CN115637638B - Inertial container of variable inertial semi-active tuning mass damper and frequency tuning method - Google Patents
Inertial container of variable inertial semi-active tuning mass damper and frequency tuning method Download PDFInfo
- Publication number
- CN115637638B CN115637638B CN202211320086.7A CN202211320086A CN115637638B CN 115637638 B CN115637638 B CN 115637638B CN 202211320086 A CN202211320086 A CN 202211320086A CN 115637638 B CN115637638 B CN 115637638B
- Authority
- CN
- China
- Prior art keywords
- inertial
- mass
- variable
- flywheel
- mass block
- 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.)
- Active
Links
- 238000000034 method Methods 0.000 title claims abstract description 27
- 230000003068 static effect Effects 0.000 claims abstract description 16
- 238000013016 damping Methods 0.000 claims description 6
- 230000001133 acceleration Effects 0.000 claims description 4
- 229910000838 Al alloy Inorganic materials 0.000 claims description 3
- 239000000956 alloy Substances 0.000 claims description 3
- 230000005484 gravity Effects 0.000 claims description 3
- 239000000463 material Substances 0.000 claims description 3
- WJIOHMVWGVGWJW-UHFFFAOYSA-N 3-methyl-n-[4-[(3-methylpyrazole-1-carbonyl)amino]butyl]pyrazole-1-carboxamide Chemical compound N1=C(C)C=CN1C(=O)NCCCCNC(=O)N1N=C(C)C=C1 WJIOHMVWGVGWJW-UHFFFAOYSA-N 0.000 abstract description 11
- 230000002829 reductive effect Effects 0.000 description 6
- 238000009434 installation Methods 0.000 description 4
- 230000033001 locomotion Effects 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- 230000001276 controlling effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000000670 limiting effect Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000002401 inhibitory effect Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
Landscapes
- Vibration Prevention Devices (AREA)
Abstract
A variable inertial mass semi-active tuning mass damper inertial container and a frequency tuning method belong to the technical field of structural vibration control. The invention solves the problem that the existing TMD cannot be applied due to overlarge static elongation when controlling the vertical vibration of a low-frequency structure, and the problem that the mode of a large-span bridge is dense and multi-order vortex vibration exists. According to the invention, based on a traditional tuned mass damper, an inertial container with a variable inertial mass is introduced, frequency tuning of TMDI is realized by changing the inertial coefficient of the inertial container, vortex-shedding frequency is calculated according to the incoming flow wind speed of a bridge and Stokes number of the section of a main beam, the mode frequency of the main beam which possibly generates vortex-induced vibration is estimated, and the required inertial coefficient and the corresponding radial position of a movable mass block are calculated by combining the dynamic characteristic of the TMDI, and the movable mass block is driven by a small motor and a screw rod to move to the required position along the radial direction, so that frequency tuning is realized. The method is applied to multi-order mode vortex-induced vibration control of the large-span bridge.
Description
Technical Field
The invention relates to a semi-active tuning mass damper inertial container and a frequency tuning method, in particular to a variable inertial semi-active tuning mass damper inertial container and a frequency tuning method, and belongs to the technical field of structural vibration control.
Background
When the near-ground wind in the boundary layer bypasses the bridge, flow separation is generated on the windward side of the main beam, vortex shedding with alternating changes is generated on the upper surface and the lower surface of the main beam, and vortex-induced resonance can be generated when the vortex shedding frequency is close to or equal to the self-oscillation frequency of a certain order of the structure. Although vortex vibration is amplitude limiting vibration with self-excitation property and does not directly affect the safety of a bridge structure, the vortex vibration generally occurs under the condition of low wind speed, has high occurrence frequency, seriously affects the travelling comfort and safety of the bridge, and causes long-term fatigue problem. Therefore, the method has great significance in eliminating or inhibiting vortex-induced vibration of the large-span bridge.
Tuned mass dampers (tuned mass damper, TMD) are one of the common methods of large span bridge vortex-induced vibration control due to their high efficiency, single mode damping performance. However, due to its mechanical structure and tuning-based vibration damping mechanism, the static elongation of TMD is inversely proportional to the square of its tuning frequency, and when vibration control is performed on a bridge with a large span, the static elongation of TMD is too large due to the low frequency, and is not applicable in the case of limited installation space inside the main beam, and additional measures such as levers, prestressed springs, etc. are often required to limit the static elongation. In addition, the frequency distribution of the bridge with large span is dense, the possibility of vortex-induced vibration of multiple modes exists under the design of passing wind speed, if only the first-order mode is controlled, the vortex-induced vibration control target cannot be realized, and TMD is only effective for a single mode, so that when the vortex-induced vibration control is carried out on the bridge with large span, multiple sets of TMDs are required to be designed, the additional mass is overlarge, and the cost is high. In order to improve the robustness of the TMD, the frequency and damping ratio of the TMD are adjusted in real time through data acquisition, mode identification and control feedback to adapt to vibration control of different modes, namely a semi-active tuned mass damper (semi-active tuned mass damper, SA-TMD), the currently commonly used parameter adjusting method is to adjust the damping ratio through electromagnetic characteristics or adjust the frequency through a guide rail moving mass block, so that the traditional SA-TMD is difficult to adapt to vibration control within a wider frequency range, and the required external energy input is larger.
