Compressor and refrigeration apparatus

Abstract

This invention provides a compressor and a refrigeration device, aiming to at least solve the problem of poor noise reduction and high exhaust resistance caused by the unreasonable matching of the valve plate cover and the exhaust port size of the muffler. The compressor includes a bearing assembly and a muffler. The bearing is provided with an exhaust port; a first valve plate is disposed on the bearing, and a first cover of the first valve plate is used to cover the exhaust port; a second valve plate is connected to the first valve plate, and a gap exists between the second cover of the second valve plate and the first cover; the muffler is connected to the bearing, and the muffler is provided with at least one exhaust port; wherein, the diameter of the first cover is D1, the diameter of the second cover is D2, the total area of ​​the exhaust port is S, and D1, D2, and S satisfy the following relationship: 1.5≤0.5×(D1+D2) / ≤5.0, where π is the square root and π is the mathematical constant pi. The compressor provided by this invention can avoid the increase in compressor power consumption caused by excessive back pressure and ensure the noise reduction effect.

Description

Technical Field

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

[0002] Current dual-valve compressors typically do not consider the relationship between the valve cover and the muffler's outlet. If the ratio of the cover size to the muffler outlet size is too small, it means the muffler outlet is too large. Since the muffler needs a certain amount of resistance to reflect sound waves, an overly large outlet results in poor noise reduction. If the ratio is too large, it means the muffler outlet is too small, leading to poor airflow and high resistance. This results in greater pressure on the valve, increasing the compressor's energy consumption. Additionally, when the compression chamber finishes discharging, high-temperature, high-pressure gas can easily flow back into the compression chamber from the bearing's exhaust port. Summary of the Invention

[0003] The present invention aims to at least solve the problem in the related art that the valve plate cover and the exhaust port of the muffler are not properly matched, resulting in poor muffler effect, high exhaust resistance or gas backflow, which affects the energy efficiency and reliability of the compressor.

[0004] The first aspect of the present invention provides a compressor, comprising: a bearing assembly, including: a bearing having an exhaust port; a first valve plate disposed on the bearing, including a first cover portion for covering the exhaust port; a second valve plate connected to the first valve plate and located on the side of the first valve plate away from the exhaust port, the second valve plate including a second cover portion, a gap being formed between the second cover portion and the first cover portion; and a muffler connected to the bearing, the muffler having at least one air outlet; wherein the diameter of the first cover portion is D1, the diameter of the second cover portion is D2, the total area of ​​the air outlet is S, and D1, D2, and S satisfy the following relationship:

[0005] 1.5≤0.5×(D1+D2) / ≤5.0, π is the square root of π, and π is the value of a circle.

[0006] A first aspect of the present invention provides a compressor, comprising: a bearing assembly and a muffler. The bearing assembly includes: a bearing, a first valve plate, and a second valve plate. An exhaust port is provided on the bearing. The first valve plate is disposed on the bearing and includes a first cover portion for covering the exhaust port, providing initial sealing and covering. The second valve plate is connected to the first valve plate and located on the side of the first valve plate away from the exhaust port. The second valve plate includes a second cover portion, which has a gap with the first cover portion, such that the two valve plates are not completely fitted together, allowing them to move sequentially or collaboratively during exhaust. The muffler is connected to the bearing and is used to reduce noise in the exhaust airflow. The muffler is provided with at least one outlet port for discharging gas passing through the muffler.

[0007] The compressor provided by this invention optimizes the flow path matching of airflow from the valve plate through the muffler by precisely defining the diameters of the first and second covers and their relationship with all the air outlets of the muffler. When the ratio is within this range, it ensures that the air outlets of the muffler have sufficient flow area to reduce exhaust resistance and avoid increased compressor power consumption due to excessive back pressure, while also preventing the air outlets from being too large and weakening the muffler's ability to reflect sound waves, thus ensuring the muffler effect. At the same time, this optimized matching can also effectively prevent high-temperature, high-pressure gas from flowing back into the compression chamber from the exhaust port at the end of exhaust, thereby significantly improving the compressor's energy efficiency and operational reliability.

[0008] In the above technical solution, optionally, the diameter of the first covering part is larger than the diameter of the exhaust hole, and the ratio of the sum of the diameters of the first covering part and the second covering part to twice the diameter of the exhaust hole is greater than or equal to 0.8 and less than or equal to 2.

[0009] In this technical solution, by limiting the diameter of the first covering part to be larger than the diameter of the exhaust hole, it is ensured that the first valve plate can completely cover the exhaust hole, guaranteeing sealing performance. Simultaneously, by limiting the ratio of the sum of the diameters of the first and second covering parts to twice the diameter of the exhaust hole, the coordination between the valve plate's coverage of the exhaust hole and gas flow is further optimized. If the ratio is too small, the valve plate covering part will be too small relative to the exhaust hole, potentially leading to poor sealing or poor airflow guidance; if the ratio is too large, the valve plate covering part will be too large, increasing the moment of inertia and affecting high-frequency response. A ratio within this range helps the valve plate to open and close stably, reducing airflow pulse impact.

[0010] In the above technical solution, optionally, the first valve plate also has a first connecting part, which is connected to the bearing, and the first cover part is connected to the first connecting part; the second valve plate also has a second connecting part, which is disposed on the side of the first connecting part away from the bearing, and the second cover part is connected to the second connecting part; the bearing assembly also includes a gasket disposed between the first connecting part and the second connecting part.

[0011] In this technical solution, the first valve plate also has a first connecting portion, which is connected to the bearing (e.g., fixed by rivets). The first cover portion is connected to the first connecting portion, forming a cantilever structure that can move elastically. The second valve plate also has a second connecting portion, which is located on the side of the first connecting portion away from the bearing, and is also fixed to the bearing together with the first connecting portion by fasteners such as rivets. The second cover portion is connected to the second connecting portion. The bearing assembly also includes a gasket, which is disposed between the first and second connecting portions. The first and second valve plates are stacked and fixed together by their respective connecting portions, forming a stable double-layer valve plate assembly. The gasket is disposed between the two to precisely control the gap between the first and second valve plates, ensuring that there is a preset initial gap between the second cover portion and the first cover portion in the free state, which is crucial for the dynamic response and sealing performance of the valve plates.

[0012] Optionally, in the above technical solution, the first cover portion bends toward the exhaust port relative to the first connecting portion.

[0013] In this technical solution, by pre-bending the first valve plate, a certain pre-tightening force is formed on the exhaust port after installation. This pre-tightening force helps to ensure that the first cover fits tightly against the exhaust port of the bearing when the compressor is stopped or under low pressure differential conditions, improving sealing performance, preventing refrigerant leakage, and ensuring volumetric efficiency during the next start-up.

