Scroll Compressor

The present disclosure relates to the field of compressor technology, and more particularly, to a scroll compressor.

The improvements of existing scroll compressors have focused primarily on increasing the suction and increasing the volumetric efficiency. Existing scroll compressors often use an orbiting scroll and a fixed scroll to compress the medium. Therefore, there is a problem of pressure imbalance between the orbiting scroll on the working chamber side and on the transmission assembly side. The pressure imbalance will cause the orbiting scroll to have axial movement. This axial movement will not only increase the noise and wear of the orbiting scroll during operation, but also cause an axial gap between the orbiting scroll and the fixed scroll. This axial gap provides a path for the medium to leak from the high-pressure working chamber to the low-pressure working chamber, thereby reducing the volumetric efficiency of the scroll compressor. To this end, there is a technical solution in the prior art that uses high-pressure media to establish backpressure on one side of the transmission assembly of the orbiting scroll to eliminate the axial gap between the orbiting scroll and the fixed scroll. However, the backpressure established by the prior art solution will exist even when there is no axial gap between the orbiting scroll and the fixed scroll, which causes the contact pressure between the orbiting scroll and the fixed scroll to increase unnecessarily, thereby aggravating the wear of the two and causing unnecessary consumption of the high-pressure medium and reducing the volumetric efficiency.

Therefore, there is an urgent need in the art for a technical solution that can achieve a better balance between eliminating axial gaps and maintaining volumetric efficiency, or even take both into account.

In order to address the problems in the prior art described above, the present disclosure provides an improved scroll compressor, comprising: a fixed scroll, the fixed scroll comprising a fixed disk body and a fixed scroll body protruding from the fixed disk body; and an orbiting scroll, the orbiting scroll comprising an orbiting disk body and an orbiting scroll body protruding from the orbiting disk body and cooperating with the fixed scroll body, the orbiting disk body having a bottom surface away from the orbiting scroll body, and the orbiting scroll body having a top surface away from the orbiting disk body; wherein the orbiting scroll is provided with a sealing groove recessed from the top surface and a through hole extending from the bottom wall of the sealing groove to the bottom surface, and also includes a sealing strip accommodated in the sealing groove, the inner end of the sealing strip respectively defining an end gap and a bottom gap with the inner end wall and the bottom wall of the sealing groove.

The present disclosure may be embodied as a schematic example in the accompanying drawings. However, it should be noted that the accompanying drawings are merely schematic and that any change contemplated under the teachings of the present disclosure shall be considered to be included within the scope of the present disclosure.

Further features and advantages of the present disclosure will become more apparent from the following description, which is made with reference to the accompanying drawings. Exemplary examples of the present disclosure are shown in the accompanying drawings, and the various accompanying drawings are not necessarily drawn in actual proportions. However, the present disclosure may be implemented in many different forms and should not be construed as necessarily limiting to the exemplary examples disclosed herein. Rather, these exemplary examples are merely provided for illustrative purposes of the present disclosure and for delivering the spirit and substance of the present disclosure to those skilled in the art.

It is the aim of the present disclosure to propose a scroll compressor with a novel design. Through the novel design of the scroll compressor, during operation, when an axial gap is generated between the orbiting scroll and the fixed scroll, the working chamber and the backpressure chamber can be automatically connected so that the high-pressure medium in the working chamber can enter the backpressure chamber, thereby generating a backpressure in the backpressure chamber that helps to eliminate the axial gap and reliably avoiding axial leakage of the medium (for example, refrigerant) caused by the axial gap. In particular, through the novel design of the scroll compressor, during operation, when there is no axial gap between the orbiting scroll and the fixed scroll, the working chamber and the backpressure chamber can also be automatically isolated, thereby avoiding the generation of unexpected backpressure in the backpressure chamber, avoiding the increase in contact pressure between the orbiting scroll and the fixed scroll due to the unexpected backpressure, which aggravates the wear of the two, and avoiding the reduction of the volumetric efficiency of the scroll compressor due to the loss of high-pressure medium. More specifically, through the novel design of the scroll compressor, a certain degree of backpressure can be maintained in the working chamber during operation, which helps to prevent the generation of an axial gap between the orbiting scroll and the fixed scroll. At the same time, the backpressure will not be large enough to significantly increase the wear of the orbiting scroll and the fixed scroll and reduce the volumetric efficiency of the scroll compressor. That is, a scroll compressor according to the present disclosure can automatically eliminate the axial gap between the orbiting scroll and the fixed scroll during operation while taking into account the wear of the orbiting scroll and the fixed scroll and the volumetric efficiency of the scroll compressor and can also prevent the generation of an axial gap between the orbiting scroll and the fixed scroll.