In recent years, a double-ended mass element (inertial container) has been used to improve the conventional vibration control method. The inertial container can convert linear motion into high-speed rotation, provides counter force proportional to relative acceleration of two ends, and can realize inertial mass far higher than physical mass. The inertial container is connected in parallel with the springs and damping elements of a conventional TMD to yield a tuned mass damper inertial container (tuned mass damper inerter, TMDI). Because the inertial container has a dynamic negative stiffness effect, TMDI has the characteristics of high static stiffness and low dynamic stiffness, the static elongation of the TMDI is obviously lower than that of the traditional TMD when the vertical vibration of a low-frequency structure is controlled, the required installation space is smaller, and the TMDI has a wide application prospect in vortex-induced vibration control of a large-span bridge.
Disclosure of Invention
In view of the facts, the invention aims at the problem that the existing TMD cannot be applied due to overlarge static elongation during vertical vibration control of a low-frequency structure, and the problem that multi-order vortex vibration is possible due to dense mode of a large-span bridge is considered, so that the invention further provides a variable inertial semi-active tuning mass damper inertial container and a frequency tuning method. On the basis of a traditional tuned mass damper, an inertial container with variable inertial mass is introduced, the incoming wind speed is monitored through a wind speed anemometer arranged on a bridge, the mode in which vortex vibration is likely to occur is predicted according to the Stokes number of the section of a main beam, and the inertial coefficient of the inertial container is regulated, so that TMDI is always in a tuned state.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
a variable inertial semi-actively tuned mass damper inertial container (variable inertance semi-active tuned mass damper inerter, VISA-TMDI) comprising a tuned mass damper and a variable inertial container; the tuning mass damper comprises an outer frame, a longitudinal mass block, a spring and a viscous damper; the longitudinal mass block is arranged in the outer frame and is connected with a top plate of the outer frame through a spring and a viscous damper, and an avoidance notch is formed in the longitudinal mass block; the variable inertial container comprises a gear, a rack, a variable moment of inertia flywheel, a deep groove ball bearing and a rotating shaft; the variable inertial container is arranged in the outer frame; the rack penetrates through the avoidance notch on the longitudinal mass block, and the upper end and the lower end of the rack are connected with the top plate and the bottom plate of the outer frame; the rotating shaft transversely penetrates through the longitudinal mass block, and a rotating connection relation is established between the rotating shaft and the longitudinal mass block through a deep groove ball bearing; the middle part of the rotating shaft is provided with a gear, the gear is arranged in an avoidance groove opening on the longitudinal mass block, and the gear is meshed with the rack; and two ends of the rotating shaft are respectively provided with a flywheel with variable moment of inertia.
Further: the variable-rotation inertia flywheel comprises a flywheel wheel disc, a screw rod, a movable mass block, a small motor, a fixed support and a radial sliding guide rail; the flywheel wheel disc is fixedly connected with the rotating shaft, and a plurality of radial sliding guide rails are arranged on the flywheel wheel disc; the inner end of the radial sliding guide rail is provided with a small motor, and the outer end of the radial sliding guide rail is provided with a fixed support; the inner end of the screw rod is connected with the output end of the small motor, and the outer end of the screw rod is connected with the fixed support; the movable mass block is in threaded connection with the screw rod and is matched with the radial sliding guide rail to move along the radial direction of the flywheel disc. The rotary inertia of the flywheel with variable rotary inertia is changed along with the distance between the movable mass block and the rotary center, so that the inertial coefficient of the inertial container is changed in a larger range.
Further: the movable mass block moves along the radial direction of the flywheel disc through the cooperation of the balls and the radial sliding guide rail. In order to reduce the driving moment of the small motor, balls are arranged between the movable mass block and the radial sliding guide rail, and can convert sliding friction into rolling friction, so that the friction force between the movable mass block and the radial sliding guide rail is obviously reduced.
Further: the movable mass blocks and the radial sliding guide rails are three to eight in number and are identical in number.
Further: the outer frame is a square frame. The top and bottom plates of the square frame are used to secure or connect the various components of the variable inertial semi-actively tuned mass damper inertial container VISA-TMDI.
Further: six radial sliding guide rails are arranged on the flywheel wheel disc. For guiding the movable mass to move radially along the flywheel.
Further: the longitudinal mass block is a main mass element of the VISA-TMDI, and the physical mass of the variable inertial container is a part of the mass element besides providing the inertial capacity coefficient, so that the mass of each element can be utilized to the maximum extent, and the control effect of the VISA-TMDI is improved. The spring is used for connecting the outer frame and the longitudinal mass block, the rigidity of the spring is selected according to the frequency corresponding to the highest order target mode, meanwhile, the allowable value of the static extension of the spring is considered, and the total rigidity of the spring meets the following conditions:
wherein k is 1 Is the total stiffness of the spring; m is m 1 And m 2 The mass of the longitudinal mass block and the physical mass of the variable inertial container are respectively; omega max The circular frequency corresponding to the highest order target mode; g is gravity acceleration; [ delta ] st ]Is the allowable value of the static elongation of the spring.
