CN212479578U - Scroll compressor having a plurality of scroll members - Google Patents

Abstract

A scroll compressor, comprising: the scroll compressor further comprises a retaining mechanism and a positioning pin, wherein the retaining mechanism is arranged around the peripheral wall to limit radial movement of the fixed scroll, and the positioning pin is connected to a first mounting hole of the retaining mechanism and a second mounting hole of the main bearing seat and is arranged between the retaining mechanism and the main bearing seat in the axial direction, so that the axial position of the retaining mechanism relative to the main bearing seat is determined. According to the utility model discloses, scroll compressor's retaining mechanism is simpler, the materials is more saved with main bearing seat's processing to retaining mechanism is lower with main bearing seat's the installation degree of difficulty.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The present invention relates to a scroll compressor, and more particularly, to a fixed scroll retaining mechanism.

Background

A scroll compressor generally includes a housing, a drive mechanism accommodated in the housing, a scroll mechanism driven by the drive mechanism, a main bearing housing supporting the scroll mechanism, and the like. The scroll mechanism generally includes an orbiting scroll and a non-orbiting scroll which are engaged with each other. The fixed scroll is positioned in the compressor by a holding mechanism. On the one hand, the retention mechanism needs to limit the movement of the fixed scroll in the radial direction and to center the fixed scroll in the radial direction; on the other hand, the retaining mechanism can allow the non-orbiting scroll to axially move within a certain range, thereby providing a certain axial flexibility to the scroll compressor.

One commonly used method of holding the non-orbiting scroll in the prior art is: the fixed scroll is provided with a lug at the periphery thereof, a through hole is formed in the lug, a screw hole is formed in the arm portion of the main bearing housing, and the fixed scroll and the main bearing housing are fixed together by a bolt with a guide sleeve, thereby achieving radial centering of the fixed scroll. Since the through-holes formed in the lugs of the non-orbiting scroll are able to slide in the axial direction along the guide sleeve, the non-orbiting scroll is allowed to move slightly axially with respect to the main bearing housing.

Another way of holding the non-orbiting scroll, commonly used in the prior art, is: a guide ring is arranged on the periphery of the fixed scroll, a through hole is formed in the guide ring, and a bolt penetrates through the through hole in the guide ring and is screwed in a threaded hole of the main bearing seat. The guide ring can limit the fixed vortex in radial direction and allow the fixed vortex to move in a certain range along the axial direction.

However, of the above two types of non-orbiting scroll retaining methods, the first type of retaining method requires machining a boss and a through hole on the non-orbiting scroll and using a guide sleeve and a bolt in cooperation, which increases the radial size of the non-orbiting scroll and increases the assembly cost and the assembly time. The second retention method requires machining features on the guide ring that match the stationary components (e.g., main bearing housing) to achieve radial centering of the guide ring, which also increases the machining difficulty and cost of the compressor. Accordingly, there is a need for improved ways of retaining non-orbiting scroll members.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a scroll compressor with new retaining mechanism who decides the vortex, this scroll compressor not only can realize deciding the radial spacing of vortex, allow to decide the vortex for main bearing housing at certain extent axial motion, and processing is simple and convenient, the installation is easy, the materials are saved.

According to an aspect of the present invention, there is provided a scroll compressor, including: the scroll compressor further comprises a retaining mechanism and a positioning pin, wherein the retaining mechanism is arranged around the peripheral wall to limit radial movement of the fixed scroll, and the positioning pin is connected to a first mounting hole of the retaining mechanism and a second mounting hole of the main bearing seat and is arranged between the retaining mechanism and the main bearing seat in the axial direction, so that the axial position of the retaining mechanism relative to the main bearing seat is determined.

Optionally, the retaining means comprises a guide ring in radial clearance fit with the outer peripheral wall to guide axial movement of the non-orbiting scroll.

Optionally, the retention mechanism further includes a muffler cover dividing an inner space of the scroll compressor into a low pressure region and a high pressure region, the guide ring being formed separately from the muffler cover.

Optionally, the sound attenuation cover is in interference fit with the guide ring or connected by a fastener to secure the guide ring between the locating pin and the sound attenuation cover.

Optionally, the sound attenuating cap is a clearance fit with the guide ring, and the guide ring and/or the sound attenuating cap includes an outer flange portion extending radially outward, the outer flange portion being fixedly connected to the housing.

