Bearing assembly and compressor

Abstract

The embodiment of the invention provides a bearing assembly and a compressor, and the bearing assembly comprises a base, the base is provided with a valve seat groove, and the valve seat groove is internally provided with an exhaust hole used for being communicated with a cylinder hole in a cylinder; the valve plate structure is arranged in the valve seat groove; the lift limiter is arranged on the base, the lift limiter and the valve plate structure are correspondingly arranged, the lift limiter comprises a first head part, a tail part and a waist part connected between the first head part and the tail part, and the tail part is connected to the base; the thickness of the waist part is larger than that of the tail part, and the thickness of the first head part is larger than that of the tail part. According to the technical scheme, targeted structural adjustment is conducted on the lift limiter, and the dual purposes of vibration energy attenuation and noise radiation control are achieved through the synergistic effect of the acoustic black hole effect.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular, to a bearing assembly and a compressor. Background Art

[0002] Currently, a compressor usually has a valve plate disposed outside the exhaust hole of a bearing. When the air pressure of the compressed refrigerant gas reaches a certain level, the valve plate will open, and after the exhaust is completed, the valve plate will close to seal the exhaust hole, and a limiter for restricting the flow area is disposed outside the valve plate. In related technologies, when the compressor is operating, as Figure 6 shown, the valve plate usually collides with the lift limiter 106' to generate vibration, resulting in relatively large noise. Summary of the Invention

[0003] The present invention aims to at least solve the technical problem of relatively large noise generated between the valve plate and the limiter during the operation of the compressor in the prior art or related technologies.

[0004] In view of this, an embodiment of the first aspect of the present invention provides a bearing assembly.

[0005] An embodiment of the second aspect of the present invention provides a compressor.

[0006] To achieve the above object, an embodiment of the present invention provides a bearing assembly, including: a base, on which a valve seat groove is provided, and an exhaust hole for communicating with a cylinder hole on a cylinder is provided in the valve seat groove; a valve plate structure disposed in the valve seat groove; a lift limiter disposed on the base and corresponding to the valve plate structure, the lift limiter including a first head, a tail, and a waist connecting between the first head and the tail, and the tail is connected to the base; wherein, the thickness of the waist is greater than the thickness of the tail, and the thickness of the first head is greater than the thickness of the tail.

[0007] The bearing assembly according to the present invention includes a base, a valve plate structure, and a lift limiter. Among them, the valve plate structure is located in the valve seat groove of the base to block the exhaust hole, and the lift limiter is located above the valve plate structure to limit the displacement generated when the valve plate structure moves away from the exhaust hole side during exhaust. It should be emphasized that in this solution, the thickness of the lift limiter is changed, and the traditional limiter with a uniform thickness is adjusted stepwise. By utilizing the synergistic effect of the acoustic black hole effect, the dual goals of vibration energy attenuation and noise radiation control are achieved.

[0008] Specifically, as a structural carrier, a valve seat groove for accommodating the valve plate structure is provided on the base. Under the action of the valve seat groove, the valve plate and the exhaust hole can be accurately positioned. The transverse displacement of the valve plate is restricted by the groove wall, and the contact pressure distribution on the sealing surface is homogenized. The center line of the exhaust hole needs to correspond to the part of the first head. For example, when the first head is circular, the center line of the exhaust hole coincides with the center of the circle of the first head, so as to guide the airflow to discharge at a specific diffusion angle and reduce the turbulent noise.

[0009] The valve plate structure has a certain elasticity. The head of the valve plate structure is correspondingly arranged with the exhaust hole to realize the opening and closing of the exhaust hole. The tail of the lift limiter is directly connected to the base, and can be specifically fixed by the stepped rivet at the tail. The waist forms a wave impedance gradient region. By limiting the thickness size relationship of the waist, the first head and the tail, the lift limiter can utilize the acoustic black hole effect to gradually reduce the energy of the wave, and finally reduce the transmission of the vibration of the first head to the tail.

[0010] Among them, the head of the valve plate structure needs to contact the head of the lift limiter.

[0011] In some technical solutions, optionally, the ratio range of the thickness of the waist to the thickness of the tail is 1.1 - 2.25; and / or the ratio range of the thickness of the first head to the thickness of the tail is 1.28 - 3.

[0012] In this technical solution, by further limiting the thickness ratio of the lift limiter, the noise reduction effect can be improved. Specifically, the ratio range of the thickness of the waist to the thickness of the tail is 1.1 - 2.25. The thickness of the waist is increased compared with the thickness of the tail, and the increase amount is 10% - 125%, forming an increasing stiffness from the tail to the waist. Since the elastic modulus E is proportional to the cube of the thickness, the bending deformation of the waist can be inhibited.

[0013] Of course, the maximum bending stress is transferred from the root of the rivet to the center of the waist, and the stress amplitude will be reduced. In addition, the thickness gradient makes the vibration wave impedance gradually increase from the tail to the waist, and the reflection coefficient decreases from total reflection to partial transmission.

[0014] When the ratio is less than 1.1, the stiffness of the waist is insufficient, and the vibration transfer rate is relatively large, so that the reduction amplitude of the noise peak value is not enough to meet the noise reduction requirements.

[0015] When the ratio is greater than 2.25, at this time, the stiffness of the waist is too high, there is a delay in the opening of the valve plate, the volumetric efficiency decreases, and it is impossible to balance the stiffness and the response speed.

[0016] Regarding the thickness of the first head, by restricting the ratio between 1.28 and 3.0, the bending wave speed decreases as the thickness increases, and the wave front energy gathers towards the head, and a higher energy attenuation coefficient can be obtained.

[0017] Meanwhile, the thickening of the head increases the length of the valve plate contact area, prolongs the collision time, and reduces the peak impact force.