Further: when the longitudinal mass block moves up and down, due to the action of the gears, the flywheel with variable rotational inertia can translate along with the longitudinal mass block and rotate around the circle center, so that the characteristic of the inertial container is realized. The movable mass block on the flywheel wheel disc can drive the movable mass block to move along the radial direction through the small motor and the screw rod according to the actual inertia coefficient requirement, so that the rotational inertia of the flywheel with variable rotational inertia is changed, and the inertia coefficient of the inertia container is changed. The inertial coefficient of the variable inertial container is:
wherein r is the diameter of the gear reference circle; j (J) 1 The rotary inertia of the flywheel wheel disc, the small motor, the screw rod and the fixed support relative to the circle center is adopted; m is m li Is the i-th active mass; r is (r) li The distance between the ith movable mass block and the center of the flywheel disc is the distance between the ith movable mass block and the center of the flywheel disc; n is the number of movable mass blocks.
Further: in order to realize the adjustment of the inertial capacity coefficient in a larger range, namely to increase the mass ratio of the movable mass block in the whole variable-moment-of-inertia flywheel, the flywheel wheel disc is made of an aluminum alloy material, meanwhile, the inside of the flywheel wheel disc is hollowed out, the movable mass block is made of a high-density material, such as lead and the like, and the inside of the flywheel wheel disc is hollowed out.
Further: the inner end of the screw rod is connected with the small motor through a single angular contact ball bearing and is used as a movable end; the outer end of the screw rod is connected with the fixed support through two angular contact ball bearings, so that radial movement of the screw rod is limited, and the movable mass block is prevented from being separated from the screw rod.
Further: the actual working frequency of the inertial container of the variable inertial semi-actively tuned mass damper is as follows:
wherein,the nominal frequency of the mass damper inertial vessel is tuned semi-actively for the variable inertial mass.
So designed that when k 1 After the determination of the formula (1), the nominal frequency of the VISA-TMDI is fixed, the static elongation of the spring is only related to the nominal frequency, the requirement of the actual installation space is met, the nominal frequency is greater than or equal to the highest order target modal frequency, and the actual working frequency of the VISA-TMDI is reduced by increasing the inertial coefficient, so that the actual working frequency is regulated within a wider frequency range.
In order to achieve the above purpose, the present invention adopts the following technical scheme II:
the method is realized based on the variable inertial semi-active tuning mass damper inertial container in the technical scheme one. The method comprises the following steps:
when the multi-order mode vortex-induced vibration of the main girder of the large-span bridge is controlled, the average wind speed in 5-15 min flowing through the main girder is measured by a wind speed anemometer arranged on the bridge deck, and the vortex-shedding frequency is calculated according to the Stokes number of the section of the main girder, namely:
st is Stoher number of the section of the girder, U is the incoming wind speed, D is the size of the windward side of the section of the girder, and is generally the height of the girder;
mode information obtained by combining finite element models of bridges is combined, and mode frequency omega of vortex vibration possibly occurring is estimated t The desired inertial coefficient is obtained by the formula (5):
the movable mass blocks have equal mass and equal distance from the center of the flywheel disc, and the distance from the movable mass blocks to the center of the flywheel disc is calculated by the method (6):
wherein m is l Mass for a single movable mass;
the movable mass block is driven to move to a designated position by controlling the small motor, so that the working frequency of the inertial container of the variable inertial semi-active tuning mass damper is adjusted, and frequency tuning is realized.
The invention has the following beneficial effects:
1. according to the invention, the inertial container is introduced into the traditional TMD, so that the TMD has the characteristics of high static stiffness and low dynamic stiffness, the static elongation of the spring can be obviously reduced, and the TMD can be used for controlling the vertical vibration of the main girder of the large-span bridge;
2. the invention provides a variable inertial semi-active tuning mass damper inertial container, which realizes a required inertial capacity coefficient by changing the radial position of a movable mass block on a flywheel, so that the frequency of TMDI is regulated within a wider frequency range;
3. according to the invention, the dynamic characteristics of TMDI are utilized, the frequency tuning of TMDI is realized by changing the inertial capacity coefficient of the inertial container, the required inertial capacity coefficient is determined according to the incoming wind speed and the Stohar number of the section of the main beam, and the method is different from the traditional TMD which is only effective on a single mode, and can be applied to the multi-order mode vortex-induced vibration control of a large-span bridge.
Drawings
FIG. 1 is a perspective view of a variable inertial semi-actively tuned mass damper inertial vessel;
FIG. 2 is a front view of a variable inertial semi-actively tuned mass damper inertial vessel;
FIG. 3 is a side view of a variable inertial semi-actively tuned mass damper inertial vessel;
FIG. 4 is a top view of a variable inertial semi-actively tuned mass damper inertial vessel (with the outer frame omitted);
FIG. 5 is a perspective view of a variable inertial container;
FIG. 6 is a schematic plan view of a variable moment of inertia flywheel;
fig. 7 is a perspective view of a variable moment of inertia flywheel.