[0014] Optionally, in the above technical solution, the compressor also includes a limiter, which is disposed on the side of the second valve plate away from the first valve plate, and is used to limit the second valve plate.

[0015] In this technical solution, the limiter restricts the maximum opening range of the second valve plate. When the compressor discharges gas, the gas pushes open the second valve plate, causing it to move upwards until it hits the limiter. The limiter prevents the second valve plate from undergoing plastic deformation or breakage due to excessive bending, ensuring the reliability of the valve plate under high frequency and high load conditions. It also controls the speed at which the valve plate falls back, reducing impact noise.

[0016] In the above technical solution, optionally, the limiter includes a third connecting part and a limiting part, the third connecting part is connected to the second connecting part, and the limiting part is bent away from the second valve plate.

[0017] In this technical solution, the limiter includes a third connecting part and a limiting part. The third connecting part is connected to the second connecting part (e.g., fixed by the same rivet), so that the limiter is also securely mounted on the bearing. The limiting part bends away from the second valve plate, forming an arched space, the apex of which is the limiting point for restricting the lift of the second valve plate. This curved limiting part has a simple structure, effectively provides limiting space, and its arched shape can also buffer the impact force when the valve plate strikes at high speed, further playing a role in vibration reduction and noise reduction.

[0018] In the above technical solution, optionally, the first valve plate is a single valve plate or multiple valve plates stacked together; and / or the gasket is a single gasket or multiple gaskets stacked together; and / or the second valve plate is a single valve plate or multiple valve plates stacked together.

[0019] In this technical solution, the total thickness, stiffness, and clearance of the valve plate assembly can be flexibly adjusted by selecting and stacking different numbers of valve plates or gaskets. For example, stacking multiple thinner valve plates can achieve different damping characteristics and fatigue life than a single thick valve plate, providing engineers with greater freedom to match designs according to different compressor models and operating conditions.

[0020] In the above technical solution, optionally, the second cover portion bends toward the direction of the exhaust hole relative to the second connecting portion; or the second cover portion bends away from the exhaust hole relative to the second connecting portion; or the second cover portion does not bend relative to the second connecting portion.

[0021] In this technical solution, the bending direction of the second valve plate determines its degree of contact and motion characteristics with the first valve plate in the initial state. Bending towards the exhaust port allows the second valve plate to contact or get closer to the first valve plate in its free state; bending away from it or not bending at all results in a larger initial gap. Different bending directions can adjust the valve plate's opening sensitivity, the resistance characteristics of airflow, and the interaction force between the two valve plates to adapt to different performance requirements.

[0022] In the above technical solution, optionally, the thickness of the first valve plate is different from the thickness of the second valve plate.

[0023] In this technical solution, a first valve plate is mounted on the bearing and covers the vent hole, while a second valve plate is connected to the first valve plate and located on the side away from the vent hole. By making the two valve plates have different thicknesses, they are given different bending stiffnesses.

[0024] In the above technical solution, optionally, the thickness of the second valve plate is greater than or equal to the thickness of the first valve plate.

[0025] In this technical solution, a first valve plate (lower valve plate) is mounted on the bearing, with its first cover covering the vent hole, serving as a preliminary seal and providing an opening response. A second valve plate (upper valve plate) is located on the side of the first valve plate furthest from the bearing, and is fixedly connected to the bearing via a first connecting part and a second connecting part, with a gap between the second cover part and the first cover part. By limiting the thickness of the second valve plate to be greater than or equal to the thickness of the first valve plate, the upper valve plate has a bending stiffness greater than or equal to that of the lower valve plate, forming a stiffness matching characteristic of "lower valve plate with low stiffness and upper valve plate with high stiffness." In ultra-low speed operation, this structure prioritizes the response to low pressure differentials, opening sensitively and reducing exhaust power consumption and low-frequency flutter noise. In medium-to-high speed operation, the upper and lower valves work together, utilizing the high stiffness of the upper valve to enhance the overall stiffness of the combination. This ensures that both valves reach maximum opening during the initial exhaust phase to reduce exhaust resistance, while the combined stiffness ensures timely closure of the lower valve at the end of exhaust, preventing backflow of high-temperature, high-pressure gas. Simultaneously, the high stiffness of the upper valve effectively reduces the speed and force on its impact limiter, extending valve life and reducing high-frequency impact noise. This solution achieves a balance of low noise, high energy efficiency, and high reliability across the entire frequency band through stiffness grading and synergy.

[0026] Optionally, in the above technical solution, the compressor further includes: a cylinder connected to a bearing assembly, the cylinder having a compression chamber and a slide groove that are interconnected; a piston rotatably disposed in the compression chamber, the piston having a groove on its outer peripheral wall; and a slide plate slidably disposed in the slide groove, one end of the slide plate having a connecting part that is embedded in the groove, so that the slide plate and the piston form a hinged connection.

[0027] In this technical solution, the compressor also includes a cylinder, a piston, and a vane. The cylinder is connected to a bearing assembly to form a compression mechanism. The cylinder has an interconnected compression chamber and a groove. The piston is rotatably disposed within the compression chamber for compressing the refrigerant. A groove is provided on the outer peripheral wall of the piston. The vane is slidably disposed within the groove, and one end of the vane has a connecting part that is embedded in the groove, forming a hinged connection between the vane and the piston. By forming a hinge between the connecting part at the end of the vane and the groove on the outer peripheral wall of the piston, the traditional sliding contact (with gaps) between the vane and the piston is replaced with a gapless hinged connection. This structure completely eliminates the radial gap between the vane and the piston, avoiding impact noise and leakage caused by gaps, while ensuring that the vane always remains in close contact with the piston, greatly improving the volumetric efficiency and operational stability of the compressor.

[0028] In the above technical solution, optionally, the connecting part of the slider is a circular connecting part or a non-circular connecting part, and the groove is an arc-shaped groove that matches the shape of the connecting part.

[0029] In this technical solution, by designing the connecting part and the groove to match each other, such as a circular protrusion with an arc groove, free rotation similar to a ball joint or column joint can be achieved, so that the slide can automatically adjust the angle when moving with the piston, making the movement more flexible and free, and avoiding jamming or abnormal wear.

[0030] Optionally, in the above technical solution, a chamfer structure is provided at the opening of the groove.

[0031] In this technical solution, a chamfer is provided at the groove opening to guide the connecting part of the slider to smoothly engage with the groove during assembly, simplifying the assembly process. Simultaneously, the chamfer also reduces stress concentration between the connecting part and the groove edge during movement, improving the fatigue life of the component.

[0032] In the above technical solution, optionally, the chamfer structure includes a first chamfer structure and a second chamfer structure. The first chamfer structure is connected to the groove wall of the groove, and the second chamfer structure is connected to the outer surface of the piston. The size of the first chamfer structure is 0.1mm to 1mm, and the size of the second chamfer structure is 0.5mm to 1.5mm.

[0033] In this technical solution, stress distribution and assembly guidance are further optimized by setting two chamfers of different sizes and positions. The first chamfer (connecting groove wall) is mainly used to reduce the root stress when the connecting part swings in the groove, while the second chamfer (connecting piston outer surface) is mainly used for assembly guidance and to reduce the contact stress between the connecting part and the piston surface. By limiting the specific dimensional range, the reliability and durability of the hinge structure under various working conditions are ensured.

[0034] Optionally, in the above technical solution, the compressor further includes: a spring hole extending from the outer periphery of the cylinder to the center of the cylinder; and an oil groove disposed in the cylinder and communicating with the spring hole and the oil groove respectively.

[0035] In this technical solution, the compressor also includes a spring bore and an oil groove. The spring bore extends from the outer periphery of the cylinder towards the center of the cylinder to accommodate the spring and provide back pressure to the sliding vane. The oil groove is located in the cylinder and communicates with both the spring bore and the sliding groove. The oil groove creates a lubricating oil channel between the spring bore and the sliding groove. Lubricating oil can flow from the spring bore (oil reservoir) to the sliding groove through the oil groove, lubricating and cooling the friction pair between the sliding vane and the sliding groove. It also lubricates the hinge joint between the sliding vane and the piston, significantly reducing friction loss and improving the mechanical efficiency and reliability of the compressor.

[0036] Optionally, in the above technical solution, the compressor further includes: a knife-removal hole, located in the cylinder, the knife-removal hole being connected to the end of the slide groove away from the center of the cylinder; wherein, the distance between the end of the spring hole near the compression chamber and the knife-removal hole is L1, and the width of the oil groove along the movement direction of the slide is L2, 0.06≤L2 / L1≤0.35.

[0037] In this technical solution, the sufficiency and stability of lubricant supply are ensured by precisely defining the ratio of the oil groove width L2 to the distance L1 from the end of the spring hole to the retraction hole. If the ratio is too small, the oil groove will be too narrow, resulting in insufficient oil supply and poor lubrication; if the ratio is too large, the oil groove will be too wide, which may lead to excessively rapid oil leakage and failure to form an effective oil film support within the groove. Controlling this ratio between 0.06 and 0.35 achieves the best lubrication effect and oil film stability.

[0038] In the above technical solution, optionally, the compressor's operating frequency range is 1Hz to 200Hz. This covers a wide operating range from extremely low frequencies to high frequencies, and the valve plate structure and hinged sliding plate structure of the present invention can exert excellent noise reduction and energy efficiency improvement effects throughout this full frequency band.

[0039] In the above technical solution, the compressor may optionally be a single-cylinder compressor, a twin-cylinder compressor, or a jet compressor.

[0040] A second aspect of the present invention provides a refrigeration device, including a compressor according to any of the technical solutions of the first aspect of the present invention. Attached Figure Description

[0041] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0042] Figure 1 A schematic diagram of the upper bearing assembly according to an embodiment of this application is shown;

[0043] Figure 2 One of the structural schematic diagrams of the lower bearing assembly according to an embodiment of this application is shown;

[0044] Figure 3 A schematic diagram of the structure of a compressor according to an embodiment of this application is shown;

[0045] Figure 4 A schematic diagram of the upper bearing according to an embodiment of this application is shown;

[0046] Figure 5 A schematic diagram of the structure of the lower bearing according to an embodiment of this application is shown;

[0047] Figure 6 An assembly diagram of the upper bearing assembly and the upper muffler according to one embodiment of this application is shown;

[0048] Figure 7 A second schematic diagram of the structure of a lower bearing assembly according to an embodiment of this application is shown;

[0049] Figure 8 One of the schematic diagrams of the pump body assembly of a compressor according to an embodiment of this application is shown;

[0050] Figure 9 A second schematic diagram of the pump body assembly of a compressor according to an embodiment of this application is shown;

[0051] Figure 10 The third schematic diagram shows the structure of the pump body assembly of a compressor according to one embodiment of this application;

[0052] Figure 11 Fourth schematic diagram of the pump body assembly of a compressor according to an embodiment of this application is shown;

[0053] Figure 12 A schematic diagram of the piston structure according to an embodiment of this application is shown;

[0054] Figure 13 A schematic diagram of the slider according to an embodiment of this application is shown;

[0055] Figure 14 A schematic diagram of the assembly structure of the slider and limiter according to an embodiment of this application is shown.

[0056] in, Figures 1 to 14 The correspondence between the reference numerals and component names in the attached drawings is as follows:

[0057] 1. Bearing assembly; 11. Bearing; 112. Exhaust port; 12. First valve plate; 122. First connecting part; 124. First cover part; 132. Clearance; 134. Gasket; 14. Second valve plate; 142. Second connecting part; 144. Second cover part; 15. Silencer; 152. Air outlet; 16. Limiter; 162. Third connecting part; 164. Limiter part; 17. Cylinder; 172. Compression chamber; 174. Slide groove; 176. Spring hole; 178. Oil groove; 179. Retracting hole; 18. Piston; 182. Groove; 184. Groove wall; 19. Slide plate; 192. Connecting part; 194. Chamfered structure; 195. First chamfered structure; 196. Second chamfered structure; 2. Compressor. Detailed Implementation

[0058] To better understand the above-mentioned objectives, features, and advantages of this application, the application 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.

[0059] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, this application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.

[0060] like Figure 1 , Figure 2 and Figure 3 As shown, the first aspect of the present invention provides a compressor 2, including: a bearing assembly 1 and a muffler 15.

[0061] Specifically, the compressor 2 includes two bearing assemblies 1, namely the upper bearing assembly (e.g., ... Figure 4 (as shown) and the lower bearing assembly (as shown) Figure 5 and Figure 7 (As shown). Both the upper and lower bearing assemblies include: a bearing 11, a first valve plate 12, and a second valve plate 14. The muffler 15 includes an upper muffler and a lower muffler, with the upper muffler assembled to the upper bearing assembly and the lower muffler assembled to the lower bearing assembly.

