CN117569473A - Inertial mass damper of screw flywheel mechanism - Google Patents
Inertial mass damper of screw flywheel mechanism Download PDFInfo
- Publication number
- CN117569473A CN117569473A CN202311663534.8A CN202311663534A CN117569473A CN 117569473 A CN117569473 A CN 117569473A CN 202311663534 A CN202311663534 A CN 202311663534A CN 117569473 A CN117569473 A CN 117569473A
- Authority
- CN
- China
- Prior art keywords
- ball screw
- inertial
- flywheel
- screw
- piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000007246 mechanism Effects 0.000 title claims abstract description 19
- 238000000034 method Methods 0.000 claims description 20
- 230000001133 acceleration Effects 0.000 claims description 17
- 238000005259 measurement Methods 0.000 claims description 14
- 230000005284 excitation Effects 0.000 claims description 9
- 230000004044 response Effects 0.000 claims description 8
- 238000006073 displacement reaction Methods 0.000 claims description 6
- 230000008569 process Effects 0.000 claims description 4
- 230000006835 compression Effects 0.000 claims description 2
- 238000007906 compression Methods 0.000 claims description 2
- 230000000694 effects Effects 0.000 abstract description 14
- 238000010521 absorption reaction Methods 0.000 abstract description 11
- 230000002411 adverse Effects 0.000 abstract description 6
- 230000035939 shock Effects 0.000 abstract description 6
- 230000001419 dependent effect Effects 0.000 abstract description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000021715 photosynthesis, light harvesting Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Abstract
The invention belongs to the field of dampers, and particularly relates to an inertial mass damper of a screw flywheel mechanism, which comprises a first ball screw inertial volume structure; a second ball screw inertial volume structure mounted on the first ball screw inertial volume structure; and the front end structure is arranged on one side of the first ball screw inertial container structure. When the energy input is small, the force provided by the device for the structure is only the sum of elastic restoring force and smaller equivalent inertial force, compared with the conventional ball screw inertial mass damper which is often dependent on the huge inertial force generated by a flywheel to realize the energy absorption and shock absorption effect of the structure, the huge inertial force can have adverse effect on the structure, the load and vibration of the structure are increased, and when the energy input is large, the inner piston reaches the deformation limit, the first ball screw inertial mass damper is added to work, so that the required equivalent inertial force is provided.
Description
Technical Field
The invention belongs to the field of dampers, and particularly relates to an inertial mass damper of a screw flywheel mechanism.
Background
The ball screw inertial Rong Zuni device is a device for structural energy dissipation and shock absorption, and is widely applied to various structural engineering needing to resist earthquake, impact or vibration.
In the structural energy dissipation and vibration reduction, the ball screw inertial Rong Zuni device is used for reducing the vibration response of the structure and reducing the dynamic response of the structure by absorbing and dissipating energy. However, existing ball screw inertial dampers tend to have the following problems:
the equivalent inertial force generated by the flywheel in the traditional ball screw inertial mass damper is constant, namely the output and the acceleration of the ball screw inertial mass damper are in linear constitutive relation, but the external excitation has the characteristic of randomness, so that the traditional ball screw inertial mass damper cannot achieve an ideal control effect.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention provides the inertial mass damper of the screw flywheel mechanism, so as to solve the problems that the equivalent inertial force generated by the flywheel in the inertial mass damper is far larger than the force generated by external excitation when the external excitation is smaller, so that the structural response is amplified, and the flywheel is required to generate enough equivalent inertial force to play a role in response control when the external excitation is larger, the requirements of small excitation and large excitation on structural response cannot be met by the traditional damper, and the force difference between the moment when the flywheel works and the moment immediately before the flywheel works is larger in the traditional damper, so that the conversion is abrupt and incoherent.
The invention provides an inertial mass damper of a screw flywheel mechanism, which comprises:
a first ball screw inertial measurement unit;
a second ball screw inertial volume structure mounted on the first ball screw inertial volume structure;
the front end structure is arranged on one side of the first ball screw inertial container structure;
the rear end structure is arranged on the second ball screw inertial volume structure and is positioned at one side of the first ball screw inertial volume structure away from the front end structure;
the piston structure comprises an inner piston and a spring, the inner piston is arranged in the first ball screw inertial volume structure, one end of the inner piston is connected with the front end structure, and the inner piston is far away from the front end structure and is connected with the second ball screw inertial volume structure;
the springs are symmetrically arranged on the inner piston;
according to the inertial mass damper of the screw flywheel mechanism, two groups of screw flywheel systems with larger inertial mass distance are arranged, when energy input is small, the force provided by the device for the structure is only the sum of elastic restoring force and smaller equivalent inertial force, compared with the traditional ball screw inertial mass damper which is usually dependent on huge inertial force generated by a flywheel to realize the energy absorption and shock absorption effect of the structure, the huge inertial force can have adverse effects on the structure, the load and vibration of the structure are increased, when the energy input is large, the inner piston reaches the deformation limit, the first ball screw inertial volume structure is added to work, and further the required equivalent inertial force is provided.
Wherein the first ball screw inertial structure and the second ball screw inertial structure are configured to provide an equivalent inertial force when excited;
the relative motion of the front end structure and the rear end structure reflects the magnitude of the structural response caused by external excitation;
the inner piston is used for driving the first ball screw inertial volume structure and the second ball screw inertial volume structure to work.
In one embodiment, the first ball screw inertial measurement structure comprises a first ball screw, a first ball nut, a large flywheel, and an outer bearing;
the first ball nut is sleeved on the first ball screw and connected with the large flywheel;
the large flywheel is mounted on the first ball screw;
the outer bearing is mounted on one side of the large flywheel.
In one embodiment, the second ball screw inertial measurement structure comprises a second ball screw, a second ball nut, a small flywheel, and an inner bearing;
the second ball screw is arranged in the first ball screw, the inner piston is arranged in the first ball screw, and one side of the inner piston is connected with the second ball screw;
the second ball nut is sleeved on the second ball screw and connected with the small flywheel;
the small flywheel is arranged on the second ball screw and is positioned on one side of the large flywheel;
the inner bearing is arranged on one side of the small flywheel away from the large flywheel.
In one embodiment, the front end structure comprises a piston rod, a front end sleeve and a front end plate;
the piston rod is arranged in the first ball screw and connected with the inner piston;
the front end sleeve is sleeved on the periphery of the piston rod;
the front end plate is mounted on one side of the front end sleeve.
In one embodiment, the rear structure includes a rear sleeve and a rear end plate;
the rear end sleeve comprises an outer cylinder and an inner cylinder, the outer cylinder is sleeved on the first ball screw, and the inner cylinder is sleeved on the second ball screw;
the rear end plate is mounted on one side of the outer cylinder.
In one embodiment, one side of the inner piston is fixedly connected with the piston rod, and one side of the inner piston, which is far away from the piston rod, is fixedly connected with the second ball screw.
In one embodiment, the first ball screw is provided with a cavity which is matched with the shapes of the first ball screw, the inner piston, the spring and the piston rod;
the second ball screw and the piston rod portion are located within the cavity;
the inner piston and the spring are located within the cavity.
In one embodiment, the second ball screw penetrates out of the cavity on the first ball screw and is in sliding connection with the inner barrel.
In one embodiment, the length of the outer barrel is greater than the length of the inner barrel.
In one embodiment, the outer cylinder is connected with the inner ring of the outer bearing, and the inner cylinder is connected with the inner ring of the inner bearing.
The inertial mass damper of the screw flywheel mechanism has the following beneficial effects:
by arranging two groups of screw flywheel structures with larger equivalent inertial mass distance, when energy input is small, the force provided by the device for the structure is only the sum of elastic restoring force and smaller equivalent inertial force, compared with the traditional ball screw inertial mass damper which is often dependent on huge inertial force generated by a flywheel to realize the energy absorption and shock absorption effect of the structure, the huge inertial force can have adverse effect on the structure, the load and vibration of the structure are increased, when the energy input is large, the inner piston reaches the deformation limit, the first ball screw inertial mass structure is added to work, and further the required equivalent inertial force is provided.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following description will briefly explain the drawings used in the embodiments or the description of the prior art, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings can be obtained according to the structures shown in these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a schematic cross-sectional view of the present invention;
FIG. 3 is a schematic view of the spring piston of the present invention;
FIG. 4 is a perspective view of a first ball screw inertial measurement unit of the present invention;
fig. 5 is a schematic diagram showing the connection between the second ball screw inertial measurement unit and the rear end sleeve.
