Scroll compressor

Abstract

The present disclosure proposes a scroll compressor, comprising: a housing (100); the two scrolls (200 and 300) are contained in the shell (100), the scroll bodies of the two scrolls (200 and 300) extend along involutes respectively and are meshed with each other, and the scroll body of at least one scroll is provided with a sealing groove (340) recessed from the top face of the scroll body. The sealing groove (340) extends from an inner end wall (341) close to the circle center of the involute base circle to an outer end wall (342) far away from the circle center of the involute base circle along the involute, and is provided with a sealing strip (350) and a pre-tightening spring (360); the pre-tightening spring (360) is wave-shaped and has a plurality of wave crest portions (363) abutting against the bottom (351) of the sealing strip (350) and a plurality of wave trough portions (364) abutting against the bottom wall (344) of the sealing groove (340), and the spring stiffness of the pre-tightening spring (360) decreases in the direction from the inner end wall (341) to the outer end wall (342).

Description

TECHNICAL FIELD

[0001] The present disclosure relates to the technical field of compressors, and more particularly, to a scroll compressor. BACKGROUND

[0002] The improvements of the existing scroll compressor mainly focus on increasing the suction volume and improving the volumetric efficiency. The existing scroll compressor often adopts the cooperation of the scroll bodies of two scrolls to compress the medium, and the scroll bodies of the two scrolls define a plurality of working chambers distributed from the periphery to the center and spaced apart from each other, the pressure in the working chambers increases as it approaches the center of the scroll body, and therefore there is a problem that the medium in the high-pressure working chamber leaks through the axial gap between the two scrolls to the low-pressure working chamber in the radial periphery, which can be referred to as radial leakage, and the radial leakage obviously has an adverse effect on the volumetric efficiency of the scroll compressor. The existing solutions often suppress the radial leakage by increasing the holding force that holds the two scrolls together and increasing the pre-tightening force applied to the sealing strip between the two scrolls, however, this way not only increases the wear and noise of the scrolls during operation, but also increases the wear of the sealing strip, thereby not only shortening the service life of the sealing strip and the scrolls, but also adversely affecting the use environment. However, if the holding force that holds the two scrolls together and the pre-tightening force applied to the sealing strip are reduced, the risk of radial leakage may increase, thereby adversely affecting the volumetric efficiency of the scroll compressor.

[0003] Therefore, there is an urgent need in the art for a technical solution that can avoid radial leakage while taking into account the wear of the scrolls and the sealing strip and the noise during operation. SUMMARY

[0004] In order to solve the above-mentioned problems in the prior art, the present disclosure proposes an improved scroll compressor, which comprises: a housing; and two scrolls accommodated in the housing, wherein each scroll comprises a disc body and a scroll body protruding from the disc body, and the scroll bodies of the two scrolls respectively extend along an involute and mesh with each other, wherein the scroll body of at least one scroll is provided with a sealing groove recessed from the top surface thereof, the sealing groove extends along the involute from an inner end wall close to the center of the base circle of the involute to an outer end wall away from the center of the base circle of the involute, and wherein the sealing groove is provided with a sealing strip and a pre-tightening spring, the pre-tightening spring has an inner end portion close to the inner end wall and an outer end portion close to the outer end wall, and is in a wave shape to have a plurality of wave peak portions abutting against the bottom of the sealing strip and a plurality of wave valley portions abutting against the bottom wall of the sealing groove, and the spring stiffness of the pre-tightening spring decreases in the direction from the inner end portion to the outer end portion.

[0005] According to an optional embodiment of the present disclosure, a top portion of the sealing strip is located outside the sealing groove when the pre-tightening spring is in a natural state.

[0006] According to an optional embodiment of the present disclosure, a top portion of the sealing strip is parallel to a top surface of the scroll when the pre-tightening spring is in a natural state.

[0007] According to an optional embodiment of the present disclosure, a bottom portion of the sealing strip is located inside the sealing groove when the pre-tightening spring is in a natural state.

[0008] According to an optional embodiment of the present disclosure, the sealing groove is defined between two side walls opposite to each other, and the sealing strip abuts against the two side walls of the sealing groove on both sides.

[0009] According to an optional embodiment of the present disclosure, the sealing groove is defined between two side walls opposite to each other, and the pre-tightening spring abuts against the two side walls of the sealing groove on both sides.

[0010] According to an optional embodiment of the present disclosure, the sealing groove is defined between two side walls opposite to each other, and a gap is formed between at least one side of the sealing strip and the corresponding side wall.

[0011] According to an optional embodiment of the present disclosure, a plurality of chambers are formed between a bottom portion of the sealing strip and a plurality of wave trough portions of the pre-tightening spring, wherein each chamber is in communication with the gap.

[0012] According to an optional embodiment of the present disclosure, a frequency of the wave shape decreases along a direction from the inner end portion to the outer end portion of the pre-tightening spring.