[0062] Since the assembly relationship between the upper bearing assembly and the upper muffler is the same as that between the lower bearing assembly and the lower muffler, the applicant will use the assembly of the upper bearing assembly and the upper muffler as an example for explanation below:

[0063] like Figure 1 , Figure 6 and Figure 14 As shown, the bearing 11 is provided with an exhaust port 112. A first valve plate 12 (hereinafter referred to as the lower valve plate) is disposed on the bearing 11 and includes a first cover portion 124, which is used to cover the exhaust port 112, providing initial sealing and covering. A second valve plate 14 (hereinafter referred to as the upper valve plate) is connected to the first valve plate 12 and is located on the side of the first valve plate 12 away from the exhaust port 112. The second valve plate 14 includes a second cover portion 144, which has a gap 132 with the first cover portion 124, so that the two valve plates are not completely fitted together and can move together during exhaust. A muffler 15 is connected to the bearing 11 and is used to reduce noise in the exhaust airflow. The muffler 15 is provided with at least one exhaust port 152 for discharging the gas passing through the muffler 15.

[0064] Wherein, the diameter of the first covering part 124 is D1, the diameter of the second covering part 144 is D2, the total area of ​​the vent 152 is S, and D1, D2 and S satisfy the following relationship:

[0065] 1.5≤0.5×(D1+D2) / ≤5.0, π is the square root of π, and π is the value of a circle.

[0066] It is important to understand that when the muffler 15 has only one vent 152, S is the area of ​​that single vent. It is directly equal to the radius of the vent 152; when the silencer 15 is provided with multiple vents 152, S is the sum of the areas of all vents. This refers to the radius of the equivalent circle after the total area of ​​these vents is equivalent to a single circular vent, which is the equivalent radius of the multiple vents 152.

[0067] Since the structures of the upper bearing assembly and the lower bearing assembly are identical, the relationship between the cover and the vent hole satisfies the above-mentioned formula for both the upper and lower bearing assemblies. That is, for the upper bearing assembly, the diameter D1 of the first cover 124, the diameter D2 of the second cover 144, and the total area S of the vent hole 152 on the muffler 15 corresponding to the upper bearing satisfy the above-mentioned formula; for the lower bearing assembly, the diameter D1 of the first cover 124, the diameter D2 of the second cover 144, and the total area S of the vent hole 152 on the muffler 15 corresponding to the lower bearing also satisfy the above-mentioned formula.

[0068] Optionally, for the upper bearing assembly, D1, D2, and S satisfy the following relationship: 1.5 ≤ 0.5 × (D1 + D2) / ≤4.0; optionally, 2≤0.5×(D1+D2) / ≤3.

[0069] Optionally, for the lower bearing assembly, D1, D2, and S satisfy the following relationship: 2.0 ≤ 0.5 × (D1 + D2) / ≤5.0; optionally, 2.5≤0.5×(D1+D2) / ≤3.5.

[0070] The compressor 2 provided by this invention optimizes the flow path matching of airflow from the valve plate through the muffler 15 by precisely defining the ratio of the average diameter of the first cover portion 124 and the second cover portion 144 in the bearing assembly to the equivalent radius of the muffler outlet port 152. When the ratio is within the above range, it ensures that the outlet port 152 of the muffler 15 has sufficient flow area to reduce exhaust resistance and avoid increased power consumption of the compressor 2 due to excessive back pressure. It also prevents the outlet port 152 from being too large, which would weaken the muffler 15's ability to reflect sound waves, thus ensuring the muffler effect. At the same time, this optimized matching can also effectively prevent high-temperature and high-pressure gas from flowing back from the exhaust port 112 to the compression chamber 172 at the end of exhaust, thereby significantly improving the energy efficiency and operational reliability of the compressor 2.

[0071] Understandably, if the cover volume is too large and the muffler outlet is too small, the small outlet will have a significant throttling effect on the cover, preventing the gas outside the cover from being discharged in time and creating a high-pressure zone. This high-pressure zone will then act on the cover, generating reverse pressure and making it difficult to open smoothly during exhaust, increasing the valve plate's opening resistance and movement lag. If the cover volume is too small and the muffler outlet is too large, the excessively large outlet will cause the gas to leak out rapidly, failing to create an effective pressure buffer outside the cover. This makes the airflow impact on the cover more direct and intense at the moment of opening, easily causing high-frequency vibration and swaying of the cover, thus compromising its movement stability. The focus of this application is to coordinate the size matching of the cover and the outlet, ensuring that neither is too large nor too small, thereby achieving a balance between reducing exhaust resistance and maintaining pressure buffer, ensuring smooth valve plate opening and stable movement.

[0072] In the above technical solution, optionally, the diameter of the first covering part 124 is greater than the diameter of the exhaust hole 112, and the ratio of the sum of the diameter of the first covering part 124 and the diameter of the second covering part 144 to twice the diameter of the exhaust hole 112 is greater than or equal to 0.8 and less than or equal to 2.

[0073] In this technical solution, the diameter of the exhaust port 112 is D3, satisfying the relationship: D1>D3, and 0.8≤(D1+D2) / (2×D3)≤2.0. Optionally, 1.2≤(D1+D2) / (2×D3)≤1.6.

[0074] In this technical solution, by limiting the diameter of the first covering portion 124 to be larger than the diameter of the exhaust hole 112, it is ensured that the first valve plate 12 can completely cover the exhaust hole 112, guaranteeing sealing performance. Simultaneously, by limiting the ratio of the average diameter of the first covering portion 124 and the second covering portion 144 to the diameter D3 of the exhaust hole 112, the coordination between the valve plate's coverage of the exhaust hole and gas flow is further optimized. If the ratio is too small (e.g., less than 0.8), the valve plate covering portion is too small relative to the exhaust hole 112, which may lead to poor sealing or poor airflow guidance; if the ratio is too large (e.g., greater than 2.0), the valve plate covering portion is too large, increasing the moment of inertia and affecting high-frequency response. Controlling the ratio between 0.8 and 2.0, especially between 1.2 and 1.6, helps the valve plate to open and close stably, reduces airflow pulse impact, and achieves a better balance between sealing performance, response speed, and airflow stability.

[0075] Optionally, in the above technical solution, the first valve plate 12 further has a first connecting portion 122, which is connected to the bearing 11, and the first covering portion 124 is connected to the first connecting portion 122; the second valve plate 14 further has a second connecting portion 142, which is disposed on the side of the first connecting portion 122 away from the bearing 11, and the second covering portion 144 is connected to the second connecting portion 142; the bearing assembly 1 further includes a gasket 134, which is disposed between the first connecting portion 122 and the second connecting portion 142.

