CN112012925A

CN112012925A - Scroll compressor having a plurality of scroll members

Info

Publication number: CN112012925A
Application number: CN201910465901.0A
Authority: CN
Inventors: 韩艳春; 梁计; 张跃; 王小燕; 刘利涛
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2019-05-30
Filing date: 2019-05-30
Publication date: 2020-12-01

Abstract

The application relates to a scroll compressor comprising a fixed scroll, a movable scroll, a main bearing seat and an axial flexible mounting mechanism. The fixed scroll is engaged with the orbiting scroll to compress a working fluid. The main bearing housing has a bearing surface for supporting the orbiting scroll end plate. Fixedly connecting the non-orbiting scroll to the connecting portion of the main bearing housing via the axially flexible mounting mechanism enables the non-orbiting scroll to move a predetermined distance in the axial direction. The non-orbiting scroll further has a flange extending radially outwardly from the peripheral wall portion thereof, the flange having an axial geometric center position between the first surface and the second surface, the flange being positioned such that the axial geometric center position is located on a side of the peripheral wall portion that is closer to the orbiting scroll end plate with respect to an axial intermediate position thereof. The scroll compressor is configured such that, in normal operation, the axial position of the point of equivalent effect of the force applied to the axially flexible mounting mechanism is offset toward the main bearing housing relative to the axial geometric center position.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The present invention relates to a scroll compressor, and more particularly, to a scroll compressor capable of preventing a failure of an axially flexible mounting mechanism.

Background

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

Scroll compressors may be used in applications such as refrigeration systems, air conditioning systems, and heat pump systems. The scroll compressor includes a compression mechanism for compressing a working fluid (e.g., a refrigerant), a main bearing housing for supporting the compression mechanism, a rotary shaft for driving the compression mechanism, and a motor for driving the rotary shaft to rotate. The compression mechanism comprises a fixed scroll and an movable scroll which orbits in translation relative to the fixed scroll. The fixed scroll and the orbiting scroll each include an end plate and a spiral vane extending from one side of the end plate. When the movable scroll orbits relative to the fixed scroll, a series of moving compression chambers, the volume of which gradually decreases from the radially outer side to the radially inner side, are formed between the spiral vanes of the fixed scroll and the movable scroll, thereby compressing the working fluid.

In normal operation of a scroll compressor, a good seal is required between the tip of the spiral vane of one of the fixed scroll and the orbiting 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 may be separated from the end plate to discharge the high-pressure fluid, thereby preventing the compression mechanism from being damaged.

To this end, the fixed scroll is mounted to the main bearing housing by an axially flexible mounting mechanism so that the fixed scroll can move axially a distance relative to the movable scroll. The axially flexible mounting mechanism typically includes a bolt and a sleeve located outside the bolt. A bolt is inserted into the mounting hole of the non-orbiting scroll to screw-couple the non-orbiting scroll to the main bearing housing. The sleeve is also inserted into the mounting hole of the fixed scroll and is arranged between the bolt head and the main bearing seat, so that a certain gap exists between the bolt head and the fixed scroll for the axial movement of the fixed scroll.

Disclosure of Invention

The inventor of the application finds that the bolt of the axial flexible mounting mechanism is easy to loosen or break, and deeply researches the reason of the fatigue damage of the bolt and provides a solution capable of improving the fatigue resistance of the bolt.

It is an object of the present disclosure to provide a scroll compressor capable of preventing or reducing damage to an axially flexible mounting mechanism.