[0013] According to an optional embodiment of the present disclosure, an amplitude of the wave shape remains unchanged, and a bottom wall of the sealing groove and a bottom portion of the sealing strip are parallel to a top surface of the scroll, so that a top portion of the sealing strip is parallel to the top surface of the scroll.

[0014] According to an optional embodiment of the present disclosure, the amplitude of the wave shape increases along a direction from the inner end portion to the outer end portion of the pre-tightening spring.

[0015] According to an optional embodiment of the present disclosure, a bottom wall of the sealing groove and / or a bottom portion of the sealing strip is inclined relative to a top surface of the scroll, so that a top portion of the sealing strip is parallel to the top surface of the scroll.

[0016] According to an optional embodiment of the present disclosure, a material thickness of the pre-tightening spring decreases along a direction from the inner end portion to the outer end portion.

[0017] According to an optional embodiment of the present disclosure, the pre-tightening spring is positioned such that the longitudinal axis of the wave shape is perpendicular to the top surface of the scroll.

[0018] According to an optional embodiment of the present disclosure, the two scrolls consist of a static scroll fixed within the housing and a dynamic scroll movably disposed within the housing.

[0019] According to an optional embodiment of the present disclosure, both of the two scrolls are movably disposed within the housing and are configured to rotate about two axes parallel and offset relative to each other, respectively.

[0020] The present disclosure can be embodied in the illustrative embodiments of the drawings. However, it should be noted that the drawings are merely illustrative, and any variations envisaged under the teachings of the present disclosure should be considered to be included within the scope of the present disclosure. BRIEF DESCRIPTION OF DRAWINGS

[0021] The accompanying drawings illustrate exemplary embodiments of the present disclosure. These drawings should not be construed as necessarily limiting the scope of the present disclosure, wherein:

[0022] Figure 1 is a schematic cross-sectional view of a scroll compressor according to an embodiment of the present disclosure;

[0023] Figure 2 is a schematic cross-sectional view of a static scroll and a dynamic scroll taken along line II-II in Figure 1

[0024] Figure 3 is a schematic perspective view of a dynamic scroll of the scroll compressor shown in Figure 1

[0025] Figure 4 is a schematic perspective cross-sectional view of the dynamic scroll taken along line IV-IV in Figure 3

[0026] Figure 5 is a schematic perspective view of a seal bar in the dynamic scroll shown in Figure 3 and Figure 4

[0027] Figure 6 is a schematic perspective view of a pre-tightening spring in the dynamic scroll shown in Figure 3 and Figure 4

[0028] Figure 7 is a partial schematic cross-sectional view of a dynamic scroll of the dynamic scroll taken along an involute shown in Figure 3 and Figure 4 ​​​​​​

[0029] Figure 8 is a partial schematic cross-sectional view of an orbiting scroll of an orbiting scroll of a scroll compressor according to another embodiment of the present disclosure, taken along an involute;

[0030] Figure 9 is a schematic perspective view of an orbiting scroll of a scroll compressor according to yet another embodiment of the present disclosure; and

[0031] Figure 10 is a schematic perspective cross-sectional view of the orbiting scroll taken along Figure 9 line X-X in DETAILED DESCRIPTION

[0032] Further features and advantages of the present disclosure will become more apparent from the following description with reference to the accompanying drawings. In the drawings, exemplary embodiments of the present disclosure are illustrated and the individual drawings are not necessarily drawn to scale. However, the present disclosure can be embodied in many different forms and should not be construed as necessarily being limited to the exemplary embodiments of the disclosure set forth herein. Rather, these exemplary embodiments are merely provided for illustrative purposes to explain the present disclosure and to convey the spirit and essence of the present disclosure to those skilled in the art.

[0033] The present disclosure aims to propose an improved scroll compressor having a novel sealing design by which different pre-tightening forces can be applied to a sealing strip for providing axial sealing between two scrolls of the scroll compressor along the length of the sealing strip, more specifically, a greater pre-tightening force can be applied to the sealing strip near a high-pressure working chamber close to the center of the scroll and a smaller pre-tightening force can be applied to the sealing strip near a low-pressure working chamber close to the periphery of the scroll, so that the sealing strip can reliably seal both the high-pressure working chamber and the low-pressure working chamber. That is, the technical solution according to the present disclosure can apply different pre-tightening forces to the sealing strip according to the difference in the pressure of the working chamber to be sealed. Therefore, compared with the technical solution of applying a greater pre-tightening force along the entire length of the sealing strip, the technical solution according to the present disclosure can reduce the wear of the sealing strip and the scroll, and compared with the technical solution of applying a smaller pre-tightening force along the entire length of the sealing strip, the technical solution according to the present disclosure can reliably seal working chambers of different pressures.

