Viscoelastic inerter damper
By using viscoelastic materials and simple mechanical structural design in the inertial volume damper, the liquid leakage problem of inertial volume damper is solved, and effective application in a maintenance-free environment is achieved, equipment life is extended and maintenance costs are reduced.
Patent Information
- Application Number
- CN202422374192.4
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-09-27
- Publication Date
- 2025-08-01
- Estimated Expiration
- 2034-09-27
AI Technical Summary
The existing inertial volume dampers have a risk of liquid leakage due to the use of viscous fluids as energy-consuming components and are not suitable for use in maintenance-free or closed environments.
Viscoelastic materials are used instead of viscoelastic fluids. By combining the screw, nut and flywheel, axial translation is converted into rotational motion, using the shear hysteresis deformation of the viscoelastic materials to consume energy and encapsulate it in a sleeve to isolate the external environmental influences.
It effectively avoids leakage of viscoelastic materials, extends the service life of the equipment, reduces maintenance and replacement frequency, improves the reliability and vibration damping performance of the system, and reduces design and production costs.
Smart Images
Figure CN223176946U_ABST
Abstract
Description
Technical Field
[0001] This application relates to the technical field of shock damping, and particularly to a viscoelastic inertial damper. Background Art
[0002] An inertial damper is a special damper that converts the axial translational motion at both ends into rotational motion, thereby providing structural tuning inertial mass and dissipating seismic energy. The working principle of the inertial damper is mainly based on the amplification effect of inertial mass. It realizes motion conversion and energy consumption through a roller screw, a flywheel and an energy dissipation component. Specifically, the roller screw converts axial translation into rotation, and the flywheel realizes the amplification of inertial mass.
[0003] In existing inertial dampers, the energy dissipation components usually consume energy through viscous or other mechanisms, thereby reducing the vibration response of the structure. Among them, by directly arranging a viscous chamber in the outer cylinder, introducing fluid into the viscous chamber, and utilizing the viscous damping effect to reduce vibration. The flow of the fluid resists motion, thereby absorbing and dissipating vibration energy. However, it has the risk of liquid leakage and is not suitable for use in environments requiring maintenance-free or airtight conditions. Summary of the Utility Model
[0004] The technical problem to be solved by this utility model is that the existing inertial damper using viscous fluid as the energy dissipation component is prone to liquid leakage.
[0005] For this reason, this utility model provides a viscoelastic inertial damper.
[0006] The technical solution adopted by this utility model to solve its technical problem is:
[0007] A viscoelastic inertial damper includes
[0008] a connecting cylinder, and
[0009] a lead screw, one end of the lead screw is inserted into the end of the connecting cylinder and slides axially along the connecting cylinder;
[0010] a nut, the nut is located inside the connecting cylinder and is in threaded cooperation with the lead screw;
[0011] a flywheel, the flywheel is connected to the nut;
[0012] a cylinder, the cylinder is arranged inside the connecting cylinder, an intermediate rod connected to the lead screw is inserted on the cylinder, and a viscoelastic material is arranged inside the cylinder.
[0013] Further, the flywheel is arranged in an H shape, and the outer side wall of the flywheel is parallel to the inner side wall of the connecting cylinder.
[0014] Further, both ends of the connecting cylinder are respectively connected with an upper end cover and a lower end cover. A lower bearing seat is connected to the lower end cover, and the lower bearing seat covers the cylinder barrel to limit the displacement of the cylinder barrel.
[0015] Further, a limiting groove is provided on the lower end cover, and the bottom end of the lower bearing seat is embedded in the limiting groove.
[0016] Further, an upper bearing seat is arranged between the upper end cover and the nut.
[0017] Further, a round hole is provided on the upper end cover. An embedded groove adapted to the round hole is provided on the outer circle of the top of the upper bearing seat. The top of the upper bearing seat is inserted into the round hole, and the bottom surface of the embedded groove abuts against the side wall of the upper end cover facing the lower end cover.
[0018] Further, the nut is located between the upper bearing seat and the lower bearing seat, and thrust bearings are arranged between the nut and the upper bearing seat and between the nut and the lower bearing seat.