A plurality of optional but non-limiting embodiments of a scroll compressor according to the present disclosure are described in detail below with reference to the various figures. It is to be noted, however, that among the terms used in the present disclosure, the terms “axial direction,” “radial direction,” “circumferential direction,” and the like have their common meanings in the art. Specifically, the axial direction can be a direction parallel to or coincident with the rotation axis of the main shaft of the scroll compressor, that is, the axial direction can be defined by the rotation axis of the main shaft; the radial direction can be any direction perpendicular to the axial direction; and the circumferential direction can be any direction surrounding the axial direction.

Referring to, there is shown a schematic cross-sectional view of a scroll compressor according to an embodiment of the present disclosure. As shown in, the scroll compressorgenerally includes a housingand a fixed scroll, an orbiting scroll, a motor, and a transmission assemblyhoused in the housing.

The fixed scrollis fixedly disposed in the housingand includes a fixed disk bodyand a fixed scroll bodyprotruding from the fixed disk bodyalong the axial direction XX', wherein the fixed scroll bodyextends from the center of the fixed disk bodytoward the periphery of the fixed disk bodyalong an involute or in the form of an involute. The orbiting scrollis movably disposed in the housingand includes an orbiting disk bodyand an orbiting scroll bodyprotruding from the orbiting disk bodyalong the axial direction XX', wherein the orbiting scroll bodyextends from the center of the orbiting disk bodytoward the periphery of the orbiting disk bodyalong an involute or in the form of an involute. The fixed scroll bodyof the fixed scrolland the orbiting scroll bodyof the orbiting scrollare arranged in a downward direction such that the fixed scroll bodyis oriented to protrude from the fixed disk bodytowards the orbiting disk body, while the orbiting scroll bodyis oriented to protrude from the orbiting disk bodytowards the fixed disk body. In addition, the sidewall of the fixed scroll bodymay be engaged with the sidewall of the orbiting scroll body, thereby defining a plurality of working chambers distributed along an involute therebetween.

The motorincludes a statorfixedly disposed in the housingand a rotorrotatably disposed in the housing, wherein the rotorcan rotate about the axial direction XX' under the drive of a rotational magnetic field generated upon power-up of the stator. The transmission assemblyincludes a spindle, a swivel shaft, and an eccentric shaftthat connects the swivel shaftto the spindle. The spindlemay be, for example, non-rotatably connected to the rotorby welding, bolts, keyways, etc., such that the spindlecan rotate about the axial direction XX′ with the rotor. The swivel shaftis connected to the orbiting scroll, for example, via a bearing, wherein the orbitingmay have a bearing seaton the opposite side of the orbiting disk bodyfrom the orbiting scroll body, the bearingmay be received in the bearing seat, and the swivel shaftmay be inserted into the bearing. In addition, the eccentric shaftmay be inserted into the spindlein a manner that is stationary and eccentric relative to the spindleand inserted into the swivel shaftin a manner that is rotatable and eccentric relative to the swivel shaftso that the swivel shaftis connected to the spindlein a manner that is eccentric and rotatable relative to the spindle. In this configuration, rotation of the spindleabout the axial direction XX′ will be converted into a revolution of the swivel shaftabout the axial direction XX′ and the revolution of the swivel axisabout the axial direction XX′ will be converted into a revolution of the orbiting scrollabout the axial direction XX′. Of course, in order to inhibit the rotation tendency of the orbiting scroll, the scroll compressormay also include an anti-rotation structure acting on the orbiting scrollin order to ensure that the orbiting scrollrevolves or translates about the axial direction XX′ without rotating

