CN115637638A - Variable inertial mass semi-active tuned mass damper inertial container and frequency tuning method - Google Patents
Variable inertial mass semi-active tuned mass damper inertial container and frequency tuning method Download PDFInfo
- Publication number
- CN115637638A CN115637638A CN202211320086.7A CN202211320086A CN115637638A CN 115637638 A CN115637638 A CN 115637638A CN 202211320086 A CN202211320086 A CN 202211320086A CN 115637638 A CN115637638 A CN 115637638A
- Authority
- CN
- China
- Prior art keywords
- variable
- mass
- inertance
- mass block
- semi
- 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.)
- Granted
Links
- 238000000034 method Methods 0.000 title claims abstract description 24
- 230000003068 static effect Effects 0.000 claims abstract description 16
- 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
- 238000013461 design Methods 0.000 claims description 3
- 230000005484 gravity Effects 0.000 claims description 3
- 239000000463 material Substances 0.000 claims description 3
- 239000000126 substance Substances 0.000 claims description 3
- 230000002829 reductive effect Effects 0.000 description 6
- 238000013016 damping Methods 0.000 description 5
- 230000033001 locomotion Effects 0.000 description 5
- 238000009434 installation Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000009471 action 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
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000011796 hollow space material Substances 0.000 description 1
- 230000002401 inhibitory effect Effects 0.000 description 1
- 230000000670 limiting 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
- 230000036961 partial effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 238000013519 translation Methods 0.000 description 1
Images
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
An inertial container of a variable inertial mass semi-active tuned mass damper and a frequency tuning method belong to the technical field of structural vibration control. The invention solves the problems that the conventional TMD cannot be applied due to overlarge static extension when controlling the vertical vibration of a low-frequency structure and the possibility of multi-stage vortex vibration exists due to the dense mode of a long-span bridge. The invention introduces an inertial container with variable inertial mass on the basis of a traditional tuned mass damper, realizes frequency tuning of TMDI (tuned mass damper) by changing the inertial volume coefficient of the inertial container, calculates vortex shedding frequency according to the incoming flow wind speed of a bridge and the Stero-Roh number of the section of a girder, estimates the modal frequency of the girder which is likely to generate vortex-induced vibration, calculates the required inertial volume coefficient and the corresponding radial position of a movable mass block by combining the dynamic characteristics of TMDI, and drives the movable mass block to move to the required position along the radial direction by a small motor and a screw rod to realize frequency tuning. The method is applied to multi-order modal vortex-induced vibration control of the large-span bridge.
Description
Technical Field
The invention relates to a semi-active tuned mass damper inerter and a frequency tuning method, in particular to a variable inerter semi-active tuned mass damper inerter and a frequency tuning method, and belongs to the technical field of structural vibration control.
Background
When the near-earth wind in the boundary layer bypasses the bridge, flow separation is generated on the windward side of the main beam, and vortex shedding which changes alternately is generated on the upper surface and the lower surface of the main beam, and vortex-induced resonance is generated when the vortex shedding frequency is close to or equal to a certain self-vibration frequency of the structure. Although the vortex vibration is amplitude-limiting vibration with self-excitation property and does not directly affect the safety of the bridge structure, the vortex vibration generally occurs under the condition of low wind speed, the frequency is high, the driving comfort and the safety of the bridge are seriously affected, and the long-term fatigue problem is caused. Therefore, the method has very important significance for eliminating or inhibiting the vortex-induced vibration of the large-span bridge.
Tuned Mass Damper (TMD) is one of the common methods for large-span bridge vortex vibration control because it has high-efficiency single-mode damping performance. However, due to the mechanical structure and the tuning-based damping mechanism, the static extension of the TMD is inversely proportional to the square of the tuning frequency, and when vibration control is performed on a large-span bridge, the static extension of the TMD is too large due to lower frequency, and is not suitable under the condition that the installation space inside the main beam is limited, and extra measures such as a lever and a pre-stressed spring are often required to limit the static extension of the main beam. In addition, the frequency distribution of the large-span bridge is dense, the possibility of vortex vibration in multiple modes exists under the designed passing wind speed, the vortex vibration control target cannot be realized if only one mode is controlled, and the TMD is only effective in a single mode, so that when the vortex vibration control is performed on the large-span bridge, a plurality of sets of TMDs need 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 the 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 (SA-TMD), and the damping ratio is adjusted through electromagnetic characteristics or the frequency is adjusted through a guide rail moving mass block in a commonly used parameter adjusting method at present, so that the traditional SA-TMD is difficult to adapt to vibration control in a wider frequency range, and the required external energy input is larger.