Optionally, the housing comprises a housing body and a top cover, and: the outer flange part of the guide ring is fixedly connected between the shell body and the top cover in the axial direction; or the outer flange portion of the guide ring is fixedly connected between the housing body and the top cover in the axial direction together with the outer flange portion of the sound-deadening cap.

Alternatively, the guide ring or the sound-deadening cap includes an inner flange portion extending radially inward, an abutment portion is formed at the non-orbiting scroll, and a predetermined distance exists between the inner flange portion and the abutment portion in the axial direction, thereby enabling the non-orbiting scroll to move axially within a range defined by the predetermined distance.

Optionally, the retaining mechanism further comprises a muffler cover dividing an inner space of the scroll compressor into a low pressure region and a high pressure region, the retaining mechanism being integrally formed with the muffler cover by the guide ring, the retaining mechanism comprising an outer flange portion extending radially outward and an inner flange portion extending radially inward, the outer flange portion being fixedly connected to the housing, the inner flange portion being axially spaced from an abutment portion of the non-orbiting scroll by a predetermined distance, thereby enabling the non-orbiting scroll to move axially within a range defined by the predetermined distance.

Alternatively, the housing includes a housing body and a top cover, and the outer flange portion of the holding mechanism is fixedly connected between the housing body and the top cover in the axial direction.

Optionally, the positioning pins are at least three positioning pins distributed along the circumferential direction.

Alternatively, the positioning pin is configured as a step pin having a first step portion that abuts against an end surface of the holding mechanism provided with the first mounting hole and/or a second step portion that abuts against an end surface of the main bearing housing provided with the second mounting hole.

Optionally, the step pin is an integrally formed integral pin, or the step pin is a split pin including a pin body and a sleeve sleeved on the pin body.

According to the scroll compressor of the utility model, the fixed scroll realizes radial centering and axial flexibility through the retaining mechanism, and the retaining mechanism is connected to the main bearing seat through the positioning pin and realizes radial centering and axial positioning, thereby avoiding the processing of the matching part of the retaining mechanism and the main bearing seat caused by the direct matching of the retaining mechanism and the main bearing seat, saving materials and reducing the processing and installation difficulty; the retaining mechanism may be integrally formed, thereby simplifying the installation process.

Drawings

The features and advantages of one or more embodiments of the present invention will become more readily apparent from the following description taken in conjunction with the accompanying drawings. The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way. The figures are not drawn to scale and some features may be exaggerated or minimized to show details of particular components. In the drawings:

FIG. 1 is a partial longitudinal cross-sectional view of a scroll compressor according to a first exemplary embodiment of the present invention;

FIG. 2 is a schematic perspective view of a portion of a scroll compressor according to a first exemplary embodiment of the present invention;

FIG. 3 is a cross-sectional view of a scroll compressor showing a cross-section of the scroll mechanism according to a first exemplary embodiment of the present invention;

FIG. 4 is an exploded isometric view of a portion of a scroll compressor according to a first exemplary embodiment of the present invention;

FIG. 5 is a fragmentary detail longitudinal sectional view of a scroll compressor according to a first exemplary embodiment of the present invention showing a retention mechanism of the scroll compressor;

fig. 6 is a perspective view of a step pin according to a first exemplary embodiment of the present invention;

fig. 7a, 7b and 7c show a perspective view of a step pin and its component parts, respectively, according to a second exemplary embodiment of the present invention;

FIG. 8 is a partial longitudinal cross-sectional view of a scroll compressor according to a third exemplary embodiment of the present invention;

FIG. 9 is a partial longitudinal cross-sectional view of a scroll compressor according to a fourth exemplary embodiment of the present invention;

FIG. 10 is a partial longitudinal cross-sectional view of a scroll compressor in accordance with a fifth exemplary embodiment of the present invention;

fig. 11 is a partial longitudinal sectional view of a scroll compressor according to a comparative example of the present invention; and

fig. 12 and 13 are perspective views of a main bearing housing and a guide ring of a scroll compressor according to a comparative example of the present invention, respectively.

Detailed Description

The preferred embodiments of the present invention will be described with reference to the accompanying drawings, which are illustrative only and do not constitute a limitation of the invention and its applications.

