CN114775828A - Inverted rail type inerter mass damper - Google Patents

Inverted rail type inerter mass damper Download PDF

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Publication number
CN114775828A
CN114775828A CN202210602351.4A CN202210602351A CN114775828A CN 114775828 A CN114775828 A CN 114775828A CN 202210602351 A CN202210602351 A CN 202210602351A CN 114775828 A CN114775828 A CN 114775828A
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flywheel
track
bevel gear
rolling
gear
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Chinese (zh)
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王菁菁
郑雨强
王殿俊
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Guangzhou University
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Guangzhou University
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    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04B—GENERAL BUILDING CONSTRUCTIONS; WALLS, e.g. PARTITIONS; ROOFS; FLOORS; CEILINGS; INSULATION OR OTHER PROTECTION OF BUILDINGS
    • E04B1/00—Constructions in general; Structures which are not restricted either to walls, e.g. partitions, or floors or ceilings or roofs
    • E04B1/62—Insulation or other protection; Elements or use of specified material therefor
    • E04B1/92—Protection against other undesired influences or dangers
    • E04B1/98—Protection against other undesired influences or dangers against vibrations or shocks; against mechanical destruction, e.g. by air-raids
    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
    • E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
    • E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
    • E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
    • E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
    • E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
    • E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
    • E04H9/0215—Bearing, supporting or connecting constructions specially adapted for such buildings involving active or passive dynamic mass damping systems
    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
    • E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
    • E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
    • E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
    • E04H9/023—Bearing, supporting or connecting constructions specially adapted for such buildings and comprising rolling elements, e.g. balls, pins
    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
    • E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
    • E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
    • E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
    • E04H9/0237—Structural braces with damping devices

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Environmental & Geological Engineering (AREA)
  • Business, Economics & Management (AREA)
  • Emergency Management (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

The invention provides an inverted orbit type inerter mass damper, which comprises: the device comprises a base, rolling parts, a rail part, an inertial container device and a rail fixing platform; the rolling part is rotatably installed on the surface of the base through the supporting component, one end of the rolling part is provided with a driving bevel gear which coaxially rotates with the rolling part, the track part is arranged at the bottom of the track fixing platform, the bottom of the track part is provided with a U-shaped track which is matched with the rolling part in an inverted mode, the track part rolls relative to the curved surface track, the inertia containing device comprises a multi-stage gear flywheel set, the multi-stage gear flywheel set comprises a driven bevel gear and a one-stage flywheel, the driven bevel gear is rotatably installed on a first shaft rod and is in adaptive transmission with the driving bevel gear, the bottom of the driven bevel gear is fixedly connected with the one-stage flywheel, and the driven bevel gear is driven to synchronously rotate around the first shaft rod. The mass damper provides equivalent mass through the inertial capacitance, greatly reduces the device volume, obtains a force-displacement relation with linear and nonlinear characteristics through track design, and improves the sensitivity to frequency and energy changes.

Description

Inverted rail type inerter mass damper
Technical Field
The invention relates to the technical field of vibration control, energy dissipation and shock absorption, in particular to an inverted track type inerter mass damper.
Background
In order to ensure the safety of the engineering structure under the action of extreme loads (such as wind load, earthquake and the like), a structure control technology is developed. The structure control technology is a technology for reducing structure vibration and accelerating energy consumption by adding a control device on a main structure or changing the characteristics of the main structure (such as changing structure rigidity, damping and the like).
Among them, Tuned Mass Damper (TMD) is a structural control device attached to the main structure. The TMD is comprised of an additional mass, a spring member, and a damping member, the additional mass being connected to the main structure through the spring member and the damping member. The TMD is generally arranged at a place where the main body structure vibrates greatly (such as the top of a building structure), the additional mass is smaller than the mass of the main body structure, when the natural vibration frequency of the TMD is tuned with the main natural vibration frequency of the main body structure, the TMD and the main body structure form a resonance mechanism, the TMD vibrates violently, and the vibration of the main body structure is reduced rapidly through self damping energy consumption. Typically, the additional mass of the TMD is sized and the desired natural frequency of vibration is achieved by adjusting the stiffness of the spring member. The device is widely applied to high-rise structures, is used for reducing the response of the structures under the action of wind load so as to achieve the purpose of improving the safety and comfort of the structures, can be realized by using a pendulum bob and the like in the TMD besides directly using spring type components, and both the purposes of providing linear stiffness with certain magnitude and enabling the TMD natural vibration frequency to meet the design requirement.
TMD belongs to mass dampers, and the larger the mass is, the better the vibration reduction effect is. In practical application, the composite material not only occupies a large amount of space and affects the use function of a building, but also has adverse effect on a main structure load-bearing member. In addition, the spring component in the TMD is a linear spring, so that the natural frequency of the TMD remains unchanged after the additional mass and spring stiffness of the TMD are determined. However, when the natural vibration frequency of the main structure changes (for example, the mass of a building changes with the use function, and the rigidity changes with the building settlement, structural damage and temperature), the TMD and the main structure are no longer tuned, an effective resonance mechanism cannot be formed between the TMD and the main structure, the vibration damping performance of the TMD is greatly degraded, and even the structural response is increased. In addition, when the TMD works, violent vibration occurs, vibration energy is consumed through the TMD damping part, the energy consumption mode of the damping part is single, the energy consumption capacity is limited, the vibration energy is often not consumed enough, in order to ensure the energy consumption efficiency, a damping device (such as a viscous damper) needs to be additionally arranged, the device size and the installation difficulty are further increased due to the additionally arranged damper, the vibration of the TMD is hindered due to the excessively large viscous damping, and the energy consumption rate is reduced.
Nonlinear Energy Sink (NES) is a kind of structural control device similar to TMD, and is still in the stage of basic research. The NES is composed of an additional mass, a spring member and a damping member similarly to the TMD, but the spring member of the NES is a nonlinear spring, i.e., the restoring force generated by the nonlinear spring varies nonlinearly with the displacement of the additional mass. The most commonly used NES uses a cubic spring component, i.e. the generated restoring force is proportional to the third power of NES displacement. FIG. 1 compares TMD (Linear) and NES (cubic non-Linear) spring restoring force versus added mass displacement. In contrast to TMD, NES varies in stiffness with displacement and has a continuously varying natural frequency, and therefore can resonate with numerous frequencies, solving the problem of TMD sensitivity to frequency variations.
The components of the NES apparatus typically include additional masses, spring packs, slide rails, fixtures, and baffles, among others. The additional mass moves along the slide rail, the baffle plates are installed at two ends of the slide rail as safety measures, and the spring group is connected with the main body structure along the direction vertical to the motion direction of the additional mass. It is worth noting that to achieve the cubic force-displacement relationship of NES, the spring assembly is kept at the original length (i.e., is not stretched) when the additional mass is at rest (i.e., when the spring assembly is perpendicular to the direction of motion of the additional mass), and this arrangement enables the spring assembly to generate approximately cubic restoring force in the direction of motion of the additional mass, which is equivalent to a cubic spring in a theoretical model.