In the figure, 1: an outer frame; 2: a longitudinal mass; 3: a spring; 4: a viscous damper; 5: a variable inertial container; 6: a gear; 7: a rack; 8: a variable moment of inertia flywheel; 9: deep groove ball bearings; 10: flywheel wheel disc; 11: a screw rod; 12: a movable mass; 13: a small motor; 14: a fixed support; 15: angular contact ball bearings; 16: a set screw; 17: a ball; 18: a radial sliding guide rail.
Detailed Description
In order to make the present application solution better understood by those skilled in the art, the following description will be made in detail and with reference to the accompanying drawings in the embodiments of the present application, it is apparent that the described embodiments are only some embodiments of the present application, not all embodiments. All other embodiments, which can be made by one of ordinary skill in the art based on the embodiments herein without making any inventive effort, shall fall within the scope of the present application.
It should be noted that the terms "first," "second," and the like in the description and claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate in order to describe the embodiments of the present application described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
In the present application, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate an azimuth or a positional relationship based on that shown in the drawings. These terms are used primarily to better describe the present application and its embodiments and are not intended to limit the indicated device, element or component to a particular orientation or to be constructed and operated in a particular orientation.
Also, some of the terms described above may be used to indicate other meanings in addition to orientation or positional relationships, for example, the term "upper" may also be used to indicate some sort of attachment or connection in some cases. The specific meaning of these terms in this application will be understood by those of ordinary skill in the art as appropriate.
Furthermore, the terms "disposed," "connected," "secured" and "affixed" are to be construed broadly. For example, "connected" may be in a fixed connection, a removable connection, or a unitary construction; may be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements, or components. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art as the case may be.
It should be noted that, in the case of no conflict, the embodiments and features in the embodiments may be combined with each other. The present application will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
Example 1:
referring to fig. 1-7, the present embodiment provides a variable inertial semi-actively tuned mass damper inertial container (variable inertance semi-active tuned mass damper inerter, VISA-TMDI) in which a mainly variable moment of inertia flywheel is provided, and the adjustment of the inertial coefficient of the inertial container can be achieved by changing the moment of inertia of the variable moment of inertia flywheel. Because the inertial container can realize the inertial coefficient which is far larger than the physical mass of the inertial container, the rotational inertia of the flywheel with variable rotational inertia can be changed with low cost, and the inertial coefficient of the inertial container can be changed in a larger range. The variable inertial semi-active tuned mass damper inertial container of the embodiment comprises a tuned mass damper and a variable inertial container 5;
the tuned mass damper comprises an outer frame 1, a longitudinal mass block 2, four springs 3 and two viscous dampers 4; the longitudinal mass block 2 is arranged in the outer frame 1, the top surface of the longitudinal mass block 2 is connected with the top plate of the outer frame 1 through four springs 3 and two viscous dampers 4, the four springs 3 are symmetrically arranged left and right along the vertical center line of the longitudinal mass block 2, the two viscous dampers 4 are symmetrically arranged front and back along the vertical center line of the longitudinal mass block 2, the longitudinal mass block 2 is provided with a avoidance notch, and the inside of the avoidance notch is hollowed for installing the variable inertial mass inertial container 5; the outer frame 1 is a square frame, the top plate and the bottom plate of the square frame are used for fixing or connecting all parts of the inertial container VISA-TMDI of the variable inertial semi-active tuning mass damper, and the height of the outer frame 1 should consider the travel of the longitudinal mass block 2 to prevent collision between the two parts;
the variable inertial container 5 comprises a gear 6, a rack 7, a variable moment of inertia flywheel 8, a deep groove ball bearing 9 and a rotating shaft; the variable inertial container 5 is arranged inside the outer frame 1; the rack 7 penetrates through the avoidance notch on the longitudinal mass block 2, and the upper end and the lower end of the rack are connected with the top plate and the bottom plate of the outer frame 1; the rotating shaft transversely penetrates through the longitudinal mass block 2, and a rotating connection relation is established between the rotating shaft and the longitudinal mass block 2 through the deep groove ball bearing 9; the middle part of the rotating shaft is provided with a gear 6, the gear 6 is arranged in an avoidance notch on the longitudinal mass block 2, and the gear 6 is meshed with a rack 7; two ends of the rotating shaft are respectively provided with a flywheel 8 with variable moment of inertia;