Fig. 1 is a partial longitudinal sectional view of a scroll compressor according to a first exemplary embodiment of the present invention. As shown in fig. 1, the scroll compressor 10 mainly includes a housing 20, a scroll mechanism, a main bearing housing 50, and a drive mechanism (not shown). The housing 20 generally includes a generally cylindrical housing body 26, a top cover 22, and a bottom cover (not shown), the housing body 26, the top cover (top cover) 22, and the bottom cover forming the complete housing 20 by, for example, welding. The scroll compressor 20 is also provided with a sound attenuating cap 24 positioned between the housing body 26 and the top cap 22 to separate the compressor interior space into the low pressure region 14 and the high pressure region 12. The working fluid enters the low pressure region 12 through a suction fitting 29 provided on the housing body 26, is compressed by the scroll mechanism and enters the high pressure region 12 and is discharged out of the scroll compressor 10 through a discharge fitting 28 provided on the top cover 22. The scroll mechanism includes a fixed scroll 30 and an orbiting scroll 40. The scroll mechanism is driven by a drive mechanism. Specifically, when the drive shaft of the drive mechanism rotates, orbiting scroll 40 can be driven via the crank pin of the drive shaft, and orbiting scroll 40 can make translational rotation with respect to non-orbiting scroll 30 due to oldham ring 80 coupled with orbiting scroll 40 and non-orbiting scroll 30. In other words, the axis of orbiting scroll 40 orbits in a circular orbit relative to the axis of non-orbiting scroll 30, but both orbiting and non-orbiting scrolls 40 and 30 do not themselves rotate about their respective axes. The scroll mechanism is supported by a main bearing housing 50, and the main bearing housing 50 is fixedly connected to the housing body 26 by, for example, caulking or the like or is formed integrally with the housing body 26.

Non-orbiting scroll 30 includes an end plate 31 and a spiral wrap 32 extending downward from one side of end plate 31. Wrap 32 of non-orbiting scroll 30 and wrap 42 of orbiting scroll 40 mesh with each other, thereby forming a series of compression pockets therebetween for compressing a fluid, such as a refrigerant. The non-orbiting scroll 30 further includes a substantially cylindrical outer peripheral wall 33 extending downward from the end plate 31 and provided at the outer periphery of the wrap 32 of the non-orbiting scroll 30. The non-orbiting scroll 30 is positioned in the scroll compressor 10 by a retaining mechanism. The retaining mechanism may include a guide ring 60. Referring to fig. 2 and 3, a guide ring 60 is disposed around the outer circumferential wall 33 of the non-orbiting scroll 30, a lower end of the guide ring 60 is connected to the main bearing housing 50 by a positioning pin 70, and an upper end of the guide ring 60 is caught by a sound-deadening cap 24. Main-bearing housing 50 includes a base and three boss portions 52 extending from one side of the base toward guide ring 60 (upward), the three boss portions 52 being circumferentially distributed on main-bearing housing 50. A positioning pin 70 is axially disposed between the guide ring 30 and the boss portion 52 of the main bearing housing 50, with one end fixed in the boss portion 52 and the other end connected to the guide ring 60, thereby determining the axial position of the guide ring 60 with respect to the main bearing housing 50. It will be understood by those skilled in the art that the number of boss portions 52 and positioning pins 70 is not limited to three as shown in the drawings, and may be more than three.

The inclusion of the guide ring 60 is described in detail below with reference to fig. 4 and 5. As shown in fig. 4 and 5, the guide ring 60 includes a generally annular ring body 61, an inner flange portion 68 extending radially inward from an inner side wall of the ring body 61, and an upper flange portion 64 extending axially upward from an upper end face of the ring body 61. The guide ring 60 is also provided with a first mounting hole 66 at a position of the lower end surface of the ring body 61 corresponding to the positioning pin 70. Second mounting hole 54 for receiving positioning pin 70 is formed in boss portion 52 of main bearing housing 50, second mounting hole 54 is axially aligned with first mounting hole 66, and positioning pin 70 is inserted at one end into first mounting hole 66 of guide ring 60 and at the other end into second mounting hole 54 of main bearing housing 50, thereby connecting guide ring 60 to main bearing housing 50. Since the boss portion 52 of the main bearing housing 50 and the second mounting holes 54 thereof are circumferentially distributed, the guide ring 60 positioned by the positioning pins 70 can be mounted in a radially centered manner. It will be appreciated by those skilled in the art that main-bearing housing 50 may not include boss portion 52, but rather, dowel pin 70 may be directly coupled to main-bearing housing 50.

