CN217813953U - Scroll compressor and cross slip ring and matching component for scroll compressor - Google Patents

Abstract

The utility model relates to a scroll compressor and be used for scroll compressor's cross sliding ring and cooperation part. The present application provides at least one of the engaging walls of the slide groove of the mating member and the key of the oldham ring with a predetermined rigidity and capable of elastic deformation by providing a hollow portion in the vicinity of the at least one of the engaging walls. Therefore, the effective contact area between the cross slip ring and the corresponding matching component can be increased, the stress concentration is reduced, the abrasion of the joint wall is reduced, the performance of the scroll compressor is improved, and the service life of the scroll compressor is prolonged.

Description

Scroll compressor and cross slip ring and matching component for scroll compressor

Technical Field

The present disclosure relates to a scroll compressor and an oldham ring and mating parts for a scroll compressor.

Background

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

A scroll compressor includes a fixed scroll member and an orbiting scroll member eccentrically opposed to each other, the orbiting scroll member orbiting with respect to the fixed scroll member to compress a working fluid. Scroll compressors also typically include a oldham ring for preventing rotation of the stop scroll member. The oldham ring generally includes an annular body and two pairs of keys projecting in an axial direction of the annular body, a first pair of keys fitting in the sliding slots of the fixed scroll member or other fixed structure of the scroll compressor and a second pair of keys fitting in the sliding slots of the orbiting scroll member so as to restrict the orbiting scroll member from rotating only with respect to the fixed scroll member and not simultaneously. Due to the existence of the key, the cross slip ring is subjected to the action of torsional moment in the working process, so that the cross slip ring can overturn and be subjected to torsional deformation in the sliding groove, the contact area between the key and the sliding groove is reduced, and further, parts are abraded due to stress concentration. This wear is particularly likely to occur in the areas where the keys contact the runners. The wear of the key may cause a deviation in an opposed angle between the fixed scroll part and the movable scroll part, a leakage of compressed gas, and the like, and may seriously affect the performance of the scroll compressor.

SUMMERY OF THE UTILITY MODEL

One object of the present disclosure is to reduce wear of mating engagement walls of an oldham ring and a scroll member in a scroll compressor.

It is another object of the present disclosure to optimize the stress distribution between the oldham ring and the scroll member in the scroll compressor, thereby improving the performance of the scroll compressor.

According to one aspect of the present disclosure, an oldham ring for a scroll compressor is provided. The oldham ring includes an annular body and a key projecting from the annular body in an axial direction of the annular body, the key being adapted to engage with a slide groove of a mating member and having a contact root portion engaged with the slide groove and a circumferential end surface, wherein at least one of the keys has a hollow portion at the contact root portion, an engagement wall having a predetermined rigidity and being elastically deformable is formed between the hollow portion and the circumferential end surface.

In one embodiment, the thickness of the radially outer side of the joint wall may be less than or equal to the thickness of the radially inner side of the joint wall.

In one embodiment, the contact root of the key may be located near a central portion of the hollow portion in the axial direction.

In one embodiment, a circumferential width of a central portion of the hollow portion may be greater than or equal to a circumferential width of end portions of the hollow portion in the axial direction.

In one embodiment, the minimum thickness of the engagement wall in the circumferential direction may be less than one third of the circumferential width of the key.

In one embodiment, the hollow portion may include at least one sink groove provided on an outer circumferential surface of the key.

In one embodiment, the sink may include a rectangular sink or a circular sink extending in the axial direction.

In one embodiment, a through hole communicating with the sink groove may be provided on an inner circumferential surface of the key.

In one embodiment, the sink groove may extend through the free end surface of the key in the axial direction.

In one embodiment, the depth of the sink groove in the radial direction may be less than the thickness of the engagement wall.

According to another aspect of the present disclosure, a mating component for an oldham ring of a scroll compressor is provided. The mating member includes a body portion having a slide slot formed therein, the slide slot adapted to engage a key of the oldham ring. Hollow portions are provided on both sides in the circumferential direction of at least one of the slide grooves, and an engagement wall having a predetermined rigidity and being elastically deformable in the circumferential direction is formed between the hollow portion and the slide groove.

