An inverted track type clutch inertia mass damper

Abstract

The present invention provides an inverted track type clutch inertia mass damper, comprising: a base, a rolling element, a track element, an inertia device and a track fixing platform; the rolling element can be rotatably mounted on the base, and is rotatably mounted with an active bevel gear through a clutch, the track element is arranged at the bottom of the track fixing platform, and an inverted track adapted to roll relative to the rolling element is arranged at the bottom thereof, the inertia 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 a first shaft, the driven bevel gear is adapted to drive with the active bevel gear, and the bottom of the driven bevel gear is fixedly connected with the first-stage flywheel, driving it to rotate synchronously around the first shaft. The mass damper of the present invention utilizes the inertia to provide equivalent mass, greatly reduces the volume of the device, controls the vibration energy transmission path through the clutch, causes the vibration energy to be consumed by friction damping in the inertia, and improves its sensitivity to frequency and energy changes through the track shape design.

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 clutch inertia 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. In contrast to TMD, the stiffness of NES changes with displacement and has a continuously changing natural frequency, so it can resonate with many frequencies, solving the problem of TMD's sensitivity 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 clutch inertia 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 clutch inertia mass damper, which increases the equivalent mass of the mass damper through an inertia box, greatly reduces the physical mass and space requirements of the device, controls the vibration energy transmission path through the clutch, so that the vibration energy is consumed by friction damping in the inertia, 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 clutch inertia mass damper, comprising: a base, a rolling element, a track element, a track fixing platform and an inertia 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, and 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, and one end of the rolling element is provided with an active bevel gear coaxially rotatably mounted therewith through a clutch, wherein the rolling element is fixedly connected to the inner ring of the clutch, and the end face of the active bevel gear is fixedly connected to the outer ring of the clutch, and the inner ring and outer ring of each group of the clutch can and can only rotate synchronously in one of the clockwise direction and the counterclockwise direction, and the synchronous rotation directions of the inner ring and outer ring of each group of the clutch are not completely the same;

[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 parts and the rolling parts are four groups, the surface of the base and the bottom surface of the track fixing platform are both rectangular, the rolling parts and the track parts are symmetrically arranged at the four corners of the base and the track fixing platform, respectively, the top of the track part is integrally fixedly connected to the bottom of the track fixing platform, and in each of the clutches connected to each of the rolling parts, the synchronous rotation direction of the inner ring and the outer ring of two of the clutches is clockwise, and the synchronous rotation direction of the inner ring and the outer ring of the other two clutches is counterclockwise.

[0016] Preferably, the rolling element is a roller.

[0017] 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.

[0018] Preferably, the inner ring of the clutch is sleeved on one end of the rolling element and fixedly connected thereto, an annular groove matching the outer ring of the clutch is provided on the end surface of the active bevel gear, and the outer ring of the clutch is fixedly installed in the annular groove.

[0019] Preferably, the clutch is a ratchet and pawl clutch, an inner ratchet structure is provided on the inner circumference of the outer ring, and at least one pawl matched with the inner ratchet structure is provided on the outer circumference of the inner ring.

[0020] Preferably, the clutch is an overrunning clutch, and a plurality of spaced-apart wedge-shaped grooves are provided on the inner circumferential surface of the outer ring, rollers are filled between the wedge-shaped grooves and the inner ring, a slot hole is opened at the wider end of the wedge-shaped groove, a spring is installed in the slot hole, and a push rod is provided between the spring and the roller, and when the outer ring and the inner ring are relatively stationary, the spring and the push rod cooperate to press the roller tightly into the wedge-shaped groove.

[0021] Preferably, there are four gear flywheel groups, and the two-stage gear flywheel group, the three-stage gear flywheel group and the four-stage gear flywheel group all include a pinion and a flywheel fixedly connected to the bottom thereof, the first-stage flywheel of the first-stage gear flywheel group is meshed with the pinion of the second-stage gear flywheel group for transmission, the flywheel of the second-stage gear flywheel group is meshed with the pinion of the next-stage gear flywheel group for transmission, and so on, and the multi-stage gear flywheel groups are meshed with each other for transmission step by step.