[0034] The various alternative but non-limiting embodiments of the scroll compressor according to the present disclosure are described in detail below with reference to the various drawings. However, it is to be noted that in the terminology used in the present disclosure, the terms "axial direction", "radial direction", "circumferential direction" and the like have their usual meaning in the art. In particular, the axial direction can be a direction parallel 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; while the circumferential direction can be any direction encircling the axial direction. In addition, it is also to be noted that, although the sealing design according to the present disclosure will be described below by way of example with a scroll compressor having a revolving configuration, it will be appreciated by the skilled person that the sealing design according to the present disclosure is obviously also applicable to scroll compressors having a co-rotating configuration, that is, wherein the two scroll wraps rotate around axes parallel and offset with respect to each other, so that the specific configuration of the scroll compressor cannot constitute a limitation to the scope of protection of the present disclosure.

[0035] Reference is made to Figure 1 wherein a schematic cross-sectional view of a scroll compressor according to an embodiment of the present disclosure is shown. As Figure 1 shown, the scroll compressor 10 generally comprises a housing 100 and two scroll wraps 200, 300, a motor 400 and a transmission assembly 500 housed in the housing 100.

[0036] The two scroll wraps 200, 300 are constituted by a stationary scroll wrap 200 fixedly arranged in the housing 100 and a movable scroll wrap 300 movably arranged in the housing 100. The stationary scroll wrap 200 comprises a stationary disc body 210 and stationary scroll wraps 220 protruding from the stationary disc body 210 along the axial direction YY'. The stationary scroll wraps 220 extend from the center of the stationary disc body 210 towards the periphery of the stationary disc body 210 along an involute or in the form of an involute. The movable scroll wrap 300 comprises a movable disc body 310 and movable scroll wraps 320 protruding from the movable disc body 310 along the axial direction YY'. The movable scroll wraps 320 extend from the center of the movable disc body 310 towards the periphery of the movable disc body 310 along an involute or in the form of an involute. The stationary scroll wraps 220 of the stationary scroll wrap 200 and the movable scroll wraps 320 of the movable scroll wrap 300 are arranged facing each other so that the stationary scroll wraps 220 are oriented to protrude from the stationary disc body 210 towards the movable disc body 310, while the movable scroll wraps 320 are oriented to protrude from the movable disc body 310 towards the stationary disc body 210. In addition, the stationary scroll wraps 220 abut against the movable disc body 310, the movable scroll wraps 320 abut against the stationary disc body 210 and the stationary scroll wraps 220 and the movable scroll wraps 320 are meshed with each other, thereby defining a plurality of working chambers between the stationary scroll wraps 220 and the movable scroll wraps 320 distributed along the involute. In particular, reference is made to Figure 2 wherein a schematic cross-sectional view of a scroll compressor according to an embodiment of the present disclosure is shown. As Figure 1Fig. 2 shows a schematic cross-sectional view of the static and dynamic volutes taken along the line II-II in Fig. 1, the static volute 220 and the dynamic volute 320 being engaged with each other so as to define a plurality of working chambers a, b, c between them, the working chambers a, b, c being distributed generally along the direction of the involute and including outer working chambers a, intermediate working chambers b and central working chambers c, as the dynamic volute 300 orbits (also referred to as translation), new working chambers a will be formed, while previously formed working chambers a will move towards the centre of the two volutes and form new working chambers b, thereby reducing their volume, previously formed working chambers b will move to the centre of the two volutes and form new working chambers c, thereby also reducing their volume, while previously formed working chambers c will reduce in volume until they disappear. In short, as the dynamic volute 300 orbits, each working chamber will move towards the centre of the two volutes and its volume will gradually reduce as it moves, whereby compression of the medium contained in each working chamber can be achieved.

[0037] Returning to Figure 1The motor 400 is configured to drive the orbiting scroll 300 to orbit about the axial direction YY' and includes a stator 410 fixedly disposed in the housing 100, a rotor 420 rotatably disposed in the housing 100, and a main shaft 430 non-rotatably connected to the rotor 420 (e.g., by welding, bolting, keying, etc.) so as to support the rotor 420 in the housing 100, wherein the main shaft 430 can orbit about the axial direction YY' along with the rotor 420 when the rotor 420 orbits about the axial direction YY' under the driving of a rotating magnetic field generated by the stator 410 upon energization. The transmission assembly 500 includes an eccentric block 510 and an eccentric shaft 520 connecting the eccentric block 510 to the main shaft 430, wherein the eccentric block 510 is connected to the orbiting scroll 300, e.g., by a bearing 610, and the orbiting scroll 300 can be provided with a bearing seat 330 on a side of the orbiting scroll body 310 opposite the orbiting scroll wrap 320, the bearing 610 can be mounted in the bearing seat 330, and the eccentric block 510 can be inserted into the bearing 610. In addition, the eccentric shaft 520 can be inserted into the main shaft 430 in a manner fixed relative to the main shaft 430 and eccentric, and inserted into the eccentric block 510 in a manner rotatable relative to the eccentric block 510 and eccentric, so that the eccentric block 510 is rotatably connected to the main shaft 430 at a position eccentric relative to the main shaft 430. In this configuration, the rotation of the main shaft 430 about the axial direction YY' can be converted into the orbit of the eccentric block 510 about the axial direction YY', and the orbit of the eccentric block 510 about the axial direction YY' can be converted into the orbit of the orbiting scroll 300 about the axial direction YY'. Of course, in order to suppress the tendency of the orbiting scroll 300 to rotate (also referred to as the tendency to spin), the scroll compressor 10 can further include an anti-rotation structure acting on the orbiting scroll 300, so as to ensure that the orbiting scroll 300 orbits or translates about the axial direction YY' without spinning.

[0038] In the above configuration, the motor 400 can drive the main shaft 430 to rotate after being energized, and the main shaft 430 can in turn drive the orbiting scroll 300 to orbit through the eccentric shaft 520, the eccentric block 510 and the bearing 610. As the orbiting scroll 300 orbits, each working chamber defined between the fixed scroll 220 and the orbiting scroll 320 will move from the periphery of the two scrolls towards the center of the two scrolls, as described above, and the working chamber that moves to the center will disappear while a new working chamber is generated at the periphery of the two scrolls, and the volume of each working chamber will gradually decrease as it moves. Therefore, during the operation of the scroll compressor 10, the medium (e.g., a refrigerant such as R22, R744 or HFC) can enter the working chamber from the periphery of the fixed scroll 220 and the orbiting scroll 320, then be transported and compressed by the working chamber towards the center of the two scrolls, and finally be discharged at the center of the two scrolls (e.g., through the discharge hole 211 provided in the fixed scroll 210). As the orbiting scroll 300 continuously orbits, the medium can be continuously received, transported, compressed and discharged in the above manner.

[0039] As can be seen from the foregoing, the pressure in each working chamber is different, specifically, the pressure in the working chamber closer to the center of the fixed scroll 220 and the orbiting scroll 320 is higher, while the pressure in the working chamber closer to the periphery of the two scrolls is lower, and the pressure in each working chamber tends to push the fixed scroll 200 and the orbiting scroll 300 away from each other, thereby generating an axial gap between the fixed scroll 220 and the orbiting scroll 310 and between the orbiting scroll 320 and the fixed scroll 210, and the medium in the high-pressure working chamber can leak through these axial gaps into the low-pressure working chamber at the radial periphery, which can be referred to as radial leakage, and will adversely affect the volumetric efficiency of the scroll compressor 10. To avoid such radial leakage, the present disclosure proposes an improved sealing design. It should be noted that although the sealing design provided at the top of the orbiting scroll 320 will be described below, those skilled in the art can understand that the sealing design can alternatively or additionally be provided at the top of the fixed scroll 220, and therefore the specific object of the sealing design cannot constitute a limitation on the protection scope of the present disclosure.

[0040] Referring to Figure 3 and Figure 4 wherein, Figure 3 shows Figure 1 a schematic perspective view of an orbiting scroll of a scroll compressor, Figure 4 shows a schematic perspective cross-sectional view of the orbiting scroll taken along line IV-IV in Figure 3 As can be seen from the foregoing, Figure 1 , Figure 3 and Figure 4As shown, the orbiting scroll 320 has an inner end portion 321 proximate to the center of the orbiting disk body 310 and an outer end portion 322 proximate to the periphery of the orbiting disk body 310, and extends along or in the form of an involute from the inner end portion 321 to the outer end portion 322, wherein the inner end portion 321 is proximate to the center of the base circle of the involute, and the outer end portion 322 is distal from the center of the base circle of the involute. In addition, the orbiting scroll 320 protrudes from the orbiting disk body 310 along the axial direction YY’ such that the orbiting scroll 320 has a top surface 323 spaced apart from the orbiting disk body 310 along the axial direction YY’, which is intended to be in contact with the fixed scroll body 210, and the orbiting scroll 320 is further provided with a sealing groove 340 recessed from the top surface 323 along the axial direction YY’. As shown in Figure 4 and the partial enlarged view thereof, the sealing groove 340 has an inner end wall 341 proximate to the inner end portion 321 of the orbiting scroll 320 (i.e., proximate to the center of the base circle of the involute), an outer end wall 342 proximate to the outer end portion 322 of the orbiting scroll 320 (i.e., distal from the center of the base circle of the involute), and two side walls 343 extending from the inner end wall 341 to the outer end wall 342 along or in the form of an involute and opposite to each other, that is, the sealing groove 340 terminates at the inner end wall 341 proximate to the center of the base circle of the involute, terminates at the outer end wall 342 distal from the center of the base circle of the involute, and is defined between the two side walls 343. In addition, the sealing groove 340 has a bottom wall 344 spaced apart from the top surface 323 of the orbiting scroll 320 along the axial direction YY’, that is, the sealing groove 340 terminates at the bottom wall 344 spaced apart from the top surface 323 of the orbiting scroll 320 along the axial direction YY’. In particular, as shown in Figure 3 and Figure 4 The sealing groove 340 does not extend along the entire length of the orbiting scroll 320 between the inner end portion 321 and the outer end portion 322, such that the inner end wall 341 and the outer end wall 342 of the sealing groove 340 are spaced apart from the inner end portion 321 and the outer end portion 322 of the orbiting scroll 320, respectively.