In one embodiment, the thickness of the engagement wall may be less than one third of the circumferential width of the chute in the circumferential direction.

In one embodiment, the mating component may be a scroll component of a scroll compressor. The scroll member may further include a wrap extending from the body portion, wherein a flange extending in a radial direction may be provided on the body portion, the flange having a sliding slot formed therein.

In one embodiment, the hollow portion may extend through the body portion in the axial direction, and the hollow portion may extend to the outer circumferential surface of the flange.

According to yet another aspect of the present disclosure, a scroll compressor is provided. The scroll compressor comprises an oldham ring according to the above aspect and/or a mating part according to the above aspect.

In various embodiments of the present disclosure, the stiffness of the interfitting joint walls of the oldham ring and corresponding mating component of a scroll compressor is reduced in a manner that cuts material, thereby allowing a predetermined degree of elastic deformation of the joint walls, increasing the effective contact area between the oldham ring and the joint walls of the corresponding mating component, spreading contact stresses and reducing component wear.

Further areas of applicability of the present disclosure 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 disclosure, are intended for purposes of illustration only and are not intended to limit the disclosure.

Drawings

Embodiments of the present disclosure will now be described, by way of example only, with reference to the accompanying drawings. In the drawings, like features or components are denoted by like reference numerals. The figures are not necessarily to scale, some features may be shown exaggerated in form, for example, for clarity. In the drawings:

fig. 1-3 schematically illustrate a top perspective view, a bottom perspective view, and a side view, respectively, of a mating non-orbiting scroll member and oldham ring in a scroll compressor according to an embodiment of the present disclosure;

FIG. 4 illustrates a perspective view of a oldham ring according to an embodiment of the present disclosure;

FIG. 5 illustrates a partial perspective view of a oldham ring according to another embodiment of the present disclosure;

FIG. 6 illustrates a partial perspective cut-away view of a oldham ring according to another embodiment of the present disclosure;

FIG. 7 illustrates a partial perspective view of a oldham ring according to another embodiment of the present disclosure;

FIG. 8 illustrates a partial perspective view of a oldham ring according to another embodiment of the present disclosure;

FIG. 9 illustrates a partial perspective view of an Oldham ring according to another embodiment of the present disclosure;

FIG. 10 illustrates a perspective view of a non-orbiting scroll member according to one embodiment of the present disclosure;

FIG. 11 illustrates an enlarged view of the chute of the non-orbiting scroll member of FIG. 10;

FIG. 12 illustrates a perspective view of a non-orbiting scroll member according to another embodiment of the present disclosure.

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.

In the following description, directional terminology used in connection with "up" and "down" is described in terms of up and down positions of the views illustrated in the drawings. In practical applications, the positional relationships between "upper" and "lower" as used herein may be defined according to practical situations, and these relationships may be reversed.

A scroll compressor 1 according to an embodiment of the present disclosure will be described first with reference to fig. 1 to 3. The scroll compressor 1 may include a housing, a compression mechanism accommodated in the housing, a driving mechanism for driving the compression mechanism, a seal assembly, and the like. For simplicity, only the non-orbiting scroll member and the oldham ring of the scroll compressor 1 are shown herein, and other known structures of the scroll compressor 1 are not shown.

Fig. 1 to 3 schematically show a top perspective view, a bottom perspective view and a side view of a non-orbiting scroll member 10 and an oldham ring 20 mated in a scroll compressor 1, respectively. The compression mechanism of the scroll compressor 1 includes a non-orbiting scroll member 10 and an orbiting scroll member (not shown). For clarity of illustration of the mating relationship between the non-orbiting scroll member 10 and the oldham ring 20, the orbiting scroll member is not shown in fig. 1-3.