According to one aspect of the present disclosure, a scroll compressor is provided. The scroll compressor comprises a fixed scroll, a movable scroll, a main bearing seat and an axial flexible mounting mechanism. The non-orbiting scroll has a non-orbiting scroll end plate and a non-orbiting scroll blade extending from one side of the non-orbiting scroll end plate. The orbiting scroll has an orbiting scroll end plate and an orbiting scroll blade extending from one side of the orbiting scroll end plate, the orbiting scroll being configured to be able to orbit relative to the non-orbiting scroll such that a series of compression chambers for compressing a working fluid are formed between the non-orbiting scroll blade and the orbiting scroll blade. The main bearing housing is fixedly mounted to a shell of the scroll compressor and has a bearing surface for slidably supporting the orbiting scroll end plate. Fixedly connecting the non-orbiting scroll to the connecting portion of the main bearing housing via the axially flexible mounting mechanism enables the non-orbiting scroll to move a predetermined distance in an axial direction. The non-orbiting scroll further has a flange extending radially outward from a peripheral wall portion thereof, the flange having a first surface facing the non-orbiting scroll end plate, a second surface facing the orbiting scroll end plate, and a mounting hole extending from the first surface to the second surface for receiving the axial flexible mounting mechanism, the flange having an axial geometric center position between the first surface and the second surface, the flange being positioned such that the axial geometric center position is located on a side of the peripheral wall portion that is close to the orbiting scroll end plate with respect to an axial intermediate position thereof. The height of the flange between the first surface and the second surface is H1, the distance between the axial position of the equivalent point of action of the force borne by the axial flexible mounting mechanism and the second surface is H1, the distance between the first surface and the end surface of the connecting part is H2, the distance between the second surface and the end surface is H2, the distance between the axial position of the equivalent point of action and the end surface is H, and H1+ H2. The scroll compressor is configured such that, in normal operation, the axial position of the point of equivalent effect of the force applied to the axially flexible mounting mechanism is offset toward the main bearing housing relative to the axial geometric center position.

According to the scroll compressor of the present disclosure, by offsetting the equivalent point of action axial position of the force applied to the axially flexible mounting mechanism with respect to the axial geometric center position toward the main bearing housing, the distance h, i.e., the moment arm distance D from the equivalent point of action axial position to the breaking position P, can be reduced, and thus the bolt breakage can be significantly alleviated or prevented.

In some examples, an outer contour of the axially flexible mounting mechanism and/or an inner contour of the mounting hole of the flange has a convex section such that the equivalent point of action axial position is offset toward the main bearing housing relative to the axial geometric center position.

In some examples, the protruding section is in the form of a curved surface or in the form of a shoulder forming a step.

In some examples, the flange includes an extension extending from the second surface in the axial direction toward the main bearing housing beyond a top surface of the non-orbiting scroll blade.

In some examples, the connection of the main bearing housing that engages the axially flexible mounting mechanism extends beyond the bearing surface in the axial direction toward the flange.

In some examples, the axially flexible mounting mechanism includes a bolt and a sleeve located outside the bolt; or the axially flexible mounting mechanism comprises a shoulder bolt.

In some examples, 0< H2/H1< 0.3; 0< H2/H2< 0.3; 0< H/H1<0.6 or 0< H/H2< 0.6.

According to the present disclosure, a scroll compressor is also provided. The scroll compressor comprises a fixed scroll, a movable scroll, a main bearing seat and an axial flexible mounting mechanism. The non-orbiting scroll has a non-orbiting scroll end plate and a non-orbiting scroll blade extending from one side of the non-orbiting scroll end plate. The orbiting scroll has an orbiting scroll end plate and an orbiting scroll blade extending from one side of the orbiting scroll end plate, the orbiting scroll being configured to be able to orbit relative to the non-orbiting scroll such that a series of compression chambers for compressing a working fluid are formed between the non-orbiting scroll blade and the orbiting scroll blade. The main bearing housing has a bearing surface for slidably supporting the orbiting scroll end plate. Fixedly connecting the non-orbiting scroll to the connecting portion of the main bearing housing via the axially flexible mounting mechanism enables the non-orbiting scroll to move a predetermined distance in an axial direction. The non-orbiting scroll also has a flange extending radially outward from a peripheral wall portion thereof, the flange having a first surface facing the non-orbiting scroll end plate, a second surface facing the orbiting scroll end plate, and a mounting hole extending from the first surface to the second surface for receiving the axially flexible mounting mechanism. The height of the flange between the first surface and the second surface is H1, the distance between the axial position of the equivalent point of action of the force borne by the axial flexible mounting mechanism and the second surface is H1, the distance between the first surface and the end surface of the connecting part is H2, the distance between the second surface and the end surface is H2, the distance between the axial position of the equivalent point of action and the end surface is H, and H1+ H2. The flange and/or the connecting portion extend toward each other in the axial direction such that the second surface of the flange passes over a top surface of the non-orbiting scroll blade and/or the end surface of the connecting portion passes over the bearing surface.