In recent years, a double ended mass element (inerter) has been used to improve conventional vibration control methods. The inerter can convert linear motion into high-speed rotation, provides counter force in direct proportion to relative acceleration at two ends, and can realize inertia mass far higher than physical mass. The inerter was connected in parallel with the spring and damping elements of a conventional TMD to yield a Tuned Mass Damper Inerter (TMDI). Because the inertial container has a dynamic negative stiffness effect, the TMDI has the characteristics of high static stiffness and low dynamic stiffness, when the vertical vibration of a low-frequency structure is controlled, the static elongation of the TMDI is obviously lower than that of the traditional TMD, the required installation space is smaller, and the TMDI has a wide application prospect in the control of the vortex-induced vibration of a large-span bridge.
Disclosure of Invention
In view of the facts, the invention provides a variable inerter semi-active tuned mass damper inerter and a frequency tuning method aiming at the problems that the conventional TMD cannot be applied due to overlarge static elongation when controlling the vertical vibration of a low-frequency structure and the problems that the large-span bridge is dense in mode and multi-stage vortex vibration is possible. On the basis of a traditional tuned mass damper, an inertial container with variable inertial mass is introduced, the incoming flow wind speed is monitored through a wind speed and wind direction meter arranged on a bridge, the mode possibly generating vortex vibration is predicted according to the Strouhal number of the section of a main beam, and the inertial volume coefficient of the inertial container is adjusted, so that TMDI is always in a tuned state.
In order to achieve the purpose, the invention adopts the following technical scheme:
a variable inertia semi-active tuned mass damper inerter (VISA-TMDI) including a tuned mass damper and a variable inertia inerter; the tuned 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 mass inertial container comprises a gear, a rack, a variable rotational inertia flywheel, a deep groove ball bearing and a rotating shaft; the variable inerter inertial container is arranged inside the outer frame; the rack penetrates through an avoidance notch in the longitudinal mass block, and the upper end and the lower end of the rack are connected with a top plate and a bottom plate of the outer frame; the rotating shaft transversely penetrates through the longitudinal mass block and establishes a rotating connection relation with the longitudinal mass block through the deep groove ball bearing; a gear is arranged in the middle of the rotating shaft, the gear is arranged in an avoidance notch on the longitudinal mass block, and the gear is meshed with the rack; two ends of the rotating shaft are respectively provided with a variable rotational inertia flywheel.
Further, the method comprises the following steps: the variable rotational 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 wheel disc. So set up, through the rotation of small-size motor drive lead screw to make the movable mass piece along flywheel rim plate radial movement, and can stop in radial sliding guide's optional position, because the distance of movable mass piece from the center of rotation is different, the inertia of variable inertia flywheel also changes along with it, thereby realizes changing the inertial volume coefficient of being used to the container in a relatively large scale.
Further: the movable mass block is matched with the radial sliding guide rail through a ball to move along the radial direction of the flywheel wheel disc. In order to reduce the driving torque of the small motor, balls are arranged between the movable mass block and the radial sliding guide rail, sliding friction can be converted into rolling friction by the balls, and 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 consistent in number and are all three to eight.
Further: the outer frame is a square frame. The top plate and the bottom plate of the square frame are used for fixing or connecting various components of the variable inertance semi-active tuned mass damper VISA-TMDI.
Further: six radial sliding guide rails are arranged on the flywheel wheel disc. For guiding the movable mass to move along the radial direction of the flywheel.
Further: the longitudinal mass block is a main mass element of the VISA-TMDI, and the variable inertial mass inertial container provides an inertial volume coefficient, and the physical mass of the variable inertial mass inertial container is also a part of the mass element, 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 stiffness of the spring is selected according to the frequency corresponding to the highest-order target mode, the static elongation allowable value of the spring is considered, and the total stiffness of the spring meets the following requirements:
wherein k is 1 Is the overall spring rate; m is 1 And m 2 Respectively the mass of the longitudinal mass block and the physical mass of the variable inertial mass inertial container; omega max The circular frequency corresponding to the highest order target mode; g is the acceleration of gravity; [ delta ] is st ]Is the allowable value of the static elongation of the spring.
Further: when the longitudinal mass block moves up and down, the variable rotational inertia flywheel moves along with the longitudinal mass block in a translation manner and also rotates around the circle center due to the action of the gear, 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 lead screw according to the actual inertia capacity coefficient requirement, so that the rotational inertia of the flywheel with the variable rotational inertia is changed, and the inertia capacity coefficient of the inertia container is changed. The inerter-inertial volume coefficient of the variable inerter-inertial container is as follows:
wherein r is the gear reference circle diameter; j. the design is a square 1 The moment of inertia of the flywheel wheel disc, the small motor, the lead screw and the fixed support relative to the circle center; m is li Mass of the ith movable mass block; r is li The distance between the ith movable mass block and the center of the flywheel wheel disc is the distance between the ith movable mass block and the center of the flywheel wheel disc; n is the number of the movable mass blocks.
Further: in order to realize the adjustment of the inertia capacity coefficient in a wider range, namely, the mass ratio of the movable mass block in the whole variable inertia flywheel is increased, the flywheel wheel disc is made of an aluminum alloy material, meanwhile, the inner part of the flywheel wheel disc is hollowed, and the movable mass block is made of a high-density material, such as lead, and the inner part of the movable mass block is also hollowed.
Further: the inner end of the screw rod is connected with the small motor through a single angular contact ball bearing to serve 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 the 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 variable inerter semi-active tuned mass damper inerter is as follows:
wherein the content of the first and second substances,
and (3) the nominal frequency of the inertance damper inertance vessel is tuned for the variable inertance semi-active tuning.
So designed that when k is 1 After the nominal frequency of the VISA-TMDI is determined by 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 an actual installation space is met, the nominal frequency is larger than or equal to the highest-order target modal frequency, the inertial capacity coefficient is increased, the actual working frequency of the VISA-TMDI can be reduced, and therefore the actual working frequency can be adjusted in a wide frequency range.
In order to achieve the purpose, the invention adopts the following technical scheme II:
the method for tuning the frequency of the variable inerter semi-actively tuned mass damper inerter is realized based on the variable inerter semi-actively tuned mass damper inerter in the technical scheme I. The method specifically comprises the following steps:
when the multi-order modal vortex-induced vibration of the girder of the long-span bridge is controlled, the average wind speed flowing through the girder within 5-15 min is measured by the anemorumbometer arranged on the bridge deck, and the vortex shedding frequency is calculated according to the stetholo number of the section of the girder, namely:
wherein St is the Strouhal number of the section of the main beam, U is the incoming wind speed, and D is the size of the windward side of the section of the main beam, generally the height of the main beam;
the modal information obtained by combining the finite element model of the bridge is combined to estimate the modal frequency omega which is likely to generate vortex vibration t The required coefficient of inertia is obtained by the formula (5):
the mass of the movable mass block is equal, and the distance from the movable mass block to the center of the flywheel wheel disc is calculated by the formula (6):
wherein m is l Is a single movable mass;
the movable mass block is driven to move to a specified position by controlling the small motor, so that the working frequency of the variable inertial mass semi-active tuned mass damper inertial container is adjusted, and frequency tuning is realized.
The invention has the following beneficial effects:
1. the inertial container is introduced into the traditional TMD, so that the TMD has the characteristics of high static stiffness-low dynamic stiffness, the static extension of the spring can be obviously reduced, and the TMD can be used for controlling the vertical vibration of the main beam of the long-span bridge;
2. the invention provides a variable inerter semi-active tuned mass damper inerter, which realizes the required inerter coefficient by changing the radial position of a movable mass block on a flywheel, thereby adjusting the frequency of TMDI (transition minimized differential mode interference) in a wider frequency range;
3. the method utilizes the dynamic characteristics of TMDI, realizes the frequency tuning of TMDI by changing the inertia capacity coefficient of the inertia container, determines the required inertia capacity coefficient according to the incoming flow wind speed and the Stero-Roha number of the section of the girder, and is effectively different from the traditional TMD only in a single mode.