[0018] If the ratio is less than 1.28, the acoustic black hole effect is weak at this time, the energy aggregation coefficient is small, and the reduction amplitude of the noise peak at 2500 Hz is not sufficient to meet the noise reduction requirements.

[0019] If the ratio is greater than 3.0, the overweight head causes the first-order frequency to drop to a value with a small frequency interval from the stator frequency, which is prone to the risk of modal coupling.

[0020] It can be understood that the thickness of the waist is greater than that of the tail, and the thickness of the first head is greater than that of the tail.

[0021] In some technical solutions, optionally, the thicknesses of the first head, the waist, and the tail decrease in sequence; or the thicknesses of the waist, the first head, and the tail decrease in sequence.

[0022] According to the different arrangement orders of the thicknesses of each part of the lift limiter, its dynamic characteristics and noise control effects will change. Specifically, when the thickness of the first head is limited to be the thickest, the acoustic black hole effect is maximized, a significant wave speed decreasing area is formed, the energy attenuation coefficient is larger, and at the same time, the low stiffness design of the tail forms a flexible connection.

[0023] When the thickness of the waist is limited to be the thickest, the maximum stress transfers from the root of the rivet to the center of the waist, the stress amplitude decreases, and at the same time, the stiffness of the waist is increased, and the overall deformation of the limiter is smaller. In addition, since the thickness of the waist is the thickest, which is greater than both the thickness of the first head and the thickness of the tail, it causes wave impedance mismatch, increases the reflection coefficient, and reduces the energy transmittance.

[0024] Furthermore, when the compressor is mainly dominated by high-frequency noise (>2000 Hz) and the rotational speed >6000 rpm, the thickening design of the head can maximize the acoustic black hole effect.

[0025] In the case of medium and low-frequency vibration dominance (<2000 Hz) or high-pressure working conditions (refrigerant pressure >4 MPa), the thickening design of the waist is more advantageous.

[0026] Generally speaking, when the thickness of the first head is the thickest, deep suppression of high-frequency noise can be achieved through the energy aggregation of the first head, and when the thickness of the waist is the thickest, the control ability of medium-frequency vibration is enhanced through the strengthening of the waist stiffness.

[0027] Furthermore, when the thickness of the first head is limited to be the thickest, holes can be dug in the first head, and when the thickness of the waist is limited to be the thickest, the gradient can be adjusted.

[0028] In some technical solutions, optionally, one side wall surface of the lift limiter facing the valve plate structure includes a smoothly transitioning lower plane section and a lower curved surface section. The tail and a part of the waist form the lower plane section on the side facing the valve plate structure, and the first head and the other part of the waist form the lower curved surface section on the side facing the valve plate structure.

[0029] In this solution, the lower surface of the lift limiter, that is, the side wall surface facing the valve plate structure, includes a lower plane section and a lower curved surface section that are smoothly transitionally connected. The lower plane section involves the tail and the first half of the waist. A certain distance is maintained between the lower plane section and the valve plate structure to form a laminar boundary layer and reduce the airflow separation noise. At the same time, as the initial contact area between the lift limiter and the valve plate structure, the lower plane section needs to provide a stable pre-tightening force.

[0030] The lower curved surface section involves the first head and the second half of the waist. The lower curved surface section guides the first head of the valve plate to open at a specific inclination angle, such as 15° - 25°, thereby reducing the lateral impact component. In addition, the curvature of the lower curved surface section needs to be coupled with the thickness gradient to increase the rate of decrease in the bending wave speed.

[0031] It should be added that the lower plane section can maintain the Reynolds number through gap control and reduce the friction noise, while the lower curved surface section induces airflow acceleration through curvature but suppresses the generation of turbulence through diffusion design.

[0032] The lower plane section provides linear guidance, and the lower curved surface section turns into an involute trajectory, thereby reducing lateral vibration.

[0033] In some technical solutions, optionally, a connection hole is provided at the tail. The connection hole is used to cooperate with the base to be connected to the base. On the side wall surface of the first head facing the valve plate structure, a reference position corresponding to the axis of the exhaust hole is provided; wherein, along the extension direction of the lower plane section, the ratio range of the second length between the connecting part of the lower plane section and the lower curved surface section and the axis of the connection hole to the first length between the reference position and the axis of the connection hole is 0.3 - 0.55.

[0034] By providing a connection hole at the tail and simultaneously providing a reference position on the bottom of the first head, that is, on the side wall surface facing the valve plate structure, to respectively define the positions corresponding to the reference position and the lower plane section. That is, along the extension direction of the lower plane section, the ratio range of the second length between the connecting part of the lower plane section and the lower curved surface section and the axis of the connection hole to the first length between the reference position and the axis of the connection hole is 0.3 - 0.55, which can balance stiffness and modal separation.

[0035] Specifically, the connection hole is in interference fit with the base to suppress the high-frequency vibration mode. The reference position is set at the position of the first head, and its specific position is aligned with the axis of the exhaust hole to ensure full coverage of the exhaust hole when the valve plate is closed and reduce the leakage rate.

[0036] L1 is the distance from the reference position to the axis of the connecting hole, that is, the effective working length of the stopper.

[0037] L2 is the distance from the connection point of the lower plane section and the lower curved surface section to the axis of the connecting hole.

[0038] By restricting the length ratio L2 / L1 = 0.3 - 0.55, both low-frequency control and high-frequency optimization can be taken into account.

[0039] In some technical solutions, optionally, in the thickness direction of the tail, the ratio range of the vertical distance between the reference position and the plane where the lower plane section is located to the thickness of the tail is 0.5 - 0.88.

[0040] In this technical solution, the vertical distance from the reference position (the contact point between the head and the valve plate) to the lower plane section of the tail, that is, the effective lift height h of the lift stopper, and the thickness of the rigid section where the stopper is connected to the base, that is, the tail thickness T1. By restricting 0.5 < h / T1 < 0.88, the balance relationship between the lift constraint of the stopper on the valve plate and its own bending stiffness can be controlled, and at the same time, it also directly affects the transfer efficiency of vibration energy from the valve plate to the stopper.

