An inverted track type inertial mass damper

Abstract

The present invention provides an inverted track type inertia mass damper, comprising: a base, a rolling member, a track member, an inertia mass device and a track fixing platform; the rolling member is rotatably mounted on the surface of the base through a support assembly, one end of which is provided with an active bevel gear that rotates coaxially with the rolling member, the track member is provided at the bottom of the track fixing platform, the bottom of the track member is provided with an inverted U-shaped track that matches the rolling member, so that it rolls relative to the curved track, the inertia mass device comprises a multi-stage gear flywheel set, the first-stage gear flywheel set comprises a driven bevel gear and a first-stage flywheel, the driven bevel gear is rotatably mounted on the first shaft, the driven bevel gear and the active bevel gear are adapted for transmission, the bottom of the driven bevel gear is fixedly connected to the first-stage flywheel, and drives it to rotate synchronously around the first shaft. The mass damper of the present invention provides equivalent mass through inertia, greatly reduces the volume of the device, obtains a linear and nonlinear force-displacement relationship through track design, and improves the sensitivity to frequency and energy changes.

Description

Technical Field

[0001] The invention relates to the technical field of vibration control and energy dissipation and shock absorption, and in particular to an inverted track type inertial mass damper. Background Art

[0002] In order to ensure the safety of engineering structures under extreme loads (such as wind loads, earthquakes, etc.), structural control technology came into being. Structural control technology is a technology that reduces structural vibration and accelerates energy consumption by adding control devices to the main structure or changing the main structure characteristics (such as changing structural stiffness, damping, etc.).

[0003] Among them, the tuned mass damper (TMD) is a structural control device attached to the main structure. The TMD consists of an additional mass, a spring component and a damping component. The additional mass is connected to the main structure through the spring component and the damping component. The TMD is generally placed at a location where the main structure vibrates more (such as the top of a building structure). The additional mass is relatively small relative to the mass of the main structure. When the natural frequency of the TMD is tuned with the main natural frequency of the main structure, the two form a resonance mechanism, the TMD vibrates violently, and consumes energy through its own damping, so that the vibration of the main structure is rapidly reduced. Usually, the size of the TMD additional mass is determined first, and then the required natural frequency is achieved by adjusting the stiffness of the spring component. It is widely used in high-rise and towering structures to reduce the response of the structure under wind loads, so as to achieve the purpose of improving structural safety and comfort. In addition to directly using spring components, the spring component in the TMD can also be realized by using a pendulum, etc. The purpose of both is to provide a certain amount of linear stiffness so that the natural frequency of the TMD meets the design requirements.

[0004] TMD is a mass damper. The larger the mass, the better the vibration reduction effect. In practical applications, it not only occupies a large amount of space and affects the use function of the building, but also has an adverse effect on the load-bearing components of the main structure. In addition, the spring component in TMD is a linear spring. Therefore, when the additional mass and spring stiffness of TMD are determined, the natural frequency of TMD remains unchanged. However, when the natural frequency of the main structure changes (such as the mass of the building changes with the use function, and the stiffness changes with the building settlement, structural damage, and temperature), TMD and the main structure are no longer tuned, and an effective resonance mechanism cannot be formed between the two. The vibration reduction performance of TMD will be greatly degraded, and even increase the structural response. In addition, TMD vibrates violently when working, and the vibration energy is consumed by the TMD damping component. The energy consumption mode of the damping component is single, and the energy consumption capacity is limited, which is often insufficient to consume the vibration energy. In order to ensure energy consumption efficiency, additional damping devices (such as viscous dampers) need to be added. However, adding dampers not only further increases the volume of the device and the difficulty of installation, but also excessive viscous damping will hinder the vibration of TMD and reduce the energy consumption rate.

[0005] Nonlinear Energy Sink (NES) is a type of structural control device similar to TMD, and is still in the basic research stage. The composition of NES is similar to that of TMD, and is also composed of additional mass, spring components and damping components, but the spring component of NES is a nonlinear spring, that is, the restoring force generated by the nonlinear spring changes nonlinearly with the displacement of the additional mass. The most commonly used NES uses a cubic spring component, that is, the restoring force generated is proportional to the cube of the NES displacement. Figure 1 The relationship between the spring restoring force and the displacement of the added mass is compared between TMD (linear) and NES (cubic nonlinear). In contrast to TMD, the stiffness of NES varies with displacement and has a continuously changing natural frequency, so it can resonate with many frequencies, solving the problem of TMD being sensitive to frequency changes.

