SCROLL COMPRESSOR

Description

BACKGROUND

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.

SUMMARY

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.

BRIEF DESCRIPTION OF THE DRAWINGS

The accompanying drawings illustrate exemplary examples of the present disclosure. These accompanying drawings should not be construed as necessarily limiting the scope of the present disclosure, wherein:

FIG. 1 is a schematic cross-sectional view of a scroll compressor according to one embodiment of the present disclosure;

FIG. 2 is a schematic top view of an orbiting scroll of the scroll compressor shown in FIG. 1 without a sealing strip;

FIG. 3A is a schematic partial cross-sectional view of the orbiting scroll taken along line A-A in FIG. 2; FIG. 3B is a schematic cross-sectional view of the orbiting scroll taken along line B-B in FIG. 2; and FIG. 4 is a schematic top view of the orbiting scroll with a sealing strip of the scroll compressor shown in FIG. 1;

FIG. 5A is a schematic partial cross-sectional view of the orbiting scroll taken along line A-A in FIG. 4; FIG. 5B is a schematic cross-sectional view of the orbiting scroll taken along line B-B in FIG. 4; and FIG. 6 is a schematic top view of the orbiting scroll with a sealing strip of the scroll compressor according to another embodiment of the present disclosure;

FIG. 7 is a schematic partial cross-sectional view of an orbiting scroll taken along line A-A in FIG. 6;

FIG. 8 is a schematic top view of an orbiting scroll of a scroll compressor without a sealing strip according to yet another embodiment of the present disclosure;

FIG. 9 is a schematic cross-sectional view of an orbiting scroll taken along line B-B in FIG. 8 with a sealing strip;

FIG. 10 is a schematic top view of an orbiting scroll of a scroll compressor without a sealing strip according to another embodiment of the present disclosure; and

FIG. 11 is a schematic cross-sectional view of an orbiting scroll taken along line B-B in FIG. 10 with a sealing strip.

DETAILED DESCRIPTION

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 FIG. 1, there is shown a schematic cross-sectional view of a scroll compressor according to an embodiment of the present disclosure. As shown in FIG. 1, the scroll compressor 10 generally includes a housing 100 and a fixed scroll 200, an orbiting scroll 300, a motor 400, and a transmission assembly 500 housed in the housing 100.

The fixed scroll 200 is fixedly disposed in the housing 100 and includes a fixed disk body 210 and a fixed scroll body 220 protruding from the fixed disk body 210 along the axial direction XX', wherein the fixed scroll body 220 extends from the center of the fixed disk body 210 toward the periphery of the fixed disk body 210 along an involute or in the form of an involute. The orbiting scroll 300 is movably disposed in the housing 100 and includes an orbiting disk body 310 and an orbiting scroll body 320 protruding from the orbiting disk body 310 along the axial direction XX', wherein the orbiting scroll body 320 extends from the center of the orbiting disk body 310 toward the periphery of the orbiting disk body 310 along an involute or in the form of an involute. The fixed scroll body 220 of the fixed scroll 200 and the orbiting scroll body 320 of the orbiting scroll 300 are arranged in a downward direction such that the fixed scroll body 220 is oriented to protrude from the fixed disk body 210 towards the orbiting disk body 310, while the orbiting scroll body 320 is oriented to protrude from the orbiting disk body 310 towards the fixed disk body 210. In addition, the sidewall of the fixed scroll body 220 may be engaged with the sidewall of the orbiting scroll body 320, thereby defining a plurality of working chambers distributed along an involute therebetween.