According to the scroll compressor of the present disclosure, by extending the connecting portions of the flange and the main bearing housing toward each other, the distance h, i.e., the moment arm distance D from the equivalent point of action axial position to the breaking position P can be reduced, and thus the bolt breakage can be significantly alleviated or prevented.

In some examples, 0< H2/H1< 0.3; 0< H2/H2< 0.3; 0< H/H1<0.6 or 0< H/H2< 0.6.

In some examples, the scroll compressor is configured such that, in normal operation, the equivalent point of action axial position is offset toward the main bearing housing relative to an axial geometric center location between the first and second surfaces.

In some examples, an outer contour of the axially flexible mounting mechanism or an inner contour of the mounting hole of the flange has a convex section such that the equivalent point of action axial position is offset toward the main bearing housing relative to the axial geometric center position.

Further areas of applicability of the present invention will become apparent from the detailed description provided hereinafter. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the invention, are intended for purposes of illustration only and are not intended to limit the invention.

Drawings

Features and advantages of one or more embodiments of the present invention will become more readily understood from the following description with reference to the accompanying drawings, in which:

FIG. 1 is a schematic perspective view of a scroll compressor according to an embodiment of the present disclosure;

FIG. 2 is a schematic partial cross-sectional view of the scroll compressor of FIG. 1;

FIG. 3 is an enlarged, fragmentary schematic view of the scroll compressor of FIG. 2;

FIG. 4 is a schematic view, partially in section, of a scroll compressor according to another embodiment of the present disclosure;

FIG. 5 is an enlarged, fragmentary schematic view of the non-orbiting scroll of the scroll compressor of FIG. 4;

FIG. 6 is a schematic view, partially in section, of a scroll compressor according to yet another embodiment of the present disclosure;

FIG. 7 is an enlarged, fragmentary schematic view of the non-orbiting scroll of the scroll compressor of FIG. 6;

FIG. 8 is a schematic view in partial cross-section of a scroll compressor according to another embodiment of the present disclosure;

FIG. 9 is an enlarged, fragmentary schematic view of a main bearing housing of the scroll compressor of FIG. 8;

FIG. 10 is a parametric dimension schematic of the axial compliant mounting mechanism of the scroll compressor in relation to the non-orbiting scroll and main bearing housing;

11 a-11 d are schematic diagrams of parameter dimensions according to various embodiments of the present disclosure;

FIG. 12 is a graph illustrating the effectiveness of a scroll compressor according to the present disclosure; and

fig. 13 is a schematic view illustrating a bolt fracture failure position.

Detailed Description

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

The exemplary embodiments are provided so that this disclosure will be thorough and will more fully convey the scope to those skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.

The general structure of the scroll compressor 100 is described below with reference to FIG. 1. As shown, the compressor 100 includes a housing 11, a compression mechanism CM, a motor 16, a rotating shaft (which may also be referred to as a drive shaft or a crankshaft) 14, and a main bearing housing 15.

The housing 11 may include a cylindrical body 11a, a top cover 11b at a top end of the cylindrical body 11a, and a bottom cover 11c at a bottom end of the cylindrical body 11 a. The housing 11 forms a closed space in which the compression mechanism CM, the motor 16 rotating shaft 14, and the main bearing housing 15 are accommodated. A partition 11d may also be provided between the top cover 11b and the cylindrical body 11 a. The partition 11d partitions the closed space of the housing 11 into a high pressure side defined by the partition 11d and the top cover 11b and a low pressure side defined by the partition 11d, the cylindrical body 11a and the bottom cover 11 c.

An inlet port (not shown) for introducing a working fluid having a suction pressure into the housing 11 is provided on the cylindrical body 11 a. The head cover 11b is provided with a discharge port 11e for discharging the working fluid compressed by the compression mechanism CM and having a discharge pressure out of the housing 11. When the scroll compressor 100 is operated, a low-pressure working fluid is introduced into the compressor 100 through the inlet port (introduced to the low-pressure side in the example of fig. 1), is then sucked into the compression mechanism CM, is discharged to the high-pressure side after being compressed, and is finally discharged out of the scroll compressor 100 through the discharge port 11 e.