[0006] The components of the NES device generally include an additional mass, a spring group, a slide rail, a fixing device, and a baffle. The additional mass moves along the slide rail, and the baffle is installed at both ends of the slide rail as a safety measure. The spring group is connected to the main structure in a direction perpendicular to the direction of movement of the additional mass. It is worth noting that in order to achieve the cubic force-displacement relationship of NES, the spring group maintains its original length (i.e., it is not stretched) when the additional mass is stationary (i.e., when the spring group is perpendicular to the direction of movement of the additional mass). This setting enables the spring group to generate an approximately cubic restoring force in the direction of movement of the additional mass, which is equivalent to the cubic spring in the theoretical model.

[0007] Although NES is insensitive to frequency changes, it is extremely sensitive to energy changes (load size). When the load on the structure is very small, the NES vibrates very little, and its corresponding stiffness is also very small, that is, when the input energy is small, the natural frequency of NES is small; on the contrary, when the load is large, the NES vibrates very much, and its corresponding stiffness also continues to remain at a large value, that is, when the input energy is large, the natural frequency of NES is large. In both cases, the natural frequency of NES is very different from the natural frequency of the main structure, making it difficult to form an effective resonance mechanism, resulting in the degradation of vibration reduction ability.

[0008] In addition, NES technology still has not solved the problem that TMD devices are large in size, have a single energy consumption method, and have weak energy consumption capacity. In fact, since the implementation method of nonlinear springs is more complicated than that of linear springs, the installation space of NES is even larger than that of TMD of the same mass.

[0009] In view of the above reasons, the present invention proposes an inverted track type inertial mass damper to overcome the above problems in the prior art. Summary of the invention

[0010] The object of the present invention is to provide an inverted track type inertial mass damper, which increases the equivalent mass of the mass damper through an inertial box, greatly reducing the physical mass and space requirements of the device, and by designing the shape trajectory of the U-shaped curved track, almost any form of restoring force-displacement relationship can be obtained. When the force-displacement relationship of the mass damper has both linear and nonlinear characteristics, its sensitivity to frequency and energy changes is improved.

[0011] The present invention provides an inverted track type inertia mass damper, comprising: a base, a rolling element, a track element, a track fixing platform and an inertia mass device;

[0012] The track member is arranged at the bottom of the track fixing platform, and an inverted U-shaped curved track is arranged at the bottom of the track member, and the number of the track members is at least three groups;

[0013] The number of the rolling elements is the same as that of the track elements. The rolling elements are rotatably connected to the base through a support assembly, and each rolling element is respectively in rolling cooperation with a U-shaped curved track at the bottom of each track element. One end of the rolling element is provided with an active bevel gear that rotates coaxially with the rolling element.

[0014] The inertia device includes a multi-stage gear flywheel group with sequential meshing transmission, wherein the first-stage gear flywheel group includes a driven bevel gear and a first-stage flywheel, the driven bevel gear is rotatably mounted on the end of the first shaft, the driven bevel gear is adapted for transmission with the driving bevel gear, and the bottom of the driven bevel gear is fixedly connected to the first-stage flywheel, and can drive it to rotate synchronously around the first shaft.

[0015] Preferably, the number of the track members and the number of the rolling members are both four.

[0016] Preferably, the surface of the base and the bottom surface of the track fixing platform are both rectangular, and the rolling element and the track element are symmetrically arranged at four corners of the base and the track fixing platform, respectively.

[0017] Preferably, the top of the track member is integrally fixedly connected to the bottom of the track fixing platform.

[0018] Preferably, the rolling element is a roller, and the active bevel gear is integrally connected to the end of the rolling element.

[0019] Preferably, the support assembly includes a group of support columns and a fixed shaft mounted on the top of the support columns, the support columns are vertically connected to the base surface, and the fixed shaft passes through the rolling element and is rotatably mounted thereon.

[0020] Preferably, the gear flywheel groups at other levels all include pinions and flywheels fixedly connected to their bottoms, the first-level flywheel of the first-level gear flywheel group meshes with the pinion of the second-level gear flywheel group for transmission, the flywheel of the second-level gear flywheel group meshes with the pinion of the next-level gear flywheel group for transmission, and so on, the gear flywheel groups at multiple levels mesh with each other for transmission.

