Solid-liquid coupling type inerter damper

Abstract

The invention discloses a solid-liquid coupling type inerter damper, and relates to the field of vibration reduction equipment, the solid-liquid coupling type inerter damper comprises a moving assembly, the moving assembly comprises a damping cylinder barrel with two cavities and an axial piston rod with one end entering one of the cavities, and a variable-section guide rod embedded into the end of the axial piston rod is arranged in the damping cylinder barrel; a sealing piston sleeved outside the end part of the axial piston rod is arranged on the variable-section guide rod; the vibration reduction assembly comprises a first medium containing cavity located in the embedded position of the axial piston rod and the variable-section guide rod, a second medium containing cavity formed in the other cavity and communicated with the first medium containing cavity, and a third medium containing cavity formed between the outer wall of the axial piston rod and the inner wall of the damping cylinder barrel and communicated with the second medium containing cavity. The inertial unit which enables the viscous fluid in the second medium containing cavity to generate the solid-liquid coupling effect by means of rotation of the inertial unit is arranged in the second medium containing cavity, the inertial effect of the damper is obvious, and compared with an existing inertial damper, the inertial damper has the better vibration reduction effect.

Description

Technical Field

[0001] The invention relates to the field of vibration reduction equipment, and in particular to a solid-liquid coupling inertial capacity damper. Background Art

[0002] As a common energy-absorbing and vibration-reducing device, dampers are widely used in various engineering fields. Among them, the inertial capacity damper introduces an inertial capacity element compared to the traditional viscous damper, which can generate a large inertial force with low mass under the action of power, thereby achieving a good vibration reduction effect.

[0003] Common inertia dampers include mechanical inertia and hydraulic inertia. Mechanical inertia is achieved by designing a mechanical inertia device based on a rack and pinion mechanism and a ball screw mechanism inside the structure, and using the corresponding mechanical structure for mechanical transmission, so that the flywheel rotates to generate inertia force. However, this type of inertia has backlash or return clearance during the meshing process between the rack and the gear or the ball and the screw. This gap causes the adjacent teeth to be unable to effectively contact during the rotation process, thus generating vibration and mechanical wear, resulting in a loss of damping force. The hydraulic inertia requires a long threaded tube to be set axially, which is complex and unsightly, and has limited inertia effect. Summary of the invention

[0004] The present application provides a solid-liquid coupling inertial capacity damper, which can solve the technical problems in the prior art that the mechanical inertial capacity damper suffers from loss of damping force due to vibration and mechanical wear during operation, while the hydraulic inertial capacity damper has a complex structure and an unclear inertia effect.

[0005] The embodiment of the present application provides a solid-liquid coupling inertia damper, comprising:

[0006] A motion assembly, the motion assembly comprising a damping cylinder having two parallel chambers and an axial piston rod with one end entering one of the chambers, a variable section guide rod embedded in the end of the axial piston rod is provided in the damping cylinder, and a sealing piston sleeved on the outer periphery of the end of the axial piston rod is provided on the variable section guide rod;

[0007] A vibration reduction assembly located in the damping cylinder, the vibration reduction assembly includes a first medium receiving chamber formed at the joint of the axial piston rod and the variable guide rod, a second medium receiving chamber formed in another chamber and connected to the first medium receiving chamber, and a third medium receiving chamber formed between the outer wall of the axial piston rod and the inner wall of the damping cylinder and connected to the second medium receiving chamber, wherein the second medium receiving chamber is provided with an inertial unit which relies on its own rotation to cause the viscous fluid in the second medium receiving chamber to produce a solid-liquid coupling effect.

[0008] In one embodiment, the variable-section guide rod includes a partition portion that fits against the inner wall of the damping cylinder and a guide rod portion that is located on a side of the partition portion close to the axial piston rod and has a reduced diameter.

[0009] In one embodiment, an end surface of the axial piston rod entering the damping cylinder is provided with an avoidance groove which is concave inwardly facing away from the variable-section guide rod for the guide rod portion to be embedded, and the first medium accommodating chamber is formed in the avoidance groove.