The labels in the figures are illustrated below:
1. a front end plate; 2. a front end sleeve; 3. a piston rod; 4. a first ball screw inertial measurement unit; 401. a first ball screw; 402. a first ball nut; 403. a large flywheel; 404. an outer bearing; 5. a rear end sleeve; 501. an outer cylinder; 502. an inner cylinder; 6. a rear end plate; 7. a second ball screw inertial measurement unit; 701. a second ball screw; 702. a second ball nut; 703. a small flywheel; 704. an inner bearing; 8. an inner piston; 9. and (3) a spring.
Detailed Description
In order to make the above objects, features and advantages of the present application more comprehensible, embodiments accompanied with figures are described in detail below. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. This application is, however, susceptible of embodiment in many other forms than those described herein and similar modifications can be made by those skilled in the art without departing from the spirit of the application, and therefore the application is not to be limited to the specific embodiments disclosed below.
In the description of the present invention, it should 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", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships as described based on the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention.
Referring to fig. 1 to 5, one embodiment of the present invention provides an inertial mass damper of a screw flywheel mechanism, including:
a first ball screw inertial measurement unit 4;
a second ball screw inertial measurement structure 7, the second ball screw inertial measurement structure 7 being mounted on the first ball screw inertial measurement structure 4;
a front end structure mounted on one side of the first ball screw inertial structure 4;
a rear end structure mounted on the second ball screw inertial volume structure 7 and located on a side of the first ball screw inertial volume structure 4 remote from the front end structure;
the piston structure comprises an inner piston 8 and a spring 9, the inner piston 8 is arranged in the first ball screw inertial container structure 4, one end of the inner piston 8 is connected with a front end structure, and the inner piston 8 is connected with the second ball screw inertial container structure 7 far away from the front end structure;
the springs 9 are symmetrically arranged on the inner piston 8;
specifically, through setting up the great screw flywheel system of two sets of inertial mass distance, when the energy input is little, the power that this device provided for the structure is only elastic restoring force and less inertial force's sum, compared, traditional ball inertial mass damper often relies on the huge inertial force that the flywheel produced to realize the energy-absorbing cushioning effect of structure, this huge inertial force can produce adverse effect to the structure, increase the load and the vibration of structure, when the energy input is great, inner piston 8 reaches the limit of deformation, first ball inertial volume structure 4 joins the work, and then provide required equivalent inertial force, compared with traditional ball inertial mass damper, the function of the steady transition of little energy to big energy is realized to this device, when the input energy is less, inner piston 8 takes place the axial motion and drives the work of second ball inertial volume structure 7 and realize the energy-absorbing effect, in addition spring 9 can make inner piston 8 realize from the reset.
It should be noted that, in addition, the terms "first" and "second" 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, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present invention, the meaning of "plurality" means at least two, for example, two, three, etc., unless specifically defined otherwise.
Wherein the first ball screw inertial structure 4 and the second ball screw inertial structure 7 are adapted to provide an equivalent inertial force when excited;
the relative motion of the front end structure and the rear end structure reflects the magnitude of the structural response caused by external excitation;
the inner piston 8 is used for driving the first ball screw inertial container structure 4 and the second ball screw inertial container structure 7 to work.
