scroll compressor

Abstract

The present disclosure relates to a scroll compressor, comprising: a scroll mechanism, which includes a fixed scroll and a movable scroll, the movable scroll being configured to be able to orbit relative to the fixed scroll to compress a working fluid; a main bearing seat, which supports the movable scroll; and an axially flexible mounting mechanism, which connects the fixed scroll to the main bearing seat via the axially flexible mounting mechanism so that the fixed scroll can move a predetermined distance in the axial direction, the axially flexible mounting mechanism including a fastener and a sleeve arranged on the outer periphery of the fastener, the size of the sleeve in the tangential direction being larger than the size in the radial direction, and the sleeve being equipped with two or more fasteners.

Description

Technical Field

[0001] The present disclosure relates to a scroll compressor, and more particularly, to an axially flexible mounting mechanism for a scroll compressor. Background Art

[0002] The contents in this section merely provide background information related to the present disclosure and may not constitute prior art.

[0003] Scroll compressors can be used in, for example, refrigeration systems, air-conditioning systems, and heat pump systems. The scroll compressor includes a scroll mechanism for compressing a working fluid (such as a refrigerant), a main bearing seat for supporting the scroll mechanism, a rotating shaft for driving the scroll mechanism, and a motor for driving the rotating shaft to rotate. The scroll mechanism includes a fixed scroll and a movable scroll that revolves relative to the fixed scroll. Both the fixed scroll and the movable scroll include an end plate and a spiral blade extending from one side of the end plate. When the movable scroll revolves relative to the fixed scroll, a series of moving compression chambers are formed between the spiral blades of the fixed scroll and the movable scroll, the volume of which gradually decreases from the radial outside to the radial inside, thereby compressing the working fluid.

[0004] During normal operation of a scroll compressor, a good seal must be achieved between the tip of the spiral blade of one of the fixed and orbiting scrolls 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 blade can separate from the end plate to unload the high-pressure fluid, thereby preventing damage to the scroll mechanism.

[0005] To this end, the fixed scroll is mounted to the main bearing seat by an axially flexible mounting mechanism so that the fixed scroll can move axially a certain distance relative to the orbiting scroll. The axially flexible mounting mechanism generally includes a fastener and a sleeve located outside the fastener. The fastener is inserted into the mounting hole of the fixed scroll's lug to thread the fixed scroll to the main bearing seat. The sleeve is also inserted into the mounting hole of the fixed scroll and is arranged between the fastener head and the main bearing seat so that there is a certain gap between the fastener head and the fixed scroll's lug to allow for axial movement of the fixed scroll. The fastener is generally a screw, bolt, or the like.

[0006] However, during the operation of scroll compressors, bolts often become loose or even break, and the connection between the main bearing seat and the bolts also poses a risk of cracking. To prevent the axially flexible mounting mechanism from failing, the bolts and the main bearing seat connected to them are often designed to be larger in size, especially in the radial direction, to ensure the strength of the bolts and the main bearing seat. However, this is not conducive to the miniaturization of scroll compressors. Summary of the Invention

[0007] The present disclosure provides a scroll compressor design that can reduce the compressor's dimensions, particularly in the radial direction, while maintaining the strength of the bolts and main bearing seat. In a scroll compressor according to the present disclosure, the risk of fracture failure of the bolts and main bearing seat is kept low, while also optimizing the space design within the scroll compressor, further miniaturizing the scroll compressor.

[0008] According to one aspect of the present disclosure, a scroll compressor is provided, comprising: a scroll mechanism, the scroll mechanism including a fixed scroll and a movable scroll, the movable scroll being configured to be able to orbit relative to the fixed scroll to compress a working fluid; a main bearing seat, the main bearing seat supporting the movable scroll; and an axially flexible mounting mechanism, the fixed scroll being connected to the main bearing seat via the axially flexible mounting mechanism, so that the fixed scroll can move a predetermined distance in an axial direction, the axially flexible mounting mechanism comprising a fastener and a sleeve arranged on the outer periphery of the fastener, the size of the sleeve in the tangential direction being larger than the size in the radial direction, and the sleeve being equipped with two or more fasteners.

[0009] Optionally, the fixed vortex includes a lug protruding radially outward from the outer peripheral surface of the fixed vortex, the lug having a mounting hole for the sleeve to pass through, the two first ends of the sleeve in the tangential direction being able to contact the inner side wall of the mounting hole, and there is a gap between the two second ends of the sleeve in the radial direction and the inner side wall of the mounting hole, so that the second ends do not contact the inner side wall of the mounting hole.