the variable moment of inertia flywheel 8 comprises a flywheel disc 10, a screw rod 11, a movable mass block 12, a small motor 13, a fixed support 14 and a radial sliding guide rail 18; the flywheel disc 10 is fixedly connected with the rotating shaft, and six radial sliding guide rails 18 are arranged on the flywheel disc 10; the inner end of the radial sliding guide rail 18 is provided with a small motor 13, and the outer end is provided with a fixed support 14; the inner end of the screw rod 11 is connected with the output end of the small motor 13, and the outer end of the screw rod 11 is connected with the fixed support 14; the movable mass block 12 is in threaded connection with the screw rod 11 and is matched with the radial sliding guide rail 18 to move along the radial direction of the flywheel disc 10, and in order to reduce the driving moment of the small motor, the ball 17 is arranged between the movable mass block 12 and the radial sliding guide rail 18, and the ball 17 can convert sliding friction into rolling friction, so that the friction force between the movable mass block and the radial sliding guide rail is obviously reduced; in order to achieve a larger range of inertia coefficient adjustment, i.e. to increase the mass ratio of the movable mass block in the whole flywheel with variable rotational inertia, the flywheel disc 10 is made of aluminum alloy material, and the inside of the flywheel disc is hollowed out, while the movable mass block 12 is made of high-density material, such as lead, and the inside of the flywheel disc is hollowed out; the inner end of the screw rod 11 is connected with the small motor 13 through a single angular contact ball bearing 15 and is used as a movable end; the outer end of the screw rod 11 is connected with a fixed support 14 through two angular contact ball bearings 15 and a fixed screw 16, so that radial movement of the screw rod 11 is limited, and the movable mass block is prevented from being separated from the screw rod. The small motor 13 drives the screw rod 11 to rotate, so that the movable mass block 12 moves radially along the flywheel disc 10 and can stay at any position of the radial sliding guide rail 18, and the moment of inertia of the flywheel with variable moment of inertia is changed due to different distances between the movable mass block 12 and the rotation center, so that the inertia coefficient of the inertial container is changed in a larger range.
More specifically: the longitudinal mass block 2 is a main mass element of the VISA-TMDI, and the physical mass of the variable inertial container 5 is a part of the mass element besides providing the inertial coefficient, so that the mass of each element can be utilized to the maximum extent, and the control effect of the VISA-TMDI is improved. The springs 3 are used for connecting the outer frame 1 and the longitudinal mass blocks 2, the rigidity of the springs 3 is selected according to the frequency corresponding to the highest order target mode, meanwhile, the allowable value of static elongation of the springs is considered, and the total rigidity of the springs meets the following conditions:
wherein k is 1 Is the total stiffness of the spring; m is m 1 And m 2 The mass of the longitudinal mass block and the physical mass of the variable inertial container are respectively; omega max The circular frequency corresponding to the highest order target mode; g is gravity acceleration; [ delta ] st ]Is the allowable value of the static elongation of the spring;
when the longitudinal mass block 2 moves up and down, due to the action of the gear 6, the flywheel 8 with variable rotational inertia moves horizontally along with the longitudinal mass block and rotates around the circle center, so that the characteristic of the inertial container is realized. The movable mass block 12 on the flywheel disc 10 can drive the movable mass block 12 to move along the radial direction through the small motor 13 and the screw rod 11 according to the actual inertia coefficient requirement, so as to change the moment of inertia of the flywheel with variable moment of inertia, thereby changing the inertia coefficient of the inertia container; the inertial coefficient of the variable inertial container 5 is:
wherein r is the diameter of the gear reference circle; j (J) 1 The rotary inertia of the flywheel wheel disc, the small motor, the screw rod and the fixed support relative to the circle center is adopted; m is m li Is the i-th active mass; r is (r) li The distance between the ith movable mass block and the center of the flywheel disc is the distance between the ith movable mass block and the center of the flywheel disc; n is the number of movable mass blocks;
the actual working frequency of the inertial container of the variable inertial semi-actively tuned mass damper is as follows:
wherein,the nominal frequency of the mass damper inertial vessel is tuned semi-actively for the variable inertial mass.
When k is 1 After the determination of the formula (1), the nominal frequency of the VISA-TMDI is fixed, the static elongation of the spring is only related to the nominal frequency, the requirement of the actual installation space is met, the nominal frequency is greater than or equal to the highest order target modal frequency, and the actual working frequency of the VISA-TMDI is reduced by increasing the inertial coefficient, so that the actual working frequency is regulated within a wider frequency range.
In embodiment 1, the variable inertial container 5 can realize the inertial coefficient far greater than the physical mass thereof, so the mass of the movable mass block 12 is far smaller than the inertial coefficient thereof, compared with the conventional SA-TMD, the required energy of the VISA-TMDI proposed in this embodiment is significantly reduced, and the inertial coefficient can be adjusted in a large range, so that the actual operating frequency adjustment range of the VISA-TMDI is significantly increased.
Embodiment 2 differs from embodiment 1 in that the number of movable masses 12 and radial sliding guides 18 is three.
Embodiment 3 differs from embodiment 1 in that the number of movable masses 12 and radial sliding guides 18 is eight.
Embodiment 4 differs from embodiment 1 in that the number of movable masses 12 and radial sliding guides 18 is five.
Embodiment 5 differs from embodiment 1 in that a ball screw is used instead of a rack and pinion to achieve the motion relationship transmission.