In one embodiment, the first ball screw inertial measurement unit 4 includes a first ball screw 401, a first ball nut 402, a large flywheel 403, and an outer bearing 404;
the first ball nut 402 is sleeved on the first ball screw 401 and is connected with the large flywheel 403;
the large flywheel 403 is mounted on the first ball screw 401;
the outer bearing 404 is mounted on one side of the large flywheel 403;
the second ball screw inertial measurement unit 7 comprises a second ball screw 701, a second ball nut 702, a small flywheel 703 and an inner bearing 704;
the second ball screw 701 is installed in the first ball screw 401, the inner piston 8 is installed in the first ball screw 401, and one side of the inner piston 8 is connected with the second ball screw 701;
the second ball nut 702 is sleeved on the second ball screw 701 and is connected with the small flywheel 703;
the small flywheel 703 is mounted on the second ball screw 701 and located at one side of the large flywheel 403;
the inner bearing 704 is mounted on the side of the small flywheel 703 away from the large flywheel 403;
the front end structure comprises a piston rod 3, a front end sleeve 2 and a front end plate 1;
the piston rod 3 is installed in the first ball screw 401 and connected with the inner piston 8;
the front end sleeve 2 is sleeved on the periphery of the piston rod 3;
the front end plate 1 is arranged on one side of the front end sleeve 2;
the rear end structure comprises a rear end sleeve 5 and a rear end plate 6;
the rear end sleeve 5 comprises an outer cylinder 501 and an inner cylinder 502, the outer cylinder 501 is sleeved on the first ball screw 401, and the inner cylinder 502 is sleeved on the second ball screw 701;
the rear end plate 6 is mounted at one side of the outer cylinder 501;
one side of the inner piston 8 is fixedly connected with the piston rod 3, and one side of the inner piston 8, which is far away from the piston rod 3, is fixedly connected with a second ball screw 701;
the first ball screw 401 is provided with a cavity which is matched with the shapes of the second ball screw 701, the inner piston 8, the spring 9 and the piston rod 3;
the second ball screw 701 and the piston rod 3 are partially located in the cavity;
said inner piston 8 and said spring 9 are located in said cavity;
the second ball screw 701 penetrates from the inside of the cavity on the first ball screw 401 and is in sliding connection with the outer cylinder 501;
the length of the outer cylinder 501 is greater than the length of the inner cylinder 502;
the outer cylinder 501 is connected to the inner ring of the outer bearing 404, and the inner cylinder 502 is connected to the inner ring of the inner bearing 704.
Specifically, the small flywheel 703 provides a smaller inertial mass than the large flywheel 403;
when the earthquake input energy is smaller (that is, the inner piston 8 is supposed to be ideal without friction, and the deformation of the spring 9 caused by the movement of the inner piston 8 is smaller than the limit deformation), the inner piston 8 moves axially under the constraint of the spring 9, so that the second ball screw is pushed to move axially, the second ball screw 701 and the second ball nut 702 are axially and relatively displaced due to the fact that the second ball nut 702 and the small flywheel 703 are fixedly connected with each other in the axial direction, the second ball nut 702 is rotated, the flywheel is fixedly connected with the small flywheel 703 through a bolt, and then the flywheel rotates at the same angular speed as the ball nut, at the moment, the first ball screw inertial volume system does not work, a small elastic restoring force is provided for the structure, and meanwhile, the provided equivalent inertial force is equal to the equivalent inertial force generated by the small flywheel 703, so that the great adverse effect of the large inertial force generated by the large flywheel 403 on the structure is avoided.
When the earthquake input energy is large (namely, when the deformation of the spring 9 caused by the movement of the inner piston 8 exceeds the limit deformation), the second ball screw 701 and the second ball nut 702 still generate axial relative displacement, so that the second ball nut 702 rotates to drive the small flywheel 703 to work, meanwhile, the inner piston 8 drives the first ball screw 401 to generate axial movement through the spring 9, so that the first ball screw is pushed to generate axial movement, the first ball screw 402 and the large flywheel 403 are fixedly connected with the rear end sleeve 5 in the axial direction, the first ball screw 401 and the first ball screw 402 generate axial relative displacement, so that the first ball screw 402 rotates, and the first ball screw 402 and the large flywheel 403 are connected through a bolt, so that the flywheel generates rotation with the same angular speed as the ball screw, and at the moment, the device provides a large equivalent inertial force for the structure to help dissipate energy, so that the effects of energy absorption and shock absorption are achieved.
Further, the compression limit of the designed spring 9 is D, and the motion displacement of the piston is assumed to be D;
when D < D, the force F generated by the device at that time 1 The sum of the restoring force of the spring 9 and the equivalent inertial force generated by the small flywheel 703:
d in 1 =d, k is the stiffness coefficient of the spring 9;
wherein the method comprises the steps ofThe method comprises the following steps:
in the above r M i Is the inertia torque caused by the small flywheel 703, r ss R is the distance between the center of the second ball screw 701 and the center of the ball 0 Is a small flywheel 703 inner diameter, r i For the outer diameter, m, of the small flywheel 703 0 For the actual mass of the small flywheel 703,is the relative acceleration of the front and rear end plates.
In addition S i The ratio of the angular acceleration to the linear acceleration in the second ball screw 701 is:
S i ＝2π/L d
in which L d Is the lead of the second ball screw 701.
When D > D, the device provides a force F 2 Is the sum of the restoring force of the spring 9, the inertial force generated by the small flywheel 703 and the equivalent inertial force generated by the large flywheel 403:
d in 2 ＝d，
Wherein the method comprises the steps ofThe method comprises the following steps:
in the above r M' i Is the inertia torque caused by the large flywheel 403, r s ' s R is the distance between the center of the first ball screw 401 and the center of the ball 0 ' is the inner diameter of the large flywheel 403, r i 'is the outer diameter of the large flywheel 403, m' 0 For the actual mass of the large flywheel 403,is the relative acceleration of the front and rear end plates.
In addition S' i The ratio of angular acceleration to linear acceleration in the first ball screw 401 is:
S'＝2π/L'
i d
in L' d A lead of the first ball screw 401;
when the spring 9 in the first ball screw 401 cavity does not reach the limit deformation, the inertial force F generated by the device at the moment in The method comprises the following steps:
in the method, in the process of the invention,for the relative acceleration of the rear end plate 6 and the front end plate 1, m 1 An equivalent inertial mass for the small flywheel 703.
When the spring 9 in the cavity of the first ball screw 401 reaches the limit deformation, the inertial force F 'generated by the device at the moment' in The method comprises the following steps:
in the method, in the process of the invention,for the relative acceleration of the rear end plate 6 and the front end plate 1, m 2 For the equivalent inertial mass, m, produced by the small flywheel 703 1 An equivalent inertial mass for the large flywheel 403.
It should be noted that, in the present invention, unless explicitly specified and limited otherwise, terms such as "mounted," "connected," "fixed," and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances;
in the present invention, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature;
when an element is referred to as being "fixed" or "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like are used herein for illustrative purposes only and are not meant to be the only embodiment.
The working principle of the invention is as follows:
when the earthquake input energy is smaller (i.e. the inner piston 8 is supposed to be ideal without friction, and the deformation of the spring 9 caused by the movement of the inner piston 8 is smaller than the limit deformation), the inner piston 8 axially moves under the constraint of the spring 9, so as to push the second ball screw to axially move, the second ball screw 701 and the second ball nut 702 are axially and fixedly connected with the rear end sleeve 5, so that the second ball screw 702 and the second ball nut 702 are axially and relatively displaced, the second ball nut 702 is further rotated, and the second ball nut 702 and the small flywheel 703 are fixedly connected through bolts, so that the flywheel rotates at the same angular speed as the ball nut, at the moment, the first ball screw inertial structure does not work, the device provides a small elastic restoring force for the structure, and simultaneously the provided equivalent inertial force is equal to the equivalent inertial force generated by the small flywheel 703, so that the adverse effect of the large inertial force generated by the large flywheel 403 on the structure is avoided; when the earthquake input energy is large (namely, when the deformation of the spring 9 caused by the movement of the inner piston 8 reaches the limit deformation), the second ball screw 701 and the second ball nut 702 still generate axial relative displacement, so that the second ball nut 702 rotates to drive the small flywheel 703 to work, meanwhile, the inner piston 8 drives the first ball screw 401 to generate axial movement through the spring 9, so that the first ball screw is pushed to generate axial movement, the first ball screw 402 and the large flywheel 403 are fixedly connected with the rear end sleeve 5 in the axial direction, the first ball screw 401 and the first ball screw 402 generate axial relative displacement, so that the first ball screw 402 rotates, and the first ball screw 402 and the large flywheel 403 are connected through a bolt, so that the flywheel generates rotation with the same angular speed as the ball screw, and at the moment, the device provides a large equivalent inertial force for the structure to help dissipate energy, so that the effects of energy absorption and shock absorption are achieved.
The foregoing description is only of the preferred embodiments of the present invention and is not intended to limit the scope of the invention, and all the equivalent structural changes made by the paper and the accompanying drawings or the direct/indirect application in other related technical fields are included in the scope of the invention.