[0010] In one embodiment, a first medium channel is axially provided on the variable-section guide rod for connecting the first medium accommodating chamber with the second medium accommodating chamber.

[0011] In one embodiment, a second medium channel is provided on the outer wall of the damping cylinder for connecting the second medium accommodating chamber with the third medium accommodating chamber.

[0012] In one embodiment, the damping cylinder includes a through-type cylinder body and sealing end covers located at openings at both ends of the through-type cylinder body, and one end of the axial piston rod passes through one of the sealing end covers and engages with the variable-section guide rod.

[0013] In one embodiment, a step portion is provided on a side of the sealing piston facing the axial piston rod for embedding the end of the axial piston rod.

[0014] In one embodiment, one end surface of the sealing piston facing the axial piston rod and a bottom surface of one of the sealing end covers of the axial piston rod form two inner walls of the third medium accommodating chamber.

[0015] In one embodiment, the inertial unit includes a hydraulic motor located in the second medium receiving chamber and a flywheel located on a rotor of the hydraulic motor.

[0016] In one embodiment, the output force at both ends of the solid-liquid coupling inertial capacity damper is composed of two parts: the viscous damping force generated by the reciprocating motion of the viscous fluid and the inertial force provided by the rotation of the inertial unit;

[0017] Among them, the viscous damping force is mainly provided by the pressure loss along the way caused by the reciprocating motion of the viscous fluid, the local pressure loss when the viscous fluid passes through the variable cross-section in the damping cylinder, and the pressure loss caused by the viscous fluid passing through the inertial unit. The inertial force includes the rotational inertial force caused by the rotation of the flywheel and the inertial force provided by the solid-liquid coupling effect generated thereby.

[0018] The beneficial effects brought by the technical solution provided in the embodiments of the present application include:

[0019] 1. The inertia capacity damper in the present application has three medium receiving chambers built in, so as to realize the reciprocating circulation of viscous fluid, and the circulation direction is arranged in series along the axial direction of the inertia capacity damper in the present application. Compared with other inertia capacity dampers, the structure is more compact, and thus the traditional double-rod viscous damper can be directly replaced, which is more convenient for transportation;

[0020] 2. The inertia-capacitance damper in the present application generates inertia force by rotating the inertia unit arranged in the second medium containing chamber, thereby providing a negative stiffness effect for the vibrating structure. At the same time, the inertia unit drives the viscous fluid in the second medium containing chamber to produce reciprocating motion, thereby producing a significant solid-liquid coupling effect, further amplifying the inertia force and effectively improving the energy consumption capacity of the damper. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0022] Figure 1 A cross-sectional view of a solid-liquid coupling inertial capacity damper provided in an embodiment of the present application;

[0023] Figure 2 A schematic diagram of the structural details of an axial piston rod and a variable-section guide rod in a solid-liquid coupling inertial capacity damper provided in an embodiment of the present application;

[0024] Figure 3 A schematic diagram of the structural details of a solid-liquid coupling inertial capacity damper provided in an embodiment of the present application;

[0025] Figure 4 A schematic diagram of another implementation of a solid-liquid coupled inertial capacity damper provided in an embodiment of the present application.

[0026] In the figure: 1. damping cylinder; 101. through-type cylinder body; 102. sealing end cover; 103. external connection ear; 2. axial piston rod; 201. avoidance groove; 3. variable-cut guide rod; 301. partition part; 302. guide rod part; 303. first medium channel; 4. sealing piston; 401. step part; 5. first medium accommodating chamber; 6. second medium accommodating chamber; 601. hydraulic motor; 602. flywheel; 603. flow transfer channel; 604. throttle valve; 7. third medium accommodating chamber; 8. second medium channel. DETAILED DESCRIPTION

[0027] In order to enable those skilled in the art to better understand the solution of the present application, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0028] The embodiment of the present application provides a solid-liquid coupling inertial capacity damper, which can solve the technical problems in the prior art that the mechanical inertial capacity damper has a loss of damping force due to vibration and mechanical wear during operation, and the hydraulic inertial capacity damper has a complex structure and an inertial effect is not obvious. The solid-liquid coupling inertial capacity damper in the present application includes a motion component and a vibration reduction component. The motion component is mainly used to form the basic form of the inertial capacity damper. The vibration reduction component includes several chambers formed inside the motion component. Viscous fluids are arranged in the chambers. When vibration or impact occurs externally, part of the structure in the motion component starts to move and squeeze the chamber, forcing the viscous fluid in the chamber to flow in multiple chambers in turn, generating resistance while flowing, and realizing vibration reduction operation. At the same time, based on the structural setting, while the viscous fluid flows, the vibration reduction component can also provide further inertial force for the viscous fluid, further improving the vibration reduction performance.