Example 6: the embodiment provides a frequency tuning method of a variable inertial semi-actively tuned mass damper inertial container, which is realized based on the variable inertial semi-actively tuned mass damper inertial container in embodiment 1. According to the incoming flow wind speed of the bridge and the Stohar number of the section of the main beam, the vortex-shedding frequency is calculated, so that the mode frequency of the main beam, in which vortex-induced vibration possibly occurs, is estimated, and is fed back to the control system, the required inertial capacity coefficient and the corresponding radial position of the movable mass block are calculated by combining the dynamic characteristics of TMDI, and the movable mass block is driven by a small motor and a screw rod to move to the required position along the radial direction, so that the frequency tuning of VISA-TMDI is realized.
The method comprises the following steps: when the multi-order mode vortex-induced vibration of the main girder of the large-span bridge is controlled, the average wind speed of 5-15 min flowing through the main girder is measured by a wind speed anemometer arranged on the bridge deck, and the vortex-shedding frequency is calculated according to the Stokes number of the section of the main girder, namely:
st is Stoher number of the section of the girder, U is the incoming wind speed, D is the size of the windward side of the section of the girder, and is generally the height of the girder;
mode information obtained by combining finite element models of bridges is combined, and mode frequency omega of vortex vibration possibly occurring is estimated t The desired inertial coefficient is obtained by the formula (5):
the movable mass blocks have equal mass and equal distance from the center of the flywheel disc, and the distance from the movable mass blocks to the center of the flywheel disc is calculated by the method (6):
wherein m is l Mass for a single movable mass;
the movable mass block is driven to move to a designated position by controlling the small motor, so that the working frequency of the inertial container of the variable inertial semi-active tuning mass damper is adjusted, and frequency tuning is realized.
As vortex-induced vibration is generally single-mode vibration and the vibration frequency is highly related to the incoming wind speed, the frequency tuning method of the variable inertial semi-active tuned mass damper inertial container provided by the embodiment can effectively control multi-order mode vortex-induced vibration of a large-span bridge.
The above embodiments are only for illustrating the technical solution of the present invention, and are not limiting thereof; although the invention has been described in detail with reference to the above embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the technical solutions according to the embodiments of the present invention.
Furthermore, it should be understood that although the present disclosure describes embodiments in terms of embodiments, not every embodiment is provided with a separate technical solution, and this description is for clarity only, and those skilled in the art should consider the disclosure as a whole, and the technical solutions in the embodiments may be combined appropriately to form other embodiments that can be understood by those skilled in the art.
Claims (6)
1. The inertial container of the variable inertial semi-active tuned mass damper is used for controlling multi-order mode vortex-induced vibration of a main girder of a large-span bridge, and is characterized in that: comprises a tuned mass damper and a variable inertial mass inertial container (5); the tuned mass damper comprises an outer frame (1), a longitudinal mass block (2), a spring (3) and a viscous damper (4); the longitudinal mass block (2) is arranged in the outer frame (1) and is connected with a top plate of the outer frame (1) through a spring (3) and a viscous damper (4), and an avoidance notch is formed in the longitudinal mass block (2); the variable inertial container (5) comprises a gear (6), a rack (7), a variable moment of inertia flywheel (8), a deep groove ball bearing (9) and a rotating shaft; the variable inertial container (5) is arranged in the outer frame (1); the rack (7) penetrates through the avoidance notch on the longitudinal mass block (2), and the upper end and the lower end of the rack are connected with the top plate and the bottom plate of the outer frame (1); the rotating shaft transversely penetrates through the longitudinal mass block (2), and a rotating connection relation is established between the rotating shaft and the longitudinal mass block (2) through a deep groove ball bearing (9); a gear (6) is arranged in the middle of the rotating shaft, the gear (6) is arranged in an avoidance notch on the longitudinal mass block (2), and the gear (6) is meshed with a rack (7); two ends of the rotating shaft are respectively provided with a flywheel (8) with variable moment of inertia;
the variable-rotational-inertia flywheel (8) comprises a flywheel wheel disc (10), a screw rod (11), a movable mass block (12), a small motor (13), a fixed support (14) and a radial sliding guide rail (18); the flywheel wheel disc (10) is fixedly connected with the rotating shaft, and a plurality of radial sliding guide rails (18) are arranged on the flywheel wheel disc (10); the inner end of the radial sliding guide rail (18) is provided with a small motor (13), and the outer end of the radial sliding guide rail is provided with a fixed support (14); the inner end of the screw rod (11) is connected with the output end of the small motor (13), and the outer end of the screw rod (11) is connected with the fixed support (14); the movable mass block (12) is in threaded connection with the screw rod (11) and is matched with the radial sliding guide rail (18) to move along the radial direction of the flywheel disc (10); the screw rod is driven to rotate by the small motor, so that the movable mass block moves along the radial direction of the flywheel disc and stays at any position of the radial sliding guide rail, and the rotational inertia of the flywheel with variable rotational inertia is changed due to different distances between the movable mass block and the rotational center, so that the inertial coefficient of the inertial container is changed;
the total stiffness of the spring (3) satisfies:
wherein k is 1 Is the total stiffness of the spring; m is m 1 And m 2 The mass of the longitudinal mass block and the physical mass of the variable inertial container are respectively; omega max The circular frequency corresponding to the highest order target mode; g is gravity acceleration; [ delta ] st ]Is the allowable value of the static elongation of the spring;
the inertial coefficient of the variable inertial container (5) is:
wherein r is the diameter of the gear reference circle; j (J) 1 The rotary inertia of the flywheel wheel disc, the small motor, the screw rod and the fixed support relative to the circle center is adopted; m is m li Is the i-th active mass; r is (r) li The distance between the ith movable mass block and the center of the flywheel disc is the distance between the ith movable mass block and the center of the flywheel disc; n is the number of movable mass blocks;
the actual working frequency of the inertial container of the variable inertial semi-actively tuned mass damper is as follows:
wherein,semi-actively tuning mass damping for variable inertial massNominal frequency of inertial vessel.