[0041] Specifically, the lift height h is positively correlated with the area of the exhaust hole, and the cube of the tail thickness T1 is proportional to the stiffness. When the ratio h / T1 increases, the equivalent stiffness decreases, and the first-order bending frequency will decrease accordingly.

[0042] When h / T1 < 0.5, the lift is insufficient, the air flow is blocked, and the efficiency decreases. When h / T1 > 0.88, the impact speed of the valve plate is too high, affecting the fatigue life.

[0043] By restricting the ratio of h and T1, the transmission rate can be reduced, the noise can be reduced, and the leakage rate can be controlled.

[0044] In some technical solutions, optionally, one side wall surface of the first head away from the valve plate structure includes a first upper curved surface section, one side wall surface of the waist away from the valve plate structure includes a second upper curved surface section and a first upper plane section with a smooth transition, and one side wall surface of the tail away from the valve plate structure includes a second upper plane section; wherein, the first upper plane section and the second upper plane section are in a stepped shape, and the first upper curved surface section and the second upper curved surface section are in a stepped shape.

[0045] In this solution, the upper wall surfaces of the first head, the waist, and the tail are respectively structurally divided. A part of the first head and the waist is in a curved surface step shape, and another part of the waist and the tail is in a flat surface step shape. The first upper curved surface section disperses the head vibration energy through the surface curvature, reducing the energy density. At the same time, it also guides the back airflow to flow at a specific diffusion angle, reducing the eddy current shedding noise. The second upper curved surface section connects the head and the tail, reducing the stress concentration coefficient. At the same time, through the surface mass distribution, the first-order frequency of the limiter is increased, as far away from the stator elliptical frequency as possible. The first upper flat surface section reflects a part of the medium-frequency vibration energy back to the head dissipation area, and the second upper flat surface section is mainly used for high-frequency vibration isolation, suppressing vibration transmission above 4000 Hz.

[0046] Generally speaking, through the structural division of the upper wall surface, this solution extends the acoustic black hole effect from the thickness gradient to the three-dimensional curved surface-step composite structure, realizing the global control of vibration energy. This design is especially suitable for high-speed variable-frequency compressors (above 9000 rpm) and can still maintain low noise and high reliability under extreme working conditions.

[0047] In some technical solutions, optionally, on the plane passing through the axis of the connection hole of the tail and the reference position of the first head, the profile radii corresponding to the first upper curved surface section, the second upper curved surface section, and the lower curved surface section are the same.

[0048] By limiting the surface radii of the lift limiter, specifically restricting the surface radii of the first upper curved surface section, the second upper curved surface section, and the lower curved surface section to be the same, the upper and lower surfaces of the lift limiter are kept parallel before and after the step, ensuring the uniformity of the thickness of each part and making it more convenient for processing.

[0049] Furthermore, taking the plane passing through the axis of the tail connection hole and the reference position of the first head as the symmetry plane, the back surface curvature of the lift limiter is exactly the same as that of the lower plane section, forming a fully symmetric profile, realizing the geometric coordination of the vibration wave propagation path. The unified curvature radius makes the bending wave speed change uniformly along the entire length of the limiter, avoiding wave reflection caused by sudden curvature changes, increasing the energy transmittance, having a small phase difference when the vibration wave propagates in the head, waist, and tail, reducing the risk of modal coupling, and improving the stability of the first-order bending frequency.

[0050] In some technical solutions, optionally, the valve plate structure includes a second head opposite to the exhaust hole, and the ratio range of the radius of the second head to the radius of the first head is 1.05 - 1.45.

[0051] In this technical solution, by restricting the radius ratio relationship between the opposite second head and the first head, the contact stress can be reduced, the contact time can be extended, and the peak value of the impact force power spectral density can be reduced. In addition, the leakage rate can also be reduced to ensure the noise reduction effect.

[0052] It can be understood that when the ratio is less than 1.05, it is close to point contact, and stress concentration may cause microcracks. When the ratio is greater than 1.45, the contact area is too long, the stiffness of the valve plate is insufficient, and the response is delayed.

[0053] In some technical solutions, optionally, the projection of the lift limiter on the plane where the valve plate structure is located covers the valve plate structure.

[0054] In this technical solution, by limiting the lift limiter to have a relatively large size, it can cover the valve plate structure to ensure that after the valve plate structure opens the exhaust hole, contact occurs between the valve plate structure and the lift limiter, ensuring the uniformity of the contact and reducing the leakage rate.

[0055] In some technical solutions, optionally, the ratio range of the thickness of the tail to the thickness of the valve plate structure is 8 - 14.5.

[0056] In this technical solution, by restricting the ratio of the thickness of the tail to the thickness of the valve plate structure, the speed at which the head of the valve plate impacts the head of the limiter can be effectively reduced.

[0057] In some technical solutions, optionally, the first - order bending natural frequency of the lift limiter is greater than 2400 Hz; wherein, the ratio range of the first - order bending natural frequency of the base to the first - order bending natural frequency of the lift limiter is 1.05 - 1.2, and the difference between the first - order bending natural frequency of the base and the first - order bending natural frequency of the lift limiter is greater than 300 Hz, and the ratio range of the first - order bending natural frequency of the valve plate structure to the first - order bending natural frequency of the lift limiter is 0.08 - 0.13.

[0058] In this technical solution, by restricting the first - order bending natural frequencies of the lift limiter, the base, and the valve plate structure, the possible modal coupling between multiple structural components can be effectively avoided, reducing the resonance noise and vibration of the compressor.