NES is not sensitive to frequency changes, but is extremely sensitive to energy changes (load size). When the structure is subjected to a small load, the NES has small vibration and small corresponding rigidity, namely the NES has small natural vibration frequency when the input energy is small; conversely, when the load is high, NES vibrates greatly, and its corresponding stiffness is continuously maintained at a large value, i.e., the natural frequency of NES is large when the input energy is large. In both cases, the natural frequency of NES is much different from that of the main structure, and it is difficult to form an effective resonance mechanism, resulting in degradation of vibration damping capability.
In addition, the NES technology still does not solve the problems of large size, single energy consumption mode and weak energy consumption capability of the TMD device. In fact, since the implementation of the non-linear spring is more complicated than the linear spring, the mounting space of the NES is even larger than the TMD of the same mass.
In view of the above, the present invention provides an inverted-track type inertance-mass damper to overcome the above-mentioned problems of the prior art.
Disclosure of Invention
The invention aims to provide an inverted rail type inerter mass damper, which increases the equivalent mass of the mass damper through an inerter box, greatly reduces the physical mass and space requirements of a device, can obtain almost any form of restoring force-displacement relation through designing the shape track of a U-shaped curved surface rail, and improves the sensitivity to frequency and energy change when the force-displacement relation of the mass damper has linear and nonlinear characteristics.
The invention provides an inverted orbit type inerter mass damper, which comprises: the device comprises a base, rolling parts, a track part, a track fixing platform and an inertial container device;
the track pieces are arranged at the bottom of the track fixing platform, inverted U-shaped curved surface tracks are arranged at the bottom of the track pieces, and the number of the track pieces is at least three;
the rolling pieces and the tracks have the same number, the rolling pieces are rotatably connected with the base through supporting components, each rolling piece is respectively matched with the U-shaped curved surface track at the bottom of each track piece in a rolling manner, and one end of each rolling piece is provided with a driving bevel gear which coaxially rotates with the rolling piece;
the inertia container comprises a plurality of stages of gear flywheel sets which are sequentially meshed for transmission, wherein each stage of gear flywheel set comprises a driven bevel gear and a stage of flywheel, the driven bevel gear is rotatably installed at the end part of a first shaft rod and is in adaptive transmission with the driving bevel gear, and the bottom of the driven bevel gear is fixedly connected with the stage of flywheel and can drive the stage of flywheel to synchronously rotate around the first shaft rod.
Preferably, the number of the rail members and the number of the rolling members are four.
Preferably, the surface of the base and the bottom surface of the track fixing platform are rectangular, and the rolling members and the track members are symmetrically arranged at four corners of the base and the track fixing platform respectively.
Preferably, the top of the rail member is integrally and fixedly connected with the bottom of the rail fixing platform.
Preferably, the rolling member is a roller, and the drive bevel gear is integrally connected with an end of the rolling member.
Preferably, the support assembly includes a set of support posts and a fixed shaft mounted on the top of the support posts, the support posts are vertically connected with the surface of the base, and the fixed shaft penetrates through the rolling member and is rotatably mounted on the rolling member.
Preferably, the other stages of the gear flywheel sets comprise pinions and flywheels fixedly connected with the bottoms of the pinions, the first-stage flywheels of the first-stage gear flywheel sets are in meshing transmission with the pinions of the second-stage gear flywheel sets, the flywheels of the second-stage gear flywheel sets are in meshing transmission with the pinions of the next-stage gear flywheel sets, and the steps are repeated to realize the step-by-step meshing transmission among the gear flywheel sets.
Preferably, the inertia container device further comprises a second shaft rod arranged in parallel with the first shaft rod, and the other stages of the flywheel gear sets are sequentially and rotatably mounted on the second shaft rod and the first shaft rod, wherein the second stage flywheel gear set is rotatably mounted on the second shaft rod.
Preferably, the inerter device further comprises an inerter tank, the inerter tank is fixedly arranged on the surface of the base, the driven bevel gear is located outside the inerter tank, the first shaft lever and the second shaft lever are fixed in the inerter tank, the top end of the first shaft lever extends out of the inerter tank and is rotatably mounted with the driven bevel gear, and the axes of the first shaft lever and the second shaft lever are perpendicular to the surface of the base.
