CN116379094A - Special-shaped gap damper with adjustable damping - Google Patents

Special-shaped gap damper with adjustable damping Download PDF

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Publication number
CN116379094A
CN116379094A CN202310316376.2A CN202310316376A CN116379094A CN 116379094 A CN116379094 A CN 116379094A CN 202310316376 A CN202310316376 A CN 202310316376A CN 116379094 A CN116379094 A CN 116379094A
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China
Prior art keywords
piston
sleeve
wall
cylinder body
damping
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CN202310316376.2A
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Chinese (zh)
Inventor
李雪平
陈晨
罗均
白如清
徐浪
赵晶雷
易进
肖登宇
蒲华燕
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Chongqing University
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Chongqing University
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Priority to CN202310316376.2A priority Critical patent/CN116379094A/en
Publication of CN116379094A publication Critical patent/CN116379094A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/19—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with a single cylinder and of single-tube type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/3207—Constructional features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/3207—Constructional features
    • F16F9/3214—Constructional features of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/3207—Constructional features
    • F16F9/3235—Constructional features of cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
    • F16F9/49—Stops limiting fluid passage, e.g. hydraulic stops or elastomeric elements inside the cylinder which contribute to changes in fluid damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

The invention discloses a damping-adjustable special-shaped gap damper, which relates to the field of vibration reduction and comprises an oil cylinder body, a piston rod assembly, a piston assembly and a first sleeve, wherein a notch is arranged on the side wall of the first sleeve along the direction parallel to the axis of the first sleeve, a middle plane is arranged on the notch along the direction parallel to the axis of the first sleeve, the size of the notch in the axial direction perpendicular to the first sleeve is reduced from the middle plane of the notch to two ends of the notch parallel to the axial direction of the first sleeve, the piston assembly is sleeved outside the piston rod assembly and is in sealing and fixing connection with the piston rod assembly, the piston assembly is symmetrical with the middle plane of the notch when the piston rod assembly does not stretch, the outer wall of the piston assembly is in sealing and sliding connection with the inner wall of the first sleeve, the outer wall of the first sleeve is in sealing and connecting with the inner wall of the oil cylinder body, one end of the piston rod assembly is sleeved in the first sleeve, the other end of the piston rod assembly is in sliding connection with the oil cylinder body, and the piston assembly can divide the inner cavity of the oil cylinder body into at least two cavities. The vibration reduction effect is good and the cost is low.

Description

Special-shaped gap damper with adjustable damping
Technical Field
The invention relates to the technical field of vibration reduction equipment, in particular to a special-shaped gap damper with adjustable damping.
Background
The damper is a device for reducing mechanical vibration and consuming kinetic energy by utilizing damping characteristics, and can quickly absorb vibration energy of a vibration system, so that the damper is widely applied to various technical fields such as aerospace, automobiles, ships, buildings and the like. However, in general, the vibration amplitude of the mechanical vibration system is not fixed, and when the vibration amplitude is large, the damper is required to have a large damping force, and when the vibration amplitude is small, the damper is required to have a small damping force. In order to adapt to different vibration amplitudes of a vibration system, an active control system is generally adopted for adjusting damping force of the existing damper, and the method specifically comprises the following steps: the damper is provided with a displacement sensor, the displacement information of the piston rod assembly or the piston is detected through the displacement sensor, and the controller adjusts the damping force according to the displacement information of the piston rod assembly or the piston. For example, chinese patent CN201721672013.9 discloses a novel magnetorheological damper capable of detecting displacement of a piston, integrating a capacitive displacement sensor with the magnetorheological damper, the capacitive displacement sensor detecting displacement of a spring connecting plate to obtain a sensing output signal containing displacement information of the spring connecting plate, and amplifying the signal in equal proportion to obtain the displacement information of the piston. And (3) according to the obtained piston displacement information, the current of the exciting coil is timely adjusted, so that optimal damping force control is achieved. As disclosed in chinese patent CN201720411824.7, a novel damper is provided with a pressure sensor and a proportional valve outside the cylinder, a displacement sensor is provided inside the cylinder, the displacement sensor is used for measuring the position of the piston rod assembly 3 in real time, and calculating the movement speed of the piston rod assembly, and the pressure sensor is used for monitoring and measuring the pressure inside the 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, the movement speed of the piston is calculated according to the displacement signal, then the displacement of the damper and the deviation between the pressure value and the set value are calculated, the deviation is fed back to the proportional valve, and the flow of fluid in the oil cylinder is regulated after the proportional valve receives the signal, so that the damping force is accurately controlled. The mode of the displacement information adjustment damping force of this piston rod subassembly or piston needs the attenuator to keep the circular telegram for a long time in order to keep continuously detecting, and displacement sensor and controller's development and maintenance work are comparatively loaded down with trivial details, and the consumption is higher and the cost is higher.
Disclosure of Invention
The invention aims to provide a special-shaped gap damper with adjustable damping, which solves the problems in the prior art, and has better damping effect and lower cost.
