Hydraulic inerter with adjustable inerter coefficient and working method thereof

Abstract

The application relates to a hydraulic inertial container with adjustable inertial coefficient, which comprises a cylinder body, the inside of the cylinder body is separated into a main cylinder body and a secondary cylinder body by a wall with a hole, a piston block is arranged in the main cylinder body, coaxial piston rods are arranged at both ends of the piston block, one end of one piston rod penetrates into the inside of the secondary cylinder body through the hole and is connected with the secondary cylinder body through a coaxial spring, the other end of the other piston rod penetrates out of the main cylinder body to the outside, the cylinder wall of the main cylinder body at both ends of the piston block is provided with reserved holes, the two reserved holes are connected through a tubular channel, and the tubular channel is composed of a straight pipe section, a spiral pipe section and a connecting pipe. The hydraulic inertial container with adjustable inertial coefficient reduces the dynamic mass of the structure by reducing the inertial coefficient when the excitation lasts for a short time; when the excitation is large, the inertial force is outputted to assist the structure in shock absorption by increasing the inertial coefficient.

Description

TECHNICAL FIELD

[0001] The present application relates to a kind of adjustable fluid flywheel inertia coefficient and its working method, and it relates to structural damping technical field. BACKGROUND

[0002] Flywheel inertia is an acceleration-dependent device, the inertia force exported is proportional to acceleration, and the coefficient before acceleration is called flywheel inertia coefficient. The existing flywheel inertia realizes various forms, including rack and pinion, ball screw, etc., the common point is to transform the horizontal displacement between the two ends of flywheel inertia, to realize the inertia force greater than the actual gravity of flywheel inertia, wherein fluid flywheel inertia converts the horizontal movement between the two ends into the flow of liquid along the tubular channel, thereby outputting the inertia force, but the existing fluid flywheel inertia can only output a fixed inertia force, and cannot realize the adjustable flywheel inertia coefficient. The flywheel inertia with fixed flywheel inertia coefficient has the following disadvantages: especially under the action of earthquake, the external excitation of structure is randomly changed, when the excitation is small, the existing flywheel inertia with fixed flywheel inertia coefficient continuously outputs inertia force of fixed size, which increases the dynamic mass of structure, and at this time, the acceleration response and displacement response of structure are small, and the inertia force is not needed to assist damping.

[0003] In order to solve the above technical problems, the present application provides a kind of adjustable fluid flywheel inertia, when the excitation is small, by reducing flywheel inertia coefficient, the dynamic mass of structure is reduced, when the excitation is large, by increasing flywheel inertia coefficient, larger inertia force is output to assist structure damping.

[0004] Therefore, the adjustable fluid flywheel inertia can enhance the damping performance of structure, and can also be applied to damping device, while reducing the mass of damping device, the adjustable flywheel inertia coefficient is used to improve the performance of damping device. Moreover, the adjustable fluid flywheel inertia not only has simple structure and low manufacturing cost, but also is convenient to arrange, and can be applied in high-rise building, bridge, machinery and other fields. SUMMARY

[0005] In view of the deficiencies of the prior art, the technical problem to be solved by the present application is to provide an adjustable fluid flywheel inertia and its working method.

[0006] In order to solve the above technical problems, the technical scheme of the present application is: a hydraulic inertial damper with adjustable inertial damper coefficient, comprising a cylinder body, the inside of the cylinder body is separated into a main cylinder body and a secondary cylinder body by a wall with a circular hole, a piston block is arranged in the inside of the main cylinder body, both ends of the piston block are coaxially fixed with piston rods, one end of one of the piston rods penetrates into the inside of the secondary cylinder body through the circular hole and is connected with the secondary cylinder body through a coaxially connected spring, the other end of the other piston rod penetrates out of the main cylinder body to the outside, the cylinder wall of the main cylinder body at both ends of the piston block is provided with a reserved hole, the two reserved holes are connected and communicated through a tubular channel, and the tubular channel is composed of a straight pipe section, a spiral pipe section and a connecting pipe.