Preferably, the number of the flywheel gear sets is four.
Compared with the prior art, the invention has the following beneficial effects:
1. by designing the shape of the curved track, almost any form of restoring force-displacement relation can be obtained, the relation is not limited to the linear relation of TMD and the cubic relation of the traditional NES, and when the force-displacement relation of the mass damper has the characteristics of linearity and nonlinearity (the nonlinearity degree is between the linearity and the cubic nonlinearity), the sensibility of the mass damper to the frequency and energy change is improved;
2. the track piece is used as an additional mass and a spring part for replacing the mass damper, so that the track piece not only plays the function of the additional mass, but also can provide restoring force similar to the spring part, and the restoring force has the characteristics of linearity and nonlinearity;
3. the inertia force generated by rotation of the inertia container device can replace the inertia force generated by mass motion, the inertia container device can be used as an equivalent mass, and compared with mass dampers such as TMD (tuned mass transfer) and NES (neutral moving System), the mass of the mass damper is greatly reduced, and the space requirement of the device is reduced;
4. simple structure, convenient and controlled structure cooperation installation.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the embodiments or the prior art descriptions will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained by those skilled in the art without creative efforts.
FIG. 1 is a graph of force-displacement relationship of TMD and NES in the prior art;
FIG. 2 is a schematic view of the overall structure of the mass damper of the present invention;
FIG. 3 is a schematic view of the rolling member, the inerter and the base of the present invention;
FIG. 4 is a front view of the internal structure of the inerter tank of the present invention;
FIG. 5 is an alternative rail shape and stress-displacement relationship for the rail member of the present invention;
FIG. 6 is a schematic view of a track member as a function of track shape;
FIG. 7 is a force analysis diagram of the rail member in a static state and a moving state;
FIG. 8 is a graph of the restoring force versus displacement for different track shapes.
Description of reference numerals:
1: a base; 2: a rolling member; 3: a rail member; 4: a rail fixing platform; 5: a support assembly; 51: a support column; 52: a fixed shaft; 6: a drive bevel gear; 7: a driven bevel gear; 8: an inerter tank; 9: a first shaft lever; 10: a second shaft lever; 11: a primary flywheel; 12. 12a, 12b, 12 c: a pinion gear; 13. 13a, 13b, 13 c: a flywheel.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the following embodiments, and it should be understood that the described embodiments are some, but not all, embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be considered as limiting the present invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, features defined as "first" and "second" may explicitly or implicitly include one or more of the described features. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise. Furthermore, the terms "mounted," "connected," and "connected" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in a specific case to those of ordinary skill in the art.
As shown in fig. 2, 3 and 4, the present invention provides an inverted orbital inertial mass damper comprising: the base 1 is fixedly connected with a controlled structure or is an installation platform of the controlled structure, the rolling members 2 are rotatably installed on the surface of the base 1 through supporting components 5, the track members 3 are installed at the bottom of the track fixing platform 4, inverted U-shaped curved tracks are arranged at the bottom of the track members 3, the controlled structure is excited by external loads to vibrate and can cause the track members 3 and the track fixing platform 4 connected with the track members 3 to move, the track members 3 and the track fixing platform 4 can replace additional masses, the track members 3 can replace spring components to provide restoring force, the track members 3 move to drive the rolling members 2 to rotate relative to the supporting components 5, and acting force is applied to the controlled structure through the supporting components 5. One end of the rolling member 2 is provided with a driving bevel gear 6 which coaxially rotates with the rolling member, and the end face of the driving bevel gear 6 is integrally and fixedly connected with the end face of the rolling member 2.
Specifically, the number of the rolling members 2 is at least three, in this embodiment, the rolling members 2 are four rolling wheels, the surface of the base 1 is rectangular, each rolling member 2 is rotatably mounted at four corners of the surface of the base 1 through the supporting components 5, and each rolling member 2 is symmetrical with respect to the axis of the base 1. The top of the track member 3 is fixedly connected with the bottom of the track fixing platform 4, the number of the track members 3 is the same as that of the rolling members 2, and the positions of the track members 3 correspond to those of the rolling members 2, so that each track member 3 can be respectively matched with each rolling member 2 positioned below the track member, and each rolling member 2 can roll relative to the inverted U-shaped curved track at the bottom of the track member 3.
In this embodiment, the supporting assembly 5 comprises a set of supporting pillars 51 arranged in parallel and a fixing shaft 52 erected between the tops of the two supporting pillars 51, wherein the supporting pillars 51 are fixedly connected to the surface of the base 1, the rolling element 2 is rotatably fitted to the fixing shaft 52, specifically, the axis of the fixing shaft 52 is parallel to the surface of the base 1, and the fixing shaft 52 penetrates through the roller and the drive bevel gear 6 simultaneously along the axial direction of the roller, so that the roller and the drive bevel gear 6 can rotate around the axes thereof under the external force.
The inerter device comprises an inerter box 8 and a multi-stage gear flywheel set, the inerter box 8 is arranged on the surface of the base 1, a first shaft rod 9 and a second shaft rod 10 which are parallel to each other are fixedly arranged in the inerter box 8, the axes of the first shaft rod 9 and the second shaft rod 10 are perpendicular to the surface of the base 1, and the top end of the first shaft rod 9 extends out of the inerter box 8. Wherein, one-level gear flywheel group includes driven bevel gear 7 and rather than the one-level flywheel 11 of bottom fixed connection, and the top of primary shaft 9 is stretched out and is rotatable the installation with driven bevel gear 7 adaptation in by being used for containing the case 8, and driven bevel gear 7 meshes the transmission with the 6 adaptations of drive bevel gear, and then drives and rotates around primary shaft 9 with the one-level flywheel 11 of 7 bottom fixed connection of driven bevel gear, and one-level flywheel 11 then drives other-level gear flywheel group transmissions. The rotation of the rolling member 2 about the horizontally arranged fixed shaft 52 can be converted into the rotation of the multi-stage geared flywheel set about the vertically arranged first shaft lever 9 or second shaft lever 10 by the drive bevel gear 6 and the driven bevel gear 7.
The other various-stage gear flywheel sets comprise small gears 12 and small-thickness large-diameter flywheels 13 fixedly connected with the bottoms of the small gears 12, the other various-stage gear flywheel sets are sequentially and rotatably arranged on the second shaft lever 10 and the first shaft lever 9, wherein the small gears 12 of the second-stage gear flywheel sets arranged on the second shaft lever 10 are in meshing transmission with the first-stage flywheels 11 of the first-stage gear flywheel sets, the flywheels 13 of the second-stage gear flywheel sets are in meshing transmission with the small gears 12 of the next-stage gear flywheel sets arranged on the first shaft lever 9, and so on, the first-stage flywheels 11 and the flywheels 13 are light, light and thin large-diameter disc-shaped members with larger rotational inertia force and larger rotational inertia force capable of replacing inertia force of mass movement, therefore, the inertia capacity device can provide equivalent mass, physical mass and space requirements of the device are reduced, and the mass damper does not need to have larger mass, has good vibration damping effect.
In this embodiment, the inerter box 8 is fixedly disposed on the surface of the base 1 and located below the rolling members 2 and the driving bevel gear 6, and inerter devices are disposed below each of the rolling members 2 and the driving bevel gear 6, and each inerter device can be respectively matched with each of the driving bevel gears 6, so that the larger rotational inertia thereof is utilized to provide equivalent mass, thereby reducing the physical mass and space requirements of the device.
As shown in fig. 4, in the present embodiment, the number of the flywheel sets is four, wherein the first flywheel set includes a driven bevel gear 7 and a first flywheel 11 rotatably mounted on the top of the first shaft 9, the second flywheel set is rotatably mounted on the second shaft 10, a pinion 12a of the second flywheel set is in meshing transmission with the first flywheel 11 mounted on the first shaft 9, a flywheel 13a fixedly connected to the bottom of the pinion 12a is in meshing transmission with a pinion 12b of the third flywheel set rotatably mounted on the first shaft 9, the third flywheel set is mounted on the side of the first flywheel 11 away from the driven bevel gear 7, the third flywheel set is not in contact with the first flywheel set, the fourth flywheel set is rotatably mounted on the lower end of the second shaft 10, and the fourth flywheel set is not in contact with the second flywheel set, the pinion 12c of the four-level gear flywheel set is in meshing transmission with the flywheel 13b of the three-level gear flywheel set, the pinion 12c drives the flywheel 13c which is fixedly connected with the bottom of the pinion to synchronously rotate around the second shaft rod 10, the rotational inertia is further increased, and therefore large equivalent mass is achieved through light inertia capacity.