In the above configuration, the motormay drive the spindleto rotate after being powered on and the spindlecan drive the orbiting scrollto revolve through the eccentric shaft, the swivel shaft, and the bearing. As the orbiting scrollrevolves, each of the multiple working chambers defined between the side walls of the fixed scroll bodyand the orbiting scroll bodywill move along the involute from the periphery of the fixed scroll bodyand the orbiting scroll bodytoward the center of the two, and the working chamber that moves to the center of the fixed scroll bodyand the orbiting scroll bodywill disappear. At the same time, a new working chamber will be generated at the periphery of the fixed scroll bodyand the orbiting scroll body, and the volume of each working chamber will gradually decrease with the above movement. Thus, during operation of the scroll compressor, the medium (e.g., air, nitrogen, or a refrigerant such as R22 or HFC) may enter the working chamber from the periphery of the fixed scroll bodyand the orbiting scroll bodyand then be transported and compressed by the working chamber toward the center of the two before finally being discharged from the working chamber at the center of the two (e.g., through the exhaust holedisposed in the fixed disk body). As the orbiting scrollcontinuously revolves, the medium may be continuously transported, compressed, and discharged in the above manner.

As can be seen from the foregoing, the pressures in the various working chambers distributed along the involute are different. Specifically, the pressure in the working chamber closer to the center of the fixed scroll bodyand the orbiting scroll bodyis higher, and vice versa. In order to prevent the medium in the high-pressure working chamber from leaking into the low-pressure working chamber through the axial gap between the fixed scrolland the orbiting scroll(this leakage may be referred to as axial leakage), it is necessary to maintain contact between the orbiting scroll bodyand the fixed disk bodyso as to eliminate the axial gap between the orbiting scroll bodyand the fixed disk bodyand to ensure contact between the fixed scroll bodyand the orbiting disk bodyso as to eliminate the axial gap between the fixed scroll bodyand the orbiting disk body. In fact, since the height of the fixed scroll bodyis the same as the height of the orbiting scroll body, the two axial gaps described above are created at the same time and can be eliminated simultaneously, so for brevity the two axial gaps are referred to as the axial gap between the fixed scrolland the orbiting scroll. However, the pressure in the various working chambers tends to push the fixed scrolland the orbiting scrollaway from each other, thereby creating an axial gap between the two. To this end, the present disclosure proposes the following technical solution for eliminating the axial gap between the fixed scrolland the orbiting scroll.

Referring to,shows a schematic top view of an orbiting scroll with no sealing strip for the scroll compressor shown in,shows a schematic partial cross-sectional view of the orbiting scroll taken along line A-A in, andshows a schematic cross-sectional view of the orbiting scroll taken along line B-B in. As shown in, the orbiting scroll bodyhas an inner endproximate to the center of the orbiting disk bodyand an outer endproximate to the periphery of the orbiting disk bodyand extends from the inner endto the outer endalong an involute or in the form of an involute. In addition, the orbiting scroll bodyalso has a top surfacethat is away from the orbiting disk bodyalong the axial direction XX′ and is intended to be in contact with the fixed disk body, and the orbiting scrollis also provided with a sealing grooverecessed from the top surfaceof the orbiting scroll body. The sealing groovehas an inner end wallclose to the inner endof the orbiting scroll body(that is, close to the center of the orbiting disk body) and an outer end wallclose to the outer endof the orbiting scroll body(that is, close to the periphery of the orbiting disk body) or is defined between the inner end walland the outer end walland also extends from the inner end wallto the outer end wallalong an involute or in the form of an involute. Of course, as shown in, the sealing groovedoes not necessarily extend over the entire length of the orbiting scroll bodyfrom the inner endto the outer end, that is, the inner end wallmay be spaced apart from the inner endand the outer end wallmay be spaced apart from the outer end.