[0010] Optionally, in the radial cross section of the sleeve, the first end is configured as an arc segment, the second end is configured as a straight line segment, and the first end and the second end are connected by a transition segment, which does not contact the inner wall of the mounting hole.

[0011] Optionally, the transition section is constructed to extend from the arc segment toward the straight line segment with a curvature radius that is the same as the curvature radius of the arc segment and is tangent to the straight line segment; or the transition section is constructed to extend from the arc segment toward the straight line segment with a curvature radius that is smaller than the curvature radius of the arc segment and is tangent to the straight line segment.

[0012] Optionally, the extension angle of the arc segment is less than 100°.

[0013] Optionally, a radial gap between the second end portion and an inner sidewall of the mounting hole is greater than 0.1 mm.

[0014] Optionally, a sidewall thickness of a tangential side end portion of the lug adjacent to the first end portion in the tangential direction is greater than 30% of the diameter of the shank portion of the fastener.

[0015] Optionally, the sleeve includes two or more axial through holes for assembling the fastener, the axial through holes are distributed in the sleeve along the tangential direction, and the side wall thickness of the sleeve in the tangential direction between the first end and the axial through hole closest to the first end is greater than 30% of the diameter of the shank of the fastener.

[0016] Optionally, there are two fasteners, and a tangential distance between the two fasteners is greater than 2.1 times the diameter of the shank of the fastener and less than 5 times the diameter of the shank of the fastener.

[0017] Optionally, the scroll compressor is provided with three or four axially flexible mounting mechanisms uniformly distributed along the circumferential direction. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The features and advantages of one or more embodiments of the present disclosure will become more readily understood through the following description with reference to the accompanying drawings. The drawings described herein are for illustrative purposes only and are not intended to limit the scope of the present disclosure in any way. The drawings are not drawn to scale, and some features may be exaggerated or minimized to show details of particular components. In the drawings:

[0019] Figure 1 is a partial longitudinal sectional view of a scroll compressor according to the present disclosure;

[0020] Figure 2 for Figure 1 An enlarged detail view of section A in FIG, showing the axially flexible mounting mechanism;

[0021] Figure 3 is a perspective schematic diagram of a scroll mechanism according to a first embodiment of the present disclosure, wherein the scroll mechanism includes four axially flexible mounting mechanisms;

[0022] Figure 4 is a radial cross-sectional view of a scroll mechanism according to a first embodiment of the present disclosure;

[0023] Figure 5 for Figure 4 An enlarged detail view of section B in FIG. 1 , showing an axially flexible mounting mechanism;

[0024] Figure 6 It is a tangential cross-sectional view of an axially flexible mounting mechanism of the scroll mechanism according to the first embodiment of the present disclosure;

[0025] Figure 7 is a radial cross-sectional view of a scroll mechanism according to a second embodiment of the present disclosure, wherein the scroll mechanism includes three axially flexible mounting mechanisms;

[0026] Figure 8 It is a radial cross-sectional view of an existing scroll mechanism, wherein the scroll mechanism includes four axially flexible mounting mechanisms;

[0027] Figure 9a and Figure 9b Schematic diagrams comparing the force and bending moment distribution of the axially flexible installation mechanism according to the first embodiment and the second embodiment of the present disclosure and the existing axially flexible installation mechanism; and

[0028] Figure 10 A modified example of the axially flexible mounting mechanism of the scroll mechanism according to the present disclosure is shown. DETAILED DESCRIPTION

[0029] Example embodiments will now be described more fully with reference to the accompanying drawings.

[0030] Exemplary embodiments are provided so that this disclosure will be exhaustive and will more fully convey the scope to those skilled in the art. Many specific details, such as examples of specific components, devices, and methods, are described to provide a thorough understanding of the various embodiments of the present disclosure. It will be clear to those skilled in the art that specific details need not be employed, and that the exemplary embodiments can be implemented 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.

[0031] Refer to the following Figure 1 The overall structure of the scroll compressor 100 is described below. As shown in the figure, the compressor 100 includes a scroll mechanism, a motor, a rotating shaft (also called a drive shaft or crankshaft) 14, a main bearing 15, and a housing 11 surrounding the scroll mechanism and other components.