The non-orbiting scroll member 10 includes a body portion having an end plate 11 and a non-orbiting scroll 12 formed at one side of the end plate 11, and the orbiting scroll member correspondingly includes a body portion having an end plate and an orbiting scroll formed at one side of the end plate. In the assembled state, the orbiting scroll member is disposed between the non-orbiting scroll member 10 and the oldham ring 20 such that the non-orbiting and orbiting scrolls 12 and 12 intermesh to form therebetween a series of compression pockets of progressively decreasing volume from the radially outer side to the radially inner side. An intake port 13 is provided radially outward of the fixed scroll member 10, and an exhaust port 14 is provided substantially at the center of the end plate 11 of the fixed scroll member 10. The body portion of the non-orbiting scroll member 10 further includes two flanges 15a, 15b located at diametrically opposite sides of the body portion and protruding radially outward around the fixed wrap 12, and sliding grooves 16a, 16b extending in the radial direction are provided at lower surfaces of the flanges 15a, 15b, respectively.

The oldham ring 20 includes an annular body 21 and a first pair of keys 22a, 22b and a second pair of keys 23a, 23b protruding from an upper surface of the annular body 21 in an axial direction of the annular body 21. It should be noted that the "annular body" described herein forms a closed annular shape but is not necessarily circular. A first pair of keys 22a, 22b are disposed opposite each other and a second pair of keys 23a, 23b are disposed opposite each other, the first pair of keys 22a, 22b being for fitting in the runners 16a, 16b on the flanges 15a, 15b of the non-orbiting scroll member 10 and the second pair of keys 23a, 23b being for fitting in the respective runners on the body portion of the orbiting scroll member, whereby the oldham 20 and the non-orbiting and orbiting scroll members define engaging walls engageable with each other in the circumferential direction. In the assembled state, there is a gap between each key and the respective runner. When the scroll compressor 1 is operated, the driving mechanism drives the movable scroll part to orbit relative to the fixed scroll part 10, and the oldham ring 20 restricts the movable scroll part to only revolve around the central axis of the fixed scroll part 10 but not to revolve around the central axis of the orbiting scroll part itself.

Fig. 4 shows a oldham ring 20 according to an embodiment of the present disclosure. The first pair of keys 22a, 22b may have the same structure, and only one of the keys 22a is described herein as an example. The key 22a is provided on the projection 24a of the ring-shaped body 21. The circumferential width of the projection 24a is larger than the circumferential width of the key 22a, so that the key 22a and the projection 24a constitute a stepped shape. Referring back to FIG. 3, in the assembled condition, the key 22a fits in the slideway 16a on the flange 15a of the non-orbiting scroll 10, with the upper surface of the projection 24a spaced from the lower surface of the flange 15a of the non-orbiting scroll 10.

The key 22a has circumferential end surfaces 31, 32 for engagement with the slideway 16a, the portions of the circumferential end surfaces 31, 32 adjacent the annular body 21 being referred to herein as contact roots 33, 34 of the key 22a. If the oldham ring 20 is upset or torsionally deformed during operation of the scroll compressor, the contact roots 33, 34 of the key 22a, particularly the radially outer sides of the contact roots 33, 34, are most susceptible to wear. In the embodiment shown in fig. 4, the key 22a extends upward in the axial direction from the annular body 21, i.e., toward the non-orbiting scroll member 10, and accordingly, the contact root portions 33, 34 of the key 22a are located at the lowermost ends of the portions of the circumferential end surfaces 31, 32 that are in contact with the sliding grooves 16a of the non-orbiting scroll member 10. However, in other embodiments, the first pair of keys of the oldham ring may also be engaged with other fixed structure in the scroll compressor other than the non-orbiting scroll member. For example, when the first pair of keys of the oldham ring extend downward in the axial direction from the annular body 21 and are engaged with the slide grooves in the respective fixed engaging members, the contact root portions of the keys may be located at the uppermost ends of the portions where the circumferential end surfaces of the keys are in contact with the slide grooves.