[0059] An embodiment of the second aspect of the present application provides a compressor, including: a cylinder, with a cylinder hole provided on the cylinder; any one of the above - mentioned bearing assemblies, provided on the end face of at least one end of the cylinder.

[0060] According to the compressor provided by the present application, including a cylinder, by arranging any one of the above - mentioned bearing assemblies at at least one end of the cylinder, that is, using the bearing assembly as the upper bearing or lower bearing of the cylinder, the noise reduction effect can be effectively achieved during the operation of the compressor.

[0061] Since the compressor includes any one of the above - mentioned bearing assemblies, it has the beneficial effects of any one of the above - mentioned bearing assemblies, which will not be elaborated here.

[0062] In some technical solutions, optionally, the compressor includes a stator assembly, and the ratio range of the elliptical natural frequency of the stator assembly to the first-order bending natural frequency of the lift limiter is 0.7 to 0.85.

[0063] In this technical solution, by limiting the ratio of the elliptical natural frequency of the stator assembly to the first-order bending natural frequency of the lift limiter, and the limited ratio range is between 0.7 and 0.85, the modal coupling between the stator assembly and the lift limiter is avoided, and the resonance noise and vibration of the compressor are reduced.

[0064] The additional aspects and advantages of the present invention will become apparent in the following description section, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0065] Figure 1 The structural schematic diagram of a bearing assembly according to an embodiment of the present invention is shown;

[0066] Figure 2 The structural schematic diagram of a lift limiter according to an embodiment of the present invention is shown;

[0067] Figure 3 The structural schematic diagram of a lift limiter according to an embodiment of the present invention is shown;

[0068] Figure 4 The structural schematic diagram of a lift limiter according to an embodiment of the present invention is shown;

[0069] Figure 5 The structural schematic diagram of a valve plate structure according to an embodiment of the present invention is shown;

[0070] Figure 6 The structural schematic diagram in the related art is shown;

[0071] Figure 7 The schematic diagram of the noise reduction effect corresponding to the bearing assembly applying an embodiment of the present invention is shown;

[0072] Figure 8 The structural schematic diagram of a compressor according to an embodiment of the present invention is shown;

[0073] Figure 9 The structural schematic diagram of a compressor according to an embodiment of the present invention is shown.

[0074] Wherein, Figures 1 to 9 The corresponding relationship between the reference numerals in the drawings and the component names is as follows:

[0075] 100: Bearing assembly; 102: Base; 1022: Valve seat groove; 1024: Exhaust hole; 104: Valve plate structure; 1042: Second head; 106: Lift limiter; 1062: First head; 1063: Reference position; 1064: Waist; 1066: Tail; 1067: Connecting hole; 1072: Lower plane section; 1074: Lower curved surface section; 1076: First upper plane section; 1078: Second upper plane section; 1080: First upper curved surface section; 1082: Second upper curved surface section;

[0076] 200: Compressor; 202: Cylinder; 2022: Cylinder bore; 204: Stator assembly;

[0077] The corresponding relationship between the reference numerals and component names in the related art is as follows:

[0078] 106’: Lift limiter. Detailed implementation manners

[0079] In order to more clearly understand the above objects, features, and advantages of the embodiments of the present invention, the embodiments of the present invention will be further described in detail below with reference to the accompanying drawings and specific implementation manners. It should be noted that, without conflict, the embodiments of the present application and the features in the embodiments may be combined with each other.

[0080] Many specific details are set forth in the following description in order to fully understand the present application. However, the embodiments of the present invention may also be implemented in other ways different from those described herein. Therefore, the protection scope of the present application is not limited to the limitations of the specific embodiments disclosed below.

[0081] The following refers to Figures 1 to 9 Describe some embodiments according to the present invention.

[0082] As Figure 1 and Figure 2 shown, this embodiment provides a bearing assembly 100, including a base 102, a valve plate structure 104, and a lift limiter 106. Among them, the valve plate structure 104 is located in the valve seat groove 1022 of the base 102 to block the exhaust hole 1024, and the lift limiter 106 is located on the upper side of the valve plate structure 104 to limit the displacement generated when the valve plate structure 104 moves away from the exhaust hole side during exhaust. It should be emphasized that in this solution, the thickness of the lift limiter 106 is changed, and the traditional uniformly thick limiter is adjusted stepwise. By utilizing the synergistic effect of the acoustic black hole effect, the dual goals of vibration energy attenuation and noise radiation control are achieved.

[0083] Specifically, the base 102 serves as a structural carrier. A valve seat groove 1022 for accommodating the valve plate structure 104 is provided on the base 102. Under the action of the valve seat groove 1022, the valve plate and the exhaust hole 1024 can be accurately positioned. The transverse displacement of the valve plate is restricted by the groove wall, and the contact pressure distribution on the sealing surface is uniformized. The center line of the exhaust hole 1024 needs to correspond to the part of the first head 1062. For example, when the first head 1062 is circular, the center line of the exhaust hole 1024 coincides with the center of the circle of the first head 1062, so as to guide the airflow to discharge at a specific diffusion angle and reduce the turbulent noise.

[0084] The valve plate structure 104 has a certain elasticity. The head of the valve plate structure 104 is correspondingly arranged with the exhaust hole 1024 to realize the opening and closing of the exhaust hole 1024. The tail 1066 of the lift limiter 106 is directly connected to the base 102. Specifically, it can be fixed by the stepped rivet of the tail 1066. The waist 1064 forms a wave impedance gradient region. By limiting the thickness size relationship of the waist 1064, the first head 1062 and the tail 1066, the lift limiter 106 can gradually reduce the energy of the wave by using the acoustic black hole effect, and finally reduce the transmission of the vibration of the first head 1062 to the tail 1066.

[0085] Among them, the head of the valve plate structure 104 needs to contact the head of the lift limiter 106.