[0076] In this technical solution, the first valve plate 12 also has a first connecting portion 122, which is connected to the bearing 11 (e.g., fixed by rivets). The first covering portion 124 is connected to the first connecting portion 122, forming a cantilever structure that can move elastically. The second valve plate 14 also has a second connecting portion 142, which is located on the side of the first connecting portion 122 away from the bearing 11, and is also fixed to the bearing 11 together with the first connecting portion 122 by fasteners such as rivets. The second covering portion 144 is connected to the second connecting portion 142. The bearing assembly 1 also includes a gasket 134, which is disposed between the first connecting portion 122 and the second connecting portion 142. The first valve plate 12 and the second valve plate 14 are stacked and fixed together by their respective connecting portions, forming a stable double-layer valve plate assembly. A gasket 134 is disposed between the two to precisely control the gap 132 between the first valve plate 12 and the second valve plate 14, ensuring that there is a preset initial gap between the second cover portion 144 and the first cover portion 124 in the free state, which is crucial for the dynamic response and sealing performance of the valve plate.

[0077] Optionally, in the above technical solution, the first cover portion 124 bends relative to the first connecting portion 122 toward the exhaust port 112.

[0078] In this technical solution, by setting the first valve plate 12 to be pre-bent, it forms a certain pre-tightening force on the exhaust port 112 after installation. This pre-tightening force helps to ensure that the first cover 124 fits tightly against the exhaust port 112 of the bearing 11 when the compressor 2 is stopped or under low pressure differential conditions, thereby improving sealing, preventing refrigerant leakage, and ensuring volumetric efficiency during the next start-up.

[0079] Optionally, in the above technical solution, the compressor 2 further includes a limiter 16, which is disposed on the side of the second valve plate 14 away from the first valve plate 12, and is used to limit the second valve plate 14.

[0080] In this technical solution, the limiter 16 limits the maximum opening range of the second valve plate 14. When the compressor 2 discharges gas, the gas pushes open the second valve plate 14, and the second valve plate 14 moves upward until it hits the limiter 16. The limiter 16 can prevent the second valve plate 14 from undergoing plastic deformation or breakage due to excessive bending, ensuring the reliability of the valve plate under high frequency and high load. At the same time, it can also control the speed of the valve plate when it falls back, reducing impact noise.

[0081] Optionally, in the above technical solution, the limiter 16 includes a third connecting part 162 and a limiting part 164. The third connecting part 162 is connected to the second connecting part 142, and the limiting part 164 is bent away from the second valve plate 14.

[0082] In this technical solution, the limiter 16 includes a third connecting portion 162 and a limiting portion 164. The third connecting portion 162 is connected to the second connecting portion 142 (e.g., fixed by the same rivet), so that the limiter 16 is also securely mounted on the bearing 11. The limiting portion 164 bends away from the second valve plate 14, forming an arched space, the apex of which is the limiting point for restricting the lift of the second valve plate 14. This curved limiting portion 164 has a simple structure, effectively provides limiting space, and its arched shape can also buffer the impact force when the valve plate strikes at high speed, further playing a role in vibration reduction and noise reduction.

[0083] In the above technical solution, optionally, the first valve plate 12 is a single valve plate or multiple valve plates stacked together; and / or the gasket 134 is a single gasket or multiple gaskets stacked together; and / or the second valve plate 14 is a single valve plate or multiple valve plates stacked together.

[0084] In this technical solution, the total thickness, stiffness, and clearance of the valve plate assembly can be flexibly adjusted by selecting different numbers of valve plates or gaskets for stacking. For example, stacking multiple thinner valve plates can achieve different damping characteristics and fatigue life than a single thick valve plate, providing engineers with greater freedom to match designs according to different compressor models and operating conditions.

[0085] In the above technical solution, optionally, the second cover portion 144 bends relative to the second connecting portion 142 toward the direction closer to the exhaust port 112; or the second cover portion 144 bends relative to the second connecting portion 142 toward the direction away from the exhaust port 112; or the second cover portion 144 does not bend relative to the second connecting portion 142.

[0086] In this technical solution, the bending direction of the second valve plate 14 determines its degree of contact and motion characteristics with the first valve plate 12 in the initial state. Bending towards the exhaust port 112 allows the second valve plate 14 to contact or get closer to the first valve plate 12 in a free state; bending away from it or not bending at all results in a larger initial gap. Different bending directions can adjust the valve plate opening sensitivity, the resistance characteristics of airflow, and the interaction force between the two valve plates to adapt to different performance requirements.

[0087] Optionally, in the above technical solution, the thickness of the first valve plate 12 is different from the thickness of the second valve plate 14.

[0088] In this technical solution, the first valve plate 12 is disposed on the bearing 11 and covers the exhaust hole 112, and the second valve plate 14 is connected to the first valve plate 12 and located on the side away from the exhaust hole 112. By making the two valve plates have different thicknesses, they are given different bending stiffnesses.

[0089] In the above technical solution, optionally, the thickness of the second valve plate 14 is greater than or equal to the thickness of the first valve plate 12.

[0090] In this technical solution, the first valve plate 12 (lower valve plate) is disposed on the bearing 11, and its first cover portion 124 covers the exhaust hole 112, serving as a preliminary seal and opening response. The second valve plate 14 (upper valve plate) is disposed on the side of the first valve plate 12 away from the bearing 11, and is fixedly connected to the bearing 11 through the first connecting portion 122 and the second connecting portion 142, and there is a gap 132 between the second cover portion 144 and the first cover portion 124. By limiting the thickness of the second valve plate 14 to be greater than or equal to the thickness of the first valve plate 12, the upper valve plate has a bending stiffness greater than or equal to that of the lower valve plate, forming a stiffness matching characteristic of "lower valve plate with low stiffness and upper valve plate with high stiffness". In ultra-low speed operation, this structure prioritizes the response to low pressure differentials, opening sensitively and reducing exhaust power consumption and low-frequency flutter noise. In medium-to-high speed operation, the upper and lower valves work together, utilizing the high stiffness of the upper valve to enhance the overall stiffness of the combination. This ensures that both valves reach maximum opening during the initial exhaust phase to reduce exhaust resistance, while the combined stiffness ensures timely closure of the lower valve at the end of exhaust, preventing backflow of high-temperature, high-pressure gas. Simultaneously, the high stiffness of the upper valve effectively reduces the speed and force on the limit switch 16, extending valve life and reducing high-frequency impact noise. This solution achieves a balance of low noise, high energy efficiency, and high reliability across the entire frequency band through stiffness grading and synergy.

[0091] In the above technical solutions, optionally, such as Figure 8 , Figure 9 , Figure 10 , Figure 11 and Figure 13As shown, the compressor 2 also includes: a cylinder 17 connected to the bearing assembly 1, the cylinder 17 having a compression chamber 172 and a slide groove 174 that are interconnected; a piston 18 rotatably disposed in the compression chamber 172, the outer peripheral wall of the piston 18 having a groove 182; and a sliding vane 19 slidably disposed in the slide groove 174, one end of the sliding vane 19 having a connecting portion 192, the connecting portion 192 being embedded in the groove 182, so that the sliding vane 19 and the piston 18 form a hinged connection.

[0092] In this technical solution, the compressor 2 also includes a cylinder 17, a piston 18, and a vane 19. The cylinder 17 is connected to the bearing assembly 1 to form a compression mechanism. The cylinder 17 has a compression chamber 172 and a sliding groove 174 that are interconnected. The piston 18 is rotatably disposed in the compression chamber 172 for compressing the refrigerant. A groove 182 is provided on the outer peripheral wall of the piston 18. The vane 19 is slidably disposed in the sliding groove 174, and one end of the vane 19 has a connecting portion 192, which is embedded in the groove 182, so that the vane 19 and the piston 18 form a hinged connection. By forming a hinge between the connecting portion 192 at the end of the vane 19 and the groove 182 on the outer peripheral wall of the piston 18, the traditional sliding contact (with gap) between the vane and the piston is changed to a gapless hinged connection. This structure completely eliminates the radial clearance between the vane 19 and the piston 18, avoiding impact noise and leakage caused by the clearance, while ensuring that the vane 19 can always be in close contact with the piston 18, greatly improving the volumetric efficiency and operational stability of the compressor 2.

[0093] In the above technical solution, optionally, the connecting part 192 of the slider 19 is a circular connecting part or a non-circular connecting part, and the groove 182 is an arc-shaped groove that matches the shape of the connecting part 192.

[0094] In this technical solution, by designing the connecting part 192 and the groove 182 into matching shapes, such as a circular protrusion with an arc groove, free rotation similar to a ball joint or column joint can be achieved, so that the slide 19 can automatically adjust its angle when moving with the piston 18, making the movement more flexible and free, and avoiding jamming or abnormal wear.

[0095] In the above technical solutions, optionally, such as Figure 12 As shown, a chamfered structure 194 is provided at the opening of the groove 182.

[0096] In this technical solution, a chamfered structure 194 is provided at the opening of the groove 182 to guide the connecting part 192 of the slider 19 to smoothly engage with the groove 182 during assembly, simplifying the assembly process. At the same time, the chamfered structure 194 can also reduce the stress concentration between the connecting part 192 and the edge of the groove during movement, thereby improving the fatigue life of the component.

[0097] In the above technical solution, optionally, the chamfer structure 194 includes a first chamfer structure 195 and a second chamfer structure 196. The first chamfer structure 195 is connected to the groove wall 184 of the groove 182, and the second chamfer structure 196 is connected to the outer surface of the piston 18. The size of the first chamfer structure 195 is 0.1mm to 1mm, and the size of the second chamfer structure 196 is 0.5mm to 1.5mm.

[0098] In this technical solution, stress distribution and assembly guidance are further optimized by setting two chamfers of different sizes and positions. The first chamfer structure 195 (connecting groove wall 184) is mainly used to reduce the root stress when the connecting part 192 swings within the groove 182, while the second chamfer structure 196 (connecting piston 18 outer surface) is mainly used for assembly guidance and to reduce the contact stress between the connecting part 192 and the piston 18 surface. By defining a specific dimensional range, the reliability and durability of this hinge structure under various working conditions are ensured.

[0099] Optionally, in the above technical solution, the compressor 2 further includes: a spring hole 176 extending from the outer periphery of the cylinder 17 to the center of the cylinder 17; and an oil groove 178 disposed in the cylinder 17 and communicating with the spring hole 176 and the slide groove 174 respectively.

[0100] In this technical solution, the compressor 2 also includes a spring hole 176 and an oil groove 178. The spring hole 176 extends from the outer periphery of the cylinder 17 towards the center of the cylinder 17 and is used to accommodate a spring to provide back pressure to the sliding vane 19. The oil groove 178 is located in the cylinder 17 and communicates with both the spring hole 176 and the sliding groove 174. The configuration of the oil groove 178 establishes a lubricating oil passage between the spring hole 176 and the sliding groove 174. Lubricating oil can flow from the spring hole 176 (oil storage area) to the sliding groove 174 through the oil groove 178, lubricating and cooling the friction pair between the sliding vane 19 and the sliding groove 174, and also providing lubrication to the hinge joint between the sliding vane 19 and the piston 18, significantly reducing friction loss and improving the mechanical efficiency and reliability of the compressor 2.

[0101] Optionally, the oil grooves 178 are distributed on both sides of the slide vane 19, allowing lubricating oil to enter the grooves 174 simultaneously from both sides of the slide vane 19, providing uniform lubrication to both working surfaces of the slide vane 19. This avoids lubrication dead zones caused by unilateral oil supply and significantly improves the lubrication effect of the slide vane 19. Furthermore, the oil grooves 178 on both sides of the slide vane 19 are equidistant from the center of the cylinder 17 (e.g., ...). Figure 8 , Figure 9 and Figure 10 (as shown) or different (such as) Figure 11As shown, the distribution of lubricating oil can be flexibly adjusted. When the distances on both sides are the same, the machining of the oil groove 178 is simpler, which helps to reduce manufacturing costs and simplifies the layout of the oil circuit. When the distances on both sides are different, the lubricating oil has a wider radial coverage, which can adapt to the lubrication needs under different working conditions and further improve the lubrication effect. Therefore, this technical solution effectively solves the problem of poor lubrication of the sliding vane 19 and improves the reliability and service life of the compressor 2.

[0102] Optionally, the oil groove 178 can be an annular groove, surrounding both sides of the slide plate 19 to form a continuous lubricating oil channel. This structure ensures that the slide plate 19 receives uniform lubrication throughout its entire stroke. Alternatively, the oil groove 178 can be multiple independent oil grooves, spaced apart radially on both sides of the slide plate 19. The design of multiple oil grooves allows for flexible adjustment of the lubricating oil supply at different positions on the slide plate 19. That is, the number of oil grooves 178 on both sides of the slide plate 19 can be the same or different, and the volume of the oil grooves 178 on both sides of the slide plate 19 can be the same or different. For example, denser oil grooves 178 can be placed in areas of the slide plate 19 where the force is greater or friction is more intense, or wider oil grooves 178 can be placed at critical locations, thereby achieving differentiated lubrication effects. In addition, the multiple oil grooves 178 can be configured to be symmetrically or asymmetrically distributed. When symmetrically distributed, the lubrication conditions on both sides of the slide 19 are consistent, which is conducive to the smooth movement of the slide 19. When asymmetrically distributed, that is, staggeredly distributed, more oil grooves 178 or larger oil grooves 178 can be set on the side with greater lubrication demand according to the force characteristics of the slide 19 in actual movement, thereby optimizing the lubrication effect and reducing friction loss.