As shown in, the sealing grooveis recessed from the top surfacealong the axial direction XX′ and terminates at the bottom wall, and a portion of the bottom wallof the sealing groovenear the inner end wallis further recessed, so that a portion of the sealing grooveclose to the inner end wallforms an auxiliary groove, that is, the auxiliary groovecan be composed of a local deepened portion of the sealing grooveor can be regarded as a local deepened portion of the sealing groove, and the local deepened portion has a greater depth relative to other portions of the sealing groove. The so-called depth can be the distance between the bottom wall of the local deepened portion or the bottom wallof the sealing grooveand the top surfacemeasured along the axial direction XX′. In particular, as shown in, the auxiliary grooveis arranged adjacent to the inner end wallof the sealing groovesuch that the auxiliary grooveis partially defined by the inner end wall. Of course, this is merely illustrative, and in an embodiment not shown, the auxiliary groovemay also be spaced apart from the inner end wallsuch that a portion of the bottom wallis located between the auxiliary grooveand the inner end wall.

As shown in, the orbiting disk bodyhas a bottom surfaceaway from the orbiting scroll bodyon the opposite side of the orbiting scroll body(which may be referred to simply as a rear side of the orbiting disk bodyor the orbiting scroll), i.e., the bottom surfacefaces a direction away from the orbiting scroll body, i.e., the back against the orbiting scroll body. The orbiting scrollis also provided with a through holeextending from the bottom wallof the sealing grooveof the orbiting scroll bodythrough the orbiting scroll bodyand the orbiting disk bodyto the bottom surfaceof the orbiting disk body, that is, the through holeleads to the sealing grooveat one end or has an opening opened on the bottom wallof the sealing groove, and leads to the rear side of the orbiting disk bodyat the other end or has an opening opened on the bottom surfaceof the orbiting disk bodyso that the through holecan fluidly connect the sealing groovewith the rear side of the orbiting scroll. In particular, as shown in, the through holeis spaced apart from the auxiliary groove, i.e., the through holeopens to the bottom wallof the sealing grooverather than the local deepened portion of the sealing groove. In particular, as shown in, the through holeextends along a straight path from the bottom wallof the sealing grooveto the bottom surfaceof the orbiting disk body, thereby reducing the pressure loss of the high-pressure medium in the through holeand helping to efficiently establish backpressure. Of course, this is merely illustrative, and in an embodiment not shown, the through holemay also extend along a bent, curved, or other shaped path.

Continuing to refer to,shows a schematic top view of an orbiting scroll with a sealing strip for the scroll compressor shown in,shows a schematic partial cross-sectional view of the orbiting scroll taken along line A-A in, andshows a schematic cross-sectional view of the orbiting scroll taken along line B-B in. As shown in, the orbiting scrollalso includes a sealing striphoused in the sealing groovehaving an inner endproximate to the inner end wallof the sealing grooveand an outer endproximate to the outer end wallof the sealing grooveand arranged to extend from the inner endto the outer endalong an involute or in the form of an involute. Further, as shown in, the inner endof the sealing stripis spaced from the inner end wallof the sealing groovesuch that a portion of the sealing groovebetween the inner endand the inner end wallforms an end gap Gl leading to the top surfaceof the orbiting scroll body, and the inner endof the sealing stripis also spaced from the bottom wallof the sealing grooveso that a portion of the sealing groovebetween the inner endand the bottom wall(i.e., below the inner end) forms a bottom gap Gthat is fluidly connected to the above-mentioned end gap G. In particular, as shown in, the opening of the through holeon the bottom wallis spaced apart from the bottom gap Gsuch that the sealing stripcan make contact with the bottom wallof the sealing grooveat the through holeto cover the through holeso as to close the opening of the through holeon the bottom wall. More particularly, as shown in, the sealing stripand the sealing grooveare sized and shaped such that the sealing stripcompletely fills the sealing groovebetween the bottom gap Gand the opening of the through holeon the bottom wallso that the sealing stripis able to prevent the high-pressure medium from flowing from the bottom gap Gto the through holewhen the orbiting scroll bodymakes contact with the fixed disk body, thereby completely closing the opening of the through holeon the bottom wall. More particularly, the sealing stripmay completely fill the sealing groovebetween the bottom gap Gand its outer end. In particular, as shown in, the length of the sealing groovebetween the bottom gap Gand the opening of the through holeon the bottom wall(e.g., measured along an involute) is less than ½, ⅕, or 1/10 of the total length of the sealing groovesuch that the opening of the through holeon the bottom wall, while spaced apart from the bottom gap G, is still proximate to the bottom gap G.

In this configuration, during the operation of the scroll compressor, on the one hand, when an axial gap is generated between the fixed scrolland the orbiting scroll(the axial gap is generated, for example, due to the medium in each working chamber applying pressure to the fixed scrolland the orbiting scroll), since the end gap Gl is positioned close to the inner endof the orbiting scroll body, the high-pressure medium in the working chamber near the center of the orbiting scroll bodycan flow through the end gap Gto the bottom gap Gand then apply pressure to the sealing stripbelow the inner endthereof. This pressure can lift the inner end, thereby causing an additional gap to be generated between the sealing stripand the bottom wallof the sealing groove. The high-pressure medium will flow into the additional gap and further lift the sealing strip, thereby causing the additional gap to gradually expand along the length of the sealing strip. The high-pressure medium can thereby gradually flow to the bottom of the entire sealing strip, thereby lifting the entire sealing stripuntil the sealing stripabuts against the fixed disk body. The sealing stripabutting against the fixed disk bodycan close the axial gap between the fixed scrolland the orbiting scroll, thereby avoiding axial leakage. In the above process where the sealing stripis gradually raised by the high-pressure medium from the bottom gap G, when the additional gap reaches the through hole, the sealing stripis not able to cover the through holedue to being lifted and thus opens the through holeso that a portion of the high-pressure medium can flow through the through holeto the rear side of the orbiting scrolland create a backpressure on the rear side of the orbiting scroll, which can push the orbiting scrolltowards the fixed scroll, thereby eliminating the axial gap between the fixed scrolland the orbiting scroll. Accordingly, the scroll compressoraccording to the present disclosure is able to automatically close and eliminate the axial gap after an axial gap is created between the fixed scrolland the orbiting scroll, thereby automatically avoiding axial leakage. In addition, since the through holeis disposed before the outer end wallof the sealing groove, especially with the through holeapproaching the bottom gap G, the above-mentioned backpressure may be established before the entire sealing stripis lifted so that the axial gap may be eliminated before the entire sealing stripis lifted and the high-pressure medium does not have to flow beneath the entire sealing strip. Thus, the scroll compressoraccording to the present disclosure can reduce the use of high-pressure medium in addition to automatically closing and eliminating the axial gap, thereby maintaining a higher volumetric efficiency. On the other hand, when no axial gap is created between the fixed scrolland the orbiting scroll, the sealing stripmay cover the through hole, thereby preventing the high-pressure medium from leaking through the through holeto the rear side of the orbiting scroll, which also maintains a high volumetric efficiency and avoids the establishment of unexpected backpressure on the rear side of the orbiting scroll, which may lead to increased wear of the fixed scrolland the orbiting scroll. In short, the scroll compressor according to the present disclosure can automatically close and eliminate the axial gap while maintaining a high volumetric efficiency when an axial gap is generated and can also maintain a high volumetric efficiency and avoid increased wear of the fixed scroll and the orbiting scroll when an axial gap is not generated.