[0029] Specifically, Figure 1 A cross-sectional view of a solid-liquid coupling inertial capacity damper provided in an embodiment of the present application, such as Figure 1 As shown, the motion component includes a damping cylinder 1 with two parallel chambers and an axial piston rod 2 with one end entering one of the chambers. A variable-section guide rod 3 embedded in the end of the axial piston rod 2 is provided in the damping cylinder 1, and a sealing piston 4 sleeved on the outer periphery of the end of the axial piston rod 2 is provided on the variable-section guide rod 3.

[0030] One end of the axial piston rod 2 enters one of the chambers in the damping cylinder 1, and the other end of the axial piston rod 2 extends out of the damping cylinder 1, and the outer diameter of the axial piston rod 2 is smaller than the inner diameter of the damping cylinder 1. When an external force occurs, the axial piston rod 2 can generate an axial displacement in the direction of the damping cylinder 1 under the push of the external force. The variable section guide rod 3 is fixedly arranged in the damping cylinder 1, which includes two parts with different diameters, wherein the part with a smaller diameter extends laterally in the direction of the axial piston rod 2 and enters the rod body of the axial piston rod 2 located in the damping cylinder 1, so that the axial piston rod 2 can move laterally in the damping cylinder 1 along the variable section guide rod 3. At the same time, the sealing piston 4 is movably arranged on the variable section guide rod 3 and sleeved on the outer periphery of the rod body end of the axial piston rod 2 entering the damping cylinder 1. The sealing piston 4 is an annular structure and is made of a flexible material. When the axial piston rod 2 moves, it will push the sealing piston 4 to move in the damping cylinder 1 together.

[0031] The vibration damping assembly includes a first medium receiving chamber 5 formed at the joint of the axial piston rod 2 and the variable guide rod 3, a second medium receiving chamber 6 formed in another chamber and connected to the first medium receiving chamber 5, and a third medium receiving chamber 7 formed between the outer wall of the axial piston rod 2 and the inner wall of the damping cylinder 1 and connected to the second medium receiving chamber 6.

[0032] In combination with the above description, the end with a smaller diameter of the variable section guide rod 3 is embedded in the rod body of the axial piston rod 2 located in the damping cylinder 1. Therefore, in order to facilitate the entry of the variable section guide rod 3, the end surface of the axial piston rod 2 entering the damping cylinder 1 is provided with an avoidance groove 201 which is concave in the direction away from the variable section guide rod 3. Figure 2 A schematic diagram of the structural details of the axial piston rod 2 and the variable-section guide rod 3 in a solid-liquid coupling inertial capacity damper provided in an embodiment of the present application is shown in FIG. Figure 2 As shown, the end of the variable-section guide rod 3 with a smaller diameter enters the avoidance groove 201, and the first medium accommodating chamber 5 is formed in the avoidance groove 201. Three adjacent side walls of the avoidance groove 201 and the end surface of the variable-section guide rod 3 facing the avoidance groove 201 together form the four inner walls of the first medium accommodating chamber 5.

[0033] Further, in combination with the above description, the interior of the damping cylinder 1 includes two parallel chambers, one of which is provided with an axial piston rod 2, a variable guide rod 3, a sealing piston 4 and other components, and the other chamber forms a second medium receiving chamber 6. At the same time, the second medium receiving chamber 6 is connected to the first medium receiving chamber 5. When the axial piston rod 2 moves toward the direction of the damping cylinder 1, the position of the variable guide rod 3 remains stationary, the volume of the first medium receiving chamber 5 decreases, and the viscous fluid in the first medium receiving chamber 5 is squeezed into the second medium receiving chamber 6.