[0032] The scroll mechanism includes a fixed scroll 12 and an orbiting scroll 13. The motor is configured to rotate a rotary shaft 14, which in turn drives the orbiting scroll 13 to orbit relative to the fixed scroll 12 (i.e., the central axis of the orbiting scroll moves around the central axis of the fixed scroll, but the orbiting scroll does not rotate about its central axis) to compress the working fluid.

[0033] The fixed scroll 12 can be fixed relative to the housing 11 in any suitable manner, such as being fixedly mounted to the main bearing seat 15 by bolts as shown, which will be described in detail later. The fixed scroll 12 may include a fixed scroll end plate 122 and a fixed scroll blade 124 extending from one side of the fixed scroll end plate 122. Figure 2 As shown, the fixed scroll 12 further has a lug 126 extending radially outward from its radially outermost outer peripheral surface. A mounting hole is provided in the lug 126 for receiving an axially flexible mounting mechanism so as to be connected to the main bearing seat 15.

[0034] The orbiting scroll 13 may include an orbiting scroll end plate 132, orbiting scroll blades 134 formed on one side of the orbiting scroll end plate 132, and a hub 131 formed on the other side of the orbiting scroll end plate 132. The fixed scroll blades 124 and the orbiting scroll blades 134 can engage with each other, forming a series of compression chambers between the fixed scroll blades 124 and the orbiting scroll blades 134 when the scroll compressor is in operation, with the volume gradually decreasing from the radially outer side to the radially inner side, thereby compressing the working fluid. The hub 131 engages with the eccentric crank pin of the rotating shaft 14 and is driven by the eccentric crank.

[0035] The main bearing seat 15 is adapted to support the orbiting scroll end plate 132 of the orbiting scroll 13. The orbiting scroll end plate 132 orbits on a supporting surface of the main bearing seat 15. The main bearing seat 15 may be fixed relative to the housing 11 of the scroll compressor 100 in any suitable manner.

[0036] In order to achieve fluid compression, effective sealing is required between the fixed scroll 12 and the movable scroll component 13 .

[0037] On the one hand, when the scroll compressor is operating normally, radial sealing is also required between the side surfaces of the spiral blades 124 of the fixed scroll 12 and the side surfaces of the spiral blades 134 of the movable scroll 13. This radial sealing between the two is usually achieved by means of the centrifugal force of the movable scroll 13 during operation and the driving force provided by the rotating shaft 14. When incompressible foreign matter (such as solid impurities and liquid refrigerant) enters the compression chamber and gets stuck between the spiral blades 124 and 134, the spiral blades 124 and 134 can be temporarily separated from each other in the radial direction to allow the foreign matter to pass through, thereby preventing damage to the spiral blades 124 and 134, thereby providing radial flexibility for the scroll compressor 100.

[0038] On the other hand, when the scroll compressor is operating normally, axial sealing is required between the top of the spiral blade 124 of the fixed scroll 12 and the end plate 132 of the orbiting scroll 13, as well as between the top of the spiral blade 134 of the orbiting scroll 13 and the end plate 122 of the fixed scroll 12. 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 gap between the top of the spiral blade 124 of the fixed scroll 12 and the end plate 132 of the orbiting scroll 13, as well as the gap between the top of the spiral blade 134 of the orbiting scroll 13 and the end plate 122 of the fixed scroll 12 to achieve unloading, thereby providing axial flexibility for the scroll compressor 100.

[0039] In order to provide axial flexibility, the fixed scroll 12 is mounted to the main bearing seat 15 through an axially flexible mounting mechanism. Figure 2The main bearing seat 15 is provided with an axially extending boss 151 at its radially outermost side, and the boss 151 is axially aligned with the lug 126 of the corresponding fixed scroll 12. The axially flexible mounting mechanism includes a bolt 17 and a sleeve 19 located on the outer periphery of the bolt 17. A clearance fit is formed between the bolt 17 and the sleeve 19. The bolt 17 has a rod, a head located at one end of the rod, and a threaded portion located at the other end of the rod. The threaded portion is configured to be screwed into the threaded hole of the boss 151 of the main bearing seat 15. A clearance fit is formed between the lower surface of the head of the bolt 17 and the upper surface of the lug 126. The sleeve 19 is also received in the mounting hole of the lug 126 of the fixed scroll 12 and a clearance fit is formed between the lower end face of the sleeve 19 and the upper surface of the boss 151. A certain gap may be reserved between the lower surface of the head of the bolt 17 and the upper surface of the lug 26 , so that the fixed scroll 12 can move a predetermined distance in the axial direction, thereby providing axial flexibility for the scroll compressor 100 .