[0019] Further, embedded grooves adapted to the thrust bearings are provided on both the lower bearing seat and the upper bearing seat.
[0020] Further, a bearing retaining ring is arranged between the nut and the thrust bearing.
[0021] The beneficial effect of the present utility model is that in this application, the viscoelastic material is placed in the sleeve, and the sleeve is arranged in the connecting cylinder, which can effectively isolate the influence of the external environment on its performance, reduce the risk of leakage of the viscoelastic material, and avoid material aging caused by factors such as sunlight and rain. Through the isolation design, the aging speed of the viscoelastic material is slowed down, which means that the service life of the equipment is extended, the frequency of maintenance and replacement is reduced, and the reliability of the overall system is improved. BRIEF DESCRIPTION OF THE DRAWINGS
[0022] The present utility model will be further described below with reference to the drawings and embodiments.
[0023] Figure 1 is a schematic structural diagram of the present utility model.
[0024] In the figure: 1. Inertia damper assembly; 11. Lead screw; 12. Nut; 13. Flywheel; 14. Thrust bearing; 15. Bearing retaining ring; 16. Upper single ear; 2. Viscoelastic damper assembly; 21. Cylinder barrel; 22. Intermediate rod; 23. Viscoelastic material; 3. Sleeve assembly; 31. Connecting cylinder; 32. Upper end cover; 321. Round hole; 33. Lower end cover; 331. Limiting groove; 34. Upper bearing seat; 341. Embedded groove; 35. Lower bearing seat; 36. Lower single ear; 37. Connecting flange. DETAILED DESCRIPTION OF THE EMBODIMENTS
[0025] The present utility model will now be described in further detail with reference to the accompanying drawings. These drawings are all simplified schematic diagrams, only showing the basic structure of the present utility model in a schematic manner, so they only show the components related to the present utility model.
[0026] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present utility model 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, so it cannot be understood as a limitation to the present utility model. In addition, the features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, unless otherwise stated, the meaning of "a plurality" is two or more.
[0027] In the description of the present utility model, it should be noted that unless otherwise clearly specified and limited, the terms "installation", "connection", and "coupling" 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 directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.
[0028] A viscoelastic inertial damper includes an inertial damper assembly 1, a viscoelastic damper assembly 2, and a sleeve assembly 3.
[0029] The sleeve assembly 3 includes a connecting cylinder 31 and end caps. There are two end caps, and the two end caps are respectively connected to both ends of the connecting cylinder 31 by screws.
[0030] The viscoelastic damper assembly 2 includes a cylinder barrel 21 and an intermediate rod 22. The cylinder barrel 21 is coaxially arranged inside the connecting cylinder 31. The cylinder barrel 21 is fixedly connected to one end cap. The end cap connected to the cylinder barrel 21 is called the lower end cap 33, and the other end cap is called the upper end cap 32. One end of the connecting cylinder 31 where the cylinder barrel 21 is arranged is the bottom end. The intermediate rod 22 is coaxially inserted into one end of the cylinder barrel 21 away from the lower end cap 33. There is a viscoelastic material 23 in the cylinder barrel 21, and the viscoelastic material 23 is connected to the cylinder barrel 21 and the intermediate rod 22 by means such as vulcanization process. A lower single ear 36 is connected to the lower end cap 33 through a connecting flange 37.
[0031] The inerter damper assembly 1 includes a lead screw 11, a nut 12, and a flywheel 13. The lead screw 11 passes through the upper end cover 32 and is threadedly connected to the upper end cover 32 through an upper bearing seat 34. One end of the lead screw 11 inserted into the connecting cylinder 31 is coaxially and fixedly connected to the intermediate rod 22, and the other end is connected with an upper single ear 16. The nut 12 is located inside the connecting cylinder 31. The nut 12 is sleeved on the lead screw 11 and is in threaded cooperation with the lead screw 11. A ball is arranged between the nut 12 and the lead screw 11. The nut 12 is slidably mated with the connecting cylinder 31 along the axial direction of the connecting cylinder 31. The flywheel 13 is located inside the connecting cylinder 31. The longitudinal section of the flywheel 13 is set in an H shape. The flywheel 13 is provided with a through hole along its axial direction. The flywheel 13 is sleeved on the nut 12 through the through hole, and the flywheel 13 is fixedly connected to the nut 12.
[0032] It should be noted that an upper bearing seat 34 is connected to the upper end cover 32, and a lower bearing seat 35 is connected to the lower end cover 33. Bearings are arranged between the upper bearing seat 34, the lower bearing seat 35 and the nut 12. A bearing retaining ring 15 is connected between the thrust bearing 14 and the nut 12. A round hole 321 is opened on the upper end cover 32. The outer circle and the bottom surface of the top of the upper bearing seat 34 are respectively provided with an embedding groove 341 having the same size as the round hole 321 and the thrust bearing 14, so as to be embedded and connected with the upper end cover 32 and the thrust bearing 14. The top of the upper bearing seat 34 is inserted into the round hole 321, and the bottom surface of the embedding groove 341 on the top surface of the upper bearing seat 34 abuts against the side wall of the upper end cover 32 facing the lower end cover 33; the bottom end of the lower bearing seat 35 is sleeved on the cylinder barrel 21, and a limiting groove 331 for embedding the bottom end of the lower bearing seat 35 is provided on the lower end cover 33. The top surface of the lower bearing seat 35 is provided with a groove having the same size as the thrust bearing 14, so as to be embedded and connected with the thrust bearing 14. The upper bearing seat 34 and the lower bearing seat 35 can limit the displacement of the lead screw 11 and the cylinder barrel 21, so that they will not generate axial sway.
[0033] The implementation principle of this application is as follows:
[0034] When the structure vibrates, the upper single ear 16 makes a translational motion along the axial direction of the lead screw 11 and drives the lead screw 11 to move. The nut 12 cooperates with the lead screw 11 to convert the linear motion of the lead screw 11 into a rotational motion, and the nut 12 drives the flywheel 13 to rotate. The lead screw 11 drives the intermediate rod 22 to move, so that the viscoelastic material generates shear hysteresis deformation to dissipate energy.
[0035] In summary, this application combines a viscoelastic damper and an inerter damper. By using inertial mass and viscoelastic materials, vibration can be effectively resisted. The design of this solution is relatively simple and usually does not require complex mechanical structures or electrical components, which is convenient for manufacturing and maintenance. This simplicity reduces the design and production costs.
[0036] A cylinder 21 is provided at the end of the lead screw 11. The shape of this cylindrical viscoelastic damper enables it to provide damping force in different directions. Due to the design of its mechanical structure, it can generate damping in both the axial and radial directions simultaneously. This design allows the damper to work effectively in various motion modes, which is particularly important for applications that require controlling multiple vibration modes (such as the swaying of buildings and the multi-directional movement of mechanical equipment).
[0037] Moreover, by placing the viscoelastic material 23 in the middle of the sleeve, it can effectively isolate the influence of the external environment on its performance, avoiding material aging caused by factors such as sunlight and rain. Through the isolation design, the aging rate of the viscoelastic material slows down, which means the service life of the equipment is extended, the frequency of maintenance and replacement is reduced, and the reliability of the overall system is improved.
[0038] The moment of inertia I of the flywheel 13 represents the resistance of an object to angular acceleration during rotational motion. According to the general calculation formula of the moment of inertia I = ∫r 2 dm, it can be found that the moment of inertia I is proportional to the mass m and proportional to the square of the radius of rotation r (where r represents the distance from the mass point to the axis of rotation, and dm represents the infinitesimal mass element). The larger the moment of inertia, the smaller the rotational acceleration of the object when it is subjected to an external force, showing stronger inertia. Increasing the moment of inertia means that under the same applied force, the motion state of the object is not easily changed, which enables it to more effectively absorb and disperse the energy from external vibrations.
[0039] The H-shaped design of the flywheel 13 optimizes the mass distribution mechanically, which can effectively enhance the inertia of the system, making more mass concentrated at a place farther from the axis of rotation. Thus, even if the actual mass of the structure itself is small, a larger inertial force can be generated, increasing the moment of inertia. Therefore, through this design, vibrations can be controlled more effectively, and the vibration damping performance of the system is improved. Therefore, such a design can, on the one hand, increase the effective mass of the rotating part, and on the other hand, move the rotating mass away from the central axis, increasing the radius of rotation, and thus increasing the moment of inertia. A larger mass can provide a greater inertial force, which can more effectively counteract the externally applied vibrations. At the same time, the upper bearing retaining ring 15 and the lower bearing retaining ring 15 connected to the nut 12 limit the radial movement of the lead screw 11 and the nut 12, and the thrust bearing 14 ensures the rotation of the lead screw 11 and the nut 12.
[0040] Due to the design of the H-shaped flywheel 13, lightweight materials can be used in this solution. The design of this application is compact, occupying a small space, reducing the overall weight, having a wide range of applications, and being convenient for installation and transportation. The simple and lightweight structure makes the construction more efficient, shortening the installation time and reducing the cost. In addition, the small space occupation is helpful for building design and equipment layout, ensuring effective vibration damping while reserving more available space.
[0041] Inspired by the above-described ideal embodiments of the present utility model, through the above description, relevant staff can completely make various changes and modifications without departing from the technical idea of this utility model. The technical scope of this utility model is not limited to the content in the specification, and its technical scope must be determined according to the scope of the claims.
Claims
1. A viscoelastic inertial damper, characterized in that, including, a connecting cylinder (31), and a lead screw (11), one end of the lead screw (11) is inserted into the end of the connecting cylinder (31) and slides axially along the connecting cylinder (31); a nut (12), the nut (12) is located inside the connecting cylinder (31) and is in threaded cooperation with the lead screw (11); a flywheel (13), the flywheel (13) is connected to the nut (12); a cylinder barrel (21), the cylinder barrel (21) is arranged inside the connecting cylinder (31), an intermediate rod (22) connected to the lead screw (11) is inserted into the cylinder barrel (21), and a viscoelastic material (23) is arranged inside the cylinder barrel (21).
2. The viscoelastic inertial-damping damper according to claim 1, wherein, The flywheel (13) is arranged in an H shape, and the outer side wall of the flywheel (13) is parallel to the inner side wall of the connecting cylinder (31).
3. The viscoelastic inertial-damping damper according to claim 1, wherein Upper end caps (32) and lower end caps (33) are respectively connected to both ends of the connecting cylinder (31), a lower bearing seat (35) is connected to the lower end cap (33), and the lower bearing seat (35) covers the cylinder barrel (21) to limit the displacement of the cylinder barrel (21).
4. The viscoelastic inertial-damping damper according to claim 3, wherein A limiting groove (331) is arranged on the lower end cap (33), and the bottom end of the lower bearing seat (35) is embedded in the limiting groove (331).
5. The viscoelastic inertial damper according to claim 3, wherein, An upper bearing seat (34) is arranged between the upper end cap (32) and the nut (12).
6. The viscoelastic inertial damper according to claim 5, wherein A round hole (321) is opened on the upper end cap (32), a fitting groove (341) adapted to the round hole (321) is opened on the outer circle at the top of the upper bearing seat (34), the top of the upper bearing seat (34) is inserted into the round hole (321), and the bottom surface of the fitting groove (341) abuts against the side wall of the upper end cap (32) facing the lower end cap (33).
7. The viscoelastic inertial-damping damper according to claim 5, characterized in that, The nut (12) is located between the upper bearing seat (34) and the lower bearing seat (35), and thrust bearings (14) are arranged between the nut (12) and the upper bearing seat (34) and the lower bearing seat (35).
8. The viscoelastic inertial-damping damper according to claim 7, wherein Fitting grooves (341) adapted to the thrust bearings (14) are arranged on both the lower bearing seat (35) and the upper bearing seat (34).
9. The viscoelastic inertial-damping damper according to claim 7, characterized in that, A bearing retaining ring (15) is arranged between the nut (12) and the thrust bearing (14).