2. The variable inertial semi-actively tuned mass damper inertial vessel of claim 1, wherein: the movable mass block (12) moves along the radial direction of the flywheel disc (10) through the cooperation of the balls (17) and the radial sliding guide rail (18).
3. A variable inertial semi-actively tuned mass damper inertial vessel according to claim 1 or 2, characterized in that: the outer frame (1) is a square frame, and the movable mass blocks (12) and the radial sliding guide rails (18) are consistent in number and are three to eight.
4. A variable inertial semi-actively tuned mass damper inertial vessel according to claim 3, wherein: the flywheel wheel disc (10) is made of aluminum alloy materials, meanwhile, the inside of the flywheel wheel disc is hollowed out, the movable mass block (12) is made of high-density materials, and the inside of the flywheel wheel disc is hollowed out.
5. The variable inertial semi-actively tuned mass damper inertial vessel of claim 4, wherein: the inner end of the screw rod (11) is connected with the small motor (13) through a single angular contact ball bearing (15), and the outer end of the screw rod (11) is connected with the fixed support (14) through two angular contact ball bearings (15).
6. A method for frequency tuning of a variable inertial semi-actively tuned mass damper inertial vessel, the method being implemented based on the variable inertial semi-actively tuned mass damper inertial vessel of claim 5, characterized by: the method comprises the following specific steps:
when the multi-order mode vortex-induced vibration of the main girder of the large-span bridge is controlled, the average wind speed in 5-15 min flowing through the main girder is measured by a wind speed anemometer arranged on the bridge deck, and the vortex-shedding frequency is calculated according to the Stokes number of the section of the main girder, namely:
st is Stoher number of the section of the main beam, U is incoming wind speed, and D is the size of the windward side of the section of the main beam;
mode information obtained by combining finite element models of bridges is combined, and mode frequency omega of vortex vibration possibly occurring is estimated t The desired inertial coefficient is obtained by the formula (5):
the movable mass blocks have equal mass and equal distance from the center of the flywheel disc, and the distance from the movable mass blocks to the center of the flywheel disc is calculated by the method (6):
wherein m is l Mass for a single movable mass;
the movable mass block is driven to move to a designated position by controlling the small motor, so that the working frequency of the inertial container of the variable inertial semi-active tuning mass damper is adjusted, and frequency tuning is realized.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211320086.7A CN115637638B (en) | 2022-10-26 | 2022-10-26 | Inertial container of variable inertial semi-active tuning mass damper and frequency tuning method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211320086.7A CN115637638B (en) | 2022-10-26 | 2022-10-26 | Inertial container of variable inertial semi-active tuning mass damper and frequency tuning method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115637638A CN115637638A (en) | 2023-01-24 |
| CN115637638B true CN115637638B (en) | 2024-01-12 |
Family
ID=84947108
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211320086.7A Active CN115637638B (en) | 2022-10-26 | 2022-10-26 | Inertial container of variable inertial semi-active tuning mass damper and frequency tuning method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115637638B (en) |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102506122A (en) * | 2011-10-08 | 2012-06-20 | 江苏大学 | Gear rack type inertial container with variable inertial coefficient |
| CN104455203A (en) * | 2014-11-19 | 2015-03-25 | 江苏大学 | Inertial container with two-level adjustable inertial mass coefficients |
| CN205557887U (en) * | 2016-04-11 | 2016-09-07 | 中铁大桥科学研究院有限公司 | Solid harmonious mass damper of coupling of controlled structural vertical stream |
| CN109667358A (en) * | 2019-02-01 | 2019-04-23 | 青岛理工大学 | Adaptive mechanical driving adjusts rotational inertia type control system |
| CN109736466A (en) * | 2019-02-27 | 2019-05-10 | 湖南大学 | The multiple tuning quality eddy current damper of close-coupled for structural vibration control |
| CN111139730A (en) * | 2020-02-11 | 2020-05-12 | 东南大学 | Low-frequency vertical tuned mass damper with negative-stiffness nonlinear energy trap |
| CN112594316A (en) * | 2020-12-17 | 2021-04-02 | 华中科技大学 | Inertial mass damping system with adjustable inertial mass coefficient |