[0007] Preferably, the outer diameter of the piston block is the same as the inner diameter of the main cylinder body.

[0008] Preferably, the axial direction of the straight pipe section is parallel to the axial direction of the spiral pipe section, and the straight pipe section is located at a spiral radius offset from the central axis of the spiral pipe section.

[0009] Preferably, the inner diameters of the cross sections of the straight pipe section and the spiral pipe section are equal, and the interiors of the two pipe intersection nodes are connected and communicated, so as to facilitate the liquid to flow through the straight pipe section and the spiral pipe section when flowing in the tubular channel.

[0010] Preferably, the two ends of the straight pipe section are respectively connected to the two ends of the spiral pipe section, that is, the starting point of the straight pipe section is the same as and communicated with the starting point of the spiral pipe section, and the ending point of the straight pipe section is the same as and communicated with the ending point of the spiral pipe section.

[0011] Preferably, the connecting pipe has two connecting pipes, one end of one of the connecting pipes is communicated with the starting point of the straight pipe section and the spiral pipe section, and the other end is communicated with one of the reserved holes, and one end of the other connecting pipe is communicated with the ending point of the straight pipe section and the spiral pipe section, and the other end is communicated with the other reserved hole, so as to facilitate the liquid inside to flow smoothly in the closed space formed by the main cylinder body and the tubular channel.

[0012] Preferably, the wall is welded and connected in the inside of the cylinder body.

[0013] Preferably, one end of the spring is fixed on the corresponding piston rod, and the other end is fixed on the secondary cylinder body.

[0014] Preferably, a sealing element is arranged between the circular hole and the corresponding piston rod.

[0015] A working method of a hydraulic inertial damper with adjustable inertial damper coefficient is performed according to the following steps:

[0016] S1: When the hydraulic inertial damper with adjustable inertial coefficient is subjected to external force at both ends, the piston block moves horizontally and axially, the piston block extrudes the liquid in the main cylinder into the tubular channel, and then drives the liquid to flow in the closed space formed by the main cylinder and the tubular channel, and the horizontal axial movement of the piston block is converted into irregular flow of the liquid in the tubular channel;

[0017] S2: When the external force decreases, the piston block moves at a reduced speed, the flow rate of the liquid in the main cylinder and the tubular channel decreases, the number of turns of the spiral pipe through which the liquid flows in the tubular channel decreases, the flow length of the liquid in the tubular channel decreases, the inertial coefficient of the inertial damper decreases, and the output inertial force also decreases; when the flow rate cannot meet the requirement of the liquid passing through the highest point of the spiral pipe segment, the liquid flows back to the straight pipe segment along the original path and flows back to the main cylinder from the end of the tubular channel;

[0018] S3: When the external force increases, the piston block moves at an increased speed, the flow rate of the liquid in the main cylinder and the tubular channel increases, the number of turns of the spiral pipe through which the liquid flows in the tubular channel increases, the flow length of the liquid in the tubular channel increases, the inertial coefficient of the inertial damper increases, and the output inertial force also increases; when the liquid flows through all turns of the spiral pipe segment, the output inertial force of the inertial damper reaches the maximum; at the same time, when the inertial damper is working, energy loss occurs at the inner wall of the tubular channel, the inner wall of the main cylinder, the start point and the end point of the tubular channel, and the friction between the piston block and the inner wall of the main cylinder all participate in resisting the external force.

[0019] Compared with the prior art, the hydraulic inertial damper with adjustable inertial coefficient has the following beneficial effects: when the excitation lasts for a short time, the inertial coefficient is reduced, and the dynamic mass of the structure is reduced; when the excitation is large, the inertial coefficient is increased, and a large inertial force is output to assist the structure in shock absorption.

[0020] The hydraulic inertial damper with adjustable inertial coefficient can enhance the shock absorption performance of the structure, and can also be applied to a shock absorption device, which can reduce the mass of the shock absorption device while playing the adjustable inertial coefficient and improving the performance of the shock absorption device. Moreover, the hydraulic inertial damper with adjustable inertial coefficient has simple structure, low manufacturing cost, and convenient arrangement, and can be applied in high-rise buildings, bridges, machinery and other fields.

[0021] The application will be further described in detail below in combination with the drawings and specific embodiments. BRIEF DESCRIPTION OF DRAWINGS

[0022] Fig. 1 The figure is a schematic view of the embodiment of the application.

[0023] Fig. 2 The figure is a time history diagram of the displacement response of the top layer of a four-layer frame structure installed with the application under Qian An seismic waves.

[0024] Fig. 3 Figure 1 is a time history diagram of the top floor acceleration response of the four-layer frame structure installed with the application under Qian An seismic waves.

[0025] In the figure: wall surface 1, main cylinder body 2, auxiliary cylinder body 3, piston block 4, piston rod 5, spring 6, reserved hole 7, straight pipe section 8, spiral pipe section 9, connecting pipe 10. DETAILED DESCRIPTION

[0026] The application will be further described below in conjunction with the drawings and examples.

[0027] It should be noted that the following detailed description is exemplary in nature and is intended to provide further description of the application. Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs.

[0028] It is to be understood that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or groups thereof.

[0029] As shown in Figs. 1-3 The embodiment provides a hydraulic inertia container with adjustable inertia coefficient. The inertia container can output inertia force greater than its actual gravity through reasonable design, and can realize adjustable inertia coefficient, reduce dynamic mass in structural vibration process, and strengthen damping performance of the structure. The hydraulic inertia container comprises a cylinder body. The cylinder body is divided into a main cylinder body 2 and an auxiliary cylinder body 3 by a wall surface 1 with a circular hole. A piston block 4 is arranged in the main cylinder body. Piston rods 5 are coaxially arranged at both ends of the piston block. One end of one piston rod penetrates into the auxiliary cylinder body through the circular hole and is connected with the auxiliary cylinder body through a coaxial spring 6. The other end of the other piston rod penetrates out of the main cylinder body and is connected with an external structure to be damped. Reserved holes 7 are arranged on the cylinder wall of the main cylinder body at both ends of the piston block. The two reserved holes are connected through a tubular channel. The tubular channel is composed of a straight pipe section 8, a spiral pipe section 9 and a connecting pipe 10.

[0030] Under the action of external force, the inertial container is stressed at both ends, and the piston block is displaced. The movement of the piston block extrudes the liquid in the main cylinder body into the tubular passage, i.e. the horizontal movement of the piston block is converted into the complex flow of the liquid in the tubular passage, so as to realize the output of the inertial force greater than the actual gravity of the inertial container. When the external force gradually increases from zero, the initial speed of the liquid extruded into the tubular passage is also gradually accelerated, and the flow length in the tubular passage is also continuously increased, from the initial "connecting pipe - straight pipe section - connecting pipe" to "connecting pipe - straight pipe section and a spiral pipe section - connecting pipe", and then to "connecting pipe - straight pipe section and all spiral pipe sections - connecting pipe". Since the size of the inertial force output by the inertial container is related to the flow length in the tubular passage, the adjustable output of the inertial force of the inertial container is realized according to the change of the flow length with the size of the external force.

[0031] In the embodiment of the present application, the outer diameter of the piston block is the same as the inner diameter of the main cylinder body.

[0032] In the embodiment of the present application, the axial direction of the straight pipe section is parallel to the axial direction of the spiral pipe section, and the straight pipe section is located at a position deviated from the central axis of the spiral pipe section by a spiral radius.

[0033] In the embodiment of the present application, the inner diameters of the cross sections of the straight pipe section and the spiral pipe section are equal, and the interiors of the two pipe intersection nodes are connected to facilitate the flow of the liquid in the tubular passage, which can flow through the straight pipe section and the spiral pipe section.

[0034] In the embodiment of the present application, the two ends of the straight pipe section are respectively connected to the two ends of the spiral pipe section, i.e. the starting point of the straight pipe section is the same as and connected to the starting point of the spiral pipe section, and the ending point of the straight pipe section is the same as and connected to the ending point of the spiral pipe section.

[0035] In the embodiment of the present application, the connecting pipe has two, one of which is connected at one end to the starting point of the straight pipe section and the spiral pipe section and at the other end to a reserved hole, and the other connecting pipe is connected at one end to the ending point of the straight pipe section and the spiral pipe section and at the other end to another reserved hole, so that the liquid encapsulated inside can flow smoothly in the sealed space formed by the main cylinder body and the tubular passage.

[0036] In the embodiment of the present application, the wall surface is welded and connected inside the cylinder body.

[0037] In the embodiment of the present application, one end of the spring is fixed to the corresponding piston rod, and the other end is fixed to the auxiliary cylinder body. The spring is provided to ensure that the piston block can be restored to the initial position in time after displacement.

[0038] In the embodiment of the present application, a sealing element is arranged between the circular hole and the corresponding piston rod.

[0039] A working method of a liquid force inertial container with adjustable inertial coefficient is performed according to the following steps:

[0040] S1: When the hydraulic flywheel mass with adjustable inertance coefficient is subjected to external force, the piston block moves horizontally and axially, the piston block pushes the liquid in the main cylinder into the tubular channel, and then drives the liquid to flow in the closed space formed by the main cylinder and the tubular channel, and the horizontal axial movement of the piston block is converted into irregular flow of the liquid in the tubular channel;

[0041] S2: When the external force decreases, the piston block moves at a reduced speed, the flow rate of the liquid in the main cylinder and the tubular channel decreases, the number of turns of the spiral pipe through which the liquid flows in the tubular channel decreases, the flow length of the liquid in the tubular channel decreases, the inertance coefficient of the flywheel mass decreases, and the output inertial force also decreases; when the flow rate cannot meet the highest point of the spiral pipe segment, the liquid flows back to the straight pipe segment along the original route, and flows back to the main cylinder from the end point of the tubular channel;

[0042] S3: When the external force increases, the piston block moves at an increased speed, the flow rate of the liquid in the main cylinder and the tubular channel increases, the number of turns of the spiral pipe through which the liquid flows in the tubular channel increases, the flow length of the liquid in the tubular channel increases, the inertance coefficient of the flywheel mass increases, and the output inertial force also increases; when the liquid flows through all turns of the spiral pipe segment, the output inertial force of the flywheel mass reaches the maximum; at the same time, when the flywheel mass works, the liquid and the inner wall of the tubular channel, the inner wall of the main cylinder, the start point and the end point of the tubular channel will produce certain energy loss, and the friction between the piston block and the inner wall of the main cylinder will also participate in resisting the external force.

[0043] To simulate the actual damping effect of the flywheel mass, a four-story frame structure model is established, and the flywheel mass is installed between the third story and the fourth story. Taking the model under the excitation of Qian An seismic wave as an example, through Fig. 2 、 Fig. 3 It can be clearly seen that the damping effect of the flywheel mass is good.

[0044] The above is only a preferred embodiment of the present application, and is not intended to limit the present application in other forms. Any skilled person in the art can modify or change the above disclosed technical content to obtain equivalent embodiments. However, any simple modification, equivalent change and modification made on the basis of the technical essence of the present application to the above embodiments still belongs to the protection scope of the present application.