A radially inwardly recessed depressed groove 26a is provided on the outer peripheral surface 25a of the key 22a, engaging walls 35, 36 having a certain thickness are formed between the depressed groove 26a and the circumferential end surfaces 31, 32 of the key 22a, and the circumferential end surfaces 31, 32 of the key 22a constitute portions where the engaging walls 35, 36 are engaged with the sliding grooves 16a of the non-orbiting scroll part 10, respectively. In one embodiment, as shown in fig. 4, sink 26a may be substantially rectangular. The undercut 26a may extend through a portion of the key 22a and a portion of the protrusion 24a in the axial direction of the oldham ring 20 such that the contact roots 33, 34 of the key 22a are located near a central portion of the undercut 26a in the axial direction.

By providing the sink groove 26a, a hollow portion located inside the key 22a is formed near the contact root portions 33, 34 of the key 22a in a material-reducing manner, thereby reducing the local rigidity of the joint walls 35, 36. Therefore, when the oldham ring 20 is subjected to the torsional moment, the engaging walls 35, 36 can be elastically deformed to some extent so as to increase the effective contact area between the engaging walls 35, 36 of the key 22a and the respective engaging walls of the slide groove 16a, distribute the contact stress, and thereby reduce the wear. Preferably, making the contact root portions 33, 34 of the key 22a substantially correspond to the central portion of the countersunk groove 26a in the axial direction can maximally reduce the local rigidity in the vicinity of the contact root portions 33, 34 of the key 22a.

In other embodiments of the present disclosure, any other suitable form of hollow portion may also be formed inside the key 22a. Fig. 5 to 9 show partial views of the key 22a with different forms of hollow.

As shown in fig. 5, through holes 28a communicating with the depressed grooves 26a are provided on the inner peripheral surface 27a of the key 22a. The diameter of the through hole 28a is smaller than the circumferential width of the sink groove 26a, so that a stepped portion is formed between the through hole 28a and the sink groove 26a. The through holes 28a may allow for the passage of lubricating oil and refrigerant, further reducing wear and enhancing cooling.

Fig. 6 shows a partial cross-sectional view of the oldham ring with variable cross-section sinker 26a 'taken along a central axial section of sinker 26 a'. In the axial direction, the contact roots 33, 34 of the key 22a (only one contact root 34 is shown in fig. 6) may be located near a central portion of the undercut 26 a'. The four side walls of the sink groove 26a ' are tapered from the radially outer side toward the radially inner side such that the dimension of the radially outer side of the sink groove 26a ' is larger than the dimension of the radially inner side of the sink groove 26a '. The thickness of the radially outer side of the engagement walls 35, 36 (only one engagement wall 36 is shown in fig. 6) of the key 22a is smaller than the thickness of the radially inner side, as viewed in the radial direction. The circumferential width of the central portion of the sink groove 26a 'is larger than the circumferential width of the end portion of the sink groove 26a' as viewed in the axial direction. In other words, the thickness t1 at the upper and lower ends of the engagement walls 35, 36 of the key 22a as viewed in the axial direction is greater than the thickness t2 at the center. Therefore, the radially outer sides of the contact root portions 33, 34 of the key 22a correspond to the thinnest areas of the engagement walls 35, 36 of the key 22a. The radially outer sides of the contact roots 33, 34 of the key 22a tend to be most susceptible to wear during operation of the scroll compressor, and the design of such a variable area sink allows for the relatively maximum flexibility of the radially outer sides of the contact roots 33, 34 of the key 22a, thereby further optimizing stress distribution in the key 22a in both the radial and axial directions.

FIG. 7 shows key 22a having a generally "8" shaped contoured depression 26a ". The sink 26a "may be considered to include two or more circular grooves connected to each other. The sinker 26a ″ may be conveniently formed by drilling two or more circular grooves connected to each other using a circular drill during the process of manufacturing the oldham ring. Fig. 8 shows that through holes 28a "communicating with the shaped recesses 26a" are provided on the inner peripheral surface 27a of the key 22a, thereby facilitating lubrication and cooling.

Fig. 9 shows a key 22a according to another embodiment. In this embodiment, a rectangular sink groove 26a' ″ extends through the free end surface 29a of the key 22a (i.e., the upper end surface of the key 22a shown in fig. 9) in the axial direction. The oldham ring with such a sink groove may be formed directly by casting without additional machining of the oldham ring.

As shown in fig. 9, the depth d of the countersunk groove 26a' ″ in the radial direction is preferably less than the thickness t of the engagement walls 35, 36, and the thickness t of the engagement walls 35, 36 is preferably less than one third or one fourth of the circumferential width w of the key 22a, so that the engagement walls 35, 36 of the key 22a have a more desirable rigidity and stress distribution. This dimensional feature may also be applied to the sink in other embodiments, particularly the rectangular sink 26a shown in fig. 4. For embodiments in which the engagement wall has a non-constant thickness, it is preferred that the minimum thickness of the engagement wall in the circumferential direction is less than one third or one quarter of the circumferential width of the key. Further, it is preferable to arrange the portion where the thickness of the joining wall is smallest in the vicinity of the contact root of the key.

In other embodiments, the key 22a may be provided with a sunken groove of any other suitable shape or a hollow of any other suitable form to reduce the rigidity of at least a portion of the engagement wall of the key 22a such that the engagement wall of the key 22a has a predetermined rigidity and is capable of being elastically deformed. For example, the key 22a may comprise a single circular recess, or the key 22a may comprise a plurality of discrete recesses, such as two axially extending slots may be provided adjacent to the two circumferential end surfaces 31, 32 of the key 22a, respectively.

It should be understood that although the above description has been made with respect to only the first pair of keys 22a, 22b of the oldham ring 20 cooperating with the non-orbiting scroll member 10, the above described key configuration with various hollow portions may also be applied to the second pair of keys 23a, 23b of the oldham ring 20 cooperating with the orbiting scroll member. The first pair of keys 22a, 22b may also engage with sliding grooves on other fixed structures of the scroll compressor 1 other than the fixed scroll member 10, such as main bearing housings.

A non-orbiting scroll member according to another aspect of the present disclosure is described below with reference to fig. 10-12.

FIG. 10 illustrates a perspective view of non-orbiting scroll member 10 according to one embodiment. The non-orbiting scroll member 10 includes flanges 15a, 15b with runners 16a, 16b. The chutes 16a and 16b may have the same structure, and only the chute 16a will be described below as an example. A pair of grooves 17a, 18a are provided on both sides of the slide groove 16a in the circumferential direction, and two engagement walls 41, 42 for engaging with the key 22a of the oldham ring 20 are formed between the grooves 17a, 18a and the slide groove 16 a. Slots 17a, 18a may be configured to provide engagement walls 41, 42 of chute 16a with a predetermined stiffness. Thereby, during operation of the scroll compressor, the engagement walls 41, 42 of the slide slot 16a can be elastically deformed to some extent in the circumferential direction, thereby increasing the effective contact area between the engagement walls 35, 36 of the key 22a of the oldham ring 20 and the engagement walls 41, 42 of the slide slot 16a, sharing contact stresses, and thereby reducing wear. Preferably, the grooves 17a, 18a extend to the outer peripheral surface 19a of the flange 15 a. Thereby, the rigidity of the radially outer side of the engagement walls 41, 42 of the chute 16a can be further reduced.

Fig. 11 shows an enlarged view of the chute 16a in fig. 10. As shown in fig. 11, the thickness T of the engaging walls 41, 42 of the sliding slot 16a of the non-orbiting scroll member 10 is preferably less than one third of the circumferential width W of the sliding slot 16a, so that the engaging walls 41, 42 of the sliding slot 16a have a preferable rigidity and stress distribution.

FIG. 12 illustrates a perspective view of non-orbiting scroll member 10 according to another embodiment. In this embodiment, the grooves 17a, 18a on both circumferential sides of the sliding groove 16a of the non-orbiting scroll 10 extend through the body portion of the non-orbiting scroll 10 in the axial direction. The non-orbiting scroll member with such a groove may be formed directly by casting without additional machining of the non-orbiting scroll member.

Although the above description has been made with respect to the chute structure of the non-orbiting scroll member 10, it should be understood that the chute structure described above is equally applicable to the orbiting scroll member or other mating components of the scroll compressor that mate with the oldham ring, such as the main bearing housing, etc.

In the embodiments of the present disclosure, the thickness and rigidity of at least one of the engaging walls of the slide groove of the mating member and the key of the oldham ring are reduced by providing a hollow portion in the vicinity of the at least one engaging wall, so that the at least one engaging wall has a predetermined rigidity and can be elastically deformed to a predetermined degree. Therefore, the effective contact area between the cross slip ring and the corresponding matching component can be increased, stress concentration is reduced, the cross slip ring is prevented from overturning, the abrasion of a joint wall is reduced, the performance of the scroll compressor is improved, and the service life of the scroll compressor is prolonged.

Exemplary embodiments of scroll compressors, oldham rings, and mating components according to the present disclosure have been described herein in detail, but it is to be understood that the present disclosure is not limited to the specific embodiments described and illustrated in detail above. Various embodiments according to the present disclosure may be used alone or in combination. Various modifications and alterations to this disclosure will become apparent to those skilled in the art without departing from the spirit and scope of this disclosure. All such variations and modifications are intended to fall within the scope of the present disclosure. Moreover, all the components described herein may be replaced by other technically equivalent components.

Claims (15)

1. An oldham ring for a scroll compressor, characterized in that the oldham ring comprises an annular body and a key projecting from the annular body in an axial direction of the annular body, the key being adapted to engage with a sliding groove of a mating member and having a contact root engaged with the sliding groove and a circumferential end surface, wherein at least one of the keys has a hollow portion at the contact root, an engagement wall having a predetermined rigidity and being elastically deformable is formed between the hollow portion and the circumferential end surface.

2. The slipring of claim 1, characterized in that the thickness of the radially outer side of the engagement wall is smaller or equal to the thickness of the radially inner side of the engagement wall.

3. The oldham ring according to claim 1, wherein a contact root of the key is located near a central portion of the hollow in the axial direction.

4. The oldham ring according to claim 3, wherein a circumferential width of the central portion of the hollow in the axial direction is greater than or equal to a circumferential width of an end portion of the hollow.

5. The oldham ring according to claim 1, wherein a minimum thickness of the engagement wall in a circumferential direction is less than one third of a circumferential width of the key.

6. The oldham ring according to any one of claims 1 to 5, wherein the hollow portion comprises at least one sink groove provided on an outer peripheral surface of the key.

7. The oldham ring according to claim 6, wherein the sink includes a rectangular sink or a circular sink extending in the axial direction.

8. The oldham ring according to claim 6, wherein a through hole communicating with the sink groove is provided on an inner peripheral surface of the key.

9. The oldham ring according to claim 6, wherein the countersink extends through a free end surface of the key in the axial direction.

10. The oldham ring according to claim 6, wherein a depth of the countersink in a radial direction is less than a thickness of the engagement wall.

11. A fitting member for an oldham ring of a scroll compressor, characterized in that the fitting member comprises a body portion on which sliding grooves adapted to be engaged with keys of the oldham ring are formed, and hollow portions are provided on both sides in a circumferential direction of at least one of the sliding grooves, and an engaging wall having a predetermined rigidity and being elastically deformable in a circumferential direction is formed between the hollow portion and the sliding groove.

12. The mating member according to claim 11, wherein a thickness of the engagement wall in the circumferential direction is less than one third of a circumferential width of the slide groove.

13. The mating component of claim 11 or 12, wherein the mating component is a scroll component of a scroll compressor, the scroll component further comprising a wrap extending from the body portion, wherein a flange is provided on the body portion extending in a radial direction, the flange having the sliding slot formed therein.

14. The fitting according to claim 13, characterized in that the hollow portion extends through the body portion in the axial direction, and the hollow portion extends to an outer peripheral surface of the flange.

15. A scroll compressor, characterized in that the scroll compressor comprises a oldham ring and mating parts mating with the oldham ring, wherein the oldham ring is the oldham ring according to any of claims 1 to 10 and/or the mating parts are the mating parts according to any of claims 11 to 14.

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