[0103] In the above technical solutions, optionally, such as Figure 9 and Figure 10 As shown, the compressor 2 also includes: a knife retraction hole 179, which is located in the cylinder 17 and is connected to the end of the slide groove 174 away from the center of the cylinder 17; wherein, the distance between the end of the spring hole 176 near the compression chamber 172 and the knife retraction hole 179 is L1, and the width of the oil groove 178 along the movement direction of the slide vane 19 is L2, 0.06≤L2 / L1≤0.35.

[0104] In this technical solution, the sufficiency and stability of lubricant supply are ensured by precisely defining the ratio of the width L2 of the oil groove 178 to the distance L1 from the end of the spring hole 176 to the retraction hole 179. If the ratio is too small, the oil groove 178 will be too narrow, resulting in insufficient oil supply and poor lubrication; if the ratio is too large, the oil groove 178 will be too wide, which may lead to excessively rapid oil leakage and failure to form an effective oil film support within the slide groove 174. Controlling this ratio between 0.06 and 0.35 achieves the best lubrication effect and oil film stability.

[0105] In the above technical solution, optionally, oil grooves 178 are provided on both sides along the radial direction of the slider 19, and the oil grooves 178 on both sides can be symmetrically arranged, such as... Figure 9 and Figure 10 As shown, this design ensures consistent lubrication conditions on both sides of the slide plate 19, resulting in a uniform oil film distribution. This balances the forces acting on the slide plate 19 during its reciprocating motion within the groove 174, reducing uneven wear and improving operational stability and reliability. Furthermore, the symmetrical oil groove structure facilitates manufacturing and reduces production costs. Of course, the oil grooves 178 on both sides can also be asymmetrically arranged, such as... Figure 11 As shown, this allows for differentiated design based on the force distribution and lubrication requirements of the vane 19 during actual operation. For example, a wider oil groove or more oil grooves can be provided on the side subjected to greater lateral force to enhance the lubrication and cooling effect on that side, thereby further optimizing the friction pair working conditions between the vane 19 and the groove 174, adapting to higher loads or more complex operating conditions, and improving the durability and efficiency of the compressor.

[0106] In the above technical solution, optionally, the operating frequency range of the compressor 2 is 1Hz to 200Hz. This covers a wide operating range from extremely low frequencies to high frequencies, and the valve plate structure and hinged sliding plate structure of the present invention can exert excellent noise reduction and energy efficiency improvement effects throughout this full frequency band.

[0107] In the above technical solution, the compressor 2 may optionally be a single-cylinder compressor, a double-cylinder compressor, a multi-cylinder compressor, or a jet compressor.

[0108] A second aspect of the present invention provides a refrigeration device, including a compressor 2 according to any of the technical solutions of the first aspect of the present invention.

[0109] Optionally, the refrigeration equipment can be an air conditioner. Compressor 2 can be a wide-range silent compressor.

[0110] Another embodiment of the present invention provides a wide-band silent compressor and an air conditioner.

[0111] It's important to understand that conventional compressors typically operate within a speed range of 15Hz to 120Hz, while wide-frequency compressors significantly extend this range to 1Hz to 200Hz. When the compressor speed decreases to 1Hz, the stress on the discharge valve plates and vanes worsens, easily generating low-frequency noise and affecting noise quality. Conversely, as the compressor speed decreases, radial leakage between the vanes and piston increases, reducing compressor efficiency. Furthermore, when the compressor speed increases to 200Hz, friction between the vanes and the groove increases, leading to increased power consumption and further reduced compressor efficiency. This invention effectively addresses the issues of increased noise and decreased efficiency inherent in wide-frequency compressors.

[0112] The compressor 2 provided in this embodiment employs a multi-valve assembly design for its exhaust valve group. The exhaust valves have the technical advantage of adaptive stiffness; at ultra-low speeds, the smaller stiffness valve group operates, while at medium and high speeds, the combined larger stiffness valve group works together. Simultaneously, the sliding vane 19 and piston 18 are hinged, preventing separation and reducing radial leakage. The cylinder 17's slide groove 174 is provided with one or more lubricating oil grooves 178. These lubricating oil grooves 178 are located within the high back pressure range where the spring hole 176 is situated, ensuring lubrication of the sliding vane 19 and reducing friction.

[0113] Specifically, in this embodiment, the compressor 2 includes a bearing assembly 1 disposed within a sealed housing. The bearing assembly 1 includes a bearing 11, a lower valve plate (i.e., a first valve plate 12), an upper valve plate (i.e., a second valve plate 14), a gasket 134, and a limiter 16. The gasket 134 is placed between the upper and lower valve plates to elastically constrain the initial lift of the lower valve plate. The bearing 11 is provided with an exhaust port 112 and a rivet hole. The lower valve plate is disposed within the valve seat of the bearing 11, and its head (i.e., the first cover portion 124) contacts the exhaust port 112 of the bearing 11 to seal the exhaust port 112. The rivet hole at the tail of the lower valve plate (i.e., the first connecting portion 122) mates with the rivet hole of the bearing 11. The gasket 134 is placed on the lower valve plate and mates with it through the rivet hole. The upper valve plate is placed on the gasket 134 and contacts it. The limiter 16 is disposed on the upper valve plate to limit the lift height of the upper and lower valve plates.

[0114] Furthermore, in order to improve the dynamic response of the exhaust valve plate, reduce the exhaust resistance of the compressor 2, and improve energy efficiency, the diameter D2 of the second cover part 144 of the upper valve plate, the diameter D1 of the first cover part 124 of the lower valve plate, and the diameter D3 of the exhaust hole 112 should satisfy 0.8≤(D1+D2) / (2×D3)≤2.0.

[0115] Furthermore, the upper valve plate is composed of one or more valve plates stacked together, with a total thickness of T1; the gasket 134 is composed of one or more gaskets stacked together, with a total thickness of T2; the lower valve plate is composed of one or more valve plates stacked together, with a total thickness of T3; satisfying T3≤T1; therefore, the lower valve plate has a low stiffness characteristic, while the upper valve plate has a higher stiffness characteristic, so that the low stiffness of the upper valve plate and the high stiffness of the lower valve plate can be better used together, taking into account both low noise and high energy efficiency in low-frequency operation and low noise and high reliability in high-frequency operation.

[0116] Furthermore, for the upper bearing assembly, the sum of the areas of at least one vent 152 of the muffler 15 is S, satisfying 1.5 ≤ 0.5 × (D1 + D2) / ≤4.0, further preferred 2≤0.5×(D1+D2) / ≤3.0.

[0117] Furthermore, for the lower bearing assembly, the sum of the areas of at least one vent 152 of the muffler 15 is S, satisfying 2 ≤ 0.5 × (D1 + D2) / ≤5.0, further preferred 2.5≤0.5×(D1+D2) / ≤3.5.

[0118] Furthermore, the thickness of the second valve plate 14 (upper valve plate) is greater than or equal to the thickness of the first valve plate 12 (lower valve plate). When the compressor 2 is running at medium to high speed, the upper and lower valve plates work together. At the beginning of exhaust, both can reach their maximum opening state. At the end of exhaust, due to the superposition effect of the high-stiffness and low-stiffness dual valve plates, the combined stiffness ensures that the lower valve plate closes in time, preventing high-temperature and high-pressure exhaust from flowing back into the pump body's suction chamber. This invention has outstanding design effects, reducing exhaust power consumption during low-frequency operation, improving the energy efficiency of the low-frequency compressor, and reducing exhaust valve chatter and impact noise. It also increases the valve plate stiffness during high-frequency operation, reducing the speed and force of the upper valve plate impacting the limit switch 16, improving valve plate life and compressor 2 reliability, and reducing the noise of the high-frequency impacting limit switch 16.

[0119] Furthermore, it should be emphasized that for the upper bearing assembly, the upper valve plate is on top and the lower valve plate is on the bottom. However, for the lower bearing assembly, the upper valve plate is on the bottom and the lower valve plate is on top.

[0120] Furthermore, the compressor 2 includes a cylinder 17, a sliding vane 19, a piston 18, and a sliding groove 174. The sliding vane 19 has a hinged structure, and the tip of the sliding vane 19 has a protruding circular or non-circular connecting part 192. The piston 18 is provided with a groove 182. The protruding connecting part 192 at the tip of the sliding vane 19 is embedded into the corresponding groove 182 of the piston 18. The two cooperate with each other to form a hinged structure.

[0121] Furthermore, the groove 182 of the piston 18 has a chamfered structure 194, including a first chamfered structure 195 and a second chamfered structure 196. The size range C1 of the first chamfered structure 195 satisfies 0.1≤C1≤1 (unit mm), and the size range C2 of the second chamfered structure 196 satisfies 0.5≤C2≤1.5 (unit mm). The slide groove 174 of the cylinder 17 is provided with one or more lubricating oil grooves 178. The distance between the deepest position of the spring hole 176 and the retraction hole 179 is L1. The opening width of the lubricating oil groove 178 is L2. The lubricating oil groove 178 is located within the high back pressure range where the spring hole 176 is located, satisfying 0.06≤L2 / L1≤0.35.

[0122] The compressor 2 of this invention, with its combination of large and small stiffness valve plates, balances low-speed energy efficiency and high-speed reliability. It reduces power consumption at low and medium speeds, improves the COP (coefficient of performance), and enhances the reliability of the exhaust valve plates during high-frequency operation. This invention achieves low-noise, low-vibration, and high-efficiency operation of a wide-range compressor across its entire speed range.

[0123] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. 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 any one embodiment or example.

[0124] Although embodiments of this application have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the claims and their equivalents.

Claims

1. A compressor characterized by, include: Bearing assembly, including: The bearing is provided with an exhaust port; A first valve plate is disposed on the bearing and includes a first cover portion, the first cover portion being used to cover the exhaust port; A second valve plate is connected to the first valve plate and is located on the side of the first valve plate away from the exhaust port. The second valve plate includes a second cover portion, and there is a gap between the second cover portion and the first cover portion. A muffler connected to the bearing, wherein the muffler is provided with at least one air outlet. Wherein, the diameter of the first covering part is D1, the diameter of the second covering part is D2, the total area of ​​the air outlet is S, and D1, D2 and S satisfy the following relationship: 1.5≤0.5×(D1+D2) / ≤5.0, π is the square root of π, and π is the value of a circle.

2. The compressor according to claim 1, characterized in that, The diameter of the first cover is greater than the diameter of the exhaust hole, and the ratio of the sum of the diameters of the first cover and the second cover to twice the diameter of the exhaust hole is greater than or equal to 0.8 and less than or equal to 2.

3. The compressor according to claim 1, characterized in that, The first valve plate also has a first connecting portion, which is connected to the bearing, and the first covering portion is connected to the first connecting portion; The second valve plate also has a second connecting portion, which is disposed on the side of the first connecting portion away from the bearing, and the second cover portion is connected to the second connecting portion; The bearing assembly also includes a gasket disposed between the first connecting portion and the second connecting portion.

4. The compressor according to claim 3, characterized in that, Also includes: A limiter is provided on the side of the second valve plate away from the first valve plate, and is used to limit the movement of the second valve plate.

5. The compressor according to claim 4, characterized in that, The limiter includes a third connecting part and a limiting part, the third connecting part being connected to the second connecting part, and the limiting part being bent away from the second valve plate.

6. The compressor according to claim 3, characterized in that, The second cover portion bends relative to the second connecting portion toward the exhaust port; or The second cover portion bends away from the vent relative to the second connecting portion; or The second cover portion is not bent relative to the second connecting portion.

7. The compressor according to claim 3, characterized in that, The first cover portion bends toward the exhaust port relative to the first connecting portion.

8. The compressor according to claim 1, characterized in that, The thickness of the second valve plate is greater than or equal to the thickness of the first valve plate.

9. The compressor according to claim 1, characterized in that, Also includes: A cylinder connected to the bearing assembly, the cylinder having a compression chamber and a slide groove in communication with each other; A piston is rotatably disposed within the compression chamber, and a groove is provided on the outer peripheral wall of the piston; A sliding plate is slidably disposed in the groove, and one end of the sliding plate has a connecting part, which is embedded in the groove, so that the sliding plate and the piston form a hinged connection.

10. The compressor according to claim 9, characterized in that, The groove opening is provided with a chamfered structure.

11. The compressor according to claim 10, characterized in that, The chamfering structure includes a first chamfering structure and a second chamfering structure. The first chamfering structure is connected to the groove wall of the groove, and the second chamfering structure is connected to the outer surface of the piston. The size of the first chamfering structure is 0.1 mm to 1 mm, and the size of the second chamfering structure is 0.5 mm to 1.5 mm.

12. The compressor according to claim 9, characterized in that, Also includes: A spring hole extending from the outer periphery of the cylinder to the center of the cylinder; An oil groove is provided in the cylinder and is connected to the spring hole and the slide groove respectively.

13. The compressor according to claim 12, characterized in that, Also includes: A tool retraction hole is provided in the cylinder, and the tool retraction hole is connected to the end of the slide groove away from the center of the cylinder; Wherein, the distance between the end of the spring hole near the compression chamber and the retraction hole is L1, and the width of the oil groove along the movement direction of the slide is L2, 0.06≤L2 / L1≤0.

35.

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

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