Referring to fig. 6, the positioning pin 70 is configured as a stepped pin having a stepped portion 74. The positioning pin 70 includes a first diameter portion 71, a second diameter portion 72, and a third diameter portion 73, and the diameters of the second diameter portion 72 and the third diameter portion 73 are smaller than the diameter of the first diameter portion 71. Second and third diameter portions 72 and 73 are formed at both ends of positioning pin 70, respectively, and first diameter portion 72 is formed at the middle section of positioning pin 70, so that first and second stepped portions 74 and 75 are formed at the junction of second diameter portion 72 and first diameter portion 71 and the junction of third diameter portion 73 and first diameter portion 71, respectively. Referring to fig. 5, the second diameter portion 72 is matched with the first mounting hole 66 of the guide ring 60, and the third diameter portion 73 is matched with the second mounting hole 54 of the main bearing housing 60, so that when the second diameter portion 72 and the third diameter portion 73 at both ends of the positioning pin 70 are inserted into the first mounting hole 66 and the second mounting hole 54, respectively, which are aligned in the axial direction, the first stepped portion 74 is abutted with the lower end surface of the ring body 61 of the guide ring 60, on which the first mounting hole 66 is provided, and the second stepped portion 75 is abutted with the upper end surface of the boss portion 52 of the main bearing housing 50, on which the second mounting hole 54 is provided, whereby the axial position of the guide ring 60 with respect to the main bearing housing 50 is determined by the positioning pin 70. An axial distance between a lower end surface of the ring body 61 of the guide ring 60 and an upper end surface of the boss portion 52 of the main bearing housing 50 may be equal to an axial length of the first diameter portion 71 of the positioning pin 70. The second and third diameter portions 72, 73 may be configured to have smooth surfaces, and the first and second mounting holes 66, 54 may be correspondingly configured as smooth blind holes. Preferably, third diameter portion 73 may be configured with external threads and second mounting hole 54 is configured as a threaded hole that mates therewith to further enhance the connection of locating pin 70 to the main bearing housing.

By configuring the pilot pin as a step pin having two steps such that the axial distance of the guide ring relative to the main bearing housing depends only on the length of the first diameter portion of the step pin regardless of the total length of the pin or the depth of the mounting hole, the axial position of the guide ring can be determined more accurately and more simply.

In addition. It will be understood by those skilled in the art that although the positioning pin 70 is configured as a stepped pin having two steps in the first exemplary embodiment, the positioning pin 70 may have only one step or no step. In this case, the axial position of the guide ring relative to the main bearing housing may be determined by the length of the positioning pin and the depth to which the first and second mounting holes can receive the positioning pin.

The upper end of the guide ring 60 may be axially restrained by the sound attenuating cap 24. Specifically, referring to fig. 5, the upper flange portion 64 of the guide ring 60 can form an interference connection or a clearance fit with the sound-deadening cap 24, thereby holding the guide ring 60 at a fixed position in the axial direction between the first step portion 74 of the dowel pin 70 and the sound-deadening cap 24. In order to fix the guide ring 60 in the casing more stably and reliably, the guide ring 60 further includes an outer flange portion 62 extending radially outward from the outer side wall of the ring body 1, and the outer flange portion 62 is inserted into the gap a between the casing body 26 and the top cover 22 to be fixedly connected between the casing body 26 and the top cover 22 in the axial direction, for example, the guide ring 60 may be fixed to the casing by welding through the outer flange portion 62 when the casing is welded. The sound-deadening cap 24 may be formed with an outer flange portion extending outward to the gap a so as to be fixedly connected between the case body 26 and the top cover 22 together with the outer flange portion 62 of the guide ring 60, and for example, the guide ring 60, the sound-deadening cap 24, the case body 26, and the top cover 22 may be welded and fixed together when the case is welded, thereby further simplifying the process and saving the processing material.