[0086] In some embodiments, optionally, by limiting the thickness ratio of the lift limiter 106, the noise reduction effect can be improved. Specifically, the ratio range of the thickness of the waist 1064 to the thickness of the tail 1066 is 1.1 - 2.25. The thickness of the waist 1064 is increased compared with the thickness of the tail 1066, and the increase amount is 10% - 125%, forming an increasing stiffness from the tail 1066 to the waist 1064. Since the elastic modulus E is proportional to the cube of the thickness, the bending deformation of the waist 1064 can be suppressed.

[0087] Of course, the maximum bending stress is transferred from the root of the rivet to the center of the waist 1064, and the stress amplitude will be reduced. In addition, the thickness gradient makes the vibration wave impedance gradually increase from the tail 1066 to the waist 1064, and the reflection coefficient decreases from total reflection to partial transmission.

[0088] When the ratio is less than 1.1, the stiffness of the waist 1064 is insufficient, and the vibration transmission rate is relatively large, so that the reduction amplitude of the noise peak value is not enough to meet the noise reduction requirements.

[0089] When the ratio is greater than 2.25, at this time, the stiffness of the waist 1064 is too high, there is a delay in the opening of the valve plate, the volumetric efficiency decreases, and it is impossible to balance the stiffness and the response speed.

[0090] Regarding the thickness of the first head 1062, by restricting the ratio to be between 1.28 and 3.0, the bending wave speed decreases as the thickness increases, and the wavefront energy gathers towards the head, enabling a higher energy attenuation coefficient to be obtained.

[0091] At the same time, thickening the head increases the length of the valve plate contact area, prolongs the collision time, and reduces the peak impact force.

[0092] If the ratio is less than 1.28, the acoustic black hole effect is weak at this time, and the energy aggregation coefficient is small. At 2500 Hz, the reduction amplitude of the noise peak is insufficient to meet the noise reduction requirements.

[0093] If the ratio is greater than 3.0, the overweight head causes the first-order frequency to drop to a value with a small interval from the stator frequency, easily triggering the risk of mode coupling.

[0094] It can be understood that the thickness of the waist 1064 is greater than the thickness of the tail 1066, and the thickness of the first head 1062 is greater than the thickness of the tail 1066.

[0095] In some embodiments, optionally, according to the different arrangement orders of the thicknesses of each part of the lift limiter 106, its dynamic characteristics and noise control effects will change. Specifically, as Figure 2 shown, when the thickness of the first head 1062 is defined as the thickest, the acoustic black hole effect is maximized, forming a significant wave speed decreasing region, with a larger energy attenuation coefficient. At the same time, the low stiffness design of the tail 1066 forms a flexible connection.

[0096] As Figure 4 shown, when the thickness of the waist 1064 is defined as the thickest, the maximum stress transfers from the root of the rivet to the center of the waist 1064, the stress amplitude decreases, and at the same time, the stiffness of the waist 1064 increases, and the overall deformation of the limiter is smaller. In addition, since the thickness of the waist 1064 is the thickest, being greater than both the thickness of the first head 1062 and the thickness of the tail 1066, it causes wave impedance mismatch, increases the reflection coefficient, and reduces the energy transmittance.

[0097] Furthermore, when the compressor 200 mainly generates high-frequency noise (>2000 Hz) and the rotational speed > 6000 rpm, the thickening design of the head can maximize the acoustic black hole effect.

[0098] Under the dominance of medium and low-frequency vibrations (<2000 Hz) or high-pressure working conditions (refrigerant pressure > 4 MPa), the thickening design of the waist 1064 is more optimal.

[0099] Generally speaking, when the thickness of the first head 1062 is the thickest, deep suppression of high-frequency noise can be achieved through the energy aggregation of the first head 1062. When the thickness of the waist 1064 is the thickest, the ability to control medium-frequency vibrations can be enhanced through the stiffness strengthening of the waist 1064.

[0100] Furthermore, when limiting the maximum thickness of the first head 1062, holes can be drilled in the first head 1062. When limiting the maximum thickness of the waist 1064, the gradient can be adjusted.

[0101] In some embodiments, optionally, the lower surface of the lift limiter 106, i.e., the side wall surface facing the valve plate structure 104, includes a lower flat section 1072 and a lower curved section 1074 that are smoothly transitionally connected. The lower flat section 1072 relates to the tail 1066 and the first half of the waist 1064. A certain distance is maintained between the lower flat section 1072 and the valve plate structure 104 to form a laminar boundary layer and reduce air separation noise. At the same time, as the initial contact area between the lift limiter 106 and the valve plate structure 104, the lower flat section 1072 needs to provide a stable pre-tightening force.

[0102] The lower curved section 1074 relates to the second half of the first head 1062 and the waist 1064. The lower curved section 1074 guides the first head 1062 of the valve plate to open at a specific inclination angle, such as 15° - 25°, thereby reducing the lateral impact component. In addition, the curvature of the lower curved section 1074 needs to be coupled with the thickness gradient to increase the rate of decrease of the bending wave speed.

[0103] It should be added that the lower flat section 1072 can maintain the Reynolds number through gap control to reduce frictional noise, while the lower curved section 1074 induces air flow acceleration through curvature but suppresses the generation of turbulence through diffusion design.

[0104] The lower flat section 1072 provides linear guidance, and the lower curved section 1074 changes to an involute trajectory, thereby reducing lateral vibration.

[0105] In some embodiments, optionally, as Figure 2 and Figure 3 shown, by setting a connection hole 1067 in the tail 1066 and simultaneously setting a reference position 1063 on the bottom of the first head 1062, i.e., the side wall surface facing the valve plate structure 104, the reference position 1063 and the position corresponding to the lower flat section 1072 are respectively defined. That is, along the extension direction of the lower flat section 1072, the ratio range of the second length between the part where the lower flat section 1072 is connected to the lower curved section and the axis of the connection hole 1067 to the first length between the reference position 1063 and the axis of the connection hole 1067 is 0.3 - 0.55, which can balance stiffness and modal separation.

