Scroll compressor

Abstract

The present disclosure relates to a scroll compressor, which includes a fixed scroll and a moving scroll. The moving scroll is configured to be able to move relative to the fixed scroll to compress a fluid; a main bearing seat that supports the moving scroll; an axial flexible mounting mechanism. The fixed scroll is connected to the main bearing seat via the axial flexible mounting mechanism, such that the fixed scroll can move a predetermined distance in the axial direction. The axial flexible mounting mechanism includes a bolt and a sleeve disposed on the outer circumference of the bolt. The sleeve includes a first section in contact with the main bearing seat and a second section in contact with the fixed scroll in the axial direction. The first section is configured to have different bending stiffnesses in the radial direction and in the tangential direction.

Description

Technical Field

[0001] The present invention relates to a scroll compressor, and more particularly, to a sleeve capable of preventing failure of an axial flexible mounting mechanism and a scroll compressor including the sleeve. Background Art

[0002] The content of this section only provides background information related to the present invention, which may not constitute prior art.

[0003] Scroll compressors can be applied to, for example, refrigeration systems, air conditioning systems, and heat pump systems. A scroll compressor includes a compression mechanism for compressing a working fluid (such as a refrigerant), a main bearing housing for supporting the compression mechanism, a rotating shaft for driving the compression mechanism, and a motor for driving the rotating shaft to rotate. The compression mechanism includes a fixed scroll and a moving scroll that orbits relative to the fixed scroll. Both the fixed scroll and the moving scroll include end plates and spiral vanes extending from one side of the end plates. When the moving scroll orbits relative to the fixed scroll, a series of moving compression chambers with volumes gradually decreasing from the radially outer side to the radially inner side are formed between the spiral vanes of the fixed scroll and the moving scroll, thereby compressing the working fluid.

[0004] During normal operation of the scroll compressor, good sealing needs to be achieved between the tip of the spiral vane of one of the fixed scroll and the moving scroll and the end plate of the other. On the other hand, for example, when the pressure in the compression chamber of the scroll compressor is too high, the spiral vane can separate from the end plate to unload the high-pressure fluid, thereby avoiding damage to the compression mechanism.

[0005] To this end, the fixed scroll is mounted to the main bearing housing through an axial flexible mounting mechanism, such that the fixed scroll can axially move a certain distance relative to the moving scroll. The axial flexible mounting mechanism generally includes a bolt and a sleeve located outside the bolt. The bolt is inserted into the mounting hole of the fixed scroll to threadedly connect the fixed scroll to the main bearing housing. The sleeve is also inserted into the mounting hole of the fixed scroll and is disposed between the bolt head and the main bearing housing, such that there is a certain gap between the bolt head and the fixed scroll for the axial movement of the fixed scroll.

[0006] However, during the operation of the scroll compressor, the phenomenon of bolt loosening or even breaking often occurs. Summary of the Invention

[0007] The inventors of the present application found that the bolts of the axial flexible mounting mechanism are prone to loosening or breaking. Therefore, they deeply studied the reasons for bolt fatigue damage and proposed a solution that can improve the fatigue strength of the bolts.

[0008] The object of the present disclosure is to provide a scroll compressor capable of preventing or reducing damage to the axial flexible mounting mechanism.

[0009] According to one aspect of the present disclosure, there is provided a scroll compressor, which includes a fixed scroll and a moving scroll. The moving scroll is configured to be able to move relative to the fixed scroll to compress a fluid; a main bearing seat that supports the moving scroll; and an axial flexible mounting mechanism that connects the fixed scroll to the main bearing seat via the axial flexible mounting mechanism such that the fixed scroll can move a predetermined distance in the axial direction. The axial flexible mounting mechanism includes a bolt and a sleeve disposed on the outer periphery of the bolt. Wherein, the sleeve includes a first section in contact with the main bearing seat and a second section in contact with the fixed scroll in the axial direction, and the first section is configured to have different bending stiffnesses in the radial direction and the tangential direction.

[0010] Wherein, for a scroll compressor in which the sleeve is subjected to a relatively large load in the radial direction, the sleeve is configured to have a relatively large bending stiffness in the radial direction; for a scroll compressor in which the sleeve is subjected to a relatively large load in the tangential direction, the sleeve is configured to have a relatively large bending stiffness in the tangential direction.

[0011] Wherein, the sleeve includes a cylindrical portion and a wing portion extending outward from the outer periphery of the cylindrical portion. The first section is formed by the section of the sleeve provided with the wing portion, and the second section is formed by the section of the sleeve including only the cylindrical portion.

[0012] Wherein, the size of the wing portion in the tangential direction is different from its size in the radial direction. For a scroll compressor in which the sleeve is subjected to a relatively large load in the radial direction, the radial dimension of the wing portion is larger, while for a scroll compressor in which the sleeve is subjected to a relatively large load in the tangential direction, the tangential dimension of the wing portion is larger.

[0013] Optionally, the cylindrical portion and the wing portion are formed integrally or separately.

[0014] Optionally, in the case where the cylindrical portion and the wing portion are formed separately: the lower end surface of the cylindrical portion is flush with the lower end surface of the wing portion, and the two together form the end surface of the sleeve in contact with the main bearing seat; or the lower end surface of the cylindrical portion is not flush with the lower end surface of the wing portion, and the lower end surface of the wing portion forms the end surface of the sleeve in contact with the main bearing seat.

[0015] Optionally, in the case where the cylindrical portion and the wing portion are formed separately, the cylindrical portion and the wing portion are connected in an interference fit manner.

[0016] Optionally, the main bearing seat includes a boss connected to the axial flexible mounting mechanism, and the wing portion extends no more than the outer contour of the boss in the direction in which the load on the sleeve is relatively large.

[0017] Optionally, the boss is further provided with an alignment wall extending in the axial direction toward the fixed scroll.

