus, the pressure-increasing surface 131 has an overall spirally upward structure. The starting position of the pressure-increasing surface 131 from the back pressure surface 124 can be the middle of the fan-shaped edge 12. As the eccentric sleeve 1 rotates, the spiral upward shape of the pressure boosting surface 131 can compress the space of the back pressure chamber 31, compressing the gas in the back pressure chamber 31 to form back pressure. Based on the back pressure provided by the back pressure surface 124 itself, the back pressure is further increased.

[0046] Continue to refer to Figure 1 Furthermore, the width of the counterweight 13 is smaller than the width of the rear end edge 122. To minimize the generation of eddies, the counterweight 13 has an arc-shaped structure extending along the outer edge 123. As the height of the counterweight 13 gradually increases, it forms inner and outer sidewalls. The distance between the inner and outer sidewalls of the counterweight 13 is the width of the counterweight 13. The width of the counterweight 13 can vary; for example, the initial section may be narrower, the middle section wider, and the final section narrower again. The inner and outer sidewalls of the counterweight 13, along with the rear end edge 122, form an oil-backing surface. Because the width of the final section of the counterweight 13 is narrower, the area of ​​this oil-backing surface is also relatively small, minimizing oil churning. Since the entire width of the counterweight 13 is smaller than the width of the rear end edge 122, the counterweight 13 occupies only a small portion of the edge 12, further minimizing oil churning.

[0047] Reference Figure 2 and Figure 3In one embodiment, a limiting hole 1241 is provided on the back pressure surface 124. Specifically, the limiting hole 1241 is provided on the periphery of the shaft portion 11 and adjacent to the shaft portion 11. The limiting hole 1241 is used to connect with the second pin 22 at the top of the crankshaft 2. The limiting hole 1241 and the second pin 22 are clearance fit to avoid and prevent the eccentric sleeve 1 from rotating and generating abnormal noise.

[0048] Continue to refer to Figure 2 and Figure 3 In one embodiment, a pressure relief hole 1242 is provided on the back pressure surface 124. Specifically, the pressure relief hole 1242 is located on the periphery of the shaft portion 11 and adjacent to the shaft portion 11. The pressure relief hole 1242 is mainly used to prevent excessive pressure in the back pressure chamber 31 and to prevent wear of the compressor gear tips due to excessive back pressure. Excessive back pressure in the back pressure chamber 31 can be released internally through the pressure relief hole 1242.

[0049] Continue to refer to Figure 1 In one embodiment, the shaft portion 11 includes a cylindrical body 111 and an annular platform 112 protruding outward around the cylindrical body 111. The edge portion 12 is formed along a portion of the edge of the annular platform 112. An air outlet 113 is provided on the portion of the annular platform 112 adjacent to the front end edge 121 and the rear end edge 122. Specifically, the cylindrical body 111 and the annular platform 112 are cylindrical in shape. The diameter of the annular platform 112 is larger than the diameter of the cylindrical body 111. The annular platform 112 has a certain height and is hollow. A pin hole 1111 is provided on the cylindrical body 111, and the top of the crankshaft 2 is fitted with the pin hole 1111 through a first pin 21 with a clearance fit. The front end edge 121 of the edge portion 12 spirals upward along the edge of the annular platform 112 from the bottom until it reaches the top of the annular platform 112, forming the rear end edge 122. The fan-shaped edge 12 is three-quarters of a circle, with the remaining quarter serving as the air outlet 113. That is, the air outlet 113 is located between the portion of the annular platform 112 without the edge 12, the lower front edge 121, and the higher rear edge 122. In this way, the gas-liquid mixture exiting from the top of the crankshaft 2 can exit through this air outlet 113 and enter the back pressure chamber 31.