[0106] Specifically, the connection hole 1067 is in interference fit with the base 102 to suppress high-frequency vibration modes. The reference position 1063 is set at the position of the first head 1062, and its specific position is aligned with the axis of the exhaust hole 1024 to ensure full coverage of the exhaust hole 1024 when the valve plate is closed, reducing the leakage rate.

[0107] L1 is the distance from the reference position 1063 to the axis of the connecting hole 1067, that is, the effective working length of the limiter.

[0108] L2 is the distance from the connection point of the lower plane section 1072 and the lower curved surface section to the axis of the connecting hole 1067.

[0109] By restricting the length ratio L2 / L1 = 0.3 - 0.55, both low-frequency control and high-frequency optimization are taken into account.

[0110] In some embodiments, optionally, as Figure 3 shown, the vertical distance from the reference position 1063 (the contact point between the head and the valve plate) to the lower plane section 1072 of the tail 1066 is the effective lift height h of the lift limiter 106, and the thickness of the rigid section where the limiter is connected to the base 102, that is, the thickness T1 of the tail 1066. By restricting 0.5 < h / T1 < 0.88, the balance relationship between the lift constraint of the limiter on the valve plate and its own bending stiffness can be controlled, and at the same time, it also directly affects the transfer efficiency of vibration energy from the valve plate to the limiter.

[0111] Specifically, the lift height h is positively correlated with the area of the exhaust hole 1024, and the cube of the thickness T1 of the tail 1066 is proportional to the stiffness. When the h / T1 ratio increases, the equivalent stiffness decreases, and the first-order bending frequency will decrease accordingly.

[0112] When h / T1 < 0.5, the lift is insufficient, the air flow is blocked, and the efficiency decreases. When h / T1 > 0.88, the impact speed of the valve plate is too high, affecting the fatigue life.

[0113] By restricting the ratio of h and T1, the transmission rate can be reduced, the noise can be reduced, and the leakage rate can be controlled.

[0114] In some embodiments, optionally, as Figure 3 shown, the upper wall surfaces of the first head 1062, the waist 1064, and the tail 1066 are respectively structurally divided. A part of the first head 1062 and the waist 1064 is in a curved surface step shape, and another part of the waist 1064 and the tail 1066 is in a plane step shape. The first upper curved surface section 1080 disperses the head vibration energy through the surface curvature, reducing the energy density while also guiding the back air flow to flow at a specific diffusion angle, reducing the vortex shedding noise. The second upper curved surface section 1082 connects the head and the tail 1066, reducing the stress concentration coefficient, and at the same time, increasing the first-order frequency of the limiter through the surface mass distribution, as far as possible away from the stator elliptical frequency. The first upper plane section 1076 reflects a part of the intermediate-frequency vibration energy back to the head dissipation area, and the second upper plane section 1078 is mainly used for high-frequency vibration isolation, suppressing the vibration transmission above 4000 Hz.

[0115] Generally speaking, this solution divides the upper wall surface structurally, extends the acoustic black hole effect from the thickness gradient to the three-dimensional curved surface-step composite structure, and realizes the global control of vibration energy. This design is particularly applicable to high-speed variable-frequency compressors (above 9000 rpm) and can still maintain low noise and high reliability under extreme working conditions.

[0116] In some embodiments, optionally, the curved surface radius of the lift limiter 106 is limited. Specifically, the curved surface radii of the first upper curved surface segment 1080, the second upper curved surface segment 1082, and the lower curved surface segment 1074 are limited to be the same, all being R1, so that the upper and lower surfaces of the lift limiter 106 are parallel before and after the step, thereby ensuring the uniformity of the thickness of each part and making processing more convenient.

[0117] Furthermore, taking the plane passing through the axis of the connecting hole 1067 of the tail 1066 and the reference position 1063 of the first head 1062 as the symmetric plane, the back curved surface of the lift limiter 106 is completely consistent with the curvature of the lower plane segment 1072, forming a fully symmetric profile, and realizing the geometric coordination of the vibration wave propagation path. The unified curvature radius makes the bending wave speed change uniformly along the entire length of the limiter, avoiding wave reflection caused by sudden curvature changes, increasing the energy transmittance, having a small phase difference when the vibration wave propagates through the head, the waist 1064, and the tail 1066, reducing the risk of modal coupling, and enhancing the stability of the first-order bending frequency.

[0118] In some embodiments, optionally, as Figure 2 and Figure 5 shown, restricting the radius ratio relationship between the relative second head 1042 and the first head 1062, that is, R3 and R2, can reduce the contact stress, extend the contact time, and reduce the peak value of the impact force power spectral density. In addition, the leakage rate can also be reduced to ensure the noise reduction effect.

[0119] It can be understood that when the ratio is less than 1.05, it is close to point contact, and stress concentration may lead to microcracks. When the ratio is greater than 1.45, the contact area is too long, the stiffness of the valve plate is insufficient, and the response is delayed.

[0120] In some embodiments, optionally, the size of the lift limiter 106 is restricted to be relatively large, which can cover the valve plate structure 104 to ensure the contact between the valve plate structure 104 and the lift limiter 106 after the exhaust hole 1024 is opened, ensure the uniformity of the contact, and reduce the leakage rate.

[0121] In some embodiments, optionally, as Figure 5 shown, the ratio of the thickness of the tail 1066 to the thickness of the valve plate structure 104 is restricted, that is, T1 and T4, and the ratio is restricted to be between 8 and 14.5, which can effectively reduce the speed at which the head of the valve plate impacts the head of the limiter.