Drawings
FIG. 1 is a perspective view of a variable inertance semi-active tuned mass damper inertance vessel;
FIG. 2 is a front view of a variable inertance semi-active tuned mass damper inertance vessel;
FIG. 3 is a side view of a variable inertance semi-actively tuned mass damper inertance vessel;
FIG. 4 is a top view of a variable inertance semi-actively tuned mass damper inertance vessel (outer frame omitted);
FIG. 5 is a perspective view of a variable inerter;
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 block; 3: a spring; 4: a viscous damper; 5: a variable inerter; 6: a gear; 7: a rack; 8: a variable moment of inertia flywheel; 9: a deep groove ball bearing; 10: a flywheel disk; 11: a screw rod; 12: a movable mass block; 13: a small-sized motor; 14: a fixed support; 15: angular contact ball bearings; 16: fixing screws; 17: a ball bearing; 18: a radial sliding guide rail.
Detailed Description
In order to make the technical solutions better understood by those skilled in the art, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only partial embodiments of the present application, but not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
It should be noted that the terms "first," "second," and the like in the description and claims of this application and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It should be understood that the data so used may be interchanged under appropriate circumstances such that embodiments of the application described herein may be used. 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 this application, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings. These terms are used primarily to better describe the present application and its embodiments, and are not used to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation.
Moreover, some of the above terms may be used to indicate other meanings besides the orientation or positional relationship, for example, the term "on" may also be used to indicate some kind of attachment or connection relationship 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," and "secured" are to be construed broadly. For example, "connected" may be a fixed connection, a detachable connection, or a unitary construction; can 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 above terms in the present application can be understood by those of ordinary skill in the art as appropriate.
It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present application will be described in detail below with reference to the embodiments with reference to the attached drawings.
Preferred embodiments of the present invention are explained in detail below with reference to the accompanying drawings.
Example 1:
referring to fig. 1 to 7, in the present embodiment, a variable inertia semi-active tuned mass damper inerter (VISA-TMDI) is provided, in which a variable inertia flywheel is mainly provided to provide a rotational inertia, and the adjustment of the inertance coefficient of the inerter can be achieved by changing the rotational inertia of the variable inertia flywheel. Because the inerter can realize the inerter coefficient far larger than the physical mass of the inerter, the rotational inertia of the flywheel with the variable rotational inertia can be changed with low cost, and the inerter coefficient of the inerter can be changed in a larger range. The variable inerter semi-active tuned mass damper inerter of the embodiment comprises a tuned mass damper and a variable inerter 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 inside 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, an avoiding notch is formed in the longitudinal mass block 2, and a hollow space is formed in the longitudinal mass block 2 and used for installing the variable inertial mass container 5; the outer frame 1 is a square frame, a top plate and a bottom plate of the square frame are used for fixing or connecting various components of the variable inertial mass semi-active tuned mass damper inertial container VISA-TMDI, and the height of the outer frame 1 is in consideration of the stroke of the longitudinal mass block 2 so as to prevent the two from colliding;
the variable inertia mass inertia container 5 comprises a gear 6, a rack 7, a variable rotational inertia flywheel 8, a deep groove ball bearing 9 and a rotating shaft; the variable inerter 5 is arranged inside the outer frame 1; the rack 7 penetrates through an avoidance notch on the longitudinal mass block 2, and the upper end and the lower end of the rack are connected with a top plate and a bottom plate of the outer frame 1; the rotating shaft transversely penetrates through the longitudinal mass block 2 and establishes a rotating connection relation with 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 avoiding 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 variable rotational inertia flywheel 8;
the variable moment of 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 six 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-sized 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 wheel disc 10, in order to reduce the driving torque of the small motor, a ball 17 is arranged between the movable mass block 12 and the radial sliding guide rail 18, the ball 17 can convert sliding friction into rolling friction, and the friction force between the movable mass block and the radial sliding guide rail is obviously reduced; in order to realize the adjustment of the inertia capacity coefficient in a wider range, namely to increase the mass ratio of the movable mass block in the whole variable inertia flywheel, the flywheel wheel disc 10 is made of an aluminum alloy material, and meanwhile, the inside of the flywheel wheel disc is hollowed, and the movable mass block 12 is made of a high-density material, such as lead, and the inside of the flywheel wheel disc is also hollowed; the inner end of the screw rod 11 is connected with a small motor 13 through a single angular contact ball bearing 15 to serve 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 the 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 along the radial direction of the flywheel wheel disc 10 and can stay at any position of the radial sliding guide rail 18, and the rotary inertia of the flywheel with variable rotary inertia is changed along with the different distances from the rotary center of the movable mass block 12, so that the inertial volume 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 variable inertance inertial container 5 provides an inertial volume coefficient, and the physical mass of the variable inertance inertial container is a part of the mass element, 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 3 is used for connecting the outer frame 1 and the longitudinal mass block 2, the stiffness of the spring 3 is selected according to the frequency corresponding to the highest-order target mode, and the allowable value of the static extension of the spring is considered, so that the total stiffness of the spring meets the following requirements:
wherein k is 1 Is the overall spring rate; m is a unit of 1 And m 2 Respectively the mass of the longitudinal mass block and the physical mass of the variable inertial mass inertial container; omega max The circular frequency corresponding to the highest order target mode; g is the acceleration of gravity; [ Delta ] of st ]Is the allowable value of the static elongation of the spring;
when the longitudinal mass block 2 moves up and down, the variable rotational inertia flywheel 8 also rotates around the circle center besides translating along with the longitudinal mass block due to the action of the gear 6, so that the characteristic of the inertial container is realized. The movable mass block 12 on the flywheel wheel disc 10 can drive the movable mass block 12 to move along the radial direction through the small motor 13 and the lead screw 11 according to the actual inertia capacity coefficient requirement, so that the rotational inertia of the flywheel with variable rotational inertia is changed, and the inertia capacity coefficient of the inertia container is changed; the inerter-inertia coefficient of the variable inerter-inertia vessel 5 is as follows:
wherein r is the gear reference circle diameter; j. the design is a square 1 The flywheel wheel disc, the small motor, the lead screw and the fixed support are relative to the rotational inertia of the circle center; m is li Mass of the ith movable mass block; r is li The distance between the ith movable mass block and the center of the flywheel wheel disc is the distance between the ith movable mass block and the center of the flywheel wheel disc; n is the number of the movable mass blocks;
the actual working frequency of the variable inerter semi-active tuned mass damper inerter is as follows:
wherein the content of the first and second substances,
and (3) the nominal frequency of the inertance damper inertance vessel is tuned for the variable inertance semi-active tuning.
When k is 1 Nominal frequency of VISA-TMDI after determination by equation (1)The spring is fixed, the static extension of the spring is only related to the nominal frequency, the requirement of an actual installation space is met, the nominal frequency is larger than or equal to the highest-order target modal frequency, the inertial capacitance coefficient is increased, the actual working frequency of the VISA-TMDI can be reduced, and therefore the actual working frequency can be adjusted in a wide frequency range.
In embodiment 1, since the variable inerter-inertial container 5 can realize an inerter coefficient much larger than its physical mass, the mass of the movable mass block 12 is much smaller than the inerter coefficient realized by the variable inerter-inertial container, compared with the conventional SA-TMD, the VISA-TMDI proposed in this embodiment has significantly reduced energy requirement, and the inerter coefficient can be adjusted in a large range, so that the actual operating frequency adjustment range of the VISA-TMDI is significantly increased.
Embodiment 4 differs from embodiment 1 in that the number of movable masses 12 and radial sliding guides 18 is five.
Example 6: the embodiment provides a frequency tuning method for a variable inerter semi-actively tuned mass damper inerter, which is implemented based on the variable inerter semi-actively tuned mass damper inerter described in embodiment 1. The vortex shedding frequency is calculated according to the incoming flow wind speed of the bridge and the Stero-Ha number of the section of the girder, so that the modal frequency of the girder which is likely to generate vortex-induced vibration is estimated, the modal frequency is fed back to a control system, the required inertial volume coefficient and the corresponding radial position of the movable mass block are calculated by combining the dynamic characteristics of TMDI, the movable mass block is driven by a small motor and a lead screw to move to the required position in the radial direction, and the VISA-TMDI frequency tuning is realized.
The method specifically comprises the following steps: when the multi-order modal vortex-induced vibration of the girder of the long-span bridge is controlled, the average wind speed of 5-15 min flowing through the girder is measured by the anemorumbometer arranged on the bridge floor, and the vortex shedding frequency is calculated according to the Stollo number of the section of the girder, namely:
wherein St is the Strouhal number of the section of the main beam, U is the incoming wind speed, and D is the size of the windward side of the section of the main beam, generally the height of the main beam;
the modal information obtained by combining the finite element model of the bridge is combined to estimate the modal frequency omega which is likely to generate vortex vibration t The required coefficient of inertia is obtained by the formula (5):
the mass of the movable mass block is equal, and the distance from the movable mass block to the center of the flywheel wheel disc is calculated by the formula (6):
wherein m is l Is a single movable mass;
the movable mass block is driven to move to a specified position by controlling the small motor, so that the working frequency of the variable inertial mass semi-active tuned mass damper inertial container is adjusted, and frequency tuning is realized.