The pilot ring 60 enables radial centering of the non-orbiting scroll 30, since the pilot ring 60 is radially and axially limited by the locating pin 70, so that the pilot ring 60 can be fixed in the compressor housing radially centered and at a desired axial height. In addition, the guide ring 60 can also achieve axial position limitation of the non-orbiting scroll 40 in case the non-orbiting scroll 30 needs to have axial flexibility. Specifically, referring to fig. 5, the inner side wall of the ring body 61 of the guide ring 60 forms a clearance fit with the outer peripheral wall 33 of the non-orbiting scroll 30, thereby achieving radial centering of the non-orbiting scroll 30 and restricting radial movement of the non-orbiting scroll 30 (making the non-orbiting scroll 30 hardly movable in the radial direction), and in addition, the inner side wall of the ring body 61 can also serve as a guide surface for guiding axial movement of the non-orbiting scroll 30. The outer peripheral wall 33 of the non-orbiting scroll 30 is also formed with a third step portion 34 (abutting portion), and a certain gap (a predetermined distance in the axial direction) is formed between the lower surface of the inner flange portion 68 of the guide ring 60 and the upper surface of the third step portion 34, thereby allowing the non-orbiting scroll 30 to move in the axial direction within a predetermined range defined by the predetermined distance. Since the axial position of the guide ring 60 is determined by the positioning pin 70, the size of the gap between the lower surface of the inner flange portion 68 of the guide ring 60 and the upper surface of the third stepped portion 34, that is, the range in which the non-orbiting scroll 30 can move in the axial direction is also indirectly determined by the positioning pin 70. That is, in the case where the sizes of other components are determined, the size of the pilot pin 70, particularly, the axial length of the first diameter section 71 is determined, that is, the axial movement range of the non-orbiting scroll 30 can be determined. In addition, it will be appreciated by those skilled in the art that the inner sidewall of the inner flange 68 of the guide ring 60 may also form a clearance fit with the outer peripheral wall 33 of the non-orbiting scroll 30 to help achieve radial centering of the non-orbiting scroll 30 and to limit radial movement of the non-orbiting scroll 30.

Effects of the present invention will be described below with reference to the scroll compressor 10a in the comparative example shown in fig. 11 to 13. As shown in fig. 11, 12, 13, in the comparative example, the non-orbiting scroll 30a of the scroll compressor 10a is held in position in the housing by the pilot ring 60 a. The guide ring 60a includes a substantially annular ring body 61a and a lower flange portion 68a extending axially downward from the ring body 61 a. The inner side wall of the ring body 61a forms a clearance fit with the outer peripheral wall 33a of the non-orbiting scroll 30a, thereby achieving radial centering of the non-orbiting scroll 30a and guiding axial movement of the non-orbiting scroll 30 a. A certain gap is formed between the free end surface 65a of the lower flange portion 68a and the upper surface of the third stepped portion 34a of the outer peripheral wall 33a of the non-orbiting scroll 30a, thereby allowing the non-orbiting scroll 30a to move within a certain range in the axial direction.

Radial centering and axial restraint of guide ring 60a is achieved by mating with main bearing housing 50 a. Specifically, referring to fig. 12, main-bearing housing 50a includes a base portion and a plurality of arm portions 52a (four in the example in the drawing) extending from one side of the base portion toward guide ring 60a (upward), the plurality of arm portions 52a being distributed on main-bearing housing 50a in the circumferential direction. Arm 52a includes an inside surface 56a and an upper surface 57 a. When the guide ring 60a is installed in the main bearing housing 50a, on the one hand, the inner side surfaces 56a of the arm portions 52a form a clearance fit with the outer side surfaces 63a of the lower flange portions 68a of the guide ring 60a, thereby radially centering the guide ring 60a and restricting the radial movement of the guide ring 60 a; on the other hand, the upper surfaces 57a of the arm portions 52a abut against the lower surface 69a of the ring body 61a of the guide ring 60a, thereby determining the axial position of the guide ring 60 a. Finally, the guide ring 60a is fixedly coupled to the main-bearing housing 50a by inserting fasteners (not shown) into the mounting holes 67a of the guide ring 60a and the mounting holes 59a on the arm portions 52a of the main-bearing housing 50 a.

In this comparative example, in order to achieve radial centering and axial limitation of the guide ring 60a, it is necessary to machine mutually matching structural features, such as the arm portion 52a including the inner side surface 56a, the upper surface 57a and the mounting hole 59a, and the lower flange portion 68a including the outer side surface 63a, on the guide ring 60a and the main bearing housing 50a, respectively. Therefore, both the guide ring 60a and the main bearing 50a have complicated structures, which not only make the machining and installation difficult, but also consume more material and cause an increase in cost. In contrast, in the present invention, the guide ring 60 is radially centered and the determination of the axial position of the guide ring 60 is achieved by a plurality (three or more) of the positioning pins 70, without processing mutually matching structural features on the guide ring and the main bearing housing. The positioning pin 70 is a universal part, and is easier to produce and install, so the holding mechanism for the fixed scroll of the present invention is easier to produce and assemble, saves more material, and has good reliability. Additionally, the utility model discloses can also adopt current production module to produce, consequently have good suitability.