The compression mechanism CM includes a fixed scroll 12 and an orbiting scroll 13 fixed to the housing 11 (specifically, the cylindrical body 11 a). The motor 16 is configured to rotate the rotary shaft 14, and then the rotary shaft 14 drives the orbiting scroll 13 to orbit relative to the non-orbiting scroll 12 (i.e., the central axis of the orbiting scroll moves around the central axis of the non-orbiting scroll, but the orbiting scroll does not rotate around the central axis thereof) to compress the working fluid. The translational rotation is achieved by means of a cross slip ring 17 (see fig. 2).

Non-orbiting scroll 12 may be fixed relative to housing 11 in any suitable manner, as illustrated by being fixedly bolted to main bearing housing 15, as will be described in detail below. Non-orbiting scroll 12 may include a non-orbiting scroll end plate 122, a non-orbiting scroll blade 124 extending from one side of the non-orbiting scroll end plate 122, and a discharge port 121 located substantially at a central portion of the non-orbiting scroll end plate 122. For convenience of description, the radially outermost portion of the non-orbiting scroll blade 124 will be referred to herein as a peripheral wall portion 126. As shown in fig. 2, the non-orbiting scroll 12 further has a flange 128 extending radially outward from the outer peripheral surface of the peripheral wall portion 126. Mounting holes 127 are provided in flange 128 for receiving an axially flexible mounting mechanism for attachment to main bearing housing 15.

Orbiting scroll 13 may include an orbiting scroll end plate 132, an orbiting scroll blade 134 formed at one side of the orbiting scroll end plate 132, and a hub 131 formed at the other side of the orbiting scroll end plate 132. The non-orbiting scroll blade 124 and the orbiting scroll blade 134 are engageable with each other such that a series of moving compression chambers, the volume of which is gradually reduced from the radially outer side to the radially inner side, are formed between the non-orbiting scroll blade 124 and the orbiting scroll blade 134 when the scroll compressor is operated, thereby achieving compression of the working fluid. The boss portion 131 is engaged with an eccentric crank pin of the rotary shaft 14 and is driven by the eccentric crank.

Main bearing housing 15 is adapted to support orbiting scroll end plate 132 of orbiting scroll 13. Orbiting scroll end plate 132 orbits on a bearing surface 155 (see fig. 2) of main bearing housing 15. The main bearing housing 15 may be fixed relative to the housing 11 of the scroll compressor 100 by any suitable means.

In order to achieve compression of fluid, an effective seal is required between the non-orbiting scroll 12 and the orbiting scroll 13.

On the one hand, radial sealing is also required between the side surface of the spiral vane 124 of the non-orbiting scroll 12 and the side surface of the spiral vane 134 of the orbiting scroll 13 in normal operation of the scroll compressor. This radial seal between the two is typically achieved by means of centrifugal force of the orbiting scroll 13 during operation and the driving force provided by the rotating shaft 14. When incompressible foreign objects such as solid foreign objects and liquid refrigerant enter the compression chamber to get caught between the

spiral vanes

124 and 134, the

spiral vanes

124 and 134 can be temporarily separated from each other in the radial direction to allow the foreign objects to pass through, thereby preventing damage to the

spiral vanes

124 and 134, thereby providing radial flexibility to the scroll compressor 100.

On the other hand, in normal operation of the scroll compressor, axial sealing is required between the tip of the spiral vane 124 of the non-orbiting scroll 12 and the end plate 132 of the orbiting scroll 13, and between the tip of the spiral vane 134 of the orbiting scroll 13 and the end plate 122 of the non-orbiting scroll 12. When the pressure in the compression chambers of the scroll compressor is excessive, the fluid in the compression chambers will leak to the low pressure side through the gap between the tips of the spiral vanes 124 of the non-orbiting scroll 12 and the end plate 132 of the orbiting scroll 13 and the gap between the tips of the spiral vanes 134 of the orbiting scroll 13 and the end plate 122 of the non-orbiting scroll 12 for unloading, thereby providing axial flexibility to the scroll compressor 100.

