Bearing assembly and compressor

Abstract

The embodiment of the utility model provides a bearing assembly and a compressor, the bearing assembly comprises a base, a valve seat groove is arranged on the base, and an exhaust hole used for being communicated with a cylinder hole on a cylinder is arranged in the valve seat groove; 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 carried out 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] This utility model relates to the field of compressor technology, and more specifically, to a bearing assembly and a compressor. Background Technology

[0002] Currently, compressors typically have a valve plate installed outside the exhaust port of the bearing. When the pressure of the compressed refrigerant gas reaches a certain level, the valve plate opens; after exhaust, the valve plate closes to seal the exhaust port. A limiter is installed outside the valve plate to restrict the flow area. In related technologies, during compressor operation, such as... Figure 6 As shown, the valve plate usually collides with the lift limiter 106', causing vibration and resulting in loud noise. Utility Model Content

[0003] The present invention aims to at least solve the technical problem of excessive noise generated by valve plates and limiters during compressor operation in existing or related technologies.

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

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

[0006] To achieve the above objectives, embodiments of this utility model provide a bearing assembly, comprising: a base, a valve seat groove on the base, an exhaust port for communicating with a cylinder bore on a cylinder; a valve plate structure disposed in the valve seat groove; and a lift limiter disposed on the base, with the lift limiter corresponding to the valve plate structure. The lift limiter includes a first head, a tail, and a waist portion connected between the first head and the tail, the tail portion being connected to the base. The thickness of the waist portion is greater than the thickness of the tail portion, and the thickness of the first head portion is greater than the thickness of the tail portion.

[0007] The bearing assembly proposed in this utility model includes a base, a valve plate structure, and a lift limiter. The valve plate structure is located within a valve seat groove in the base to block the exhaust port, and the lift limiter is located above the valve plate structure to limit the displacement caused by the valve plate structure moving away from the exhaust port during exhaust. It is important to emphasize that this solution modifies the thickness of the lift limiter, making a stepped adjustment to the traditional uniform thickness limiter. Utilizing the synergistic effect of the acoustic black hole, it achieves the dual objectives of vibration energy attenuation and noise radiation control.

[0008] Specifically, the base serves as a structural support and has a valve seat groove for accommodating the valve plate structure. Under the action of the valve seat groove, the valve plate and the exhaust hole can be accurately positioned. The lateral displacement of the valve plate is restricted by the groove wall, and the contact pressure distribution of the sealing surface is made uniform. The center line of the exhaust hole needs to be aligned with the part of the first head. For example, if the first head is circular, the center line of the exhaust hole coincides with the center of the first head, thereby guiding the airflow to be discharged at a specific diffusion angle and reducing turbulence noise.

[0009] The valve plate structure has a certain degree of elasticity. The head of the valve plate structure is correspondingly set with the exhaust port to realize the opening and closing of the exhaust port. The tail of the lift limiter is directly connected to the base, which can be fixed by the stepped rivets at the tail. The waist forms a wave impedance gradient zone. By limiting the thickness relationship between the waist, the first head and the tail, the lift limiter can gradually reduce the wave energy by utilizing the acoustic black hole effect, and finally reduce the transmission of vibration from the first head to the tail.

[0010] The head of the valve plate structure must contact the head of the lift limit switch.

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

[0012] In this technical solution, the noise reduction effect can be improved by further limiting the thickness ratio of the lift limiter. Specifically, the ratio of the thickness of the waist to the thickness of the tail is in the range of 1.1 to 2.25. The thickness of the waist is increased compared to the thickness of the tail by 10% to 125%, forming a gradual increase in 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 suppressed.

[0013] Of course, the maximum bending stress shifts from the rivet root to the center of the waist, and the stress amplitude will decrease. In addition, the thickness gradient causes the vibration wave impedance to 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 waist stiffness is insufficient and the vibration transmission rate is large, which makes the reduction of the noise peak insufficient to meet the noise reduction requirements.

[0015] When the ratio is greater than 2.25, the waist stiffness is too high, the valve plate opening is delayed, the volumetric efficiency decreases, and the stiffness and response speed cannot be balanced.