[0040] Figure 3 A three-dimensional schematic diagram of a scroll mechanism according to a first embodiment of the present disclosure is shown, wherein the fixed scroll 12 includes four lugs 126 evenly distributed along its circumference, with adjacent lugs forming an angle of 90°, and the main bearing seat 15 includes four bosses 151 axially aligned with the four lugs 126 of the fixed scroll 12, respectively. The fixed scroll 12 is mounted to the main bearing seat 15 by four axially flexible mounting mechanisms that are fixedly matched with each lug 126 and the corresponding boss 151. In other words, the four axially flexible mounting mechanisms are also evenly distributed along the circumferential direction of the fixed scroll 12, with adjacent axially flexible mounting mechanisms forming an angle of 90°. For a single axially flexible mounting mechanism including a bolt 17 and a sleeve 19, the bolt 17 includes two bolts 171 and 172, and the two bolts 171 and 172 are both assembled in one sleeve 19.

[0041] Figure 4 A radial cross-sectional view of a scroll mechanism according to a first embodiment of the present disclosure is shown. The sleeve 19 of the axially flexible mounting mechanism has a roughly racetrack-shaped radial cross-section, and its size in the radial direction is smaller than its size in the tangential direction. The sleeve 19 has two axial through holes 191, 192 distributed along the tangential direction, and two bolts 171, 172 are respectively inserted into the two axial through holes 191, 192 of the sleeve 19. Correspondingly, each lug 126 of the fixed scroll 12 has a mounting hole 127 that is roughly racetrack-shaped in radial cross-section and matches the outer circumferential surface of the sleeve 19, for accommodating the sleeve 19 and its bolts to pass through. In addition, the boss 151 of the main bearing seat 15 for supporting the sleeve 19 also has a radial cross-sectional shape that is adapted to the roughly racetrack-shaped radial cross-section of the sleeve 19, that is, the size of the radial cross-section of the boss 151 in the radial direction is also smaller than its size in the tangential direction.

[0042] See also Figure 5 A lug 126 of the fixed scroll 12 is shown ( Figure 4 In the enlarged detail view of section B in FIG, sleeve 19 is assembled in mounting hole 127 of lug 126. Sleeve 19 includes two first ends P1 and P2 in the tangential direction and two second ends Q1 and Q2 in the radial direction. The two first ends P1 and P2 form a small clearance fit with the inner sidewall of mounting hole 127 of lug 126, while the two second ends Q1 and Q2 form a clearance fit with the inner sidewall of mounting hole 127 of lug 126, forming a radial clearance d1. It should be noted that in this context, a small clearance fit means that when the sleeve is unloaded, there is a very small clearance between the first ends P1 and P2 and the inner sidewall of mounting hole 127 of lug 126, or the first ends P1 and P2 contact the inner sidewall of mounting hole 127 of lug 126 without generating any force on the contact surface. When the sleeve is loaded, the first ends P1 and P2 can contact the inner sidewall of mounting hole 127 of lug 126 and generate a force on the contact surface. The clearance fit means that no matter whether the sleeve is subjected to a load or not, the two second end portions Q1 and Q2 do not contact the inner side wall of the mounting hole 127 of the lug 126 .

[0043] The following combination Figure 6 A tangential cross-sectional view of a scroll mechanism according to a first embodiment of the present disclosure is shown; Figure 8 The radial cross-sectional view of the vortex mechanism in the prior art is shown to illustrate the difference in force conditions between the axial flexible mounting mechanism in the first embodiment of the present disclosure and the axial flexible mounting mechanism in the prior art, thereby illustrating how the axial flexible mounting mechanism in the present disclosure can achieve the effect of reducing its radial size while ensuring its strength.

[0044] See also Figure 8 , the existing vortex mechanism also includes a fixed vortex 2, a movable vortex 3 and an axially flexible mounting mechanism. The fixed vortex 2 has four lugs 26 evenly distributed along its circumference and the four axially flexible mounting mechanisms are respectively installed in the mounting holes of the four lugs 26. The difference from the first embodiment of the present disclosure is that each axially flexible mounting mechanism includes a sleeve 9 and a bolt 7. The sleeve 9 is roughly cylindrical and has an annular radial cross-section, and the bolt 7 is inserted into the mounting hole in the center of the sleeve 9. Correspondingly, the mounting hole of the lug 26 also has a circular radial cross-section, thereby matching the cylindrical outer contour of the sleeve 9.