Claims

1. A method of operating a hydraulic inertial capacitor with adjustable inertance coefficient, characterized in that: The hydraulic inertial damper with adjustable inertial coefficient comprises a cylinder, the inside of the cylinder is separated into a main cylinder and a secondary cylinder by a wall with a hole, a piston block is arranged in the inside of the main cylinder, both ends of the piston block are coaxially fixed with piston rods, one end of one of the piston rods penetrates into the inside of the secondary cylinder through the hole and is connected with the secondary cylinder through a coaxially connected spring, the other end of the other piston rod penetrates out of the main cylinder to the outside, the cylinder wall of the main cylinder on both ends of the piston block is provided with reserved holes, the two reserved holes are connected and communicated through a tubular channel, the tubular channel is composed of a straight pipe section, a spiral pipe section and a connecting pipe; the working method of the hydraulic inertial damper with adjustable inertial coefficient comprises the following steps: S1: when the hydraulic inertial damper with adjustable inertial coefficient is subjected to external force at both ends, the piston block moves horizontally and axially, the piston block extrudes the liquid in the main cylinder into the tubular channel, and then drives the liquid to flow in the closed space formed by the main cylinder and the tubular channel, and converts the horizontal axial movement of the piston block into irregular flow of the liquid in the tubular channel; S2: when the external force decreases, the movement speed of the piston block decreases, the flow rate of the liquid in the main cylinder and the tubular channel decreases, the number of turns of the spiral pipe section through which the liquid flows in the tubular channel decreases, the flow length of the liquid in the tubular channel decreases, the inertial coefficient of the inertial damper decreases, and the output inertial force also decreases; when the flow rate cannot meet the requirement that the liquid passes through the highest point of a certain turn of the spiral pipe section, the liquid flows back to the straight pipe section along the original path and flows back to the main cylinder from the end point of the tubular channel; S3: when the external force increases, the movement speed of the piston block increases, the flow rate of the liquid in the main cylinder and the tubular channel increases, the number of turns of the spiral pipe section through which the liquid flows in the tubular channel increases, the flow length of the liquid in the tubular channel increases, the inertial coefficient of the inertial damper increases, and the output inertial force also increases, and when the liquid flows through all turns of the spiral pipe section, the output inertial force of the inertial damper reaches the maximum; at the same time, when the inertial damper works, energy loss occurs at the liquid and the inner wall of the tubular channel, the inner wall of the main cylinder, the start point and the end point of the tubular channel, and the friction between the piston block and the inner wall of the main cylinder all jointly resist the external force.

2. The method of operating a hydraulic inertial flywheel according to claim 1, wherein: The outer diameter of the piston block is the same as the inner diameter of the main cylinder.

3. The method of operating a hydraulically based inerter with adjustable inerter coefficient according to claim 1, characterized in that: The axial direction of the straight pipe section is parallel to the axial direction of the spiral pipe section, and the straight pipe section is located at a spiral radius away from the central axis of the spiral pipe section.

4. The method of claim 1, wherein: The inner diameters of the cross sections of the straight pipe section and the spiral pipe section are equal, and the interiors of the two pipe intersection nodes are connected, so that the liquid can flow through the straight pipe section and the spiral pipe section when flowing in the tubular channel.

5. The method of claim 1, wherein: The two ends of the straight pipe section are respectively connected to the two ends of the spiral pipe section, that is, the start point of the straight pipe section is the same as and communicates with the start point of the spiral pipe section, and the end point of the straight pipe section is the same as and communicates with the end point of the spiral pipe section.

6. The method of operating a hydraulically based inerter with adjustable inerter coefficient according to claim 5, characterized in that: The connecting pipe has two connecting pipes, one end of one of the connecting pipes communicates with the start point of the straight pipe section and the spiral pipe section, and the other end communicates with one of the reserved holes, and one end of the other connecting pipe communicates with the end point of the straight pipe section and the spiral pipe section, and the other end communicates with the other reserved hole, so that the liquid in the enclosed space formed by the main cylinder and the tubular channel can flow smoothly.

7. The method of operating a hydraulically based inerter with adjustable inerter coefficient according to claim 1, characterized in that: The wall is welded and connected in the inside of the cylinder.

8. The method of operating a hydraulically based inerter with adjustable inerter coefficient according to claim 1, characterized in that: One end of the spring is fixed on the corresponding piston rod, and the other end is fixed on the auxiliary cylinder body.

9. The method of operating a hydraulically based inerter with adjustable inerter coefficient according to claim 1, characterized in that: The round hole is provided with a sealing element between the round hole and the corresponding piston rod.

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