[0021] Preferably, the inertia capacity device also includes a second shaft arranged parallel to the first shaft, and the other stages of the gear flywheel group are rotatably mounted on the second shaft and the first shaft in sequence, wherein the second stage gear flywheel group is rotatably mounted on the second shaft.

[0022] Preferably, the inertial containment device also includes an inertial containment box, the inertial containment box is fixedly arranged on the base surface, the driven bevel gear is located outside the inertial containment box, the first shaft rod and the second shaft rod are fixed in the inertial containment box, and the top end of the first shaft rod extends out of the inertial containment box and is rotatably mounted with the driven bevel gear, and the axes of the first shaft rod and the second shaft rod are both perpendicular to the base surface.

[0023] Preferably, the number of the gear flywheel set is four.

[0024] Compared with the prior art, the present invention has the following beneficial effects:

[0025] 1. By designing the shape of the curved track, almost any form of restoring force-displacement relationship can be obtained, not limited to the linear relationship of TMD and the cubic relationship of traditional NES. When the force-displacement relationship of the mass damper has both linear and nonlinear characteristics (the degree of nonlinearity is between linear and cubic nonlinearity), its sensitivity to frequency and energy changes is improved;

[0026] 2. The track member serves as an additional mass and spring component that replaces the mass damper, so that it can not only play the additional mass function, but also provide a restoring force similar to a spring component, and its restoring force has both linear and nonlinear characteristics;

[0027] 3. The inertial force of the inertial device can replace the inertial force of mass motion. The inertial device can be used as an equivalent mass. Compared with mass dampers such as TMD and NES, the volume of the mass damper is greatly reduced, and the space requirement of the device is reduced;

[0028] 4. The structure is simple and easy to install with the controlled structure. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] In order to more clearly illustrate the specific implementation methods of the present invention or the technical solutions in the prior art, the drawings required for use in the specific implementation methods or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some implementation methods of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0030] Figure 1 It is a force-displacement relationship diagram of TMD and NES in the prior art;

[0031] Figure 2 is a schematic diagram of the overall structure of the mass damper in the present invention;

[0032] Figure 3 It is a schematic diagram of the installation of the rolling element, the inertia device and the base in the present invention;

[0033] Figure 4 It is a front view of the internal structure of the inertia container in the present invention;

[0034] Figure 5 The track shapes and corresponding stress-displacement relationships that can be selected for the track members in the present invention;

[0035] Figure 6 is a schematic diagram of the track shape function of the track member;

[0036] Figure 7 It is the force analysis diagram of the track parts in static and moving states;

[0037] Figure 8 Figure 2 is the restoring force-displacement relationship diagram corresponding to different track shapes.

[0038] Description of reference numerals:

[0039] 1: base; 2: rolling element; 3: track element; 4: track fixing platform; 5: support assembly; 51: support column; 52: fixed shaft; 6: driving bevel gear; 7: driven bevel gear; 8: inertia box; 9: first shaft rod; 10: second shaft rod; 11: primary flywheel; 12, 12a, 12b, 12c: pinion gear; 13, 13a, 13b, 13c: flywheel. DETAILED DESCRIPTION

[0040] The technical solution of the present invention will be clearly and completely described below in conjunction with the embodiments. Obviously, the described embodiments are part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0041] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise" and the like 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 invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0042] In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "multiple" means two or more, unless otherwise clearly and specifically defined. In addition, 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 indirectly connected through an intermediate medium, or it can be the internal connection of two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0043] like Figure 2 , 3 As shown in Figure 4, the present invention provides an inverted track type inertial mass damper, comprising: a base 1, a rolling member 2, a track member 3, a track fixing platform 4 and an inertial mass device, wherein the base 1 is fixedly connected to the controlled structure or is the mounting platform of the controlled structure, the rolling member 2 is rotatably mounted on the surface of the base 1 through a support assembly 5, the track member 3 is mounted at the bottom of the track fixing platform 4, and an inverted U-shaped curved track is arranged at the bottom of the track member 3, the controlled structure vibrates when excited by external loads, which causes the track member 3 and the track fixing platform 4 connected thereto to move, wherein the track member 3 and the track fixing platform 4 can replace the additional mass, the track member 3 can replace the spring member to provide restoring force, the movement of the track member 3 drives the rolling member 2 to rotate relative to the support assembly 5, and applies a force to the controlled structure through the support assembly 5. An active bevel gear 6 is arranged at one end of the rolling member 2 to rotate coaxially with it, and the end face of the active bevel gear 6 is integrally fixedly connected with the end face of the rolling member 2.

[0044] Specifically, the number of rolling elements 2 is at least three groups. In this embodiment, the rolling elements 2 are rollers, and the number is four groups. The surface of the base 1 is rectangular, and each rolling element 2 is rotatably mounted at the four corners of the surface of the base 1 through the support assembly 5, and each rolling element 2 is symmetrical about the axis of the base 1. The top of the track member 3 is integrally fixedly connected with the bottom of the track fixing platform 4. The number of track members 3 is the same as the number of rolling elements 2, and their positions correspond to the positions of the rolling elements 2, so that each track member 3 can be respectively adapted to each rolling element 2 located below it, so that each rolling element 2 can roll relative to the inverted U-shaped curved track at the bottom of the track member 3.

[0045] In this embodiment, the support assembly 5 includes a group of support columns 51 arranged in parallel and a fixed shaft 52 mounted between the tops of the two support columns 51, wherein the support columns 51 are vertically fixedly connected to the surface of the base 1, and the rolling element 2 and the fixed shaft 52 are rotatably installed. Specifically, the axis of the fixed shaft 52 is parallel to the surface of the base 1, and the fixed shaft 52 passes through the roller and the active bevel gear 6 along the axial direction of the roller, so that the roller and the active bevel gear 6 can rotate around their axes under the action of external force.

[0046] The inertia device includes an inertia box 8 and a multi-stage gear flywheel group. The inertia box 8 is arranged on the surface of the base 1. The first shaft 9 and the second shaft 10 are fixedly installed in the inertia box 8 and are parallel to each other. The axes of the first shaft 9 and the second shaft 10 are perpendicular to the surface of the base 1. The top of the first shaft 9 extends out of the inertia box 8. Among them, the first-stage gear flywheel group includes a driven bevel gear 7 and a first-stage flywheel 11 fixedly connected to the bottom thereof. The top of the first shaft 9 extends out of the inertia box 8 and is adapted to be rotatably installed with the driven bevel gear 7. The driven bevel gear 7 is adapted to mesh with the driving bevel gear 6 for transmission, thereby driving the first-stage flywheel 11 fixedly connected to the bottom of the driven bevel gear 7 to rotate around the first shaft 9, and the first-stage flywheel 11 further drives the transmission of other stage gear flywheel groups. The rotation of the rolling element 2 around the horizontally arranged fixed shaft 52 can be converted into the rotation of the multi-stage gear flywheel group around the vertically arranged first shaft 9 or second shaft 10 through the driving bevel gear 6 and the driven bevel gear 7.

[0047] The other gear flywheel groups at various levels include a pinion 12 and a flywheel 13 with a small thickness and a large diameter fixedly connected to the bottom thereof. The other gear flywheel groups at various levels are rotatably mounted on the second shaft 10 and the first shaft 9 in turn, wherein the pinion 12 of the secondary gear flywheel group mounted on the second shaft 10 is meshed with the primary flywheel 11 of the primary gear flywheel group for transmission, and the flywheel 13 of the secondary gear flywheel group is meshed with the pinion 12 of the next gear flywheel group mounted on the first shaft 9 for transmission, and so on. Both the primary flywheel 11 and the flywheel 13 are light, thin, and large-diameter disc-shaped members with a large moment of inertia. The inertial force can replace the inertial force of mass motion. Therefore, the inertial capacity device can provide an equivalent mass, thereby reducing the physical mass and space requirements of the device, so that the mass damper does not need to have a large mass to have a good vibration reduction effect.

[0048] In this embodiment, the inertia box 8 is fixedly arranged on the surface of the base 1 and is located below the rolling element 2 and the active bevel gear 6. An inertia device is arranged below each rolling element 2 and the active bevel gear 6. Each inertia device can cooperate with each active bevel gear 6 respectively, and use its larger rotational inertia to provide equivalent mass, thereby reducing the physical mass and space requirements of the device.

[0049] like Figure 4 As shown, in this embodiment, the number of gear flywheel groups is four groups, wherein the first-stage gear flywheel group includes a driven bevel gear 7 and a first-stage flywheel 11 rotatably mounted on the top of the first shaft 9, the second-stage gear flywheel group is rotatably mounted on the second shaft 10, the pinion 12a in the second-stage gear flywheel group is meshed with the first-stage flywheel 11 mounted on the first shaft 9 for transmission, and the flywheel 13a fixedly connected to the bottom of the pinion 12a is meshed with the pinion 12b in the third-stage gear flywheel group rotatably mounted on the first shaft 9 for transmission, and the third-stage gear flywheel group is mounted on On the side of the first-stage flywheel 11 away from the driven bevel gear 7, the third-stage gear flywheel group does not contact the first-stage gear flywheel group, the fourth-stage gear flywheel group is rotatably installed on the lower end of the second shaft 10, and the fourth-stage gear flywheel group does not contact the second-stage gear flywheel group. The pinion 12c of the fourth-stage gear flywheel group is meshed with the flywheel 13b of the third-stage gear flywheel group for transmission, and the pinion 12c drives the small-thickness and large-diameter flywheel 13c fixedly connected to its bottom to rotate synchronously around the second shaft 10, further increasing the moment of inertia, thereby achieving a larger equivalent mass with a lighter inertia.

[0050] In another embodiment, a third shaft parallel to the first shaft 9 and the second shaft 10 can be added according to the size of the inertia box 8 and the number of stages of the gear flywheel set, and the multi-stage gear flywheel set can be respectively arranged on each shaft to have a larger moment of inertia. In practical applications, more stages of gear flywheel sets can be arranged to meet the use requirements. A flywheel with a small mass and a large surface area can provide sufficient friction damping without the need to additionally arrange a viscous damper.

[0051] When the base 1 is fixedly installed with the controlled structure, a mounting hole is set at the bottom of the base 1, and the base is fixedly installed with the controlled structure through the mounting hole and the fastener. The platform connected to the inverted track can also be directly used as a floor or a water tank and other equipment can be placed on the platform. Its working principle is as follows: the controlled structure vibrates under the excitation of external loads, causing the track member 3 and the track fixing platform 4 connected to it to move, and the movement of the track member 3 drives the rolling member 2 and the active bevel gear 6 to rotate around the fixed shaft 52, and applies a force to the controlled structure through the support column 51, and the active bevel gear 6 drives the driven bevel gear 7 and the first-stage flywheel 11 to rotate around the first shaft 9, and the first-stage flywheel 11 then drives the pinion 12a meshing with the first-stage flywheel 11 on the second shaft 10 to rotate, and the pinion 12a drives the flywheel 13a fixedly connected to it to rotate around the second shaft 10, and so on, thereby driving the next-stage gear flywheel group to transmit.

[0052] In practical engineering applications, by designing the curved track shape at the bottom of the track member 3, almost any form of restoring force-displacement relationship can be obtained, which is not limited to the linear relationship of TMD and the cubic relationship of traditional NES, such as Figure 5 As shown in the figure, the possible track shapes and corresponding stress-displacement relationships in this embodiment, wherein the upper side of the figure is the descending track, the asymmetric track and the bistable track, and the lower side is the force-displacement relationship corresponding to the three tracks. When the force-displacement relationship of the mass damper has both linear and nonlinear characteristics (the degree of nonlinearity is between linear and cubic nonlinearity), its sensitivity to frequency and energy changes is improved.

[0053] like Figure 6 As shown, the shape of the inverted track can be represented by a continuous function h(x), where x is the horizontal distance from the point on the track to the track origin O. The relationship between the angle θ between the tangent line at a certain point on the track and the horizontal direction and the track shape function h(x) is as follows:

[0054]

[0055] like Figure 7 As shown in the figure, the force analysis of the track parts is carried out, where O N is a fixed point (simplified by a fixed axis), u N and v Nare the horizontal displacement and vertical displacement of the track member 3 relative to the fixed point, respectively, and F Normal is the force of the fixed shaft on the track member 3 (direction perpendicular to the tangent of the track shape), m N is the mass of the track member 3 and the track fixing platform 4 connected thereto, and g is the acceleration due to gravity.

[0056] When the track member 3 is stationary, the track is subjected to F Normal and gravity m N g, and the two maintain static equilibrium.

[0057] When the track member 3 moves, except F Normal and m N In addition to g, the orbit is also subject to inertial forces and Since the track member 3 is symmetrically arranged on the track fixing platform, it can be considered that the point of action of the resultant force on the track member 3 is the same as the point of action of gravity. Figure 7 All forces in are plotted at the same point.

[0058] Depend on Figure 7 It can be seen that when the track moves, the force balance equation in the horizontal direction is as follows:

[0059] F Normal sin(θ)=-m N ü N ,

[0060] The vertical force balance equation is:

[0061]

[0062] And according to Figure 6 , we have formulas 4, 5, and 6

[0063] v N =h(u N )

[0064]

[0065] tan(θ)=h′(u N )

[0066] Substituting the above relationship into the force balance equations 2 and 3, we can obtain the equation of motion of the track in the horizontal direction, formula 7:

[0067] ü N m N +F N =0;

[0068] where F N It is the restoring force of track member 3, expressed as formula 8

[0069]

[0070] When the track moves, the restoring force acts in the opposite direction on the track member 3 to pull it back to the static position, which is the same as the effect of a spring, that is, the track member 3 functions as a spring component.

[0071] Track restoring force F N Depending on the track shape h(x), any form of restoring force-displacement relationship can be realized. Figure 8 It is shown in Figure 1 that when h(x) is a quadratic, cubic, or quartic function (a is a constant coefficient), the orbital restoring force F N With orbital displacement u N The relationship between the spring and the control unit is greater than that of the traditional spring components.

[0072] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. An inverted track type inertial mass damper, characterized in that: include: Base, rolling parts, track parts, track fixing platform and inertia device; The track member is arranged at the bottom of the track fixing platform, and an inverted U-shaped curved track is arranged at the bottom of the track member, and the number of the track members is at least three groups; The number of the rolling elements is the same as that of the track elements. The rolling elements are rotatably connected to the base through a support assembly, and each of the rolling elements is respectively in rolling cooperation with a U-shaped curved track at the bottom of each track element. An active bevel gear coaxially rotating with the rolling element is provided at one end of the rolling element. The rolling element is a roller. The active bevel gear is integrally connected to the end of the rolling element. The support assembly includes a group of support columns and a fixed shaft mounted on the top thereof. The support columns are vertically connected to the surface of the base, and the fixed shaft passes through the rolling element and is rotatably mounted with the rolling element. The inertia-capacity device includes an inertia-capacity box and a multi-stage gear flywheel group with sequential meshing transmission. The inertia-capacity box is arranged on the surface of the base. A first shaft is fixedly installed in the inertia-capacity box, and the axis of the first shaft is perpendicular to the surface of the base. The first-stage gear flywheel group includes a driven bevel gear and a first-stage flywheel. The top end of the first shaft extends out of the inertia-capacity box and is rotatably mounted with the driven bevel gear. The driven bevel gear is adapted for transmission with the driving bevel gear, and the bottom of the driven bevel gear is fixedly connected to the first-stage flywheel, which can drive it to rotate synchronously around the first shaft.

2. The inverted track type inertial mass damper according to claim 1, characterized in that: The number of the track members and the number of the rolling members are both four.

3. The inverted track type inertial mass damper according to claim 2, characterized in that: The surface of the base and the bottom surface of the track fixing platform are both rectangular, and the rolling parts and the track parts are symmetrically arranged at the four corners of the base and the track fixing platform respectively.

4. The inverted track type inertial mass damper according to claim 2, characterized in that: The top of the track member is integrally fixedly connected to the bottom of the track fixing platform.

5. The inverted track type inertial mass damper according to claim 1, characterized in that: The gear flywheel sets at other levels all include a pinion and a flywheel fixedly connected to the bottom thereof. The first-level flywheel of the first-level gear flywheel set meshes with the pinion of the second-level gear flywheel set for transmission, and the flywheel of the second-level gear flywheel set meshes with the pinion of the next-level gear flywheel set for transmission. The gear flywheel sets at multiple levels mesh with each other for transmission in a step-by-step manner.

6. The inverted track type inertial mass damper according to claim 5, characterized in that: The inertia capacity device also includes a second shaft arranged in parallel with the first shaft, and the other stages of the gear flywheel group are rotatably mounted on the second shaft and the first shaft in sequence, wherein the second stage gear flywheel group is rotatably mounted on the second shaft.

7. The inverted track type inertial mass damper according to claim 6, characterized in that: The second shaft is fixed in the inertia box, and the axis of the second shaft is perpendicular to the surface of the base.

8. The inverted track type inertial mass damper according to claim 5, characterized in that: The number of the gear flywheel set is four.

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