[0018] Optionally, the wing portion further includes a cutting portion extending axially from the lower end surface of the wing portion in contact with the main bearing seat toward the fixed scroll, for accommodating the alignment wall.

[0019] Optionally, the alignment wall is in contact with the cutting portion and / or the cylindrical portion to limit the position of the sleeve.

[0020] Optionally, the lower end of the wing portion is configured to have a pair of crescent-shaped stepped portions, which are arranged on both sides of the through hole at the center of the wing portion along the direction in which the sleeve is subjected to a greater load, and the lower end surface of the stepped portion is configured as the lower end surface of the wing portion in contact with the main bearing seat.

[0021] Optionally, the lower end of the wing portion is configured to have a stepped portion, which is arranged to surround the through hole at the center of the wing portion, and the stepped portion has the same size as or a smaller size than the cylindrical portion in the direction in which the sleeve is subjected to a smaller load, and the lower end surface of the stepped portion is configured as the lower end surface of the wing portion in contact with the main bearing seat.

[0022] Optionally, the first segment is located between the fixed scroll and the main bearing seat, and at least a part of the second segment is inserted into the mounting hole of the fixed scroll.

[0023] From the following detailed description, other application fields of the present invention will become more obvious. It should be understood that these detailed descriptions and specific examples, although showing the preferred embodiments of the present invention, are for the purpose of illustrative explanation only and are not intended to limit the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Through the following description with reference to the drawings, the features and advantages of one or more embodiments of the present invention will become more readily understood, in the drawings:

[0025] Figure 1 is a radial longitudinal sectional view of an existing scroll compressor;

[0026] Figure 2 is Figure 1 a partial perspective schematic view of the scroll compressor of

[0027] Figure 3a and Figure 3b are Figure 1 a partial radial longitudinal sectional view and a partial tangential longitudinal sectional view of the scroll compressor of

[0028] Figure 4 is a partial perspective schematic view of a scroll compressor according to the first embodiment of the present disclosure, showing the main bearing seat and the flexible mounting mechanism;

[0029] Figure 5a andFigure 5b A partial radial longitudinal sectional view and a partial tangential longitudinal sectional view of a scroll compressor according to a first embodiment of the present disclosure, respectively;

[0030] Figure 6a and Figure 6b A perspective schematic view and a top view of a sleeve of a scroll compressor according to a first embodiment of the present disclosure, respectively;

[0031] Figure 7 A partial perspective schematic view of a scroll compressor according to a second embodiment of the present disclosure, which shows a main bearing seat and a flexible mounting mechanism;

[0032] Figure 8a and Figure 8b A partial radial longitudinal sectional view and a partial tangential longitudinal sectional view of a scroll compressor according to a second embodiment of the present disclosure, respectively;

[0033] Figure 9a A perspective schematic view of a sleeve of a scroll compressor according to a second embodiment of the present disclosure;

[0034] Figure 9b , Figure 9c and Figure 9d respectively are Figure 9a A perspective schematic view of a wing portion of the sleeve, a perspective schematic view of a cylindrical portion of the sleeve, and a bottom view of the wing portion of the sleeve;

[0035] Figure 10 A partial perspective schematic view of a scroll compressor according to a third embodiment of the present disclosure, which shows a main bearing seat and an axial flexible mounting mechanism;

[0036] Figure 11a and Figure 11b A partial radial longitudinal sectional view and a partial tangential longitudinal sectional view of a scroll compressor according to a third embodiment of the present disclosure, respectively;

[0037] Figure 12a A perspective schematic view of a sleeve of a scroll compressor according to a third embodiment of the present disclosure;

[0038] Figure 12b is Figure 12a A perspective schematic view of a wing portion of the sleeve;

[0039] Figure 13 A partial perspective schematic view of a scroll compressor according to a fourth embodiment of the present disclosure, which shows a main bearing seat and an axial flexible mounting mechanism;

[0040] Figure 14 A perspective schematic view of a sleeve assembly of a scroll compressor according to a fourth embodiment of the present disclosure;

[0041] Figure 15a and Figure 15b are respectively a three-dimensional schematic view of a sleeve of a scroll compressor according to a fifth embodiment of the present disclosure and a three-dimensional schematic view of a wing portion of the sleeve;

[0042] Figure 16a and Figure 16b are respectively schematic views of the force conditions of the sleeve and the bolt during the operation of the compressor. Detailed implementation manners

[0043] Exemplary embodiments will now be described more fully with reference to the accompanying drawings.

[0044] Exemplary embodiments are provided so that the present disclosure will be thorough and will convey the scope more fully to those skilled in the art. Many specific details such as examples of specific components, devices, and methods are set forth to provide a thorough understanding of the various embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, and that the exemplary embodiments may be embodied in many different forms and should not be construed as limiting the scope of the present disclosure. In some exemplary embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.

[0045] The following will refer to Figure 1 to describe the overall structure of the scroll compressor 10. As shown, the compressor 10 includes a housing 1, a compression mechanism, a motor 6, a rotating shaft (which may also be referred to as a drive shaft or a crankshaft) 4, and a main bearing seat 5.

[0046] The compression mechanism includes a stationary scroll 2 and an orbiting scroll 3. The motor 6 is configured to rotate the rotating shaft 4, and then, the rotating shaft 4 drives the orbiting scroll 3 to move around the stationary scroll 2 (i.e., the central axis of the orbiting scroll moves around the central axis of the stationary scroll, but the orbiting scroll does not rotate around its central axis) to compress the working fluid.

[0047] The stationary scroll 2 can be fixed to the housing 1 in any suitable manner, as shown by being fixedly mounted to the main bearing seat 5 through bolts, which will be described in detail later. The stationary scroll 2 may include a stationary scroll end plate 22 and stationary scroll blades 24 extending from one side of the stationary scroll end plate 22. As Figure 2 shown, the stationary scroll 2 also has a flange 26 extending radially outward from its radially outermost peripheral surface. Mounting holes are provided in the flange 26 for receiving an axially flexible mounting mechanism to connect to the main bearing seat 5.

