Compressor and refrigeration apparatus

Abstract

The application provides a compressor and a refrigeration device, and aims to at least solve the technical problem of poor lubrication effect of a sliding vane caused by improper setting of an oil groove in the prior art. The compressor comprises: a cylinder, the cylinder having a compression chamber and a sliding groove, and an oil inlet hole being arranged on the outer wall surface of the cylinder; a piston, rotatably arranged in the compression chamber; a sliding vane, slidably arranged in the sliding groove, and one end of the sliding vane being hingedly connected to the piston; and an oil groove, arranged on the cylinder, and in communication with the oil inlet hole and the sliding groove, and the oil groove being distributed on both sides of the sliding vane along the radial direction of the piston, and the distances from the oil grooves on both sides of the sliding vane to the center of the cylinder being the same or different. The compressor provided by the application can adapt to the lubrication requirements under different working conditions and further improve the lubrication 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] The cylinder of a compressor typically has a sliding groove, in which a sliding vane is slidably positioned. A spring or high-pressure gas pushes the vane against the outer wall of the piston, ensuring a seal in the compression chamber. To guarantee proper lubrication between the vane and the groove, the cylinder usually has an oil inlet and an oil groove. Lubricating oil enters the oil groove through the inlet and then flows into the groove to lubricate the vane.

[0003] However, the oil sump position of existing compressors is often not set reasonably, resulting in uneven distribution of lubricating oil during the reciprocating motion of the vanes. Some parts of the vanes are difficult to be fully lubricated, which can easily lead to increased wear, increased frictional power consumption, or even jamming, seriously affecting the reliability and service life of the compressor. Summary of the Invention

[0004] The present invention aims to at least solve the technical problem in the related art that improper setting of the oil groove position leads to poor lubrication effect of the sliding plate.

[0005] The first aspect of the present invention provides a compressor, comprising: a cylinder having a compression chamber and a slide groove, and an oil inlet hole provided on the outer wall surface of the cylinder; a piston rotatably disposed in the compression chamber; a slide vane slidably disposed in the slide groove, and one end of the slide vane being hinged to the piston; and an oil groove disposed in the cylinder, communicating with the oil inlet hole and the slide groove respectively, wherein the oil groove is distributed on both sides of the slide vane along the radial direction of the piston, and the distance of the oil groove on both sides of the slide vane from the center of the cylinder is the same or different.

[0006] The compressor provided by this invention includes a cylinder, which is the body component of the compressor. Its internal compression chamber accommodates a piston and forms a working volume. A sliding groove is disposed on the cylinder to accommodate and guide the reciprocating motion of a sliding vane. An oil inlet is located on the outer wall of the cylinder and serves as the inlet for lubricating oil. The piston is rotatably disposed within the compression chamber, forming a closed working chamber together with the cylinder and the sliding vane. The sliding vane is slidably disposed within the sliding groove, with one end hinged to the piston, allowing the vane to reciprocate within the groove as the piston rotates, while maintaining constant contact with the piston. An oil groove is disposed on the cylinder, with one end connected to the oil inlet and the other end connected to the sliding groove, forming a flow channel for lubricating oil.

[0007] The compressor provided by this invention, by distributing oil grooves on both sides of the sliding vane, allows lubricating oil to enter the grooves simultaneously from both sides of the vane, providing uniform lubrication to both working surfaces of the vane. This avoids lubrication dead zones caused by unilateral oil supply and significantly improves the lubrication effect of the vane. By controlling the distance between the oil grooves on both sides of the vane and the cylinder center to be the same or different, the distribution of lubricating oil can be flexibly adjusted. When the distances on both sides are the same, the processing of the oil grooves is simpler, which helps to reduce manufacturing costs and simplifies the oil circuit layout. When the distances on both sides are different, the radial coverage of the lubricating oil is wider, which can adapt to the lubrication needs under different operating conditions and further improve the lubrication effect. Therefore, this technical solution effectively solves the problem of poor vane lubrication and improves the reliability and service life of the compressor.

[0008] Optionally, in the above technical solution, the compressor further includes a bearing assembly, which includes: a bearing connected to the cylinder, the bearing having an exhaust port; a first valve plate disposed on the bearing, the first valve plate including a sealing portion for closing or opening the exhaust port; a second valve plate disposed on the side of the first valve plate away from the bearing, the second valve plate including an abutment portion corresponding to the sealing portion, and a gap being provided between the abutment portion and the sealing portion; and a limiter disposed on the side of the second valve plate away from the first valve plate for limiting the abutment portion.