[0022] Preferably, the inertia capacity device also includes a second shaft arranged parallel to the first shaft, the two-stage gear flywheel set and the four-stage gear flywheel set can be rotatably mounted on the second shaft, and the three-stage gear flywheel set can be rotatably mounted on the first shaft.

[0023] 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 fixedly connected to the inner wall of 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.

[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 rolling element is connected to the active bevel gear through the clutch. When the rolling element rotates in the same direction as the synchronous rotation direction of the inner and outer rings of the clutch, and the rolling element speed is greater than the driving bevel gear speed, the rolling element drives the inertia device to rotate synchronously; when the rolling element rotates in the same direction as the synchronous rotation direction of the inner and outer rings of the clutch, and the rolling element speed is less than the driving bevel gear speed or the rolling element rotates in the opposite direction to the synchronous rotation direction of the inner and outer rings of the clutch, the inertia is not affected by the rolling element; since the speed of the inertia device is always less than or equal to the rolling element speed during synchronous rotation, the inertia device can only be driven by the inverted track but cannot reversely drive the inverted track, which is equivalent to energy can only be transmitted along the path of "controlled structure → inverted track → inertia device", and cannot return from the inertia device to the controlled structure, and the flywheel in the inertia device has a small mass and a large surface area, which can provide sufficient friction damping, so that a large amount of energy is consumed during the rotation of the inertia device. Since the synchronous rotation directions of the inner and outer rings of different clutches are not exactly the same, the above energy transmission and consumption process can occur in both reciprocating directions of the track member;

[0029] 5. The structure is simple and easy to install with the controlled structure. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] 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.

[0031] Figure 1 is a schematic diagram of the overall structure of the mass damper in the present invention;

[0032] Figure 2 It is a schematic diagram of the installation of the rolling element, the clutch, the inertia device and the base in the present invention;

[0033] Figure 3 It is a schematic diagram of disassembly and assembly of the clutch, rolling element and active bevel gear in the present invention;

[0034] Figure 4 Schematic diagram of the structure of the ratchet pawl clutch used in the embodiment of the present invention;

[0035] Figure 5 It is a structural schematic diagram of an overrunning clutch used in another embodiment of the present invention;

[0036] Figure 6 It is a front view of the internal structure of the inertia container in the present invention;

[0037] Figure 7 The track shapes and corresponding stress-displacement relationships that can be selected for the track members in the present invention;

[0038] Figure 8 is a schematic diagram of the track shape function of the track member;

[0039] Fig. 9 It is the force analysis diagram of the track parts in static and moving states;

[0040] Fig.10 Figure 2 is the restoring force-displacement relationship diagram corresponding to different track shapes.

[0041] Description of reference numerals:

[0042] 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; 14: clutch; 14a: ratchet and pawl clutch; 14b: overrunning clutch; 141: inner ring; 142: outer ring; 143: inner ratchet structure; 144: pawl; 145: wedge groove; 146: roller; 147: slot; 148: spring; 149: push rod. DETAILED DESCRIPTION

[0043] 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.

[0044] 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.

[0045] 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.

[0046] like Figure 1-3 As shown, the present invention provides an inverted track type clutch inertia mass damper, comprising: a base 1, a rolling member 2, a track member 3, a track fixing platform 4 and an inertia device, wherein the base 1 is fixedly connected to a controlled structure or is a mounting platform for 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, an inverted U-shaped curved track is arranged at the bottom of the track member 3, the controlled structure vibrates under the excitation of an external load, and the track member 3 and the track fixing platform 4 connected thereto are caused to move, wherein the track member 3 and the track fixing platform 4 can replace the additional mass action, the track member 3 can replace the spring component to provide a 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. One end of the rolling element 2 is provided with a driving bevel gear 6 which is coaxially rotatably mounted therewith through a clutch 14, wherein an inner ring 141 of the clutch 14 is sleeved on the outside of one end of the rolling element 2 and fixedly connected thereto, and an annular groove matching the outer ring 142 of the clutch 14 is provided on the end face of the driving bevel gear 6, and the outer ring 142 is fixedly mounted in the annular groove, so that the rolling element 2 can only drive the driving bevel gear 6 to rotate in one direction through the clutch 14.