[0034] Further, in combination with the above description, the outer diameter of the axial piston rod 2 is smaller than the inner diameter of the damping cylinder 1. Therefore, there is a certain distance between the outer wall of the axial piston rod 2 and the inner wall of the damping cylinder 1. At the same time, since a sealing piston 4 is provided at the end of the rod body where the axial piston rod 2 enters the damping cylinder 1, based on this structural setting, two adjacent inner walls of the damping cylinder 1, part of the outer wall of the axial piston rod 2, and the end face of the sealing piston 4 facing the axial piston rod 2, together form the four inner walls of the third chamber. At the same time, the third medium receiving chamber 7 is connected to the second medium receiving chamber 6. When the viscous fluid in the first medium receiving chamber 5 is squeezed into the second medium receiving chamber 6, since the volume of the second medium receiving chamber 6 is quantitative, excess viscous fluid will flow into the third medium receiving chamber 7.

[0035] Furthermore, an inertial unit is provided in the second medium receiving chamber 6, which rotates by itself to cause the viscous fluid in the second medium receiving chamber 6 to produce a solid-liquid coupling effect. Figure 3A schematic diagram of the structural details of a solid-liquid coupling inertial capacity damper provided in an embodiment of the present application is shown in FIG. Figure 3 As shown, the inertial unit includes a hydraulic motor 601 located in the second medium containing chamber 6 and a flywheel 602 located on the rotor of the hydraulic motor 601. When the hydraulic motor 601 is started, the flywheel 602 rotates synchronously, which can effectively drive the viscous fluid in the second medium containing chamber 6 to produce reciprocating motion, thereby producing a significant solid-liquid coupling effect, which not only provides a significant inertial force, but also can provide a damping force caused by pressure loss to a certain extent. Therefore, it is realized that the damping force and the inertial force are provided simultaneously in a single mode, achieving dual use of one liquid.

[0036] Meanwhile, the inertial force is mainly determined by the mass and geometric shape of the flywheel 602, while its damping force is mainly derived from the local pressure loss in the hydraulic motor 601 and the local pressure loss in the case of viscous fluid. Therefore, by rationally designing and optimizing the structure of the flywheel 602 and the viscous fluid flow channel, the magnitude of the damping force and the inertial force can be adjusted more flexibly, thereby better meeting the requirements under different working conditions.

[0037] When the axial piston rod 2 of the inertial capacity damper in the present application moves, the viscous fluid flows through the first medium containing chamber 5, the second medium containing chamber 6 and the third medium containing chamber 7 in sequence. While the viscous fluid flows, the flywheel 602 in the inertial unit rotates, which causes the viscous fluid to produce a solid-liquid coupling effect, further providing an inertial force, that is, the output of the inertial capacity damper in the present application is composed of the damping force generated by the viscous fluid and the inertial force further provided by the inertial unit, which can provide a better vibration reduction effect.

[0038] For further information, see Figure 2 The variable-section guide rod 3 includes a partition portion 301 that fits the inner wall of the damping cylinder 1 and a guide rod portion 302 that is located on a side of the partition portion 301 close to the axial piston rod 2 and has a reduced diameter. The partition portion 301 and the guide rod portion 302 are both cylindrical. The outer diameter of the partition portion 301 is equal to the inner diameter of the damping cylinder 1 and fits tightly against the inner wall of the damping cylinder 1, so as to divide the internal space of the damping cylinder 1 into two parallel chambers. The guide rod portion 302 has a reduced diameter and is fixedly connected to the side of the partition portion 301 facing the axial piston rod 2 to form a whole. The overall longitudinal section of the variable-section guide rod 3 is a horizontal "T" shape.

[0039] Furthermore, a first medium channel 303 is axially provided on the variable-section guide rod 3 for connecting the first medium receiving chamber 5 with the second medium receiving chamber 6. In one embodiment of the present application, the first medium channel 303 is horizontally arranged and passes through the partition portion 301 and the guide rod portion 302 at the same time. The viscous fluid flowing out of the first medium receiving chamber 5 enters the second medium receiving chamber 6 through the first medium channel 303. In one embodiment of the present application, the first medium channel 303 is a straight-through type. Based on this arrangement, the built-in straight-through first medium channel 303 can make the overall structure more compact and easy to install and transport.

[0040] Furthermore, a second medium channel 8 is provided on the outer wall of the damping cylinder 1 for connecting the second medium receiving chamber 6 with the third medium receiving chamber 7. The second medium channel 8 is external, and its two ends are respectively connected to the second medium receiving chamber 6 and the third medium receiving chamber 7. In one embodiment of the present application, one end of the second medium channel 8 connected to the second medium receiving chamber 6 can directly pass through the outer wall of the damping cylinder 1, or a channel connected to the second medium receiving chamber 6 can be opened on the variable guide rod 3, and the second medium channel 8 connects the channel. The specific setting method is not specifically limited in the present application.

[0041] As an optional embodiment, Figure 4 A schematic diagram of another implementation of a solid-liquid coupling inertia damper provided in an embodiment of the present application is shown in FIG. Figure 4 As shown, no viscous fluid is arranged in the second medium containing chamber 6, and a flow transfer channel 603 is added to the hydraulic motor 601. The outflow end of the first medium channel 303 and the inflow end of the second medium channel 8 are connected to the flow transfer channel 603 on the hydraulic motor 601. The viscous fluid in the first medium containing chamber 5 directly enters the third medium containing chamber 7 after being transferred through the hydraulic motor 601. At the same time, a throttle valve 604 is added to the inflow end of the first medium channel 303. Since the viscous fluid in the second medium containing chamber 6 is eliminated, the inertial capacity damper in the second embodiment cannot produce a solid-liquid coupling effect, so its vibration reduction ability is slightly inferior to that of the inertial capacity damper in the first embodiment. However, under this structure, it is only necessary to reasonably design the shape and mass of the flywheel 602 to accurately design the size of the damper inertia force, and by changing the model of the throttle valve 604, the size of the viscous damping force can be accurately designed.

[0042] For further information, see Figure 3 The damping cylinder 1 includes a through-type cylinder body 101 and sealing end covers 102 located at the openings at both ends of the through-type cylinder body 101. One end of the axial piston rod 2 passes through one of the sealing end covers 102 and is engaged with the variable guide rod 3. In one embodiment of the present application, internal threads are provided on the inner walls at both ends of the through-type cylinder body 101, and the two sealing end covers 102 are respectively threadedly connected to the through-type cylinder body 101.

[0043] Furthermore, as an optional embodiment, an external connection ear 103 is provided at the outer end of one of the sealing end covers 102 where the axial piston rod 2 is not provided. At the same time, an external connection ear 103 is also provided at the end of the axial piston rod 2 that does not enter the damping cylinder 1 for connecting to an external structure.

[0044] For further information, see Figure 2 A step portion 401 is provided on the side of the sealing piston 4 facing the axial piston rod 2 to embed the end of the axial piston rod 2. Combined with the above description, the axial piston rod 2 is sleeved on the outer periphery of the guide rod portion 302 in the variable-section guide rod 3. Therefore, the diameter of the sealing piston 4 is larger than the diameter of the guide rod portion 302. At this time, the step portion 401 on the sealing piston 4 can be used to simultaneously wrap the rod body end of the axial piston rod 2 entering the damping cylinder 1 and the guide rod portion 302.

[0045] One end face of the sealing piston 4 facing the axial piston rod 2 (i.e., the end face protruding from the step portion 401) and the bottom surface of one of the sealing end covers 102 with the axial piston rod 2 form two inner walls of the third medium containing chamber 7. Therefore, the four inner walls of the third medium containing chamber 7 are composed of the bottom surface of one of the sealing end covers 102 with the axial piston rod 2, the one end face of the sealing piston 4 facing the axial piston rod 2, part of the outer wall of the axial piston rod 2 and part of the inner wall of the damping cylinder 1. The outer diameter of the sealing piston 4 is not less than the inner diameter of the damping cylinder 1, so as to achieve the sealing of the third medium containing chamber 7. At the same time, the sealing piston 4 is supported by a flexible material, which can also ensure that the sealing piston 4 can be displaced in the damping cylinder 1 synchronously with the axial piston rod 2.

[0046] The inertia capacity damper in the present application is designed with three interconnected cavities for storing viscous fluid. This structural layout is conducive to providing stable inertial force. During the vibration process of the inertia capacity damper, the sum of the volumes of the first medium receiving chamber 5 and the third medium receiving chamber 7 is equal to the volume of the second medium receiving chamber 6, thereby ensuring the stability of the total volume of the viscous fluid. At the same time, through the inertial unit set in the second medium receiving chamber 6, the viscous fluid in the second medium receiving chamber 6 can be effectively driven to reciprocate, thereby generating a significant solid-liquid coupling effect and providing a significant inertial force. At the same time, the flow path of the viscous fluid is arranged along the axial direction of the inertia capacity damper in the present application, making the overall structure more compact and convenient for transportation.

[0047] Further, based on the above structure, the output force at both ends of the solid-liquid coupling inertial capacity damper in the present application is composed of two parts: the viscous damping force generated by the reciprocating motion of the viscous fluid and the inertial force provided by the rotation of the inertial unit;

[0048] Among them, the viscous damping force is mainly provided by the pressure loss along the path caused by the reciprocating motion of the viscous fluid, the local pressure loss when the viscous fluid passes through the variable cross-section in the damping cylinder 1, and the pressure loss caused by the viscous fluid passing through the inertial unit;

[0049] The viscous damping force can be calculated as:

[0050]

[0051] Among them, f d is the viscous damping force, A c is the actual action area of ​​the viscous fluid, μ is the kinematic viscosity coefficient of the viscous fluid, l 1 is the length of the first medium channel 303, d 1 A is the diameter of the first medium channel 303, p is the actual working area of ​​the sealing piston 4, is the speed of the axial piston rod 2, l 2 is the length of the second medium channel 8, d 2 is the diameter of the second medium channel 8, K is a constant related to the structural design of the hydraulic motor 601, ζ is the local pressure loss coefficient of the variable cross-section area in the damping cylinder 1, and ρ is the density of the viscous fluid. The above values ​​can be directly obtained from the manual or calculated using existing methods, and will not be elaborated here.

[0052] The inertial force includes the rotational inertial force caused by the rotation of the flywheel 602 in the inertial unit and the inertial force provided by the solid-liquid coupling effect generated thereby.

[0053] The inertia force is calculated as:

[0054]

[0055] Among them, F b is the inertia force, I is the moment of inertia of the flywheel 602, D is the rotation diameter of the flywheel 602, Δ m The additional inertia coefficient provided for the solid-liquid coupling effect, is the acceleration of the axial piston rod 2. The above values ​​can be directly obtained from the manual or calculated using existing methods, and will not be elaborated here.

[0056] The output force at both ends of the damper is:

[0057]

[0058] Among them, F 1 Output force at both ends of the damper.

[0059] Furthermore, the damper in another embodiment does not produce a solid-liquid coupling effect. Therefore, in this embodiment, the output at both ends of the damper is provided by the pressure loss along the way caused by the reciprocating motion of the viscous fluid, the local pressure loss when the viscous fluid passes through the variable cross-section in the damping cylinder 1, the pressure loss generated by the viscous fluid passing through the inertial unit, and the rotational inertia force caused by the rotation of the flywheel 602. Specifically:

[0060]

[0061] Among them, F 2 The damper outputs at both ends in another embodiment.

[0062] In the description of the present application, it should be noted that the terms "upper", "lower", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application. Unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be an indirect connection through an intermediate medium, or it can be a connection between the two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to the specific circumstances.

[0063] It should be noted that, in this application, relational terms such as "first" and "second" are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Moreover, the terms "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, the elements defined by the sentence "comprise a ..." do not exclude the presence of other identical elements in the process, method, article or device including the elements.