[0009] In this technical solution, the bearing assembly is connected to the cylinder to support the compressor crankshaft and control gas discharge. The bearing has an exhaust port for discharging the compressed high-pressure gas. A first valve plate is mounted on the bearing, and its sealing portion quickly closes the exhaust port at the end of the exhaust process to prevent backflow of high-pressure gas. A second valve plate is located on the side of the first valve plate away from the bearing, with its abutting portion corresponding to the sealing portion of the first valve plate, and a certain gap existing between them. A limiter is located on the side of the second valve plate away from the first valve plate to limit the opening height of the second valve plate.

[0010] This technical solution employs a dual-valve structure, enabling the valve assembly to adapt to the compressor's operating requirements at different frequencies. During low-frequency operation, only the first valve operates, flexibly responding to minute changes in gas pressure. During high-frequency operation, the first valve drives the second valve to move together, jointly resisting the impact of high-frequency airflow, thereby improving the valve assembly's reliability and service life. This dual-valve structure effectively reduces exhaust noise and enhances the compressor's overall performance.

[0011] In the above technical solution, optionally, the axial distance between the closing part and the abutting part is T2, the abutting part is a circular structure, the axial distance between the center of the abutting part near the limiter and the surface of the limiter facing the second valve plate is T4, the thickness of the limiter is T5, and the relationship is satisfied: 0.8≤T5 / (T2+T4)≤2.5.

[0012] In this technical solution, T2 represents the initial distance between the first and second valve plates, which is the stroke that the first valve plate can move independently before contacting the second valve plate. T4 represents the distance from the center of the contact portion of the second valve plate to the surface of the limiter, which is the stroke that the second valve plate can continue to move after being pushed by the first valve plate. The sum of T2 and T4 constitutes the maximum opening height of the valve assembly, i.e., the total lift. T5 is the thickness of the limiter itself.

[0013] This technical solution achieves an optimal balance between limiter strength and valve assembly space utilization by limiting the ratio of limiter thickness T5 to total lift (T2+T4) to between 0.8 and 2.5. When the ratio is below 0.8, the limiter is too thin and prone to fatigue fracture under repeated impacts from the second valve plate during high-frequency operation, leading to valve assembly failure. When the ratio is above 2.5, the limiter is too thick and heavy, which will occupy the effective space of the exhaust chamber, increase exhaust resistance, and reduce compressor efficiency. Therefore, this technical solution precisely controls this ratio to ensure sufficient strength of the limiter while optimizing the exhaust flow area, thereby improving the reliability and efficiency of the compressor.

[0014] In the above technical solution, T4 and T2 can optionally satisfy the following relationship: 5.0≤T4 / T2≤7.0.

[0015] In this technical solution, the ratio of T4 / T2 reflects the stroke distribution relationship between the first and second valve plates. By setting T4 to 5 to 7 times T2, a gradient matching of valve plate stiffness is achieved. When the compressor operates at low frequency, the gas pressure is relatively low, and the first valve plate moves independently within the small stroke range of T2. Utilizing its low stiffness characteristics, it opens slightly with the airflow, avoiding premature contact with the second valve plate and the resulting slapping noise. When the compressor speed increases and the discharge volume increases, the first valve plate can promptly surpass the T2 stroke and push the second valve plate, extending the total lift to T4. The high stiffness of the second valve plate withstands the impact of high-frequency airflow, preventing valve plate flutter and breakage. This stroke distribution method allows the valve assembly to automatically adjust the opening height and stiffness according to the compressor speed, balancing low noise during low-frequency operation and high reliability during high-frequency operation.

[0016] 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.

[0017] In this technical solution, by setting the thickness of the second valve plate to be no less than that of the first valve plate, the second valve plate has greater stiffness than the first valve plate. This further enhances the stiffness grading characteristics of the dual valve plate structure, ensuring that the first valve plate with lower stiffness mainly operates at low frequencies, while the second valve plate with higher stiffness provides sufficient strength to resist impact at high frequencies, thus optimizing the dynamic response characteristics of the valve assembly.

[0018] Optionally, in the above technical solution, the bearing assembly further includes: a gasket; the first valve plate further includes a first connecting portion, disposed on the bearing and connected to the sealing portion; the second valve plate further includes a second connecting portion, disposed on the side of the first connecting portion away from the bearing and connected to the abutting portion; the gasket is disposed between the second connecting portion and the first connecting portion.

[0019] In this technical solution, the first connecting part of the first valve plate and the second connecting part of the second valve plate are used to fix the valve plates to the bearing, forming a cantilever beam structure. A gasket is placed between the two connecting parts, serving as a spacer and support. The thickness T2 of the gasket determines the initial gap between the first and second valve plates, i.e., the independent working stroke of the first valve plate. This structure is simple and reliable, easy to assemble and adjust, and provides a basis for precise control of the valve plate stroke.