To provide axial flexibility, non-orbiting scroll 12 is mounted to main bearing housing 15 by an axially flexible mounting mechanism 18. Referring to FIG. 2, the axially flexible mounting mechanism 18 includes a bolt 181 and a sleeve 182 located radially outward of the bolt 181. The bolt 181 has a shank 1813, a head 1811 at one end of the shank 1813, and a threaded portion 1817 at the other end of the shank 1813. The head 1811 has an abutment surface 1812 for abutting an upper end face 1821 (see fig. 3) of the sleeve 182 and an upper surface (first surface) 1281 of the flange 128. The threaded portion 1817 is configured to be screwed into the threaded hole 151 of the main bearing housing 15. Sleeve 182 is also received in mounting hole 127 of flange 128 of non-orbiting scroll 12 and between head 1811 and upper surface 153 of main bearing housing 15, thereby defining the position of head 1811 such that non-orbiting scroll 12 can move a predetermined distance in the axial direction.

The inventors have found that the bolts of existing axially flexible mounting mechanisms are susceptible to loosening or breaking. The reason why the bolt is easily loosened or broken is analyzed with reference to fig. 13. The stressing of the bolt is complicated and the description is simplified here only to understand the cause of the break. The position P indicated by the dotted line is a position where the bolt is easily broken and fails, and is located at the upper screw joint portion between the bolt 3 and the main bearing housing 2. This "upper threaded engagement portion" is referred to herein as a proximal engagement portion, depending on the distance from the flange 128. As described above, when the orbiting scroll (not shown in fig. 13) orbits with respect to the non-orbiting scroll 1, a blade side contact force (acting force) is generated due to centripetal acceleration, which is transmitted to the bolt 3 via the sleeve 4. It is generally considered that the equivalent point of action of the force F exerted by the non-orbiting scroll 1 on the bolt 3 is at a position corresponding to the axial geometric center point of the flange of the non-orbiting scroll 1. The position P is at a distance D from the force F, thus producing a moment M (product of the force F and the distance D) about the position P as a fulcrum. This moment M makes the bolt susceptible to breaking at the position P. The present disclosure is directed to mitigating or preventing bolt breakage by reducing distance D. For convenience of description herein, it is assumed that the distance of the position P from the upper surface 2a of the main bearing housing 2 (i.e., the axial height of the counterbore 2 b) is constant in the respective embodiments. Thus, by reducing the distance h from the upper surface 2a of the main bearing housing 2 to the point of equivalent action of the force F, bolt breakage can be slowed or prevented.

When the compressor is normally operated, the orbiting scroll applies a force to the sleeve through a flange (lug) of the non-orbiting scroll. Typically, the flange of the non-orbiting scroll is in face-to-face contact engagement with the sleeve, and thus the force applied to the sleeve can be considered as a distributed force over a certain contact area. When the effect of these distributed forces is equated to a concentrated force (force F as described herein), the location of this concentrated force F is the axial location of the point of equivalence of force F as described herein.

To reduce the distance h, the flange 182 of the non-orbiting scroll is located at a position of the peripheral wall portion 126 below the lower half close to the main bearing housing 15, preferably, extending radially outward from the end of the peripheral wall portion 126 (the lower surface 1283 of the flange 182 is substantially flush with the top surface of the vane 124).

Fig. 1-3 show one example of reducing the distance h by modifying the outer profile of the sleeve 182. As shown, the outer profile (outer circumferential surface) of the sleeve 182 is not a cylindrical shape of constant diameter, but has a convex section 1828. The dashed line C1 in fig. 2 represents the axial geometric center position of the flange 128, and the dashed line C2 corresponds to the maximum diameter portion 1829 of the projecting section 1828 and thus represents the position of contact with the mounting hole 127 of the flange 182 (i.e., the equivalent point of action axial position of the force F). The protruding section 1828 has a decreasing diameter from the maximum diameter 1829 toward the upper surface (first surface) 1281 and the lower surface (second surface) 1283 of the flange 128. In the illustrated example, sleeve 182 also has a straight section 1827 of constant diameter on a side adjacent to main bearing housing 15. In FIG. 2, the distance from position P to the equivalent point of action axial position C2 is significantly less than the distance from position P to the axial geometric center position C1.