In order to achieve the above object, the present invention provides the following solutions:
the invention provides a damping-adjustable special-shaped gap damper which comprises an oil cylinder body, a piston rod assembly, a piston assembly and a first sleeve, wherein a notch which is arranged along the axis direction parallel to the first sleeve is arranged on the side wall of the first sleeve, the notch penetrates through the first sleeve along the axis direction parallel to the first sleeve, the notch is provided with a middle plane along the axis direction parallel to the first sleeve, the size of the notch along the axis direction perpendicular to the first sleeve is gradually reduced from the middle plane of the notch to two ends of the notch along the axis direction parallel to the first sleeve, the piston assembly is sleeved outside the piston rod assembly and is in sealing and fixed connection with the piston rod assembly, the piston assembly is symmetrically arranged about the middle plane of the notch when the piston rod assembly does not stretch, the outer wall of the piston assembly is in sealing and sliding connection with the inner wall of the first sleeve, the outer wall of the first sleeve is in sealing connection with the inner wall of a part of the oil cylinder body, one end of the piston assembly is sleeved inside the first sleeve, and at least two inner cavities can be separated from the piston assembly, and at least two inner cavities can be connected with the piston assembly.
Preferably, the piston assembly comprises a piston body, and the piston body is symmetrically arranged about the middle plane of the notch when the piston rod assembly is not in telescopic operation.
Preferably, the piston assembly comprises a first piston and a second piston, the first piston and the second piston are sleeved outside the piston rod assembly and are in sealing and fixed connection with the piston rod assembly, the first piston and the second piston are symmetrically arranged relative to the middle plane of the notch when the piston rod assembly is not in extension and retraction, the outer wall of the first piston and the outer wall of the second piston are in sealing and sliding connection with the inner wall of the first sleeve, and 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.
Preferably, the piston rod assembly comprises a rod body and a screw rod, one end of the rod body is in sliding connection with the oil cylinder body, the other end of the rod body is fixedly connected with one end of the screw rod, the other end of the screw rod is provided with a first threaded section and a second threaded section, threads of the first threaded section are opposite to threads of the second threaded section in rotation direction, the first piston is sleeved outside the first threaded section and is in sealing and threaded connection with the first threaded section, and the second piston is sleeved outside the second threaded section and is in sealing and threaded connection with the second threaded section.
Preferably, a first surface and a second surface which are connected with the inner side wall and the outer side wall 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, and the distance from the first surface and/or the second surface to the first axial section is gradually reduced from the middle plane of the notch to two ends of the notch parallel to the axial direction of the first sleeve.
Preferably, the portion of the middle cylindrical surface in the thickness direction of the first sleeve, corresponding to the notch, is a third surface, the length of an intersection line of the third surface and a plane perpendicular to the axis of the 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:
Figure SMS_1
wherein 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 of the second surface in the length direction to the midpoint of the center line of the second surface in the length direction.
Preferably, the hydraulic oil cylinder further comprises 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 is abutted to one end of the first sleeve, which is far away from the rod body, the other end of the second sleeve is abutted to one inner wall of the oil cylinder body in the axial direction, the other end of the first sleeve is abutted to the other inner wall of the oil cylinder body in the axial direction, the outer wall of the spacer is in sealing and sliding connection with 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 and the two inner walls of the oil cylinder body in the axial direction, and the spacer can divide the second end cavity into a liquid cavity and a gas cavity.
Preferably, the hydraulic oil cylinder further comprises a first baffle ring, a second baffle ring and at least one guide rod, wherein the first baffle ring and the second baffle ring are arranged in the inner cavity of the oil cylinder body, one end of the first baffle ring is abutted and sealed with one axial inner wall of the oil cylinder body, the other end of the first baffle ring is abutted and sealed with one axial end of the first sleeve away from the second sleeve, one end of the second baffle ring is abutted and sealed with the other axial inner wall of the oil cylinder body, the other end of the second baffle ring is abutted with one axial end of the second sleeve away from the first sleeve, the two axial inner walls of the oil cylinder body can clamp the first sleeve and the second sleeve through the first baffle ring and the second baffle ring, a first through hole is arranged in the center of the first baffle ring, a rod body is sleeved in the first through hole, and a gap is reserved between the inner wall of the first through hole and the rod body; the first baffle ring, the first piston, the second piston and the second baffle ring are respectively provided with at least one guide hole, each guide rod can sequentially penetrate through one guide hole of the first baffle ring, one guide hole of the first piston, one guide hole of the second piston and one guide hole of the second baffle ring, two ends of each guide rod are respectively abutted with two inner walls in the axial direction of the oil cylinder body, and the first piston and the second piston are respectively connected to each guide rod in a sliding manner.
Preferably, the hydraulic oil cylinder further comprises at least one limiting component, wherein at least one first limiting groove is formed in the outer walls of the first baffle ring and the second baffle ring, at least one second limiting groove is formed in the inner wall of the oil cylinder body, each limiting component is arranged between each first limiting groove and each second limiting groove, part of the side wall of each limiting component is in contact with the inner wall of each first limiting groove, part of the side wall of each limiting component is in contact with the inner wall of each second limiting groove, one end of each limiting component is in contact with the bottom wall of each second limiting groove, and the other end of each limiting component is in contact with the inner wall of the length direction of the oil cylinder body.