[0047] 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. 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 matched with 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. In each clutch 14 connected to each rolling element 2, the synchronous rotation direction of the inner ring 141 and the outer ring 142 of two clutches 14 is clockwise, and the synchronous rotation direction of the inner ring 141 and the outer ring 142 of the other two clutches 14 is counterclockwise.

[0048] 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.

[0049] In this embodiment, if Figure 4 As shown, the clutch 14 adopts a ratchet pawl clutch 14a, wherein the inner ring 141 and the outer ring 142 of the two ratchet pawl clutches 14a can only rotate synchronously in the clockwise direction. There are two of them, and an inner ratchet structure 143 is processed on the inner circumference of the outer ring 142. The outer circumference of the inner ring 141 is provided with at least one pawl 144 that is adapted to the inner ratchet structure 143 and can rotate relative to the inner ring 141. Specifically, there are four pawls 144, which are evenly distributed on the outer circumference of the inner ring 141. When the inner ring 141 rotates clockwise relative to the outer ring 142, the pawl 144 pushes the inner ratchet structure 143, so that the inner ring 141 drives the outer ring 142 to rotate; when the inner ring 141 rotates counterclockwise relative to the outer ring 142, the pawl 144 slides over the inner ratchet structure 143, that is, the inner ring 141 has no effect on the outer ring 142 and will not drive it to rotate. In this embodiment, the inner ring 141 and the outer ring 142 of the other two ratchet and pawl clutches 14a can only rotate synchronously counterclockwise, and the arrangement direction of the inner ratchet structure 143 and the pawl 144 is the same as that of the inner ratchet structure 143 and the pawl 144. Figure 4 The ratchet pawl clutch 14a is similar to the clutch operating principle of a bicycle flywheel.

[0050] In another embodiment, if Figure 5As shown, the clutch 14 adopts an overrunning clutch 14b, and the inner ring 141 and the outer ring 142 can only rotate synchronously in the clockwise direction. There are two of them, and a plurality of spaced wedge grooves 145 are provided on the inner circumferential surface of the outer ring 142. Specifically, there are four wedge grooves 145, and the wide end to the narrow end of the wedge grooves 145 are arranged along the clockwise direction of the inner surface of the outer ring 142. Rollers 146 are filled between the wedge grooves 145 and the outer surface of the inner ring 141. A slot hole 147 is opened at the wider end of the wedge groove 145, and a spring 148 is installed in the slot hole 147. A push rod 149 is provided between the spring 148 and the roller 146. The diameter of roller 146 is the same as the middle height of the space between wedge-shaped groove 145 and inner ring 141. When outer ring 142 and inner ring 141 are relatively stationary, spring 148 and push rod 149 cooperate to press roller 146 against the middle of wedge-shaped groove 145. When inner ring 141 rotates clockwise relative to outer ring 142, roller 146 is driven to move to the narrower end of the wedge-shaped space. At this time, roller 146 is stuck between the inner and outer rings, and rolling element 2 and inner ring 141 rotate as a whole, thereby driving outer ring 142 to rotate; when inner ring 141 rotates counterclockwise relative to outer ring 142, roller 146 moves to the wider end of the wedge-shaped space. At this time, there is a gap between roller 146 and the inner and outer rings, and inner ring 141 has no effect on outer ring 142 and will not drive it to rotate. In this embodiment, the inner ring 141 and the outer ring 142 of the other two overrunning clutches 14b can only rotate synchronously counterclockwise, and the arrangement direction of the wedge groove 145, the slot hole 147, the spring 148 and the push rod 149 is the same as that of the inner ring 141 and the outer ring 142 of the other two overrunning clutches 14b. Figure 5 The working principle of the overrunning clutch 14b is similar to the overrunning clutch of a motorcycle.