[0041] With continued reference to Figure 3 and Figure 4The mobile scroll 320 further comprises a seal bar 350 (e.g. made of a self-lubricating non-metallic material) housed in a seal groove 340 and a pre-tension spring 360 (e.g. made of a metallic material) disposed between (in particular, clamped between) a bottom wall 344 of the seal groove 340 and a bottom portion 351 of the seal bar 350. In other words, the bottom portion 351 of the seal bar 350 is spaced apart from the bottom wall 344 of the seal groove 340 so as to define a chamber therebetween for housing the pre-tension spring 360. In this configuration, the pre-tension spring 360 can exert a pre-tension force to the seal bar 350 biasing it in a direction away from the bottom wall 344 of the seal groove 340, that is, the pre-tension spring 360 tends to push the seal bar 350 out of the seal groove 340. With reference to Figure 5 and Figure 6 wherein, Figure 5 is shown Figure 3 and Figure 4 is shown Figure 6 is shown Figure 3 and Figure 4The sealing strip 350 also has a top portion 352 opposite the bottom portion 351 thereof and extends along or in the form of an involute from an inner end portion 353 proximate to the inner end wall 341 of the sealing groove 340 (i.e., proximate to the center of the base circle of the involute) to an outer end portion 354 proximate to the outer end wall 342 of the sealing groove 340 (i.e., distal to the center of the base circle of the involute) so that the sealing strip 350 can be disposed in the sealing groove 340. The pre-tightening spring 360 likewise extends along or in the form of an involute from an inner end portion 361 proximate to the inner end wall 341 of the sealing groove 340 (i.e., proximate to the center of the base circle of the involute) to an outer end portion 362 proximate to the outer end wall 342 of the sealing groove 340 (i.e., distal to the center of the base circle of the involute) so that the pre-tightening spring 360 can also be disposed in the sealing groove 340, and in particular, the pre-tightening spring 360 is wavy (e.g., in the form of a sine wave or a cosine wave) along the involute (in other words, along its defined height in the axial direction YY’ or in the depth direction of the sealing groove 340) so that the pre-tightening spring 360 has a plurality of crest portions 363 intended to be in contact with the bottom portion 351 of the sealing strip 350 and a plurality of trough portions 364 intended to be in contact with the bottom wall 344 of the sealing groove 340. The above wavy configuration enables the pre-tightening spring 360 to be elastically deformed in the axial direction YY’ or in the depth direction of the sealing groove 340 and to generate an elastic restoring force, whereby the pre-tightening spring 360 can exert a pre-tightening force (also referred to as an elastic force) on the sealing strip 350 through the respective crest portions 363 to bias the sealing strip 350 away from the bottom wall 344 of the sealing groove 340. In this configuration, after the stationary scroll 200 and the orbiting scroll 300 are assembled together, the stationary disc body 210 can compress the pre-tightening spring 360 through the sealing strip 350 to cause it to be elastically deformed, and the pre-tightening spring 360 can push the sealing strip 350 toward the stationary disc body 210 to cause it to abut against the stationary disc body 210, thereby sealing the axial gap between the stationary disc body 210 and the orbiting scroll 320, whereby radial leakage of the medium can be prevented, and thus the volumetric efficiency of the scroll compressor 10 can be maintained. In particular, the pre-tightening spring 360 is arranged such that its spring stiffness decreases in the direction from the inner end portion 361 to the outer end portion 362, that is, the spring stiffness of the pre-tightening spring 360 is not constant along the involute or its length, but is maximum at or near the inner end portion 361 thereof and is minimum at or near the outer end portion 362 thereof, while decreasing in the direction from the inner end portion 361 to the outer end portion 362.

[0042] In the above configuration, since the static disc body 210 presses the entire sealing strip 350 along the axial direction YY' during assembly, the compression amount of each portion of the pre-tightening spring 360 in the axial direction YY' is the same, and since the spring stiffness of the pre-tightening spring 360 decreases from the inner end portion 361 to the outer end portion 362, the pre-tightening force exerted by the pre-tightening spring 360 on the sealing strip 350 will be the largest at the inner end portion 361 and the smallest at the outer end portion 362, and decreases in the direction from the inner end portion 361 to the outer end portion 362, in other words, the sealing strip 360 will be pushed against the static disc body 210 around the high-pressure working chamber close to the centers of the two vortex bodies by a larger pre-tightening force, and the larger pre-tightening force enables the sealing strip 350 to reliably seal the high-pressure working chamber, and the sealing strip 360 will be pushed against the static disc body 210 around the low-pressure working chamber close to the peripheries of the two vortex bodies by a smaller pre-tightening force, but the smaller pre-tightening force is also sufficient to enable the sealing strip 350 to reliably seal the low-pressure working chamber. Therefore, the above configuration enables different pre-tightening forces to be exerted on different portions of the sealing strip 350 according to the pressure of each working chamber, without having to exert a larger pre-tightening force on the entire sealing strip 350 just to seal the high-pressure working chamber, or exert a smaller pre-tightening force on the entire sealing strip 350 just to alleviate wear, so that the sealing design according to the present disclosure not only enables reliable sealing of each working chamber, thereby maintaining a higher volumetric efficiency of the scroll compressor, but also alleviates the aggravation of wear of the sealing strip and the vortex disc caused by a larger pre-tightening force, thereby maintaining a longer service life of the sealing strip and the vortex disc.

[0043] As shown in Figure 5 , the sealing strip 350 has two side portions 355 opposite to each other and intended to face the two side walls 343 of the sealing groove 340. In particular, as shown in Figure 4 and the partial enlarged view therein, the two side portions 355 of the sealing strip 350 are respectively in contact with the two side walls 343 of the sealing groove 340, in short, the sealing strip 350 abuts against the two side walls 343 of the sealing groove 340 on both sides. In addition, the pre-tightening spring 360 can also abut against the two side walls 343 of the sealing groove 340 on both sides. In this configuration, the sealing groove 340 can reliably limit the moving direction of the sealing strip 350 and the pre-tightening force exerted by the pre-tightening spring 360 in the axial direction YY', thereby avoiding the sealing strip 350 from turning over during the revolution of the moving vortex disc 300, so that the reliability of the sealing can be further improved.

[0044] Referring to Figure 7 , wherein it is shown that Figure 3 and Figure 4A partial schematic cross-sectional view of a moving scroll of the orbiting scroll of the illustrated orbiting scroll taken along an involute, for the sake of clarity the schematic cross-sectional view is drawn with the involute being unrolled into a straight line, and the inner end 321 and the outer end 322 of the moving scroll 320 are located on the left and right sides of the figure, respectively. As Figure 7 As illustrated, the above-mentioned variation of the stiffness of the pre-tightening spring 360 is achieved by varying the frequency of its wave shape. More specifically, the frequency of the wave shape of the pre-tightening spring 360 decreases along a direction from the inner end 361 to the outer end 362, in other words, the period of the wave shape of the pre-tightening spring 360 increases along a direction from the inner end 361 to the outer end 362, which period can be embodied as the distance between adjacent crest portions 363 or adjacent trough portions 364. In this configuration, the slope of the wave shape of the pre-tightening spring 360 will decrease along a direction from the inner end 361 to the outer end 362, thereby resulting in that the spring stiffness of the pre-tightening spring 360 will also decrease along a direction from the inner end 361 to the outer end 362, so that different pre-tightening forces can be exerted on different portions of the sealing strip 350.

[0045] Reference is made to Figure 8 wherein a partial schematic cross-sectional view of a moving scroll of an orbiting scroll of a scroll compressor according to another embodiment of the present disclosure is shown taken along an involute. Figure 8 The illustrated embodiment differs from the one shown in Figure 7 The illustrated embodiment differs from the one shown in

[0046] Although the above has been described by way of example with the aid of Figure 7 and Figure 8Two different methods for adjusting the spring stiffness of the preload spring 360 are described, but these two methods can be combined. For example, the frequency of the wave pattern of the preload spring 360 decreases along the direction from the inner end 361 to the outer end 362, while its amplitude increases along the same direction, thereby allowing for adjustment of the spring stiffness of the preload spring 360 over a wider range. Furthermore, the spring stiffness of the preload spring 360 can also be adjusted in other ways than those described above. For example, the material thickness of the preload spring 360 can decrease along the direction from the inner end 361 to the outer end 362, thereby also causing the spring stiffness of the preload spring 360 to decrease along the same direction. Therefore, specific methods for adjusting the spring stiffness of the preload spring 360 do not constitute a limitation on the scope of this disclosure. The above-described and various other methods for adjusting the spring stiffness of the preload spring 360, whether used individually or in any combination, fall within the scope of this disclosure.

[0047] In particular, such as Figure 7 and Figure 8 As shown, the sealing strip 350 and the preload spring 360 are configured such that the top 352 of the sealing strip 350 is outside the sealing groove 340 when the preload spring 360 is in its natural state. That is, when the preload spring 360 is not compressed or elastically deformed, the sum of the height of the sealing strip 350 and the height of the preload spring 360 is greater than the depth of the sealing groove 340, so that the top 352 of the sealing strip 350 protrudes from or above the top surface 323 of the moving scroll 320. In this configuration, when the stationary scroll 200 and the moving scroll 300 are assembled together, the stationary scroll 210 can push the entire sealing strip 350, allowing the entire sealing strip 350 to be preloaded by the preload spring 360, thereby providing a more reliable seal for each working chamber. More specifically, the sealing strip 350 and the preload spring 360 are configured such that the bottom 351 of the sealing strip 350 is within the sealing groove 340 when the preload spring 360 is in its natural state. That is, when the preload spring 360 is not compressed or has not undergone elastic deformation, the height of the preload spring 360 is less than the depth of the sealing groove 340, so that the bottom 351 of the sealing strip 350 is within the sealing groove 340 or below the top surface 323 of the moving scroll 320. With this configuration, the sealing groove 340 can reliably hold the sealing strip 350, thereby preventing the sealing strip 350 from flipping during the revolution of the moving scroll 200.

[0048] In particular, such as Figure 7 and Figure 8As shown, the sealing strip 350 and the pre-tightening spring 360 are configured such that the top portion 352 of the sealing strip 350 is parallel to the top surface 323 of the orbiting scroll 320 when the pre-tightening spring 360 is in the natural state, that is, the plane in which the top portion 352 of the sealing strip 350 lies is parallel to the plane in which the top surface 323 of the orbiting scroll 320 lies. In this configuration, when the fixed scroll 200 is assembled with the orbiting scroll 300, the surface of the fixed scroll body 210 will also be parallel to the top portion 352 of the sealing strip 350, which makes each portion of the sealing strip 350 generate the same displacement when the fixed scroll body 210 presses the sealing strip 350 downward, thereby ensuring that the compression amount of each portion of the pre-tightening spring 360 in the axial direction YY’ is the same, so that the pre-tightening force exerted on each portion of the sealing strip 350 by adjusting the spring stiffness of each portion of the pre-tightening spring 360 can be changed. For example, as shown in Figure 7 As shown, since the amplitude of the wave shape of the pre-tightening spring 360 remains unchanged, the bottom wall 344 of the sealing groove 340 and the bottom portion 351 of the sealing strip 350 can be parallel to the top surface 323 of the orbiting scroll 320 so that the top portion 352 of the sealing strip 350 is parallel to the top surface 323 of the orbiting scroll 320. For another example, as shown in Figure 8 As shown, in order to adapt to the change in the amplitude of the wave shape of the pre-tightening spring 360, the bottom wall 344 of the sealing groove 340 and / or the bottom portion 351 of the sealing strip 350 can be inclined with respect to the top surface 323 of the orbiting scroll 320 so that the top portion 352 of the sealing strip 350 can be parallel to the top surface 323 of the orbiting scroll 320 after the sealing strip 350 and the pre-tightening spring 360 are placed in the sealing groove 340.

[0049] In particular, as shown in Figure 7 and Figure 8 As shown, the pre-tightening spring 360 is positioned such that the longitudinal axis of the wave shape (i.e., the height direction of the wave shape) is perpendicular to the top surface 323 of the orbiting scroll 320. In this configuration, it can be ensured that the pre-tightening force exerted by the pre-tightening spring 360 on the sealing strip 350 is along the axial direction YY’, that is, it can be ensured that the pre-tightening spring 360 biases the sealing strip 350 in the direction toward the fixed scroll body 210, without biasing the sealing strip 350 in the inclined direction, thereby avoiding the sealing strip 350 from being flipped during the revolution of the orbiting scroll 300, so that the reliability of the seal can be further improved.

[0050] Reference is made to Figure 9 and Figure 10 wherein, Figure 9 a schematic perspective view of an orbiting scroll of a scroll compressor according to yet another embodiment of the present disclosure is shown, and Figure 10 a schematic perspective cross-sectional view of the orbiting scroll taken along the line X-X in Figure 9 is shown. Figure 9 andFigure 10 The illustrated embodiment differs from Figure 3 and Figure 4 The illustrated embodiment differs from the embodiment shown in FIG. 1 in that the two side portions 355 of the sealing strip 350 are not in contact with the two side walls 343 of the sealing groove 340, respectively, but at least one side portion 355 is spaced apart from the respective side wall 343 it faces, in short, the sealing strip 350 is spaced apart from the respective side wall 343 of the sealing groove 340 at least on one side, thereby defining a gap G between this side of the sealing strip 350 and the side wall 343 of the sealing groove 340. In this configuration, as Figure 7 and Figure 8 The illustrated embodiment differs from the embodiment shown in FIG. 1 in that the two side portions 355 of the sealing strip 350 are not in contact with the two side walls 343 of the sealing groove 340, respectively, but at least one side portion 355 is spaced apart from the respective side wall 343 it faces, in short, the sealing strip 350 is spaced apart from the respective side wall 343 of the sealing groove 340 at least on one side, thereby defining a gap G between this side of the sealing strip 350 and the side wall 343 of the sealing groove 340. In this configuration, as

[0051] The above detailed description of alternative but non-limiting embodiments of a scroll compressor according to the present disclosure has been given with the aid of the accompanying drawings. Modifications and additions to the techniques and structures, as well as re-combinations of features in the various embodiments, will be apparent to those of ordinary skill in the art without departing from the spirit and scope of the present disclosure. Such modifications and additions, as well as re-combinations of features in the various embodiments, are therefore to be considered within the scope of the present disclosure. The scope of the present disclosure includes equivalent technologies known at the time of the present disclosure and equivalent technologies not yet foreseen.

Claims

1. A scroll compressor characterized by comprising: Comprising: a housing (100); and two scroll plates (200, 300) accommodated in the housing (100), wherein each scroll plate comprises a plate body and scroll bodies protruding from the plate body, and the scroll bodies of the two scroll plates (200, 300) respectively extend along an involute and mesh with each other, wherein the scroll bodies of at least one scroll plate are provided with a sealing groove (340) recessed from a top surface thereof, the sealing groove (340) extends along the involute from an inner end wall (341) close to a center of a base circle of the involute to an outer end wall (342) away from the center of the base circle of the involute, and wherein the sealing groove (340) is provided with a sealing strip (350) and a pre-tightening spring (360), the pre-tightening spring (360) has an inner end portion (361) close to the inner end wall (341) and an outer end portion (362) close to the outer end wall (342), and is wavy-shaped to have a plurality of peak portions (363) abutting against a bottom (351) of the sealing strip (350) and a plurality of valley portions (364) abutting against a bottom wall (344) of the sealing groove (340), and a spring stiffness of the pre-tightening spring (360) decreases along a direction from the inner end portion (361) to the outer end portion (362). A top (352) of the sealing strip (350) is located outside the sealing groove (340) when the pre-tightening spring (360) is in a natural state.

2. The scroll compressor of claim 1, wherein The top (352) of the sealing strip (350) is parallel to a top surface of the scroll bodies when the pre-tightening spring (360) is in the natural state.

3. The scroll compressor of claim 2, wherein A bottom (351) of the sealing strip (350) is located inside the sealing groove (340) when the pre-tightening spring (360) is in the natural state.

4. The scroll compressor of claim 2, wherein The sealing groove (340) is defined between two side walls (343) opposite to each other, and the sealing strip (350) abuts against the two side walls (343) of the sealing groove (340) on both sides.

5. The scroll compressor according to any one of claims 1 to 4, characterized in that, The sealing groove (340) is defined between two side walls (343) opposite to each other, and the pre-tightening spring (360) abuts against the two side walls (343) of the sealing groove (340) on both sides.

6. The scroll compressor according to any one of claims 1 to 4, characterized in that, The sealing groove (340) is defined between two side walls (343) opposite to each other, and a gap (G) is formed between at least one side of the sealing strip (350) and the corresponding side wall (343).

7. The scroll compressor according to any one of claims 1 to 4, characterized in that, A plurality of cavities (C) are formed between the bottom (351) of the sealing strip (350) and the plurality of valley portions (364) of the pre-tightening spring (360), wherein each cavity (C) communicates with the gap (G).

8. The scroll compressor of claim 7, wherein A frequency of the wavy shape decreases along a direction from the inner end portion (361) to the outer end portion (362) of the pre-tightening spring (360).

9. The scroll compressor according to any one of claims 1 to 4, characterized in that, ​ 10. The scroll compressor of claim 9, wherein, The amplitude of the wave shape remains constant and the bottom wall (344) of the sealing groove (340) and the bottom (351) of the sealing bar (350) are parallel to the top surface of the scroll to make the top (352) of the sealing bar (350) parallel to the top surface of the scroll.

11. The scroll compressor according to any one of claims 1 to 4, characterized in that, The amplitude of the wave shape increases along a direction from the inner end (361) to the outer end (362) of the pre-tension spring (360).

12. The scroll compressor of claim 11, wherein, The bottom wall (344) of the sealing groove (340) and / or the bottom (351) of the sealing bar (350) are inclined relative to the top surface of the scroll to make the top (352) of the sealing bar (350) parallel to the top surface of the scroll.

13. The scroll compressor according to any one of claims 1-4, wherein The material thickness of the pre-tension spring (360) decreases along a direction from the inner end (361) to the outer end (362).

14. The scroll compressor according to any one of claims 1-4, wherein, The pre-tension spring (360) is positioned such that the longitudinal axis of the wave shape is perpendicular to the top surface of the scroll.

15. The scroll compressor according to any one of claims 1-4, wherein, The two scrolls (200, 300) consist of a static scroll (200) fixed within the housing (100) and a dynamic scroll (300) movably disposed within the housing (100).

16. The scroll compressor according to any one of claims 1-4, wherein The two scrolls (200, 300) are both movably disposed within the housing (100) and are configured to rotate about two axes parallel and offset relative to each other, respectively.

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