[0064] The above is only a specific implementation of the present application, so that those skilled in the art can understand or implement the present application. Various modifications to these embodiments will be apparent to those skilled in the art, and the general principles defined herein can be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application will not be limited to the embodiments shown herein, but will conform to the widest range consistent with the principles and novel features applied for herein.

Claims

1. A solid-liquid coupling inertial capacity damper, characterized in that: include: A motion component, the motion component comprising a damping cylinder (1) having two parallel chambers and an axial piston rod (2) with one end entering one of the chambers, the damping cylinder (1) being provided with a variable section guide rod (3) embedded in the end of the axial piston rod (2), the variable section guide rod (3) being provided with a sealing piston (4) sleeved on the outer periphery of the end of the axial piston rod (2); A vibration reduction assembly is located in a damping cylinder (1), the vibration reduction assembly comprising a first medium receiving chamber (5) formed at the joint between the axial piston rod (2) and the variable guide rod (3), a second medium receiving chamber (6) formed in another chamber and connected to the first medium receiving chamber (5), and a third medium receiving chamber (7) formed between the outer wall of the axial piston rod (2) and the inner wall of the damping cylinder (1) and connected to the second medium receiving chamber (6), wherein the second medium receiving chamber (6) is provided with an inertial unit which, by its own rotation, causes the viscous fluid in the second medium receiving chamber (6) to produce a solid-liquid coupling effect.

2. A solid-liquid coupling inertia damper as claimed in claim 1, characterized in that: The variable-section guide rod (3) comprises a partition portion (301) fitted to the inner wall of the damping cylinder (1) and a guide rod portion (302) located on a side of the partition portion (301) close to the axial piston rod (2) and having a reduced diameter.

3. A solid-liquid coupling inertia damper as claimed in claim 2, characterized in that: An end surface of the axial piston rod (2) entering the damping cylinder (1) is provided with an escape groove (201) which is concave inwardly facing away from the variable-section guide rod (3) for the guide rod portion (302) to be embedded, and the first medium accommodating chamber (5) is formed in the escape groove (201).

4. The solid-liquid coupling inertia damper according to claim 1, characterized in that: The variable-section guide rod (3) is axially provided with a first medium channel (303) for connecting the first medium receiving chamber (5) with the second medium receiving chamber (6).

5. The solid-liquid coupling inertia damper according to claim 1, characterized in that: A second medium channel (8) is provided on the outer wall of the damping cylinder (1) for connecting the second medium receiving chamber (6) with the third medium receiving chamber (7).

6. The solid-liquid coupling inertia damper according to claim 1, characterized in that: The damping cylinder (1) comprises a through-type cylinder body (101) and sealing end covers (102) located at the openings at both ends of the through-type cylinder body (101); one end of the axial piston rod (2) passes through one of the sealing end covers (102) and is engaged with the variable-section guide rod (3).

7. A solid-liquid coupling inertia damper as claimed in claim 6, characterized in that: The sealing piston (4) is provided with a step portion (401) on the side facing the axial piston rod (2) for the end of the axial piston rod (2) to be embedded.

8. The solid-liquid coupling inertia damper according to claim 7, characterized in that: One end surface of the sealing piston (4) facing the axial piston rod (2) and the bottom surface of one of the sealing end covers (102) provided with the axial piston rod (2) form two inner walls of the third medium accommodating chamber (7).

9. A solid-liquid coupling inertia damper as claimed in claim 8, characterized in that: The inertial unit includes a hydraulic motor (601) and a flywheel (602) located on the rotor of the hydraulic motor (601).

10. The solid-liquid coupling inertia damper according to claim 9, characterized in that: The output force at both ends of the solid-liquid coupling inertial capacity damper is composed of two parts: the viscous damping force generated by the reciprocating motion of the viscous fluid and the inertial force provided by the rotation of the inertial unit; The viscous damping force is mainly provided by the pressure loss along the path caused by the reciprocating motion of the viscous fluid, the local pressure loss when the viscous fluid passes through the variable cross-section in the damping cylinder (1), and the pressure loss caused by the viscous fluid passing through the inertial unit. The inertial force includes the rotational inertial force caused by the rotation of the flywheel (602) and the inertial force provided by the solid-liquid coupling effect generated thereby.

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