[0050] Reference Figures 5-9 The present invention also provides a scroll compressor. Figure 5This is an exploded view of a scroll compressor according to an embodiment of the present invention. The scroll compressor includes an eccentric sleeve 1, a crankshaft 2, a bracket 3, a moving disc 4, a first bearing 5, a second bearing 6, a first seal 7, and a second seal 8. The first seal 7 is a shaft seal, and the second seal 8 is made of PTFE (polytetrafluoroethylene). The first bearing 5 is a bearing for the bracket 3, and the second bearing 6 is a bearing for the moving disc 4. The moving disc 4 is mounted on the top of the bracket 3. A mounting hole is provided at the center of the bracket 3. The mounting hole has a multi-segment structure along the axial direction of the bracket 3 to facilitate the installation of the shaft seal, the bracket 3 bearing, the eccentric sleeve 1, and the moving disc 4 bearing. The crankshaft 2 passes through the mounting hole and sequentially through the shaft seal and the bracket 3 bearing. The shaft seal is located below the bracket 3 bearing for sealing. The top of the crankshaft 2 is located below the eccentric sleeve 1. The top end face of the crankshaft 2 is connected to the pin hole 1111 and the limiting hole 1241 of the eccentric sleeve 1 via the first pin 21 and the second pin 22, respectively. The shaft portion 11 of the eccentric sleeve 1 is inserted into the bearing of the moving disc 4, which is located below the moving disc 4. The moving disc 4 is sealed to the bracket 3 via PTFE. The back surface of the moving disc 4, the upper surface of the eccentric sleeve 1, and the side wall of the bracket 3 together form a back pressure cavity 31. The eccentric sleeve 1 includes a shaft portion 11 and a side portion 12. The side portion 12 includes a front edge 121 and a rear edge 122 located radially from the shaft portion 11. The side portion 12 is formed by the front edge 121 extending around the edge of the shaft portion 11 toward the rear edge 122. The front edge 121 and / or the rear edge 122 are at least partially sectional. It should be noted that the eccentric sleeve 1 can also be the structure of the above embodiment, but for the sake of brevity, it will not be described again here.

[0051] Reference Figure 5 and Figure 6 In this embodiment, the scroll compressor includes a crankshaft 2 connected to a shaft portion 11. An intake channel 23, extending through both ends of the crankshaft 2, is formed along its axial direction. Specifically, the intake channel 23 extends from the bottom to the top of the crankshaft 2, along its axial direction, and an outlet hole is formed at the top of the crankshaft 2, located at the center of the top. A first pin 21 and a second pin 22 connected to the top of the crankshaft 2 are eccentrically positioned relative to the center of the top of the crankshaft 2. A gas-liquid mixture enters from the bottom of the crankshaft 2 through the intake channel 23, exits through the outlet hole at the top of the crankshaft 2, and then enters the back pressure chamber 31 via the outlet 113 of the eccentric sleeve 1. This achieves the introduction of gas into the back pressure chamber 31 through the crankshaft 2.

[0052] Reference Figure 7When the compressor is working, high-temperature, low-pressure gas enters from the crankshaft 2, passes through the suction port on the outside of the bracket 3 (the notch on the edge of the bracket), and enters the moving plate 4. The gas is then compressed by the mutual motion of the vortex. During this process, some of the gas-liquid mixture enters the back pressure chamber 31 from the intake passage 23 of the crankshaft 2. As the compressor rotates, the crankshaft 2 drives the first pin 21 and the second pin 22 to rotate, simultaneously causing the eccentric sleeve 1 to rotate eccentrically. While balancing the shaft torque, the eccentric sleeve 1 compresses the gas-liquid mixture towards the moving plate 4, thus forming the back pressure chamber 31 on the back of the moving plate 4. A PTFE seal is used between the bracket 3 and the moving plate 4. To prevent excessive pressure in the back pressure chamber 31, a pressure discharge hole 1242 is designed on the spiral structure of the eccentric sleeve 1 to prevent wear on the compressor gear tips due to excessive back pressure. A limiting hole 1241 is also added to the eccentric sleeve 1 to prevent excessive rotation and abnormal noise. The eccentric sleeve 1 adopts a spiral structure throughout, which effectively prevents oil churning.