In particular, as shown in, the inner endof the sealing stripis suspended over the auxiliary groovesuch that a portion of the auxiliary grooveis under the sealing strip, forming a bottom gap Gin the auxiliary groove, while another portion of the auxiliary groovepasses through the end gap Gl to the top surfaceof the orbiting scroll body. That is, the sealing stripcovers only a portion of the auxiliary groovesuch that it forms a bottom gap Gand leaves another portion of the auxiliary grooveuncovered such that the bottom gap Gcan be fluidly connected to the end gap Gl through the other portion. More particularly, as shown in, the auxiliary grooveis adjacent to the inner end wallof the sealing groove. Thus, as long as the inner endof the sealing stripis spaced apart from the inner end wallof the sealing groove, an end gap Gl can be formed between the inner endand the inner end wall, and a bottom gap Gcan be formed below the inner end. In this configuration, merely machining the auxiliary grooveat the inner end wallof the sealing groovecan form the bottom gap Gwithout special machining of the sealing strip, thereby reducing the configuration cost of the orbiting scroll.

In particular, referring to,shows a schematic top view of an orbiting scroll with a sealing strip of a scroll compressor according to another embodiment of the present disclosure andshows a schematic partial cross-sectional view of the orbiting scroll taken along line A-A in. As shown in, the sealing stripis thinned at the inner end, i.e., the sealing striphas a thinned portion at the inner end, which is less than the thickness of the other portions of the sealing stripsuch that the inner endis spaced apart from the bottom wallof the sealing groove, forming a bottom gap Gbetween the inner endand the bottom wall. Thus, the embodiment shown indiffers from the embodiment shown inin that the bottom gap Gis formed by the thinning of the sealing striprather than by the auxiliary groove. In this configuration, the bottom gap Gcan be formed by merely machining the thinned portion at the inner endof the sealing stripwithout special machining of the bottom wallof the sealing groove, thereby reducing the configuration cost of the orbiting scroll. Of course, in the embodiment shown in, the auxiliary groovemay also be present so as to form the bottom gap Gwith the thinned portion of the sealing strip.

In particular, referring to,shows a schematic top view of an orbiting scroll without a sealing strip of a scroll compressor according to another embodiment of the present disclosure andshows a schematic partial cross-sectional view of an orbiting scroll with a sealing strip taken along line B-B in. The embodiment shown inanddiffers from the embodiment shown inin that the orbiting scrollalso has an auxiliary grooverecessed from the bottom wallof the sealing groove. The auxiliary grooveextends from the bottom gap G(in particular, the auxiliary groove) along the sealing groovetowards the outer end wallof the sealing groove. That is, the auxiliary grooveopens into the bottom gap Gat one end and extends along an involute or in the form of an involute from this end towards the outer end wallof the sealing groovein the bottom wallof the sealing groove. In this configuration, the high-pressure medium flowing through the end gap Gl into the bottom gap Gmay further flow into the auxiliary grooveand in turn be quickly directed below the sealing stripby the auxiliary grooveso that the high-pressure medium can apply pressure to the sealing stripin the auxiliary groove, which helps ensure successful lifting of the sealing strip. Therefore, compared with the configuration shown in, the configuration shown incan more reliably ensure that the sealing stripis lifted up when an axial gap is generated so as to close the axial gap through the auxiliary groove, especially when the sealing stripis bonded to the sealing grooveby lubricating oil. The auxiliary groovecan also reduce the contact area between the sealing stripand the bottom wallso as to reduce the resistance encountered by the sealing stripwhen it is lifted.