Fig. 7a, 7b and 7c show a positioning pin 70' according to a second exemplary embodiment of the invention. In the second exemplary embodiment of the present invention, the main structure and function of the scroll compressor are substantially the same as those of the scroll compressor 10 of the first exemplary embodiment, and therefore, the description thereof is omitted. The difference is that the scroll positioning pin 70' is configured as a stepped pin formed by the co-assembly of a pin body 701 and a sleeve 702 that is fitted over the pin body 701. Specifically, the pin body 701 passes through a through hole in the sleeve 702 such that the sleeve 702 is located at the middle section of the pin body 701, thereby forming the first diameter portion 71' of the stepped pin. Two sections of the pin body 701 located outside the sleeve 702 form the second diameter portion 72 'and the third diameter portion 73' of the stepped pin, respectively. A clearance fit or interference fit is formed between the pin body 701 and the sleeve 702, thereby forming a first step 74 'between the first diameter portion 71' and the second diameter portion 72', and a second step 75' between the first diameter portion 71 'and the third diameter portion 73'.

According to the second exemplary embodiment, since the positioning pin 70' is assembled by the pin body 701 and the bushing 702, the processing difficulty is further reduced and the processing process is simplified as compared to an integrally formed step pin.

Fig. 8 is a partial longitudinal sectional view of a scroll compressor 110 according to a third exemplary embodiment of the present invention. The scroll compressor 110 is substantially identical to the main structure and function of the scroll compressor 10 of the first exemplary embodiment and therefore will not be described in detail. The difference is that the retaining mechanism of the scroll compressor 110 includes not only the guide ring but also the silencing cover, and the guide ring and the silencing cover are integrally formed to configure the silencing cover 160 having the function of the guide ring. The sound-deadening cap 160 includes a substantially annular ring body 161 and a cap-like portion 124 located above the ring body 161. The sound-deadening cap 160 further includes an inner flange portion 168 extending radially inward from the inner sidewall of the ring body 161 and an outer flange portion 162 extending radially outward from the outer sidewall of the ring body 161. The lower end of the ring body 161 of the sound-deadening cap 160 is provided with a first mounting hole 166 for receiving the second diameter portion 72 of the dowel pin 70, so that the sound-deadening cap 160 is connected to the main bearing housing 50 through the dowel pin 70. The outer flange portion 162 of the sound-deadening cap 160 is inserted into the gap a for welding between the case body 26 and the top cover 22, so that the sound-deadening cap 160 is weld-fixed to the case when the case is welded. On one hand, the inner side wall of the ring body 161 of the sound-deadening cap 160 forms a clearance fit with the outer peripheral wall 33 of the non-orbiting scroll 30, thereby achieving radial centering of the non-orbiting scroll 30 and restricting radial movement of the non-orbiting scroll 30, and the inner side wall of the ring body 161 can also serve as a guide surface for guiding axial movement of the non-orbiting scroll 30; on the other hand, a certain gap is formed between the inner flange portion 168 of the sound-deadening cap 160 and the third stepped portion 34 of the outer peripheral wall 33 of the non-orbiting scroll 30, thereby allowing the non-orbiting scroll 30 to move within a certain range in the axial direction. In addition, the cover-shaped portion 124 of the sound-deadening cover 160 is disposed between the housing body 26 and the top cover 22 to divide the compressor internal space into the low-pressure region and the high-pressure region 12.

According to the third exemplary embodiment, since the holding mechanism is configured as the noise elimination cover having the guide ring function, the number of parts is further reduced, the mounting process is simplified, and the mounting accuracy is improved, as compared with the guide ring and the noise elimination cover which are separate bodies.