In another embodiment, a third shaft lever parallel to the first shaft lever 9 and the second shaft lever 10 can be added according to the size of the inertia container 8 and the number of stages of the flywheel sets, and the flywheel sets of the multi-stage gears are respectively arranged on the shaft levers to enable the flywheel sets to have larger rotational inertia. In practical application, more gear flywheel sets can be arranged to meet the use requirement. Through the flywheel with small mass and large surface area, sufficient friction damping can be provided, and a viscous damper does not need to be additionally arranged.
When the base 1 is fixedly installed with the controlled structure, the bottom of the base 1 is provided with an installation hole, and the base is fixedly installed with the controlled structure through the installation hole and a fastener. The platform connected with the inverted track can also be directly used as a floor slab or used for placing equipment such as a water tank and the like on the platform. The working principle is as follows: the controlled structure is excited by external load to vibrate, so that the track piece 3 and the track fixing platform 4 connected with the track piece are caused to move, the track piece 3 moves to drive the rolling piece 2 and the driving bevel gear 6 to rotate around the fixing shaft 52, acting force is applied to the controlled structure through the supporting column 51, the driving bevel gear 6 drives the driven bevel gear 7 and the first-stage flywheel 11 to rotate around the first shaft rod 9, the first-stage flywheel 11 further drives the pinion 12a which is arranged on the second shaft rod 10 and meshed with the first-stage flywheel 11 to rotate, the pinion 12a drives the flywheel 13a fixedly connected with the pinion to rotate around the second shaft rod 10, and the rest is done in the same way, and then the next-stage gear flywheel set is driven to transmit.
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, and is not limited to the linear relationship of TMD and the cubic relationship of the conventional NES, as shown in fig. 5, which is the possible track shape and the corresponding stress-displacement relationship in the present embodiment, wherein the upper diagram is respectively a descending track, an asymmetric track and a bistable track, and the lower diagram is a corresponding force-displacement relationship of the three tracks. When the force-displacement relation of the mass damper has linear and nonlinear characteristics (the nonlinear degree is between linear and cubic nonlinearity), the sensitivity of the mass damper to frequency and energy changes is improved.
As shown in fig. 6, the shape of the inverted track can be represented by a continuous function h (x), where x is the horizontal distance of a point on the track from the track origin O. The relationship between the angle theta between the tangent line of a certain point of the track and the horizontal direction and the track shape function h (x) is shown in formula 1
Figure BDA0003669813620000101
Force analysis of the rail member, shown in FIG. 7, wherein ONFor fixing points (simplified by fixed axles), uNAnd vNHorizontal and vertical displacements of the orbital member 3 with respect to a fixed point, respectively, FNormalM is the force of the fixed shaft on the rail member 3 (the direction is perpendicular to the tangent of the rail shape), mNThe mass of the rail member 3 and the rail fixing platform 4 connected with the rail member is g, and g is gravity acceleration.
When the rail member 3 is stationary, the rail is subjected to FNormalAnd gravity mNg, and both are kept in static equilibrium.
When the rail member 3 moves, except for FNormalAnd mNg, the rail is also subjected to inertial forces
Figure BDA0003669813620000102
And
Figure BDA0003669813620000103
since the track member 3 is symmetrically arranged on the track fixing platform, the acting point of the resultant force applied to the track member 3 can be considered to be the same as the acting point of the gravity, so all the forces in fig. 7 are drawn at the same point.
As can be seen from fig. 7, when orbiting, the force balance equation in the horizontal direction is shown as equation 2:
FNormalsin(θ)＝-mNüN，
equation 3 for force balance in the vertical direction:
Figure BDA0003669813620000111
and according to FIG. 6, there are equations 4, 5, 6
vN＝h(uN)
Figure BDA0003669813620000112
tan(θ)＝h′(uN)
By substituting the above relationship into the force balance equations 2 and 3, equation 7 of motion of the orbit in the horizontal direction can be obtained as
üNmN+FN＝0；
Wherein FNI.e. the restoring force of the rail member 3, the expression is formula 8
Figure BDA0003669813620000113
When the track is moved, this restoring force acts against the track element 3, pulling it back into the rest position, in the same way as a spring, i.e. the track element 3 functions as a spring element.
Track restoring force FNIn relation to the track shape h (x), an arbitrary form of restoring force-displacement relationship can be achieved. FIG. 8 shows the orbital recovery force F when h (x) is a quadratic, cubic, or quartic function (a is a constant coefficient), respectivelyNWith orbital displacement uNHas greater flexibility than the traditional spring component.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and these modifications or substitutions do not depart from the spirit of the corresponding technical solutions of the embodiments of the present invention.