[0016] Regarding the thickness of the first head, by limiting the ratio between 1.28 and 3.0, the bending wave velocity decreases with increasing thickness, and the wavefront energy concentrates towards the head, thus obtaining a higher energy attenuation coefficient.

[0017] Meanwhile, the increased thickness 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 and the energy concentration coefficient is small. At 2500Hz, the reduction in noise peak is insufficient to meet the noise reduction requirements.

[0019] If the ratio is greater than 3.0, the excessive weight of the head will cause the first-order frequency to drop to a smaller interval with the stator frequency, which may easily lead to the risk of modal coupling.

[0020] It is understandable 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 thickness of the first head, waist and tail decreases sequentially; or the thickness of the waist, first head and tail decreases sequentially.

[0022] Depending on the thickness arrangement of the various parts of the lift limiter, its dynamic characteristics and noise control effect will change. Specifically, when the thickness of the first head is limited to the thickest, the acoustic black hole effect is maximized, forming a significant wave velocity reduction zone and a larger energy attenuation coefficient. 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 the maximum, the maximum stress is transferred from the root of the rivet to the center of the waist, the stress amplitude is reduced, the stiffness of the waist is increased, and the overall deformation of the limiter is small. In addition, since the waist is the thickest, it is greater than the thickness of both the first head and the tail, resulting in wave impedance mismatch, increased reflection coefficient, and reduced energy transmittance.

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

[0025] The thickened waist design is superior under conditions dominated by low-to-medium frequency vibration (<2000Hz) or high pressure (refrigerant pressure >4MPa).

[0026] In summary, when the thickness of the first head is the greatest, high-frequency noise can be deeply suppressed through energy concentration in the first head. When the thickness of the waist is the greatest, mid-frequency vibration control capability can be improved through waist stiffness enhancement.

[0027] Furthermore, when the thickness of the first head is limited to its maximum, a hole can be drilled in the first head; when the thickness of the waist is limited to its maximum, the gradient can be adjusted.

[0028] In some technical solutions, optionally, the side wall of the lift limiter facing the valve plate structure includes a smoothly transitioned lower flat section and a lower curved section, the tail and a portion of the waist form the lower flat section on the side facing the valve plate structure, and the first head and another portion of the waist form the lower curved section on the side facing the valve plate structure.

[0029] In this design, the lower surface of the lift limiter, i.e., the side wall facing the valve plate structure, includes a smoothly transitioned lower flat section and a lower curved section. The lower flat section involves the tail and the front half of the waist. The lower flat section maintains a certain distance from the valve plate structure, forming a laminar boundary layer and reducing airflow separation noise. At the same time, the lower flat section, as the initial contact area between the lift limiter and the valve plate structure, needs to provide a stable preload force.

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

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

[0032] The lower plane segment provides linear guidance, while the lower curved segment transitions to an involute trajectory, thereby reducing lateral vibration.

[0033] In some technical solutions, optionally, a connecting hole is provided at the tail end for engaging with the base to connect to the base, and a reference position corresponding to the axis of the exhaust hole is provided on the side wall of the first head facing the valve plate structure; wherein, along the extension direction of the lower plane segment, the ratio of the second length between the portion of the lower plane segment connected to the lower curved surface segment and the axis of the connecting hole to the first length between the reference position and the axis of the connecting hole ranges from 0.3 to 0.55.

[0034] By setting a connecting hole at the tail and setting a reference position at the bottom of the first head, i.e. on the side wall facing the valve plate structure, the reference position and the corresponding position of the lower plane segment are defined respectively. That is, along the extension direction of the lower plane segment, the ratio of the second length between the part of the lower plane segment connected to the lower curved surface segment and the axis of the connecting hole to the first length between the reference position and the axis of the connecting hole is in the range of 0.3 to 0.55, which can take into account both stiffness and modal separation.

[0035] Specifically, the connecting hole is interference-fitted with the base to suppress high-frequency vibration modes. The reference position is set at the first head position, and its specific position is aligned with the axis of the exhaust hole to ensure that the valve plate fully covers the exhaust hole when closed, reducing the leakage rate.

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

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

[0038] By limiting the length ratio L2 / L1 to 0.3 to 0.55, both low-frequency control and high-frequency optimization are taken into account.

[0039] In some technical solutions, optionally, the ratio between the vertical distance between the reference position and the plane containing the lower plane segment and the thickness of the tail is in the thickness direction of the tail is in the range of 0.5 to 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 of the tail section, i.e. the effective lift height h of the lift limiter, and the thickness of the rigid section connecting the limiter and the base, i.e. the tail thickness T1, can be controlled by limiting 0.5 < h / T1 < 0.88. This balance between the limiter's lift constraint on the valve plate and its own bending stiffness can be controlled, and it also directly affects the efficiency of vibration energy transmission from the valve plate to the limiter.

[0041] Specifically, the lift height h is positively correlated with the exhaust port area, the cube of the tail thickness T1 is proportional to the stiffness, and when the h / T1 ratio 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 airflow is blocked, and the efficiency decreases. When h / T1 > 0.88, the valve plate impact speed is too high, which affects the fatigue life.

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

[0044] In some technical solutions, optionally, the side wall of the first head away from the valve plate structure includes a first upper curved surface segment, the side wall of the waist away from the valve plate structure includes a smoothly transitioning second upper curved surface segment and a first upper flat surface segment, and the side wall of the tail away from the valve plate structure includes a second upper flat surface segment; wherein, the first upper flat surface segment and the second upper flat surface segment are stepped, and the first upper curved surface segment and the second upper curved surface segment are stepped.

[0045] In this design, the upper walls of the first head, waist, and tail sections are structurally divided. A portion of the first head and waist section has a curved, stepped shape, while another portion of the waist and tail section has a planar, stepped shape. The first upper curved section disperses the head's vibration energy through its curvature, reducing energy density and guiding the back airflow at a specific diffusion angle, thus reducing eddy current noise. The second upper curved section connects the head and tail, reducing stress concentration and, through surface mass distribution, raising the first-order frequency of the limiter to as far away as possible from the stator elliptical frequency. The first upper planar section reflects some mid-frequency vibration energy back to the head dissipation region, while the second upper planar section is primarily used for high-frequency vibration isolation, suppressing vibration transmission above 4000Hz.

[0046] In summary, this solution extends the acoustic black hole effect from the thickness gradient to a three-dimensional curved surface-stepped composite structure by structurally dividing the upper wall, achieving full-domain control of vibration energy. This design is particularly suitable for high-speed variable frequency compressors (above 9000 rpm), maintaining low noise and high reliability even under extreme operating conditions.

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

[0048] By limiting the radius of the lifting limiter's surface, specifically restricting the radii of the first upper surface segment, the second upper surface segment, and the lower surface segment to be the same, the lifting limiter remains parallel on the upper and lower surfaces before and after the step, thereby ensuring the uniformity of the thickness of each part and making it easier to process.

[0049] Furthermore, the plane between the axis passing through the tail connection hole and the reference position of the first head is a symmetrical plane. The curvature of the back surface of the lift limiter is completely consistent with that of the lower plane segment, forming a fully symmetrical profile, thus achieving geometric coordination of the vibration wave propagation path. The uniform radius of curvature ensures that the bending wave velocity varies uniformly along the entire length of the limiter, avoiding wave reflection caused by abrupt changes in curvature, improving energy transmittance, and reducing the phase difference of the vibration wave as it propagates in the head, waist, and tail, thereby reducing the risk of modal coupling and improving the stability of the first-order bending frequency.

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

[0051] In this technical solution, by limiting the relative radius ratio between the second and first heads, contact stress can be reduced, contact time can be extended, and the peak value of the impact force power spectral density can be lowered. Furthermore, the leakage rate can be reduced, ensuring noise reduction effectiveness.

[0052] It is understandable that when the ratio is less than 1.05, near-point contact and stress concentration may lead to microcracks. When the ratio is greater than 1.45, the contact area is too long, the valve plate stiffness 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 size of the lift limiter to be large enough to cover the valve plate structure, the contact between the valve plate structure and the lift limiter after the exhaust port is opened is ensured, thus guaranteeing the uniformity of the contact and reducing the leakage rate.

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

[0056] In this technical solution, by proportionally limiting the thickness of the tail section and the thickness of the valve plate structure, the speed at which the valve plate head impacts the limiter head can be effectively reduced.

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

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

[0059] An embodiment of the second aspect of this application provides a compressor, including: a cylinder having a cylinder bore; and any of the aforementioned bearing assemblies disposed on the end face of at least one end of the cylinder.

[0060] The compressor provided in this application includes a cylinder. By placing any of the aforementioned bearing assemblies at at least one end of the cylinder, that is, by using the bearing assembly as the upper or lower bearing of the cylinder, noise reduction can be effectively achieved during the operation of the compressor.

[0061] Since the compressor includes any of the aforementioned bearing assemblies, it has the beneficial effects of any of the aforementioned bearing assemblies, which will not be elaborated further here.

[0062] In some technical solutions, the compressor may optionally include a stator assembly, wherein the ratio of the elliptic natural frequency of the stator assembly to the first-order bending natural frequency of the lift limiter is in the range of 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, the ratio is limited to a range of 0.7 to 0.85, thereby avoiding modal coupling between the stator assembly and the lift limiter and reducing compressor resonance noise vibration.

[0064] Additional aspects and advantages of this invention will become apparent in the description that follows, or may be learned by practice of this invention. Attached Figure Description

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

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

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

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

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

[0070] Figure 6 A schematic diagram of the structure in the related technology is shown;

[0071] Figure 7 A schematic diagram showing the noise reduction effect of a bearing assembly according to an embodiment of the present invention is shown;

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

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

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

[0075] 100: Bearing assembly; 102: Base; 1022: Valve seat groove; 1024: Exhaust port; 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 correspondence between reference numerals and component names in related technologies is as follows:

[0078] 106': Lift limit switch. Detailed Implementation

[0079] To better understand the above-mentioned objectives, features, and advantages of the embodiments of this utility model, the embodiments of this utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0080] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, embodiments of the present invention 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.

[0081] The following reference Figures 1 to 9 Some embodiments of the present invention are described below.

[0082] like Figure 1 and Figure 2 As shown, this embodiment provides a bearing assembly 100, including a base 102, a valve plate structure 104, and a lift limiter 106. The valve plate structure 104 is located within a valve seat groove 1022 of the base 102 to block the exhaust port 1024, and the lift limiter 106 is located above the valve plate structure 104 to limit the displacement of the valve plate structure 104 away from the exhaust port during exhaust. It is important to emphasize that this solution modifies the thickness of the lift limiter 106, making a stepped adjustment to the traditional uniform thickness limiter. Utilizing the synergistic effect of the acoustic black hole, it achieves the dual objectives of vibration energy attenuation and noise radiation control.

[0083] Specifically, the base 102 serves as a structural support, and a valve seat groove 1022 is provided on the base 102 to accommodate the valve plate structure 104. Under the action of the valve seat groove 1022, the valve plate and the exhaust hole 1024 can be accurately positioned. The lateral displacement of the valve plate is restricted by the groove wall, and the contact pressure distribution of the sealing surface is made uniform. The center line of the exhaust hole 1024 needs to be aligned with the part corresponding to the first head 1062. For example, if the first head 1062 is circular, the center line of the exhaust hole 1024 coincides with the center of the first head 1062, thereby guiding the airflow to be discharged at a specific diffusion angle and reducing turbulence noise.

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

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

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

[0087] Of course, the maximum bending stress shifts from the rivet root to the center of the waist 1064, and the stress amplitude will decrease. In addition, the thickness gradient causes the vibration wave impedance to 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 section 1064 is insufficient and the vibration transmission rate is large, which makes the reduction of the noise peak insufficient to meet the noise reduction requirements.

[0089] When the ratio is greater than 2.25, the stiffness of the waist section 1064 is too high, the valve plate opening is delayed, the volumetric efficiency decreases, and the stiffness and response speed cannot be balanced.

[0090] For the thickness of the first head 1062, by limiting the ratio between 1.28 and 3.0, the bending wave velocity decreases with increasing thickness, and the wavefront energy concentrates towards the head, thus obtaining a higher energy attenuation coefficient.

[0091] Meanwhile, the increased thickness of 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 and the energy concentration coefficient is small. At 2500Hz, the reduction in noise peak is insufficient to meet the noise reduction requirements.

[0093] If the ratio is greater than 3.0, the excessive weight of the head will cause the first-order frequency to drop to a smaller interval with the stator frequency, which may easily lead to the risk of modal coupling.

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

[0095] In some embodiments, optionally, the dynamic characteristics and noise control effect of the lift limiter 106 will change depending on the thickness arrangement order of its various parts. Specifically, for example... Figure 2 As shown, when the thickness of the first head 1062 is limited to the maximum, the acoustic black hole effect is maximized, forming a significant wave velocity reduction zone and a larger energy attenuation coefficient. At the same time, the low stiffness design of the tail 1066 forms a flexible connection.

[0096] like Figure 4 As shown, when the thickness of the waist 1064 is limited to the maximum, the maximum stress is transferred from the root of the rivet to the center of the waist 1064, the stress amplitude is reduced, and the stiffness of the waist 1064 is increased, resulting in a smaller overall deformation of the limiter. In addition, since the waist 1064 is the thickest, it is greater than both the thickness of the first head 1062 and the thickness of the tail 1066, which leads to wave impedance mismatch, an increase in the reflection coefficient, and a decrease in energy transmittance.

[0097] Furthermore, when the compressor 200 is dominated by high-frequency noise (>2000Hz) and the speed is >6000rpm, the thickened head design can maximize the acoustic black hole effect.

[0098] Under conditions dominated by low-to-medium frequency vibration (<2000Hz) or high-pressure conditions (refrigerant pressure >4MPa), the 1064 thickened waist design is superior.

[0099] In summary, when the thickness of the first head 1062 is the thickest, high-frequency noise can be deeply suppressed through the energy concentration of the first head 1062. When the thickness of the waist 1064 is the thickest, the mid-frequency vibration control capability can be improved through the stiffness enhancement of the waist 1064.

[0100] Furthermore, when the thickness of the first head 1062 is limited to its maximum, a hole can be drilled in the first head 1062; when the thickness of the waist 1064 is limited to its maximum, the gradient can be adjusted.

[0101] In some embodiments, optionally, the lower surface of the lift limiter 106, i.e., the side wall facing the valve plate structure 104, includes a smoothly transitioned lower flat section 1072 and a lower curved section 1074. The lower flat section 1072 involves the tail 1066 and the front half of the waist 1064. The lower flat section 1072 and the valve plate structure 104 maintain a certain distance, forming a laminar boundary layer to reduce airflow separation noise. At the same time, the lower flat section 1072, as the initial contact area between the lift limiter 106 and the valve plate structure 104, needs to provide a stable preload force.

[0102] The lower curved section 1074 involves the rear 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 angle, such as 15° to 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 velocity.

[0103] It should be added that the lower plane section 1072 can maintain the Reynolds number and reduce friction noise through gap control, while the lower curved section 1074 accelerates the airflow through curvature, but suppresses turbulence generation through diffusion design.

[0104] The lower plane segment 1072 provides linear guidance, while the lower curved surface segment 1074 transitions to an involute trajectory, thereby reducing lateral vibration.

[0105] In some embodiments, optionally, such as Figure 2 and Figure 3 As shown, by providing a connecting hole 1067 at the tail 1066 and a reference position 1063 at the bottom of the first head 1062, i.e., on the side wall facing the valve plate structure 104, the positions corresponding to the reference position 1063 and the lower plane segment 1072 are defined respectively. That is, along the extension direction of the lower plane segment 1072, the ratio between the second length of the part of the lower plane segment 1072 connected to the lower curved surface segment and the axis of the connecting hole 1067 and the first length of the reference position 1063 and the axis of the connecting hole 1067 is in the range of 0.3 to 0.55, which can take into account both stiffness and modal separation.

[0106] Specifically, the connecting hole 1067 is interference-fitted with the base 102 to suppress high-frequency vibration modes. The reference position 1063 is set at the first head 1062, and its specific position is aligned with the axis of the exhaust hole 1024 to ensure that the valve plate is fully covered by the exhaust hole 1024 when closed, thereby reducing the leakage rate.

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

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

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

[0110] In some embodiments, optionally, such as Figure 3 As shown, the vertical distance from the reference position 1063 (the contact point between the head and the valve plate) to the lower plane segment 1072 of the tail 1066 is the effective lift height h of the lift limiter 106. The thickness of the rigid section connecting the limiter and the base 102 is the thickness T1 of the tail 1066. By limiting 0.5 < h / T1 < 0.88, the balance between the limiter's lift constraint on the valve plate and its own bending stiffness can be controlled, which also directly affects the transmission 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 port 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 airflow is blocked, and the efficiency decreases. When h / T1 > 0.88, the valve plate impact speed is too high, which affects the fatigue life.

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

[0114] In some embodiments, optionally, such as Figure 3 As shown, the upper walls of the first head 1062, waist 1064, and tail 1066 are structurally divided. A portion of the first head 1062 and waist 1064 are curved stepped surfaces, while another portion of the waist 1064 and tail 1066 are planar stepped surfaces. The first upper curved surface segment 1080 disperses the head vibration energy through its curvature, reducing energy density and guiding the back airflow at a specific diffusion angle, thus reducing eddy current noise. The second upper curved surface segment 1082 connects the head and tail 1066, reducing stress concentration and simultaneously increasing the first-order frequency of the limiter through surface mass distribution, keeping it as far away as possible from the stator elliptical frequency. The first upper planar surface segment 1076 reflects a portion of the mid-frequency vibration energy back to the head dissipation region, while the second upper planar surface segment 1078 is mainly used for high-frequency vibration isolation, suppressing vibration transmission >4000Hz.

[0115] In summary, this solution extends the acoustic black hole effect from the thickness gradient to a three-dimensional curved surface-stepped composite structure by structurally dividing the upper wall, achieving full-domain control of vibration energy. This design is particularly suitable for high-speed variable frequency compressors 200 (above 9000 rpm), maintaining low noise and high reliability even under extreme operating conditions.

[0116] In some embodiments, the radius of curvature of the lift limiter 106 may be limited. Specifically, the radius of curvature of the first upper curved surface segment 1080, the second upper curved surface segment 1082, and the lower curved surface segment 1074 may be limited to the same value, R1, so that the lift limiter 106 remains parallel on the upper and lower surfaces before and after the step, thereby ensuring the uniformity of the thickness of each part and making it easier to process.

[0117] Furthermore, the plane connecting the axis through the connecting hole 1067 at the tail 1066 and the reference position 1063 at the first head 1062 is a symmetrical plane. The curvature of the back surface of the lift limiter 106 is completely consistent with the curvature of the lower plane segment 1072, forming a fully symmetrical profile, thus achieving geometric coordination of the vibration wave propagation path. The uniform radius of curvature makes the bending wave velocity change uniformly along the entire length of the limiter, avoiding wave reflection caused by abrupt changes in curvature, improving energy transmittance, and reducing the phase difference of the vibration wave when propagating in the head, waist 1064, and tail 1066, thereby reducing the risk of modal coupling and improving the stability of the first-order bending frequency.

[0118] In some embodiments, optionally, such as Figure 2 and Figure 5 As shown, limiting the relative radius ratio of the second head 1042 and the first head 1062, i.e., R3 and R2, can reduce contact stress, prolong contact time, and lower the peak value of the impact force power spectral density. Furthermore, it can reduce leakage rate and ensure noise reduction effect.

[0119] It is understandable that when the ratio is less than 1.05, near-point contact and stress concentration may lead to microcracks. When the ratio is greater than 1.45, the contact area is too long, the valve plate stiffness is insufficient, and the response is delayed.

[0120] In some embodiments, the size of the limiter 106 is optionally large enough to cover the valve plate structure 104, so as to ensure that the contact between the valve plate structure 104 and the limiter 106 after the vent hole 1024 is opened, thus ensuring the uniformity of the contact and reducing the leakage rate.

[0121] In some embodiments, optionally, such as Figure 5 As shown, the thickness of the tail section 1066 and the thickness of the valve plate structure 104 are proportionally limited, namely T1 and T4, with the ratio between 8 and 14.5, which can effectively reduce the speed at which the valve plate head hits the limiter head.

[0122] The lower limit of the ratio is 8 to ensure that the stiffness of the tail section (1066) is sufficient to suppress vibration. 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, which could lead to breakage or response delay. This needs to be combined with material strengthening processes.

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

[0124] This application provides another embodiment of a compressor 200, such as Figure 8 and Figure 9 As shown, the compressor 200 includes a cylinder 202 with a cylinder bore 2022. By setting any of the bearing assemblies 100 at at least one end of the cylinder 202, the bearing assembly 100 is used as the upper or lower bearing of the cylinder 202, thereby effectively reducing noise during the operation of the compressor 200.

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

[0126] Wherein, the direction of fluid movement is as follows Figure 9 As indicated by the middle arrow.

[0127] In some embodiments, the ratio of the elliptic natural frequency of the stator assembly 204 to the first-order bending natural frequency of the lift limiter 106 may be limited to a range of 0.7 to 0.85, thereby avoiding modal coupling between the stator assembly 204 and the lift limiter 106 and reducing the resonant noise 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 of the stator structure when it undergoes a bending vibration mode with an elliptical trajectory. 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 when bending vibration occurs, which is also the natural vibration frequency of the most basic bending vibration.

[0130] In one specific embodiment, an exhaust structure, a compressor, and a refrigeration device are provided. The exhaust structure includes a bearing (i.e., base 102), an exhaust valve plate (i.e., valve plate structure 104), and a lift limiter 106. The limiter has a multi-stage stepped distribution, where the first stage (i.e., tail 1066) has a thickness of T1 and is connected to a rivet; the second stage (i.e., waist 1064) has a thickness of T2; and the third stage (i.e., first head 1062) has a thickness of T3 and corresponds to the valve plate head (i.e., second head 1042), satisfying 1.1≤T2 / T1≤2.25, 1.28≤T3 / T1≤3.0, and T1≥1.5mm. This embodiment can reduce the impact force of the exhaust valve plate on the lift limiter during operation, preventing vibration from being transmitted to components such as the pump body or housing, and effectively improving vibration and noise during compressor operation.

[0131] When the compressor operates at high speed, the pressure difference between the inside and outside of the valve plate is relatively large. During the opening of the exhaust valve plate, the waist and head of the valve plate impact the waist and head of the limiter, causing the limiter to vibrate and excite the first-order bending natural frequency resonance of the limiter. This invention reduces the vibration response of the limiter head by using a stepped combination of different thicknesses in the limiter, especially with the second and third sections being thicker than the first section. The acoustic black hole vibration reduction and noise reduction mechanism is a structure that forms a wave-focusing effect by gradually reducing the geometric parameters or material properties of the system. Ideally, the wave propagation speed gradually decreases to zero with the change of the medium, and no reflection occurs. Furthermore, at this point, the thicknesses of the three sections of the limiter satisfy T1 < T2 < T3, and the entire limiter structure resembles an acoustic black hole structure, which can more effectively reduce the transmission of vibration from the limiter head to the limiter tail, further reducing the vibration transmission to the pump body and casing, thereby reducing noise radiation.

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

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

[0134] Furthermore, in order to reduce the speed at which the valve head impacts the limiter head, the limiter head radius is R2 and the exhaust valve head radius is R3, satisfying 1.05≤R3 / R2≤1.45.

[0135] Furthermore, the limiter lift height corresponding to the center of the bearing vent hole is h, which satisfies 0.5 < h / T1 < 0.88.

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

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

[0138] The above solution effectively avoids modal coupling among multiple structural components, reducing noise and vibration. Figure 7 As shown, the vertical axis represents decibels, and the horizontal axis represents noise in a specific frequency band. The rightmost part of the graph represents the combined noise value calculated from all frequency bands on the left. Specifically, at a rotational speed of 60Hz, the peak noise level in the 2500Hz band is reduced by 13.6dB; at a rotational speed of 90Hz, the peak noise level in the 2500Hz band is reduced by 6.7dB, and the total noise value in the core influential frequency band of the valve group (2000-4000Hz) is reduced by 5.2dB, effectively improving the peak noise level and noise quality of the valve group.

[0139] In this utility model, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance; the term "multiple" refers to two or more unless otherwise explicitly defined. The terms "install," "connect," "join," and "fix" should be interpreted broadly. For example, "connect" can be a fixed connection, a detachable connection, or an integral connection; "join" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0140] In the description of this utility model, it should be understood that the terms "upper", "lower", "left", "right", "front", "rear", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or unit referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0141] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0142] The above are merely preferred embodiments of this utility model and are not intended to limit the scope of this utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A bearing assembly, characterized in that, include: A base, wherein a valve seat groove is provided on the base, and an exhaust port for communicating with a cylinder bore on a cylinder is provided in the valve seat groove; The valve disc structure is disposed within the valve seat groove; A lift limiter is disposed on the base and is correspondingly disposed to the valve plate structure. The lift limiter includes a first head, a tail and a waist connected between the first head and the tail. The tail is connected to the base. 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 of the thickness of the waist portion to the thickness of the tail portion ranges from 1.1 to 2.25; and / or The ratio of the thickness of the first head to the thickness of the tail ranges from 1.28 to 3.

3. The bearing assembly according to claim 1, characterized in that, The thickness of the first head, the waist, and the tail decreases sequentially; or The thickness of the waist, the first head, and the tail decreases sequentially.

4. The bearing assembly according to claim 1, characterized in that, The lift limiter has a side wall facing the valve plate structure that includes a smoothly transitioned lower flat section and a lower curved section. The tail and a portion of the waist form the lower flat section on the side facing the valve plate structure, and the first head and another portion of the waist form the lower curved section on the side facing the valve plate structure.

5. The bearing assembly according to claim 4, characterized in that, The tail is provided with a connecting hole for engaging with the base to connect to the base, and the first head has a reference position on the side wall facing the valve plate structure that corresponds to the axis of the exhaust hole. Wherein, along the extension direction of the lower plane segment, the ratio of the second length between the portion of the lower plane segment connected to the lower curved surface segment and the axis of the connecting hole to the first length between the reference position and the axis of the connecting hole ranges from 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 between the vertical distance between the reference position and the plane containing the lower plane segment and the thickness of the tail ranges from 0.5 to 0.

88.

7. The bearing assembly according to claim 6, characterized in that, The first head has a first upper curved surface segment on the side wall away from the valve plate structure, the waist has a second upper curved surface segment and a first upper flat surface segment with a smooth transition on the side wall away from the valve plate structure, and the tail has a second upper flat surface segment on the side wall away from the valve plate structure. The first upper plane segment and the second upper plane segment are stepped, and the first upper curved surface segment and the second upper curved surface segment are stepped.

8. The bearing assembly according to claim 7, characterized in that, On a plane passing through the axis of the connecting hole at the tail and the reference position of the first head, the profile radius corresponding to the first upper curved surface segment, the profile radius corresponding to the second upper curved surface segment, and the profile radius corresponding to the lower curved surface segment 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 port, and the ratio of the radius of the second head to the radius of the first head is in the range of 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 between the thickness of the tail section and the thickness of the valve plate structure ranges from 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 2400Hz; The ratio of the first-order bending natural frequency of the base to the first-order bending natural frequency of the lift limiter ranges from 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 of the first-order bending natural frequency of the valve plate structure to the first-order bending natural frequency of the lift limiter ranges from 0.08 to 0.

13.

13. A compressor, characterized in that, include: A cylinder, wherein the cylinder is provided with a cylinder bore; The bearing assembly as described in any one of claims 1 to 12 is disposed 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, the ratio of the elliptical natural frequency of the stator assembly to the first-order bending natural frequency of the lift limiter is in the range of 0.7 to 0.85.

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