[0045] When the movable scroll 3 revolves relative to the fixed scroll 2, a force F (not shown in the figure) is generated on the sleeve 9. The force F includes a force in the tangential direction and a force F1 in the radial direction. In particular, the force F1 distributed in the radial direction is transmitted to the bolt 7 through the sleeve 9, thereby generating bending moment and stress at the connection between the bolt 7 and the boss of the main bearing seat. In order to prevent the bending moment and stress here from causing the bolt 7 and / or the boss of the main bearing seat to fracture and fail, it is usually necessary to select large-sized bolts and design the radial dimensions of the boss of the main bearing seat to be larger, so as to ensure that the bolt 7 and the main bearing seat have sufficient strength to withstand the load. Obviously, this design is not conducive to reducing the radial dimensions of the compressor and is contrary to the trend of miniaturization of compressors.

[0046] In contrast, the axially flexible mounting mechanism according to the first embodiment of the present disclosure uses a sleeve 19 having a radial cross-section that is roughly runway-shaped, and each sleeve 19 is equipped with two bolts 171 and 172 in the tangential direction. Since the two first ends P1 and P2 of the sleeve 19 in the tangential direction can contact the lug 126 of the fixed scroll 12, while the two second ends Q1 and Q2 of the sleeve 19 in the radial direction cannot contact the lug 126, the force acting on the sleeve 19 of the present disclosure is basically converted into a force F2 that is distributed only in the tangential direction. In other words, the radial force acting on the sleeve 19 is greatly reduced, and therefore the bending moment and stress generated at the connection between the bolt and the main bearing seat are also greatly reduced. On the other hand, in the tangential direction, the double-bolt structure formed by the bolts 171 and 172 can better balance the bending moment, resulting in less stress. Specifically, in a single-bolt structure, due to the tangential load on the sleeve, a bending moment is generated. A couple of tensile and compressive stresses is generated at the shank of bolt 7 to balance the bending moment. Because the tensile and compressive stress regions are very close (approximately half the diameter of the shank of bolt 7), the resulting stress is relatively high. In contrast, in the dual-bolt structure according to the present invention, one of the two bolts 171 and 172 generates tensile stress while the other generates compressive stress, synergistically creating a couple that balances the bending moment. Because the distance d2 between the two bolts 171 and 172 is larger, the resulting stress is relatively low. Therefore, when comparing a single bolt 171 or 172 with bolt 7, the required dimensions of the single bolt 171 or 172 are reduced relative to those of bolt 7, provided the overall strength requirements of the axially flexible mounting mechanism are substantially the same.

[0047] In addition, for the boss 151 of the main bearing seat 15, since its size in the tangential direction is larger than that in the radial direction, its strength in the tangential direction is greater, which also matches the load direction of the boss 151. In other words, in the direction where the boss of the main bearing seat is subjected to a larger load (i.e., the tangential direction), the boss is stronger; in the direction where the boss of the main bearing seat is subjected to a smaller load (i.e., the radial direction), the boss is also weaker. Therefore, compared to Figure 8 The boss in the conventional scroll compressor shown, the radial dimension of the boss 151 is also reduced.

[0048] The present disclosure can reduce the radial size of the axial flexible mechanism and the main bearing seat (boss) by reducing the size of the bolts and optimizing the design of the sleeve and the main bearing seat, optimize the internal space design of the compressor, and facilitate the miniaturization of the compressor.

[0049] Refer to the following Figure 5 and Figure 10 The specific structure of the axially flexible mounting mechanism according to the first embodiment and its modified examples of the present disclosure is described. Figure 5In the first embodiment shown, from a radial cross-section, the first end P1 is configured as an arc segment S1, and the second end Q1 is configured as a straight segment S3. The first and second ends P1 and Q1 are connected by a transition segment S2 between the first and second ends P1 and Q1. Transition segment S2 is configured as an extension of arc segment S1 and is tangential to straight segment S3. In other words, transition segment S2 extends toward straight segment S3 with the same radius of curvature as arc segment S1. The other first end P2 and the other second end Q2 have the same structures as the first and second ends P1 and Q1, respectively. The two axial through-holes 191 and 192 of the sleeve 19 for inserting bolts 171 and 172 are positioned near the first and second ends P1 and P2, respectively, with the bolts 171 and 172 separated by a distance d2. Furthermore, assuming that the centers of the radial cross sections of the two bolts 171 and 172 lie on line 1, this line 1 intersects the circumferential contour of axial through-hole 192 at point R1, intersects arc segment S1 at point R2, intersects the circumferential contour of mounting hole 127 at point R3 (when first end P2 contacts lug 126, intersection R2 and intersection R3 coincide), and intersects the outer contour of lug 126 at point R4. The distance between R1 and R2 is h1, and the distance between R3 and R4 is h2. Of course, the first end P1 also has a similar structure to that of the first end P2. That is to say, the first end portion is respectively spaced apart from the tangential side wall of the axial through hole of the sleeve 19 closest to the first end portion, that is, the side wall thickness of the sleeve 19 in the tangential direction between the first end portion and the axial through hole of the sleeve 19 closest to the first end portion is h1, and the lug 126 has a tangential side end portion 128 adjacent to the first end portion, and the side wall thickness of the tangential side end portion 128 in the tangential direction is h2.