| CN216380080U (en) * | 2021-11-15 | 2022-04-26 | 中铁大桥局集团有限公司 | Ultra-low frequency tuned mass inertial mass damper |
| CN114912324A (en) * | 2022-05-20 | 2022-08-16 | 哈尔滨工业大学 | Distributed MTMDI-based multi-order vortex-induced vibration control method for large-span bridge |
| JP2022140357A (en) * | 2021-03-11 | 2022-09-26 | 株式会社免制震ディバイス | Rotational inertia mass damper and setting method of its equivalent mass |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011142980A2 (en) * | 2010-05-13 | 2011-11-17 | Lawrence Pumps, Inc. | Vibration damping device for vertically cantilevered pump assemblies |
| US11248389B2 (en) * | 2019-09-20 | 2022-02-15 | Dalian University Of Technology | Inertial mass amplification type tuned mass damper |
-
2022
- 2022-10-26 CN CN202211320086.7A patent/CN115637638B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102506122A (en) * | 2011-10-08 | 2012-06-20 | 江苏大学 | Gear rack type inertial container with variable inertial coefficient |
| CN104455203A (en) * | 2014-11-19 | 2015-03-25 | 江苏大学 | Inertial container with two-level adjustable inertial mass coefficients |
| CN205557887U (en) * | 2016-04-11 | 2016-09-07 | 中铁大桥科学研究院有限公司 | Solid harmonious mass damper of coupling of controlled structural vertical stream |
| CN109667358A (en) * | 2019-02-01 | 2019-04-23 | 青岛理工大学 | Adaptive mechanical driving adjusts rotational inertia type control system |
| CN109736466A (en) * | 2019-02-27 | 2019-05-10 | 湖南大学 | The multiple tuning quality eddy current damper of close-coupled for structural vibration control |
| CN111139730A (en) * | 2020-02-11 | 2020-05-12 | 东南大学 | Low-frequency vertical tuned mass damper with negative-stiffness nonlinear energy trap |
| CN112594316A (en) * | 2020-12-17 | 2021-04-02 | 华中科技大学 | Inertial mass damping system with adjustable inertial mass coefficient |
| JP2022140357A (en) * | 2021-03-11 | 2022-09-26 | 株式会社免制震ディバイス | Rotational inertia mass damper and setting method of its equivalent mass |
| CN216380080U (en) * | 2021-11-15 | 2022-04-26 | 中铁大桥局集团有限公司 | Ultra-low frequency tuned mass inertial mass damper |
| CN114912324A (en) * | 2022-05-20 | 2022-08-16 | 哈尔滨工业大学 | Distributed MTMDI-based multi-order vortex-induced vibration control method for large-span bridge |
Non-Patent Citations (1)
| Title |
|---|
| 郭应龙主编.《机械动力学》.水利电力出版社,1994,第6-7页. * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN115637638A (en) | 2023-01-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20180252287A1 (en) | Vibration absorber having a rotating mass | |
| CN111164326B (en) | Rotary damper and vibration damper equipped with the same | |
| US10718232B2 (en) | Vibration absorber having an electromagnetic brake for wind turbines | |
| EP2295795A1 (en) | System and method for damping vibrations in a wind turbine | |
| US11255409B2 (en) | Rotating vibration absorber comprising a belt drive | |
| CN103086237A (en) | Elevator with vibration damper | |
| CN111086662B (en) | Three-dimensional active gravity unloading device suitable for multi-degree-of-freedom experimental object | |
| US11965578B2 (en) | Method for inerter with adaptively adjusted inertia ratio | |
| CN115637638B (en) | Inertial container of variable inertial semi-active tuning mass damper and frequency tuning method | |
| CN109577363A (en) | A kind of universal vibration tuned mass damper of spherical linkage formula ultralow frequency | |
| CN109654162A (en) | Actively compound variable damping control device for pivoting | |
| CN114775405B (en) | main beam corner control type bridge damping vibration attenuation device | |
| CN201627276U (en) | High-rise building vibration absorbing and cushioning device | |
| AU2010352460A1 (en) | Railway freight car bogie | |
| CN105650194A (en) | Blade type energy-consuming and tuning vibration damper | |
| CN105465261A (en) | Electromagnetic energy feeding type vehicle active suspension actuator and control method thereof | |
| CN112257194B (en) | Design method for inertia ratio self-adaptive adjustment inertia container | |
| CN109667358B (en) | Self-adaptive mechanical driving adjusting rotary inertia type control system | |
| CN112832399B (en) | Multistage self-adaptive composite inertial volume vibration reduction device, method and structure | |
| CN113982137A (en) | Inertial volume type multidirectional tuning energy-absorbing vibration-damping device | |
| CN210476951U (en) | Series elastic driving device | |
| CN116043667A (en) | Low-frequency tuning mass damper | |
| CN112160881A (en) | Wind power generation device and installation method thereof | |
| CN108488299B (en) | Inertia mass coefficient adjustable type heavy vehicle inertia container | |
| CN110202567A (en) | A kind of series connection flexible drive device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |