阅读说明：本技术 涡旋压缩机 (Scroll compressor having a plurality of scroll members ) 是由 黄幼玲 杨东辉 束宏飞 于 2020-04-30 设计创作，主要内容包括：本公开提供了一种涡旋压缩机,其包括：壳体；压缩机构,该压缩机构包括动涡旋和定涡旋,动涡旋和定涡旋以彼此啮合的方式接合以形成一系列的压缩腔；主轴承座,该主轴承座用于支承压缩机构；以及定位组件,该定位组件包括定位销,其中,定涡旋形成有第一孔口,主轴承座形成有第二孔口,并且壳体或与壳体固定连接的固定部件形成有第三孔口,定位销配合在第一孔口、第二孔口以及第三孔口中以保持定涡旋、主轴承座以及壳体中任意两者的相对角度位置并且允许定涡旋相对于主轴承座进行轴向运动。根据本公开的涡旋压缩机能够保持定涡旋、主轴承座以及壳体之间的相对角度位置,并且可以在确保涡旋压缩机可靠性的情况下实现紧凑的设计。(The present disclosure provides a scroll compressor, which includes: a housing; a compression mechanism including an orbiting scroll and a non-orbiting scroll engaged with each other in an intermeshing fashion to form a series of compression chambers; a main bearing seat for supporting the compression mechanism; and a positioning assembly including a positioning pin, wherein the fixed scroll is formed with a first hole, the main bearing housing is formed with a second hole, and the housing or a fixing member fixedly connected with the housing is formed with a third hole, the positioning pin being fitted in the first hole, the second hole, and the third hole to maintain relative angular positions of any two of the fixed scroll, the main bearing housing, and the housing and to allow the fixed scroll to axially move with respect to the main bearing housing. The scroll compressor according to the present disclosure can maintain the relative angular positions between the fixed scroll, the main bearing housing, and the casing, and can achieve a compact design while ensuring the reliability of the scroll compressor.)

1. A scroll compressor, comprising:

a housing (10a, 10 b);

a compression mechanism including an orbiting scroll (20a) and a non-orbiting scroll (30a) meshingly engaged with each other to form a series of compression chambers;

a main bearing housing (50a) for supporting the compression mechanism; and

a positioning assembly comprising a positioning pin (80), characterized in that,

the non-orbiting scroll (30a) is formed with a first aperture (346), the main bearing housing (50a) is formed with a second aperture (526), and the housing (10a, 10b) or a fixed member (90b) fixedly connected with the housing is formed with a third aperture (116, 92b), the positioning pins being fitted in the first, second, and third apertures to maintain the relative angular positions of any two of the non-orbiting scroll (30a), the main bearing housing, and the housing (10a, 10b) and to allow the non-orbiting scroll (30a) to axially move with respect to the main bearing housing (50 a).

2. The scroll compressor of claim 1,

the locating pin is clearance fit within the first aperture and the locating pin is fixed or clearance fit within each of the second and third apertures; or

The locating pin is fixedly fit within the first aperture and the locating pin is clearance fit within each of the second and third apertures.

3. The scroll compressor of any one of claims 1 to 2,

the positioning assembly further comprises an axial positioning member, the axial positioning member (90a, 90b) being disposed on a side of the non-orbiting scroll (30a) facing away from the orbiting scroll (20a) and the axial positioning member (90a, 90b) being spaced apart from the non-orbiting scroll (30a) in an axial direction by a predetermined distance.

4. The scroll compressor of claim 3,

the scroll compressor further includes a sound-deadening cap for partitioning an inner space of the scroll compressor into a high-pressure region and a low-pressure region, the sound-deadening cap serving as the axial positioning member.

5. The scroll compressor of any one of claims 1 to 2,

the positioning assembly further comprises a radial positioning member formed by an inner peripheral wall of the housing (10a, 10b) forming a radial clearance fit with the non-orbiting scroll (30 a).

6. The scroll compressor of any one of claims 1 to 2,

the scroll compressor further includes an oldham ring (60a) engaged with the orbiting scroll (20a) and the main bearing housing (50a) to prevent the orbiting scroll from spinning and to allow the orbiting scroll (20a) to orbit relative to the non-orbiting scroll (30 a).

7. The scroll compressor of claim 6,

the orbiting scroll (20a) is provided with a pair of key grooves (262a, 262b) to which a pair of positioning keys of the oldham ring are engaged, the pair of key grooves (262a, 262b) being blind grooves formed at an end plate (22a) of the orbiting scroll (20 a).

8. The scroll compressor of any one of claims 1 to 2,

the radially outer end portion of the orbiting scroll (20a) directly faces the inner peripheral wall of the housing (10a, 10b), or only the positioning pin is provided between the radially outer end portion of the orbiting scroll (20a) and the inner peripheral wall.

9. The scroll compressor of any one of claims 1 to 2, wherein:

the housing comprises a radial protrusion (110a) protruding radially inwards from an inner circumferential wall of the housing, the third aperture (116) being provided at the radial protrusion; or

The scroll compressor further includes a sound-deadening cover for partitioning an inner space of the scroll compressor into a high-pressure region and a low-pressure region, the sound-deadening cover serving as the fixing member and the third orifice (92b) being provided at the sound-deadening cover.

10. A scroll compressor, comprising:

a housing (10a, 10 b);

a compression mechanism including an orbiting scroll (20a) and a non-orbiting scroll (30a) meshingly engaged with each other to form a series of compression chambers;

a main bearing housing (50a) for supporting the compression mechanism; and

a positioning assembly comprising a positioning pin (80), characterized in that,

the non-orbiting scroll (30a) is formed with a first aperture (346), the main bearing housing (50a) is formed with a second aperture (526), and the housing (10a, 10b) or a fixed member (90b) fixedly connected with the housing is formed with a third aperture (116, 92b), the positioning pins being fitted in the first, second, and third apertures, the fitting of the positioning pins with the first and second apertures being configured such that an angular position of the non-orbiting scroll (30a) relative to the main bearing housing (50a) is maintained, the non-orbiting scroll (30a) being axially movable relative to the main bearing housing (50 a).

11. The scroll compressor of claim 10, wherein,

the locating pin is clearance-fit in the first aperture and fixedly-fit in the second aperture, and the locating pin is clearance-or fixedly-fit in the third aperture; or

The locating pin is fixedly fit within the first aperture and the locating pin is clearance fit within each of the second and third apertures.

Technical Field

The present invention relates to 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 may generally include an orbiting scroll and a non-orbiting scroll which are intermeshed with each other. In order to hold the scroll members (particularly the non-orbiting scrolls) in place, various positioning mechanisms need to be provided. These positioning mechanisms are often required to be used in conjunction with additional bolt components that require sufficient diametral dimensions to withstand the respective loads, which inevitably takes up limited radial space within the compressor, thereby making it difficult to provide a compact, miniaturized compressor. In addition, there is a need for an improved positioning mechanism to improve the relative angular positioning accuracy between the non-orbiting scroll, the main bearing housing, and the housing.

Accordingly, there is a need to provide an improved scroll compressor.

Disclosure of Invention

It is an object of one or more embodiments of the present disclosure to maintain the relative angular positioning of any two of the non-orbiting scroll, the main bearing housing, and the shell.

It is an object of one or more embodiments of the present disclosure to provide a solution that enables a compact design of a scroll compressor in a simple manner.

According to one aspect of the present disclosure, there is provided a scroll compressor including: a housing; a compression mechanism including an orbiting scroll and a non-orbiting scroll engaged in meshing engagement with each other to form a series of compression chambers; a main bearing seat for supporting the compression mechanism; and a positioning assembly including a positioning pin, wherein the non-orbiting scroll is formed with a first aperture, the main bearing housing is formed with a second aperture, and the housing or a fixed member fixedly connected with the housing is formed with a third aperture, the positioning pin being fitted in the first aperture, the second aperture, and the third aperture to maintain a relative angular position of any two of the non-orbiting scroll, the main bearing housing, and the housing and to allow axial movement of the non-orbiting scroll relative to the main bearing housing.

According to one aspect of the present disclosure, the locating pin is clearance fit within the first aperture and the locating pin is fixed or clearance fit within each of the second and third apertures; or the locating pin is a fixed fit within the first aperture and the locating pin is a clearance fit within each of the second and third apertures.

According to one aspect of the present disclosure, the positioning assembly further includes an axial positioning member disposed on a side of the non-orbiting scroll facing away from the orbiting scroll and axially spaced from the non-orbiting scroll by a predetermined distance.

According to one aspect of the present disclosure, the scroll compressor further includes a sound-deadening cap for partitioning an inner space of the scroll compressor into a high-pressure region and a low-pressure region, the sound-deadening cap serving as the axial positioning member.

According to one aspect of the present disclosure, the positioning assembly further includes a radial positioning member formed by an inner peripheral wall of the housing forming a radial clearance fit with the non-orbiting scroll.

According to one aspect of the present disclosure, the scroll compressor further includes an oldham ring engaged with the orbiting scroll and the main bearing housing to prevent the orbiting scroll from spinning and to allow the orbiting scroll to orbit relative to the non-orbiting scroll.

According to one aspect of the present disclosure, the orbiting scroll is provided with a pair of key grooves engaged with a pair of positioning keys of the oldham ring, the pair of key grooves being blind grooves formed at an end plate of the orbiting scroll.

According to an aspect of the present disclosure, a radially outer end portion of the orbiting scroll directly faces an inner circumferential wall of the housing, or only a positioning pin is provided between the radially outer end portion of the orbiting scroll and the inner circumferential wall.

According to an aspect of the present disclosure, the housing includes a radial protrusion protruding radially inward from an inner circumferential wall of the housing, the third aperture being provided at the radial protrusion; or the scroll compressor further comprises a noise reduction cover for dividing an inner space of the scroll compressor into a high pressure region and a low pressure region, the noise reduction cover serving as the fixing member and the third port being provided at the noise reduction cover.

According to another aspect of the present disclosure, there is provided a scroll compressor including: a housing; a compression mechanism including an orbiting scroll and a non-orbiting scroll engaged in meshing engagement with each other to form a series of compression chambers; a main bearing seat for supporting the compression mechanism; and a positioning assembly including a positioning pin, characterized in that the fixed scroll is formed with a first hole, the main bearing housing is formed with a second hole, and the housing or a fixing member fixedly connected with the housing is formed with a third hole, the positioning pin is fitted in the first hole, the second hole, and the third hole, and the fitting of the positioning pin with the first hole and the second hole is configured so that an angular position of the fixed scroll with respect to the main bearing housing is maintained, the fixed scroll being axially movable with respect to the main bearing housing.

According to another aspect of the present disclosure, the locating pin is clearance fit within the first aperture and fixedly fit within the second aperture, and the locating pin is clearance or fixedly fit within the third aperture; or the locating pin is a fixed fit within the first aperture and the locating pin is a clearance fit within each of the second and third apertures.

The scroll compressor according to the present disclosure can maintain the relative angular positioning between the fixed scroll, the main bearing housing, and the shell, improve the positioning accuracy thereof, and can achieve a compact design while ensuring the reliability of the scroll compressor.

Drawings

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 sectional view schematically showing a scroll compressor according to a comparative example;

fig. 2 is an exploded perspective view schematically showing a scroll compressor according to a comparative example;

FIG. 3 is a cross-sectional view schematically illustrating a scroll compressor according to a first embodiment of the present disclosure;

FIG. 4 is a perspective view schematically illustrating an orbiting scroll used in the scroll compressor of FIG. 3;

FIG. 5 is a perspective view schematically illustrating a main bearing housing used in the scroll compressor of FIG. 3;

FIG. 6 is a perspective view schematically illustrating an oldham ring for use in the scroll compressor of FIG. 3;

FIG. 7 is a perspective view schematically illustrating a non-orbiting scroll used in the scroll compressor of FIG. 3;

FIG. 8 is a cross-sectional view schematically illustrating a scroll compressor according to a second embodiment of the present disclosure; and

fig. 9 is a sectional view schematically showing a scroll compressor according to a third embodiment of the present disclosure.

Detailed Description

The present disclosure will now be described with reference to the accompanying drawings, which are illustrative only and are not to be construed as limiting the disclosure and its applications.

Fig. 1 shows a longitudinal sectional view of a compressor according to a comparative example. As shown in fig. 1, the scroll compressor 1 includes a housing 10. The housing 10 houses an orbiting scroll 20 and a non-orbiting scroll 30. Orbiting and non-orbiting scrolls 20 and 30 include orbiting and non-orbiting scroll blades, respectively, that are meshingly engaged with each other and extend from non-orbiting scroll end plate 22 and non-orbiting scroll end plate 32, respectively.

To properly position the scroll components, the scroll compressor 1 includes a pilot ring 70, an oldham ring 60, and a locating pin 80 (see FIG. 2). The guide ring 70 is disposed between the non-orbiting scroll 30 and the casing 10 to achieve radial centering and limiting of the non-orbiting scroll. Also, the guide ring 70 has a stepped portion 72 extending toward the flange of the non-orbiting scroll 30, and the stepped portion 72 can abut against the flange of the non-orbiting scroll, thereby limiting the movement range of the non-orbiting scroll 30 in the axial direction.

Main bearing housing 50 is adapted to support a compression mechanism including a non-orbiting scroll and an orbiting scroll, and includes an annular central body (or central thrust plate 52) and an arm portion 54 (see fig. 2) located radially outward of central thrust plate 52 and extending axially upward. The upper surface of central thrust plate 52 provides a thrust surface adapted to support orbiting scroll 20. Each of the arms 54 has an aperture provided therein. As shown in fig. 2, pilot ring 70 is fixed relative to main bearing housing 50 and thus relative to the housing by extending bolts 8 through apertures of pilot ring 70 and into apertures of main bearing housing 50, while also allowing a range of movement of non-orbiting scroll 30 in an axial direction relative to main bearing housing 50 by axial guidance and axial restraint of non-orbiting scroll 30 by pilot ring 70.

The oldham ring 60 is provided to be engaged with the orbiting scroll 20 and the non-orbiting scroll 30 to prevent the orbiting scroll 20 from rotating. As shown in fig. 2, the oldham ring 60 has an annular body 62, and two pairs of engagement keys are provided on the annular body 62, a first pair of engagement keys 64a, 64b for engaging with corresponding key slots 32a, 32b on the non-orbiting scroll 30, and a second pair of engagement keys 66a (only a single engagement key 66a is shown in fig. 2) for engaging with corresponding key slots 22a (only a single key slot 22a is shown in fig. 2) on the orbiting scroll 20. During operation, the first pair of engagement keys 64a, 64b and the second pair of engagement keys move within the corresponding keyways, respectively. Thus, since the fixed scroll 30 is a fixed member, the orbiting scroll 20 can be allowed to orbit with respect to the fixed scroll 30 while preventing the orbiting scroll 20 from rotating.

Locating pin 80 extends through non-orbiting scroll 30 and main bearing housing 50 to prevent non-orbiting scroll 30 from rotating relative to main bearing housing 50. Specifically, one end of the positioning pin 80 may be fixed to the main bearing housing 50 and the other end may be clearance-fitted with the non-orbiting scroll to restrict movement of the non-orbiting scroll in the circumferential direction.

In the compressor according to the comparative example, since the guide ring 70 is fixed to the main bearing housing 50 by bolts, in order to achieve a firm connection, the diameters of the bolts need to be large enough to meet the respective strength requirements, and accordingly, the main bearing housing to which the bolts are connected and the guide ring need to meet certain wall thickness requirements to provide threaded holes and to provide sufficient connection strength, and therefore, these components need to occupy a certain radial space to withstand the respective loads and maintain strength. In addition, it is also required to provide a sufficient movement space for the oldham ring engaged with the orbiting and non-orbiting scrolls to secure the performance of the compressor. This makes it difficult to provide a compact and miniaturized compressor design without affecting compressor reliability. Furthermore, due to the provision of the guide ring, the guide ring not only takes up radial space but also the radial limitation and radial centering of the non-orbiting scroll need to be achieved indirectly by means of the guide ring, which complicates the radial limitation and radial centering and also reduces the accuracy thereof.

Further, the compressor according to the comparative example includes a plurality of positioning members, however, these positioning members still fail to provide a satisfactory positioning effect. For example, in compressors with enhanced vapor injection functionality that have been widely used, the compressor includes an enhanced vapor injection conduit. The enhanced vapor injection pipeline passes through the shell of the compressor and is connected with the fixed scroll, and therefore refrigerant in the enhanced vapor injection pipeline flows into an intermediate-pressure cavity of the compressor through a gas supplementing port on the fixed scroll. By injecting liquid or gaseous refrigerant into the intermediate pressure chamber of the compressor, the amount of gas in the compressor is increased while the temperature in the compression chamber is reduced. At this time, a portion of the enhanced vapor injection conduit may be disposed in the shell of the compressor and another portion disposed in the non-orbiting scroll, which places higher demands on the relative positioning between the components of the compressor.

A compressor according to an exemplary embodiment of the present disclosure will be described in detail below with reference to the accompanying drawings.

First embodiment

Fig. 3 is a partial longitudinal sectional view of a scroll compressor according to a first exemplary embodiment of the present invention. The compressor 1a according to the first exemplary embodiment of the present disclosure may include a housing 10 a. The housing 10a may house therein a compression mechanism including an orbiting scroll 20a and a non-orbiting scroll 30 a. Non-orbiting scroll 30a may include a non-orbiting scroll end plate 32a and orbiting scroll blades 34a formed on one side of non-orbiting scroll end plate 32a and annular walls 36a and 38a formed on the other side of orbiting scroll end plate 32 a. Further, the non-orbiting scroll further includes a peripheral wall portion 340 located on the outermost side in the radial direction around the non-orbiting scroll blade 34 a. As shown in fig. 3, the non-orbiting scroll 30a further has a flange 342 extending radially outward from the outer peripheral surface of the peripheral wall portion 340. The flange 342 of the non-orbiting scroll 30a is disposed within the housing 10a with a small clearance fit. Here, the small clearance fit is such that the outer diameter of the flange 342 of the given scroll 30a is slightly smaller than the inner diameter of the housing 10a, so that the fixed scroll 30a can be freely installed into the housing 10a while the fixed scroll 30a can move to some extent in the axial direction relative to the housing 10a after installation, but the radial movement of the fixed scroll relative to the housing is restricted. Therefore, the fixed scroll can be limited radially through the inner wall of the shell. Flange 342 of non-orbiting scroll 30a may include a first aperture 346 extending in an axial direction from a lower or first surface to an upper or second surface of flange 342.

The sound-deadening cap 90a may be fixedly coupled to the casing 10a and disposed above the non-orbiting scroll 20 a. A predetermined axial distance is left between the upper end portion of the non-orbiting scroll 30a (i.e., the end portion facing away from the orbiting scroll 20a) and the lower end portion of the sound-deadening cap 90a, whereby the sound-deadening cap 90a can allow the non-orbiting scroll 30a to perform a certain degree of movement in the axial direction while axially restricting the non-orbiting scroll 30a, i.e., the sound-deadening cap 90a can constitute a longitudinal direction positioning member (also referred to as an axial direction positioning member). Of course, the present disclosure is not so limited and, for example, a top cover or other component may be provided to cooperate with the non-orbiting scroll in a similar manner to serve as the longitudinal locating member.

Orbiting scroll 20a may include an orbiting scroll end plate 22a, orbiting scroll blades 24a formed at one side of the orbiting scroll end plate 22a, and an annular hub 26a formed at the other side of the orbiting scroll end plate 22 a. The non-orbiting scroll blade 34a and the orbiting scroll blade 24a 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 and the orbiting scroll blade when the scroll compressor is operated, thereby achieving compression of the working fluid.

Main bearing housing 50a is adapted to support orbiting scroll 20a and non-orbiting scroll 30 a. Main-bearing housing 50a may include a main body portion 52a and a cylindrical portion 54a extending axially downward from main body portion 52 a. The upper surface of body portion 52a is adapted to support end plate 22a of orbiting scroll 20a to form a thrust surface. The main body portion 52a may extend radially outward relative to the cylindrical portion 54a to form a stepped portion, and the stepped portion of the main bearing housing 50a is provided on the radially protruding portion 110a of the housing 10a, so that the main bearing housing 50a can be firmly held to the housing. Radial protrusion 110a of housing 10a may be formed with third aperture 116 at a location corresponding to second aperture 526 of body portion 52a of main-bearing housing 50 a. As shown in fig. 5, body portion 52a of main-bearing housing 50a may include a second aperture 526 extending in an axial direction from an upper or first surface 522 to a lower or second surface of body portion 52 a.

In order to prevent the orbiting scroll 20a from rotating, an oldham ring 60a is provided to be engaged with the orbiting scroll 20a and the main bearing housing 50 a. As shown in fig. 6, the oldham ring 60a may include an annular body 62a and first and second pairs of protrusions 622a, 622b, 624a, 624b extending radially outward from the annular body 62a, which pairs of protrusions may be provided with first and second pairs of engagement keys 626a, 626b, 628a, 628b, respectively. An oldham ring 60a may be disposed between the main bearing housing 50a and the orbiting scroll 20 a. A first pair of keys 626a, 626b of the oldham ring 60a is adapted to engage corresponding key slots 562a, 562b on the main bearing housing 50a and a second pair of engaging keys 628a, 628b is adapted to engage corresponding key slots 262a, 262b on the orbiting scroll 20a, thereby allowing the orbiting scroll 20a to orbit relative to the non-orbiting scroll 30a while preventing the orbiting scroll 20a from self-rotating.

Fig. 4 and 5 clearly show the keyways 262a, 262b and the keyways 562a, 562b for the oldham ring. As shown in fig. 4, key grooves 262a, 262b may be formed on the end plate 22a of the orbiting scroll 20 a. Preferably, the keyways 262a, 262b may be blind slots formed in the end plate 22 a. The blind groove does not extend through the end plate 22a to the other side of the end plate where the orbiting scroll blade is formed. At this time, the oldham ring itself and its movement and the orbiting scroll blade may be independent from each other in the axial direction without interference with each other, so that a radial space of a scroll profile may be further increased, a discharge capacity of the compressor may be enlarged and a structure of the compressor may be more compact in case of the enlarged discharge capacity of the compressor. Referring to fig. 5, main body portion 52a of main-bearing housing 50a is formed with a first pair of recesses 56a, 56b and a second pair of recesses 58a, 58 b. The first pair of recesses 56a, 56b includes circumferential grooves 564a, 564b and key slots 562a, 562b disposed below the circumferential grooves 564a, 564b and extending in the radial direction, respectively. The depth of the second pair of recesses 58a, 58b is substantially the same as the depth of the circumferential grooves 564a, 564 b. During operation, the first and second pairs of protrusions 622a, 622b, 624a, 624b of the oldham ring 60a are received in the circumferential grooves 564a, 564b and the second pair of recesses 58a, 58b, respectively, and the first pair of keys 626a, 626b move within the keyways 562a, 562 b.

As shown in fig. 3, the locating pin 80 may extend in an axial direction through the first aperture 346 of the non-orbiting flange, the second aperture 526 of the main body portion 52a of the main bearing housing 50a, and the third aperture 116 of the radial protrusion 110a of the housing 10 a. Specifically, locating pin 80 is fixedly fit within second aperture 526 of main bearing housing 50a, and locating pin 80 is slidably fit within first aperture 346 of non-orbiting scroll 30a and third aperture 116 of housing 10 a. In the exemplary embodiment of fig. 3, locating pin 80 is secured within second bore 526 of main bearing housing 50a by an interference fit, and locating pin 80 is clearance fit within first bore 346 and third bore 116. Of course, the locating pin may be fixedly and/or slidably fitted within the first through third apertures in any other suitable manner. Preferably, the dowel pins can be fitted into and removed from the first to third bores in a simple manner by means of an interference fit and a clearance fit. By clearance fit herein is meant that the outer diameter of the interfitting locating pins is slightly less than the inner diameter of the first through third apertures such that the locating pins can be freely inserted into the first through third apertures while radial movement of the locating pins relative to the first through third apertures is limited. Referring to fig. 3, first aperture 346 of non-orbiting scroll 30a, third aperture 116 of the housing, and second aperture 526 of bearing seat 50a may preferably be disposed radially outward of the compression pockets (in other words, radially outward of the radially outermost position that the orbiting scroll end plate can reach in the orbiting motion) to avoid interference of locating pin 80 with the motion of the scroll and to provide as much active space as possible for the scroll.

As shown in fig. 3, the positioning pin 80 is simultaneously fitted in the first aperture 346 of the non-orbiting scroll 30a and the third aperture 116 of the housing, and thus it is possible to prevent the non-orbiting scroll 30a from being angularly deviated with respect to the housing 10a, maintaining the angular positioning of the non-orbiting scroll 30a with respect to the housing 10 a. Also, the positioning pin 80 is slidably fitted in the first aperture of the non-orbiting scroll 30a, so that the non-orbiting scroll 30a can perform a certain range of axial movement in the axial direction without being hindered by the positioning pin, thereby providing the scroll assembly with a certain axial flexibility to increase reliability and safety of the compressor. Further, the positioning pin 80 is simultaneously fitted in the second aperture of the main bearing housing 50a, and therefore, the positioning pin 80 can prevent the fixed scroll 30a from rotating relative to the main bearing housing 50 a. Thus, by fitting the positioning pins 80 in the first, second, and third apertures at the same time, it is made possible to simultaneously maintain the relative angular positions of any two of the fixed scroll, the main bearing housing, and the housing and to enable axial floating of the fixed scroll relative to the main bearing housing. Although in fig. 3, the first aperture 346 is exemplarily illustrated as a through hole extending from the lower surface to the upper surface of the flange 242 of the driven scroll 20a, it may be formed as a blind hole not extending to the upper surface. It is preferable to form a through hole penetrating the flange 242 to prevent the non-orbiting scroll from moving axially, and the positioning pin may be blocked by the first hole 346 not penetrating.

Fig. 3 shows locating pin 80 fixedly fitted within second bore 526 of main bearing housing 50a, and locating pin 80 slidably fitted within first bore 346 of non-orbiting scroll 30a and third bore 116 of housing 10a, but other alternative arrangements are possible, such as in an alternative embodiment, locating pin 80 fixedly fitted within third bore 116 of housing 10a, and locating pin 80 slidably clearance fitted within first bore 346 of non-orbiting scroll 30a and second bore 526 of main bearing housing 50 a. Additionally, another alternative embodiment is also contemplated in which non-orbiting scroll 80 is slidably disposed within third aperture 116 of housing 10a, second aperture 526 of main bearing housing 50a, and first aperture 346 of non-orbiting scroll 30 a. In these alternative embodiments, it is also possible to maintain the relative angular positions of any two of the non-orbiting scroll, the main bearing housing, and the housing and to enable axial floating of the non-orbiting scroll relative to the main bearing housing by simultaneously fitting the positioning pins 80 in the first, second, and third bores.

In the first embodiment shown in fig. 3, the positioning pin 80 is fixedly fitted in the first aperture 346 of the fixed scroll 30a, whereby, compared with the alternative embodiment in which the positioning pin is clearance-fitted in the first aperture 346, it is possible to eliminate the fitting clearance of the positioning pin 80 and the fixed scroll 30a, reduce the angular positioning error between the fixed scroll and the main bearing housing, and thereby improve the accuracy of the angular positioning of the fixed scroll relative to the main bearing housing, and since the oldham ring 60a is simultaneously fitted with the movable scroll 20a and the main bearing housing 50a, the improved accuracy of the angular positioning between the fixed scroll 30a and the main bearing housing 50a can further improve the accuracy of the angular positioning of the fixed scroll 30a and the movable scroll 20a, so that the overall performance of the compressor can be effectively improved by the accurate positioning between the fixed scroll and the movable scroll relative to each other. On the other hand, in the first embodiment, the positioning pin 80 is fixedly fitted in the second hole 526 of the main bearing housing 50a, in this way, as compared with the alternative embodiment in which the positioning pin is clearance-fitted in the second hole 526, the fitting clearance of the positioning pin 80 with the main bearing housing 50a can be eliminated, and also the relative angular error between the main bearing housing and the housing can be reduced, thereby improving the accuracy of the angular positioning of the main bearing housing with respect to the housing, further enabling components such as the oil return hole or the air suction hole fitted on the main bearing housing to be positioned more accurately with respect to the housing. Further, in the alternative embodiment in which the positioning pin 80 is fixedly fitted in the third aperture 116 and is clearance-fitted in the first and second apertures 346 and 526, since the positioning pin is fixedly fitted in the third aperture of the housing, it is possible to eliminate the fitting clearance of the positioning pin 80 with the housing 10a, further reduce the angular positioning error between the fixed scroll and the housing, and thus improve the accuracy of the angular positioning of the fixed scroll with respect to the housing, as compared with the embodiment in which the positioning pin is clearance-fitted in the third aperture.

In the compressor according to the exemplary embodiment of the present application, as shown in fig. 3, the radially outer end portion of the end plate 22a of the orbiting scroll 20a directly faces the inner circumferential wall of the housing 10a on the side where the positioning pin 80 is not provided, and only the positioning pin is provided between the radially outer end portion of the orbiting scroll 20a and the housing 10a on the side where the positioning pin 80 is provided. Herein, directly facing means that no other member or component (such as a component of the non-orbiting scroll and/or a component of the main bearing housing) is located therebetween. In contrast to the compressor according to the comparative example, the main bearing housing of the compressor according to the exemplary embodiment of the present application does not include the arm portion 54 for bolting with the pilot ring and located radially outward of the orbiting scroll end plate. Therefore, the compressor 10a according to the present disclosure can further increase the end plate area of the orbiting scroll, thereby facilitating scroll overturning and axial force management, and improving the performance and reliability of the compressor.

In comparison with the compressor according to the comparative example, the compressor according to the exemplary embodiment of the present disclosure does not include any bolt for connection, whereby it is possible to avoid the use of a radial space required for bolts, screw holes, and the like, thereby facilitating the provision of a compact and miniaturized compressor design and also simplifying the assembly and installation process of the scroll. Also, according to the exemplary embodiments of the present disclosure, it is possible to utilize parts of the compressor itself as the radial positioning part and the axial positioning part, without additionally providing a guide ring, which further saves the occupied space and simplifies the installation process. Further, in the compressor according to the exemplary embodiment of the present application, since the oldham ring is engaged with the main bearing housing and the orbiting scroll, it is possible to transmit half of the rotation torque to the shell through the main bearing housing, in such a manner that the half of the rotation torque is received by the shell and the half of the rotation torque is received by the pilot pin, thereby improving the reliability of the compressor.