Because the vortex-induced vibration is generally single-mode vibration, and the vibration frequency is highly related to the incoming flow wind speed, the frequency tuning method of the variable inerter semi-active tuned mass damper inerter provided by the embodiment can effectively control the large-span bridge Liang Duojie modal vortex-induced vibration.
The above examples are only for illustrating the technical solutions of the present invention, and not for limiting the same; although the present invention has been described in detail with reference to the above embodiments, it should be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present invention.
Furthermore, it should be understood that although the present description refers to embodiments, not every embodiment may contain only a single embodiment, and such description is for clarity only, and those skilled in the art should integrate the description, and the embodiments may be combined as appropriate to form other embodiments understood by those skilled in the art.
Claims (10)
1. The variable inerter semi-active tuned mass damper inerter is characterized in that: comprises a tuned mass damper and a variable inerter (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 inside 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 inerter-inertia container (5) comprises a gear (6), a rack (7), a variable rotational inertia flywheel (8), a deep groove ball bearing (9) and a rotating shaft; the variable inerter inertial container (5) is arranged inside the outer frame (1); the rack (7) penetrates through an avoidance notch on the longitudinal mass block (2), and the upper end and the lower end of the rack are connected with a top plate and a bottom plate of the outer frame (1); the rotating shaft transversely penetrates through the longitudinal mass block (2) and establishes a rotating connection relation with 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 the rack (7); and two ends of the rotating shaft are respectively provided with a variable rotational inertia flywheel (8).
2. The variable inertance semi-active tuned mass damper inertance vessel of claim 1, wherein: the variable moment of 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 wheel disc (10).
3. The variable inertance semi-active tuned mass damper inertance vessel of claim 2, wherein: the movable mass block (12) is matched with the radial sliding guide rail (18) through a ball (17) to move along the radial direction of the flywheel wheel disc (10).
4. The variable inertance semi-active tuned mass damper inertance vessel of claim 2 or 3, wherein: the outer frame (1) is a square frame, and the number of the movable mass blocks (12) is three to eight, while the number of the movable mass blocks is consistent with that of the radial sliding guide rails (18).
5. The variable inertance semi-active tuned mass damper inertance vessel of claim 4, wherein: the total stiffness of the spring (3) satisfies:
wherein k is 1 Is the overall spring rate; m is 1 And m 2 Respectively the mass of the longitudinal mass block and the physical mass of the variable inertial mass inertial container; omega max The circular frequency corresponding to the highest order target mode; g is gravity acceleration; [ delta ] is st ]Is the allowable value of the static elongation of the spring.
6. The variable inertance semi-active tuned mass damper inertance vessel of claim 5, wherein: the inertance coefficient of the variable inertance vessel (5) is as follows:
wherein r is the gear reference circle diameter; j. the design is a square 1 The moment of inertia of the flywheel wheel disc, the small motor, the lead screw and the fixed support relative to the circle center; m is li Mass of the ith movable mass block; r is li The distance between the ith movable mass block and the center of the flywheel wheel disc is the distance between the ith movable mass block and the center of the flywheel wheel disc; n is the number of the movable mass blocks.
7. The variable inertance semi-active tuned mass damper inertance vessel of claim 4, wherein: the flywheel wheel disc (10) is made of aluminum alloy materials, the interior of the flywheel wheel disc is hollowed, the movable mass block (12) is made of high-density materials, and the interior of the movable mass block is also hollowed.
8. The variable inertance semi-active tuned mass damper inertance vessel of claim 7, 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).
9. The variable inertance semi-active tuned mass damper inertance vessel of claim 6, wherein: the actual working frequency of the variable inerter semi-active tuned mass damper inerter is as follows:
wherein the content of the first and second substances,
and (3) the nominal frequency of the inertance damper inertance vessel is tuned for the variable inertance semi-active tuning.
