Compressor and refrigeration apparatus

Abstract

The utility model provides a kind of compressor and refrigeration equipment, compressor includes: separation component;Pump body structure, pump body structure includes static disc subassembly and moving disc, static disc subassembly and moving disc form compression cavity, static disc subassembly is equipped with floating groove in side away from moving disc;Floating subassembly, movably be in floating groove, floating subassembly is equipped with recess in side towards separation component;Sealing component, at least a portion of sealing component is located in recess, sealing component includes first sealing piece and elastic piece, along the axial direction of moving disc, elastic piece is located in the side of first sealing piece away from separation component;Wherein, based on floating subassembly movement to first position, first sealing piece and separation component are in contact, and elastic piece is in compression state, floating subassembly and the groove wall of floating groove are enclosed and form back pressure cavity, back pressure cavity is communicated with compression cavity, simultaneously realize axial seal and radial seal, reduce the leakage of high-pressure refrigerant, it is favorable to promote the capacity and energy efficiency level of compressor.

Description

Technical Field

[0001] This utility model relates to the field of compressor equipment technology, and more specifically, to a compressor and refrigeration equipment. Background Technology

[0002] Currently, scroll compressors include a partition plate and wear-resistant plates. The wear-resistant plates are mounted on the partition plate, and when the scroll compressor is running, the upper surface of the float plate abuts against the wear-resistant plates to form a seal. In related technologies, the sealing performance between the float plate and the wear-resistant plates is relatively poor, which can easily cause leakage of high-pressure refrigerant, affecting the capacity and energy efficiency of the scroll compressor. Utility Model Content

[0003] The embodiments of this utility model are intended to solve at least one of the technical problems existing in the prior art.

[0004] Therefore, a first aspect of the embodiments of this utility model provides a compressor.

[0005] A second aspect of the present invention provides a refrigeration device.

[0006] In view of the above, according to a first aspect of the present invention, a compressor is provided, the compressor comprising: a separating assembly; a pump body structure including a stationary disc assembly and a moving disc, the stationary disc assembly and the moving disc forming a compression chamber, the stationary disc assembly having a floating groove on the side opposite to the moving disc; a floating assembly movably disposed in the floating groove, the floating assembly having a groove on the side facing the separating assembly; a sealing assembly, at least a portion of the sealing assembly being located within the groove, the sealing assembly including a first sealing member and an elastic member, the elastic member being located on the side of the first sealing member opposite to the separating assembly along the axial direction of the moving disc; wherein, based on the floating assembly moving to a first position, the first sealing member abuts against the separating assembly, the elastic member is in a compressed state, the floating assembly and the groove wall of the floating groove enclose a back pressure chamber, the back pressure chamber communicating with the compression chamber.

[0007] The compressor provided in this embodiment includes a separating assembly, a pump body structure, a floating assembly, and a sealing assembly. Specifically, the pump body structure includes a stationary disc assembly and a moving disc, which together form a compression chamber. A floating groove is provided on the side of the stationary disc assembly facing away from the moving disc, and the floating assembly is movably disposed in the floating groove. Optionally, the stationary disc assembly includes a stationary disc and a back pressure plate, wherein the stationary disc and the moving disc form a compression chamber, the back pressure plate is disposed on the side of the stationary disc facing away from the moving disc, and a portion of the back pressure plate and a portion of the stationary disc form a floating groove.

[0008] Specifically, the floating assembly can move between a first position and a second position. When the compressor is running, the floating assembly moves towards the side where the separating assembly is located until it reaches the first position. At this point, the floating assembly and the wall of the floating groove enclose a back pressure chamber. Since the back pressure chamber is connected to the compression chamber, a medium pressure can be introduced into the back pressure chamber during compressor operation. Under the action of this medium pressure, a certain axial force can be applied to the stationary disc assembly to ensure the sealing between the stationary disc and the moving disc. Simultaneously, since the moving disc can rotate relative to the stationary disc assembly to compress the refrigerant in the compression chamber, when the pressure of the compressed refrigerant reaches the discharge pressure, the high-pressure refrigerant is discharged from the exhaust port on the stationary disc. Because the first seal abuts against the separating assembly, a seal is achieved between the high-pressure chamber (exhaust chamber) and the low-pressure chamber (suction chamber).

[0009] When the compressor stops running, the floating component moves to the side away from the partition component until it reaches the second position. At this point, the high-pressure chamber and the low-pressure chamber are connected because the first seal separates from the partition component.

[0010] Since the elastic element is located on the side of the first seal away from the separator assembly, and the elastic element is in a compressed state when the first seal abuts against the separator assembly, the elastic element can apply an axial elastic force to the first seal towards the separator assembly, i.e., an upward axial elastic force. This elastic force can increase the clamping force between the first seal and the separator assembly, thereby enabling the first seal and the separator assembly to fit tightly in the axial direction and ensuring an axial seal between the first seal and the separator assembly.

[0011] Furthermore, the floating component has a groove on the side facing the separating component, and at least a portion of the sealing component is located within the groove. Optionally, at least a portion of the first seal and the elastic element are located within the groove, or the elastic element is located within the groove. The specific configuration can be adjusted according to actual needs.

[0012] It is understandable that the radially inner side of the location where the first seal abuts against the separator assembly is under high pressure, while the radially outer side is under low pressure. Thus, under the action of this pressure difference, radial sealing can be achieved between the first seal and the separator assembly. In other words, by setting up the first seal and the elastic element, both axial and radial sealing can be achieved simultaneously, significantly improving the sealing performance between the separator assembly and the floating assembly, achieving effective sealing between high and low pressure, reducing leakage of high-pressure refrigerant, and consequently improving the compressor's capacity and energy efficiency.

[0013] Moreover, since at least part of the sealing components are located within the groove, the sealing components located within the groove can be limited. During the movement of the floating component relative to the floating groove between the first and second positions, displacement of the sealing components can be prevented, thereby ensuring that a reliable seal is always maintained between the floating component and the separating component, which is beneficial to improving the reliability of the compressor.

[0014] In some technical solutions, the first seal may optionally include a first surface and a second surface that are radially opposite to each other along the moving disk, with the first surface being closer to the central axis of the moving disk than the second surface; wherein a portion of the first surface is exposed in the groove.

[0015] In this technical solution, it can be understood that the radially inner side of the position where the first seal abuts against the separator assembly is under high pressure, while the radially outer side is under low pressure. Since part of the first surface is exposed in the groove, during compressor operation, the inner high pressure directly acts on the inner surface of the first seal, thereby allowing the inner high pressure to press the first seal tightly. This improves the sealing effect between the first seal and the separator assembly, further reduces leakage of high-pressure refrigerant, and ensures the compressor's energy efficiency.

[0016] In some technical solutions, optionally, the floating component includes a first float plate, the first float plate includes a plate body, a first protrusion and a second protrusion, wherein the first protrusion and the second protrusion are respectively disposed on the side of the plate body facing the separating component and are spaced apart along the radial direction of the moving disk, the first protrusion is located inside the second protrusion, and the first protrusion, the second protrusion and the plate body surround to form a groove; along the axial direction of the moving disk, the height of the first protrusion is lower than the height of the second protrusion.

[0017] In this technical solution, the first protrusion, the second protrusion, and the plate together form a groove, meaning the first seal is located between the first and second protrusions. Because the axial height of the first protrusion is lower than that of the second protrusion, the inner surface of the first seal is exposed outside the groove. During compressor operation, the high internal pressure acts directly on the inner surface of the first seal, allowing it to press firmly against the first seal, thus improving the sealing effect between the first seal and the separator assembly.

[0018] Meanwhile, since the elastic element is located on the side of the first seal away from the separator assembly, and the elastic element is in a compressed state when the first seal abuts against the separator assembly, the elastic element can apply an axial elastic force to the first seal towards the separator assembly, i.e., an upward axial elastic force. This elastic force can increase the clamping force between the first seal and the separator assembly, thereby ensuring a tight axial fit between the first seal and the separator assembly and guaranteeing an axial seal between them. Moreover, under the action of the internal and external pressure difference, a radial seal can also be achieved between the first seal and the separator assembly, significantly improving the sealing performance between the separator assembly and the floating assembly, achieving effective sealing between high and low pressures, reducing high-pressure refrigerant leakage, and thus contributing to improving the compressor's capacity and energy efficiency.

[0019] In some technical solutions, optionally, along the axial direction of the moving disk, the height of the first protrusion is h1 and the height of the second protrusion is h2, wherein 0.5mm≤h2-h1≤2mm.

[0020] In this technical solution, by setting the height difference between the first and second protrusions between 0.5mm and 2mm, the first seal is pressed against the separator assembly under the elastic force of the elastic element, achieving axial sealing. Simultaneously, the high pressure inside can directly and effectively act on the first seal, achieving radial sealing, thereby improving the sealing effect between high and low pressure. Furthermore, it can effectively limit the movement of the first seal, ensuring that the floating assembly maintains a reliable seal with the separator assembly during axial reciprocating motion.

[0021] In some technical solutions, optionally, based on the movement of the floating component to the first position, the end face of the second protrusion away from the plate body is in contact with the side of the separator component facing the pump body structure.

[0022] In this technical solution, since the end face of the second protrusion away from the plate is in contact with the side of the separator assembly facing the pump body structure, a multi-seal structure can be formed between the separator assembly and the floating assembly, which effectively improves the sealing effect between the separator assembly and the floating assembly, significantly improves the leakage problem of high-pressure refrigerant, and enhances the compressor's capacity and energy efficiency.

[0023] In some technical solutions, optionally, along the axial direction of the moving disc, the height of the second protrusion is h2, the height of the elastic element in its natural state is h3, and the thickness of the first sealing element is t1, wherein h2≤t1+0.8×h3.

[0024] In this technical solution, since h2≤t1+0.8×h3, where h2 is the axial height of the second protrusion and t1 is the axial thickness of the first seal, when the floating assembly moves to the first position and the first seal abuts against the partition assembly, it can ensure that the elastic element has an effective compression amount. Then, under the action of the elastic force of the elastic element, the first seal is pressed against the partition assembly, ensuring the axial seal between the floating assembly and the partition assembly. This is beneficial to further improve the sealing effect between the partition assembly and the floating assembly and reduce the leakage of high-pressure refrigerant.

[0025] In some technical solutions, optionally, along the axial direction of the moving disc, the height of the second protrusion is h2, the thickness of the first seal is t1, and the thickness of the elastic element is t2, wherein h2≥t1+2×t2.

[0026] In this technical solution, since h2≥t1+2×t2, where h2 is the axial height of the second protrusion, t1 is the axial thickness of the first seal, and t2 is the thickness of the elastic element, when the floating assembly moves to the first position and the first seal abuts against the separating assembly, the elastic element can be prevented from being over-compressed, thus preventing failure due to over-compression of the elastic element. This ensures that when the first seal abuts against the separating assembly, the elastic element can apply an upward axial force to the first seal to guarantee the axial seal between the floating assembly and the separating assembly, thereby improving the sealing effect between high and low pressure.

[0027] In some technical solutions, optionally, along the axial direction of the moving disc, the height of the first protrusion is h1, the height of the elastic element in its natural state is h3, and the thickness of the first sealing element is t1, wherein h1≥t1 / 2+h3.

[0028] In this technical solution, since h1≥t1 / 2+h3, where h1 is the axial height of the first protrusion and t1 is the axial thickness of the first seal, the first seal can be effectively limited, thereby ensuring that the floating assembly can always maintain a reliable seal with the separating assembly during the axial reciprocating motion.

[0029] In some technical solutions, the first seal may optionally include a flexible element.

[0030] In this technical solution, since the first sealing element is a flexible element, that is, the first sealing element adopts a flexible sealing material, compared with the related technology that uses a wear-resistant plate made of hard metal material and a floating plate made of hard metal material for contact sealing, it can effectively reduce the leakage between the floating component and the separation component due to the metal seal, and improve the compressor's capacity and energy efficiency.

[0031] In some technical solutions, optionally, the first seal is cross-sectioned along the axial direction of the moving disc, and the cross-sectional shape of the first seal is rectangular; and / or the first seal includes a sealing ring.

[0032] In this technical solution, since the cross-sectional shape of the first seal is rectangular, optionally, the first seal is a rectangular sealing ring. By setting the cross-sectional shape of the first seal to be rectangular, compared to setting the cross-sectional shape of the first seal to be circular, the contact area between the first seal and the separator assembly can be increased when the first seal abuts against the separator assembly. This is beneficial to improving the sealing effect between the first seal and the separator assembly, further reducing the leakage of high-pressure refrigerant, and improving the energy efficiency of the compressor.

[0033] Since the first seal is a sealing ring, i.e., an annular seal, it helps to further improve the sealing performance between the first seal and the separator assembly. It can be understood that, because the first seal is a sealing ring, the groove is constructed as an annular groove.

[0034] In some technical solutions, the first seal may optionally include an inclined surface, a first end and a second end, the first end and the second end being arranged circumferentially along the first seal and being separable, the inclined surface being provided at least one of the first end and the second end, the inclined surface extending obliquely relative to the axial direction of the moving disc.

[0035] In this technical solution, since the inclined surface is provided at least one of the first end and the second end, and the inclined surface extends obliquely relative to the axial direction, when the inner high pressure acts on the first seal, the component of the force exerted by the gas pressure on the first seal includes the axial upward component, which effectively increases the clamping force between the first seal and the separator assembly, which is conducive to further improving the sealing effect between the floating assembly and the separator assembly, reducing the leakage of high-pressure refrigerant, and improving the energy efficiency of the compressor.

[0036] In some technical solutions, optionally, the angle between the plane containing the inclined plane and the horizontal plane is θ, where 30°≤θ≤60°.

[0037] In this technical solution, since 30°≤θ≤60°, the inclination angle of the inclined plane is limited to between 30° and 60°. Therefore, when the inner high pressure acts on the first seal, the component of the force exerted by the gas pressure on the first seal can be as much as possible as the axial upward component, that is, the axial upward component is increased, which further enhances the clamping force between the first seal and the separator assembly, and significantly improves the sealing effect between high and low pressure.

[0038] In some technical solutions, optionally, there are two inclined surfaces, including a first inclined surface and a second inclined surface, with the first inclined surface located at a first end and the second inclined surface located at a second end; wherein at least a portion of the first inclined surface and at least a portion of the second inclined surface are arranged opposite to each other.

[0039] In this technical solution, since there are two inclined surfaces, including a first inclined surface and a second inclined surface, the first inclined surface is located at the first end and the second inclined surface is located at the second end. Since at least a portion of the first inclined surface is opposite to at least a portion of the second inclined surface, that is, the opening of the first seal is an angled structure, it can ensure the sealing performance at the opening of the first seal while, when the internal high pressure acts on the first seal, under the action of gas pressure, it can further increase the axial upward component force, improve the clamping force between the first seal and the separator assembly, and significantly improve the sealing effect between high and low pressure.

[0040] In some technical solutions, optionally, the first seal includes a body, and along the circumference of the first seal, a first end and a second end are respectively located at both ends of the body. The end of the first end away from the body is provided with a first notch, so that the first end forms a first inclined surface. The end of the second end away from the body is provided with a second notch, so that the second end forms a second inclined surface. Wherein, at least a portion of the second end is located within the first notch, and at least a portion of the first end is located within the second notch.

[0041] In this technical solution, since at least a portion of the second end is located within the first notch, and at least a portion of the first end is located within the second notch, when the internal high pressure acts on the first seal, the component of the gas pressure force acting on the first seal includes an axial upward component. This effectively increases the clamping force between the first seal and the separator assembly while preventing interference between the first or second end and the groove wall due to the first or second end protruding from the inner or outer wall of the body. This ensures that the first seal can be pressed tightly onto the separator assembly under the action of the elastic element, which is beneficial for ensuring a sealing effect. Furthermore, the structure is simple and easy to manufacture.

[0042] In some technical solutions, optionally, the compressor further includes a housing, and the separation assembly includes a partition plate, a wear-resistant block, and a second seal. The partition plate is disposed inside the housing and divides the housing into an intake chamber and an exhaust chamber. The pump body structure is disposed in the intake chamber, and the compression chamber can communicate with the exhaust chamber. The wear-resistant block is connected to the partition plate and includes a sealing part located on the side of the partition plate facing the pump body structure. Based on the movement of the floating assembly to a first position, the first seal abuts against the sealing part, and the second seal is disposed between the wear-resistant block and the partition plate.

[0043] In this technical solution, the second sealing element between the wear-resistant block and the partition plate can effectively improve the sealing performance between the wear-resistant block and the partition plate. When the first sealing element abuts against the sealing part, it can achieve effective sealing on both sides of the sealing part in the axial direction, further improving the sealing effect between high and low pressure. This significantly improves the problem of poor sealing between high and low pressure caused by factors such as the ring welding of the partition plate and the riveting of the wear-resistant sheet in related technologies, reduces the leakage of high-pressure refrigerant, and helps to improve the compressor's capacity and energy efficiency.

[0044] In some technical solutions, optionally, a sealing groove is provided on the side of the sealing part away from the pump body structure, and at least a portion of the second seal is located in the sealing groove and abuts against the side of the partition plate facing the pump body structure.

[0045] In this technical solution, a sealing groove is provided on the side of the sealing part away from the pump body structure, in which at least part of the second sealing element is embedded. This can improve the sealing effect between high and low pressure, significantly improve the problem of poor sealing between high and low pressure caused by factors such as the ring welding of the partition plate and the riveting of the wear-resistant sheet in related technologies, reduce high-pressure refrigerant leakage, and at the same time, limit the second sealing element, which is conducive to improving the installation stability of the second sealing element and ensuring reliable sealing between the partition plate and the wear-resistant block.

[0046] In addition, since a sealing groove is provided on the side of the sealing part away from the pump body structure, the second sealing element can be reliably installed while the side of the sealing part away from the pump body structure can be tightly fitted with the partition plate, thereby forming a multi-seal structure between the sealing part and the partition plate, which is beneficial to further improve the sealing effect between high and low pressure.

[0047] In some technical solutions, the partition plate is optionally provided with mounting holes, and the wear-resistant block also includes a mounting part. Along the axial direction of the moving disc, the mounting part is located on the side of the sealing part away from the pump body structure. The mounting part is inserted into the mounting hole and connected to the partition plate.

[0048] In this technical solution, the wear-resistant block is further defined as including a mounting part. Specifically, along the axial direction of the moving disc, the mounting part is located on the side of the sealing part away from the pump body structure, and the mounting part is inserted into the mounting hole and connected to the partition plate, thereby realizing the fixed connection between the wear-resistant block and the partition plate.

[0049] Optionally, the mounting part is interference-fitted with the wall of the mounting hole to connect the mounting part to the partition plate. In other words, the wear-resistant block and the partition plate are connected by an interference fit, which ensures reliable assembly between the wear-resistant block and the partition plate while effectively reducing deformation of both during installation. This further improves the sealing effect between the partition plate and the wear-resistant block, as well as between the wear-resistant block and the floating assembly, thereby enhancing the compressor's energy efficiency.

[0050] In some technical solutions, optionally, the thickness of the sealing part along the axial direction of the moving disc is t3, wherein t3 ≥ 3 mm.

[0051] In this technical solution, since the axial thickness of the sealing part is greater than or equal to 3mm, it is understood that the thickness of the wear-resistant sheet in related technologies is relatively thin, generally around 1mm. That is to say, by setting the axial thickness of the sealing part that abuts against the first sealing element to be relatively thick, the overall structural strength of the sealing part and the wear-resistant block can be significantly improved, deformation of the sealing part can be reduced, the sealing effect between the wear-resistant block and the partition plate, and between the wear-resistant block and the floating assembly can be improved, ensuring effective sealing between high and low pressure, reducing leakage of high-pressure refrigerant, improving compressor energy efficiency, and also helping to extend the service life of the wear-resistant block.

[0052] In some technical solutions, the floating assembly may optionally include a second float and a third seal, wherein the second float is disposed on the first float along the axial direction of the moving disk and is located on the side of the first float away from the separating assembly, and the third seal is disposed between the first float and the second float along the radial direction of the moving disk, with both ends of the third seal abutting against the wall of the floating groove.

[0053] In this technical solution, the floating assembly also includes a second float and a third seal. The second float is connected to the first float, and a portion of the second float is located on the side of the first float closer to the compression chamber. The third seal is disposed between the first and second floats, and both ends of the third seal in the radial direction of the moving disc abut against the wall of the floating groove, thereby ensuring the sealing of the back pressure chamber.

[0054] According to a second aspect of this utility model, a refrigeration device is provided, including a compressor as provided in any of the above technical solutions, and thus possesses all the beneficial technical effects of the compressor, which will not be repeated here.

[0055] Additional aspects and advantages of the present invention will be set forth in the description which follows, in part will be obvious from the description, or may be learned by practice of the present invention. Attached Figure Description

[0056] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0057] Figure 1 One of the partial structural schematic diagrams of a compressor according to an embodiment of the present invention is shown;

[0058] Figure 2 A second partial structural schematic diagram of a compressor according to an embodiment of the present invention is shown;

[0059] Figure 3 One of the structural schematic diagrams of an elastic member according to an embodiment of the present invention is shown;

[0060] Figure 4 A second schematic diagram of the structure of an elastic member according to an embodiment of the present invention is shown;

[0061] Figure 5 One of the structural schematic diagrams of a first sealing member according to an embodiment of the present invention is shown;

[0062] Figure 6 A second schematic diagram of the structure of a first sealing member according to an embodiment of the present invention is shown;

[0063] Figure 7 The third part of the schematic diagram of a compressor according to an embodiment of the present invention is shown.

[0064] in, Figures 1 to 7 The correspondence between the reference numerals and component names in the attached drawings is as follows:

[0065] 1 Compressor, 10 Separator assembly, 12 Separator plate, 122 Mounting hole, 14 Wear-resistant block, 142 Sealing part, 144 Sealing groove, 146 Mounting part, 16 Second seal, 20 Pump body structure, 22 Stationary disc assembly, 222 Floating groove, 224 Stationary disc, 226 Back pressure plate, 24 Moving disc, 26 Compression chamber; 30 Floating assembly, 32 Groove, 34 First float plate, 342 Plate body, 344 First protrusion, 346 Second protrusion, 36 Second float plate, 38 Third seal, 40 Sealing assembly, 42 First seal, 421 First surface, 422 Second surface, 423 Inclined surface, 424 First end, 425 Second end, 426 First inclined surface, 427 Second inclined surface, 428 First notch, 429 Second notch, 430 Body, 44 Elastic element, 50 Back pressure chamber, 60 Housing, 62 Intake chamber, 64 Exhaust chamber. Detailed Implementation

[0066] To better understand the above-mentioned objectives, features, and advantages of this utility model, the present utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0067] Many specific details are set forth in the following description in order to provide a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present invention is not limited to the specific embodiments disclosed below.

[0068] The following reference Figures 1 to 7The present invention will be described in some embodiments of the compressor 1 and refrigeration equipment provided.

[0069] In one embodiment according to this application, such as Figure 1 , Figure 2 and Figure 7 As shown, a compressor 1 is proposed, comprising: a separating assembly 10; a pump body structure 20, the pump body structure 20 including a stationary disc assembly 22 and a moving disc 24, the stationary disc assembly 22 and the moving disc 24 forming a compression chamber 26, the stationary disc assembly 22 having a floating groove 222 on the side away from the moving disc 24; a floating assembly 30 movably disposed in the floating groove 222, the floating assembly 30 having a groove 32 on the side facing the separating assembly 10; and a sealing assembly 40, at least a portion of the sealing assembly 40 being located within the groove 32, the sealing assembly 40 including a first sealing member 42 and an elastic member 44, the elastic member 44 being located on the side of the first sealing member 42 away from the separating assembly 10 along the axial direction of the moving disc 24; wherein, based on the floating assembly 30 moving to a first position, the first sealing member 42 abuts against the separating assembly 10, the elastic member 44 is in a compressed state, the floating assembly 30 and the groove wall of the floating groove 222 enclose a back pressure chamber 50, the back pressure chamber 50 being connected to the compression chamber 26.

[0070] The compressor 1 provided in this embodiment includes a separating component 10, a pump body structure 20, a floating component 30, and a sealing component 40. Specifically, the pump body structure 20 includes a stationary disc assembly 22 and a moving disc 24, which together form a compression chamber 26. A floating groove 222 is provided on the side of the stationary disc assembly 22 facing away from the moving disc 24, and the floating component 30 is movably disposed in the floating groove 222. Optionally, the stationary disc assembly 22 includes a stationary disc 224 and a back pressure plate 226, wherein the stationary disc 224 and the moving disc 24 form the compression chamber 26, and the back pressure plate 226 is disposed on the side of the stationary disc 224 facing away from the moving disc 24, with a portion of the back pressure plate 226 and a portion of the stationary disc 224 forming the floating groove 222.

[0071] Specifically, the floating component 30 can move between a first position and a second position. When the compressor 1 is running, the floating component 30 moves towards the side where the separating component 10 is located until it reaches the first position. At this time, the floating component 30 and the wall of the floating groove 222 enclose a back pressure chamber 50. Since the back pressure chamber 50 is connected to the compression chamber 26, a medium pressure can be introduced into the back pressure chamber 50 during the operation of the compressor 1. Under the action of the medium pressure, a certain axial force can be applied to the stationary plate assembly 22 to ensure the sealing between the stationary plate 224 and the moving plate 24. At the same time, since the moving plate 24 can rotate relative to the stationary plate assembly 22 to compress the refrigerant in the compression chamber 26, when the pressure of the compressed refrigerant reaches the discharge pressure, the high-pressure refrigerant is discharged from the exhaust port on the stationary plate 224. Since the first seal 42 abuts against the separating component 10, a seal can be achieved between the high-pressure chamber (exhaust chamber 64) and the low-pressure chamber (suction chamber 62).

[0072] When the compressor 1 stops running, the floating component 30 moves to the side away from the partition component 10 until it moves to the second position. At this time, since the first seal 42 is separated from the partition component 10, the high-pressure chamber and the low-pressure chamber are connected.

[0073] Since the elastic element 44 is located on the side of the first seal 42 away from the partition assembly 10, and the elastic element 44 is in a compressed state when the first seal 42 abuts against the partition assembly 10, that is, the elastic element 44 can apply an axial elastic force to the first seal 42 toward the partition assembly 10, i.e., an axially upward elastic force. This elastic force can increase the clamping force between the first seal 42 and the partition assembly 10, so that the first seal 42 and the partition assembly 10 can fit tightly in the axial direction, ensuring the axial seal between the first seal 42 and the partition assembly 10.

[0074] Furthermore, since the floating component 30 has a groove 32 on the side facing the separating component 10, and at least a portion of the sealing component 40 is located within the groove 32. Optionally, at least a portion of the first sealing member 42 and the elastic member 44 are located within the groove 32, or the elastic member 44 is located within the groove 32. The specific configuration can be adjusted according to actual needs.

[0075] It is understood that the radially inner side of the position where the first seal 42 abuts against the separator assembly 10 is under high pressure, and the radially outer side is under low pressure. Thus, under the action of the internal and external pressure difference, radial sealing can be achieved between the first seal 42 and the separator assembly 10. That is, by setting the first seal 42 and the elastic element 44, axial sealing and radial sealing can be achieved simultaneously, significantly improving the sealing performance between the separator assembly 10 and the floating assembly 30, achieving effective sealing between high and low pressure, reducing leakage of high-pressure refrigerant, and thus helping to improve the capacity and energy efficiency of the compressor 1.

[0076] Moreover, since at least a portion of the sealing component 40 is located within the groove 32, the sealing component 40 located within the groove 32 can be limited. During the movement of the floating component 30 relative to the floating groove 222 between the first and second positions, the sealing component 40 can be prevented from shifting, thereby ensuring that the floating component 30 and the separating component 10 always maintain a reliable seal, which is beneficial to improving the reliability of the compressor 1.

[0077] Optionally, the elastic element 44 includes a spring or an elastic washer. The spring may be a wave spring.

[0078] like Figure 2 As shown, in some embodiments, optionally, the first seal 42 includes a first surface 421 and a second surface 422 that are radially opposite to each other along the moving disk 24, the first surface 421 being closer to the central axis of the moving disk 24 than the second surface 422; wherein a portion of the first surface 421 is exposed in the groove 32.

[0079] In this embodiment, the first sealing member 42 includes a first surface 421 and a second surface 422, wherein the first surface 421 and the second surface 422 are opposite each other along the radial direction of the moving disk 24, and the first surface 421 is closer to the central axis of the moving disk 24 than the second surface 422. That is, the first surface 421 is located radially inside the second surface 422, that is, the first surface 421 is the inner surface of the first sealing member 42, and the second surface 422 is the outer surface of the first sealing member 42.

[0080] It is understandable that the radially inner side of the position where the first seal 42 abuts against the separator assembly 10 is under high pressure, while the radially outer side is under low pressure. Since part of the first surface 421 is exposed outside the groove 32, that is, during the operation of the compressor 1, the inner high pressure acts directly on the inner surface of the first seal 42, thereby allowing the inner high pressure to press the first seal 42 tightly, which helps to improve the sealing effect between the first seal 42 and the separator assembly 10, further reducing the leakage of high-pressure refrigerant and ensuring the energy efficiency level of the compressor 1.

[0081] like Figure 2 As shown, in some embodiments, optionally, the floating component 30 includes a first float plate 34, the first float plate 34 including a plate body 342, a first protrusion 344 and a second protrusion 346, wherein the first protrusion 344 and the second protrusion 346 are respectively disposed on the side of the plate body 342 facing the separating component 10 and are arranged at intervals along the radial direction of the moving disk 24, the first protrusion 344 is located inside the second protrusion 346, and the first protrusion 344, the second protrusion 346 and the plate body 342 surround to form a groove 32; along the axial direction of the moving disk 24, the height of the first protrusion 344 is lower than the height of the second protrusion 346.

[0082] In this embodiment, the floating assembly 30 includes a first floating plate 34, wherein the first floating plate 34 includes a plate body 342, a first protrusion 344, and a second protrusion 346. Specifically, the first protrusion 344 and the second protrusion 346 are respectively disposed on the side of the plate body 342 facing the separating assembly 10, the first protrusion 344 and the second protrusion 346 are radially spaced along the moving disk 24, and the first protrusion 344 is located radially inside the second protrusion 346.

[0083] Since the first protrusion 344, the second protrusion 346, and the plate 342 enclose and form a groove 32, the first seal 42 is located between the first protrusion 344 and the second protrusion 346. Because the axial height of the first protrusion 344 is lower than the axial height of the second protrusion 346, the inner surface of the first seal 42 is exposed outside the groove 32. During the operation of the compressor 1, the internal high pressure acts directly on the inner surface of the first seal 42, allowing the internal high pressure to press the first seal 42 tightly, which helps improve the sealing effect between the first seal 42 and the separator assembly 10.

[0084] Meanwhile, since the elastic element 44 is located on the side of the first seal 42 away from the separator assembly 10, and the elastic element 44 is in a compressed state when the first seal 42 abuts against the separator assembly 10, the elastic element 44 can apply an axial elastic force to the first seal 42 towards the separator assembly 10, i.e., an upward axial elastic force. This elastic force can increase the clamping force between the first seal 42 and the separator assembly 10, thereby enabling the first seal 42 and the separator assembly 10 to fit tightly in the axial direction, ensuring an axial seal between the first seal 42 and the separator assembly 10. Moreover, under the action of the internal and external pressure difference, a radial seal can also be achieved between the first seal 42 and the separator assembly 10, significantly improving the sealing performance between the separator assembly 10 and the floating assembly 30, achieving effective sealing between high and low pressure, reducing leakage of high-pressure refrigerant, and thus helping to improve the capacity and energy efficiency of the compressor 1.

[0085] Optionally, the plate 342, the first protrusion 344, and the second protrusion 346 are an integral structure.

[0086] like Figure 2 , Figure 3 and Figure 4 As shown, in some embodiments, optionally, along the axial direction of the moving disk 24, the height of the first protrusion 344 is h1, and the height of the second protrusion 346 is h2, wherein 0.5mm≤h2-h1≤2mm.

[0087] In this embodiment, since h2-h1 is between 0.5mm and 2mm, the height difference between the first protrusion 344 and the second protrusion 346 is limited to between 0.5mm and 2mm.

[0088] Understandably, if the height difference between the first protrusion 344 and the second protrusion 346 is too small, i.e., less than 0.5 mm, the exposed portion of the inner surface of the first seal 42 will be too small, and the high pressure inside will not be able to effectively act on the inner surface of the first seal 42. If the height difference between the first protrusion 344 and the second protrusion 346 is too large, i.e., greater than 2 mm, the axial depth of the groove 32 will be too shallow, and it will be unable to effectively limit the first seal 42. During the axial reciprocating motion of the floating assembly 30, the first seal 42 will easily come out of the groove 32, causing the seal between the floating assembly 30 and the separating assembly 10 to fail.

[0089] By setting the height difference between the first protrusion 344 and the second protrusion 346 between 0.5mm and 2mm, under the elastic force of the elastic member 44, the first sealing member 42 is pressed against the separating assembly 10 to achieve axial sealing. At the same time, the high pressure inside can directly and effectively act on the first sealing member 42 to achieve radial sealing, thereby improving the sealing effect between high and low pressure. Moreover, it can also effectively limit the first sealing member 42, ensuring that the floating assembly 30 can always maintain a reliable seal with the separating assembly 10 during axial reciprocating motion.

[0090] Optionally, h2-h1 can be any one of 0.5mm, 1mm, 1.5mm and 2mm.

[0091] In some embodiments, optionally, based on the movement of the floating component 30 to the first position, the end face of the second protrusion 346 away from the plate 342 is in contact with one side of the separator component 10 facing the pump body structure 20.

[0092] In this embodiment, when the floating component 30 moves to the first position, the first seal 42 abuts against the partition component 10, and under the action of the elastic force of the elastic member 44, the first seal 42 is pressed against the partition component 10, thereby achieving axial sealing between the floating component 30 and the partition component 10. At the same time, under the action of the pressure difference between the inside and outside of the first seal 42, radial sealing between the floating component 30 and the partition component 10 can also be achieved.

[0093] Meanwhile, since the end face of the second protrusion 346 facing away from the plate 342 is in contact with the side of the separator 10 facing the pump body structure 20, a multi-seal structure can be formed between the separator 10 and the floating assembly 30, which effectively improves the sealing effect between the separator 10 and the floating assembly 30, significantly improves the leakage problem of high-pressure refrigerant, and enhances the capacity and energy efficiency of the compressor 1.

[0094] like Figure 2 , Figure 3 and Figure 4As shown, in some embodiments, optionally, along the axial direction of the moving disk 24, the height of the second protrusion 346 is h2, the height of the elastic member 44 in its natural state is h3, and the thickness of the first seal member 42 is t1, wherein h2≤t1+0.8×h3.

[0095] In this embodiment, the height of the elastic member 44 in its natural state is h3, that is, the axial height of the elastic member 44 when it is not compressed is h3.

[0096] Since h2≤t1+0.8×h3, where h2 is the axial height of the second protrusion 346 and t1 is the axial thickness of the first seal 42, when the floating assembly 30 moves to the first position and the first seal 42 abuts against the partition assembly 10, the elastic member 44 can be ensured to have an effective compression amount. Then, under the action of the elastic force of the elastic member 44, the first seal 42 is pressed against the partition assembly 10, ensuring the axial seal between the floating assembly 30 and the partition assembly 10. This is beneficial to further improve the sealing effect between the partition assembly 10 and the floating assembly 30 and reduce the leakage of high-pressure refrigerant.

[0097] like Figure 2 , Figure 3 and Figure 4 As shown, in some embodiments, optionally, along the axial direction of the moving disk 24, the height of the second protrusion 346 is h2, the thickness of the first seal 42 is t1, and the thickness of the elastic member 44 is t2, wherein h2≥t1+2×t2.

[0098] In this embodiment, since h2≥t1+2×t2, where h2 is the axial height of the second protrusion 346, t1 is the axial thickness of the first seal 42, and t2 is the thickness of the elastic member 44, when the floating assembly 30 moves to the first position and the first seal 42 abuts against the separating assembly 10, the elastic member 44 can be prevented from being over-compressed, thereby preventing failure due to over-compression of the elastic member 44. This ensures that when the first seal 42 abuts against the separating assembly 10, the elastic member 44 can apply an upward axial force to the first seal 42 to ensure the axial seal between the floating assembly 30 and the separating assembly 10, thereby improving the sealing effect between high and low pressure.

[0099] like Figure 2 , Figure 3 and Figure 4 As shown, in some embodiments, optionally, along the axial direction of the moving disk 24, the height of the first protrusion 344 is h1, the height of the elastic member 44 in its natural state is h3, and the thickness of the first seal member 42 is t1, wherein h1≥t1 / 2+h3.

[0100] In this embodiment, the height of the elastic member 44 in its natural state is h3, that is, the axial height of the elastic member 44 when it is not compressed is h3.

[0101] Since h1≥t1 / 2+h3, where h1 is the axial height of the first protrusion 344 and t1 is the axial thickness of the first seal 42, the first seal 42 can be effectively limited, thereby ensuring that the floating assembly 30 can always maintain a reliable seal with the separating assembly 10 during the axial reciprocating motion.

[0102] In some embodiments, the first seal 42 may optionally include a flexible element.

[0103] In this embodiment, since the first seal 42 is a flexible component, that is, the first seal 42 adopts a flexible sealing material, compared with the related technology of using a wear-resistant sheet made of hard metal material and a float plate made of hard metal material for abutment sealing, it can effectively reduce the leakage between the floating component 30 and the separation component 10 due to the metal seal, thereby improving the capacity and energy efficiency of the compressor 1.

[0104] Optionally, the first seal 42 includes a plastic component.

[0105] Optionally, the first seal 42 can be a high-performance non-metallic sealing material such as PTFE (polytetrafluoroethylene).

[0106] In some embodiments, the first seal 42 may be cross-sectioned along the axial direction of the moving disc 24, and the cross-sectional shape of the first seal 42 is rectangular; and / or the first seal 42 includes a sealing ring.

[0107] In this embodiment, since the cross-sectional shape of the first seal 42 is rectangular, optionally, the first seal 42 is a rectangular sealing ring. By setting the cross-sectional shape of the first seal 42 to rectangular, compared to setting the cross-sectional shape of the first seal 42 to circular, the contact area between the first seal 42 and the separator assembly 10 can be increased when the first seal 42 abuts against the separator assembly 10. This is beneficial to improving the sealing effect between the first seal 42 and the separator assembly 10, further reducing the leakage of high-pressure refrigerant, and improving the energy efficiency of the compressor 1.

[0108] Since the first seal 42 is a sealing ring, that is, the first seal 42 is an annular seal, it is beneficial to further improve the sealing performance between the first seal 42 and the separator assembly 10. It can be understood that, because the first seal 42 is a sealing ring, the groove 32 is constructed as an annular groove.

[0109] like Figure 5 and Figure 6As shown, in some embodiments, optionally, the first seal 42 includes a ramp 423, a first end 424 and a second end 425, the first end 424 and the second end 425 being arranged circumferentially along the first seal 42 and being separable, the ramp 423 being disposed on at least one of the first end 424 and the second end 425, the ramp 423 extending obliquely relative to the axial direction of the moving disc 24.

[0110] In this embodiment, the first seal 42 includes an inclined surface 423, a first end 424 and a second end 425, wherein the first end 424 and the second end 425 are arranged circumferentially along the first seal 42 and the first end 424 and the second end 425 are separable. That is to say, the first seal 42 has an opening. During the assembly process of the compressor 1, the first seal 42 with an opening can facilitate assembly and improve assembly efficiency.

[0111] The first end 424 is provided with a slope 423, or the second end 425 is provided with a slope 423, or both the first end 424 and the second end 425 are provided with slopes 423. The specific configuration can be made according to actual needs.

[0112] Since the inclined surface 423 is provided at least one of the first end 424 and the second end 425, and the inclined surface 423 extends obliquely relative to the axial direction, when the inner high pressure acts on the first seal 42, the component of the force of the gas pressure on the first seal 42 includes the axial upward component, which effectively increases the clamping force between the first seal 42 and the separator assembly 10, which is conducive to further improving the sealing effect between the floating assembly 30 and the separator assembly 10, reducing the leakage of high-pressure refrigerant, and improving the energy efficiency of the compressor 1.

[0113] like Figure 6 As shown, in some embodiments, optionally, the angle between the plane containing the inclined plane 423 and the horizontal plane is θ, where 30°≤θ≤60°.

[0114] In this embodiment, since 30°≤θ≤60°, the inclination angle of the inclined surface 423 is limited to between 30° and 60°. Thus, when the inner high pressure acts on the first seal 42, the component of the force exerted by the gas pressure on the first seal 42 can be as much as possible as the axial upward component, that is, the axial upward component is increased, which further enhances the clamping force between the first seal 42 and the separator assembly 10, and significantly improves the sealing effect between high and low pressure.

[0115] Optionally, θ can be any one of 30°, 45°, and 60°.

[0116] like Figure 5 and Figure 6As shown, in some embodiments, optionally, there are two inclined surfaces 423, including a first inclined surface 426 and a second inclined surface 427. The first inclined surface 426 is disposed at a first end 424, and the second inclined surface 427 is disposed at a second end 425; wherein at least a portion of the first inclined surface 426 and at least a portion of the second inclined surface 427 are disposed opposite to each other.

[0117] In this embodiment, since there are two inclined surfaces 423, including a first inclined surface 426 and a second inclined surface 427, the first inclined surface 426 is located at the first end 424 and the second inclined surface 427 is located at the second end 425. Since at least a portion of the first inclined surface 426 is opposite to at least a portion of the second inclined surface 427, that is, the opening of the first seal 42 is an angled structure, it can ensure the sealing performance at the opening of the first seal 42. When the internal high pressure acts on the first seal 42, under the action of gas pressure, the axial upward component force can be further increased, the clamping force between the first seal 42 and the separator assembly 10 can be improved, and the sealing effect between high and low pressure can be significantly improved.

[0118] like Figure 5 As shown, in some embodiments, optionally, the first seal 42 includes a body 430. Along the circumference of the first seal 42, a first end 424 and a second end 425 are respectively located at both ends of the body 430. The end of the first end 424 away from the body 430 is provided with a first notch 428, so that the first end 424 forms a first inclined surface 426. The end of the second end 425 away from the body 430 is provided with a second notch 429, so that the second end 425 forms a second inclined surface 427. At least a portion of the second end 425 is located within the first notch 428, and at least a portion of the first end 424 is located within the second notch 429.

[0119] In this embodiment, the first sealing element 42 includes a body 430, wherein the first end 424 and the second end 425 are located at the two ends of the body 430 in the circumferential direction. The end of the first end 424 away from the body 430 is provided with a first notch 428, and the end of the second end 425 away from the body 430 is provided with a second notch 429, thereby forming a first inclined surface 426 and a second inclined surface 427. Under the action of gas pressure, the axial upward component force can be further increased, the clamping force between the first sealing element 42 and the separating assembly 10 can be improved, and the sealing effect between high and low pressure can be significantly improved.

[0120] Since at least a portion of the second end 425 is located within the first notch 428, and at least a portion of the first end 424 is located within the second notch 429, when the internal high pressure acts on the first seal 42, the component of the force exerted by the gas pressure on the first seal 42 includes an upward axial component. This effectively increases the clamping force between the first seal 42 and the separator assembly 10, while preventing interference between the first end 424 or the second end 425 and the groove wall of the groove 32 due to the first end 424 or the second end 425 protruding from the inner or outer wall of the body 430. This ensures that the first seal 42 can be pressed tightly onto the separator assembly 10 under the action of the elastic member 44, which is beneficial for ensuring the sealing effect. Furthermore, the structure is simple and easy to manufacture.

[0121] like Figure 1 and Figure 2 As shown, in some embodiments, the compressor 1 may optionally include a housing 60, and the partition assembly 10 includes a partition plate 12, a wear-resistant block 14, and a second seal 16. The partition plate 12 is disposed within the housing 60 and divides the housing 60 into an intake chamber 62 and an exhaust chamber 64. The pump body structure 20 is disposed in the intake chamber 62, and the compression chamber 26 is in communication with the exhaust chamber 64. The wear-resistant block 14 is connected to the partition plate 12 and includes a sealing portion 142. The sealing portion 142 is located on the side of the partition plate 12 facing the pump body structure 20. When the floating assembly 30 moves to the first position, the first seal 42 abuts against the sealing portion 142, and the second seal 16 is disposed between the wear-resistant block 14 and the partition plate 12.

[0122] In this embodiment, the partition assembly 10 includes a partition plate 12, a wear-resistant block 14, and a second seal 16. Specifically, the partition plate 12 divides the housing 60 into an intake chamber 62 and an exhaust chamber 64. Specifically, when the compressor 1 is running, low-pressure refrigerant is drawn into the compression chamber 26. Since the moving disc 24 can rotate relative to the stationary disc assembly 22 to compress the refrigerant in the compression chamber 26, when the pressure of the compressed refrigerant reaches the exhaust pressure, the high-pressure refrigerant is discharged from the exhaust port on the stationary disc 224 into the exhaust chamber 64. That is, the exhaust chamber 64 is the high-pressure chamber, and the intake chamber 62 is the low-pressure chamber.

[0123] Furthermore, the floating assembly 30 moves towards the side where the separating assembly 10 is located until it reaches the first position. At this point, the first seal 42 abuts against the sealing portion 142 of the wear-resistant block 14, and the floating assembly 30 and the groove wall of the floating groove 222 enclose and form a back pressure chamber 50. Since the back pressure chamber 50 is connected to the compression chamber 26, a medium pressure can be introduced into the back pressure chamber 50 during the operation of the compressor 1. Under the action of the medium pressure, a certain axial force can be applied to the stationary disc assembly 22 to ensure the sealing between the stationary disc 224 and the moving disc 24.

[0124] Because a second seal 16 is provided between the wear-resistant block 14 and the partition plate 12, the sealing performance between the wear-resistant block 14 and the partition plate 12 can be effectively improved. When the first seal 42 abuts against the sealing part 142, the sealing part 142 can be effectively sealed on both sides of the axial direction, further improving the sealing effect between high and low pressure. This significantly improves the problem of poor sealing between high and low pressure caused by factors such as the ring welding of the partition plate 12 and the riveting of the wear-resistant sheet in related technologies, reduces the leakage of high-pressure refrigerant, and helps to improve the capacity and energy efficiency of the compressor 1.

[0125] Optionally, the second seal 16 includes a sealing ring or sealant.

[0126] like Figure 1 and Figure 2 As shown, in some embodiments, optionally, the sealing part 142 is provided with a sealing groove 144 on the side away from the pump body structure 20, and at least a portion of the second sealing member 16 is located in the sealing groove 144 and abuts against the side of the partition plate 12 facing the pump body structure 20.

[0127] In this embodiment, since a sealing groove 144 is provided on the side of the sealing part 142 away from the pump body structure 20, at least a portion of the second sealing element 16 is embedded in the sealing groove 144, thereby improving the sealing effect between high and low pressure. This significantly improves the problem of poor sealing between high and low pressure caused by factors such as the circumferential welding of the partition plate 12 and the riveting of the wear-resistant sheet in related technologies. While reducing high-pressure refrigerant leakage, it can also limit the second sealing element 16, which is beneficial to improving the installation stability of the second sealing element 16 and ensuring a reliable seal between the partition plate 12 and the wear-resistant block 14.

[0128] Furthermore, since a sealing groove 144 is provided on the side of the sealing part 142 away from the pump body structure 20, the second sealing element 16 can be reliably installed while the side of the sealing part 142 away from the pump body structure 20 can be tightly fitted with the partition plate 12, thereby forming a multi-seal structure between the sealing part 142 and the partition plate 12, which is beneficial to further improve the sealing effect between high and low pressure.

[0129] like Figure 1 As shown, in some embodiments, optionally, the partition plate 12 is provided with mounting holes 122, and the wear-resistant block 14 also includes a mounting part 146. Along the axial direction of the moving plate 24, the mounting part 146 is located on the side of the sealing part 142 away from the pump body structure 20. The mounting part 146 is inserted into the mounting hole 122 and connected to the partition plate 12.

[0130] In this embodiment, the wear-resistant block 14 is further defined as including a mounting part 146. Specifically, along the axial direction of the moving disk 24, the mounting part 146 is disposed on the side of the sealing part 142 away from the pump body structure 20, and the mounting part 146 is inserted into the mounting hole 122 and connected to the partition plate 12, thereby realizing the fixed connection between the wear-resistant block 14 and the partition plate 12.

[0131] Optionally, the mounting part 146 is interference-fitted with the wall of the mounting hole 122 to connect the mounting part 146 to the partition plate 12. That is, the wear-resistant block 14 and the partition plate 12 are connected by an interference fit, which can effectively reduce the deformation of the partition plate 12 and the wear-resistant block 14 due to the installation process while ensuring reliable assembly between the wear-resistant block 14 and the partition plate 12. This is beneficial to further improve the sealing effect between the partition plate 12 and the wear-resistant block 14, as well as between the wear-resistant block 14 and the floating assembly 30, thereby improving the energy efficiency of the compressor 1.

[0132] like Figure 2 As shown, in some embodiments, optionally, the thickness of the sealing portion 142 along the axial direction of the moving disk 24 is t3, wherein t3 ≥ 3 mm.

[0133] In this embodiment, since the axial thickness of the sealing part 142 is greater than or equal to 3mm, it is understood that the thickness of the wear-resistant sheet in the related art is relatively thin, generally around 1mm. That is to say, by setting the axial thickness of the sealing part 142 that abuts against the first sealing member 42 to be relatively thick, the overall structural strength of the sealing part 142 and the wear-resistant block 14 can be significantly improved, the deformation of the sealing part 142 can be reduced, the sealing effect between the wear-resistant block 14 and the partition plate 12 and between the wear-resistant block 14 and the floating assembly 30 can be improved, ensuring effective sealing between high and low pressure, reducing leakage of high-pressure refrigerant, improving the energy efficiency of the compressor 1, and at the same time, it is also beneficial to extend the service life of the wear-resistant block 14.

[0134] like Figure 1 and Figure 2 As shown, in some embodiments, the floating assembly 30 may optionally include a second float plate 36 and a third seal 38, wherein the second float plate 36 is disposed on the first float plate 34 along the axial direction of the moving disk 24, and the second float plate 36 is located on the side of the first float plate 34 away from the separating assembly 10; the third seal 38 is disposed between the first float plate 34 and the second float plate 36 along the radial direction of the moving disk 24, and both ends of the third seal 38 abut against the groove wall of the floating groove 222.

[0135] In this embodiment, the floating assembly 30 further includes a second float 36 and a third seal 38. The second float 36 is connected to the first float 34, and a portion of the second float 36 is located on the side of the first float 34 near the compression chamber 26. The third seal 38 is disposed between the first float 34 and the second float 36, and both ends of the third seal 38 in the radial direction of the moving disc 24 abut against the groove wall of the floating groove 222, thereby ensuring the sealing of the back pressure chamber 50.

[0136] Optionally, the third seal 38 includes a sealing cup, or the third seal 38 includes two radially distributed sealing rings. The specific configuration can be adjusted according to actual needs.

[0137] Optionally, the partition plate 12 is provided with mounting holes, and the wear-resistant block 14 includes a mounting part located on the side of the sealing part away from the pump body structure. The mounting part is inserted into the mounting hole, and the mounting part is interference-fitted with the wall of the mounting hole. That is, the outer wall of the mounting part is interference-fitted with the wall of the mounting hole. In other words, the wear-resistant block 14 and the partition plate 12 are connected by an interference fit. This allows for reliable assembly between the wear-resistant block 14 and the partition plate 12, while effectively reducing the deformation of the partition plate 12 and the wear-resistant block 14 during the installation process. This avoids the problem of poor sealing between high and low pressure due to the deformation of the wear-resistant block 14, reduces the leakage of high-pressure refrigerant, and improves the energy efficiency of the compressor 1.

[0138] Optionally, the wear-resistant block 14 also includes an exhaust passage, specifically, the exhaust passage is connected to the compression chamber 26. Specifically, during the operation of the compressor 1, when the pressure of the refrigerant compressed in the compression chamber 26 reaches the exhaust pressure, the high-pressure refrigerant flows out of the compression chamber 26 and into the exhaust chamber 64 through the exhaust passage, and is then discharged outside the casing. This improves the sealing effect between the high and low pressures while ensuring reliable exhaust of the compressor 1, thus guaranteeing the capacity of the compressor 1.

[0139] Optionally, the stationary plate assembly 22 also includes an exhaust port, and the stationary plate 224 is provided with an exhaust port. The compression chamber 26 is connected to the exhaust passage via the exhaust port; that is, either the compression chamber 26 or the exhaust passage is connected to the exhaust port. Specifically, during the operation of the compressor 1, when the pressure of the refrigerant compressed in the compression chamber 26 reaches the exhaust pressure, the high-pressure refrigerant flows out of the compression chamber 26 from the exhaust port and flows into the exhaust chamber 64 through the exhaust passage, and is then discharged outside the casing.

[0140] Since the minimum flow area of ​​the exhaust passage is greater than or equal to the flow area of ​​the exhaust port, a reliable seal can be achieved between high and low pressure, reducing high-pressure refrigerant leakage and improving the energy efficiency of compressor 1. At the same time, it helps to reduce the flow resistance of compressor 1 during exhaust, ensuring the exhaust efficiency of compressor 1, and thus ensuring the performance of compressor 1.

[0141] Optionally, the exhaust passage includes a first exhaust section, wherein the first exhaust section includes a first end and a second end that are opposite to each other along the axial direction of the moving disc, and the first end is closer to the pump body structure than the second end, that is, the first end is the lower end and the second end is the upper end.

[0142] The radial width of the first end is greater than or equal to the radial width of the second end. When the radial width of the first end is greater than that of the second end, the first exhaust section is formed into a trumpet-shaped structure with a flared lower end. This guides the exhaust airflow when the compressor 1 discharges, reducing the exhaust airflow from flowing to both sides. This reduces flow resistance, improves exhaust efficiency, and further reduces high-pressure refrigerant leakage, thus enhancing the capacity and energy efficiency of the compressor 1. Furthermore, when the radial width of the first end is equal to that of the second end, the first exhaust section is a straight section, which reduces the processing difficulty of the exhaust passage and lowers the manufacturing cost of the compressor 1.

[0143] According to a second aspect of the present invention, a refrigeration device is provided, including a compressor 1 as provided in any of the above embodiments, and thus possesses all the beneficial technical effects of the compressor 1, which will not be repeated here.

[0144] Alternatively, the refrigeration equipment may include air conditioners, refrigerators, or freezers.

[0145] Optionally, the compressor 1 includes a separating assembly 10, a pump body structure 20, a floating assembly 30, and a sealing assembly 40. Specifically, the pump body structure 20 includes a stationary disc assembly 22 and a moving disc 24, which form a compression chamber 26. A floating groove 222 is provided on the side of the stationary disc assembly 22 facing away from the moving disc 24, and the floating assembly 30 is movably disposed in the floating groove 222. Optionally, the stationary disc assembly 22 includes a stationary disc 224 and a back pressure plate 226, wherein the stationary disc 224 and the moving disc 24 form the compression chamber 26, and the back pressure plate 226 is disposed on the side of the stationary disc 224 facing away from the moving disc 24, with a portion of the back pressure plate 226 and a portion of the stationary disc 224 forming the floating groove 222.

[0146] Specifically, the floating component 30 can move between a first position and a second position. When the compressor 1 is running, the floating component 30 moves towards the side where the separating component 10 is located until it reaches the first position. At this time, the floating component 30 and the wall of the floating groove 222 enclose a back pressure chamber 50. Since the back pressure chamber 50 is connected to the compression chamber 26, a medium pressure can be introduced into the back pressure chamber 50 during the operation of the compressor 1. Under the action of the medium pressure, a certain axial force can be applied to the stationary plate assembly 22 to ensure the sealing between the stationary plate 224 and the moving plate 24. At the same time, since the moving plate 24 can rotate relative to the stationary plate assembly 22 to compress the refrigerant in the compression chamber 26, when the pressure of the compressed refrigerant reaches the discharge pressure, the high-pressure refrigerant is discharged from the exhaust port on the stationary plate 224. Since the first seal 42 abuts against the separating component 10, a seal can be achieved between the high-pressure chamber (exhaust chamber 64) and the low-pressure chamber (suction chamber 62).

[0147] When the compressor 1 stops running, the floating component 30 moves to the side away from the partition component 10 until it moves to the second position. At this time, since the first seal 42 is separated from the partition component 10, the high-pressure chamber and the low-pressure chamber are connected.

[0148] Since the elastic element 44 is located on the side of the first seal 42 away from the partition assembly 10, and the elastic element 44 is in a compressed state when the first seal 42 abuts against the partition assembly 10, that is, the elastic element 44 can apply an axial elastic force to the first seal 42 toward the partition assembly 10, i.e., an axially upward elastic force. This elastic force can increase the clamping force between the first seal 42 and the partition assembly 10, so that the first seal 42 and the partition assembly 10 can fit tightly in the axial direction, ensuring the axial seal between the first seal 42 and the partition assembly 10.

[0149] Furthermore, since the floating component 30 has a groove 32 on the side facing the separating component 10, and at least a portion of the sealing component 40 is located within the groove 32. Optionally, at least a portion of the first sealing member 42 and the elastic member 44 are located within the groove 32, or the elastic member 44 is located within the groove 32. The specific configuration can be adjusted according to actual needs.

[0150] It is understood that the radially inner side of the position where the first seal 42 abuts against the separator assembly 10 is under high pressure, and the radially outer side is under low pressure. Thus, under the action of the internal and external pressure difference, radial sealing can be achieved between the first seal 42 and the separator assembly 10. That is, by setting the first seal 42 and the elastic element 44, axial sealing and radial sealing can be achieved simultaneously, significantly improving the sealing performance between the separator assembly 10 and the floating assembly 30, achieving effective sealing between high and low pressure, reducing leakage of high-pressure refrigerant, and thus helping to improve the capacity and energy efficiency of the compressor 1.

[0151] Moreover, since at least a portion of the sealing component 40 is located within the groove 32, the sealing component 40 located within the groove 32 can be limited. During the movement of the floating component 30 relative to the floating groove 222 between the first and second positions, the sealing component 40 can be prevented from shifting, thereby ensuring that the floating component 30 and the separating component 10 always maintain a reliable seal, which is beneficial to improving the reliability of the compressor 1.

[0152] Optionally, the elastic element 44 includes a spring or an elastic washer. The spring may be a wave spring.

[0153] In the description of this specification, the terms "connection," "installation," and "fixing," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0154] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0155] The above are merely preferred embodiments of this utility model and are not intended to limit the scope of this utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A compressor, characterized in that, include: Separator component; The pump body structure includes a stationary disc assembly and a moving disc, the stationary disc assembly and the moving disc forming a compression chamber, and a floating groove provided on the side of the stationary disc assembly opposite to the moving disc; A floating component is movably disposed in the floating groove, and the floating component has a groove on the side facing the separating component; A sealing assembly, at least a portion of which is located within the groove, the sealing assembly including a first seal and an elastic element, along the axial direction of the moving disc, the elastic element being located on the side of the first seal opposite to the separating assembly; Wherein, based on the movement of the floating component to the first position, the first sealing member abuts against the separating component, the elastic member is in a compressed state, the floating component and the groove wall of the floating groove enclose to form a back pressure cavity, and the back pressure cavity is connected to the compression cavity.

2. The compressor according to claim 1, characterized in that, The first seal includes a first surface and a second surface that are radially opposite to the moving disk, wherein the first surface is closer to the central axis of the moving disk than the second surface; Part of the first surface is exposed outside the groove.

3. The compressor according to claim 2, characterized in that, The floating component includes a first float plate, the first float plate comprising: plate body; The first protrusion and the second protrusion are respectively disposed on the side of the plate facing the separating component and are arranged radially spaced along the moving disk. The first protrusion is located inside the second protrusion. The first protrusion, the second protrusion and the plate together form the groove. Along the axial direction of the moving disk, the height of the first protrusion is lower than the height of the second protrusion.

4. The compressor according to claim 3, characterized in that, Along the axial direction of the moving disk, the height of the first protrusion is h1, and the height of the second protrusion is h2, wherein 0.5mm≤h2-h1≤2mm.

5. The compressor according to claim 3, characterized in that, As the floating component moves to the first position, the end face of the second protrusion facing away from the plate body fits against the side of the separating component facing the pump body structure.

6. The compressor according to claim 3, characterized in that, Along the axial direction of the moving disc, the height of the second protrusion is h2, the height of the elastic element in its natural state is h3, and the thickness of the first seal is t1, wherein h2≤t1+0.8×h3.

7. The compressor according to claim 3, characterized in that, Along the axial direction of the moving disc, the height of the second protrusion is h2, the thickness of the first seal is t1, and the thickness of the elastic element is t2, wherein h2≥t1+2×t2.

8. The compressor according to claim 3, characterized in that, Along the axial direction of the moving disc, the height of the first protrusion is h1, the height of the elastic element in its natural state is h3, and the thickness of the first seal is t1, wherein h1 ≥ t1 / 2 + h3.

9. The compressor according to any one of claims 1 to 8, characterized in that, The first sealing element includes a flexible element.

10. The compressor according to any one of claims 1 to 8, characterized in that, The first seal is cross-sectioned along the axial direction of the moving disc, and the cross-sectional shape of the first seal is rectangular; and / or the first seal includes a sealing ring.

11. The compressor according to any one of claims 1 to 8, characterized in that, The first seal includes a bevel, a first end, and a second end, the first end and the second end being arranged circumferentially along the first seal and being separable, the bevel being disposed at at least one of the first end and the second end, the bevel extending obliquely relative to the axial direction of the moving disc.

12. The compressor according to claim 11, characterized in that, The angle between the plane containing the inclined plane and the horizontal plane is θ, where 30°≤θ≤60°.

13. The compressor according to claim 11, characterized in that, The number of inclined surfaces is two, including a first inclined surface and a second inclined surface. The first inclined surface is located at the first end, and the second inclined surface is located at the second end. In this configuration, at least a portion of the first inclined surface is disposed opposite to at least a portion of the second inclined surface.

14. The compressor according to claim 13, characterized in that, The first seal includes: The body has a first end and a second end located at opposite ends of the first sealing member along its circumference. The first end has a first notch at the end furthest from the body, forming the first inclined surface. The second end has a second notch at the end furthest from the body, forming the second inclined surface. Wherein, at least a portion of the second end is located within the first notch, and at least a portion of the first end is located within the second notch.

15. The compressor according to any one of claims 1 to 8, characterized in that, The compressor also includes a housing, and the partition assembly includes: A partition plate is disposed inside the housing and divides the housing into an intake chamber and an exhaust chamber. The pump body structure is disposed in the intake chamber, and the compression chamber can communicate with the exhaust chamber. A wear-resistant block, connected to the partition plate, the wear-resistant block including a sealing part, the sealing part being located on the side of the partition plate facing the pump body structure, based on the movement of the floating assembly to the first position, the first seal abuts against the sealing part; The second seal is disposed between the wear-resistant block and the partition plate.

16. The compressor according to claim 15, characterized in that, The sealing part has a sealing groove on the side away from the pump body structure, and at least a portion of the second sealing element is located in the sealing groove and abuts against the side of the partition plate facing the pump body structure.

17. The compressor according to claim 15, characterized in that, The partition plate is provided with mounting holes, and the wear-resistant block further includes: The mounting part is located along the axial direction of the moving disc, on the side of the sealing part away from the pump body structure, the mounting part is inserted into the mounting hole and connected to the partition plate.

18. The compressor according to claim 15, characterized in that, Along the axial direction of the moving disc, the thickness of the sealing part is t3, where t3 ≥ 3 mm.

19. The compressor according to any one of claims 3 to 8, characterized in that, The floating component also includes: A second float plate is disposed on the first float plate along the axial direction of the moving disk, and the second float plate is located on the side of the first float plate opposite to the separating assembly; A third sealing element is disposed between the first float and the second float, along the radial direction of the moving disc, with both ends of the third sealing element abutting against the wall of the floating groove.

20. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 19.

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