[0050] In order to reduce the radial force acting on the sleeve as much as possible so that the force acting on the sleeve is basically distributed only in the tangential direction, preferably, the extension angle α of the arc segment S1 is less than 100°, that is, the angle at which the first end of the sleeve contacts the lug of the fixed vortex is less than 100°. In addition, in the prior art, the lugs of the sleeve and the fixed vortex are mostly installed with a clearance fit, and the clearance is usually less than 0.05mm. Preferably, in the present disclosure, the radial clearance d1 between the second end portions Q1, Q2 and the inner side wall of the mounting hole 127 of the lug 126 is greater than 0.1mm, thereby ensuring that the second end portions Q1, Q2 do not contact the fixed vortex, so as to reduce the radial force acting on the sleeve as much as possible. The clearance between the second end portions Q1, Q2 and the transition section S2 and the lug 126 can be obtained by appropriately cutting material from the inner side wall of the mounting hole 127, thereby making it more convenient and flexible to adjust the size of the mounting hole, and being applicable to sleeves of more sizes. For example, see Figure 5Mounting hole 127 is cut into a radial cross-section consisting of an arc and a tangent at a certain angle. The arc is tangent to the sleeve's arc segment S1 but has a greater radius of curvature than that of arc segment S1. The tangent is parallel to straight segment S3 and separated from it by a gap d1. Furthermore, to enhance the dual-bolt structure's ability to balance bending moments, while maintaining the sleeve's total tangential length, the two bolts are preferably positioned as close as possible to the sleeve's tangentially outermost edges. The tangential distance d2 between the two bolts can be greater than 2.1 times the bolt shank diameter and less than 5 times the bolt shank diameter. This minimizes the bending moment experienced by the bolts while ensuring the strength of the axially flexible mounting mechanism and effectively utilizing the compressor's internal space. Furthermore, to ensure the strength of the fixed scroll and main bearing housing that cooperate with the axially flexible mounting mechanism, the sidewall thickness h1 of the sleeve 19 and the sidewall thickness h2 of the tangential end 128 of the lug 126 need to be greater than 0.3 times the bolt shank diameter.

[0051] It will be understood by those skilled in the art that although Figure 3 and Figure 4 It is shown that the fixed scroll is mounted to the corresponding four bosses of the main bearing seat through four lugs evenly distributed along its circumference and four axially flexible mounting mechanisms, but in a single scroll compressor, the number of axially flexible mounting mechanisms is not limited to four, but can be three or other suitable numbers.

[0052] Figure 7 A radial cross-sectional view of a scroll mechanism according to a second embodiment of the present disclosure is shown. The fixed scroll 22 has three lugs 226 evenly distributed along its circumference, with adjacent lugs 226 spaced 120° apart. Three axially flexible mounting mechanisms are inserted into the three lugs 226, respectively, to mount the fixed scroll 22 to the main bearing seat. Similar to the first embodiment, the axially flexible mounting mechanisms also include a sleeve 29 having a generally racetrack-shaped radial cross-section and two bolts 271, 272 inserted into the sleeve 29.

[0053] Figure 9a and Figure 9b Shown as Figure 8 The prior art shown in Figure 6 The first embodiment shown and Figure 7 The force and bending moment of the axially flexible mounting mechanism in the second embodiment are shown in FIG. Wherein, X represents the tangential direction and Y represents the radial direction. Figure 9aAs shown in the prior art, as the orbiting vortex disturbs the fixed vortex, the force acting on the sleeve is almost evenly distributed in a plane perpendicular to the axial direction. That is, the force acting on the sleeve includes both radial and tangential forces, and the magnitudes of the radial and tangential forces are substantially the same. Figure 6 The first embodiment shown and Figure 7 In the second embodiment shown, the forces acting on the sleeve are converted to be distributed almost only in the tangential direction, while the forces distributed in the radial direction are greatly reduced. Figure 9b As shown, the bending moment formed on the bolts in the first and second embodiments of the present disclosure is also greatly reduced compared with the prior art.