[0122] The lower limit of the ratio is 8 to ensure that the stiffness of the tail 1066 is sufficient to suppress vibration, and the flexibility of the valve plate avoids stress concentration. The upper limit of the ratio is 14.5 to prevent the valve plate from being too thin and causing fracture or response delay, and a material strengthening process needs to be combined.

[0123] In some embodiments, optionally, the first-order bending natural frequency of the lift limiter 106 is greater than 2400 Hz; wherein, the ratio range of the first-order bending natural frequency of the base 102 to the first-order bending natural frequency of the lift limiter 106 is 1.05 - 1.2, and the difference between the first-order bending natural frequency of the base 102 and the first-order bending natural frequency of the lift limiter 106 is greater than 300 Hz. The ratio range of the first-order bending natural frequency of the valve plate structure 104 to the first-order bending natural frequency of the lift limiter 106 is 0.08 - 0.13, thereby restricting the first-order bending natural frequencies of the lift limiter 106, the base 102, and the valve plate structure 104, effectively avoiding possible modal coupling between multiple structural components, and reducing the resonance noise and vibration of the compressor 200.

[0124] This application provides another embodiment of the compressor 200, as Figure 8 and Figure 9 shown, including a cylinder 202, on which a cylinder hole 2022 is provided. By disposing any one of the above bearing assemblies 100 at at least one end of the cylinder 202, that is, using the bearing assembly 100 as the upper bearing or the lower bearing of the cylinder 202, an effective noise reduction effect can be achieved during the operation of the compressor 200.

[0125] Since the compressor 200 includes any one of the above bearing assemblies 100, it has the beneficial effects of any one of the above bearing assemblies 100, which will not be elaborated here.

[0126] Among them, the fluid movement direction is as Figure 9 shown by the arrow in

[0127] In some embodiments, optionally, the ratio of the elliptical natural frequency of the stator assembly 204 to the first-order bending natural frequency of the lift limiter 106 is limited, and the limiting ratio range is between 0.7 and 0.85, to avoid modal coupling between the stator assembly 204 and the lift limiter 106, and reduce the resonance noise and vibration of the compressor 200.

[0128] It should be added that the elliptical natural frequency of the stator assembly 204 refers to the natural vibration frequency corresponding to the bending vibration mode of the stator structure when an elliptical trajectory occurs. In other words, when the stator undergoes this specific elliptical bending vibration, its natural vibration frequency is the elliptical bending natural frequency.

[0129] The first-order bending natural frequency of the lift limiter 106 refers to the natural vibration frequency in its first-order bending vibration mode. In other words, this is the first-order modal frequency of the lift limiter 106 during bending vibration, that is, the natural vibration frequency during the most basic bending vibration.

[0130] In a specific embodiment, an exhaust structure, a compressor, and a refrigeration device are provided. Among them, the exhaust structure includes a bearing (i.e., the base 102), an exhaust valve plate (i.e., the valve plate structure 104), and a lift limiter 106. The limiter is distributed in multiple steps. The thickness of the first section (i.e., the tail 1066) is T1 and is connected to the rivet. The thickness of the second section (i.e., the waist 1064) is T2, and the thickness of the third section (i.e., the first head 1062) is T3, corresponding to the valve plate head (i.e., the second head 1042), satisfying 1.1 ≤ T2 / T1 ≤ 2.25, 1.28 ≤ T3 / T1 ≤ 3.0, and T1 ≥ 1.5 mm. This embodiment can reduce the slapping force of the exhaust valve plate on the lift limiter during operation, avoid the transmission of vibration to components such as the pump body or the housing, and can effectively improve the vibration and noise during the operation of the compressor.

[0131] When the compressor operates at a high speed, the pressure difference inside and outside the valve plate is relatively large. During the opening process of the exhaust valve plate, the waist and head of the valve plate will impact the waist and head of the limiter, causing the limiter to vibrate and exciting the resonance of the first-order bending natural frequency of the limiter. The structure of the present invention, through the stepped combination of different thicknesses of the limiter, especially the thicknesses of the second and third sections of the limiter being greater than the thickness of the first section, reduces the vibration response of the limiter head. The vibration reduction and noise reduction mechanism of the acoustic black hole is a structure with an aggregation effect on waves formed by gradually reducing the geometric parameter or material characteristic parameter of the system. In an ideal situation, the wave propagation speed gradually decreases to zero with the change of the medium and no reflection occurs. In addition, at this time, the thicknesses of the three sections of the limiter satisfy T1 < T2 < T3, and the entire limiter structure is similar to an acoustic black hole structure, which can more effectively reduce the transmission of the limiter head vibration to the limiter tail, further reduce the vibration transmission to the pump body and the housing, and thus reduce the noise radiation.

[0132] Further, the limiter is composed of a straight section and an arc section. The center distance of the limiter is L1, and the length of the straight section is L2, satisfying 0.30 ≤ L2 / L1 ≤ 0.55.

[0133] Further, the profile radius of the limiter is R1, satisfying 2.5 ≤ R1 / L1 ≤ 4.5.

[0134] Further, in order to reduce the speed of the valve plate head impacting the limiter head, the radius of the limiter head is R2, and the radius of the exhaust valve plate head is R3, satisfying 1.05 ≤ R3 / R2 ≤ 1.45.

[0135] Further, the lift height of the stopper corresponding to the center of the bearing exhaust hole is h, satisfying 0.5 < h / T1 < 0.88.

[0136] Further, the thickness of the exhaust valve is T4, satisfying 8.0 < T1 / T4 < 14.5.

[0137] Further, the first-order bending natural frequency of the stopper is f1, the first-order bending natural frequency of the valve plate is f2, the first-order bending natural frequency of the upper bearing is f3, and the elliptical natural frequency of the stator is f4, satisfying f1–f4 > 300 Hz, f3–f1 > 300 Hz, 0.08 ≤ f2 / f1 ≤ 0.13, 1.05 ≤ f3 / f1 ≤ 1.2, 0.7 ≤ f4 / f1 ≤ 0.85, and f1 > 2400 Hz, thereby effectively avoiding the modal coupling of multiple structural components and reducing noise and vibration.