Claims (10)
1. An inertial mass damper for a screw flywheel mechanism, comprising:
a first ball screw inertial measurement unit;
a second ball screw inertial volume structure mounted on the first ball screw inertial volume structure;
the front end structure is arranged on one side of the first ball screw inertial container structure;
the rear end structure is arranged on the second ball screw inertial volume structure and is positioned at one side of the first ball screw inertial volume structure away from the front end structure;
the piston structure comprises an inner piston and a spring, the inner piston is arranged in the first ball screw inertial volume structure, one end of the inner piston is connected with the front end structure, and the inner piston is far away from the front end structure and is connected with the second ball screw inertial volume structure;
the springs are symmetrically arranged on the inner piston;
wherein the first ball screw inertial structure and the second ball screw inertial structure are configured to provide an equivalent inertial force when excited;
the relative movement of the front end structure and the back end structure reflects the magnitude of the structural response caused by external excitation;
the inner piston is used for driving the first ball screw inertial volume structure and the second ball screw inertial volume structure to work.
2. An inertial mass damper for a screw flywheel mechanism as claimed in claim 1,
the first ball screw inertial container structure comprises a first ball screw, a first ball nut, a large flywheel and an outer bearing;
the first ball nut is sleeved on the first ball screw and connected with the large flywheel;
the large flywheel is mounted on the first ball screw;
the outer bearing is mounted on one side of the large flywheel.
3. An inertial mass damper for a screw flywheel mechanism as claimed in claim 2,
the second ball screw inertial container structure comprises a second ball screw, a second ball nut, a small flywheel and an inner bearing;
the second ball screw is arranged in the first ball screw, the inner piston is arranged in the first ball screw, and one side of the inner piston is connected with the second ball screw;
the second ball nut is sleeved on the second ball screw and connected with the small flywheel;
the small flywheel is arranged on the second ball screw and is positioned on one side of the large flywheel;
the inner bearing is arranged on one side of the small flywheel away from the large flywheel.
4. An inertial mass damper for a screw flywheel mechanism as claimed in claim 3,
the front end structure comprises a piston rod, a front end sleeve and a front end plate;
the piston rod is arranged in the first ball screw and connected with the inner piston;
the front end sleeve is sleeved on the periphery of the piston rod;
the front end plate is mounted on one side of the front end sleeve.
5. An inertial mass damper for a screw flywheel mechanism as claimed in claim 4 wherein,
the rear end structure comprises a rear end sleeve and a rear end plate;
the rear end sleeve comprises an outer cylinder and an inner cylinder, the outer cylinder is sleeved on the first ball screw, and the inner cylinder is sleeved on the second ball screw;
the rear end plate is mounted on one side of the outer cylinder.
6. An inertial mass damper for a screw flywheel mechanism as claimed in claim 5 wherein,
one side of the inner piston is fixedly connected with the piston rod, and one side of the inner piston, which is far away from the piston rod, is fixedly connected with the second ball screw.
7. An inertial mass damper for a screw flywheel mechanism as claimed in claim 6 wherein,
the first ball screw is provided with a cavity which is matched with the second ball screw, the inner piston, the spring and the piston rod in shape;
the second ball screw and the piston rod portion are located within the cavity;
the inner piston and the spring are located within the cavity.
8. An inertial mass damper for a screw flywheel mechanism as claimed in claim 7 wherein,
the second ball screw penetrates out of the cavity on the first ball screw and is in sliding connection with the inner barrel.
9. An inertial mass damper for a screw flywheel mechanism as claimed in claim 5 wherein,
the length of the outer cylinder is longer than that of the inner cylinder;
the outer cylinder is connected with the inner ring of the outer bearing, and the inner cylinder is connected with the inner ring of the inner bearing.