[0020] In the above technical solution, optionally, the thickness of the second valve plate is T1, the thickness of the first valve plate is T3, and T1, T2, T3 and T5 satisfy the following relationship: 2.0≤T5 / (T1+T2+T3)≤8.0.

[0021] In this technical solution, T1 + T2 + T3 constitute the total thickness of the valve assembly. This solution further defines the ratio of the limiter thickness T5 to the total valve assembly thickness. When the ratio is below 2.0, the limiter is insufficiently strong and cannot withstand high-frequency impacts; when the ratio is above 8, the limiter is too thick, affecting exhaust efficiency. By controlling this ratio, the limiter and the overall valve assembly structure are more coordinated, further optimizing the compressor's exhaust performance and reliability.

[0022] Optionally, in the above technical solution, the sealing part bends toward the exhaust port relative to the first connecting part.

[0023] In this technical solution, the sealing portion of the first valve plate is designed with a curved shape, allowing it to better fit the exhaust port and improve the sealing effect. This structural design reduces the resistance when the valve plate opens, while enhancing the sealing performance when closed, thus helping to improve the volumetric efficiency of the compressor.

[0024] 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.

[0025] 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.

[0026] Optionally, in the above technical solution, a groove is provided on the outer peripheral wall of the piston, and one end of the sliding plate has a connecting part, which is embedded in the groove.

[0027] In this technical solution, the groove on the piston and the connecting part at the end of the slide plate form a fitting structure, realizing a hinged connection between the slide plate and the piston. This hinged structure allows the slide plate to have a certain degree of swing freedom relative to the piston while rotating with it, which can better adapt to the piston's movement trajectory and reduce friction and wear.

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

[0029] In this technical solution, the connecting part can be circular or other shapes, and correspondingly, the groove of the piston is also set to a matching arc shape. This shape-matching design can ensure that the contact stress distribution between the slide and the piston is uniform, avoid local stress concentration, and improve the reliability and service life of the hinge structure.

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

[0031] In this technical solution, the first chamfer (connecting groove wall) is mainly used to reduce the root stress when the connecting part swings within 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 defining a specific dimensional range, the reliability and durability of this hinge structure under various working conditions are ensured.

[0032] In the above technical solution, optionally, the size of the first chamfer structure is 0.1mm to 0.5mm, and the size of the second chamfer structure is 0.5mm to 1.2mm.

[0033] Optionally, in the above technical solution, the compressor further includes: a spring hole, which extends from the outer wall of the cylinder toward the center of the cylinder, and an oil inlet is formed at one end of the spring hole near the outer wall of the cylinder; the oil groove is connected to the spring hole and the slide groove respectively.

[0034] In this technical solution, the compressor also includes a spring bore. The spring bore extends from the outer periphery of the cylinder towards the center of the cylinder, and an oil groove communicates with both the spring bore and the slide groove. The oil groove is configured to create a lubricating oil channel between the spring bore and the slide groove. Lubricating oil can flow from the spring bore (oil reservoir) to the slide groove through the oil groove, lubricating and cooling the friction pair between the vane and the slide groove. It also lubricates the hinge joint between the vane and the piston, significantly reducing friction loss and improving the compressor's mechanical efficiency and reliability.

[0035] Optionally, in the above technical solution, the compressor further includes: a knife-removal hole, which 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 knife-removal hole is L1, and the width of the oil groove along the movement direction of the slide is L2, and satisfies the relationship: 0.06≤L2 / L1≤0.35.

[0036] 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.

[0037] 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

[0038] 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:

[0039] Figure 1 One of the structural schematic diagrams of the upper bearing assembly according to an embodiment of this application is shown;

[0040] Figure 2 One of the structural schematic diagrams of the lower bearing assembly according to an embodiment of this application is shown;

[0041] Figure 3 A schematic diagram of the structure of a compressor according to an embodiment of this application is shown;

[0042] Figure 4 A schematic diagram of the upper bearing according to an embodiment of this application is shown;

[0043] Figure 5 A schematic diagram of the structure of a lower bearing according to an embodiment of this application is shown;

[0044] Figure 6 An assembly diagram of the upper bearing assembly and the upper muffler according to one embodiment of this application is shown;

[0045] Figure 7 A second schematic diagram of the structure of a lower bearing assembly according to an embodiment of this application is shown;

[0046] Figure 8 One of the structural schematic diagrams of a compressor according to an embodiment of this application is shown;

[0047] Figure 9 A second schematic diagram of the compressor according to an embodiment of this application is shown;

[0048] Figure 10 The third schematic diagram shows the structure of a compressor according to one embodiment of this application;

[0049] Figure 11 The fourth schematic diagram shows the structure of a compressor according to one embodiment of this application;

[0050] Figure 12 A schematic diagram of the piston structure according to an embodiment of this application is shown;

[0051] Figure 13 A schematic diagram of the slider according to an embodiment of this application is shown;

[0052] Figure 14 This paper shows a schematic diagram of the assembly structure of the slider and the limiter according to an embodiment of this application;

[0053] Figure 15 A schematic diagram of the groove on a piston according to one embodiment of this application is shown;

[0054] Figure 16 The second schematic diagram of the upper bearing assembly according to one embodiment of this application is shown.

[0055] Among them, 1 is a bearing assembly, 11 is a bearing, 112 is an exhaust port, 12 is a first valve plate, 122 is a first connecting part, 124 is a sealing part, 132 is a gap, 134 is a gasket, 14 is a second valve plate, 142 is a second connecting part, 144 is an abutment part, 15 is a muffler, 152 is an air outlet, 16 is a limiter, 17 is a cylinder, 172 is a compression chamber, 174 is a slide groove, 176 is a spring hole, 177 is an oil inlet, 178 is an oil groove, 179 is a knife retraction hole, 18 is a piston, 182 is a groove, 184 is a groove wall, 19 is a slide plate, 192 is a connecting part, 194 is a chamfered structure, 195 is a first chamfered structure, 196 is a second chamfered structure, and 2 is a compressor. Detailed Implementation

[0056] 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.

[0057] 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.

[0058] like Figure 3 , Figure 8 , Figure 9 , Figure 10 and Figure 11 As shown, this embodiment provides a compressor 2, including a cylinder 17, a piston 18, a sliding vane 19, and an oil groove 178. The cylinder 17 has a compression chamber 172 and a sliding groove 174. An oil inlet hole 177 is provided on the outer wall surface of the cylinder 17. The piston 18 is rotatably disposed in the compression chamber 172. The sliding vane 19 is slidably disposed in the sliding groove 174, and one end of the sliding vane 19 is hinged to the piston 18. The oil groove 178 is disposed in the cylinder 17 and communicates with the oil inlet hole 177 and the sliding groove 174 respectively. Along the radial direction of the piston 18, the oil groove 178 is distributed on both sides of the sliding vane 19, and the distance of the oil groove 178 on both sides of the sliding vane 19 from the center of the cylinder 17 is the same or different.

[0059] The compressor 2 provided by this invention includes a cylinder 17, which is a body component of the compressor 2. Its internal compression chamber 172 accommodates a piston 18 and forms a working volume. A slide groove 174 is disposed on the cylinder 17 to accommodate and guide the reciprocating motion of a sliding vane 19. An oil inlet 177 is disposed on the outer wall of the cylinder 17 and serves as the inlet for lubricating oil. The piston 18 is rotatably disposed within the compression chamber 172, forming a closed working chamber together with the cylinder 17 and the sliding vane 19. The sliding vane 19 is slidably disposed within the slide groove 174, with one end hinged to the piston 18, allowing the vane 19 to reciprocate within the slide groove 174 as the piston 18 rotates, while maintaining constant contact with the piston 18. An oil groove 178 is disposed on the cylinder 17, with one end communicating with the oil inlet 177 and the other end communicating with the slide groove 174, forming a flow channel for lubricating oil.

[0060] The compressor 2 provided by this invention, by distributing oil grooves 178 on both sides of the vane 19, allows lubricating oil to enter the grooves 174 simultaneously from both sides of the vane 19, providing uniform lubrication to both working surfaces of the vane 19. This avoids lubrication dead zones caused by unilateral oil supply and significantly improves the lubrication effect of the vane 19. By controlling the distance of the oil grooves 178 on both sides of the vane 19 from the center of the cylinder 17 to be the same (e.g., ...), ... Figure 8 , Figure 9 and Figure 10 (as shown) or different (such as) Figure 11 As 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.

[0061] 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.

[0062] In the above technical solutions, optionally, such as Figure 1 , Figure 2 , Figure 4 , Figure 5 , Figure 14 and Figure 16 As shown, the compressor 2 also includes a bearing assembly 1, which includes: a bearing 11 connected to the cylinder 17, the bearing 11 having an exhaust port 112 with a diameter of D3; a first valve plate 12 disposed on the bearing 11, the first valve plate 12 including a sealing portion 124 for closing or opening the exhaust port 112; a second valve plate 14 disposed on the side of the first valve plate 12 away from the bearing 11, the second valve plate 14 including an abutment portion 144 corresponding to the sealing portion 124, and a gap 132 between the abutment portion 144 and the sealing portion 124; and a limiter 16 disposed on the side of the second valve plate 14 away from the first valve plate 12 for limiting the abutment portion 144.