In particular, as shown in, the auxiliary grooveextends from the bottom gap Gto the outer end wallof the sealing groove. In this configuration, the high-pressure medium may be directed below the entire sealing stripby the auxiliary grooveso as to more reliably ensure lift of the sealing strip. In particular, as shown in, the sealing groovealso has two sidewallsor is defined between the two sidewallsthat are opposite each other along the radial direction and coupled through the inner end walland the outer end wall, and the orbiting scrollhas two auxiliary grooves, wherein each secondary grooveis adjacent to one sidewallso as to extend along the sidewall. In this configuration, the two auxiliary groovesare arranged substantially symmetrically on both sides of the sealing stripsuch that the high-pressure medium in the two auxiliary groovesapplies substantially the same pressure to the sealing strip, thereby merely raising the sealing stripwithout causing the sealing stripto twist. In particular, as shown in, the auxiliary grooveis spaced apart from the through holesuch that the through holeonly leads to the bottom wallof the sealing groovebut not to the auxiliary groove. In this configuration, the sealing stripmay still block the flow of the high-pressure medium in the bottom gap Gto the through holewhen the orbiting scroll bodyis in contact with the fixed disk body, thereby maintaining higher volumetric efficiency for the scroll compressor.

In particular, referring to,shows a schematic top view of an orbiting scroll without a sealing strip of a scroll compressor according to another embodiment of the present disclosure andshows a schematic partial cross-sectional view of an orbiting scroll with a sealing strip taken along line B-B in. The embodiment shown indiffers from the embodiment shown inin that the through holeintersects the auxiliary groovesuch that the through holeleads to both the sealing grooveand the auxiliary groove. In other words, the through holehas openings on both the bottom wallof the sealing grooveand the bottom wallof the auxiliary groove. In this configuration, because the sealing stripcan only cover the opening of the through holeon the bottom wallof the sealing groovebut cannot cover the opening of the through holeon the bottom wallof the auxiliary groove, even if the sealing stripis not lifted, the high-pressure medium entering the bottom gap Gl can enter the through holethrough the opening of the through holeon the bottom wallof the auxiliary groove, thereby establishing a certain degree of backpressure on the rear side of the orbiting scroll. Therefore, the above configuration helps to maintain a certain degree of backpressure on the rear side of the orbiting scrollto prevent the generation of axial gaps. Of course, because the through holeis only partially connected to the auxiliary groove, the backpressure established in the above manner is limited and will not cause a substantial increase in the wear of the fixed scrolland the orbiting scrollor a significant decrease in volumetric efficiency. In particular, with the orbiting scrollhaving two or more auxiliary grooves, the through holemay intersect any one or more of the auxiliary grooves.

In particular, returning to, a backpressure chamberis formed on the rear side of the orbiting disk body, which is fluidly connected to the through hole, i.e., the through holeopens to the backpressure chamberat the bottom surfaceof the orbiting disk body. More particularly, an end of the swivel shaftis spaced apart from the bottom surfaceof the orbiting disk bodysuch that the backpressure chamberis jointly defined in the bearing seatby an inside surface of the bearing, a bottom surfaceof the orbiting disk body, and an end of the swivel shaft. In this configuration, the low volume of the backpressure chamberis such that a small amount of high-pressure medium is sufficient to establish sufficient backpressure in the backpressure chamber, thereby reducing the amount of high-pressure medium used to establish the backpressure and helping to maintain the higher volumetric efficiency of the scroll compressor. The backpressure chamberis generally closed, thereby preventing leakage of the high-pressure medium from the backpressure chamberand helping to maintain backpressure in the backpressure chamber.

The above optional but non-limiting examples of a scroll compressor according to the present disclosure are described in detail above with reference to the figures. For those skilled in the art, without departing from the spirit and substance of the present disclosure, modifications and additions to techniques and structures and recombination of features in various examples shall clearly be considered to be included within the scope of the present disclosure. As a result, these modifications and supplements that may be conceived under the guidance of the present disclosure shall be considered as a part of the present disclosure. The scope of the present disclosure includes known equivalent technologies and equivalent technologies not yet foreseen as of the filing date of this disclosure.