[0048] The orbiting scroll 3 may include an orbiting scroll end plate 32, an orbiting scroll vane 34 formed on one side of the orbiting scroll end plate 32, and a hub portion 31 formed on the other side of the orbiting scroll end plate 32. The fixed scroll vane 24 and the orbiting scroll vane 34 can be engaged with each other so that a series of moving compression chambers with volumes gradually decreasing from the radially outer side to the radially inner side are formed between the fixed scroll vane 24 and the orbiting scroll vane 34 when the scroll compressor operates, thereby realizing the compression of the working fluid. The hub portion 31 is eccentrically crank-pinned to the rotating shaft 4 and is driven by the eccentric crank.

[0049] The main bearing housing 5 is adapted to support the orbiting scroll end plate 32 of the orbiting scroll 3. The orbiting scroll end plate 32 rotates around on the supporting surface of the main bearing housing 5. The main bearing housing 5 can be fixed relative to the housing 1 of the scroll compressor 10 in any suitable manner.

[0050] In order to realize the compression of the fluid, effective sealing is required between the fixed scroll 2 and the orbiting scroll component 3.

[0051] On the one hand, when the scroll compressor operates normally, radial sealing is also required between the side surface of the spiral vane 24 of the fixed scroll 2 and the side surface of the spiral vane 34 of the orbiting scroll 3. This radial sealing between the two is usually realized by means of the centrifugal force during the operation of the orbiting scroll 3 and the driving force provided by the rotating shaft 4. When incompressible foreign matters (such as solid impurities and liquid refrigerant) enter the compression chamber and get stuck between the spiral vanes 24 and 34, the spiral vanes 24 and 34 can be temporarily separated from each other radially to allow the foreign matters to pass through, thereby preventing damage to the spiral vanes 24 and 34, and thus providing radial flexibility for the scroll compressor 10.

[0052] On the other hand, when the scroll compressor operates normally, axial sealing is required between the top end of the spiral vane 24 of the fixed scroll 2 and the end plate 32 of the orbiting scroll 3, and between the top end of the spiral vane 34 of the orbiting scroll 3 and the end plate 22 of the fixed scroll 2. When the pressure in the compression chamber of the scroll compressor is too high, the fluid in the compression chamber will leak to the low-pressure side through the gaps between the top end of the spiral vane 24 of the fixed scroll 2 and the end plate 32 of the orbiting scroll 3 and between the top end of the spiral vane 34 of the orbiting scroll 3 and the end plate 22 of the fixed scroll 2 to achieve unloading, thereby providing axial flexibility for the scroll compressor 10.

[0053] To provide axial flexibility, the fixed scroll 2 is installed on the main bearing housing 5 through an axial flexibility installation mechanism. See Figure 2, the main bearing block 5 is provided with a boss 51 extending axially at its outermost radial side, and the boss 51 is aligned axially with the flange 26 of the corresponding fixed scroll 2. It should be noted that, since sufficient installation space needs to be reserved for other components in the radial direction, the boss 51 is usually designed as a generally frustoconical shape with a length in the radial direction smaller than the length in the circumferential (tangential) direction. In addition, an alignment wall 52 extending axially towards the flange 26 is provided on the outermost radial side of the boss 51 to facilitate the alignment and assembly of the fixed scroll 2, the axial flexible mounting mechanism, and the main bearing block 5.

[0054] See Figure 3a and Figure 3b , the axial flexible mounting mechanism includes a bolt 9 and a sleeve 8 located radially outside the bolt 9. The bolt 9 has a shank portion, a head 91 at one end of the shank portion, and a threaded portion 92 at the other end of the shank portion. The head 91 contacts the upper end face (second end face) 82 of the sleeve 8 and the upper surface 261 of the flange 26. The threaded portion 92 is configured to be screwed into a threaded hole of the boss 51 of the main bearing block 5. The sleeve 8 is also received in the mounting hole of the flange 26 of the fixed scroll 2, and the lower end face (first end face) 81 of the sleeve 8 contacts the upper surface (contact surface) 511 of the boss 51, that is to say, the sleeve 8 is located between the head 91 and the upper surface 511 of the boss 51 of the main bearing block 5, thereby defining the position of the head 91 such that the fixed scroll 2 can move a predetermined distance axially.

[0055] Since the sleeve 8 is received in the mounting hole of the flange 26 of the fixed scroll to guide the axial movement of the fixed scroll 2, the sleeve 8 usually has a cylindrical outer contour so as to be adapted to the mounting hole of the flange 26. The outer wall at the outermost radial side of the sleeve 8 contacts the alignment wall 52 of the boss 51, thereby restricting the position of the sleeve 8 in the radial direction. In existing scroll compressors, the position of the sleeve in the tangential direction is usually not restricted.

[0056] The inventor found that the bolts of the existing axial flexible mounting mechanism are prone to loosening or breaking. When the orbiting scroll 3 orbits relative to the fixed scroll 2, due to the centripetal acceleration, side contact of the vanes occurs, and a force F acting on the sleeve 8 is generated. This force F applies a load to the bolt 9 via the sleeve 8, thereby causing the bolt 9 to break and fail. If the force F is too large or the sleeve and the bolt are not fully aligned during installation, it will also cause the sleeve to contact the shank portion of the bolt, resulting in a sharp increase in the load applied to the bolt, and the bolt is more likely to loosen and break.

[0057] Figure 16a and Figure 16bSimplified force diagrams of the sleeve and the bolt are shown respectively when there is no contact between the sleeve and the shank of the bolt. For the sleeve, the acting force F is balanced with the forces f1 and f2 respectively received on the upper end face (second end face) and the lower end face (first end face) of the sleeve, that is, the formula F = f1 + f2 is satisfied. At the same time, the bolt is subjected to a force with the same magnitude as f1 and the opposite direction at the head in contact with the second end face of the sleeve. Under the action of this force, the bolt is prone to fracture failure at its threaded part, that is, at the position of the end part of the bolt. The bending moment at the end part of the bolt can be calculated by the following formula: M S-Thread = f1L - M S-Head .

[0058] It should be noted that in the existing scroll compressors, the acting force F is often very large in one direction of the tangential direction and the radial direction and very small in the other direction. For the sake of description, the present disclosure takes the example that the sleeve is subjected to a large load in the tangential direction for illustration.

[0059] The present disclosure aims to reduce the load on the bolt and slow down or prevent the bolt from loosening or breaking by making the stiffness direction of the sleeve match the load direction. That is to say, in the direction where the sleeve is subjected to a large load, the bending stiffness of the sleeve is also large; in the direction where the sleeve is subjected to a small load, the bending stiffness of the sleeve is also small.

[0060] Figure 4 A partial schematic view of a scroll compressor according to a first embodiment of the present invention is shown, in which the axial flexible mounting mechanism has been mounted on the boss 151 of the main bearing housing 15, and the fixed scroll has been removed to more clearly observe the axial flexible mounting mechanism. The axial flexible mounting mechanism includes a bolt 19 and a sleeve 18 located radially outside the bolt 19. In the first embodiment, the structure of the fixed scroll, the main bearing housing 15, the bolt 19, and their mounting positions and methods are similar to those of the existing scroll compressor described above, so they will not be elaborated here. Refer to Figure 5a and Figure 5b , the sleeve 18 is received in the mounting hole of the flange 126 of the fixed scroll and is located between the head of the bolt 19 and the upper surface (contact surface) 1511 of the boss 151 of the main bearing housing 15. The upper end face (second end face) 182 of the sleeve 18 contacts the lower surface of the head of the bolt 19, and the lower end face (first end face) 181 of the sleeve 18 contacts the upper surface (contact surface) 1511 of the boss 151.

[0061] As Figure 6a and Figure 6bAs shown, different from the generally cylindrical sleeve 8 in the existing axial flexible mounting mechanism, the sleeve 18 includes a first section 183 having a first end face 181 and a second section 184 having a second end face 182. The second section 184 is generally cylindrical, and its dimensions in the radial direction and the tangential direction are substantially the same. The first section 183 is configured to have wing-like portions extending outward from the outer peripheral wall of the second section 184, especially extending outward in the tangential direction, such that the outer contour of the first section 183 has a larger dimension in the tangential direction than in the radial direction. In the tangential direction, the outer contour of the first section 183 does not extend beyond the contour of the upper surface (contact surface) 1511 of the boss 151, and the outer contour of the first section 183 is preferably substantially the same as the contour of the upper surface (contact surface) 1511 of the boss 151, so as to increase the size of the first section as much as possible within a limited space and facilitate processing and installation. In the radial direction, the outermost outer wall of the first section 183 is substantially flush with the outer peripheral wall of the second section 184 and contacts the alignment wall 152 of the boss 151. The innermost outer wall of the first section 183 can be substantially flush with or slightly exceed the radial inner wall of the boss 151 as long as there is no interference with other components inside the compressor.

[0062] Since the dimension of the first section in the tangential direction is larger than that in the radial direction, the bending stiffness of the sleeve in the tangential direction is increased. Regarding Figure 16a and Figure 16b the force conditions of the sleeve and the bolt shown, when the acting force F remains unchanged, increasing the bending stiffness of the sleeve in the tangential direction can change the bending moment distribution on the sleeve, thereby causing the force f1 received by the upper surface of the sleeve to decrease. Thus, the f1 acting on the bolt also decreases, thereby reducing the bending moment and stress at the end portion of the bolt, enhancing the fatigue strength of the bolt, and greatly reducing the risk of fracture failure of the bolt. In addition, when the first section contacts the alignment wall, since the first section is set as a non-cylindrical structure with a larger dimension in the tangential direction than in the radial direction, it can effectively prevent the sleeve from rotating. Moreover, compared with the existing cylindrical sleeve, the area of the first end face of the sleeve increases, so the imprint of the sleeve on the boss can be reduced.

[0063] As Figure 5a and Figure 5bAs shown, in the scroll compressor, preferably, the upper surface 1831 of the first section 183 does not exceed the lower surface 1262 of the flange 126 axially. That is to say, the first section 183 is located between the flange 126 of the fixed scroll end plate and the boss 151 of the main bearing seat 15 without being inserted into the mounting hole of the flange 126, and only the second section 184 is inserted into the mounting hole of the flange 126. Since the second section 184 can have dimensions adapted to the mounting holes of the existing flange 126, the problem of bolt breakage or loosening can be improved only by replacing the sleeve according to the present disclosure without modifying or replacing other components such as the moving scroll plate. Of course, the upper surface 1831 of the first section 183 can also exceed the lower surface 1262 of the flange 126 axially as long as the mounting holes of the flange 126 are manufactured in a shape adapted to the outer contour of the first section 183.

[0064] The following will be combined with Figures 7 to 9d to describe the scroll compressor according to the second embodiment of the present invention. Similar to the scroll compressor according to the first embodiment of the present invention shown in Figures 4 to 6b , the scroll compressor according to the second embodiment of the present invention includes a fixed scroll, an axially flexible mounting mechanism, a main bearing seat 25, etc. The axially flexible mounting mechanism includes a bolt 29 and a sleeve 28 located radially outside the bolt 29. In the second embodiment, the structures, positions, manners, etc. of the fixed scroll, the main bearing seat 25, and the bolt 29 are similar to those of the scroll compressor in the first embodiment described above, and thus will not be described in detail.

[0065] Figure 7 FIG. shows a partial schematic view of the scroll compressor according to the second embodiment of the present invention, in which the axially flexible mounting mechanism has been installed on the main bearing seat 25, and the fixed scroll has been removed to more clearly observe the axially flexible mounting mechanism. Referring to Figure 8a and Figure 8b , the sleeve 28 is received in the mounting hole of the flange of the fixed scroll and is located between the head of the bolt 29 and the upper surface (contact surface) 2511 of the boss 251 of the main bearing seat 25. The second end face 282 of the sleeve 28 contacts the lower surface of the head of the bolt 29, and the first end face 281 of the sleeve 28 contacts the upper surface 2511 of the boss 251.

[0066] As Figures 9a to 9d shown, different from the integrally formed sleeve 18 including the wing portion in the first embodiment, the sleeve 28 is constructed in the form of an assembly including a split cylindrical portion 286 and a wing portion 285. Figure 9a FIG. shows the sleeve after the cylindrical portion and the wing portion are assembled, in which the lower end of the cylindrical portion 286 is inserted into the through hole in the center of the wing portion 285. Figure 9c and Figure 9bThe unassembled cylindrical part and the wing part are shown respectively. Among them, the cylindrical part 286 is similar to the generally cylindrical sleeve structure in the existing scroll compressor, including an upper end face and a lower end face. The wing part 285 is configured to be similar to the shape of the wing part in the first embodiment, and the dimension of its outer contour in the tangential direction is larger than that in the radial direction.

[0067] For the convenience of production, processing and assembly, the lower end of the wing part 285 can be configured to have a pair of crescent-shaped stepped portions 2851. The stepped portions 2851 are arranged on both sides of the through hole around the center of the wing part 285 in the tangential direction. There is a small gap between the stepped portions 2851 and the through hole for easy assembly. The height of the stepped portions 2851 in the axial direction is equal to or greater than the height of the alignment wall 252 of the boss 251. When the cylindrical part 286 and the wing part 285 are assembled together to form the sleeve 28, the lower end face of the cylindrical part 286 is flush with the lower end face of the wing part 285 (stepped portion 2851). Thus, the sleeve-shaped 286 is formed with a first segment 284 having a generally cylindrical shape and a second segment 283 whose dimension in the tangential direction is larger than that in the radial direction.

[0068] In order to be adapted to the alignment wall 252 of the boss 251, the wing part 285 also has a cutting part 2852 at its outermost radial side. The cutting part 2852 extends axially upward from the lower end face of the wing part 285 (stepped portion 2851). The height of the cutting part 2852 in the axial direction and the length in the radial direction are respectively greater than or equal to the height and length of the alignment wall 252, and the height of the cutting part 2852 in the axial direction can be the same as the height of the stepped portion 2851, so that the alignment wall 252 is received in the cutting part 2852 when the sleeve is installed on the boss. A cutting part can also be provided at the innermost radial side of the wing part 285 to avoid interference between the sleeve 28 and other components.

[0069] When as Figure 9a shown, the assembled sleeve 28 is installed on the main bearing seat 25, referring to FIGS. 8a and Figure 8b, the upper end surface of the cylindrical portion 286 constitutes the second end surface 282 of the sleeve 28, and the lower end surface of the cylindrical portion 286 and the lower end surface of the wing portion 285 (step portion 2851) together constitute the first end surface 281 of the sleeve 28. Additionally, the alignment wall 252 of the main bearing seat 25 is placed in the radially outermost cutting portion 2852 of the wing portion 285, such that the alignment wall 252 contacts the cutting portion 2852 of the wing portion 285 and / or the outer wall of the cylindrical portion 286. Preferably, the alignment wall 252 contacts only the outer wall of the cylindrical portion 286 and does not contact the cutting portion 2852 of the wing portion 285. Thus, when the sleeve 28 is installed on the main bearing seat 25, the positioning of the sleeve 28 in the radial direction is completed by the cylindrical portion 286 and the alignment wall 252. Since the machining accuracy of the cylindrical portion is relatively high and machining is relatively convenient, using only the cylindrical portion for positioning can reduce the machining accuracy requirements for the wing portion. Additionally, since the sleeve in the second embodiment can be manufactured by directly adding a wing portion to the outer periphery of an existing cylindrical sleeve, the alignment wall not contacting the cutting portion of the wing portion also means that during the machining process of the wing portion, there is no need to consider precise matching with the alignment wall, reducing the machining requirements for the wing portion.

[0070] In the tangential direction, the wing portion 285 extends not beyond the contour of the upper surface 2511 of the boss 251, and the outer contour of the wing portion 285 is preferably substantially the same as the contour of the upper surface 2511 of the boss 251, thereby maximizing the size of the second segment within the limited space. In the radial direction, preferably, the radially outermost outer wall of the step portion 2851 of the wing portion 285 is substantially flush with the outer wall of the cylindrical portion 286; the radially outermost outer wall of the portion of the wing portion 285 other than the step portion 2851 is substantially flush with the radially outer wall of the boss 251. The radially innermost outer wall of the wing portion 285 can be substantially flush with or slightly exceed the radially inner wall of the boss 251, as long as the sleeve 25 does not interfere with other components within the compressor. In the axial direction, similar to the first embodiment, in the scroll compressor, preferably, the wing portion 285 is located between the flange 226 of the fixed scroll end plate and the boss 251 of the main bearing seat 25, that is, the first segment 283 where the wing portion 285 of the sleeve 28 is located is not inserted into the mounting hole of the flange 226, and only the second segment 284 of the sleeve 28 is inserted into the mounting hole of the flange 226.

[0071] Similar to the first embodiment, since the second section 283 of the sleeve 28 has a larger dimension in the tangential direction than in the radial direction, the bending stiffness of the sleeve 28 in the tangential direction is increased, thus matching the larger load received by the sleeve in the tangential direction. Thereby, the bending moment and stress at the end of the bolt are reduced, the fatigue strength of the bolt is enhanced, and the risk of fracture failure of the bolt is greatly reduced. This structure of the sleeve can also effectively prevent the sleeve from rotating and reduce the indentation of the sleeve on the boss. In addition, in the second embodiment, there is no need to replace the sleeve. By inserting the existing cylindrical sleeve into the wing portion 285, the split sleeve in the second embodiment can be formed, which is more convenient for production, installation and use, has a lower cost, and a wider adaptation range.

[0072] Figure 10 FIG. shows a partial schematic view of a scroll compressor according to a third embodiment of the present invention, in which an axial flexible mounting mechanism has been installed on the main bearing housing 35, and the fixed scroll has been removed to more clearly observe the axial flexible mounting mechanism. Refer to Figure 11a and Figure 11b , the sleeve 38 is received in the mounting hole of the flange 326 of the fixed scroll and is located between the head of the bolt 39 and the upper surface (contact surface) 3511 of the boss 351 of the main bearing housing 35. The second end face 382 of the sleeve 38 contacts the lower surface of the head of the bolt 39, and the first end face 381 of the sleeve 38 contacts the upper surface 3511 of the boss 351.

[0073] As Figure 12a and Figure 12b shown, similar to the split sleeve 28 in the second embodiment, the sleeve 38 is constructed in the form of an assembly including a split cylindrical portion 386 and a wing portion 385. Figure 12a FIG. shows the sleeve 38 after the cylindrical portion 386 and the wing portion 385 are assembled. Figure 12b FIG. shows the unassembled wing portion 385, and the cylindrical portion 386 is similar to the generally cylindrical sleeve structure in the existing scroll compressor, so it is not shown in the figure.

[0074] In the third embodiment, the wing portion 385 is also configured such that the dimension of its outer contour in the tangential direction is greater than the dimension in the radial direction. Different from the second embodiment, the upper surface of the wing portion 385 has a blind hole 3855 that is substantially the same diameter as the cylindrical portion 386, and the lower surface of the wing portion 385 has a through hole 3856 for the bolt 39 to pass through and adapted to the size of the bolt 39. The blind hole 3855 and the through hole 3856 are coaxial and communicate with each other. The cylindrical portion 386 is inserted into the blind hole 3855 of the wing portion 385. The lower end of the wing portion 385 is configured to have a stepped portion 3851 disposed around the through hole 3856. The stepped portion 3851 preferably has substantially the same dimension as the cylindrical portion 386 in the radial direction (especially radially outward), and extends from the through hole 3856 to the outermost tangential side of the wing portion 385 in the tangential direction. The height of the stepped portion 3851 in the axial direction can be greater than or equal to the height of the alignment wall 352 of the main bearing seat 35. When the cylindrical portion 386 and the wing portion 385 are assembled together to form the sleeve 38, the lower end surface of the cylindrical portion 386 is not flush with the lower end surface of the wing portion 385 (stepped portion 3851), that is, the cylindrical portion 386 does not penetrate the wing portion 385. Thus, the sleeve 38 is formed to have a first segment 384 with a substantially cylindrical shape and a second segment 383 whose dimension in the tangential direction is greater than the dimension in the radial direction.

[0075] To expand the fitting range of the sleeve, the wing portion 385 also has a cutting portion 3852 at its outermost radial side. The cutting portion 3852 extends axially upward from the lower end surface of the wing portion 385 (or the stepped portion 3851). The height of the cutting portion 3852 in the axial direction can be equal to or greater than the height of the alignment wall 352 and can be equal to the axial height of the stepped portion 3851. The length of the cutting portion 3852 in the radial direction can be equal to or greater than the length of the alignment wall 352. A cutting portion can also be provided at the innermost radial side of the wing portion 385 to avoid interference between the sleeve 38 and other components.

[0076] When the assembled sleeve as shown in Figure 12a is installed on the main bearing seat, referring to Figure 11a and Figure 11b , the upper end surface of the cylindrical portion 386 constitutes the second end surface 382 of the sleeve 38, and the lower end surface of the stepped portion 3851 of the wing portion 385 constitutes the first end surface 381 of the sleeve 38. In addition, the alignment wall 352 of the main bearing seat 35 is received in the cutting portion 3852 at the outermost radial side of the wing portion 385, such that the alignment wall 352 contacts the cutting portion 3852 of the wing portion 385 and / or the outer wall at the outermost radial side of the cylindrical portion 386. For example Figure 11a and Figure 12aAs shown, since the axial height of the through hole 3856 is less than the axial height of the stepped portion 3851, and the radial length of the cutting portion 3852 of the wing portion 385 is greater than the radial length of the alignment wall 352, a notch 3853 is formed on the radial side wall of the stepped portion 3851, and the outer wall of the cylindrical portion 386 is exposed from the notch 3853 of the stepped portion 3851 and contacts the alignment wall 352. Similar to the second embodiment, preferably, the alignment wall 352 only contacts the outer wall of the cylindrical portion 386 and does not contact the cutting portion 3852 of the wing portion 385. Therefore, when the sleeve 38 is installed on the main bearing seat 35, the radial positioning of the sleeve 38 is completed by the cylindrical portion 386 and the alignment wall 352.

[0077] In the tangential direction, the wing portion 385 extends not beyond the contour of the upper surface 3511 of the boss 351. The outer contour of the wing portion 385 is preferably substantially the same as the contour of the upper surface 3511 of the boss 351, so as to increase the size of the second segment 383 as much as possible within a limited space. In the radial direction, preferably, the outermost radial outer wall of the stepped portion 3851 of the wing portion 385 is substantially flush with the outer wall of the cylindrical portion 386 and jointly contacts the alignment wall 352; the outermost radial outer wall of the portion of the wing portion 386 other than the step is substantially flush with the radial outer wall of the boss 352. The innermost radial outer wall of the sleeve 38 can be substantially flush with or slightly exceed the radial inner wall of the boss 35 as long as there is no interference with other components in the compressor. In the axial direction, similar to the foregoing embodiments, in the scroll compressor, preferably, the wing portion 385 is located between the flange 326 of the fixed scroll end plate and the boss 351 of the main bearing seat 35, that is, the first segment 383 where the wing portion 385 of the sleeve 38 is located is not inserted into the mounting hole of the flange 326, and only the second segment 384 of the sleeve 38 is inserted into the mounting hole of the flange 326.

[0078] The sleeve 38 in the third embodiment has similar effects to the sleeve 28 in the second embodiment in preventing the sleeve from rotating, reducing the imprint of the sleeve on the boss, and facilitating production, installation, and use. In addition, the sleeve structure in the third embodiment can also obtain greater bending stiffness in the tangential direction, thereby enhancing the fatigue resistance of the bolt to a greater extent.

[0079] The alignment wall on the boss of the main bearing seat can also be omitted. In this case, the radial position of the sleeve is restricted by the inner wall of the housing. Figures 13 to 16b A sleeve capable of being installed on a main bearing seat without an alignment wall is shown.

[0080] Figure 13 and Figure 14The split sleeve 48 in the fourth embodiment is shown. The sleeve 48 is similar in structure to the sleeve 28 in the second embodiment. The sleeve 48 has a cylindrical portion 486 and a wing portion 485. The cylindrical portion 486 is inserted into a through hole in the center of the wing portion 485. Different from the sleeve in the second embodiment, the lower end of the wing portion 485 is not provided with a stepped portion and a cutting portion, but forms a plane with only a central through hole. The lower end surface of the cylindrical portion 486 is flush with the planar lower end surface of the wing portion 485, thus constituting the first end surface of the sleeve 48. When the sleeve 48 is installed on the boss 451 of the main bearing housing 45, the first end surface of the sleeve 48 contacts the upper surface of the boss 451. Preferably, the outer contour of the first end surface of the wing portion 485 is substantially the same as the outer contour of the upper surface of the boss 451, which can more effectively increase the bending moment of the wing portion 485 in the tangential direction, reduce stamping, and make manufacturing and installation more convenient.

[0081] Figure 15a and Figure 15b The split sleeve 58 in the fourth embodiment is shown. The sleeve 58 is similar in structure to the sleeve 38 in the third embodiment. The sleeve has a cylindrical portion 586 and a wing portion 585. The upper surface of the wing portion 585 has a blind hole 5855 that matches the cross-sectional shape of the cylindrical portion 586. The lower surface of the wing portion 585 has a through hole 5856 for the bolt to pass through, and the blind hole 5855 and the through hole 5856 are coaxial and communicate with each other. The cylindrical portion 586 is inserted into the blind hole 5855 of the wing portion 585. Different from the sleeve in the third embodiment, the lower end of the wing portion 585 is not provided with a stepped portion and a cutting portion, but forms a plane with only the through hole 5856. The lower end surface of the cylindrical portion 586 is not flush with the planar lower end surface of the wing portion 585, and only the lower end surface of the wing portion 585 constitutes the first end surface of the sleeve 58. When the sleeve 58 is installed on the boss, the first end surface of the sleeve 58 contacts the upper surface of the boss. Preferably, the outer contour of the lower end surface of the wing portion 585 (i.e., the first end surface of the sleeve 58) is the same as the outer contour of the upper surface (contact surface) of the boss, which can more effectively increase the bending moment of the wing portion in the tangential direction, reduce stamping, and make manufacturing and installation more convenient.

[0082] In the split sleeves described above, the cylindrical portion and the wing portion are preferably fixedly connected in a slightly interference fit manner. Additionally, although in the embodiments of the present disclosure, the inventors improved the sleeve for the case where the load on the sleeve in the tangential direction is greater than the load in the radial direction, that is, making the size of the sleeve in the tangential direction larger than the size in the radial direction. However, those skilled in the art will understand that for a compressor where the load on the sleeve in the radial direction is greater than the load in the tangential direction, the improvement method of the present disclosure is still applicable, and only the sleeve needs to be adaptively adjusted to have a larger size in the radial direction than in the tangential direction.

[0083] The following Table 1 lists the simulation analysis results of the force conditions of the axial flexible mounting mechanism in the existing scroll compressor and the scroll compressor according to the present disclosure, and a comparison is made in two cases where the bolt contacts the sleeve and the bolt does not contact the sleeve. Among them, referring to Figure 16a and Figure 16b , F represents the tangential force applied to the sleeve due to the perturbation of the moving scroll relative to the fixed scroll, and f1 and f2 respectively represent the forces on the upper and lower end faces of the sleeve.

[0084] Table 1

[0085]

[0086]

[0087] It can be observed from Table 1 that in the existing scroll compressor, when the sleeve is subjected to a large load (force F) in the tangential direction, the bending moment at the end of the bolt is large. Especially when the sleeve contacts the bolt, the bending moment of the bolt will rise sharply, with an increase of up to 25.6%, greatly increasing the risk of bolt loosening and fracture. However, in the scroll compressor according to the present disclosure, regardless of whether the bolt contacts the sleeve, the bending moment of the bolt is smaller than that of the bolt in the existing scroll compressor when the bolt does not contact the sleeve. When the bolt does not contact the sleeve, the bending moment of the bolt decreases by 37.6%. Even when the bolt contacts the sleeve, the bending moment of the bolt is still 22.5% lower than that of the bolt in the existing case when the bolt does not contact the sleeve. Therefore, the scroll compressor according to the present disclosure can significantly improve the fatigue strength of the bolt and greatly improve the problem of bolt loosening and fracture.

[0088] Although the present invention has been described with reference to exemplary embodiments, it should be understood that the present invention is not limited to the specific embodiments described and illustrated in detail herein. Without departing from the scope defined by the claims, those skilled in the art can make various changes to the exemplary embodiments. It should also be understood that, without conflict in the technical solutions, the features of each embodiment can be combined with each other or omitted.

Claims

1. A scroll compressor, comprising: a fixed scroll (2) and a moving scroll (3), the moving scroll (3) being configured to be able to move relative to the fixed scroll (2) to compress a fluid; a main bearing seat (5; 15; 25; 35; 45), the main bearing seat supporting the moving scroll (3); an axial flexible mounting mechanism, via which the fixed scroll (2) is connected to the main bearing seat such that the fixed scroll (2) can move a predetermined distance in the axial direction, the axial flexible mounting mechanism including bolts (9; 19; 29; 39) and sleeves (8; 18; 28; 38; 48; 58) provided on the outer periphery of the bolts, wherein the sleeve includes a first section (183; 283; 383) in contact with the main bearing seat and a second section (184; 284; 384) in contact with the fixed scroll in the axial direction, and the first section is configured to have a bending stiffness in the radial direction different from that in the tangential direction, wherein: for a scroll compressor in which the sleeve is subjected to a relatively large load in the radial direction, the sleeve is configured to have a relatively large bending stiffness in the radial direction; for a scroll compressor in which the sleeve is subjected to a relatively large load in the tangential direction, the sleeve is configured to have a relatively large bending stiffness in the tangential direction.

2. A scroll compressor, comprising: a fixed scroll (2) and a moving scroll (3), the moving scroll (3) being configured to be able to move relative to the fixed scroll (2) to compress a fluid; a main bearing seat (5; 15; 25; 35; 45), the main bearing seat supporting the moving scroll (3); an axial flexible mounting mechanism, via which the fixed scroll (2) is connected to the main bearing seat such that the fixed scroll (2) can move a predetermined distance in the axial direction, the axial flexible mounting mechanism including bolts (9; 19; 29; 39) and sleeves (8; 18; 28; 38; 48; 58) provided on the outer periphery of the bolts, wherein the sleeve includes a first section (183; 283; 383) in contact with the main bearing seat and a second section (184; 284; 384) in contact with the fixed scroll in the axial direction, and the first section is configured to have a bending stiffness in the radial direction different from that in the tangential direction, wherein the sleeve includes a cylindrical portion (186; 286; 386; 486) and a wing portion (185; 285; 385; 485; 585) extending outward from the outer periphery of the cylindrical portion, the first section being formed by the section of the sleeve provided with the wing portion, and the second section being formed by the section of the sleeve including only the cylindrical portion.

3. The scroll compressor according to claim 2, wherein, The wing portion has a different dimension in the tangential direction from its dimension in the radial direction. For a scroll compressor in which the sleeve is subjected to a relatively large load in the radial direction, the radial dimension of the wing portion is larger, and for a scroll compressor in which the sleeve is subjected to a relatively large load in the tangential direction, the tangential dimension of the wing portion is larger.

4. The scroll compressor according to claim 2, wherein, The cylindrical portion and the wing portion are formed integrally or separately.

5. The scroll compressor according to claim 4, wherein, When the cylindrical part and the wing-shaped part are formed separately: The lower end surface of the cylindrical part is flush with the lower end surface of the wing-shaped part, and the two together form the end surface of the sleeve that contacts the main bearing seat; or The lower end surface of the cylindrical part is not flush with the lower end surface of the wing-shaped part, and the lower end surface of the wing-shaped part forms the end surface of the sleeve that contacts the main bearing seat.

6. The scroll compressor according to claim 4, wherein, When the cylindrical part and the wing-shaped part are formed separately, the cylindrical part and the wing-shaped part are connected in an interference fit manner.

7. The scroll compressor according to claim 3, wherein The main bearing seat includes a boss (51; 151; 251; 351; 451) connected to the axial flexible mounting mechanism, and the wing-shaped part does not extend beyond the outer contour of the boss in the direction where the load on the sleeve is larger.

8. The scroll compressor according to claim 2, wherein, The main bearing seat includes a boss (51; 151; 251; 351; 451) connected to the axial flexible mounting mechanism, and the boss is provided with an alignment wall (52; 152; 252; 352) extending axially towards the fixed scroll. The wing-shaped part further includes a cutting part (2852; 3852) extending axially from the lower end surface of the wing-shaped part that contacts the main bearing seat towards the fixed scroll, for accommodating the alignment wall.

9. The scroll compressor according to claim 8, wherein, The alignment wall contacts the cutting part and / or the cylindrical part, for restricting the position of the sleeve.

10. The scroll compressor according to any one of claims 2 to 9, wherein, The lower end of the wing-shaped part (285) is configured to have a pair of crescent-shaped stepped parts (2851), and the stepped parts (2851) are arranged on both sides of the through hole at the center of the wing-shaped part (285) along the direction where the load on the sleeve is larger. The lower end surface of the stepped parts (2851) is configured to be the lower end surface of the wing-shaped part (285) that contacts the main bearing seat.

11. The scroll compressor according to any one of claims 2 to 9, wherein, The lower end of the wing-shaped part (385) is configured to have a stepped part (3851), and the stepped part (3851) is arranged to surround the through hole (3856) at the center of the wing-shaped part (285). The stepped part (3851) has the same size as or a smaller size than the cylindrical part (386) in the direction where the load on the sleeve is smaller. The lower end surface of the stepped part (3851) is configured to be the lower end surface of the wing-shaped part (385) that contacts the main bearing seat.

12. The scroll compressor according to claim 1 or 2, wherein, The first section is located between the fixed scroll and the main bearing seat, and at least a part of the second section is inserted into the mounting hole of the fixed scroll.

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