[0063] In this technical solution, the bearing assembly 1 is connected to the cylinder 17 to support the crankshaft of the compressor 2 and control the gas discharge. The bearing 11 has an exhaust port 112 for discharging the compressed high-pressure gas. A first valve plate 12 is mounted on the bearing 11, and its closing portion 124 quickly closes the exhaust port 112 at the end of the exhaust process to prevent backflow of high-pressure gas. A second valve plate 14 is located on the side of the first valve plate 12 away from the bearing 11, and its abutment portion 144 corresponds to the closing portion 124 of the first valve plate 12, with a certain gap 132 between them. A limiter 16 is located on the side of the second valve plate 14 away from the first valve plate 12 to limit the opening height of the second valve plate 14.

[0064] This technical solution employs a dual-valve structure, enabling the valve assembly to adapt to the operating requirements of the compressor 2 at different frequencies. During low-frequency operation, only the first valve 12 operates, flexibly responding to minute changes in gas pressure. During high-frequency operation, the first valve 12 drives the second valve 14 to move together, jointly resisting the impact of high-frequency airflow, thereby improving the reliability and service life of the valve assembly. This dual-valve structure effectively reduces exhaust noise and enhances the overall performance of the compressor 2.

[0065] Understandably, the bearing assembly 1 of this application includes an upper bearing assembly (such as...) Figure 1 and Figure 4 (as shown) and the lower bearing assembly (as shown) Figure 2 , Figure 5 and Figure 7 As shown), the upper bearing assembly and the lower bearing assembly are respectively located on both sides of the cylinder 17. Figure 6 As shown, the compressor 2 also includes a muffler 15, which includes an upper muffler and a lower muffler. The upper muffler is assembled with an upper bearing assembly, and the lower muffler is assembled with a lower bearing assembly. The muffler 15 is provided with at least one air outlet 152 for discharging the gas passing through the muffler 15.

[0066] In the above technical solution, optionally, the axial distance between the closing part 124 and the abutting part 144 is T2, the abutting part 144 is a circular structure, the axial distance between the center of the surface of the abutting part 144 near the limiter 16 and the surface of the limiter 16 facing the second valve plate 14 is T4, the thickness of the limiter 16 is T5, and the relationship is satisfied: 0.8≤T5 / (T2+T4)≤2.5.

[0067] In this technical solution, T2 represents the initial distance between the first valve plate 12 and the second valve plate 14, which is the stroke that the first valve plate 12 can move independently before contacting the second valve plate 14. T4 represents the distance from the center of the abutment portion 144 of the second valve plate 14 to the surface of the limiter 16, which is the stroke that the second valve plate 14 can continue to move after being pushed by the first valve plate 12. The sum of T2 and T4 constitutes the maximum opening height of the valve assembly, i.e., the total lift. T5 is the thickness of the limiter 16 itself.

[0068] This technical solution achieves an optimal balance between the strength of the limiter 16 and the space utilization of the valve assembly by limiting the ratio of the thickness T5 of the limiter 16 to the total lift (T2+T4) to between 0.8 and 2.5. When the ratio is below 0.8, the limiter 16 is too thin and is prone to fatigue fracture under repeated impacts from the second valve plate 14 during high-frequency operation, leading to valve assembly failure. When the ratio is above 2.5, the limiter 16 is too thick and heavy, which will occupy the effective space of the exhaust chamber, increase exhaust resistance, and reduce the energy efficiency of the compressor 2. Therefore, this technical solution optimizes the exhaust flow area and improves the reliability and energy efficiency of the compressor 2 by precisely controlling this ratio, ensuring that the limiter 16 has sufficient strength.

[0069] In the above technical solution, T4 and T2 can optionally satisfy the following relationship: 5.0≤T4 / T2≤7.0.

[0070] In this technical solution, the ratio of T4 / T2 reflects the stroke distribution relationship between the first valve plate 12 and the second valve plate 14. By setting T4 to 5 to 7 times T2, a gradient matching of valve plate stiffness is achieved. When the compressor 2 operates at low frequency, the gas pressure is relatively low, and the first valve plate 12 moves independently within the small stroke range of T2. Utilizing its low stiffness characteristics, it opens slightly with the airflow, avoiding premature contact with the second valve plate 14 and preventing slapping noise. When the compressor 2 speed increases and the discharge volume increases, the first valve plate 12 can promptly exceed the T2 stroke and push the second valve plate 14, extending the total lift to T4. The high stiffness of the second valve plate 14 withstands the impact of high-frequency airflow, preventing valve plate flutter and breakage. This stroke distribution method allows the valve assembly to automatically adjust the opening height and stiffness according to the compressor 2 speed, balancing low noise during low-frequency operation and high reliability during high-frequency operation.