[0054] Since the radial force on the sleeve is greatly reduced in the present disclosure, the bending moment on the bolt is also greatly reduced. Under the condition that the overall load-bearing strength requirement of the compressor remains unchanged, the size of the bolt and the radial size of the sleeve, the lug of the fixed scroll and the boss of the main bearing seat can be reduced, thereby facilitating the miniaturization of the compressor. Figure 8 In the prior art shown in FIG, four axial flexible mounting mechanisms are evenly arranged along the circumference of the fixed scroll, including four M11 bolts, while the outer diameter of the compressor shell reaches 225 mm. Figure 6 In the first embodiment of the present disclosure, four axially flexible mounting mechanisms are evenly arranged along the circumference of the fixed scroll, including eight bolts of only M8 size. The outer diameter of the compressor shell can be only 190mm, reducing and saving about 16% of the radial size and material. Figure 7 The second embodiment of the present disclosure utilizes three axially flexible mounting mechanisms evenly spaced along the circumference of the fixed scroll, including six M9 bolts. This reduces the compressor casing outer diameter to just 200 mm, saving approximately 11% in radial dimension and material. Furthermore, because the bending moment on the bolts is significantly reduced, compressor reliability is further improved.

[0055] Figure 10A modified example of the axially flexible mounting mechanism according to the present disclosure is shown. Similar to the first embodiment, the axially flexible mounting mechanism in this modified example includes a sleeve 39 having a generally racetrack-shaped radial cross-section and two bolts 371, 372, respectively, inserted into two axial through holes distributed in the tangential direction of the sleeve 39. The sleeve 39 includes two first end portions P'1, P'2 in the tangential direction and two second end portions Q'1, Q'2 in the radial direction, and the two first end portions P'1, P'2 can contact the inner sidewall of the mounting hole 327 of the lug 326 of the fixed scroll, while the two second end portions Q'1, Q'2 do not contact the inner sidewall of the mounting hole 327 of the lug 326 of the fixed scroll. Specifically, from a radial cross-section, the first end portion P'1 is configured as an arc segment S'1, and the second end portion Q'1 is configured as a straight line segment S'3. The first end portion P'1 and the second end portion Q'1 are connected by a transition segment S'2 between the first end portion P'1 and the second end portion Q'1, and the transition segment S'2 does not contact the inner sidewall of the mounting hole 327 of the fixed scroll lug 326. Unlike the first embodiment, the transition segment S'2 is not configured as an extended arc segment of the arc segment S'1, but rather as an arc segment with a smaller curvature radius than the arc segment S'1 and is tangent to the straight line segment S'3. That is to say, during the processing and manufacturing process, a sleeve processing part that matches the inner wall of the mounting hole 327 of the lug 326 can be first manufactured (that is, if the sleeve processing part is inserted into the mounting hole 327 of the lug 326, the entire outer circumferential surface of the sleeve processing part can contact the inner wall of the mounting hole 327 of the lug 326), and then the outer circumferential surface of the sleeve processing part is appropriately cut off, that is, the part of the sleeve processing part other than the first end parts P'1 and P'2 is appropriately cut off to form the second end parts Q'1, Q'2 and the transition section S'2 that do not contact the fixed vortex to obtain the required sleeve finished product.

[0056] The axially flexible mounting component shown in this modified example can not only achieve the effect of reducing the bolt size and reducing the radial size of the boss of the fixed vortex and the main bearing seat similar to the axially flexible mounting component in the first embodiment, but also the sleeve is easier to produce and manufacture and has better adaptability.

[0057] In the embodiment described above, the sleeve's roughly runway-shaped radial cross-section design is combined with a double-bolt structure to achieve the effect of reducing the radial force on the sleeve, reducing the bending moment on the bolts, and thus reducing the radial dimensions of the axially flexible mounting mechanism, the fixed vortex, and the main bearing seat. However, it is conceivable for those skilled in the art that for a sleeve with a roughly runway-shaped radial cross-section, it can be used in conjunction with not only double bolts, but also multiple bolts greater than two, as long as it can reduce the radial force on the sleeve and / or reduce the bending moment on the bolts. In other words, the number of bolts provided in the sleeve is not limited to two. It is also conceivable for those skilled in the art that the component for connecting the fixed vortex and the main bearing seat in the axially flexible mounting mechanism is not limited to bolts, but can be screws or any other fasteners that can achieve similar effects.