Compared with the prior art, the invention has the following technical effects:
the invention provides a damping-adjustable special-shaped gap damper, which comprises an oil cylinder body, a piston rod assembly, a piston assembly and a first sleeve, wherein the outer wall of the piston assembly is in sealing and sliding connection with the inner wall of the first sleeve; when the piston assembly is driven by external vibration, damping medium flows from a cavity close to the output end of the piston assembly to a cavity far away from the output end of the piston assembly, otherwise, when the piston assembly is driven by external vibration to retract inwards, the damping medium flows from a cavity far away from the output end of the piston assembly to a cavity close to the output end of the piston assembly; since the dimension of the notch in the axial direction perpendicular to the first sleeve is gradually reduced from the middle plane of the notch to the two ends of the notch parallel to the axial direction of the first sleeve, when the piston moves from the initial position to the two ends far away from the initial position, the dimension of the damping channel between the outer wall of the piston assembly and the inner wall of the cylinder body is gradually reduced, namely the opening degree of the damping hole of the damper is gradually reduced, and the damping force is gradually increased. The damper provided by the invention can be passively adjusted along with the change of the vibration amplitude of the mechanical vibration system, namely, when the vibration is increased, the opening degree of the damping hole of the damper is reduced, the damping force is increased, and the damper has a good vibration reduction effect; meanwhile, compared with a mode of adjusting damping force by using a displacement sensor, the damper does not need to increase the cost and add the displacement sensor and a corresponding controller, does not need to keep an electrifying device in the use process, omits the development and maintenance work of the complicated displacement sensor and the controller, and saves the cost.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of a damping-adjustable special-shaped gap damper according to the present invention;
FIG. 2 is a cross-sectional view of a damper with adjustable damping for a shaped gap according to embodiments 2-3;
FIG. 3 is an exploded view of a damper with a damper adjustable for a special-shaped gap according to embodiment 2-3;
FIG. 4 is an exploded view of the cylinder, first stop collar, stop member and guide rod provided by the present invention;
FIG. 5 is a schematic view of a notch according to the present invention;
FIG. 6 is a graph of notch width as a function of example 3;
FIG. 7 is a graph of damping coefficient as a function of piston displacement in example 3;
FIG. 8 is a plot of equivalent damping coefficient as a function of piston displacement for example 3;
FIG. 9 is a radial cross-sectional view of the first sleeve in example 3;
fig. 10 is a schematic structural view of a first sleeve in embodiment 3;
in the figure: 100. a special-shaped gap damper with adjustable damping; 1. an oil cylinder body; 101. a first end cavity; 102. a second end cavity; 103. a middle cavity; 104. a liquid chamber; 105. a gas cavity; 106. an end cap; 107. a cylinder; 2. a piston rod assembly; 201. a rod body; 202. a screw rod; 203. a first thread segment; 204. a second thread segment; 3. a piston assembly; 301. a first piston; 302. a second piston; 4. a first sleeve; 401. a notch; 402. a first surface; 403. a second surface; 404. a notched arc; 405. a sector; 406. a first inclined plane; 407. a second inclined plane; 408. a middle cambered surface; 409. a third surface; 5. a second sleeve; 6. a spacer; 7. a first baffle ring; 701. a first through hole; 8. a second baffle ring; 9. a guide rod; 10. a guide hole; 11. a limiting member; 12. a first limit groove; 13. the second limit groove; 14. a seal ring; 15. and (5) hanging rings.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The invention aims to provide a special-shaped gap damper with adjustable damping, which solves the problems in the prior art, and has better damping effect and lower cost.
In order that the above-recited objects, features and advantages of the present invention will become more readily apparent, a more particular description of the invention will be rendered by reference to the appended drawings and appended detailed description.
Example 1
As shown in fig. 1, the invention provides a special-shaped gap damper 100 with adjustable damping, which comprises an oil cylinder body 1, a piston rod assembly 2, a piston assembly 3 and a first sleeve 4, wherein a notch 401 arranged along the axis direction parallel to the first sleeve 4 is arranged on the side wall of the first sleeve 4, the notch 401 penetrates through the first sleeve 4 along the axis direction parallel to the first sleeve 4, the notch 401 is provided with a middle plane in the axis direction parallel to the first sleeve 4, the size of the notch 401 in the axis direction perpendicular to the first sleeve 4 is gradually reduced from the middle plane of the notch 401 to two ends of the notch 401 in the axis direction parallel to the first sleeve 4, the piston assembly 3 is sleeved outside the piston rod assembly 2 and is in sealing and fixed connection with the piston rod assembly 2, the piston assembly 3 is symmetrically arranged about the middle plane of the notch 401 when the piston rod assembly 2 does not extend and retract, the outer wall of the piston assembly 3 is in sealing and sliding connection with the inner wall of the first sleeve 4, the outer wall of the first sleeve 4 is in sealing connection with part of the inner wall of the oil cylinder body 1, one end of the piston assembly 2 is sleeved in the first sleeve 4, the other end of the piston assembly 2 is in the cylinder body 2 is in sliding connection with the other end of the piston assembly 1, and the piston assembly 2 is capable of separating at least two inner cavities 1.
Because the outer wall of the piston assembly 3 is in sealing and sliding connection with the inner wall of the first sleeve 4, the outer wall of the first sleeve 4 is in sealing connection with part of the inner wall of the oil cylinder body 1, damping medium in the plurality of cavities can only flow through a damping channel formed by the outer wall of the piston assembly 3 and the inner wall of the oil cylinder body 1 at the notch 401, namely the channel is equivalent to a 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, when the piston rod assembly 2 is driven by external vibration to extend outwards, damping medium flows from a cavity close to the output end of the piston rod assembly 2 to a cavity far away from the output end of the piston rod assembly 2, otherwise, when the piston rod assembly 2 is driven by external vibration to retract inwards, damping medium flows from a cavity far away from the output end of the piston rod assembly 2 to a cavity close to the output end of the piston rod assembly 2; since the dimension of the notch 401 in the direction perpendicular to the axis of the first sleeve 4 is gradually reduced from the middle plane of the notch 401 to both ends of the notch 401 in the direction parallel to the axis of the first sleeve 4, a damper having a gap of different natures (notch) is formed; when the piston assembly 3 moves from the initial position to the two ends far 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 oil cylinder body 1 is gradually reduced, namely the opening degree of the damping hole of the damping-adjustable special-shaped gap damper 100 is gradually reduced, and the damping force is gradually increased. The special-shaped gap damper 100 with adjustable damping can be passively adjusted along with the change of the vibration amplitude of a mechanical vibration system, namely when the vibration amplitude is increased, the opening degree of a damping hole of the special-shaped gap damper 100 with adjustable damping is reduced, the damping force is increased, and the special-shaped gap damper has a good vibration reduction effect; meanwhile, compared with the mode of adjusting damping force by using a displacement sensor, the damping-adjustable special-shaped gap damper 100 does not need to increase the cost and add the displacement sensor and a corresponding controller, does not need to keep an electrifying device in the use process, saves the development and maintenance work of the complicated displacement sensor and the controller, and saves the cost.
The piston assembly 3 comprises a piston body which is arranged symmetrically with respect to the median plane of the notch 401 when the piston rod assembly 2 is not being extended or retracted.
Example 2
The present 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:
as shown in fig. 2-3, the piston assembly 3 includes a first piston 301 and a second piston 302, the first piston 301 and the second piston 302 are both sleeved outside the piston rod assembly 2 and are in sealing and fixed connection with the piston rod assembly 2, when the piston rod assembly 2 is not in extension and retraction, the first piston 301 and the second piston 302 are symmetrically arranged about a middle plane of the notch 401, an outer wall of the first piston 301 and an outer wall of the second piston 302 are both in sealing and sliding connection with an inner wall of the first sleeve 4, the first piston 301 and the second piston 302 can divide an inner cavity of the cylinder body 1 into a first end cavity 101, a second end cavity 102 and a middle cavity 103, a first damping channel is formed between the outer wall of the first piston 301 and the inner wall of the 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 cylinder body 1 at the notch 401. In the initial state, the first piston 301 and the second piston 302 are respectively located at two ends of the center of the notch 401, when the piston rod assembly 2 is driven by external vibration to extend outwards, damping medium in the first end cavity 101 is compressed and flows to the middle cavity 103, the pressure of the middle cavity 103 is increased, the damping medium in the middle cavity 103 flows to the second end cavity 102, namely, the first liquid channel and the second liquid channel are equivalent to damping holes of the damper, damping force is generated when the damping medium flows through the damping holes, and the smaller the damping holes are, the larger the damping force is; by reasonably setting the reduction degree of the width of the notch 401 from the middle to the two ends, the total opening degree of the first liquid channel and the second liquid channel can be reduced, namely the total opening degree of the damping hole of the damper is reduced, so that the damping force is increased when the damping medium flows through the first liquid channel and the second liquid channel; similarly, when the piston rod assembly 2 is retracted inwards under the drive of external vibration, the opening of the first liquid channel is increased, the opening of the second liquid channel is reduced, and as shown by calculation, the total opening of the first liquid channel and the second liquid channel is reduced, and the damping force is increased when the damping medium flows through the first liquid channel and the second liquid channel. The special-shaped gap damper 100 with adjustable damping can be passively adjusted along with the change of the vibration amplitude of a mechanical vibration system, namely when the vibration is increased, the total opening of a damping hole of the special-shaped gap damper 100 with adjustable damping is reduced, the damping force is increased, and the special-shaped gap damper has a good vibration reduction effect.
As shown in fig. 2-3, the piston rod assembly 2 includes a rod 201 and a screw rod 202, one end of the rod 201 is slidably connected with the cylinder body 1, preferably, a sealing ring 14 is disposed between an outer wall of the rod 201 and an inner wall of the cylinder body 1, the other end of the rod 201 is fixedly connected, preferably threaded, with one end of the screw rod 202, the other end of the screw rod 202 has a first threaded section 203 and a second threaded section 204, the threads of the first threaded section 203 are opposite to the threads of the second threaded section 204, a first piston 301 is sleeved outside the first threaded section 203 and is in sealing and threaded connection with the first threaded section 203, and a second piston 302 is sleeved outside the second threaded section 204 and is in sealing and threaded connection with the second threaded section 204. Through rotating body of rod 201, can drive lead screw 202 and rotate to make first piston 301 and second piston 302 follow the direction motion that is close to each other or deviate from each other, because the width of breach 401 reduces gradually to both ends from the centre, through adjusting the position of first piston 301 and second piston 302, can adjust the aperture of first liquid passage and second liquid passage, and then realize the regulation to the damping force of attenuator, 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 are both reduced relative to the initial opening degrees, and when the rod 201 is extended or retracted by the same distance outward relative to the opening degrees of the first liquid channel and the second liquid channel which are not adjusted, the total opening degrees of the first liquid channel and the second liquid channel are reduced, and the corresponding damping forces are increased; conversely, when the first piston 301 and the second piston 302 move in directions approaching each other, the opening degrees of the first liquid passage and the second liquid passage are both increased with respect to the initial opening degrees, and when the rod 201 is extended or retracted by the same distance outward with respect to the opening degrees of the first liquid passage and the second liquid passage which are not adjusted, the total opening degrees of the first liquid passage and the second liquid passage are increased, and the corresponding damping forces are reduced.
As shown in fig. 5, a first surface 402 and a second surface 403 that meet both 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 a first axial section, and the distance from the first surface 402 and/or the second surface 403 to the first axial section gradually decreases from the middle plane of the notch 401 to both ends of the notch 401 parallel to the axial direction of the first sleeve 4, so that the width of the notch 401 gradually decreases from the middle to both ends.
As a preferred embodiment, when the vibration amplitude of the vibration to be suppressed is the same on both sides of the initial position, the first surface 402 and the second surface 403 are symmetrically disposed about the middle plane of the notch 401 when the piston rod assembly 2 is not being extended and contracted.
As shown in fig. 2-3, the damping-adjustable special-shaped gap damper 100 provided by the invention further comprises a second sleeve 5 and a spacer 6, wherein the second sleeve 5 is arranged in the inner cavity of the oil cylinder body 1, one end of the second sleeve 5 is abutted against one end of the first sleeve 4, which is far away from the rod body 201, the other end of the second sleeve 5 is abutted against one inner wall of the oil cylinder body 1 in the axial direction, the other end of the first sleeve 4 is abutted against the other inner wall of the oil cylinder body 1 in the axial direction, the outer wall of the spacer 6 is in sealing and sliding connection with the inner wall of the second sleeve 5, an inner cavity of the oil cylinder body 1 is formed among the inner wall of the first sleeve 4, the inner wall of the second sleeve 5 and the two inner walls of the oil cylinder body 1 in the axial direction, and the spacer 6 can separate the second end cavity 102 into a liquid cavity 104 and a gas cavity 105. The gas chamber 105 is filled with gas, and when the rod 201 is retracted inward, the gas is compressed, the pressure in the gas chamber 105 increases, and the gas is preferably nitrogen gas, which has an auxiliary shock absorbing effect.
As shown in fig. 2-4, the hydraulic oil cylinder further comprises a first baffle ring 7, a second baffle ring 8 and at least one guide rod 9, wherein the first baffle ring 7 and the second baffle ring 8 are arranged in the inner cavity of the oil cylinder body 1, preferably, the outer wall of the first baffle ring 7 and the outer wall of the second baffle ring 8 are both in contact with the inner wall of the oil cylinder body 1, one end of the first baffle ring 7 is abutted and sealed with one axial inner wall of the oil cylinder body 1, the other end of the first baffle ring 7 is abutted and sealed with one axial end of the first sleeve 4, which is far away from the second sleeve 5, one axial end of the second baffle ring 8 is abutted and sealed with one axial end of the second sleeve 5, which is far away from the first sleeve 4, the two axial inner walls of the oil cylinder body 1 can clamp the first sleeve 4 and the second sleeve 5 through the first baffle ring 7 and the second baffle ring 8, thereby 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 formed in the center of the first baffle ring 7, a rod body 201 is sleeved in the first through hole 701 of the first baffle ring 7, and a gap is reserved between the inner wall of the first through hole 701 and the rod body 201; the first baffle ring 7, the first piston 301, the second piston 302 and the second baffle ring 8 are respectively provided with at least one guide hole 10, each guide rod 9 can sequentially pass through one guide hole 10 of the first baffle ring 7, one guide hole 10 of the first piston 301, one guide hole 10 of the second piston 302 and one guide hole 10 of the second baffle ring 8, two ends of each guide rod 9 are respectively abutted with two inner walls in the axial direction of the oil cylinder body 1, and the first piston 301 and the second piston 302 are respectively connected onto each guide rod 9 in a sliding manner. As a preferred embodiment, a sealing ring 14 is arranged between the first baffle ring 7 and the oil cylinder body 1, and a sealing ring 14 is arranged between the second baffle ring 8 and the oil cylinder body 1; the axes of the holes in the first baffle ring 7, the first piston 301, the second piston 302 and the second baffle 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, so that the running stability is ensured.
As shown in fig. 4, the damping-adjustable special-shaped gap damper 100 provided by the invention further comprises at least one limiting component 11, preferably two limiting components 11, at least one first limiting groove 12 is arranged on the outer walls of the first baffle ring 7 and the second baffle ring 8, at least one second limiting groove 13 is arranged on the inner wall of the cylinder body 1, each limiting component 11 is arranged between each first limiting groove 12 and each second limiting groove 13, part of the side wall of each limiting component 11 is in contact with the inner side wall of each first limiting groove 12, part of the side wall of each limiting component 11 is in contact with the inner side wall of each second limiting groove 13, one end of each limiting component 11 is in contact with the bottom wall of each second limiting groove 13, and the other end of each limiting component 11 is in contact with the inner wall of the cylinder body 1 in the length direction. The limiting component 11 can limit the rotation of the first baffle ring 7 and the second baffle ring 8 around the axial direction of the limiting component, reduce or avoid the movement of the guide rod 9 caused by the rotation of the first baffle ring 7 and the second baffle ring 8, and ensure the running stability.
As a preferred embodiment, the cylinder body 1 includes two end caps 106 and a cylinder body 107, the two end caps 106 are respectively fixedly connected to two ends of the cylinder body 107, a sealing ring 14 is disposed between the inner walls of the two end caps 106 and the first baffle ring 7 and the second baffle ring 8, and two ends of the guide rod 9 are respectively abutted to the inner walls of the two end caps 106. One end of the rod 201, which is far away from the piston assembly 3, is fixedly connected with a lifting ring 15, and the end cover 106, which is far away from the rod 201, is also fixedly connected with the lifting ring 15.
Other matters in this embodiment are the same as those in embodiment 1.
Example 3
The present embodiment provides a damping-adjustable special-shaped gap damper 100, which is different from the damping-adjustable special-shaped gap damper 100 in embodiment 2 in that:
as shown in fig. 5, a portion of the intermediate cylindrical surface in the thickness direction of the first sleeve 4 corresponding to the notch 401 is a third surface 409, a length of an intersection line of the third surface 409 and a plane perpendicular to the axis of the cylinder body 1 is a 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:
Figure SMS_2
where n and m are notch parameters, n=0.2 to 0.3, m=8 to 12, and x is the distance from any point on the centerline of the second surface 403 parallel to the axis of the first sleeve 4 to the midpoint of the centerline of the second surface 403 parallel to the axis of the first sleeve 4. The width of the notch 401 is plotted as a function of the width as shown in fig. 6.
The method for calculating the damping coefficient of the preferred embodiment is as follows:
1. when the length of the first piston 301 or the second piston 302 is dx, the calculation method of the pressure difference across the first piston 301 or the second piston 302 is as follows (hereinafter, the first piston 301 is described as a representative):
1.1, the intersection line of the third surface 409 and the plane perpendicular to the axis of the cylinder body 1 is a notch arc line 404, the notch arc line 404 corresponds to a fan-shaped surface 405, the center of the fan-shaped surface 405 is on the axis of the first sleeve 4, a micro-fan-shaped surface 405 with an angle dθ is taken on the fan-shaped surface 405, and the flow rate of damping medium allowed to pass through by the dθ micro-fan-shaped surface 405 is as follows:
Figure SMS_3
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 notched arc 404 of the first sleeve 4.
The pressure difference across the first piston 301 of length dx is 1.2:
Figure SMS_4
wherein Q is the flow rate of the first damping channel.
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:
defining the position x of the axial middle plane of the first piston 301 Piston The positions of the two bottom surfaces of the two ends of the first piston 301 are x Piston +H and x Piston -H. Integrating the formula (3) to obtain a pressure difference calculation formula of the two bottom surfaces of the first piston 301 is:
Figure SMS_5
defining a distance between the axial center plane of the first piston 301 and the axial center plane of the second piston 302 as 2b, and the axial midpoint of the first piston 301 and the second piston 302 is positioned as x 0 (the position x of the first piston 301 and the second piston 302 with the midpoint of the center line of the second surface 403 parallel to the axis of the first sleeve 4 being the zero point of the x coordinate axis) Piston 1 、x Piston 2 Respectively x 0 +b、x 0 B, x is 0 Substitution of +b into equation (4) yields a pressure difference across the first piston 301 of:
Figure SMS_6
similarly, x is 0 Substituting b into equation (4) yields a pressure difference across the second piston 302 of:
Figure SMS_7
adding equation (5) and equation (6) yields a 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 of:
Figure SMS_8
3. the method for calculating the damping coefficient of the damping-adjustable special-shaped gap damper 100 is as follows:
the damping force of the damping-adjustable special-shaped gap damper 100 is:
Figure SMS_9
wherein q=sv 0 ，v 0 Substituting the movement speed of the piston rod assembly 2 into formula (8) yields:
Figure SMS_10
wherein S is the area of the end face of the piston,
Figure SMS_11
F＝cv 0 substituting it into equation (9) yields the damping coefficient c and the position x of the piston rod assembly 2 0 The relation of (2) is:
Figure SMS_12
as can be seen from the formula (9), the greater the zero point of the piston rod assembly 2 deviated from the x coordinate axis, the greater the damping coefficient of the damping-adjustable special-shaped gap damper 100, that is, the greater the distance the piston rod assembly 2 extends outward or the greater the distance the piston retracts into the cylinder body 1, the greater the damping coefficient of the damping-adjustable special-shaped gap damper 100. c and x 0 As shown in fig. 7, the damping coefficient exhibits a parabolic shape as a function of displacement of the piston rod assembly 2.
From equation (9), at x 0 At a certain time, the larger b is, the larger the damping coefficient is, i.e., the larger the distance between the two pistons is, the larger the damping coefficient is when the piston rod is extended or retracted the same distance.
4. The method for calculating the equivalent damping coefficient of the damping-adjustable special-shaped gap damper 100 when the piston rod assembly 2 vibrates in a sinusoidal manner is as follows:
x when the piston rod assembly 2 vibrates in a sinusoidal manner 0 ＝Asin(2πft 0 )，v 0 ＝A·2πfcos(2πft 0 ) Wherein A is the vibration amplitude and f is the vibration frequency. Within half a cycle of piston oscillation, i.e.
Figure SMS_13
x 0 ∈[-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:
Figure SMS_14
since the damper dissipates vibration energy by damping, the damping force F in equation (9) is integrated over displacement [ -A, A ], the dissipated energy being:
Figure SMS_15
and for a damper with a constant damping coefficient, the damping force is:
Figure SMS_16
the energy dissipated by a damper with a constant damping coefficient is:
Figure SMS_17
can be made of W 1 ＝W 2 The relationship of the equivalent damping coefficient of the variable damping adjustable special-shaped gap damper 100 along with the vibration amplitude is obtained as follows:
Figure SMS_18
as can be seen from the formula (12), when the amplitude a is larger, the equivalent damping coefficient of the damping-adjustable shaped gap damper 100 is larger, that is, when the maximum distance of the piston rod assembly 2 extending outwards is larger or the maximum distance of the piston retracting into the cylinder body 1 is larger, the equivalent damping coefficient of the damping-adjustable shaped gap damper 100 is larger, so that the damping of the damping-adjustable shaped gap damper 100 is larger when the vibration amplitude is large and the frequency is low, and the requirement that the damping of the damping-adjustable shaped gap damper 100 is smaller when the vibration amplitude is small and the frequency is high can be realized. The curve of the equivalent damping coefficient as a function of vibration amplitude is shown in fig. 8, and the equivalent damping coefficient exhibits a parabolic shape as a function of vibration amplitude.
As can be seen from the equation (12), the larger the amplitude a is, the larger the damping coefficient is, i.e., the larger the distance between the two pistons is, the larger the damping coefficient is.
It should be noted that, the first surface 402 in this embodiment is not limited to a curved surface, and may be in other forms capable of satisfying that the damping coefficient increases with increasing amplitude and the damping coefficient decreases with decreasing amplitude: as shown in fig. 10, 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 symmetrical with respect to the intermediate plane of the notch 401, a distance from an end of the first inclined plane 406 near the second inclined plane 407 to the first axial section is greater than a distance from an end of the other end of the first inclined plane 406 to the first axial section, a distance from an end of the second inclined plane 407 near the first inclined plane 406 to the first axial section is greater than a distance from an end of the other end of the second inclined plane 407 to the first axial section, the intermediate arc surface 408 is a plane, and a notch size y (x) corresponding to the intermediate arc surface 408 varies less in the axial direction along the first sleeve 4. The length of the middle cambered surface 408 is determined according to the vibration amplitude, preferably, the first piston 301 is located at the transition position of the first inclined plane 406 and the middle cambered surface 408, the second piston 302 is located at the transition position of the second inclined plane 407 and the middle cambered surface 408, so that in the vibration period, one piston moves in the first inclined plane 406 or the second inclined plane 407 corresponding to the first sleeve section, the other piston moves in the middle cambered surface 408 corresponding to the first sleeve section, and further, in the process of moving the other piston in the middle cambered surface 408 along the axis of the first sleeve 4, the piston damping change is small or even negligible. Therefore, when the piston assembly 3 moves upwards, the gap corresponding to the first piston 301 is gradually reduced, the gap corresponding to the second piston 302 is not changed greatly, and the overall damping is greatly affected by the first piston 301, namely, the overall damping is increased; similarly, when the piston assembly 3 moves downward, the overall damping is greatly affected by the second piston 302, i.e., the overall damping increases. The inclination angles of the first inclined plane 406 and the second inclined plane 407 and the radius of the middle cambered surface 408 may be determined by calculation and/or experiment according to prior experience.
The other portions in this embodiment are the same as those in embodiment 2.
The principles and embodiments of the present invention have been described in detail with reference to specific examples, which are provided to facilitate understanding of the method and core ideas of the present invention; also, it is within the scope of the present invention to be modified by those of ordinary skill in the art in light of the present teachings. In view of the foregoing, this description should not be construed as limiting the invention.

Claims (9)

1. A damping-adjustable special-shaped gap damper is characterized in that: including hydro-cylinder body, piston rod subassembly, piston subassembly and first sleeve, be equipped with on the lateral wall of first sleeve along being on a parallel with the breach that first telescopic axis direction set up, just the breach runs through along being on a parallel with first telescopic axis direction first sleeve, the breach is on a parallel with first telescopic axis direction has the mid-plane, the breach is perpendicular to in the size on the first telescopic axis direction by the mid-plane of breach to the breach is on a parallel with first telescopic axis direction's both ends reduce gradually, the piston subassembly cover is established outside the piston rod subassembly and with piston rod subassembly is sealed and fixed connection, the piston subassembly is with when not carrying out the flexible breach the mid-plane symmetry sets up, the outer wall of piston subassembly with the sealed and sliding connection of first telescopic inner wall, the outer wall of first telescopic with the partial inner wall sealing connection of hydro-cylinder body, the one end cover of piston rod subassembly is established in the first telescopic axis direction by the mid-plane of breach is parallel with the both ends of first telescopic axis direction of breach, the piston rod subassembly cover is established the piston rod subassembly other end with the hydro-cylinder body sliding connection can be two at least the chamber of cylinder subassembly.
2. The damping-adjustable profiled gap damper as claimed in claim 1 wherein: the piston assembly comprises a piston body, and the piston body is symmetrically arranged about the middle plane of the notch when the piston rod assembly is not in telescopic operation.
3. The damping-adjustable profiled gap damper as claimed in claim 1 wherein: the piston assembly comprises a first piston and a second piston, the first piston and the second piston are sleeved outside the piston rod assembly and are in sealing and fixed connection with the piston rod assembly, the first piston and the second piston are symmetrically arranged relative to the middle plane of the notch when the piston rod assembly is not in extension, the outer wall of the first piston and the outer wall of the second piston are in sealing and sliding connection with the inner wall of the first sleeve, and 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. A damping-adjustable profiled gap damper as claimed in claim 3, characterized in that: the piston rod assembly comprises a rod body and a screw rod, one end of the rod body is in sliding connection with the oil cylinder body, the other end of the rod body is fixedly connected with one end of the screw rod, a first threaded section and a second threaded section are arranged at the other end of the screw rod, threads of the first threaded section are opposite to threads of the second threaded section in rotation direction, the first piston is sleeved outside the first threaded section and is in sealing and threaded connection with the first threaded section, and the second piston is sleeved outside the second threaded section and is in sealing and threaded connection with the second threaded section.
5. A damping-adjustable profiled gap damper as claimed in claim 3, characterized in that: the gap of the first sleeve is provided with a first surface and a second surface which are connected with the inner side wall and the outer side wall of the first sleeve, the axial section of the first sleeve between the first surface and the second surface is a first axial section, and the distance from the first surface and/or the second surface to the first axial section is gradually reduced from the middle plane of the gap to the two ends of the gap parallel to the axial direction of the first sleeve.
6. The damping-adjustable profiled gap damper as claimed in claim 5 wherein: the middle cylindrical surface in the thickness direction of the first sleeve corresponds to the notch, the third surface is a third surface, the length of an intersection line of the third surface and a plane perpendicular to the axis of the 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 as follows:
Figure FDA0004150962630000021
where n and m are gap parameters, n=0.2 to 0.3, m=8 to 12, y (x) is the width of the gap, and x is the distance from any point on the centerline of the second surface parallel to the axis of the first sleeve 4 to the midpoint of the centerline of the second surface parallel to the axis of the first sleeve 4.
7. The damping-adjustable profiled gap damper as claimed in claim 4 wherein: still include second sleeve and isolation pad, the second sleeve set up in the inner chamber of hydro-cylinder body, the one end of second sleeve with first sleeve is kept away from the one end butt of the body of rod, the telescopic other end of second with the axial inner wall butt of hydro-cylinder body, the telescopic other end of first with the axial other inner wall butt of hydro-cylinder body, the outer wall of isolation pad with the telescopic inner wall of second is sealed and sliding connection, the telescopic inner wall of first second with be formed with between two axial inner walls of hydro-cylinder body the inner chamber of hydro-cylinder body, the isolation pad can with second tip cavity is separated into liquid cavity and gas cavity.
8. The damping-adjustable profiled gap damper as claimed in claim 7 wherein: the hydraulic oil cylinder comprises an oil cylinder body, and is characterized by further comprising a first baffle ring, a second baffle ring and at least one guide rod, wherein the first baffle ring and the second baffle ring are arranged in an inner cavity of the oil cylinder body, one end of the first baffle ring is abutted against and sealed with one axial inner wall of the oil cylinder body, the other end of the first baffle ring is abutted against and sealed with one axial end of the first sleeve away from the second sleeve, one end of the second baffle ring is abutted against and sealed with the other axial inner wall of the oil cylinder body, the other end of the second baffle ring is abutted against one axial end of the second sleeve away from the first sleeve, the two axial inner walls of the oil cylinder body can clamp the first sleeve and the second sleeve through the first baffle ring, a first through hole is formed in the center of the first baffle ring, a rod body is sleeved in the first through hole, and a gap is reserved between the inner wall of the first through hole and the rod body; the first baffle ring, the first piston, the second piston and the second baffle ring are respectively provided with at least one guide hole, each guide rod can sequentially penetrate through one guide hole of the first baffle ring, one guide hole of the first piston, one guide hole of the second piston and one guide hole of the second baffle ring, two ends of each guide rod are respectively abutted with two inner walls in the axial direction of the oil cylinder body, and the first piston and the second piston are respectively connected to each guide rod in a sliding manner.
9. The damping-adjustable profiled gap damper as claimed in claim 8 wherein: the oil cylinder comprises an oil cylinder body, and is characterized by further comprising at least one limiting component, wherein at least one first limiting groove is formed in the outer walls of the first baffle ring and the second baffle ring, at least one second limiting groove is formed in the inner wall of the oil cylinder body, each limiting component is arranged between each first limiting groove and each second limiting groove, part of the side wall of each limiting component is in contact with the inner wall of each first limiting groove, part of the side wall of each limiting component is in contact with the inner wall of each second limiting groove, one end of each limiting component is in contact with the bottom wall of each second limiting groove, and the other end of each limiting component is in contact with the inner wall of the length direction of the oil cylinder body.
CN202310316376.2A 2023-03-28 2023-03-28 Special-shaped gap damper with adjustable damping Pending CN116379094A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116950267A (en) * 2023-09-21 2023-10-27 江苏安之恒振控科技有限公司 Damper for remote control and test system thereof

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116950267A (en) * 2023-09-21 2023-10-27 江苏安之恒振控科技有限公司 Damper for remote control and test system thereof
CN116950267B (en) * 2023-09-21 2023-12-08 江苏安之恒振控科技有限公司 Damper for remote control and test system thereof

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