[0071] 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.

[0072] In this technical solution, by setting the thickness of the second valve plate 14 to be no less than that of the first valve plate 12, the second valve plate 14 has greater stiffness than the first valve plate 12. This further enhances the stiffness grading characteristics of the dual valve plate structure, ensuring that the first valve plate 12 with lower stiffness mainly operates at low frequencies, while the second valve plate 14 with higher stiffness can provide sufficient strength to resist impact at high frequencies, thus optimizing the dynamic response characteristics of the valve assembly.

[0073] Optionally, in the above technical solution, the bearing assembly 1 further includes: a gasket 134; the first valve plate 12 further includes a first connecting portion 122, which is disposed on the bearing 11 and connected to the sealing portion 124; the second valve plate 14 further includes a second connecting portion 142, which is disposed on the side of the first connecting portion 122 away from the bearing 11 and connected to the abutting portion 144; the gasket 134 is disposed between the second connecting portion 142 and the first connecting portion 122.

[0074] In this technical solution, the first connecting portion 122 of the first valve plate 12 and the second connecting portion 142 of the second valve plate 14 are used to fix the valve plates to the bearing 11, forming a cantilever beam structure. A gasket 134 is disposed between the two connecting portions, serving as a spacer and support. The thickness T2 of the gasket 134 determines the initial gap 132 between the first valve plate 12 and the second valve plate 14, i.e., the independent working stroke of the first valve plate 12. This structure is simple and reliable, easy to assemble and adjust, and provides a basis for precise control of the valve plate stroke.

[0075] In the above technical solutions, optionally, such as Figure 14 As shown, the thickness of the second valve plate 14 is T1, the thickness of the first valve plate 12 is T3, and T1, T2, T3 and T5 satisfy the following relationship: 2.0≤T5 / (T1+T2+T3)≤8.0.

[0076] In this technical solution, T1 + T2 + T3 constitute the total thickness of the valve assembly. This solution further defines the ratio of the limiter 16 thickness T5 to the total valve assembly thickness. When the ratio is below 2.0, the limiter 16 lacks sufficient strength and cannot withstand high-frequency impacts; when the ratio is above 8, the limiter 16 is too thick, affecting exhaust efficiency. By controlling this ratio, the limiter 16 is more coordinated with the overall valve assembly structure, further optimizing the exhaust performance and reliability of the compressor 2.

[0077] In the above technical solution, optionally, the sealing part 124 bends relative to the first connecting part 122 toward the exhaust hole 112.

[0078] In this technical solution, the sealing portion 124 of the first valve plate 12 is configured in a curved shape, allowing it to better fit the exhaust port 112 and improve the sealing effect. This structural design reduces the resistance when the valve plate is opened, while enhancing the sealing performance when closed, which helps to improve the volumetric efficiency of the compressor 2.

[0079] 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.

[0080] 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.

[0081] In the above technical solutions, optionally, such as Figure 12 and Figure 13 As shown, a groove 182 is provided on the outer peripheral wall of the piston 18, and one end of the slide 19 has a connecting part 192, which is embedded in the groove 182.

[0082] In this technical solution, the groove 182 on the piston 18 and the connecting part 192 at the end of the slide 19 form a fitting structure, realizing the hinged connection between the slide 19 and the piston 18. This hinged structure allows the slide 19 to have a certain degree of swing freedom relative to the piston 18 while rotating with the piston 18, which can better adapt to the movement trajectory of the piston 18 and reduce friction and wear.

[0083] In the above technical solution, optionally, the connecting part 192 of the slide 19 is a circular connecting part or a non-circular connecting part, and the groove 182 of the piston 18 is an arc-shaped groove that matches the shape of the connecting part 192.

[0084] In this technical solution, the connecting part 192 can be circular or other shapes, and correspondingly, the groove 182 of the piston 18 is also set to a matching arc shape. This shape matching design can ensure that the contact stress distribution between the slide 19 and the piston 18 is uniform, avoid local stress concentration, and improve the reliability and service life of the hinge structure.

[0085] In the above technical solutions, optionally, such as Figure 12 and Figure 15 As shown, a chamfer structure 194 is provided at the opening of the groove 182. 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.

[0086] In this technical solution, the first chamfered structure 195, connected to the groove wall 184, is mainly used to reduce the root stress of the connecting part 192 when it swings within the groove 182. The second chamfered structure 196, connected to the outer surface of the piston 18, is mainly used for assembly guidance and to reduce the contact stress between the connecting part 192 and the surface of the piston 18. By defining a specific dimensional range, the reliability and durability of this hinge structure under various working conditions are ensured.