[0058] Although the present disclosure has been described with reference to exemplary embodiments, it should be understood that the present disclosure is not limited to the specific embodiments described and illustrated herein, and that those skilled in the art may make various changes to the exemplary embodiments without departing from the scope defined by the claims. It should also be understood that the features of the various embodiments may be combined or omitted without conflicting technical solutions.

Claims

1. A scroll compressor (100), comprising: A vortex mechanism, the vortex mechanism comprising a fixed vortex (12) and a movable vortex (13), wherein the movable vortex (13) is configured to be able to orbit relative to the fixed vortex (12) to compress a working fluid; a main bearing seat (15), the main bearing seat (15) supporting the movable scroll (13); and An axially flexible mounting mechanism is provided, wherein the fixed scroll (12) is connected to the main bearing seat (15) via the axially flexible mounting mechanism, so that the fixed scroll (12) can move a predetermined distance in the axial direction, The axially flexible installation mechanism includes fasteners (17, 171, 172, 271, 272, 371, 372) and sleeves (19, 29, 39) arranged on the periphery of the fasteners. It is characterized in that the overall size of the sleeve in the tangential direction is larger than the size in the radial direction, and the sleeve is equipped with two or more fasteners, the radial direction is the radial direction of the vortex mechanism, and the tangential direction is the direction perpendicular to the radial direction on the orbiting plane of the vortex mechanism.

2. The scroll compressor (100) according to claim 1, characterized in that The fixed vortex (12) includes a lug (126) protruding radially outward from the outer peripheral surface of the fixed vortex (12), and the lug (126) has a mounting hole (127) for the sleeve to pass through. The two first end portions (P1, P2, P'1, P'2) of the sleeve in the tangential direction can contact the inner side wall of the mounting hole (127), and there is a gap between the two second end portions (Q1, Q2, Q'1, Q'2) of the sleeve in the radial direction and the inner side wall of the mounting hole (127), so that the second end portions do not contact the inner side wall of the mounting hole (127).

3. The scroll compressor according to claim 2, wherein: On the radial cross section of the sleeve, the first end is constructed as a circular arc segment (S1, S'1), the second end is constructed as a straight line segment (S3, S'3), and the first end and the second end are connected by a transition segment (S2, S'2), and the transition segment does not contact the inner side wall of the mounting hole (127).

4. The scroll compressor according to claim 3, wherein: The transition section (S2) is configured to extend from the arc section (S1) toward the straight section (S3) with a curvature radius that is the same as that of the arc section (S1), and to be tangent to the straight section (S3); or The transition segment (S'2) is configured to extend from the arc segment (S'1) toward the straight segment (S'3) with a curvature radius smaller than that of the arc segment (S'1), and be tangent to the straight segment (S'3).

5. The scroll compressor according to claim 3, wherein: The extension angle (α) of the circular arc segment (S1, S'1) is less than 100°.

6. The scroll compressor according to any one of claims 2 to 5, characterized in that: A radial gap (d1) between the second end portion and the inner side wall of the mounting hole (127) is greater than 0.1 mm.

7. The scroll compressor according to any one of claims 2 to 5, characterized in that The side wall thickness (h2) of the tangential side end portion (128) of the lug (126) adjacent to the first end portion in the tangential direction is greater than 30% of the diameter of the shank portion of the fastener.

8. The scroll compressor according to any one of claims 2 to 5, characterized in that: The sleeve comprises two or more axial through holes (191, 192) for assembling the fastener, the axial through holes (191, 192) being distributed in the sleeve along the tangential direction, and the side wall thickness (h1) of the sleeve in the tangential direction between the first end and the axial through hole closest to the first end is greater than 30% of the diameter of the shank of the fastener.

9. The scroll compressor according to any one of claims 1 to 5, characterized in that: There are two fasteners, and a tangential distance (d2) between the two fasteners is greater than 2.1 times the diameter of the shank of the fastener and less than 5 times the diameter of the shank of the fastener.

10. The scroll compressor according to any one of claims 1 to 5, characterized in that: The scroll compressor is provided with three or four axially flexible mounting mechanisms evenly distributed along the circumferential direction.

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