The motor 400 includes a stator 410 fixedly disposed in the housing 100 and a rotor 420 rotatably disposed in the housing 100, wherein the rotor 420 can rotate about the axial direction XX' under the drive of a rotational magnetic field generated upon power-up of the stator 410. The transmission assembly 500 includes a spindle 510, a swivel shaft 520, and an eccentric shaft 530 that connects the swivel shaft 520 to the spindle 510. The spindle 510 may be, for example, non-rotatably connected to the rotor 420 by welding, bolts, keyways, etc., such that the spindle 510 can rotate about the axial direction XX′ with the rotor 420. The swivel shaft 520 is connected to the orbiting scroll 300, for example, via a bearing 610, wherein the orbiting 300 may have a bearing seat 380 on the opposite side of the orbiting disk body 310 from the orbiting scroll body 320, the bearing 610 may be received in the bearing seat 380, and the swivel shaft 520 may be inserted into the bearing 610. In addition, the eccentric shaft 530 may be inserted into the spindle 510 in a manner that is stationary and eccentric relative to the spindle 510 and inserted into the swivel shaft 520 in a manner that is rotatable and eccentric relative to the swivel shaft 520 so that the swivel shaft 520 is connected to the spindle 510 in a manner that is eccentric and rotatable relative to the spindle 510. In this configuration, rotation of the spindle 510 about the axial direction XX′ will be converted into a revolution of the swivel shaft 520 about the axial direction XX′ and the revolution of the swivel axis 520 about the axial direction XX′ will be converted into a revolution of the orbiting scroll 300 about the axial direction XX′. Of course, in order to inhibit the rotation tendency of the orbiting scroll 300, the scroll compressor 10 may also include an anti-rotation structure acting on the orbiting scroll 300 in order to ensure that the orbiting scroll 300 revolves or translates about the axial direction XX′ without rotating

In the above configuration, the motor 400 may drive the spindle 510 to rotate after being powered on and the spindle 510 can drive the orbiting scroll 300 to revolve through the eccentric shaft 530, the swivel shaft 520, and the bearing 610. As the orbiting scroll 300 revolves, each of the multiple working chambers defined between the side walls of the fixed scroll body 220 and the orbiting scroll body 320 will move along the involute from the periphery of the fixed scroll body 220 and the orbiting scroll body 320 toward the center of the two, and the working chamber that moves to the center of the fixed scroll body 220 and the orbiting scroll body 320 will disappear. At the same time, a new working chamber will be generated at the periphery of the fixed scroll body 220 and the orbiting scroll body 320, and the volume of each working chamber will gradually decrease with the above movement. Thus, during operation of the scroll compressor 10, 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 body 220 and the orbiting scroll body 320 and 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 hole 211 disposed in the fixed disk body 210). As the orbiting scroll 300 continuously 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 body 220 and the orbiting scroll body 320 is 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 scroll 200 and the orbiting scroll 300 (this leakage may be referred to as axial leakage), it is necessary to maintain contact between the orbiting scroll body 320 and the fixed disk body 210 so as to eliminate the axial gap between the orbiting scroll body 320 and the fixed disk body 210 and to ensure contact between the fixed scroll body 220 and the orbiting disk body 310 so as to eliminate the axial gap between the fixed scroll body 220 and the orbiting disk body 310. In fact, since the height of the fixed scroll body 220 is the same as the height of the orbiting scroll body 320, 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 scroll 200 and the orbiting scroll 300. However, the pressure in the various working chambers tends to push the fixed scroll 200 and the orbiting scroll 300 away 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 scroll 200 and the orbiting scroll 300.

Referring to FIGS. 2-3B, FIG. 2 shows a schematic top view of an orbiting scroll with no sealing strip for the scroll compressor shown in FIG. 1, FIG. 3A shows a schematic partial cross-sectional view of the orbiting scroll taken along line A-A in FIG. 2, and FIG. 3B shows a schematic cross-sectional view of the orbiting scroll taken along line B-B in FIG. 2. As shown in FIGS. 1-3B, the orbiting scroll body 320 has an inner end 321 proximate to the center of the orbiting disk body 310 and an outer end 322 proximate to the periphery of the orbiting disk body 310 and extends from the inner end 321 to the outer end 322 along an involute or in the form of an involute. In addition, the orbiting scroll body 320 also has a top surface 323 that is away from the orbiting disk body 310 along the axial direction XX′ and is intended to be in contact with the fixed disk body 210, and the orbiting scroll 300 is also provided with a sealing groove 330 recessed from the top surface 323 of the orbiting scroll body 320. The sealing groove 330 has an inner end wall 331 close to the inner end 321 of the orbiting scroll body 320 (that is, close to the center of the orbiting disk body 310) and an outer end wall 332 close to the outer end 322 of the orbiting scroll body 320 (that is, close to the periphery of the orbiting disk body 310) or is defined between the inner end wall 331 and the outer end wall 332 and also extends from the inner end wall 331 to the outer end wall 332 along an involute or in the form of an involute. Of course, as shown in FIG. 2, the sealing groove 330 does not necessarily extend over the entire length of the orbiting scroll body 320 from the inner end 321 to the outer end 322, that is, the inner end wall 331 may be spaced apart from the inner end 321 and the outer end wall 332 may be spaced apart from the outer end 322.

As shown in FIGS. 2 and 3A, the sealing groove 330 is recessed from the top surface 323 along the axial direction XX′ and terminates at the bottom wall 333, and a portion of the bottom wall 333 of the sealing groove 330 near the inner end wall 331 is further recessed, so that a portion of the sealing groove 330 close to the inner end wall 331 forms an auxiliary groove 340, that is, the auxiliary groove 340 can be composed of a local deepened portion of the sealing groove 330 or can be regarded as a local deepened portion of the sealing groove 330, and the local deepened portion has a greater depth relative to other portions of the sealing groove 330. The so-called depth can be the distance between the bottom wall of the local deepened portion or the bottom wall 333 of the sealing groove 330 and the top surface 323 measured along the axial direction XX′. In particular, as shown in FIGS. 2 and 3A, the auxiliary groove 340 is arranged adjacent to the inner end wall 331 of the sealing groove 330 such that the auxiliary groove 340 is partially defined by the inner end wall 331. Of course, this is merely illustrative, and in an embodiment not shown, the auxiliary groove 340 may also be spaced apart from the inner end wall 331 such that a portion of the bottom wall 333 is located between the auxiliary groove 340 and the inner end wall 331.

As shown in FIGS. 2 and 3B, the orbiting disk body 310 has a bottom surface 311 away from the orbiting scroll body 320 on the opposite side of the orbiting scroll body 320 (which may be referred to simply as a rear side of the orbiting disk body 310 or the orbiting scroll 300), i.e., the bottom surface 311 faces a direction away from the orbiting scroll body 320, i.e., the back against the orbiting scroll body 320. The orbiting scroll 300 is also provided with a through hole 350 extending from the bottom wall 333 of the sealing groove 330 of the orbiting scroll body 320 through the orbiting scroll body 320 and the orbiting disk body 310 to the bottom surface 311 of the orbiting disk body 310, that is, the through hole 350 leads to the sealing groove 330 at one end or has an opening opened on the bottom wall 333 of the sealing groove 330, and leads to the rear side of the orbiting disk body 310 at the other end or has an opening opened on the bottom surface 311 of the orbiting disk body 310 so that the through hole 350 can fluidly connect the sealing groove 330 with the rear side of the orbiting scroll 300. In particular, as shown in FIG. 2, the through hole 350 is spaced apart from the auxiliary groove 340, i.e., the through hole 350 opens to the bottom wall 333 of the sealing groove 330 rather than the local deepened portion of the sealing groove 330. In particular, as shown in FIG. 3B, the through hole 350 extends along a straight path from the bottom wall 333 of the sealing groove 330 to the bottom surface 311 of the orbiting disk body 310, thereby reducing the pressure loss of the high-pressure medium in the through hole 350 and helping to efficiently establish backpressure. Of course, this is merely illustrative, and in an embodiment not shown, the through hole 350 may also extend along a bent, curved, or other shaped path.

Continuing to refer to FIGS. 4-5B, FIG. 4 shows a schematic top view of an orbiting scroll with a sealing strip for the scroll compressor shown in FIG. 1, FIG. 5A shows a schematic partial cross-sectional view of the orbiting scroll taken along line A-A in FIG. 4, and FIG. 5B shows a schematic cross-sectional view of the orbiting scroll taken along line B-B in FIG. 4. As shown in FIGS. 1 and 4-5B, the orbiting scroll 300 also includes a sealing strip 360 housed in the sealing groove 330 having an inner end 361 proximate to the inner end wall 331 of the sealing groove 330 and an outer end 362 proximate to the outer end wall 332 of the sealing groove 330 and arranged to extend from the inner end 361 to the outer end 362 along an involute or in the form of an involute. Further, as shown in FIGS. 4 and 5A, the inner end 361 of the sealing strip 360 is spaced from the inner end wall 331 of the sealing groove 330 such that a portion of the sealing groove 330 between the inner end 361 and the inner end wall 331 forms an end gap Gl leading to the top surface 323 of the orbiting scroll body 320, and the inner end 361 of the sealing strip 360 is also spaced from the bottom wall 333 of the sealing groove 330 so that a portion of the sealing groove 330 between the inner end 361 and the bottom wall 333 (i.e., below the inner end 361) forms a bottom gap G2 that is fluidly connected to the above-mentioned end gap G1. In particular, as shown in FIGS. 2 and 5B, the opening of the through hole 350 on the bottom wall 333 is spaced apart from the bottom gap G2 such that the sealing strip 360 can make contact with the bottom wall 333 of the sealing groove 330 at the through hole 350 to cover the through hole 350 so as to close the opening of the through hole 350 on the bottom wall 333. More particularly, as shown in FIG. 5B, the sealing strip 360 and the sealing groove 330 are sized and shaped such that the sealing strip 360 completely fills the sealing groove 330 between the bottom gap G2 and the opening of the through hole 350 on the bottom wall 333 so that the sealing strip 360 is able to prevent the high-pressure medium from flowing from the bottom gap G2 to the through hole 350 when the orbiting scroll body 320 makes contact with the fixed disk body 210, thereby completely closing the opening of the through hole 350 on the bottom wall 333. More particularly, the sealing strip 360 may completely fill the sealing groove 330 between the bottom gap G2 and its outer end 362. In particular, as shown in FIG. 2, the length of the sealing groove 330 between the bottom gap G2 and the opening of the through hole 350 on the bottom wall 333 (e.g., measured along an involute) is less than ½, ⅕, or 1/10 of the total length of the sealing groove 330 such that the opening of the through hole 350 on the bottom wall 333, while spaced apart from the bottom gap G2, is still proximate to the bottom gap G2.

In this configuration, during the operation of the scroll compressor 10, on the one hand, when an axial gap is generated between the fixed scroll 200 and the orbiting scroll 300 (the axial gap is generated, for example, due to the medium in each working chamber applying pressure to the fixed scroll 200 and the orbiting scroll 300), since the end gap Gl is positioned close to the inner end 321 of the orbiting scroll body 320, the high-pressure medium in the working chamber near the center of the orbiting scroll body 320 can flow through the end gap G1 to the bottom gap G2 and then apply pressure to the sealing strip 360 below the inner end 361 thereof. This pressure can lift the inner end 361, thereby causing an additional gap to be generated between the sealing strip 360 and the bottom wall 333 of the sealing groove 330. The high-pressure medium will flow into the additional gap and further lift the sealing strip 360, thereby causing the additional gap to gradually expand along the length of the sealing strip 360. The high-pressure medium can thereby gradually flow to the bottom of the entire sealing strip 360, thereby lifting the entire sealing strip 360 until the sealing strip 360 abuts against the fixed disk body 210. The sealing strip 360 abutting against the fixed disk body 210 can close the axial gap between the fixed scroll 200 and the orbiting scroll 300, thereby avoiding axial leakage. In the above process where the sealing strip 360 is gradually raised by the high-pressure medium from the bottom gap G2, when the additional gap reaches the through hole 350, the sealing strip 360 is not able to cover the through hole 350 due to being lifted and thus opens the through hole 350 so that a portion of the high-pressure medium can flow through the through hole 350 to the rear side of the orbiting scroll 300 and create a backpressure on the rear side of the orbiting scroll 300, which can push the orbiting scroll 300 towards the fixed scroll 200, thereby eliminating the axial gap between the fixed scroll 200 and the orbiting scroll 300. Accordingly, the scroll compressor 10 according to the present disclosure is able to automatically close and eliminate the axial gap after an axial gap is created between the fixed scroll 200 and the orbiting scroll 300, thereby automatically avoiding axial leakage. In addition, since the through hole 350 is disposed before the outer end wall 332 of the sealing groove 330, especially with the through hole 350 approaching the bottom gap G2, the above-mentioned backpressure may be established before the entire sealing strip 360 is lifted so that the axial gap may be eliminated before the entire sealing strip 360 is lifted and the high-pressure medium does not have to flow beneath the entire sealing strip 360. Thus, the scroll compressor 10 according 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 scroll 200 and the orbiting scroll 300, the sealing strip 360 may cover the through hole 350, thereby preventing the high-pressure medium from leaking through the through hole 350 to the rear side of the orbiting scroll 300, which also maintains a high volumetric efficiency and avoids the establishment of unexpected backpressure on the rear side of the orbiting scroll 300, which may lead to increased wear of the fixed scroll 200 and the orbiting scroll 300. 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 FIGS. 4 and 5A, the inner end 361 of the sealing strip 360 is suspended over the auxiliary groove 340 such that a portion of the auxiliary groove 340 is under the sealing strip 360, forming a bottom gap G2 in the auxiliary groove 340, while another portion of the auxiliary groove 340 passes through the end gap Gl to the top surface 323 of the orbiting scroll body 320. That is, the sealing strip 360 covers only a portion of the auxiliary groove 340 such that it forms a bottom gap G2 and leaves another portion of the auxiliary groove 340 uncovered such that the bottom gap G2 can be fluidly connected to the end gap Gl through the other portion. More particularly, as shown in FIGS. 4 and 5A, the auxiliary groove 340 is adjacent to the inner end wall 331 of the sealing groove 330. Thus, as long as the inner end 361 of the sealing strip 360 is spaced apart from the inner end wall 331 of the sealing groove 330, an end gap Gl can be formed between the inner end 361 and the inner end wall 331, and a bottom gap G2 can be formed below the inner end 361. In this configuration, merely machining the auxiliary groove 340 at the inner end wall 331 of the sealing groove 330 can form the bottom gap G2 without special machining of the sealing strip 360, thereby reducing the configuration cost of the orbiting scroll 300.

In particular, referring to FIGS. 6 and 7, FIG. 6 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 and FIG. 7 shows a schematic partial cross-sectional view of the orbiting scroll taken along line A-A in FIG. 6. As shown in FIGS. 6 and 7, the sealing strip 360 is thinned at the inner end 361, i.e., the sealing strip 360 has a thinned portion at the inner end 361, which is less than the thickness of the other portions of the sealing strip 360 such that the inner end 361 is spaced apart from the bottom wall 333 of the sealing groove 330, forming a bottom gap G2 between the inner end 361 and the bottom wall 333. Thus, the embodiment shown in FIGS. 6 and 7 differs from the embodiment shown in FIGS. 2-5B in that the bottom gap G2 is formed by the thinning of the sealing strip 360 rather than by the auxiliary groove 340. In this configuration, the bottom gap G2 can be formed by merely machining the thinned portion at the inner end 361 of the sealing strip 360 without special machining of the bottom wall 333 of the sealing groove 330, thereby reducing the configuration cost of the orbiting scroll 300. Of course, in the embodiment shown in FIGS. 6 and 7, the auxiliary groove 340 may also be present so as to form the bottom gap G2 with the thinned portion of the sealing strip 360.

In particular, referring to FIGS. 8 and 9, FIG. 8 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 and FIG. 9 shows a schematic partial cross-sectional view of an orbiting scroll with a sealing strip taken along line B-B in FIG. 8. The embodiment shown in FIG. 8 and FIG. 9 differs from the embodiment shown in FIGS. 1-7 in that the orbiting scroll 300 also has an auxiliary groove 370 recessed from the bottom wall 333 of the sealing groove 330. The auxiliary groove 370 extends from the bottom gap G2 (in particular, the auxiliary groove 340) along the sealing groove 330 towards the outer end wall 332 of the sealing groove 330. That is, the auxiliary groove 370 opens into the bottom gap G2 at one end and extends along an involute or in the form of an involute from this end towards the outer end wall 332 of the sealing groove 330 in the bottom wall 333 of the sealing groove 330. In this configuration, the high-pressure medium flowing through the end gap Gl into the bottom gap G2 may further flow into the auxiliary groove 370 and in turn be quickly directed below the sealing strip 360 by the auxiliary groove 370 so that the high-pressure medium can apply pressure to the sealing strip 360 in the auxiliary groove 370, which helps ensure successful lifting of the sealing strip 360. Therefore, compared with the configuration shown in FIGS. 1-7, the configuration shown in FIGS. 8 and 9 can more reliably ensure that the sealing strip 360 is lifted up when an axial gap is generated so as to close the axial gap through the auxiliary groove 370, especially when the sealing strip 360 is bonded to the sealing groove 330 by lubricating oil. The auxiliary groove 370 can also reduce the contact area between the sealing strip 360 and the bottom wall 333 so as to reduce the resistance encountered by the sealing strip 360 when it is lifted.

In particular, as shown in FIG. 8, the auxiliary groove 370 extends from the bottom gap G2 to the outer end wall 332 of the sealing groove 330. In this configuration, the high-pressure medium may be directed below the entire sealing strip 360 by the auxiliary groove 370 so as to more reliably ensure lift of the sealing strip 360. In particular, as shown in FIGS. 8 and 9, the sealing groove 330 also has two sidewalls 334 or is defined between the two sidewalls 334 that are opposite each other along the radial direction and coupled through the inner end wall 331 and the outer end wall 332, and the orbiting scroll 300 has two auxiliary grooves 370, wherein each secondary groove 370 is adjacent to one sidewall 334 so as to extend along the sidewall 334. In this configuration, the two auxiliary grooves 370 are arranged substantially symmetrically on both sides of the sealing strip 360 such that the high-pressure medium in the two auxiliary grooves 370 applies substantially the same pressure to the sealing strip 360, thereby merely raising the sealing strip 360 without causing the sealing strip 360 to twist. In particular, as shown in FIG. 8, the auxiliary groove 370 is spaced apart from the through hole 350 such that the through hole 350 only leads to the bottom wall 333 of the sealing groove 330 but not to the auxiliary groove 370. In this configuration, the sealing strip 360 may still block the flow of the high-pressure medium in the bottom gap G2 to the through hole 350 when the orbiting scroll body 320 is in contact with the fixed disk body 210, thereby maintaining higher volumetric efficiency for the scroll compressor 10.

In particular, referring to FIGS. 10 and 11, FIG. 10 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 and FIG. 11 shows a schematic partial cross-sectional view of an orbiting scroll with a sealing strip taken along line B-B in FIG. 10. The embodiment shown in FIGS. 10 and 11 differs from the embodiment shown in FIGS. 8 and 9 in that the through hole 350 intersects the auxiliary groove 370 such that the through hole 350 leads to both the sealing groove 330 and the auxiliary groove 370. In other words, the through hole 350 has openings on both the bottom wall 333 of the sealing groove 330 and the bottom wall 371 of the auxiliary groove 370. In this configuration, because the sealing strip 360 can only cover the opening of the through hole 350 on the bottom wall 333 of the sealing groove 330 but cannot cover the opening of the through hole 350 on the bottom wall 371 of the auxiliary groove 370, even if the sealing strip 360 is not lifted, the high-pressure medium entering the bottom gap Gl can enter the through hole 350 through the opening of the through hole 350 on the bottom wall 371 of the auxiliary groove 370, thereby establishing a certain degree of backpressure on the rear side of the orbiting scroll 300. Therefore, the above configuration helps to maintain a certain degree of backpressure on the rear side of the orbiting scroll 300 to prevent the generation of axial gaps. Of course, because the through hole 350 is only partially connected to the auxiliary groove 370, the backpressure established in the above manner is limited and will not cause a substantial increase in the wear of the fixed scroll 200 and the orbiting scroll 300 or a significant decrease in volumetric efficiency. In particular, with the orbiting scroll 300 having two or more auxiliary grooves 370, the through hole 350 may intersect any one or more of the auxiliary grooves 370.

In particular, returning to FIG. 1, a backpressure chamber 710 is formed on the rear side of the orbiting disk body 310, which is fluidly connected to the through hole 350, i.e., the through hole 350 opens to the backpressure chamber 710 at the bottom surface 311 of the orbiting disk body 310. More particularly, an end of the swivel shaft 520 is spaced apart from the bottom surface 311 of the orbiting disk body 310 such that the backpressure chamber 710 is jointly defined in the bearing seat 380 by an inside surface of the bearing 610, a bottom surface 311 of the orbiting disk body 310, and an end of the swivel shaft 520. In this configuration, the low volume of the backpressure chamber 710 is such that a small amount of high-pressure medium is sufficient to establish sufficient backpressure in the backpressure chamber 710, 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 10. The backpressure chamber 710 is generally closed, thereby preventing leakage of the high-pressure medium from the backpressure chamber 710 and helping to maintain backpressure in the backpressure chamber 710.

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.