Claims (10)

1. An inverted orbital inertial mass damper, comprising: the device comprises a base, rolling parts, a track part, a track fixing platform and an inertial container device;
the track pieces are arranged at the bottom of the track fixing platform, inverted U-shaped curved surface tracks are arranged at the bottom of the track pieces, and the number of the track pieces is at least three;
the rolling pieces and the tracks have the same number, the rolling pieces are rotatably connected with the base through supporting components, each rolling piece is respectively matched with the U-shaped curved surface track at the bottom of each track piece in a rolling manner, and one end of each rolling piece is provided with a driving bevel gear which coaxially rotates with the rolling piece;
the inertia container device comprises a plurality of stages of gear flywheel sets which are sequentially meshed for transmission, wherein each stage of gear flywheel set comprises a driven bevel gear and a stage of flywheel, the driven bevel gear is rotatably arranged at the end part of the first shaft rod and is in adaptive transmission with the driving bevel gear, and the bottom of the driven bevel gear is fixedly connected with the stage of flywheel and can drive the stage of flywheel to synchronously rotate around the first shaft rod.
2. The inverted orbital inertance mass damper of claim 1, wherein the number of the orbital members and the rolling members are four.
3. The inverted orbital inerter mass damper of claim 2, wherein the surface of the base and the bottom surface of the orbital fixed platform are rectangular and the rolling members and the orbital members are symmetrically disposed at four corners of the base and the orbital fixed platform, respectively.
4. The inverted rail inertance mass damper of claim 2, wherein the top of the rail member is integrally fixedly connected to the bottom of the rail fixed platform.
5. The inverted rail inertial mass damper according to any one of claims 1 to 4, wherein the rolling member is a roller, and the drive bevel gear is integrally connected to an end of the rolling member.
6. The inverted orbital inertance mass damper according to claim 5, wherein the support assembly comprises a plurality of support posts vertically attached to the base surface and a stationary shaft mounted on top of the support posts, the stationary shaft extending through the rolling member and rotatably mounted thereto.
7. The inverted-orbit inerter mass damper according to claim 1, wherein the other stages of the gear flywheel sets each comprise a pinion and a flywheel fixedly connected with the bottom of the pinion, the first stage flywheel of the first stage gear flywheel set is in meshing transmission with the pinion of the second stage gear flywheel set, the flywheel of the second stage gear flywheel set is in meshing transmission with the pinion of the next stage gear flywheel set, and so on, the multistage gear flywheel sets are in progressive meshing transmission.
8. The inverted orbital inertia mass damper according to claim 7, further comprising a second shaft arranged parallel to the first shaft, the other stages of the flywheel gear sets being rotatably mounted on the second shaft and the first shaft in turn, wherein the second stage of the flywheel gear sets is rotatably mounted on the second shaft.
9. The inverted-orbit inertial mass damper according to claim 8, wherein the inertial container device further comprises an inertial container fixedly arranged on the surface of the base, the driven bevel gear is arranged outside the inertial container, the first shaft lever and the second shaft lever are fixed in the inertial container, the top end of the first shaft lever extends out of the inertial container and is rotatably mounted with the driven bevel gear, and the axes of the first shaft lever and the second shaft lever are perpendicular to the surface of the base.
10. The inverted orbital inertia mass damper of claim 7, wherein the number of flywheel sets is four.
CN202210602351.4A 2022-05-30 2022-05-30 Inverted rail type inerter mass damper Pending CN114775828A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202210602351.4A CN114775828A (en) 2022-05-30 2022-05-30 Inverted rail type inerter mass damper

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202210602351.4A CN114775828A (en) 2022-05-30 2022-05-30 Inverted rail type inerter mass damper

Publications (1)

Publication Number Publication Date
CN114775828A true CN114775828A (en) 2022-07-22

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202210602351.4A Pending CN114775828A (en) 2022-05-30 2022-05-30 Inverted rail type inerter mass damper

Country Status (1)

Country Link
CN (1) CN114775828A (en)

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