It should be understood that the disclosure is not limited to the particular examples illustrated. For example, projecting section 1828 may have a decreasing diameter from maximum diameter portion 1829 only toward first surface 1281 of flange 128, while having a constant diameter from maximum diameter portion 1829 to the end adjacent main bearing housing 15. In this case, the equivalent point of action axial position may be further shifted downward, that is, the distance from the position P to the equivalent point of action of the force may be further reduced. In the illustrated example, the protruding section 1828 is in the form of a curved surface, however, it should be understood that the protruding section 1828 may also be in the form of a shoulder that forms a step, and so forth. In the illustrated example, the sleeve 182 and the bolt 181 are separate components, however it should be understood that the sleeve 182 and the bolt 181 may be a unitary piece, i.e., a shoulder bolt.

As can be seen from the above, having the outer profile of the axially flexible mounting mechanism 18 with a convex section and having the equivalent point of action axial position C2 below the axial geometric center position C1 can mitigate or prevent the bolt 181 from breaking.

Fig. 4 and 5 show an example of reducing the distance h by improving the inner profile (shape of the inner wall) of the mounting hole 227 of the flange 228. As shown, the inner profile (shape of the inner wall) of the mounting hole 227 is not a cylindrical shape with a constant diameter, but has a protruding section 2272. Thus, the sleeve 282 may be cylindrical in shape with a constant diameter. Similar to the example of fig. 1-3, the dashed line C2 corresponds to the maximum diameter 2279 of the protruding section 2272 and thus represents the location of contact with the sleeve 282 (i.e., the equivalent point of action axial location of the force F). The projection sections 2272 have a reduced diameter from the maximum diameter portion 2279 toward the upper (first) surface 2281 and lower (second) surface 2283 of the flange 228. In the illustrated example, the mounting hole 227 also has a constant diameter straight section 2271 on a side adjacent the upper surface (first surface) 2281. In FIG. 4, the distance from position P to the equivalent point of action axial position C2 is significantly less than the distance from position P to the axial geometric center position C1.

It should be understood that the disclosure is not limited to the particular examples illustrated. For example, the projection section 2272 may have any other suitable form as long as the equivalent point of action axial position C2 is below the axial geometric center position C1.

Fig. 6 and 7 show another example of reducing the distance h by improving the structure of the flange 328. As shown, flange 328 also has an extension 3285 extending axially downward from lower surface (second surface) 3283 such that a lower end surface (third surface) 3284 of extension 3285 is below the top surface of non-orbiting scroll blade 124. In this example, the mounting hole 327 of the flange 328 may have a constant inner diameter, and the sleeve 382 may also have a constant outer diameter that is approximately equal to the inner diameter of the mounting hole 327.

In the example of fig. 6 and 7, the dashed line C1 still represents the axial geometric center position from the upper surface (first surface) 3281 to the lower surface (second surface) 3283, while the dashed line C2 corresponds to the axial geometric center position from the upper surface (first surface) 3281 to the lower end surface (third surface) 3284 and thus represents the equivalent point of action axial position of the force F exerted on the bolt. In this example, by extending the length of mounting hole 327 toward main bearing housing 15 such that the equivalent point of action axial position is offset toward main bearing housing 15, the distance from position P to the equivalent point of action axial position, i.e., distance h, may be reduced.

Fig. 8 and 9 show another example of reducing the distance h by improving the structure of the main bearing housing 15. As shown, the main bearing housing 15 has a connecting portion 452 for threaded engagement with a bolt 481. The connecting portion 452 may extend toward the flange such that an upper end surface 453 of the connecting portion 452 is higher than a support surface 455 for supporting the end plate 432 of the orbiting scroll 13, and more preferably, near a lower surface 4283 of the flange 428. As noted above, for ease of description herein, it is assumed that the distance of position P from the upper surface of the main bearing housing (i.e., the axial height of the counterbore) is constant in the various embodiments. Thus, in the example of fig. 8 and 9, the position P is offset toward the flange 428 by extending the connecting portion 452 toward the flange 428, thereby reducing the distance h.

The inventors have also conducted finite element analysis on certain parameters associated with the axially flexible mounting mechanism 18 and have designed to mitigate or prevent bolt breakage by optimizing certain parameters. Reference is now made to fig. 10 for an understanding of the parameters associated with mitigating or preventing bolt breakage. The same components in fig. 10 as those in fig. 8 are denoted by the same reference numerals as those in fig. 8.

As shown in fig. 10, the flange 428 has a height H1 between the first surface 4281 and the second surface 4283. The distance between the equivalent point of action axial position C2 of the force applied by the flange 428 to the axially flexible mounting mechanism and the second surface 4283 is h 1. The distance between the first surface 4281 and the end surface 453 of the connection portion 452 is H2. The distance between the second surface 4283 and the end surface 453 is h 2. The distance between the equivalent point of action axial position C2 and the end surface 453 is h, h being h1+ h 2.

The inventor finds that the bolt fracture can be remarkably relieved or prevented when the following conditions are met through finite element analysis: 0< H2/H1< 0.3; 0< H2/H2< 0.3; 0< H/H1< 0.6; or 0< H/H2< 0.6.

The inventors also tested the various embodiments described above within these parameters. Fig. 11a corresponds to the embodiment of fig. 1 to 3, and fig. 11b corresponds to the embodiment of fig. 4 and 5. In the example of fig. 11a and 11b, H1/H1 is 0.25 and H is 14.5, which tests show that this parameter can significantly mitigate or prevent bolt breakage.

Fig. 11c corresponds to the embodiment of fig. 8 and 9. In the example of fig. 11c, H2/H2 is 0.06, H/H2 is 0.36, and H is 9.3, which tests show that this parameter can significantly mitigate or prevent bolt breakage. Fig. 11d corresponds to the embodiment of fig. 6 and 7. In the example of fig. 11d, H2/H2 is 0.10, H/H2 is 0.55, and H is 14.3, which tests have shown to be able to significantly mitigate or prevent bolt breakage.

The inventors also tested the moment generated at position P at different distances h under the same force. In this test, the flange, main bearing housing and axially flexible mounting mechanism were identically constructed, only the value of distance h was changed. The test results are shown in table 1 below.

TABLE 1

Acting force F (N)	Distance h (mm)	Moment at position P (Nmm)
			3000	8.2	2803
3000	10.2	3229
			3000	12.2	3665
3000	14.2	4105
			3000	16.2	4546
3000	18.2	4975
			3000	20.2	5418
3000	22.2	5851
			3000	24.2	6289

The graph is plotted according to table 1, see fig. 12. Fig. 12 shows more intuitively that the smaller the distance h, the smaller the moment at position P. Therefore, by reducing the distance h, the bolt breakage can be significantly alleviated or prevented.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the specific embodiments described and illustrated in detail herein, and that various changes may be made to the exemplary embodiments by those skilled in the art without departing from the scope defined by the appended claims. It should also be understood that features of the various embodiments may be combined with each other or may be omitted without departing from the scope of the claims.

Claims

1. A scroll compressor, comprising:

a non-orbiting scroll having a non-orbiting scroll end plate and a non-orbiting scroll blade extending from one side of the non-orbiting scroll end plate;

an orbiting scroll having an orbiting scroll end plate and orbiting scroll blades extending from one side of the orbiting scroll end plate, the orbiting scroll configured to be able to orbit relative to the non-orbiting scroll such that a series of compression chambers for compressing a working fluid are formed between the non-orbiting scroll blades and the orbiting scroll blades;

a main bearing housing fixedly mounted to a shell of the scroll compressor and having a bearing surface for slidably supporting the orbiting scroll end plate; and

an axial flexible mounting mechanism via which the non-orbiting scroll is fixedly connected to the connecting portion of the main bearing housing such that the non-orbiting scroll can move a predetermined distance in an axial direction,