10. An inertial mass damper for a screw flywheel mechanism as claimed in claim 5 wherein,
the compression limit of the spring is D, and the motion displacement of the piston is D;
when D is less than D, the force F generated by the device at the moment 1 The sum of the restoring force of the spring and the equivalent inertial force generated by the small flywheel:
d in 1 =d, k is the spring rate;
wherein the method comprises the steps ofThe method comprises the following steps:
in the above r M i Is the inertia torque caused by a small flywheel, r ss Between the center of the second ball screw and the center of the ballDistance r 0 Is the inner diameter of a small flywheel, r i Is the outer diameter of a small flywheel, m 0 For the actual mass of the small flywheel,relative acceleration for the front and rear end plates;
in addition S i The ratio of the angular acceleration to the linear acceleration in the second ball screw is:
S i ＝2π/L d ；
in which L d A lead of the second ball screw;
when D > D, the device provides a force F 2 The sum of the restoring force of the spring, the equivalent inertial force generated by the small flywheel and the equivalent inertial force generated by the large flywheel is as follows:
d in 2 ＝d，
Wherein the method comprises the steps ofThe method comprises the following steps:
in the above r M′ i Is the inertia torque caused by a large flywheel, r' ss Is the distance between the center of the first ball screw and the center of the ball, r' 0 Is the inner diameter of a large flywheel, r' i Is the outer diameter of a large flywheel, m' 0 For the actual mass of a large flywheel,relative acceleration for the front and rear end plates;
in addition S' i The ratio of angular acceleration to linear acceleration in the first ball screw is:
S′ i ＝2π/L' d ；
in L' d A lead of the first ball screw;
when the spring in the first ball screw cavity does not reach the limit deformation, the inertial force F generated by the device at the moment in The method comprises the following steps:
in the method, in the process of the invention,for the relative acceleration of the rear end plate and the front end plate, m 1 Equivalent inertial mass generated for the small flywheel;
when the spring in the first ball screw cavity reaches the limit deformation, the inertial force F 'generated by the device at the moment' in The method comprises the following steps:
in the method, in the process of the invention,for the relative acceleration of the rear end plate and the front end plate, m 2 For producing equivalent inertial mass, m, of small flywheel 1 The equivalent inertial mass generated for a large flywheel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311663534.8A CN117569473A (en) | 2023-12-06 | 2023-12-06 | Inertial mass damper of screw flywheel mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311663534.8A CN117569473A (en) | 2023-12-06 | 2023-12-06 | Inertial mass damper of screw flywheel mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117569473A true CN117569473A (en) | 2024-02-20 |
Family
ID=89886196
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311663534.8A Pending CN117569473A (en) | 2023-12-06 | 2023-12-06 | Inertial mass damper of screw flywheel mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117569473A (en) |
-
2023
- 2023-12-06 CN CN202311663534.8A patent/CN117569473A/en active Pending
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2012189104A (en) | Inertial mass damper | |
| CN111005613A (en) | Viscoelastic friction type energy-consumption self-resetting buckling-restrained brace | |
| JP2000055117A (en) | Base isolation device | |
| CN111623074B (en) | Fluid-excited fluid-solid mixed damper | |
| CN111156283A (en) | Crank piston type inertial volume damping dynamic vibration isolator | |
| JP3140718B2 (en) | Vibration reduction method and active control device for vibration reduction | |
| CN109025451B (en) | Double-torsion anti-destabilization method | |
| CN110762150A (en) | Shock absorber | |
| CN110725598A (en) | Friction compound type buckling restrained energy dissipation brace | |
| CN117569473A (en) | Inertial mass damper of screw flywheel mechanism | |
| CN110670753B (en) | One-way idle-stroke-free friction damper | |
| JP2017053364A (en) | Stopper and damping device | |
| JP6726381B2 (en) | Installation structure of rotary mass damper | |
| CN112081858B (en) | Viscous damper | |
| CN114277952A (en) | Composite damper | |
| CN211622802U (en) | Friction compound type buckling restrained energy dissipation brace | |
| CN117569472A (en) | Mass damper of double ball screw system | |
| CN2923862Y (en) | Friction damper | |
| CN109811641B (en) | Buffering limiting type rotary friction mass damper | |
| CN219825687U (en) | Self-resetting tuned inertial mass damper for adjacent structure | |
| CN216406346U (en) | Parallel type graded sliding friction energy dissipater | |
| CN220195979U (en) | Damping device for lower press roller press of lithium battery | |
| CN216195630U (en) | STF rotary damper based on ball screw | |
| CN219794273U (en) | Anti-seismic energy dissipation damper for building structure | |
| CN216242009U (en) | Stepped energy consumption viscous damper |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication |