A special-shaped clearance damper with adjustable damping

Abstract

The special-shaped gap damper with adjustable damping disclosed by the present invention relates to the field of vibration damping, and includes an oil cylinder body, a piston rod assembly, a piston assembly and a first sleeve. A notch is provided on the side wall of the first sleeve along the direction parallel to the axis of the first sleeve. The notch has a middle plane in the direction parallel to the axis of the first sleeve. The dimension of the notch in the direction perpendicular to the axis of the first sleeve decreases from the middle plane of the notch to both ends of the notch parallel to the axis of the first sleeve. The piston assembly is sleeved outside the piston rod assembly and is hermetically and fixedly connected to the piston rod assembly. When the piston rod assembly does not expand or contract, the piston assembly is symmetric about the middle plane of the notch. The outer wall of the piston assembly is hermetically and slidably connected to the inner wall of the first sleeve. The outer wall of the first sleeve is hermetically connected to the inner wall of the oil cylinder body. One end of the piston rod assembly is sleeved inside the first sleeve, and the other end of the piston rod assembly is slidably connected to the oil cylinder body. The piston assembly can divide the inner cavity of the oil cylinder body into at least two cavities. It has good vibration damping effect and low cost.

Description

Technical Field

[0001] The present invention relates to the technical field of vibration damping devices, and particularly to a special-shaped clearance damper with adjustable damping Background Art

[0002] A damper is a device that uses damping characteristics to slow down mechanical vibrations and consume kinetic energy. Since it can quickly absorb the vibration energy of a vibration system, it has currently been widely used in various technical fields such as aerospace, automobiles, ships, and buildings. However, the vibration amplitude of a mechanical vibration system is usually not fixed. When the vibration amplitude is large, a damper with a large damping force is required, and when the vibration amplitude is small, a damper with a small damping force is required. In order to adapt to different vibration amplitudes of the vibration system, the existing dampers usually use an active control system to adjust the damping force. Specifically: a displacement sensor is set in the damper, and the displacement information of the piston rod assembly or the piston is detected through the displacement sensor. The controller adjusts the magnitude of the damping force according to the displacement information of the piston rod assembly or the piston. For example, Chinese Patent CN201721672013.9 discloses a new type of magnetorheological damper capable of detecting piston displacement, integrating a capacitive displacement sensor with the magnetorheological damper. The capacitive displacement sensor detects the displacement of the spring connecting plate to obtain a sensing output signal containing the displacement information of the spring connecting plate, and this signal can obtain the displacement information of the piston after being amplified in proportion. According to the obtained piston displacement information, the magnitude of the exciting coil current is adjusted in a timely manner to achieve optimal damping force control. Another example is a new type of damper disclosed in Chinese Patent CN201720411824.7. It sets a pressure sensor and a proportional valve outside the oil cylinder, and a displacement sensor inside the oil cylinder. The displacement sensor is used to measure the position of the piston rod assembly 3 in real time and calculate the movement speed of the piston rod assembly. The pressure sensor is used to monitor and measure the pressure inside the oil cylinder in real time. The data collected by the displacement sensor and the pressure sensor are input into the controller. The controller receives the data input by the displacement sensor and the pressure sensor, calculates the piston movement speed according to the displacement signal, then calculates the deviation between the damper displacement and pressure value and the set value, and feeds back this deviation to the proportional valve. After receiving the signal, the proportional valve adjusts the flow rate of the fluid in the oil cylinder to achieve precise control of the damping force. The method of adjusting the magnitude of the damping force according to the displacement information of the piston rod assembly or the piston requires the damper to be continuously powered on for a long time to maintain continuous detection, and the development and maintenance work of the displacement sensor and the controller is relatively cumbersome, with high power consumption and high cost. Summary of the Invention

[0003] The purpose of the present invention is to provide a special-shaped clearance damper with adjustable damping to solve the problems existing in the above-mentioned prior art, with good vibration damping effect and low cost.

[0004] To achieve the above object, the present invention provides the following solutions:

[0005] The present invention provides a special-shaped clearance damper with adjustable damping, which includes an oil cylinder body, a piston rod assembly, a piston assembly and a first sleeve. A notch is provided on the side wall of the first sleeve along the direction parallel to the axis of the first sleeve, and the notch penetrates through the first sleeve along the direction parallel to the axis of the first sleeve. The notch has a middle plane in the direction parallel to the axis of the first sleeve, and the dimension of the notch in the direction perpendicular to the axis of the first sleeve gradually decreases from the middle plane of the notch to both ends of the notch parallel to the axis of the first sleeve. The piston assembly is sleeved outside the piston rod assembly and is hermetically and fixedly connected to the piston rod assembly. When the piston rod assembly does not extend or retract, the piston assembly is symmetrically arranged with respect to the middle plane of the notch. The outer wall of the piston assembly is hermetically and slidably connected to the inner wall of the first sleeve. The outer wall of the first sleeve is hermetically connected to a part of the inner wall of the oil cylinder body. One end of the piston rod assembly is sleeved inside the first sleeve, and the other end of the piston rod assembly is slidably connected to the oil cylinder body. The piston assembly can divide the inner cavity of the oil cylinder body into at least two cavities.

[0006] Preferably, the piston assembly includes a piston body, and when the piston rod assembly does not extend or retract, the piston body is symmetrically arranged with respect to the middle plane of the notch.

[0007] Preferably, the piston assembly includes a first piston and a second piston. The first piston and the second piston are both sleeved outside the piston rod assembly and are hermetically and fixedly connected to the piston rod assembly. When the piston rod assembly does not extend or retract, the first piston and the second piston are symmetrically arranged with respect to the middle plane of the notch. The outer walls of the first piston and the second piston are hermetically and slidably connected to the inner wall of the first sleeve. The first piston and the second piston can divide the inner cavity of the oil cylinder body into a first end cavity, a second end cavity and a middle cavity.

[0008] Preferably, the piston rod assembly includes a rod body and a lead screw. One end of the rod body is slidably connected to the oil cylinder body, and the other end of the rod body is fixedly connected to one end of the lead screw. The other end of the lead screw has a first thread section and a second thread section. The threads of the first thread section and the second thread section have opposite helix directions. The first piston is sleeved outside the first thread section and is hermetically and threadedly connected to the first thread section. The second piston is sleeved outside the second thread section and is hermetically and threadedly connected to the second thread section.

[0009] Preferably, a first surface and a second surface that are both connected to the inner and outer side walls of the first sleeve are formed at the notch of the first sleeve. The axial cross-section of the first sleeve between the first surface and the second surface is a first axial cross-section. The distance from the first surface and / or the second surface to the first axial cross-section gradually decreases from the middle plane of the notch to both ends of the notch in the direction parallel to the axis of the first sleeve.

[0010] Preferably, the part of the middle cylindrical surface in the thickness direction of the first sleeve corresponding to the notch is a third surface. The length of the intersection line of the third surface and the plane perpendicular to the axis of the oil cylinder body is the width of the notch. The first surface is a curved surface, the second surface is a plane, and the width of the notch is:

[0011]

[0012] where n = 0.2, m = 10, y(x) is the width of the notch, and x is the distance from any point on the center line in the length direction of the second surface to the midpoint of the center line in the length direction of the second surface.

[0013] Preferably, it further includes a second sleeve and a spacer. The second sleeve is arranged in the inner cavity of the oil cylinder body. One end of the second sleeve abuts against the end of the first sleeve away from the rod body. The other end of the second sleeve abuts against an inner wall in the axial direction of the oil cylinder body. The other end of the first sleeve abuts against the other inner wall in the axial direction of the oil cylinder body. The outer wall of the spacer is hermetically and slidably connected to the inner wall of the second sleeve. The inner cavity of the oil cylinder body is formed between the inner walls of the first sleeve, the inner wall of the second sleeve, and the two inner walls in the axial direction of the oil cylinder body. The spacer can divide the second end cavity into a liquid cavity and a gas cavity.

[0014] Preferably, it further includes a first retaining ring, a second retaining ring and at least one guide rod. The first retaining ring and the second retaining ring are both arranged in the inner cavity of the cylinder body. One end of the first retaining ring abuts against and seals an inner wall of the cylinder body axially, and the other end of the first retaining ring abuts against one end of the first sleeve away from the second sleeve. One end of the second retaining ring abuts against and seals the other inner wall of the cylinder body axially, and the other end of the second retaining ring abuts against one end of the second sleeve away from the first sleeve. The two inner walls of the cylinder body axially can clamp the first sleeve and the second sleeve through the first retaining ring and the second retaining ring. A first through hole is provided in the center of the first retaining ring, and the rod body is sleeved in the first through hole of the first retaining ring, and there is a gap between the inner wall of the first through hole and the rod body; at least one guide hole is provided on each of the first retaining ring, the first piston, the second piston and the second retaining ring. Each guide rod can sequentially pass through a guide hole of the first retaining ring, a guide hole of the first piston, a guide hole of the second piston and a guide hole of the second retaining ring. Two ends of each guide rod respectively abut against two inner walls of the cylinder body axially, and the first piston and the second piston are both slidably connected to each guide rod.

[0015] Preferably, it further includes at least one limiting component. At least one first limiting groove is provided on the outer walls of the first retaining ring and the second retaining ring, and at least one second limiting groove is provided on the inner wall of the cylinder body. Each limiting component is arranged between each first limiting groove and each second limiting groove, and part of the side walls of each limiting component are in contact with the inner walls of each first limiting groove, and part of the side walls of each limiting component are in contact with the inner walls of each second limiting groove. One end of each limiting component abuts against the bottom wall of each second limiting groove, and the other end of each limiting component abuts against the inner wall of the cylinder body in the length direction.

[0016] The present invention has achieved the following technical effects compared with the prior art:

[0017] The damping-adjustable special-shaped gap damper provided by the present invention comprises a cylinder body, a piston rod assembly, a piston assembly and a first sleeve. The outer wall of the piston assembly is sealed and slidably connected to the inner wall of the first sleeve. The outer wall of the first sleeve is sealed and connected to part of the inner wall of the cylinder body. Therefore, the damping medium in the multiple cavities can only flow through the damping channel formed by the outer wall of the piston assembly and the inner wall of the cylinder body at the notch, that is, the channel is equivalent to the damping hole of the damper; in the initial state, the piston assembly is symmetrically arranged about the middle plane of the notch. When the piston rod assembly extends outward under the drive of external vibration, the damping medium is output from the outlet near the piston assembly. The damping medium flows from the cavity at the end to the cavity away from the output end of the piston assembly. Conversely, when the piston rod assembly retracts inwardly under the drive of external vibration, the damping medium flows from the cavity away from the output end of the piston assembly to the cavity close to the output end of the piston assembly. Since the size of the notch in the direction perpendicular to the axis of the first sleeve gradually decreases from the middle plane of the notch to the two ends of the notch parallel to the axis of the first sleeve, when the piston moves from the initial position to the two ends away from the initial position, the size of the damping channel between the outer wall of the piston assembly and the inner wall of the cylinder body gradually decreases, that is, the opening of the damping hole of the damper gradually decreases, and the damping force gradually increases. The damper provided by the present invention can be passively adjusted as the vibration amplitude of the mechanical vibration system changes, that is, when the vibration increases, the opening of the damping hole of the damper decreases, the damping force increases, and it has a better vibration reduction effect; at the same time, compared with the method of using a displacement sensor to adjust the damping force, the damper in the present invention does not need to increase the cost of adding a displacement sensor and its corresponding controller, and does not need to keep the device powered during use, and eliminates the complicated development and maintenance of the displacement sensor and controller, saving costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0019] Figure 1 A schematic structural diagram of a special-shaped gap damper with adjustable damping provided by the present invention;

[0020] Figure 2 It is a cross-sectional view of the damping-adjustable special-shaped gap damper of Example 2-3;

[0021] Figure 3 It is an exploded view of the damping-adjustable special-shaped gap damper of Example 2-3;

[0022] Figure 4Explosion diagram of the cylinder block, first retaining ring, limiting component and guide rod provided by the present invention;

[0023] Figure 5 Schematic structural diagram of the notch provided by the present invention;

[0024] Figure 6 Function curve graph of the notch width in Embodiment 3;

[0025] Figure 7 Function curve graph of the damping coefficient and piston displacement in Embodiment 3;

[0026] Figure 8 Function curve graph of the equivalent damping coefficient and piston displacement in Embodiment 3;

[0027] Figure 9 Radial cross-sectional view of the first sleeve in Embodiment 3;

[0028] Figure 10 Schematic structural diagram of the first sleeve in Embodiment 3;

[0029] In the figure: 100, special-shaped clearance damper with adjustable damping; 1, oil cylinder body; 101, first end cavity; 102, second end cavity; 103, intermediate cavity; 104, liquid cavity; 105, gas cavity; 106, end cover; 107, cylinder block; 2, piston rod assembly; 201, rod body; 202, lead screw; 203, first thread section; 204, second thread section; 3, piston assembly; 301, first piston; 302, second piston; 4, first sleeve; 401, notch; 402, first surface; 403, second surface; 404, notch arc; 405, fan-shaped surface; 406, first inclined plane; 407, second inclined plane; 408, intermediate arc surface; 409, third surface; 5, second sleeve; 6, isolation pad; 7, first retaining ring; 701, first through hole; 8, second retaining ring; 9, guide rod; 10, guide hole; 11, limiting component; 12, first limiting groove; 13, second limiting groove; 14, sealing ring; 15, lifting ring. Detailed implementation manners

[0030] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0031] The purpose of the present invention is to provide a special-shaped clearance damper with adjustable damping to solve the problems existing in the above-mentioned prior art, having a better vibration damping effect and lower cost.

[0032] To make the above objects, features, and advantages of the present invention more obvious and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0033] Embodiment 1

[0034] As Figure 1 shown, the present invention provides a special-shaped gap damper 100 with adjustable damping, including an oil cylinder body 1, a piston rod assembly 2, a piston assembly 3, and a first sleeve 4. A notch 401 is provided on the side wall of the first sleeve 4 and is arranged along the axis direction of the first sleeve 4, and the notch 401 penetrates the first sleeve 4 along the axis direction of the first sleeve 4. The notch 401 has a middle plane in the axis direction parallel to the first sleeve 4, and the dimension of the notch 401 in the direction perpendicular to the axis of the first sleeve 4 gradually decreases from the middle plane of the notch 401 to both ends of the notch 401 parallel to the axis of the first sleeve 4. The piston assembly 3 is sleeved outside the piston rod assembly 2 and is sealed and fixedly connected to the piston rod assembly 2. When the piston rod assembly 2 does not expand or contract, the piston assembly 3 is symmetrically arranged with respect to the middle plane of the notch 401. The outer wall of the piston assembly 3 is sealed and slidably connected to the inner wall of the first sleeve 4. The outer wall of the first sleeve 4 is sealed and connected to a part of the inner wall of the oil cylinder body 1. One end of the piston rod assembly 2 is sleeved inside the first sleeve 4, and the other end of the piston rod assembly 2 is slidably connected to the oil cylinder body 1. The piston assembly 3 can divide the inner cavity of the oil cylinder body 1 into at least two cavities.

[0035] Since the outer wall of the piston assembly 3 is sealed and slidably connected to the inner wall of the first sleeve 4, and the outer wall of the first sleeve 4 is sealed and connected to part of the inner wall of the cylinder body 1, the damping medium in the multiple cavities can only flow through the damping channel formed by the outer wall of the piston assembly 3 and the inner wall of the cylinder body 1 at the notch 401, that is, the channel is equivalent to the damping hole of the damping adjustable special-shaped gap damper 100; in the initial state, the piston assembly 3 is symmetrically arranged about the middle plane of the notch 401, and when the piston rod assembly 2 extends outward under the drive of external vibration, the damping medium flows from the cavity close to the output end of the piston rod assembly 2 to the cavity away from the output end of the piston rod assembly 2, and vice versa, when the piston rod assembly 2 is outside When retracting inward under the drive of vibration, the damping medium flows from the cavity away from the output end of the piston rod assembly 2 to the cavity close to the output end of the piston rod assembly 2; since the size of the notch 401 in the direction perpendicular to the axis of the first sleeve 4 gradually decreases from the middle plane of the notch 401 to the two ends of the notch 401 parallel to the axis of the first sleeve 4, a damper with anisotropic gap (notch) is formed; when the piston assembly 3 moves from the initial position to the two ends away from the initial position, the size of the damping channel between the outer wall of the piston assembly 3 and the inner wall of the cylinder body 1 gradually decreases, that is, the opening of the damping hole of the damping adjustable special-shaped gap damper 100 gradually decreases, and the damping force gradually increases. The damping-adjustable special-shaped gap damper 100 provided by the present invention can be passively adjusted as the vibration amplitude of the mechanical vibration system changes, that is, when the vibration amplitude increases, the opening of the damping hole of the damping-adjustable special-shaped gap damper 100 decreases, and the damping force increases, which has a better vibration reduction effect; at the same time, compared with the method of using a displacement sensor to adjust the damping force, the damping-adjustable special-shaped gap damper 100 in the present invention does not need to increase the cost of adding a displacement sensor and its corresponding controller, and does not need to keep the device powered on during use, and eliminates the complicated development and maintenance of the displacement sensor and controller, saving costs.

[0036] The piston assembly 3 includes a piston body, and the piston body is symmetrically arranged about the middle plane of the notch 401 when the piston rod assembly 2 is not extended or retracted.

[0037] Example 2

[0038] This embodiment provides a damping-adjustable special-shaped gap damper 100, which is different from the damping-adjustable special-shaped gap damper 100 in Embodiment 1 in that:

[0039] like Figures 2-3As shown in the figure, the piston assembly 3 includes a first piston 301 and a second piston 302. Both the first piston 301 and the second piston 302 are sleeved outside the piston rod assembly 2 and are hermetically and fixedly connected to the piston rod assembly 2. When the piston rod assembly 2 does not extend or retract, the first piston 301 and the second piston 302 are symmetrically arranged with respect to the middle plane of the notch 401. The outer walls of the first piston 301 and the second piston 302 are hermetically and slidably connected to the inner wall of the first sleeve 4. The first piston 301 and the second piston 302 can divide the inner cavity of the oil cylinder body 1 into a first end cavity 101, a second end cavity 102, and an intermediate cavity 103. A first damping channel is formed between the outer wall of the first piston 301 and the inner wall of the oil cylinder body 1 at the notch 401, and a second damping channel is formed between the outer wall of the second piston 302 and the inner wall of the oil cylinder body 1 at the notch 401. In the initial state, the first piston 301 and the second piston 302 are respectively located at both ends of the center position of the notch 401. When the piston rod assembly 2 extends outward driven by an external vibration, the damping medium in the first end cavity 101 is compressed and flows into the intermediate cavity 103. The pressure in the intermediate cavity 103 increases and the damping medium in the intermediate cavity 103 flows into the second end cavity 102. That is, the first liquid channel and the second liquid channel are equivalent to the damping holes of the damper. When the damping medium flows through the damping holes, a damping force will be generated, and the smaller the damping holes, the greater the damping force. By reasonably setting the degree of decrease of the width of the notch 401 from the middle to both ends, the total opening of the first liquid channel and the second liquid channel can be reduced, that is, the total opening of the damping holes of the damper is reduced. Therefore, the damping force when the damping medium flows through the first liquid channel and the second liquid channel increases. Similarly, when the piston rod assembly 2 retracts inward driven by an external vibration, the opening of the first liquid channel increases and the opening of the second liquid channel decreases. Through calculation, it can be known that the total opening of the first liquid channel and the second liquid channel decreases, and the damping force when the damping medium flows through the first liquid channel and the second liquid channel increases. The variable-damping special-shaped gap damper 100 provided by the present invention can be passively adjusted with the change of the vibration amplitude of the mechanical vibration system. That is, when the vibration increases, the total opening of the damping holes of the variable-damping special-shaped gap damper 100 decreases and the damping force increases, having a good vibration damping effect.

[0040] As Figures 2-3As shown, the piston rod assembly 2 includes a rod body 201 and a lead screw 202. One end of the rod body 201 is slidably connected to the cylinder body 1. Preferably, a sealing ring 14 is provided between the outer wall of the rod body 201 and the inner wall of the cylinder body 1. The other end of the rod body 201 is fixedly connected to one end of the lead screw 202, preferably by threaded connection. The other end of the lead screw 202 has a first thread section 203 and a second thread section 204. The threads of the first thread section 203 and the second thread section 204 have opposite helix directions. The first piston 301 is sleeved outside the first thread section 203 and is hermetically and threadedly connected to the first thread section 203. The second piston 302 is sleeved outside the second thread section 204 and is hermetically and threadedly connected to the second thread section 204. By rotating the rod body 201, the lead screw 202 can be driven to rotate, so that the first piston 301 and the second piston 302 move in a direction approaching or departing from each other. Since the width of the notch 401 gradually decreases from the middle to both ends, by adjusting the positions of the first piston 301 and the second piston 302, the opening degrees of the first liquid channel and the second liquid channel can be adjusted, and further the damping force of the damper can be adjusted. Specifically, when the first piston 301 and the second piston 302 move in a direction away from each other, the opening degrees of the first liquid channel and the second liquid channel both decrease relative to the initial opening degrees. Then, when the rod body 201 extends or retracts by the same distance relative to when the opening degrees of the first liquid channel and the second liquid channel are not adjusted, the total opening degree of the first liquid channel and the second liquid channel decreases, and the corresponding damping force increases. On the contrary, when the first piston 301 and the second piston 302 move in a direction approaching each other, the opening degrees of the first liquid channel and the second liquid channel both increase relative to the initial opening degrees. Then, when the rod body 201 extends or retracts by the same distance relative to when the opening degrees of the first liquid channel and the second liquid channel are not adjusted, the total opening degree of the first liquid channel and the second liquid channel increases, and the corresponding damping force decreases.

[0041] As Figure 5 shown, a first surface 402 and a second surface 403 that are both connected to the inner and outer side walls of the first sleeve 4 are formed at the notch 401 of the first sleeve 4. The axial section of the first sleeve 4 between the first surface 402 and the second surface 403 is the first axial section. The distances from the first surface 402 and / or the second surface 403 to the first axial section gradually decrease from the middle plane of the notch 401 to both ends in the direction parallel to the axis of the first sleeve 4, so that the width of the notch 401 gradually decreases from the middle to both ends.

[0042] As a preferred embodiment, when the vibration amplitudes of the vibrations to be suppressed are the same on both sides of the initial position, the first surface 402 and the second surface 403 are symmetrically arranged with respect to the middle plane of the notch 401 when the piston rod assembly 2 does not extend or retract.

[0043] As Figures 2-3As shown in the figure, the special-shaped gap damper 100 with adjustable damping provided by the present invention further includes a second sleeve 5 and a spacer 6. The second sleeve 5 is disposed inside the inner cavity of the cylinder body 1. One end of the second sleeve 5 abuts against the end of the first sleeve 4 away from the rod body 201, and the other end of the second sleeve 5 abuts against an inner wall of the cylinder body 1 in the axial direction. The other end of the first sleeve 4 abuts against the other inner wall of the cylinder body 1 in the axial direction. The outer wall of the spacer 6 is hermetically and slidably connected to the inner wall of the second sleeve 5. An inner cavity of the cylinder body 1 is formed between the inner walls of the first sleeve 4, the second sleeve 5, and the two inner walls of the cylinder body 1 in the axial direction. The spacer 6 can divide the second end cavity 102 into a liquid cavity 104 and a gas cavity 105. The gas cavity 105 is filled with gas. When the rod body 201 retracts inwardly, the gas is compressed, and the pressure in the gas cavity 105 increases, playing an auxiliary shock-absorbing effect. The gas is preferably nitrogen.

[0044] As Figures 2-4 shown in the figure, it further includes a first retaining ring 7, a second retaining ring 8, and at least one guide rod 9. The first retaining ring 7 and the second retaining ring 8 are both disposed inside the inner cavity of the cylinder body 1. Preferably, the outer walls of the first retaining ring 7 and the second retaining ring 8 are both in contact with the inner wall of the cylinder body 1. One end of the first retaining ring 7 abuts against and seals an inner wall of the cylinder body 1 in the axial direction, and the other end of the first retaining ring 7 abuts against the end of the first sleeve 4 away from the second sleeve 5. One end of the second retaining ring 8 abuts against and seals the other inner wall of the cylinder body 1 in the axial direction, and the other end of the second retaining ring 8 abuts against the end of the second sleeve 5 away from the first sleeve 4. The two inner walls of the cylinder body 1 in the axial direction can clamp the first sleeve 4 and the second sleeve 5 through the first retaining ring 7 and the second retaining ring 8, realizing the fixed connection of the first sleeve 4 and the second sleeve 5 and limiting the axial direction of the first sleeve 4 and the second sleeve 5. A first through hole 701 is provided at the center of the first retaining ring 7. The rod body 201 is sleeved inside the first through hole 701 of the first retaining ring 7, and a gap is left between the inner wall of the first through hole 701 and the rod body 201. At least one guide hole 10 is provided on each of the first retaining ring 7, the first piston 301, the second piston 302, and the second retaining ring 8. Each guide rod 9 can sequentially pass through a guide hole 10 of the first retaining ring 7, a guide hole 10 of the first piston 301, a guide hole 10 of the second piston 302, and a guide hole 10 of the second retaining ring 8. Both ends of each guide rod 9 abut against the two inner walls of the cylinder body 1 in the axial direction. The first piston 301 and the second piston 302 are both slidably connected to each guide rod 9. As a preferred embodiment, a sealing ring 14 is provided between the first retaining ring 7 and the cylinder body 1, and a sealing ring 14 is provided between the second retaining ring 8 and the cylinder body 1. The axes of the multiple holes on the first retaining ring 7, the first piston 301, the second piston 302, and the second retaining ring 8 for the same guide rod 9 to pass through are collinear. The guide rod 9 can guide the first piston 301 and the second piston 302 to ensure the stability of operation.

[0045] As Figure 4 shown, the special-shaped gap damper 100 with adjustable damping provided by the present invention further includes at least one limiting member 11. Preferably, there are two limiting members 11. At least one first limiting groove 12 is provided on the outer walls of the first retaining ring 7 and the second retaining ring 8, and at least one second limiting groove 13 is provided on the inner wall of the cylinder body 1. Each limiting member 11 is arranged between each first limiting groove 12 and each second limiting groove 13, and part of the side walls of each limiting member 11 are in contact with the inner side walls of each first limiting groove 12, and part of the side walls of each limiting member 11 are in contact with the inner side walls of each second limiting groove 13. One end of each limiting member 11 abuts against the bottom wall of each second limiting groove 13, and the other end of each limiting member 11 abuts against the inner wall of the cylinder body 1 in the length direction. The limiting member 11 can limit the rotation of the first retaining ring 7 and the second retaining ring 8 around their own axial directions, reduce or avoid the movement of the guide rod 9 caused by the rotation of the first retaining ring 7 and the second retaining ring 8, and ensure the stability of operation.

[0046] As a preferred embodiment, the cylinder body 1 includes two end covers 106 and a cylinder block 107. The two end covers 106 are respectively fixedly connected to both ends of the cylinder block 107. A sealing ring 14 is provided between the inner walls of the two end covers 106 and the first retaining ring 7 and the second retaining ring 8. Both ends of the guide rod 9 abut against the inner walls of the two end covers 106 respectively. A lifting ring 15 is fixedly connected to the end of the rod body 201 far from the piston assembly 3, and a lifting ring 15 is also fixedly connected to the end cover 106 far from the rod body 201.

[0047] Other contents in this embodiment are the same as those in Embodiment 1.

[0048] Embodiment 3

[0049] This embodiment provides a special-shaped gap damper 100 with adjustable damping. The difference from the special-shaped gap damper 100 in Embodiment 2 is that:

[0050] As Figure 5 shown, the middle cylindrical surface in the thickness direction of the first sleeve 4 and the part corresponding to the notch 401 is the third surface 409. The length of the intersection line of the third surface 409 and the plane perpendicular to the axis of the cylinder body 1 is the width of the notch 401. The first surface 402 is a curved surface, the second surface 403 is a plane, and the width of the notch 401 is:

[0051]

[0052] wherein, n and m are notch parameters, n = 0.2 - 0.3, m = 8 - 12, and x is the distance from any point on the center line of the second surface 403 parallel to the axis of the first sleeve 4 to the midpoint of the center line of the second surface 403 parallel to the axis of the first sleeve 4. The function curve of the width of the notch 401 is asFigure 6 as shown

[0053] The calculation method of the damping coefficient of this preferred embodiment is as follows:

[0054] 1. Calculate the method for calculating the pressure difference at both ends of the first piston 301 or the second piston 302 when the length is dx as follows (hereinafter, the first piston 301 is taken as an example for illustration):

[0055] 1.1. The intersection line of the third surface 409 and the plane perpendicular to the axis of the oil cylinder body 1 is the notch arc 404. The notch arc 404 corresponds to a sector surface 405. The center of the sector surface 405 is on the axis of the first sleeve 4. Take a micro-sector surface 405 with an angle of dθ on the sector surface 405. The flow rate of the damping medium allowed to pass through the micro-sector surface 405 of dθ is:

[0056]

[0057] where t is the thickness of the first sleeve 4, k is the consistency coefficient of the damping medium, M is the flow index of the damping medium (Newtonian liquid), M = 1, and R is the radius of the notch arc 404 of the first sleeve 4.

[0058] 1.2. The pressure difference at both ends of the first piston 301 with a length of dx is:

[0059]

[0060] where Q is the flow rate of the first damping channel.

[0061] 2. The pressure difference between the two bottom surfaces of the first piston 301 when the thickness of the first piston 301 is 2H is:

[0062] Define the position of the middle surface in the axial direction of the first piston 301 as x 活塞 , then the positions of the two bottom surfaces at both ends of the first piston 301 are x 活塞 +H and x 活塞 -H. Integrate formula (3) to obtain the calculation formula for the pressure difference between the two bottom surfaces of the first piston 301 as:

[0063]

[0064] Define the distance between the axial center surface of the first piston 301 and the axial center surface of the second piston 302 as 2b, and the position of the axial midpoint of the first piston 301 and the second piston 302 as x0 (taking the midpoint of the center line of the second surface 403 parallel to the axis of the first sleeve 4 as the zero point of the x coordinate axis). The positions x 活塞1 、x 活塞2They are x0 + b and x0 - b respectively. Substituting x0 + b into formula (4), the pressure difference at both ends of the first piston 301 is obtained as follows:

[0065]

[0066] Similarly, substituting x0 - b into formula (4), the pressure difference at both ends of the second piston 302 is obtained as follows:

[0067]

[0068] Adding formula (5) and formula (6), the total pressure difference between the end face of the first piston 301 away from the second piston 302 and the end face of the second piston 302 away from the first piston 301 is obtained as follows:

[0069]

[0070] 3. The calculation method of the damping coefficient of the variable-damping special-shaped clearance damper 100 is as follows:

[0071] The damping force of the variable-damping special-shaped clearance damper 100 is:

[0072]

[0073] Among them, Q = Sv0, where v0 is the moving speed of the piston rod assembly 2. Substituting it into formula (8), we get:

[0074]

[0075] Among them, S is the area of the piston end face. F = cv0. Substituting it into formula (9), the relationship between the damping coefficient c and the position x0 of the piston rod assembly 2 is obtained as follows:

[0076]

[0077] It can be seen from formula (9) that the greater the deviation of the piston rod assembly 2 from the zero point of the x coordinate axis, the greater the damping coefficient of the variable-damping special-shaped clearance damper 100. That is, when the distance that the piston rod assembly 2 extends outwards or the distance that the piston retracts into the oil cylinder body 1 is greater, the damping coefficient of the variable-damping special-shaped clearance damper 100 is greater. The function curve of c and x0 is as Figure 7 shown, and the change of the damping coefficient with the displacement of the piston rod assembly 2 presents a parabolic shape.

[0078] It can be seen from formula (9) that when x0 is constant, the greater the value of b, the greater the damping coefficient. That is, when the piston rod extends or retracts by the same distance, the greater the distance between the two pistons, the greater the damping coefficient.

[0079] 4. The calculation method of the equivalent damping coefficient of the special-shaped clearance damper 100 with adjustable damping when the piston rod assembly 2 vibrates in a sine manner is as follows:

[0080] When the piston rod assembly 2 vibrates in a sine manner, x0 = Asin(2πft0), v0 = A·2πfcos(2πft0), where A is the vibration amplitude and f is the vibration frequency. During half a cycle of piston vibration, that is when x0 ∈ [-A, A], the relationship between the speed of the piston rod assembly 2 and the displacement of the piston rod assembly 2 can be expressed as:

[0081]

[0082] Since the damper dissipates vibration energy through damping, integrating the damping force F in formula (9) over the displacement [-A, A], the dissipated energy can be obtained as:

[0083]

[0084] For a damper with a constant damping coefficient, its damping force is:

[0085]

[0086] The energy dissipated by the damper with a constant damping coefficient is:

[0087]

[0088] Then, from W1 = W2, the relationship between the equivalent damping coefficient of the special-shaped clearance damper 100 with variable damping and the vibration amplitude can be obtained as:

[0089]

[0090] It can be seen from formula (12) that when the amplitude A is larger, the equivalent damping coefficient of the special-shaped clearance damper 100 with adjustable damping is larger, that is, when the maximum distance that the piston rod assembly 2 extends outwards or the maximum distance that the piston retracts into the oil cylinder body 1 is larger, the equivalent damping coefficient of the special-shaped clearance damper 100 with adjustable damping is larger. It can meet the requirement that when the vibration amplitude is large and the frequency is low, the damping of the special-shaped clearance damper 100 with adjustable damping is larger, and when the vibration amplitude is small and the frequency is high, the damping of the special-shaped clearance damper 100 with adjustable damping is smaller. The function curve of the equivalent damping coefficient and the vibration amplitude is as Figure 8 shown, and the change of the equivalent damping coefficient with the vibration amplitude presents a parabolic shape.

[0091] It can be seen from formula (12) that when the amplitude A is constant, the larger b is, the larger the damping coefficient is, that is, the larger the distance between the two pistons is, the larger the damping coefficient is.

[0092] It should be noted that the first surface 402 in this embodiment is not limited to a curved surface, and can also be other forms that can satisfy the damping coefficient increasing with the increase of the amplitude and decreasing with the decrease of the amplitude: such as Figure 10 As shown, the first surface 402 includes a first inclined plane 406, a second inclined plane 407 and an intermediate arc surface 408 that are connected to each other. The first inclined plane 406 and the second inclined plane 407 are smoothly connected through the intermediate arc surface 408. The first inclined plane 406 and the second inclined plane 407 are symmetric about the intermediate plane of the notch 401. The distance from the end of the first inclined plane 406 close to the second inclined plane 407 to the first axial section is greater than the distance from the end of the other end of the first inclined plane 406 to the first axial section. The distance from the end of the second inclined plane 407 close to the first inclined plane 406 to the first axial section is greater than the distance from the end of the other end of the second inclined plane 407 to the first axial section. The second surface 403 of the intermediate arc surface 408 is a plane, and the size y(x) of the notch corresponding to the intermediate arc surface 408 changes little in the direction of the axis of the first sleeve 4. The length of the intermediate arc surface 408 is determined according to the vibration amplitude. Preferably, the first piston 301 is located at the transition between the first inclined plane 406 and the intermediate arc surface 408, and the second piston 302 is located at the transition between the second inclined plane 407 and the intermediate arc surface 408, ensuring that within the vibration period, one piston moves corresponding to the first sleeve section on the first inclined plane 406 or the second inclined plane 407, and the other piston moves corresponding to the first sleeve section on the intermediate arc surface 408. Furthermore, when the other piston moves along the axis of the first sleeve 4 at the position of the intermediate arc surface 408, the change in piston damping is small, or even negligible. Therefore, when the piston assembly 3 moves upward, the notch corresponding to the first piston 301 gradually decreases, and the change in the notch corresponding to the second piston 302 is small. The overall damping is greatly affected by the first piston 301, that is, the overall damping increases; similarly, when the piston assembly 3 moves downward, the overall damping is greatly affected by the second piston 302, that is, the overall damping increases. It should be noted that the inclination angles of the first inclined plane 406 and the second inclined plane 407 and the radius of the intermediate arc surface 408 can be determined by calculation and / or experiment according to existing experience.

[0093] Other parts in this embodiment are the same as those in Embodiment 2.

[0094] Specific examples are used in the present invention to elaborate on the principles and implementation manners of the present invention. The descriptions of the above embodiments are only used to help understand the method and its core idea of the present invention; at the same time, for those of ordinary skill in the art, according to the idea of the present invention, there will be changes in the specific implementation manners and application scopes. In summary, the content of this specification should not be construed as a limitation to the present invention.

Claims

1. A special-shaped gap damper with adjustable damping, characterized in that: It includes an oil cylinder body, a piston rod assembly, a piston assembly and a first sleeve. A notch is provided on the side wall of the first sleeve and is arranged along the direction parallel to the axis of the first sleeve, and the notch penetrates through the first sleeve along the direction parallel to the axis of the first sleeve. The notch has a middle plane in the direction parallel to the axis of the first sleeve, and the dimension of the notch in the direction perpendicular to the axis of the first sleeve gradually decreases from the middle plane of the notch to both ends of the notch parallel to the axis of the first sleeve. The piston assembly is sleeved outside the piston rod assembly and is hermetically and fixedly connected to the piston rod assembly. When the piston rod assembly does not extend or retract, the piston assembly is symmetrically arranged with respect to the middle plane of the notch. The outer wall of the piston assembly is hermetically and slidably connected to the inner wall of the first sleeve. The outer wall of the first sleeve is hermetically connected to a part of the inner wall of the oil cylinder body. One end of the piston rod assembly is sleeved inside the first sleeve, and the other end of the piston rod assembly is slidably connected to the oil cylinder body. The piston assembly can divide the inner cavity of the oil cylinder body into at least two cavities.

2. The variable-damping special-shaped clearance damper according to claim 1, wherein: The piston assembly includes a piston body. When the piston rod assembly does not extend or retract, the piston body is symmetrically arranged with respect to the middle plane of the notch.

3. The special-shaped clearance damper with adjustable damping according to claim 1, characterized in that: The piston assembly includes a first piston and a second piston. The first piston and the second piston are both sleeved outside the piston rod assembly and are hermetically and fixedly connected to the piston rod assembly. When the piston rod assembly does not extend or retract, the first piston and the second piston are symmetrically arranged with respect to the middle plane of the notch. The outer walls of the first piston and the second piston are hermetically and slidably connected to the inner wall of the first sleeve. The first piston and the second piston can divide the inner cavity of the oil cylinder body into a first end cavity, a second end cavity and a middle cavity.

4. The variable-damping special-shaped clearance damper according to claim 3, characterized in that: The piston rod assembly includes a rod body and a lead screw. One end of the rod body is slidably connected to the oil cylinder body, and the other end of the rod body is fixedly connected to one end of the lead screw. The other end of the lead screw has a first thread section and a second thread section. The thread of the first thread section and the thread of the second thread section have opposite helix directions. The first piston is sleeved outside the first thread section and is hermetically and threadedly connected to the first thread section. The second piston is sleeved outside the second thread section and is hermetically and threadedly connected to the second thread section.

5. The variable-damping special-shaped clearance damper according to claim 3, wherein: A first surface and a second surface that are both connected to the inner and outer side walls of the first sleeve are formed at the notch of the first sleeve. The axial section of the first sleeve between the first surface and the second surface is a first axial section. The distance from the first surface and / or the second surface to the first axial section gradually decreases from the middle plane of the notch to both ends of the notch parallel to the axis of the first sleeve.

6. The variable-damping special-shaped clearance damper according to claim 5, characterized in that: The part of the middle cylindrical surface in the thickness direction of the first sleeve corresponding to the notch is the third surface. The length of the intersection line between the third surface and the plane perpendicular to the axis of the oil cylinder body is the width of the notch. The first surface is a curved surface, the second surface is a plane, and the width of the notch is: where n and m are notch parameters, n = 0.2 - 0.3, m = 8 - 12, y(x) is the width of the notch, and x is the distance from any point on the center line of the second surface parallel to the axis of the first sleeve 4 to the midpoint of the center line of the second surface parallel to the axis of the first sleeve 4.

7. The variable-damping special-shaped clearance damper according to claim 4, wherein: It further includes a second sleeve and a spacer. The second sleeve is arranged in the inner cavity of the oil cylinder body. One end of the second sleeve abuts against the end of the first sleeve away from the rod body, the other end of the second sleeve abuts against an inner wall in the axial direction of the oil cylinder body, the other end of the first sleeve abuts against the other inner wall in the axial direction of the oil cylinder body. The outer wall of the spacer is hermetically and slidably connected to the inner wall of the second sleeve. The inner cavity of the oil cylinder body is formed between the inner wall of the first sleeve, the inner wall of the second sleeve, and the two inner walls in the axial direction of the oil cylinder body. The spacer can divide the second end cavity into a liquid cavity and a gas cavity.

8. The variable-damping special-shaped clearance damper according to claim 7, wherein: It further includes a first retaining ring, a second retaining ring, and at least one guide rod. The first retaining ring and the second retaining ring are both arranged in the inner cavity of the oil cylinder body. One end of the first retaining ring abuts against and seals an inner wall in the axial direction of the oil cylinder body, and the other end of the first retaining ring abuts against the end of the first sleeve away from the second sleeve. One end of the second retaining ring abuts against and seals the other inner wall in the axial direction of the oil cylinder body, and the other end of the second retaining ring abuts against the end of the second sleeve away from the first sleeve. The two inner walls in the axial direction of the oil cylinder body can clamp the first sleeve and the second sleeve through the first retaining ring and the second retaining ring. A first through hole is provided in the center of the first retaining ring, and the rod body is sleeved in the first through hole of the first retaining ring, and there is a gap between the inner wall of the first through hole and the rod body; at least one guide hole is provided on the first retaining ring, the first piston, the second piston, and the second retaining ring. Each guide rod can sequentially pass through a guide hole of the first retaining ring, a guide hole of the first piston, a guide hole of the second piston, and a guide hole of the second retaining ring. Both ends of each guide rod abut against the two inner walls in the axial direction of the oil cylinder body, and the first piston and the second piston are both slidably connected to each guide rod.

9. The variable-damping special-shaped clearance damper according to claim 8, wherein: It further includes at least one limiting member. At least one first limiting groove is provided on the outer walls of the first retaining ring and the second retaining ring, and at least one second limiting groove is provided on the inner wall of the cylinder body. Each of the limiting members is disposed between each of the first limiting grooves and each of the second limiting grooves, and a partial side wall of each of the limiting members contacts the inner wall of each of the first limiting grooves, a partial side wall of each of the limiting members contacts the inner wall of each of the second limiting grooves, one end of each of the limiting members abuts against the bottom wall of each of the second limiting grooves, and the other end of each of the limiting members abuts against the inner wall in the length direction of the cylinder body.

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