wherein the non-orbiting scroll further has a flange extending radially outwardly from a peripheral wall portion thereof, the flange having a first surface facing the non-orbiting scroll end plate, a second surface facing the orbiting scroll end plate, and a mounting hole extending from the first surface to the second surface for receiving the axial flexible mounting mechanism, the flange having an axial geometric center position between the first surface and the second surface, the flange being positioned such that the axial geometric center position is located on a side of the peripheral wall portion that is close to the orbiting scroll end plate with respect to an axial intermediate position thereof,

the height of the flange between the first surface and the second surface is H1, the distance between the axial position of the equivalent point of action of the force born by the axial flexible mounting mechanism and the second surface is H1, the distance between the first surface and the end surface of the connecting part is H2, the distance between the second surface and the end surface is H2, the distance between the axial position of the equivalent point of action and the end surface is H, H1+ H2,

the scroll compressor is configured such that, in normal operation, the equivalent point of action axial position is offset toward the main bearing housing relative to the axial geometric center position.

2. The scroll compressor of claim 1, wherein an outer profile of the axially flexible mounting mechanism and/or an inner profile of the mounting hole of the flange has a convex section such that the equivalent point of action axial position is offset toward the main bearing housing relative to the axial geometric center position.

3. The scroll compressor of claim 2, wherein the raised section is in the form of a curved surface or in the form of a shoulder forming a step.

4. The scroll compressor of claim 1, wherein the flange includes an extension extending from the second surface in the axial direction toward the main bearing housing over a top surface of the non-orbiting scroll blade.

5. The scroll compressor of claim 1, wherein a connection of the main bearing housing that engages the axially flexible mounting mechanism extends beyond the bearing surface in the axial direction toward the flange.

6. The scroll compressor of any one of claims 1 to 5, wherein the axially flexible mounting mechanism comprises a bolt and a sleeve located outside the bolt; or

The axially flexible mounting mechanism comprises a shoulder bolt.

7. The scroll compressor of any one of claims 1 to 5, wherein 0< H2/H1< 0.3.

8. The scroll compressor of any one of claims 1 to 5, wherein 0< H2/H2< 0.3.

9. The scroll compressor of any one of claims 1 to 5, wherein 0< H/H1< 0.6.

10. The scroll compressor of any one of claims 1 to 5, wherein 0< H/H2< 0.6.

11. A scroll compressor, comprising:

a main bearing housing having a support surface for slidably supporting the orbiting scroll end plate; and

wherein the non-orbiting scroll further has a flange extending radially outward from a peripheral wall portion thereof, the flange having a first surface facing the non-orbiting scroll end plate, a second surface facing the orbiting scroll end plate, and a mounting hole extending from the first surface to the second surface for receiving the axially flexible mounting mechanism,

the flange and/or the connecting portion extend toward each other in the axial direction such that the second surface of the flange passes over a top surface of the non-orbiting scroll blade and/or the end surface of the connecting portion passes over the bearing surface.

12. The scroll compressor of claim 11, wherein 0< H2/H1< 0.3.

13. The scroll compressor of claim 11, wherein 0< H2/H2< 0.3.

14. The scroll compressor of claim 11, wherein 0< H/H1< 0.6.

15. The scroll compressor of claim 11, wherein 0< H/H2< 0.6.

16. The scroll compressor of any one of claims 11 to 15, wherein the axially flexible mounting mechanism comprises a bolt and a sleeve located outside the bolt; or

The axially flexible mounting mechanism comprises a shoulder bolt.

17. The scroll compressor of any one of claims 11 to 15, wherein the scroll compressor is configured such that, in normal operation, the equivalent point of action axial position is offset toward the main bearing housing relative to an axial geometric center position between the first and second surfaces.

18. The scroll compressor of claim 17, wherein an outer profile of the axially flexible mounting mechanism or an inner profile of the mounting hole of the flange has a convex section such that the equivalent point of action axial position is offset toward the main bearing housing relative to the axial geometric center position.

19. The scroll compressor of claim 18, wherein the convex section is in the form of a curved surface or in the form of a shoulder forming a step.