Bearing assembly, compressor and refrigeration equipment

Abstract

The utility model provides a bearing assembly, a compressor and refrigeration equipment. The bearing assembly comprises a bearing, a first valve plate, a second valve plate, a gasket and a limiter; the bearing is provided with a first exhaust hole; the first valve plate comprises a first connecting part and a first covering part, the first connecting part is connected with the bearing, and the first covering part is connected with the first connecting part and covers the first exhaust hole; the second valve plate comprises a second connecting part and a second covering part, the second connecting part is arranged on the side, away from the bearing, of the first connecting part, the second covering part is connected with the second connecting part, the gasket is arranged between the first connecting part and the second connecting part, and a gap is formed between the first covering part and the second covering part; the limiter is arranged on the side, away from the first valve plate, of the second valve plate. Wherein the thickness of the first valve plate is a first thickness, the thickness of the second valve plate is a second thickness, and the first thickness is smaller than or equal to the second thickness. The first valve plate is matched with the second valve plate, and vibration and noise in the exhaust process of the compressor are reduced.

Description

Technical Field

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

[0002] Currently, in related technologies, refrigeration equipment is equipped with variable frequency compressors. When the variable frequency compressor operates at high speed, the pressure difference inside and outside the compression chamber is large, and the refrigerant flow through the exhaust port is high, which puts great force on the exhaust valve plate. Therefore, the exhaust valve plate needs high rigidity to ensure that the valve plate can close in time and prevent high-temperature and high-pressure refrigerant from flowing back into the pump body suction chamber through the exhaust port. However, when the variable frequency compressor operates at low speed, the pressure difference inside and outside the compression chamber is small, and the refrigerant flow through the exhaust port is small. The valve plate will repeatedly open and close, and the valve plate will repeatedly strike the valve seat, increasing the vibration and noise of the compressor. Utility Model Content

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art or related technologies.

[0004] Therefore, the first aspect of this utility model proposes a bearing assembly.

[0005] The second aspect of this utility model provides a compressor.

[0006] The third aspect of this utility model proposes a refrigeration device.

[0007] In view of the above, a first aspect of the present invention provides a bearing assembly, including a bearing, a first valve plate, a second valve plate, a gasket, and a limiter; the bearing is provided with a first vent hole; the first valve plate includes a first connecting portion and a first covering portion, the first connecting portion being connected to the bearing, the first covering portion being connected to the first connecting portion and covering the first vent hole; the second valve plate includes a second connecting portion and a second covering portion, the second connecting portion being disposed on the side of the first connecting portion away from the bearing, the second covering portion being connected to the second connecting portion, the gasket being disposed between the first connecting portion and the second connecting portion, and a gap being formed between the first covering portion and the second covering portion; the limiter being disposed on the side of the second valve plate away from the first valve plate; wherein, the thickness of the first valve plate is a first thickness, the thickness of the second valve plate is a second thickness, and the first thickness is less than or equal to the second thickness.

[0008] The bearing assembly provided in this application includes a bearing for supporting a rotating shaft, thereby ensuring the stability of a compressor equipped with the bearing assembly during operation. The bearing has a first exhaust port. The bearing assembly also includes a first valve plate and a second valve plate. A first connecting portion is connected to the bearing, and a first covering portion is connected to the first connecting portion and covers the first exhaust port. The second valve plate includes a second connecting portion and a second covering portion. The second connecting portion is located on the side of the first connecting portion away from the bearing, and the second covering portion is connected to the second connecting portion. Thus, the first exhaust port is controlled by the first valve plate and the second valve plate. The bearing assembly also includes a gasket disposed between the first connecting part and the second connecting part, creating a gap between the first covering part and the second covering part. When the compressor operates at a low speed, the pressure inside the exhaust port is higher than the pressure outside the exhaust port, but the pressure difference between the inside and outside of the exhaust port is small. The first valve plate moves away from the exhaust port, opening the first exhaust port and thus achieving exhaust. When the compressor operates at a high speed, the pressure inside the exhaust port is higher than the pressure outside the exhaust port, and the pressure difference between the inside and outside of the exhaust port is large. The first valve plate and the second valve plate move away from the exhaust port, opening the first exhaust port and thus achieving exhaust. Because the thickness of the first valve plate is less than that of the second valve plate, the stiffness of the first valve plate is lower. Even when the compressor operates at a low speed and the pressure difference between the inside and outside of the compression chamber is small, the first valve plate can maintain a certain opening, reducing the probability of the first valve plate repeatedly opening and closing, thereby reducing the impact of the first valve plate on the bearing and reducing vibration and noise during the compressor's exhaust process. When the compressor is running at a low speed, when the first cover moves a certain displacement away from the exhaust port, the probability of the first cover and the second cover coming into contact is small due to the gap between them. This reduces the probability of vibration and noise caused by the first cover hitting the second cover, and further reduces the vibration and noise of the compressor when running at low frequency.

[0009] Because the thickness of the first valve plate is less than that of the second valve plate, the stiffness of the first valve plate is lower, which reduces the pressure required for the first valve plate to open, reduces energy loss during exhaust from the compression chamber, and improves the exhaust efficiency of the compressor.

[0010] When the compressor operates at high speed, the first and second valve plates move together, increasing the rigidity of the valve plate controlling the exhaust port. This, in turn, enhances the fatigue resistance of both valve plates, extends their service life, and improves the stability of the compressor during operation. Furthermore, the coordinated movement of the first and second valve plates increases the rigidity of the valve plate controlling the exhaust port. At the moment exhaust begins, the first and second valve plates will not rapidly impact the limit switch. While reducing the movement speed of the first and second valve plates, even if the second valve plate does collide with the limit switch, the resulting vibration and noise are minimized, further reducing compressor vibration and noise during high-frequency operation.

[0011] The first valve plate works in conjunction with the second valve plate to control the first exhaust port, enabling the first exhaust port to be switched to a closed state more quickly when the compressor is not discharging, thereby reducing the probability of high-temperature and high-pressure refrigerant backflow and improving the compressor's energy efficiency.

[0012] In some technical solutions of this utility model, optionally, the first thickness is greater than or equal to 0.2 mm and less than or equal to 0.31 mm.

[0013] In this technical solution, the first thickness is greater than or equal to 0.2 mm and less than or equal to 0.31 mm, which not only ensures the fatigue resistance of the first valve plate, but also reduces the stiffness of the first valve plate. This allows the first valve plate to maintain the exhaust state continuously when the compressor is running at low speed, reducing the frequency of opening and closing of the first valve plate and reducing the vibration and noise of the compressor.

[0014] In some technical solutions of this utility model, optionally, the ratio of the second thickness to the first thickness is greater than or equal to 1 and less than or equal to 2.1.

[0015] In this technical solution, the ratio of the second thickness to the first thickness is greater than or equal to 1 and less than or equal to 2.1, which gives the second valve plate greater rigidity and the first valve plate less rigidity. The first and second valve plates can work together better to reduce vibration and noise during low-frequency and high-frequency operation of the compressor, while improving the energy efficiency of the compressor and enhancing its reliability during operation.

[0016] In some technical solutions of this utility model, optionally, the thickness of the gasket is a third thickness, and the first thickness is less than the third thickness.

[0017] In this technical solution, the thickness of the gasket is the third thickness, and the first thickness is less than the third thickness. That is, the thickness of the first valve plate is less than the thickness of the gasket, which allows the first valve plate to have a larger movement space. When the compressor is running at low frequency, the number of collisions between the first valve plate and the first exhaust port of the bearing is reduced in each working cycle, further reducing the vibration and noise of the compressor during low-frequency operation.

[0018] In some technical solutions of this utility model, optionally, the ratio of the third thickness to the first thickness is greater than or equal to 1.4 and less than or equal to 2.6.

[0019] In this technical solution, the ratio of the third thickness to the first thickness is greater than or equal to 1.4 and less than or equal to 2.6. When the compressor is running at low frequency, the first valve plate has more room to move, thereby reducing the number of collisions between the first valve plate and the first exhaust port of the bearing in each working cycle. When the compressor is running at high frequency, the first valve plate can contact the second valve plate in time, so that the first valve plate and the second valve plate work together, reducing the probability of the first valve plate being crushed by the high-pressure refrigerant due to its low rigidity, thereby improving the stability of the first valve plate in the compressor exhaust process.

[0020] In some technical solutions of this utility model, optionally, the limiter includes a third connecting part and a limiting part; the third connecting part is in contact with the second valve plate; the first end of the limiting part is connected to the third connecting part, and the second end of the limiting part extends away from the second valve plate; wherein, in the axial direction of the bearing, when the first covering part moves away from the first exhaust hole to a position contacting the second covering part, the rising height of the first covering part is the first height; in the axial direction of the bearing, when the second covering part moves away from the first exhaust hole to a position contacting the limiter, the rising height of the second covering part is the second height; the ratio of the second height to the first height is greater than or equal to 3.3 and less than or equal to 7.2.

[0021] In this technical solution, the limiter includes a third connecting part, which fits against the second valve plate to achieve installation and fixation of the limiter, improving its stability during operation. The limiter also includes a limiting part, the first end of which connects to the third connecting part, and the second end of which extends away from the second valve plate. When the second valve plate moves away from the first exhaust port, it can contact the limiting part, thereby supporting the second valve plate and limiting its movement. This reduces the probability of permanent deformation of the second valve plate under pressure, improving the stability of its movement. The ratio of the rising height of the second cover to the rising height of the first cover is greater than or equal to 3.3 and less than or equal to 7.2, resulting in less vibration and noise generated when the first and second valve plates work together. This reduces vibration and noise in the compressor during low-frequency and high-frequency operation, improving compressor quality.

[0022] In some technical solutions of this utility model, optionally, the length of the third connecting part is the first length; the length of the gasket is the second length; the ratio of the first length to the second length is greater than or equal to 0.8 and less than or equal to 1.3.

[0023] In this technical solution, the third connecting part cooperates with the gasket to constrain the fixed area of ​​the first valve plate, that is, to constrain the first connecting part, thereby limiting the effective working length of the first valve plate. The ratio of the length of the third connecting part to the length of the gasket is greater than or equal to 0.8 and less than or equal to 1.3, which gives the first valve plate a more reasonable effective working length, thereby enabling the first valve plate to open or close the first exhaust port according to the exhaust needs of the first exhaust port, improving the smoothness of the compressor exhaust process.

[0024] In some technical solutions of this utility model, optionally, the length of the gasket is the second length; the center distance of the limiter is the third length; the ratio of the second length to the third length is greater than or equal to 0.25 and less than or equal to 0.4.

[0025] In this technical solution, the ratio of the length of the gasket to the center distance of the limiter is greater than or equal to 0.25 and less than or equal to 0.4, thereby more effectively controlling the vibration and noise generated by the first valve plate striking the bearing when the compressor is running at ultra-low frequency.

[0026] Optionally, in some technical solutions of this utility model, the first valve plate further includes a transition portion, the first end of the transition portion is connected to the first connecting portion, the second end of the transition portion is connected to the first covering portion, and the transition portion is provided with a first groove, which extends from the end of the transition portion near the first connecting portion to the end of the transition portion near the first covering portion.

[0027] In this technical solution, the first valve plate also includes a transition portion. A first end of the transition portion is connected to a first connecting portion, and a second end of the transition portion is connected to a first covering portion. This allows the first covering portion to move relative to the first connecting portion via the transition portion, improving the stability of the first valve plate during the compressor's exhaust process. The transition portion is provided with a first groove extending from one end of the transition portion near the first connecting portion to the other end near the first covering portion. This groove ensures a minimum thickness for the first valve plate while reducing its rigidity, thereby ensuring the fatigue resistance of the first valve plate and extending its service life.

[0028] In some technical solutions of this utility model, optionally, the center distance of the limiter is the third length; the length of the first groove is the fourth length; the ratio of the fourth length to the third length is greater than or equal to 0.1 and less than or equal to 0.75.

[0029] In this technical solution, the ratio of the length of the first groove to the center distance of the limiter is greater than or equal to 0.1 and less than or equal to 0.75. This optimizes the size of the first groove, ensuring that the first valve plate has a certain thickness while reducing the rigidity of the first valve plate, further ensuring the fatigue resistance of the first valve plate and extending its service life.

[0030] In some technical solutions of this utility model, optionally, the width of the transition portion is a first width; the width of the first groove is a second width; and the ratio of the second width to the first width is less than or equal to 0.5.

[0031] In this technical solution, the ratio of the width of the first groove to the width of the transition section is less than or equal to 0.5, which optimizes the size of the first groove. While ensuring that the first valve plate has a certain thickness, the rigidity of the first valve plate is reduced, further ensuring the fatigue resistance of the first valve plate and extending the service life of the first valve plate.

[0032] In some technical solutions of this utility model, optionally, the diameter of the second cover is the first diameter; the second cover is provided with a second vent hole, the diameter of the second vent hole is the second diameter; the ratio of the second diameter to the first diameter is greater than or equal to 0.15 and less than or equal to 0.67.

[0033] In this technical solution, during the compressor's discharge process, the second cover is provided with a second vent hole. The refrigerant passing through the first valve plate can continue to move away from the compression chamber through the second vent hole, reducing the resistance of the second valve plate to the refrigerant and improving the compressor's discharge efficiency and smoothness. At the end of the compressor's discharge process, the second cover, with its second vent hole, allows the first and second valve plates to separate and reset more smoothly, reducing the probability of adhesion between them due to refrigerant oil. This also allows the first vent hole to be sealed more promptly, further improving the stability of the compressor's discharge process. The ratio of the diameter of the second vent hole to the diameter of the second cover is greater than or equal to 0.15 and less than or equal to 0.67, ensuring both smooth compressor discharge and sufficient strength for the second cover, thereby improving its reliability.

[0034] Optionally, in some technical solutions of this utility model, the bearing assembly further includes a connector, which passes through the limiter, the second valve plate, the gasket and the first valve plate, and is connected to the bearing.

[0035] In this technical solution, the bearing assembly also includes a connector, which passes through the limiter, the second valve plate, the gasket, and the first valve plate, and is connected to the bearing. The connector enables the installation and fixation of the limiter, the second valve plate, the gasket, and the first valve plate, thereby improving the stability of the limiter, the second valve plate, the gasket, and the first valve plate during the operation of the compressor.

[0036] The second aspect of this utility model provides a compressor that includes a bearing assembly as described in any of the above technical solutions, and thus the compressor possesses all the beneficial effects of the bearing assembly as described in any of the above technical solutions.

[0037] Specifically, the compressor is a variable frequency compressor.

[0038] The compressor can be a single-cylinder, twin-cylinder, or multi-cylinder compressor.

[0039] The third aspect of this utility model provides a refrigeration device, including a bearing assembly as described in any of the above technical solutions, or a compressor as described in any of the above technical solutions. Therefore, the refrigeration device has all the beneficial effects of the bearing assembly as described in any of the above technical solutions or the compressor as described in any of the above technical solutions.

[0040] Specifically, the refrigeration equipment includes refrigerators, air conditioners, freezers, or display cases.

[0041] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0042] 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:

[0043] Figure 1 An exploded view of a valve plate assembly according to an embodiment of the present invention;

[0044] Figure 2 An exploded view of a bearing assembly according to an embodiment of the present invention;

[0045] Figure 3 This is a schematic diagram of the noise spectrum obtained by testing a compressor operating at ultra-low frequency according to an embodiment of the present invention.

[0046] Figure 4 This is a schematic diagram of the structure of a valve plate assembly according to an embodiment of the present invention;

[0047] Figure 5 This is a schematic diagram of the structure of the first valve plate of a valve plate assembly according to an embodiment of the present invention;

[0048] Figure 6 This is a schematic diagram of the structure of the second valve plate of a valve plate assembly according to an embodiment of the present invention;

[0049] Figure 7 This is a partial schematic diagram of a bearing assembly according to an embodiment of the present invention;

[0050] Figure 8 This is a schematic diagram of the mode shape of the first-order bending natural frequency of the second valve plate according to an embodiment of the present invention;

[0051] Figure 9 This is a schematic diagram of the mode shape of the first bending natural frequency of the first valve plate according to an embodiment of the present invention.

[0052] in, Figures 1 to 9 The correspondence between the reference numerals and component names in the attached drawings is as follows:

[0053] 100 Bearing, 110 First vent, 200 First valve plate, 210 First connecting part, 220 First cover part, 230 Transition part, 232 First groove, 300 Second valve plate, 310 Second connecting part, 320 Second cover part, 322 Second vent, 330 Gap, 400 Gasket, 500 Limiter, 510 Third connecting part, 520 Limiter part, 600 Connector. Detailed Implementation

[0054] 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.

[0055] 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.

[0056] The following reference Figures 1 to 9 This invention describes bearing assemblies, compressors, and refrigeration equipment according to some embodiments of the present invention.

[0057] In one embodiment of this utility model, such as Figure 1 and Figure 2 As shown, a bearing assembly is provided, including a bearing 100, a first valve plate 200, a second valve plate 300, a gasket 400, and a limiter 500; the bearing 100 is provided with a first vent hole 110; the first valve plate 200 includes a first connecting portion 210 and a first covering portion 220, the first connecting portion 210 being connected to the bearing 100, and the first covering portion 220 being connected to the first connecting portion 210 and covering the first vent hole 110; the second valve plate 300 includes a second connecting portion 310 and a second covering portion 320, the second connecting portion 310 being provided with a first vent hole 110; the second valve plate 300 includes a second connecting portion 310 and a second covering portion 320, the second connecting portion 310 being provided with a first vent hole 110; the first valve plate 200 includes a second connecting portion 310 and a second covering portion 320, the second connecting portion 310 being provided with a first vent hole 110; the second valve plate 3 ... On the side of the first connecting portion 210 away from the bearing 100, the second covering portion 320 is connected to the second connecting portion 310, the gasket 400 is disposed between the first connecting portion 210 and the second connecting portion 310, and there is a gap 330 between the first covering portion 220 and the second covering portion 320; the limiter 500 is disposed on the side of the second valve plate 300 away from the first valve plate 200; wherein, the thickness of the first valve plate 200 is a first thickness T1, the thickness of the second valve plate 300 is a second thickness T2, and the first thickness T1 is less than or equal to the second thickness T2.

[0058] In this embodiment, the bearing assembly includes a bearing 100, which supports the rotating shaft, thereby ensuring the stability of the compressor equipped with the bearing assembly during operation. The bearing 100 is provided with a first exhaust port 110. The bearing assembly also includes a first valve plate 200 and a second valve plate 300. A first connecting portion 210 is connected to the bearing 100, and a first covering portion 220 is connected to the first connecting portion 210 and covers the first exhaust port 110. The second valve plate 300 includes a second connecting portion 310 and a second covering portion 320. The second connecting portion 310 is located on the side of the first connecting portion 210 away from the bearing 100, and the second covering portion 320 is connected to the second connecting portion 310. Thus, the first exhaust port 110 is controlled by the first valve plate 200 and the second valve plate 300. The bearing assembly also includes a gasket 400, which is disposed between the first connecting portion 210 and the second connecting portion 310, creating a gap 330 between the first covering portion 220 and the second covering portion 320. When the compressor operates at a lower speed, the pressure inside the exhaust port is higher than the pressure outside the exhaust port, but the pressure difference between the inside and outside of the exhaust port is small. The first valve plate 200 moves away from the exhaust port, opening the first exhaust port 110 and thus achieving exhaust. When the compressor operates at a higher speed, the pressure inside the exhaust port is higher than the pressure outside the exhaust port, and the pressure difference between the inside and outside of the exhaust port is small. The first valve plate 200 and the second valve plate 300 move away from the exhaust port, opening the first exhaust port 110 and thus achieving exhaust. Because the thickness of the first valve plate 200 is less than that of the second valve plate 300, the first valve plate 200 has lower rigidity. Even when the compressor is running at low speed and the pressure difference inside and outside the compression chamber is small, the first valve plate 200 can maintain a certain opening degree, reducing the probability of repeated opening and closing of the first valve plate 200, thereby reducing the impact of the first valve plate 200 on the bearing 100 and reducing vibration and noise during the compressor's exhaust process. When the compressor is running at a lower speed, when the first cover 220 moves a certain displacement away from the exhaust port, because there is a gap 330 between the first cover 220 and the second cover 320, the probability of contact between the first cover 220 and the second cover 320 is small, thus reducing the probability of vibration and noise caused by the first cover 220 impacting the second cover 320, further reducing vibration and noise of the compressor during low-frequency operation.