[0138] Through the above solution, the modal coupling of multiple structural components is effectively avoided, and noise and vibration are reduced. As Figure 7 shown, the ordinate represents the decibel number, the abscissa represents the noise in a specific frequency band, and the rightmost part in the figure represents the noise value calculated by synthesizing all the frequency bands on the left. Specifically, at a rotational speed of 60 Hz, the noise peak value in the 2500 Hz frequency band is reduced by 13.6 dB; at a rotational speed of 90 Hz, the noise peak value in the 2500 Hz frequency band is reduced by 6.7 dB, and the total value of the noise in the core influence frequency band of 2000 - 4000 Hz of the valve group is reduced by 5.2 dB, effectively improving the noise peak value and noise quality of the valve group.

[0139] In the present invention, the terms "first", "second", and "third" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance; the term "plural" means two or more unless otherwise clearly defined. Terms such as "installation", "connection", "connection", and "fixation" should be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; "connection" can be a direct connection or an indirect connection through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0140] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "upper", "lower", "left", "right", "front", "rear", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or unit referred to must have a specific direction, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention.

[0141] In the description of this specification, the descriptions of terms such as "one embodiment", "some embodiments", "specific embodiments", etc. mean that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0142] The above are only the preferred embodiments of the present invention and are not used to limit the present invention. For those skilled in the art, the present invention can have various changes and modifications. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A bearing assembly, characterized in that, Comprising: A base, on which a valve seat groove is provided, and an exhaust hole for communicating with a cylinder hole on a cylinder is provided in the valve seat groove; A valve plate structure, arranged in the valve seat groove; A lift limiter, arranged on the base, and the lift limiter is correspondingly arranged with the valve plate structure. The lift limiter includes a first head, a tail, and a waist connected between the first head and the tail, and the tail is connected to the base; Wherein, the thickness of the waist is greater than the thickness of the tail, and the thickness of the first head is greater than the thickness of the tail.

2. The bearing assembly according to claim 1, characterized in that The ratio range of the thickness of the waist to the thickness of the tail is 1.1 to 2.25; and / or The ratio range of the thickness of the first head to the thickness of the tail is 1.28 to 3.

3. The bearing assembly according to claim 1, characterized in that The thicknesses of the first head, the waist, and the tail decrease in sequence; or The thicknesses of the waist, the first head, and the tail decrease in sequence.

4. The bearing assembly according to claim 1, wherein, One side wall surface of the lift limiter facing the valve plate structure includes a smooth transition lower plane section and a lower curved surface section. The tail and a part of the waist form the lower plane section on the side facing the valve plate structure, and the first head and the other part of the waist form the lower curved surface section on the side facing the valve plate structure.

5. The bearing assembly according to claim 4, wherein The tail is provided with a connection hole for cooperating with the base to be connected to the base, and a reference position corresponding to the axis of the exhaust hole is provided on one side wall surface of the first head facing the valve plate structure; Wherein, along the extension direction of the lower plane section, the ratio of the second length between the part where the lower plane section is connected to the lower curved surface section and the axis of the connection hole to the first length between the reference position and the axis of the connection hole is in the range of 0.3 to 0.

55.

6. The bearing assembly according to claim 5, characterized in that, In the thickness direction of the tail, the ratio of the vertical distance between the reference position and the plane where the lower plane section is located to the thickness of the tail is in the range of 0.5 to 0.

88.

7. The bearing assembly according to claim 6, characterized in that, One side wall surface of the first head away from the valve plate structure includes a first upper curved surface section, one side wall surface of the waist away from the valve plate structure includes a smooth transition second upper curved surface section and a first upper plane section, and one side wall surface of the tail away from the valve plate structure includes a second upper plane section; Wherein, the first upper plane section and the second upper plane section are in a stepped shape, and the first upper curved surface section and the second upper curved surface section are in a stepped shape.

8. The bearing assembly according to claim 7, wherein On the plane passing through the axis of the connection hole of the tail and passing through the reference position of the first head, the profile radii corresponding to the first upper curved surface section, the second upper curved surface section, and the lower curved surface section are the same.

9. The bearing assembly according to any one of claims 1 to 8, characterized in that, The valve plate structure includes a second head opposite to the exhaust hole, and the ratio range of the radius of the second head to the radius of the first head is 1.05 to 1.

45.

10. The bearing assembly according to any one of claims 1 to 8, characterized in that, The projection of the lift limiter on the plane where the valve plate structure is located covers the valve plate structure.

11. The bearing assembly according to any one of claims 1 to 8, characterized in that, The ratio range between the thickness of the tail part and the thickness of the valve plate structure is 8 to 14.

5.

12. The bearing assembly according to any one of claims 1 to 8, characterized in that, The first-order bending natural frequency of the lift limiter is greater than 2400 Hz; Among them, the ratio range between the first-order bending natural frequency of the base and the first-order bending natural frequency of the lift limiter is 1.05 to 1.2, and the difference between the first-order bending natural frequency of the base and the first-order bending natural frequency of the lift limiter is greater than 300 Hz. The ratio range between the first-order bending natural frequency of the valve plate structure and the first-order bending natural frequency of the lift limiter is 0.08 to 0.

13.

13. A compressor, characterized in that, Comprising: A cylinder provided with a cylinder hole on the cylinder; The bearing assembly according to any one of claims 1 to 12 is arranged on the end face of at least one end of the cylinder.

14. The compressor according to claim 13, characterized in that, The compressor includes a stator assembly, and the ratio range between the elliptical natural frequency of the stator assembly and the first-order bending natural frequency of the lift limiter is 0.7 to 0.85.

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