[0053] In other embodiments, the eccentric sleeve 1 can also take other forms, such as a sheet-like structure. Since compressors typically have weight-reduction design requirements, the eccentric sleeve 1 in this embodiment is designed for weight reduction. Of course, if weight reduction is not a consideration for the eccentric sleeve 1, its structure can be enlarged and the support 3 lengthened, which helps to achieve pressure control of a larger back pressure chamber 31 and is easier to manufacture. Furthermore, the intake method can be replaced by direct intake from below the support 3, eliminating the design of the intake passage 23 of the crankshaft 2. This has the advantages of increasing the strength of the crankshaft 2, reducing the need for shaft seals in the sealing structure, and improving reliability.

[0054] By implementing the scroll compressor of this embodiment, oil churning by the eccentric sleeve 1 can be effectively prevented, and back pressure can be provided, thereby preventing leakage at the top of the compressor teeth and ensuring the working efficiency of the compressor. At the same time, compared with the back pressure scheme, the structure is simple, the sealing structure is reduced, and the reliability of the compressor is improved.

[0055] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in the present invention, and these modifications or substitutions should all be covered within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. An eccentric sleeve for a scroll compressor, characterized in that, It includes a shaft portion and an edge portion, the edge portion including a front end edge and a rear end edge disposed radially on the shaft portion, the edge portion being formed by the front end edge extending around the edge of the shaft portion toward the rear end edge; wherein, the front end edge and / or the rear end edge are at least partially sectional in structure; The edge also includes an outer edge connecting the front edge and the rear edge, the front edge, the rear edge and the outer edge together forming a back pressure surface, at least a portion of the back pressure surface being higher than the front edge in the axial direction of the shaft portion.

2. The eccentric sleeve of the scroll compressor according to claim 1, characterized in that, Both the front edge and the rear edge extend radially along the shaft.

3. The eccentric sleeve of the scroll compressor according to claim 1, characterized in that, The front edge and the rear edge are at different heights along the axial direction of the shaft.

4. The eccentric sleeve of the scroll compressor according to claim 1, characterized in that, The back pressure surface gradually rises in a spiral shape from the front edge to the rear edge.

5. The eccentric sleeve of the scroll compressor according to claim 1, characterized in that, The eccentric sleeve also includes a counterweight portion, which extends along the outer edge and is formed on the back pressure surface.

6. The eccentric sleeve of the scroll compressor according to claim 5, characterized in that, The counterweight portion forms a pressure-increasing surface axially toward the shaft portion, and the pressure-increasing surface gradually rises toward the rear end edge and connects with the rear end edge.

7. The eccentric sleeve of the scroll compressor according to claim 6, characterized in that, The width of the counterweight is smaller than the width of the rear end edge.

8. The eccentric sleeve of the scroll compressor according to claim 1, characterized in that, A limiting hole is provided on the back pressure surface; and / or, a pressure relief hole is provided on the back pressure surface.

9. The eccentric sleeve of the scroll compressor according to claim 1, characterized in that, The shaft portion includes a cylindrical body and an annular platform that protrudes outward around the cylindrical body. The edge portion is formed along a portion of the edge of the annular platform, and an air outlet is provided on the portion of the annular platform adjacent to the front edge and the rear edge.

10. A scroll compressor, characterized in that, Includes the eccentric sleeve of the scroll compressor as described in any one of claims 1-9.

11. The scroll compressor according to claim 10, characterized in that, The scroll compressor includes a crankshaft connected to a shaft portion, and an intake passage extending through both ends of the crankshaft is provided along its axial direction.

12. The scroll compressor according to claim 11, characterized in that, The scroll compressor includes a bracket and a moving plate. The moving plate is installed on the top surface of the bracket. An eccentric sleeve is installed inside the bracket. A back pressure chamber is formed between the eccentric sleeve and the moving plate inside the bracket. The air intake passage is connected to the back pressure chamber.

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