[0051] like Figure 3 and 6As shown, the rolling element 2 is connected to the active bevel gear 6 through the clutch 14. When the rolling element 2 rotates in the same direction as the synchronous rotation direction of the inner and outer rings of the clutch 14, and the speed of the rolling element 2 is greater than the speed of the active bevel gear 6, the rolling element 2 drives the inertia device to rotate synchronously; when the rolling element 2 rotates in the same direction as the synchronous rotation direction of the inner and outer rings of the clutch 14, and the speed of the rolling element 2 is less than the speed of the active bevel gear 6, or the rolling element 2 rotates in the opposite direction to the synchronous rotation direction of the inner and outer rings of the clutch 14, the inertia device is not affected by the rolling element 2; since the speed of the inertia device is always less than or equal to the speed of the rolling element 2 during synchronous rotation, the inertia device can only be driven by the inverted U-shaped track and cannot reversely drive the track member 3, which is equivalent to that the energy can only be transmitted along the path of "controlled structure → inverted track → inertia device", and cannot return from the inertia device to the controlled structure. Since the synchronous rotation directions of the inner and outer rings of different clutches 14 in the present invention are not exactly the same, the above energy transmission process can occur in both reciprocating directions of the track member 3. The present invention uses the clutch 14 to transmit the vibration energy from the controlled structure to the inertia device and cannot return to the controlled structure from the inertia device. The clutch 14 is not limited to the above two structural forms, and other types of overrunning clutches (such as wedge type, support type), ratchet pawl clutches (external meshing type, internal meshing type), hydraulic clutches, etc. can also be used.

[0052] 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 rod 9 and the second shaft rod 10 are fixedly installed in the inertia box 8 and are parallel to each other. The axes of the first shaft rod 9 and the second shaft rod 10 are perpendicular to the surface of the base 1. The top of the first shaft rod 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 rod 9 extends out of the inertia box 8 and is 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 rod 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 rod 9 or the second shaft rod 10 through the driving bevel gear 6 and the driven bevel gear 7.

[0053] 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 sequence, 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 disc-shaped parts with small mass and large surface area, which have a large moment of inertia, and the inertial force can replace the inertial force of mass motion. Therefore, the inertia device can provide equivalent mass, thereby reducing the physical mass and space requirements of the device. At the same time, it can provide sufficient friction damping, so that a large amount of energy is consumed during the rotation of the inertia device, so that the mass damper does not need to have a large mass to have a good vibration reduction effect.

[0054] 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.

[0055] 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 one On the side of the first-stage flywheel 11 away from the driven bevel gear 7, the third-stage gear flywheel group and the first-stage gear flywheel group do not contact each other, the fourth-stage gear flywheel group can be rotatably installed on the lower end of the second shaft rod 10, the fourth-stage gear flywheel group and the second-stage gear flywheel group do not contact each other, 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, the pinion 12c drives the small-thickness and large-diameter flywheel 13c fixedly connected to its bottom to rotate synchronously around the second shaft rod 10, further increasing the moment of inertia, thereby achieving a larger equivalent mass with a lighter inertia.

[0056] 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.

[0057] 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, the track member 3 moves to drive the rolling member 2 to rotate around the fixed axis 52, and applies a force to the controlled structure through the support column 51, the rolling member 2 drives the active bevel gear 6 to rotate around the fixed axis 52 in a specific direction through the clutch 14, the active bevel gear 6 drives the driven bevel gear 7 and the first-stage flywheel 11 to rotate around the first shaft 9, the first-stage flywheel 11 then drives the pinion 12a on the second shaft 10 that is meshed with the first-stage flywheel 11 to rotate, 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.

[0058] 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 7 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.

[0059] like Figure 8 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:

[0060]

[0061] like Fig. 9 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 vN are the horizontal displacement and vertical displacement of the track member 3 relative to the fixed point, respectively, Normal is the force of the fixed axis 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.

[0062] 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.

[0063] 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. Fig. 9 All forces in are plotted at the same point.

[0064] Depend on Fig. 9 It can be seen that when the track moves, the force balance equation in the horizontal direction is as follows:

[0065]

[0066] The force balance equation in the vertical direction is as follows:

[0067]

[0068] And according to Figure 8 , we have formulas 4, 5, and 6

[0069] v N =h(u N )

[0070]

[0071] tan(θ)=h′(u N )

[0072] Substituting the above relationship into the force balance equations 2 and 3, we can get the equation of motion of the track in the horizontal direction, formula 7, as follows:

[0073]

[0074] where F N It is the restoring force of the track member 3, which is expressed by the following formula 8

[0075]

[0076] 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.

[0077] Track restoring force F N Depending on the track shape h(x), any form of restoring force-displacement relationship can be realized. Fig.10 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.

[0078] 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 clutch inertia 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, both being four groups. The rolling elements are rotatably connected to the base through a support assembly, and each of the rolling elements is respectively rollingly matched with a U-shaped curved track at the bottom of each track element. One end of each of the rolling elements is provided with an active bevel gear coaxially rotatably mounted therewith through a clutch, wherein the rolling element is fixedly connected to the inner ring of the clutch, and the end face of the active bevel gear is fixedly connected to the outer ring of the clutch. The inner ring and outer ring of each group of the clutch can and can only rotate synchronously in one of the clockwise direction and the counterclockwise direction, and the synchronous rotation directions of the inner ring and outer ring of each group of the clutch are not completely the same; The surface of the base and the bottom surface of the track fixing platform are both rectangular, the rolling element and the track element are symmetrically arranged at the four corners of the base and the track fixing platform respectively, the top of the track element is integrally fixedly connected with the bottom of the track fixing platform, and the synchronous rotation direction of the inner ring and the outer ring of two of the clutches connected to each of the rolling elements is clockwise, and the synchronous rotation direction of the inner ring and the outer ring of the other two clutches is counterclockwise; the inner ring of the clutch is sleeved on one end of the rolling element and fixedly connected thereto, an annular groove adapted to the outer ring of the clutch is provided on the end surface of the active bevel gear, and the outer ring of the clutch is fixedly installed in the annular groove; 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.

2. The inverted track type clutch inertia mass damper according to claim 1, characterized in that: The rolling element is a roller.

3. The inverted track type clutch inertia mass damper according to claim 2, characterized in that: 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 surface of the base, and the fixed shaft penetrates the rolling element and is rotatably mounted thereon.

4. The inverted track type clutch inertia mass damper according to claim 1, characterized in that: The clutch is a ratchet-pawl clutch, an inner ratchet structure is arranged on the inner circumference of the outer ring, and at least one pawl matched with the inner ratchet structure is arranged on the outer circumference of the inner ring.

5. The inverted track type clutch inertia mass damper according to claim 1, characterized in that: The clutch is an overrunning clutch, and a plurality of spaced wedge-shaped grooves are provided on the inner circumferential surface of the outer ring, rollers are filled between the wedge-shaped grooves and the inner ring, a slot hole is opened at the wider end of the wedge-shaped groove, a spring is installed in the slot hole, and a push rod is provided between the spring and the roller, and when the outer ring and the inner ring are relatively stationary, the spring and the push rod cooperate to press the roller tightly into the wedge-shaped groove.

6. The inverted track type clutch inertia mass damper according to claim 1, characterized in that: There are four gear flywheel groups. The two-stage gear flywheel group, the three-stage gear flywheel group and the four-stage gear flywheel group all include a pinion and a flywheel fixedly connected to the bottom thereof. The first-stage flywheel of the first-stage gear flywheel group is meshed with the pinion of the second-stage gear flywheel group for transmission. The flywheel of the second-stage gear flywheel group is meshed with the pinion of the next-stage gear flywheel group for transmission. And so on. The multi-stage gear flywheel groups are meshed with each other for transmission step by step.

7. The inverted track type clutch inertia mass damper according to claim 6, characterized in that: The inertia capacity device also includes a second shaft rod arranged in parallel with the first shaft rod, the second-stage gear flywheel set and the fourth-stage gear flywheel set can be rotatably mounted on the second shaft rod, and the third-stage gear flywheel set can be rotatably mounted on the first shaft rod.

8. The inverted track type clutch inertia mass damper according to claim 7, characterized in that: The inertia container device also includes an inertia container box, which is fixedly arranged on the surface of the base, and the driven bevel gear is located outside the inertia container box. The first shaft rod and the second shaft rod are fixedly connected to the inner wall of the inertia container box, and the top end of the first shaft rod extends out of the inertia container box and is rotatably mounted with the driven bevel gear. The axes of the first shaft rod and the second shaft rod are perpendicular to the surface of the base.

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