FIG. 9 is a partial longitudinal cross-sectional view of a scroll compressor 210 according to a fourth exemplary embodiment of the present invention. The scroll compressor 210 is substantially identical to the main structure and function of the scroll compressor 10 of the first exemplary embodiment and therefore will not be described in detail. The difference is that the retention mechanism of the scroll compressor 210 includes the pilot ring 260 and the sound attenuating cap 224, wherein the pilot ring 260 is no longer secured to the housing (e.g., welded to the housing by the outer flange portion 62 of the pilot ring 260 as shown in FIG. 5), but is only secured in its axial position by the sound attenuating cap 224. Specifically, the guide ring 260 includes a substantially annular ring body 261 and an inner flange 268 extending radially inward from an inner sidewall of the ring body 261, and a certain gap is formed between the inner flange 268 and the third step 34 of the outer peripheral wall 33 of the non-orbiting scroll 30, thereby allowing the non-orbiting scroll 30 to move within a certain range in the axial direction. In one aspect, the lower end of the ring body 261 of the guide ring 260 is provided with a first mounting hole 266 for receiving the second diameter portion 72 of the guide pin 70, so that the guide ring 260 is coupled to the main bearing housing 50 through the guide pin 70. On the other hand, a fourth stepped portion 265 is formed at the upper end of the ring body 261 of the guide ring 260, and the peripheral edge portion 225 of the muffler cover 224 abuts against the fourth stepped portion 265 to be interference-coupled with the guide ring 260, thereby fixing the guide ring 260 in the axial direction. Further, the sound-deadening cap 224 has an outer flange portion 262 extending radially outward from its outer side wall, and the outer flange portion 262 is inserted into the gap a for welding between the case body 26 and the top cover 22, so that the sound-deadening cap 224 is welded and fixed to the case through the outer flange portion 262 when the case is welded. Thereby, the guide ring 260 is sandwiched between the sound-deadening cap 224 and the positioning pin 70, specifically, between the peripheral edge portion 225 of the sound-deadening cap 224 and the second stepped portion 74 of the positioning pin 70, and is held fixed in the housing.

According to the fourth exemplary embodiment, since the guide ring is held and fixed in the housing only by the sound deadening cap and the positioning pin, it is no longer necessary to provide an outer flange portion for weld fixation on the guide ring, thereby further simplifying the processing and assembling process and reducing the production difficulty.

FIG. 10 is a partial longitudinal cross-sectional view of a scroll compressor 310 according to a fourth exemplary embodiment of the present invention. The scroll compressor 310 is substantially identical in main structure and function to the scroll compressor 210 of the third exemplary embodiment, and therefore, will not be described in detail. The difference is that the pilot ring 260 in the retention mechanism of the scroll compressor 310 is only used to achieve radial centering of the non-orbiting scroll 30, while axial retention of the non-orbiting scroll 30 is achieved by the sound-deadening cap 324. Specifically, the guide ring 360 is formed in a substantially annular shape. The lower end of the guide ring 360 is provided with a first mounting hole 366 for receiving the second diameter portion 72 of the positioning pin 70, so that the guide ring 360 is coupled to the main bearing housing 50 through the positioning pin 70. The upper end of guide ring 360 is interference-coupled with peripheral edge portion 325 of sound-deadening cap 324 or coupled by a fastener such as a bolt, thereby restraining guide ring 360 in the axial direction. Thereby, guide ring 360 is sandwiched between sound-deadening cover 324 and positioning pin 70, specifically, between peripheral edge portion 325 of sound-deadening cover 324 and second stepped portion 74 of positioning pin 70, and is held fixed in the housing. The inner side wall of the guide ring 360 forms a clearance fit with the outer peripheral wall 33 of the non-orbiting scroll 30, thereby achieving radial centering of the non-orbiting scroll 30 and restricting radial movement of the non-orbiting scroll 30 (making the non-orbiting scroll 30 hardly movable in the radial direction), and in addition, the inner side wall of the guide ring 360 can serve as a guide surface for guiding axial movement of the non-orbiting scroll 30.

Sound-deadening cap 324 includes an outer flange portion 362 extending radially outwardly from its outer sidewall and an inner flange portion 368 extending radially inwardly from its inner sidewall. Outer flange portion 362 is inserted into gap a for welding between housing body 26 and top cover 22, so that sound-deadening cover 324 is welded and fixed to the housing by outer flange portion 362 at the time of welding the housing. A certain gap is formed between the inner flange portion 368 and the third stepped portion 34 of the outer peripheral wall 33 of the fixed scroll 30, thereby allowing the fixed scroll 30 to move within a certain range in the axial direction.