10. The frequency tuning method of the variable inerter semi-actively tuned mass damper inerter is realized based on the variable inerter semi-actively tuned mass damper inerter of claim 9, and is characterized in that: the method comprises the following specific steps:
when the multi-order modal vortex-induced vibration of the girder of the long-span bridge is controlled, the average wind speed flowing through the girder within 5-15 min is measured by the anemorumbometer arranged on the bridge deck, and the vortex shedding frequency is calculated according to the stetholo number of the section of the girder, namely:
wherein St is the Strouhal number of the section of the main beam, U is the incoming wind speed, and D is the size of the windward side of the section of the main beam;
the modal information obtained by combining the finite element model of the bridge is combined to estimate the modal frequency omega which is likely to generate vortex vibration t The required coefficient of inertia is obtained by the formula (5):
the mass of the movable mass block is equal, the distance between the movable mass block and the center of the flywheel wheel disc is equal, and the distance between the movable mass block and the center of the flywheel wheel disc is calculated by the formula (6):
wherein m is l Is a single movable mass;
the movable mass block is driven to move to a specified position by controlling the small motor, so that the working frequency of the variable inertial mass semi-active tuned mass damper inertial container 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 true CN115637638A (en) | 2023-01-24 |
| CN115637638B 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) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US12017498B2 (en) | 2021-06-07 | 2024-06-25 | Apple Inc. | Mass damper system |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20110278777A1 (en) * | 2010-05-13 | 2011-11-17 | Jason Douglas Allaire | Vibration damping device for vertically cantilevered pump assemblies |
| 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 |
| US20210087841A1 (en) * | 2019-09-20 | 2021-03-25 | Dalian University Of Technology | Inertial mass amplification type tuned mass damper |
| 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 |
-
2022
- 2022-10-26 CN CN202211320086.7A patent/CN115637638B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20110278777A1 (en) * | 2010-05-13 | 2011-11-17 | Jason Douglas Allaire | Vibration damping device for vertically cantilevered pump assemblies |
| 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 |
| US20210087841A1 (en) * | 2019-09-20 | 2021-03-25 | Dalian University Of Technology | Inertial mass amplification type tuned mass damper |
| 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, pages: 6 - 7 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US12017498B2 (en) | 2021-06-07 | 2024-06-25 | Apple Inc. | Mass damper system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN115637638B (en) | 2024-01-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106948256B (en) | A kind of ultralow frequency liquid quality tuned damper and design method | |
| JP6965239B2 (en) | Vibration absorber with rotating mass | |
| CN115637638A (en) | Variable inertial mass semi-active tuned mass damper inertial container and frequency tuning method | |
| EP2458199B1 (en) | Wind turbine with compensated motor torque | |
| CN112257194B (en) | Design method for inertia ratio self-adaptive adjustment inertia container | |
| CN108643666A (en) | A kind of efficient spatial directly supports the damper of second displacement amplifying device using type end | |
| CN111086662B (en) | Three-dimensional active gravity unloading device suitable for multi-degree-of-freedom experimental object | |
| US11390500B2 (en) | Drive drum for overhead doors | |
| CN111287916B (en) | Tuned collision inerter mass damping device for fan | |
| US20230347702A1 (en) | Adaptive damping nonlinear spring-variable damping system and mobile platform system | |
| CN112854506A (en) | Rod type tuned particle mass damping device combined with collision damping | |
| CN109403487B (en) | Semi-active flexible particle collision inertia damper | |
| CN201627276U (en) | High-rise building vibration absorbing and cushioning device | |
| CN115560031A (en) | Ball screw type tuned mass damping inertial container suitable for fan tower | |
| CN216380080U (en) | Ultra-low frequency tuned mass inertial mass damper | |
| CN113982137A (en) | Inertial volume type multidirectional tuning energy-absorbing vibration-damping device | |
| CN210476951U (en) | Series elastic driving device | |
| CN114016631A (en) | Ultra-low frequency tuned mass inertial mass damper | |
| CN109667358A (en) | Adaptive mechanical driving adjusts rotational inertia type control system | |
| CN110202567A (en) | A kind of series connection flexible drive device | |
| CN112832398A (en) | Box type tuning particle mass damping device combined with collision damping | |
| CN114838074B (en) | Constant tension buffer mechanism based on hinge zero-stiffness spring | |
| CN116043667A (en) | Low-frequency tuning mass damper | |
| CN113794318B (en) | Active variable inertial volume damping system | |
| US11815150B1 (en) | Magnetostriction-based vibration suppression apparatus for steel pipe of power transmission tower and suppression method thereof |
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 |