[0059] Because the thickness of the first valve plate 200 is less than that of the second valve plate 300, the rigidity of the first valve plate 200 is lower, which reduces the pressure required for the first valve plate 200 to open, reduces energy loss during exhaust from the compression chamber, and improves the exhaust efficiency of the compressor.

[0060] When the compressor operates at a high speed, the first valve plate 200 and the second valve plate 300 move together, increasing the rigidity of the valve plate controlling the exhaust port. This, in turn, enhances the fatigue resistance of the first and second valve plates 200 and 300, extends their service life, and improves the stability of the compressor during operation. Furthermore, the coordinated movement of the first and second valve plates 200 and 300 increases the rigidity of the valve plate controlling the exhaust port. At the moment exhaust begins, the first and second valve plates 200 and 300 will not rapidly impact the limiter 500. While reducing the movement speed of the first and second valve plates 200 and 300, even if the second valve plate 300 collides with the limiter 500, the vibration and noise generated by this impact are minimal, further reducing the vibration and noise of the compressor during high-frequency operation.

[0061] The first valve plate 200 and the second valve plate 300 work together to control the first exhaust port 110, so that the first exhaust port 110 can be switched to the closed state more quickly when the compressor is not discharging, thereby reducing the probability of high temperature and high pressure refrigerant backflow and improving the energy efficiency of the compressor.

[0062] Specifically, the bearing 100 is provided with a mounting groove, which is connected to the first exhaust port 110. The first exhaust port 110 extends from the bottom wall of the mounting groove into the compression chamber.

[0063] The first valve plate 200, the second valve plate 300, the gasket 400 and the limiter 500 constitute the basic structure of the valve plate assembly. The valve plate assembly is set in the mounting groove, thereby realizing the control of the first exhaust port 110.

[0064] The first valve plate 200, the gasket 400, the second valve plate 300, and the limiter 500 are stacked in sequence.

[0065] Specifically, both the first valve plate 200 and the second valve plate 300 are elastic valve plates.

[0066] Gasket 400 is used to constrain the initial stroke of the first valve plate 200, and limiter 500 is used to constrain the stroke of the second valve plate 300.

[0067] Specifically, different compressor operating frequencies result in significant differences in refrigerant flow rate, velocity, and suction / discharge pressure difference in air conditioning systems. When a variable frequency rotary compressor operates at high speed in an air conditioning system, the pressure difference is large and the flow rate is high, resulting in significant force on the valve plates. This requires high valve plate rigidity and elasticity to ensure timely valve closure and prevent the high-temperature, high-pressure exhaust refrigerant from flowing back into the pump's suction chamber, reducing the compressor's cooling capacity and energy efficiency. However, when the compressor operates at low speed, the air conditioning system load is light, the suction / discharge pressure difference is small, and the exhaust pressure, velocity, and flow rate are all relatively low. At this time, when the valve plate momentarily opens, the pressure inside the compression chamber quickly equals the back pressure of the valve plate assembly, the pressure difference between the inside and outside of the valve plate disappears, and the exhaust flow rate is very small, insufficient to fully open the valve plate. This makes it difficult to maintain the valve plate in an open state for an extended period, causing it to spring back and fall back onto the exhaust port of bearing 100. As compression continues, the pressure in the compression chamber of the cylinder rises again, pushing the valve plate open again, the pressure difference disappears, and it falls back again. This process repeats until exhaust is complete. Experimental results show that when the compressor is running at low frequency, the exhaust valve experiences severe chattering, constantly opening and closing, continuously striking the bearing 100 valve seat, generating resonance noise inside the cylinder and continuous valve plate striking noise, resulting in poor compressor noise quality.

[0068] To solve this problem, simply reducing the stiffness of the valve plate to decrease its own elasticity, such as by reducing the valve plate thickness, would allow the valve plate to open easily even when the pressure difference and flow rate are relatively low. However, reducing the stiffness of the valve plate would introduce several problems during high-frequency operation of the compressor:

[0069] (1) When the compressor is running at high frequency, if the stiffness of the valve plate decreases, the valve plate will quickly impact the limit switch 500 at the moment of opening, which will increase the impact speed between the valve plate and the limit switch 500 and generate greater impact noise.

[0070] (2) When the exhaust ends, the valve plate needs to fall back onto the first exhaust port 110 under its own elastic force to prevent the high-temperature and high-pressure exhaust from flowing back into the pump body suction chamber. Therefore, when the elastic force of the valve plate is small, the valve plate rebound speed is slowed down, resulting in delayed closing, which leads to exhaust backflow, thereby reducing the suction flow rate, resulting in a reduction in cooling capacity, an increase in power consumption, and a decrease in compressor efficiency.

[0071] (3) If the stiffness of the valve plate decreases, the impact force and impact speed between the valve plate and the limiter 500 and the valve seat will increase when the valve plate is opened and closed, respectively. This will increase the stress on the valve plate, increase the risk of fatigue fracture, and affect the overall reliability of the compressor.

[0072] Based on the above analysis, it can be seen that a structural design that only sets one valve plate and reduces the thickness of the valve plate cannot simultaneously meet the needs of low-frequency and high-frequency operation, and cannot meet the requirements of quiet, efficient and high-reliability operation of refrigeration equipment across the wide frequency range.

[0073] This application achieves control of the first exhaust port 110 by cooperating with the first valve plate 200 and the second valve plate 300. The thickness of the first valve plate 200 is less than or equal to the thickness of the second valve plate 300, which can take into account the needs of low-frequency operation and high-frequency operation, and meet the requirements of quiet, high-efficiency and high-reliability operation of refrigeration equipment in the wide frequency range.

[0074] The first valve plate 200 is the lower valve plate, and the second valve plate 300 is the upper valve plate.