Second embodiment

Fig. 8 is a partial longitudinal sectional view of a scroll compressor according to a second exemplary embodiment of the present invention. Hereinafter, the same components are denoted by the same reference numerals, and "a" in the first exemplary embodiment is replaced with "b" in the second exemplary embodiment for similar components, while the rest remains the same. The scroll compressor has the same basic structure and function as the scroll compressor of the first exemplary embodiment, and therefore, the description thereof is omitted, and only the differences thereof will be described below.

As shown in fig. 8, the radially protruding portion 110b of the housing 10b of the scroll compressor 1b according to the second exemplary embodiment of the present disclosure does not include the third aperture, and the sound-deadening cap 90b is formed with the third aperture 92b at a position corresponding to the first aperture 346 (the sound-deadening cap 90b corresponds to a component fixedly connected to the housing according to the present invention and also corresponds to an axial positioning member according to the present invention). Similar to scroll compressor 1a according to the first exemplary embodiment of the present disclosure, locating pin 80 may extend through third aperture 92b of sound-damping cover 90b, first aperture 346 of non-orbiting scroll 30a, and second aperture 526 of main bearing housing 50a in scroll compressor 1 b. Specifically, in the exemplary embodiment of fig. 8, locating pin 80 is fixedly fitted within second aperture 526 of main bearing housing 50a and third aperture 92b of sound-damping cover 90b, and locating pin 80 is slidably fitted within first aperture 346 of non-orbiting scroll 30 a. For example, the locating pin 80 is secured within the second aperture 526 of the main bearing housing 50a and the third aperture 92b of the sound attenuating cover 90b by an interference fit, and the locating pin 80 is a small clearance fit within the first aperture 346. Of course, the locating pin may be fixedly and/or slidably fitted within the first through third apertures in any other suitable manner.

As shown in fig. 8, the positioning pin 80 is fitted in both the first aperture 346 of the non-orbiting scroll 30a and the third aperture 92b of the sound-deadening cap 90b fixed to the housing 10b, and therefore it is possible to prevent the non-orbiting scroll 30a from being angularly displaced with respect to the housing 10b, maintaining the angular positioning of the non-orbiting scroll 30a with respect to the housing 10 b. Also, the positioning pin 80 is slidably fitted in the aperture of the non-orbiting scroll 30a, so that the non-orbiting scroll 30a can perform a certain range of axial movement in the axial direction without being hindered by the positioning pin, thereby providing the scroll assembly with a certain axial flexibility to increase reliability and safety of the compressor. Further, positioning pin 80 is also fitted in the hole of main bearing housing 50a at the same time, and therefore, positioning pin 80 can prevent rotation of non-orbiting scroll 30a with respect to main bearing housing 50 a. Thus, by fitting the positioning pins 80 in the first, second, and third apertures at the same time, it is made possible to simultaneously maintain the relative angular positions of any two of the fixed scroll, the main bearing housing, and the housing and to enable axial floating of the fixed scroll relative to the main bearing housing. Further, in the second embodiment shown in fig. 8, since the positioning pin 80 is fixedly fitted in the second aperture 526 of the main bearing housing 50a and the third aperture 92b of the sound-deadening cap 90b fixedly connected to the housing, fitting clearances of the positioning pin 80 with the main bearing housing 50a and the housing 10a are simultaneously eliminated, whereby an angular positioning error between any two of the fixed scroll, the main bearing housing, and the housing can be simultaneously reduced. In this way, on the one hand, the accuracy of the angular positioning of the fixed scroll with respect to the main bearing housing is improved, and since the oldham ring 60a is simultaneously fitted with the movable scroll 20a and the main bearing housing 50a, the improved accuracy of the angular positioning between the fixed scroll 30a and the main bearing housing 50a can further improve the accuracy of the angular positioning of the fixed scroll 30a and the movable scroll 20a, so that the overall performance of the compressor can be effectively improved by the accurate positioning between the fixed scroll and the movable scroll. On the other hand, the improved angular positioning accuracy of the main bearing housing relative to the housing enables components such as oil return holes or air suction holes that are fitted on the main bearing housing to be positioned more accurately relative to the housing. In still another aspect, an angular positioning error between the non-orbiting scroll and the housing may be further reduced, thereby improving accuracy of angular positioning of the non-orbiting scroll with respect to the housing.

It should be noted herein that although the compressor of the above-described exemplary embodiment includes the orifice fitted to the sound-deadening cap, it should be understood by those skilled in the art that exemplary embodiments according to the present disclosure are not limited thereto, and the orifice may be provided on any component fixedly connected to the housing of the compressor.

Third embodiment

Fig. 9 is a partial longitudinal sectional view of a scroll compressor according to a third exemplary embodiment of the present invention. Hereinafter, the same components are denoted by the same reference numerals, and "c" is substituted for "b" in the second exemplary embodiment for similar components in the third exemplary embodiment, while the rest remains the same. The main structure and function of the scroll compressor are substantially the same as those of the scroll compressor of the second exemplary embodiment, and therefore, the description is omitted, and only the differences will be described below.

As shown in fig. 9, similar to the scroll compressor 1b according to the second exemplary embodiment of the present disclosure, the positioning pin 80 may extend through the third aperture 92b of the sound-deadening cover 90b, the first aperture 346 of the non-orbiting scroll 30a, and the second aperture 526 of the main bearing housing 50a in the scroll compressor 1 c. Specifically, in the exemplary embodiment of fig. 9, locating pin 80 is fixedly fit within first aperture 346 of non-orbiting scroll 30a, and slidably fit within second aperture 526 of main bearing housing 50a and third aperture 92b of sound attenuating cover 90 b. For example, locating pin 80 is secured within first aperture 346 of non-orbiting scroll 30a by an interference fit, and locating pin 80 is fitted within second aperture 526 of main bearing housing 50a and third aperture 92b of sound-deadening cap 90b by a small clearance fit. Of course, the locating pin may be fixedly and/or slidably engaged within the aperture in any other suitable manner.

As shown in fig. 9, the positioning pin 80 is fitted in both the first aperture 346 of the orbiting scroll 20a and the third aperture 92b of the sound-deadening cap 90b fixed to the housing, and therefore it is possible to prevent the fixed scroll 30a from being angularly displaced with respect to the housing 10b, and to maintain the angular positioning of the fixed scroll 30a with respect to the housing 10 b. Also, since the positioning pin 80 is slidably fitted in the second aperture 526 of the main bearing housing 50a and the third aperture 92b of the sound-deadening cover 90b, the positioning pin 80 can perform a certain range of axial movement in the axial direction together with the non-orbiting scroll, thereby providing a certain axial flexibility to the scroll assembly to increase the reliability and safety of the compressor. Further, positioning pin 80 is also fitted in the hole of main bearing housing 50a at the same time, so that positioning pin 80 can prevent rotation of non-orbiting scroll 30a with respect to main bearing housing 50 a. Thus, by fitting the positioning pins 80 in the first, second, and third apertures at the same time, it is made possible to simultaneously maintain the relative angular positions of any two of the fixed scroll, the main bearing housing, and the housing and to enable axial floating of the fixed scroll relative to the main bearing housing. In the third embodiment shown in fig. 9, the positioning pin 80 is fixedly fitted in the first aperture 346 of the fixed scroll 30a, whereby, compared with the embodiment in which the positioning pin is clearance-fitted in the first aperture 346, it is possible to eliminate the fitting clearance of the positioning pin 80 and the fixed scroll 30a, reduce the angular positioning error between the fixed scroll and the main bearing housing, and thereby improve the accuracy of the angular positioning of the fixed scroll relative to the main bearing housing, while since the oldham ring 60a is simultaneously fitted with the movable scroll 20a and the main bearing housing 50a, the improved accuracy of the angular positioning between the fixed scroll 30a and the main bearing housing 50a can further improve the accuracy of the angular positioning of the fixed scroll 30a and the movable scroll 20a, and thereby the overall performance of the compressor can be effectively improved. On the other hand, the positioning pin is fixedly fitted in the first hole, and the fitting clearance of the positioning pin 80 and the fixed scroll 30a is eliminated, so that the angular positioning error between the fixed scroll and the housing can also be reduced as compared with the embodiment in which the positioning pin is clearance fitted in the first hole, thereby improving the accuracy of the angular positioning of the fixed scroll relative to the housing.

As described above, the positioning pin 80 of the exemplary embodiment of the present disclosure may be fitted in the hole formed in the non-orbiting scroll, the main bearing housing, and the shell or the member fixedly connected to the shell in various ways as long as it can maintain the relative angular positioning between the non-orbiting scroll, the main bearing housing, and the shell and allow the non-orbiting scroll to perform an axial movement with respect to the main bearing housing. Preferably, the precise positioning of the fixed scroll with respect to the main bearing housing may be achieved by adjusting the fitting manner of the positioning pin in the first and second apertures, as in the first, second and third embodiments described above, the positioning pin 80 is fixedly fitted in the second aperture 526 of the main bearing housing 50a or the first aperture 346 of the fixed scroll 30a, in this way, the fitting clearance of the positioning pin 80 with the fixed scroll 30a or the main bearing housing 50a may be eliminated, the angular positioning error between the fixed scroll and the main bearing housing is reduced, thereby improving the precision of the angular positioning of the fixed scroll with respect to the main bearing housing, and at the same time, since the oldham ring is fitted with the movable scroll and the main bearing housing at the same time, the improved precision of the angular positioning between the fixed scroll and the main bearing housing, the precision of the angular positioning of the fixed scroll 30a and the movable scroll 20a can be further improved, therefore, the overall performance of the compressor can be effectively improved by utilizing the relative accurate positioning between the fixed scroll and the movable scroll.

Although various embodiments of the present invention have been described in detail herein, it is to be understood that this invention is not limited to the particular embodiments described and illustrated in detail herein, 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 be within the scope of the present invention. Moreover, all the components described herein may be replaced by other technically equivalent components.