[0087] In the above technical solution, optionally, the size of the first chamfer structure 195 is 0.1mm to 0.5mm, and the size of the second chamfer structure 196 is 0.5mm to 1.2mm.

[0088] Optionally, in the above technical solution, the compressor 2 further includes: a spring hole 176, which extends from the outer wall of the cylinder 17 toward the center of the cylinder 17, and an oil inlet hole 177 is formed at one end of the spring hole 176 near the outer wall of the cylinder 17; and an oil groove 178 is connected to the spring hole 176 and the slide groove 174 respectively.

[0089] In this technical solution, the compressor 2 also includes a spring hole 176. The spring hole 176 extends from the outer periphery of the cylinder 17 towards the center of the cylinder 17, and an oil groove 178 communicates with both the spring hole 176 and the slide groove 174. The configuration of the oil groove 178 establishes a lubricating oil channel between the spring hole 176 and the slide groove 174. Lubricating oil can flow from the oil storage area of ​​the spring hole 176 to the slide groove 174 through the oil groove 178, lubricating and cooling the friction pair between the sliding vane 19 and the slide 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.

[0090] Optionally, in the above technical solution, the compressor 2 further includes: a knife-removal hole 179, which 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-removal hole 179 is L1, and the width of the oil groove 178 along the movement direction of the slide vane 19 is L2, and satisfies the relationship: 0.06≤L2 / L1≤0.35.

[0091] 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.

[0092] In the above technical solution, the compressor 2 may optionally be a low-noise wide-band compressor.

[0093] Another embodiment of the present invention provides a low-noise, wide-range compressor 2. It should be understood that conventional compressors 2 typically operate within a speed range of 15Hz to 120Hz, while the wide-range compressor 2 significantly extends its operating speed range to 1Hz to 200Hz. When the compressor 2's speed is extended downwards to 1Hz, the stress on the exhaust valve plate and the sliding vane 19 deteriorates, easily generating low-frequency abnormal noise and affecting noise quality. As the compressor 2's speed decreases, radial leakage between the sliding vane 19 and the piston 18 increases, reducing the compressor 2's energy efficiency. Furthermore, when the compressor 2's speed is extended upwards to 200Hz, the friction between the sliding vane 19 and the sliding groove 174 increases, leading to increased power consumption and further reducing the compressor 2's energy efficiency. The present invention can effectively improve the problems of increased noise and decreased energy efficiency present in the wide-range compressor 2.

[0094] The low-noise, wide-band compressor 2 provided in this embodiment employs a multi-valve assembly design for its exhaust valve group. The exhaust valves feature adaptive stiffness, allowing the smaller stiffness valve group to operate at ultra-low speeds, while the larger stiffness valve group works together at medium to high speeds. Simultaneously, the sliding vane 19 and piston 18 are hinged, preventing disengagement and reducing radial leakage. The cylinder 17's slide groove 174 is equipped with one or more oil grooves 178, positioned within the high back pressure range of the spring hole 176, ensuring lubrication of the sliding vane 19 and reducing friction.

[0095] Specifically, the low-noise wideband rotary compressor 2 provided by the present invention includes a cylinder 17, a sliding vane 19, a piston 18, and a sliding groove 174. The sliding vane 19 has a hinged structure, with a protruding circular or non-circular head (i.e., the connecting portion 192) at its tip. The piston 18 has a groove 182, and the protruding head of the sliding vane 19 is inserted into the corresponding groove 182 of the piston 18, forming a hinged structure. The groove 182 of the piston 18 has a chamfer, with the first chamfer structure 195 ranging from 0.1 mm to 0.5 mm and the second chamfer structure ranging from 0.5 mm to 1.2 mm. The sliding groove 174 has one or more oil grooves 178.

[0096] The low-noise wide-range rotary compressor 2 also includes a bearing assembly 1 sealed within a housing. The bearing assembly 1 includes a bearing 11, a lower valve plate (i.e., the aforementioned first valve plate 12), an upper valve plate (i.e., the aforementioned 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 a bearing seat, and a sealing 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 aforementioned first connecting portion 122) mates with the rivet hole of the bearing 11. The gasket 134 is placed on the lower valve plate and engages with it through the rivet hole. The upper valve plate is placed on and contacts the gasket 134. The limiter 16 is disposed on the upper valve plate to limit the lift height of both the upper and lower valve plates.

[0097] In the structure of this invention, the upper valve plate has a thickness T1, the gasket 134 has a thickness T2 (first lift), the lower valve plate has a thickness T3, and the limiter 16 corresponding to the center of the upper valve plate's contact portion 144 has a lift T4 (second lift), satisfying 5.0≤T4 / T2≤7.0 and T3≤T1. Therefore, the lower valve plate has low stiffness, while the upper valve plate has high stiffness, allowing the low stiffness of the upper valve plate and the high stiffness of the lower valve plate to work together better, balancing low noise and high energy efficiency in low-frequency operation with low noise and high reliability in high-frequency operation. The limiter 16 head thickness T5 has a relationship with the total thickness of the valve assembly of 2.0≤T5 / (T1+T2+T3)≤8.0, and further 2.5≤T5 / (T1+T2+T3)≤5.0. The sum of the first and second lifts of the exhaust valve assembly is T2 + T4. The thickness T5 of the limiter 16 head satisfies the relationship 0.8 ≤ T5 / (T2 + T4) ≤ 2.5 with respect to the sum of the first and second lifts. When compressor 2 operates at ultra-low frequency, the lower valve lift is relatively low, within the height range of T2. As the compressor 2 speed gradually increases, the lower valve lift gradually exceeds T2 and contacts the upper valve, pushing the upper valve to open. The limiter 16 lift corresponding to the center of the upper valve head is T4, which can better reduce valve assembly noise at low and high speeds.

[0098] 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.

[0099] 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.

[0100] 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 in that, include: A cylinder having a compression chamber and a slide groove, and an oil inlet hole provided on the outer wall surface of the cylinder; A piston is rotatably disposed within the compression chamber; A sliding plate is slidably disposed within the sliding groove, and one end of the sliding plate is hinged to the piston; An oil groove is provided in the cylinder and is connected to the oil inlet and the slide groove respectively. Along the radial direction of the piston, the oil groove is distributed on both sides of the slide plate, and the distance of the oil groove on both sides of the slide plate from the center of the cylinder is the same or different.

2. The compressor according to claim 1, characterized in that, It also includes a bearing assembly, the bearing assembly comprising: A bearing, connected to the cylinder, is provided with an exhaust port; A first valve plate is disposed on the bearing, and the first valve plate includes a sealing portion for closing or opening the exhaust port; The second valve plate is located on the side of the first valve plate away from the bearing. The second valve plate includes an abutment portion, which is disposed corresponding to the sealing portion, and a gap is provided between the abutment portion and the sealing portion. A limiter is disposed on the side of the second valve plate away from the first valve plate, and is used to limit the abutment portion.

3. The compressor according to claim 2, characterized in that, The axial distance between the closing part and the abutting part is T2. The abutting part is a circular structure. The axial distance between the center of the abutting part near the limiter and the surface of the limiter facing the second valve plate is T4. The thickness of the limiter is T5, and the following relationship is satisfied: 0.8≤T5 / (T2+T4)≤2.

5.

4. The compressor according to claim 3, characterized in that, The relationship between T4 and T2 is as follows: 5.0 ≤ T4 / T2 ≤ 7.

0.

5. The compressor according to claim 2, characterized in that, The thickness of the second valve plate is greater than or equal to the thickness of the first valve plate.

6. The compressor according to claim 3, characterized in that, The bearing assembly also includes: Gasket; The first valve plate further includes a first connecting portion disposed on the bearing and connected to the sealing portion; The second valve plate further includes a second connecting portion, which is located on the side of the first connecting portion away from the bearing and is connected to the abutting portion; The gasket is disposed between the second connecting part and the first connecting part.

7. The compressor according to claim 6, characterized in that, The thickness of the second valve plate is T1, the thickness of the first valve plate is T3, and T1, T2, T3 and T5 satisfy the following relationship: 2.0≤T5 / (T1+T2+T3)≤8.

0.

8. The compressor according to claim 6, characterized in that, The closure portion bends toward the vent relative to the first connecting portion.

9. The compressor according to claim 6, characterized in that, 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.

10. The compressor according to claim 1, characterized in that, The piston has a groove on its outer peripheral wall, and one end of the slide has a connecting part that is embedded in the groove.

11. The compressor according to claim 10, characterized in that, The connecting part of the slide can be a circular connecting part or a non-circular connecting part, and the groove of the piston is an arc-shaped groove that matches the shape of the connecting part.

12. The compressor according to claim 10, characterized in that, The groove opening is provided with a chamfer structure, which includes a first chamfer structure and a second chamfer structure. The first chamfer structure is connected to the groove wall, and the second chamfer structure is connected to the outer surface of the piston.

13. The compressor according to claim 1, characterized in that, Also includes: A spring hole extends from the outer wall of the cylinder towards the center of the cylinder, and the oil inlet hole is formed at one end of the spring hole near the outer wall of the cylinder. The oil groove is connected to the spring hole and the slide groove respectively.

14. The compressor according to claim 13, characterized in that, Also includes: A tool retraction hole, wherein 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, and satisfies the relationship: 0.06≤L2 / L1≤0.

35.

15. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 14.

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