In the fifth exemplary embodiment, similar to the fourth exemplary embodiment, since the guide ring is held and fixed in the housing only by the noise reduction cover and the positioning pin, the processing and assembling processes are further simplified, and the production difficulty is reduced. In addition, the guide ring only has a simple annular structure, so that the existing production module can be directly utilized, the applicability is better, and the production cost is lower.

It will be appreciated by those skilled in the art that the present invention allows for a variety of axial limitations to control the axial position of the guide ring and secure the guide ring in the housing, and is not limited to the specific means described in the exemplary embodiments of the invention.

Although various embodiments of the present invention have been described in detail herein, it is to be understood that the invention is not limited to the precise embodiments herein described and illustrated, and that other modifications and variations may be effected by one skilled in the art without departing from the spirit and scope of the invention. All such variations and modifications are intended to fall within the scope of the present invention. Moreover, all the components described herein may be replaced by other technically equivalent components.

Claims (12)

1. A scroll compressor, the scroll compressor comprising:

a housing;

vortex mechanism, vortex mechanism is including deciding the vortex, decide the vortex and include: an end plate, a scroll extending from the end plate, and an outer peripheral wall provided at an outer periphery of the scroll; and

a main bearing housing supporting the scroll mechanism;

characterized in that the scroll compressor further includes a retaining mechanism disposed around the outer peripheral wall to restrict radial movement of the non-orbiting scroll, and a positioning pin connected to a first mounting hole of the retaining mechanism and a second mounting hole of the main bearing housing and disposed axially between the retaining mechanism and the main bearing housing to determine an axial position of the retaining mechanism relative to the main bearing housing.

2. The scroll compressor of claim 1, wherein the retention mechanism includes a guide ring radially clearance fitted with the outer peripheral wall to guide axial movement of the non-orbiting scroll.

3. The scroll compressor of claim 2, wherein the retention mechanism further comprises a muffler cover dividing an interior space of the scroll compressor into a low pressure region and a high pressure region, the pilot ring being formed separately from the muffler cover.

4. The scroll compressor of claim 3, wherein the sound dampening cover is in interference fit with the pilot ring or is connected by fasteners to secure the pilot ring between the pilot pin and the sound dampening cover.

5. The scroll compressor of claim 3, wherein the sound attenuating cap is a clearance fit with the pilot ring, the pilot ring and/or the sound attenuating cap including a radially outwardly extending outer flange portion fixedly connected to the housing.

6. The scroll compressor of claim 5, wherein the housing includes a housing body and a top cover, and wherein:

an outer flange portion of the guide ring is fixedly connected between the housing body and the top cover in an axial direction; or

The outer flange portion of the guide ring is fixedly connected in the axial direction between the housing body and the top cover together with the outer flange portion of the silencing cover.

7. The scroll compressor of claim 3, wherein the guide ring or the sound attenuating cap includes an inner flange portion extending radially inward, an abutment portion being formed at the non-orbiting scroll, and a predetermined distance exists between the inner flange portion and the abutment portion in an axial direction, thereby enabling the non-orbiting scroll to move axially within a range defined by the predetermined distance.

8. The scroll compressor of claim 2, wherein the retention mechanism further comprises a sound-deadening cap that separates an interior space of the scroll compressor into a low-pressure region and a high-pressure region, the retention mechanism being integrally formed with the sound-deadening cap by the guide ring, the retention mechanism comprising an outer flange portion extending radially outward and an inner flange portion extending radially inward, the outer flange portion being fixedly connected to the housing, the inner flange portion being axially spaced from an abutment portion of the fixed scroll by a predetermined distance so as to enable axial movement of the fixed scroll within a range defined by the predetermined distance.

9. The scroll compressor of claim 8, wherein the housing includes a housing body and a top cover, and the outer flange portion of the retention mechanism is fixedly connected in an axial direction between the housing body and the top cover.

10. The scroll compressor of any one of claims 1-9, wherein the locating pin is at least three locating pins distributed circumferentially.

11. The scroll compressor of any one of claims 1-9, wherein the positioning pin is configured as a step pin having a first step portion that abuts an end surface of the retention mechanism where the first mounting hole is provided and/or a second step portion that abuts an end surface of the main bearing housing where the second mounting hole is provided.

12. The scroll compressor of claim 11, wherein the stepped pin is an integrally formed one-piece pin or the stepped pin is a split pin including a pin body and a sleeve that fits over the pin body.

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