[0075] When the compressor operates at ultra-low speed, the refrigeration equipment is under extremely light load, with a small suction and discharge pressure difference. Discharge pressure, flow rate, and velocity are all very low, resulting in early valve assembly opening. Due to the small pressure difference between the inside and outside of the valve assembly, the force is minimal, and the valve assembly lift is very low. At this time, the low-rigidity lower valve plate effectively opens and closes promptly. Furthermore, due to its low stiffness, the lower valve plate can fully open and maintain its maximum lift under these conditions until the end of discharge, preventing severe vibration and avoiding continuous impact noise from the bearing 100 discharge port. This ensures timely opening of the low-rigidity lower valve plate during ultra-low compressor operation, reducing discharge power consumption and improving the energy efficiency of the low-frequency compressor. Simultaneously, it avoids continuous vibration and impact with the bearing 100 discharge port, eliminating abnormal noise. However, it should be noted that due to the small internal and external pressure difference, the maximum lift of the lower valve plate is still lower than the 400mm thickness of the gasket, and it will not contact the upper valve plate; therefore, the upper valve plate is ineffective.

[0076] As the compressor speed gradually increases, the load on the refrigeration equipment increases, the pressure difference between suction and discharge increases, the discharge flow rate increases, and the pressure difference formed inside and outside the valve plate assembly increases. The maximum lift of the lower valve plate begins to exceed the thickness of the gasket (400mm), resulting in a higher lift. The lower valve plate will gradually begin to contact the upper valve plate and push the upper valve plate to produce a certain lift height. At this time, the lower valve plate with low stiffness and the upper valve plate with high stiffness begin to work together. When the compressor is running at medium to high speed, the pressure difference between the inside and outside of the valve plate is large enough. The upper and lower valve plates work together, and both can reach their maximum opening state at the beginning of the exhaust. At the end of the exhaust, due to the superposition effect of the high-rigidity and low-rigidity dual valve plates, the combined stiffness can ensure that the lower valve plate closes in time, preventing the high-temperature and high-pressure exhaust from flowing back into the pump body suction chamber. This reduces the exhaust power consumption during low-frequency operation, improves the energy efficiency of the low-frequency compressor, and reduces the noise of exhaust valve flutter and impact. It also increases the stiffness of the valve plate during high-frequency operation, reduces the speed and force of the upper valve plate impacting the limit switch 500, improves the valve plate life and compressor reliability, and reduces the noise of the high-frequency impacting limit switch 500.

[0077] The compressor employing the bearing assembly provided in this application allows for easier and more timely opening and closing of the lower valve plate during ultra-low speed operation due to the small flow rate and low velocity. The upper valve plate remains inactive, preventing the conventional high-rigidity valve plate from continuously vibrating and striking the bearing 100 (valve seat), reducing lower valve plate striking noise, lowering exhaust power consumption, and improving compressor efficiency. When the compressor operates at medium to high speeds, both the lower and upper valve plates function simultaneously, increasing valve plate rigidity and ensuring valve plate reliability.

[0078] The compressor provided in this application achieves lower vibration and noise during ultra-low speed operation. This compressor employs a two-stage valve plate design (i.e., first valve plate 200 and second valve plate 300). During ultra-low frequency operation, the smaller stiffness valve plate (first valve plate 200) operates, while during medium- and high speed operation, both larger and smaller stiffness valve plates (first valve plate 200 and second valve plate 300) work together, achieving a wide-range, low-noise, low-vibration design for the compressor. Simultaneously, the combination of large and small stiffness valve plates balances low-speed energy efficiency and high-speed reliability, reducing compressor power consumption at medium and low speeds, improving the compressor's coefficient of performance (COP), and enhancing the reliability of the discharge valve plates during high-frequency operation.

[0079] like Figure 3 As shown, the compressor provided in this application, when running at ultra-low speed (the compressor operates at a frequency of 4Hz to 15Hz), shows that the noise peak in the 380Hz to 1640Hz frequency band is generally reduced by more than 10dB in the noise spectrum obtained by testing. The noise perception of refrigeration equipment and compressor is significantly improved, and low-frequency abnormal noise is effectively controlled.

[0080] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0081] like Figure 4 As shown, the first thickness T1 is greater than or equal to 0.2 mm and less than or equal to 0.31 mm.

[0082] In this embodiment, the first thickness T1 is greater than or equal to 0.2 mm and less than or equal to 0.31 mm, which ensures the fatigue resistance of the first valve plate 200 and reduces the stiffness of the first valve plate 200. This allows the first valve plate 200 to maintain the exhaust state continuously when the compressor is running at low speed, reducing the frequency of opening and closing of the first valve plate 200 and reducing the vibration and noise of the compressor.

[0083] Specifically, the first thickness T1 is 0.203 mm.

[0084] The first thickness T1 is 0.254 mm.

[0085] The first thickness T1 is 0.305 mm.

[0086] The first thickness T1 is 0.2 mm or 0.31 mm.

[0087] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0088] like Figure 4 As shown, the ratio of the second thickness T2 to the first thickness T1 is greater than or equal to 1 and less than or equal to 2.1.

[0089] In this embodiment, the ratio of the second thickness T2 to the first thickness T1 is greater than or equal to 1 and less than or equal to 2.1, which gives the second valve plate 300 greater rigidity and the first valve plate 200 less rigidity. The first valve plate 200 and the second valve plate 300 can work together better to reduce the vibration and noise of the compressor during low-frequency and high-frequency operation, while improving the energy efficiency of the compressor and enhancing the reliability of the compressor during operation.

[0090] Specifically, the ratio of the second thickness T2 to the first thickness T1 is 1, that is, the second thickness T2 is equal to the first thickness T1. Even if the second thickness T2 is equal to the first thickness T1, the thickness of the first valve plate 200 is still smaller than the thickness of the exhaust port with only one valve plate. Therefore, it can still reduce the vibration and noise of the compressor when it is running at low frequency.

[0091] The ratio of the second thickness T2 to the first thickness T1 is 1.201. For example, the second thickness T2 is 0.305 mm and the first thickness T1 is 0.254 mm.

[0092] The ratio of the second thickness T2 to the first thickness T1 is 1.251. For example, the second thickness T2 is 0.254 mm and the first thickness T1 is 0.203 mm.

[0093] The ratio of the second thickness T2 to the first thickness T1 is 1.5. For example, the second thickness T2 is 0.381 mm and the first thickness T1 is 0.254 mm.

[0094] The ratio of the second thickness T2 to the first thickness T1 is 1.502. For example, the second thickness T2 is 0.305 mm and the first thickness T1 is 0.203 mm.

[0095] The ratio of the second thickness T2 to the first thickness T1 is 1.598. For example, the second thickness T2 is 0.406 mm and the first thickness T1 is 0.254 mm.

[0096] The ratio of the second thickness T2 to the first thickness T1 is 1.877. For example, the second thickness T2 is 0.381 mm and the first thickness T1 is 0.203 mm.

[0097] The ratio of the second thickness T2 to the first thickness T1 is 2.0. For example, the second thickness T2 is 0.406 mm and the first thickness T1 is 0.203 mm.

[0098] The ratio of the second thickness T2 to the first thickness T1 is 2.1.

[0099] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0100] like Figure 4 As shown, the thickness of gasket 400 is the third thickness T3, and the first thickness T1 is less than the third thickness T3.

[0101] In this embodiment, the thickness of the gasket 400 is the third thickness T3, and the first thickness T1 is less than the third thickness T3. That is, the thickness of the first valve plate 200 is less than the thickness of the gasket 400, so that the first valve plate 200 has a larger movement space. When the compressor is running at low frequency, the number of collisions between the first valve plate 200 and the first exhaust port 110 of the bearing 100 is reduced in each working cycle, further reducing the vibration and noise of the compressor during low-frequency operation.

[0102] Furthermore, the thickness of the gasket 400 can be less than the thickness of the first valve plate 200, or the thickness of the gasket 400 can be equal to the thickness of the first valve plate 200.

[0103] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0104] like Figure 4 As shown, the ratio of the third thickness T3 to the first thickness T1 is greater than or equal to 1.4 and less than or equal to 2.6.

[0105] In this embodiment, the ratio of the third thickness T3 to the first thickness T1 is greater than or equal to 1.4 and less than or equal to 2.6. When the compressor is running at low frequency, the first valve plate 200 has more room to move, thereby reducing the number of collisions between the first valve plate 200 and the first exhaust port 110 of the bearing 100 in each working cycle. When the compressor is running at high frequency, the first valve plate 200 can contact the second valve plate 300 in time, so that the first valve plate 200 and the second valve plate 300 work together, reducing the probability of the first valve plate 200 being crushed by the high-pressure refrigerant due to its low rigidity, thereby improving the stability of the first valve plate 200 in the compressor exhaust process.

[0106] Specifically, the ratio of the third thickness T3 to the first thickness T1 is 1.4.

[0107] The ratio of the third thickness T3 to the first thickness T1 is 1.8.

[0108] The ratio of the third thickness T3 to the first thickness T1 is 2.0.

[0109] The ratio of the third thickness T3 to the first thickness T1 is 2.6.

[0110] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0111] like Figure 2 and Figure 4 As shown, the limiter 500 includes a third connecting portion 510 and a limiting portion 520; the third connecting portion 510 is in contact with the second valve plate 300; the first end of the limiting portion 520 is connected to the third connecting portion 510, and the second end of the limiting portion 520 extends away from the second valve plate 300; wherein, in the axial direction of the bearing 100 ( Figure 2 In the direction indicated by the middle arrow A, when the first cover 220 moves away from the first exhaust port 110 to a position where it contacts the second cover 320, the rising height of the first cover 220 is the first height H1; in the axial direction of the bearing 100, when the second cover 320 moves away from the first exhaust port 110 to a position where it contacts the limiter 500, the rising height of the second cover 320 is the second height H2; the ratio of the second height H2 to the first height H1 is greater than or equal to 3.3 and less than or equal to 7.2.

[0112] In this embodiment, the limiter 500 includes a third connecting portion 510, which fits against the second valve plate 300 to achieve installation and fixation of the limiter 500, thereby improving the stability of the limiter 500 during operation. The limiter 500 also includes a limiting portion 520, the first end of which is connected to the third connecting portion 510, and the second end of which extends away from the second valve plate 300. When the second valve plate 300 moves away from the first exhaust port 110, the second valve plate 300 can contact the limiting portion 520, thereby supporting the second valve plate 300 and limiting its movement. This reduces the probability of the second valve plate 300 undergoing permanent deformation under pressure, and improves the stability of the second valve plate 300 during movement. The ratio of the rising height of the second cover 320 to the rising height of the first cover 220 is greater than or equal to 3.3 and less than or equal to 7.2, which makes the vibration and noise generated when the first valve plate 200 and the second valve plate 300 work together less, thereby reducing the vibration and noise of the compressor during low-frequency and high-frequency operation and improving the quality of the compressor.

[0113] Specifically, the ratio of the second height H2 to the first height H1 is 3.3.

[0114] The ratio of the second height H2 to the first height H1 is 4.5.

[0115] The ratio of the second height H2 to the first height H1 is 6.

[0116] The ratio of the second height H2 to the first height H1 is 7.2.

[0117] Specifically, the rising height of the first cover 220 is equal to the thickness of the gasket 400.

[0118] The rising height of the second cover 320 is: when the second cover 320 is in its initial state, the distance between the second cover 320 and the limiter 500 is located at the axis of the first exhaust hole 110.

[0119] Specifically, the limiting portion 520 extends in an arc shape from one end near the third connecting portion 510 to one end away from the third connecting portion 510, and the slope of the limiting portion 520 increases from one end near the third connecting portion 510 to one end away from the third connecting portion 510.

[0120] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0121] like Figure 4 As shown, the length of the third connecting part 510 is the first length L1; the length of the gasket 400 is the second length L2; the ratio of the first length L1 to the second length L2 is greater than or equal to 0.8 and less than or equal to 1.3.

[0122] In this embodiment, the third connecting portion 510 cooperates with the gasket 400 to constrain the fixed area of ​​the first valve plate 200, that is, to constrain the first connecting portion 210, thereby limiting the effective working length of the first valve plate 200. The ratio of the length of the third connecting portion 510 to the length of the gasket 400 is greater than or equal to 0.8 and less than or equal to 1.3, which gives the first valve plate 200 a more reasonable effective working length, thereby enabling the first valve plate 200 to open or close the first exhaust port 110 according to the exhaust needs of the first exhaust port 110, improving the smoothness of the compressor exhaust process.

[0123] Specifically, the ratio of the first length L1 to the second length L2 is 0.8.

[0124] The ratio of the first length L1 to the second length L2 is 0.9.

[0125] The ratio of the first length L1 to the second length L2 is 1.1.

[0126] The ratio of the first length L1 to the second length L2 is 1.3.

[0127] Specifically, the first length L1 is the length from the axis of the through hole on the third connecting part 510 for mounting the connector 600 to the end of the third connecting part 510 connected to the limiting part 520.

[0128] The second length L2 is the length from the axis of the through hole on the gasket 400 used for mounting the connector 600 to the end of the gasket 400 near the first vent hole 110.

[0129] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0130] like Figure 4 As shown, the length of the gasket 400 is the second length L2; the center distance of the limiter 500 is the third length L3; the ratio of the second length L2 to the third length L3 is greater than or equal to 0.25 and less than or equal to 0.4.

[0131] In this embodiment, the ratio of the length of the gasket 400 to the center distance of the limiter 500 is greater than or equal to 0.25 and less than or equal to 0.4, thereby more effectively controlling the vibration and noise generated by the first valve plate 200 striking the bearing 100 when the compressor is running at ultra-low frequency.

[0132] Specifically, the ratio of the second length L2 to the third length L3 is 0.25.

[0133] The ratio of the second length L2 to the third length L3 is 0.3.

[0134] The ratio of the second length L2 to the third length L3 is 0.35.

[0135] The ratio of the second length L2 to the third length L3 is 0.4.

[0136] Specifically, the third length L3 is the distance between the axis of the through hole on the third connecting part 510 for mounting the connector 600 and the axis of the first vent hole 110.

[0137] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0138] like Figure 5 As shown, the first valve plate 200 also includes a transition portion 230. The first end of the transition portion 230 is connected to the first connecting portion 210, and the second end of the transition portion 230 is connected to the first covering portion 220. The transition portion 230 is provided with a first groove 232, which extends from the end of the transition portion 230 near the first connecting portion 210 to the end of the transition portion 230 near the first covering portion 220.

[0139] In this embodiment, the first valve plate 200 further includes a transition portion 230. A first end of the transition portion 230 is connected to the first connecting portion 210, and a second end of the transition portion 230 is connected to the first covering portion 220. This allows the first covering portion 220 to move relative to the first connecting portion 210 via the transition portion 230, improving the stability of the first valve plate 200 during the compressor's exhaust process. The transition portion 230 is provided with a first groove 232, extending from one end of the transition portion 230 near the first connecting portion 210 to the other end near the first covering portion 220. This ensures a minimum thickness for the first valve plate 200 while reducing its rigidity, thereby ensuring the fatigue resistance of the first valve plate 200 and extending its service life.

[0140] Specifically, the first slot 232 can be one or more.

[0141] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0142] like Figure 4 and Figure 5 As shown, the center distance of the limiter 500 is the third length L3; the length of the first slot 232 is the fourth length L4; the ratio of the fourth length L4 to the third length L3 is greater than or equal to 0.1 and less than or equal to 0.75.

[0143] In this embodiment, the ratio of the length of the first groove 232 to the center distance of the limiter 500 is greater than or equal to 0.1 and less than or equal to 0.75. This optimizes the size of the first groove 232, ensuring that the first valve plate 200 has a certain thickness while reducing the rigidity of the first valve plate 200, further ensuring the fatigue resistance of the first valve plate 200 and extending the service life of the first valve plate 200.

[0144] Specifically, the ratio of the fourth length L4 to the third length L3 is 0.1.

[0145] The ratio of the fourth length L4 to the third length L3 is 0.3.

[0146] The ratio of the fourth length L4 to the third length L3 is 0.5.

[0147] The ratio of the fourth length L4 to the third length L3 is 0.75.

[0148] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0149] like Figure 5As shown, the width of the transition portion 230 is the first width W1; the width of the first groove 232 is the second width W2; the ratio of the second width W2 to the first width W1 is less than or equal to 0.5.

[0150] In this embodiment, the ratio of the width of the first groove 232 to the width of the transition portion 230 is less than or equal to 0.5, which optimizes the size of the first groove 232. While ensuring that the first valve plate 200 has a certain thickness, the rigidity of the first valve plate 200 is reduced, further ensuring the fatigue resistance of the first valve plate 200 and extending the service life of the first valve plate 200.

[0151] Furthermore, the ratio of the second width W2 to the first width W1 is greater than 0.

[0152] Specifically, the ratio of the second width W2 to the first width W1 is 0.1.

[0153] The ratio of the second width W2 to the first width W1 is 0.2.

[0154] The ratio of the second width W2 to the first width W1 is 0.3.

[0155] The ratio of the second width W2 to the first width W1 is 0.5.

[0156] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0157] like Figure 6 As shown, the diameter of the second cover portion 320 is the first diameter D1; the second cover portion 320 is provided with a second vent 322, the diameter of the second vent 322 is the second diameter D2; the ratio of the second diameter D2 to the first diameter D1 is greater than or equal to 0.15 and less than or equal to 0.67.

[0158] In this embodiment, during the compressor discharge process, the second cover 320 is provided with a second vent 322. The refrigerant passing through the first valve plate 200 can continue to move away from the compression chamber through the second vent 322, reducing the resistance of the second valve plate 300 to the refrigerant and improving the compressor's discharge efficiency and smoothness. At the end of the compressor discharge process, the second cover 320, with its second vent 322, allows the first valve plate 200 and the second valve plate 300 to separate and reset more smoothly, reducing the probability of adhesion between them due to refrigerant oil. This also allows the first vent 110 to be sealed more promptly, further improving the stability of the compressor discharge process. The ratio of the diameter of the second vent 322 to the diameter of the second cover 320 is greater than or equal to 0.15 and less than or equal to 0.67, ensuring both smooth compressor discharge and sufficient strength for the second cover 320, thereby improving its reliability.

[0159] Specifically, the ratio of the second diameter D2 to the first diameter D1 is 0.15.

[0160] The ratio of the second diameter D2 to the first diameter D1 is 0.3.

[0161] The ratio of the second diameter D2 to the first diameter D1 is 0.5.

[0162] The ratio of the second diameter D2 to the first diameter D1 is 0.67.

[0163] This embodiment provides a bearing assembly, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0164] like Figure 1 , Figure 2 and Figure 7 As shown, the bearing assembly also includes a connector 600, which passes through the limiter 500, the second valve plate 300, the gasket 400 and the first valve plate 200, and is connected to the bearing 100.

[0165] In this embodiment, the bearing assembly further includes a connector 600, which passes through the limiter 500, the second valve plate 300, the gasket 400, and the first valve plate 200, and is connected to the bearing 100. The connector 600 enables the installation and fixation of the limiter 500, the second valve plate 300, the gasket 400, and the first valve plate 200, thereby improving the stability of the limiter 500, the second valve plate 300, the gasket 400, and the first valve plate 200 during compressor operation.

[0166] Specifically, the first connecting part 210 is fixed to the bearing 100 and fits against the surface of the bearing 100, the transition part 230 is connected to the first connecting part 210, the first covering part 220 is connected to the transition part 230, and the first covering part 220 and the transition part 230 can move relative to the exhaust hole.

[0167] Gasket 400 is attached to the first connecting part 210.

[0168] The second connecting part 310 is attached to the gasket 400, and the second covering part 320 is movable relative to the exhaust hole.

[0169] The third connecting part 510 is attached to the second connecting part 310.

[0170] Specifically, connector 600 is a rivet or screw.

[0171] The limiter 500, the second valve plate 300, the gasket 400 and the first valve plate 200 are provided with through holes that extend along the axis. The connector 600 passes through the through holes. The bearing 100 is provided with mounting holes. The connector 600 passes through the limiter 500, the second valve plate 300, the gasket 400 and the first valve plate 200 in sequence and is then installed in the mounting holes.

[0172] Mounting holes, rivet holes, or threaded holes.

[0173] Furthermore, such as Figure 8 As shown, Figure 8 This is a schematic diagram of the mode shape of the first-order bending natural frequency of the second valve plate 300. Figure 8 The color change in the image represents the different deformation amounts at various positions of the second valve plate 300. The first-order bending natural frequency of the second valve plate 300 is f1.

[0174] like Figure 9 As shown, Figure 9 This is a schematic diagram of the mode shape for the first bending natural frequency of the first valve plate 200. Figure 9 The color change in the image represents the different deformation amounts at various positions of the first valve plate 200. The first-order bending natural frequency of the first valve plate 200 is f2.

[0175] f1 and f2 satisfy the following relationship: f1 < 400Hz, f2 < 400Hz, and 1.4 < f1 / f2 < 1.8.

[0176] The first-order bending natural frequency of the second valve plate 300 and the first-order bending natural frequency of the first valve plate 200 satisfy the above relationship, which can significantly reduce the impact noise between the first valve plate 200 and the bearing 100.

[0177] Furthermore, the first valve plate 200 has a downward pre-bending rate, and the second valve plate 300 has an upward or downward pre-bending rate.

[0178] In one embodiment of the present invention, a compressor is provided, including a bearing assembly as described in any of the above embodiments, and thus the compressor possesses all the beneficial effects of the bearing assembly as described in any of the above embodiments.

[0179] Specifically, the compressor is a variable frequency compressor.

[0180] The compressor can be a single-cylinder, twin-cylinder, or multi-cylinder compressor.

[0181] In one embodiment of the present invention, a refrigeration device is provided, including a bearing assembly as described in any of the above embodiments, or a compressor as described in any of the above embodiments. Therefore, the refrigeration device has all the beneficial effects of the bearing assembly as described in any of the above embodiments or the compressor as described in any of the above embodiments.

[0182] Specifically, the refrigeration equipment includes refrigerators, air conditioners, freezers, or display cases.

[0183] In the claims, description, and accompanying drawings of this utility model, the term "plural" refers to two or more objects. Unless otherwise explicitly defined, the terms "upper," "lower," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this utility model and simplifying the description process, and are not intended to indicate or imply that the device or element referred to must have the described specific orientation, or be constructed and operated in a specific orientation. Therefore, these descriptions should not be construed as limitations on this utility model. The terms "connect," "install," "fix," etc., should be interpreted broadly. For example, "connect" can be a fixed connection between multiple objects, a detachable connection between multiple objects, or an integral connection; it can be a direct connection between multiple objects or an indirect connection between multiple objects through an intermediate medium. For those skilled in the art, the specific meaning of the above terms in this utility model can be understood based on the specific circumstances described above.

[0184] In the claims, description, and drawings of this utility model, 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 this utility model. In the claims, description, and drawings of this utility model, 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.

[0185] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A bearing assembly, characterized in that, include: The bearing is provided with a first vent hole; A first valve plate, comprising a first connecting portion and a first covering portion, wherein the first connecting portion is connected to the bearing, and the first covering portion is connected to the first connecting portion and covers the first exhaust port; The second valve plate includes a second connecting portion and a second covering portion. The second connecting portion is disposed on the side of the first connecting portion away from the bearing, and the second covering portion is connected to the second connecting portion. A gasket is disposed between the first connecting portion and the second connecting portion, and a gap exists between the first covering portion and the second covering portion; A limiter, wherein the limiter is disposed on the side of the second valve plate away from the first valve plate; Wherein, the thickness of the first valve plate is a first thickness T1, the thickness of the second valve plate is a second thickness T2, and the first thickness T1 is less than or equal to the second thickness T2.

2. The bearing assembly according to claim 1, characterized in that, The first thickness T1 is greater than or equal to 0.2 mm and less than or equal to 0.31 mm.

3. The bearing assembly according to claim 1, characterized in that, The ratio of the second thickness T2 to the first thickness T1 is greater than or equal to 1 and less than or equal to 2.

1.

4. The bearing assembly according to claim 1, characterized in that, The thickness of the gasket is a third thickness T3, and the first thickness T1 is less than the third thickness T3.

5. The bearing assembly according to claim 4, characterized in that, The ratio of the third thickness T3 to the first thickness T1 is greater than or equal to 1.4 and less than or equal to 2.

6.

6. The bearing assembly according to claim 1, characterized in that, The limiter includes: The third connecting part is in contact with the second valve plate; The limiting part has a first end connected to the third connecting part and a second end extending away from the second valve plate. Wherein, in the axial direction of the bearing, when the first cover moves away from the first vent hole to a position where it contacts the second cover, the rising height of the first cover is the first height H1; In the axial direction of the bearing, when the second cover moves away from the first vent hole to a position that contacts the limiter, the rising height of the second cover is the second height H2; The ratio of the second height H2 to the first height H1 is greater than or equal to 3.3 and less than or equal to 7.

2.

7. The bearing assembly according to claim 6, characterized in that, The length of the third connecting part is the first length L1; The length of the gasket is the second length L2; The ratio of the first length L1 to the second length L2 is greater than or equal to 0.8 and less than or equal to 1.

3.

8. The bearing assembly according to claim 1, characterized in that, The length of the gasket is the second length L2; The center distance of the limiter is the third length L3; The ratio of the second length L2 to the third length L3 is greater than or equal to 0.25 and less than or equal to 0.

4.

9. The bearing assembly according to claim 1, characterized in that, The first valve plate further includes: The transition portion has a first end connected to the first connecting portion and a second end connected to the first covering portion. The transition portion is provided with a first groove that extends from one end of the transition portion near the first connecting portion to one end of the transition portion near the first covering portion.

10. The bearing assembly according to claim 9, characterized in that, The center distance of the limiter is the third length L3; The length of the first slot is the fourth length L4; The ratio of the fourth length L4 to the third length L3 is greater than or equal to 0.1 and less than or equal to 0.

75.

11. The bearing assembly according to claim 9, characterized in that, The width of the transition section is a first width W1; The width of the first slot is the second width W2; The ratio of the second width W2 to the first width W1 is less than or equal to 0.

5.

12. The bearing assembly according to claim 1, characterized in that, The diameter of the second covering part is the first diameter D1; The second cover is provided with a second vent hole, the diameter of which is a second diameter D2; The ratio of the second diameter D2 to the first diameter D1 is greater than or equal to 0.15 and less than or equal to 0.

67.

13. The bearing assembly according to any one of claims 1 to 12, characterized in that, Also includes: A connector is provided through the limiter, the second valve plate, the gasket and the first valve plate, and is connected to the bearing.

14. A compressor, characterized in that, include: The bearing assembly as described in any one of claims 1 to 13.

15. A refrigeration device, characterized in that, include: The bearing assembly as described in any one of claims 1 to 13; or The compressor as described in claim 14.

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