TWI603016B - Device and method for impact semi-active mass vibration adsorption - Google Patents

Description

Impact type semi-active mass damping device and method

The invention relates to an impact semi-active mass damping device and method, in particular to a mass damper technology for reducing vibration response of buildings and civil structures under dynamic load; the invention aims to be semi-automatic The mass damper that controls the separation/combination state implements semi-active damping control, especially that the control mass has more than twice the natural vibration frequency of the controlled structure, and can overcome the off-frequency phenomenon that may occur in the traditional tuned mass damper, and can improve The damping effect of the mass damper is the inventor of its application.

According to the mass damper, it is a kind of structural and mechanical damping technology used to reduce the vibration response of structures under dynamic loads, such as displacement, velocity and acceleration. The utility model is characterized in that a mass block which is lighter than the structure is installed at a specific part of the structure, and the structure and the mass block are connected in a specific manner and generate mutual force. The main focus of its design is that its mutual production force can effectively reduce the vibration response of the main structure; the secondary focus is (1) let the mass and its coupling system absorb the main structure energy and effectively dissipate, and (2) Prevent the mass from reacting too much to the main structure.

The mass damper technology can be broadly divided into three categories: (1) passive tuned mass damper, (2) active mass damper, (3) semi-active mass damper, and the fourth of any two or all of the foregoing. (4) Mixed mass damper.

The first type of passive mass damper is connected between the main structure and the mass by a designed spring and an energy absorbing damper, and the mutual force is generated by the relative movement of the mass and the main structure. Because the mutual force is not actively controllable, it must be completely determined by the external force characteristics and the dynamic properties of the mass-spring-cannon damper, so it is called a passive mass damper. The passive mass damper was the first proposed mass damper technique. It was known at the outset that the mass-spring subsystem can exert extremely significant damping effects when it has a natural vibration frequency similar to that of the main structure. Because the tuning of the frequency is the main parameter of the damping effect, the passive mass damper is also called the Tuned Mass Damper (TMD). Many variants have been proposed, such as replacing the spring with a single pendulum suspension to allow the mass to oscillate significantly, replacing the mass column-spring-damping damper with a liquid column damper (Liquid Column Damper (LCD)). The main disadvantages of the tuned mass damper are two: (1) a large device space is required to allow the mass movement to limit the usability, and (2) Detunning-effect - to reduce the damping effect. The phenomenon of off-frequency means that the natural vibration frequency ratio of the subsystem and the main structure exceeds the effective range, which may occur in the case of poor design, changes in usage conditions, and entry of the main structure into the inelastic state under strong earthquakes. Therefore, in recent years, there have been some new ideas, among which the technology of expanding the effective frequency range by multi-mass methods with different natural frequencies is the most representative. Since the seismic force is a transient dynamic force, the tuned mass damper has a poor control effect on the maximum displacement of the structure, so the tuned mass damper is mainly used for the super high-rise structure to resist wind.

There is no significant correlation between the development of the second active mass damper-active mass damper and the tuned mass damper. The basic components of the active mass damper are mass, actuator, controller, A motion sensor, an energy supply unit, and a support rail device. The working principle is: when the structure is subjected to dynamic load to generate motion (displacement, velocity, acceleration), the motion sensor converts the necessary motion physical quantity into an electronic signal, and the controller is based on the previously established control law and the sensor. The signal determines the control that should be generated on the main structure, and this control force is generated by the reaction force generated by the actuator pushing/pulling the mass. Therefore, the controller generates an actuator control command according to the control force demand, and the actuator generates a control force for the main structure during the acceleration/deceleration of the mass. The main application of active mass dampers in earthquakes or winds is not to provide better damping than tuned mass dampers, but rather to reduce the amount of displacement of the mass, allowing for applications where space is limited. In addition, its problem of no off-frequency effect is also an important advantage. The control force determined according to the control law needs to be provided by the energy supply unit, such as a hydraulic pump, a high-voltage power supply, etc., so the active mass damper has an dependence on external energy. Active mass dampers require many components such as inductors, controllers, precision-controlled actuators, and huge energy supplies. Due to the high cost of setup, reliability is relatively questionable. Therefore, the active mass damper is practically used to improve the usability and comfort of the structure, rather than for the purpose of improving safety.

The third semi-active mass damper refers to calculating the control force according to the control law of the active control method, and releasing the spring coupling between the mass block and the main structure when the direction of the actual mutual force is opposite to the direction of the demand control force, and instantaneously releasing the mass. Spring strain energy between the main structure and the main structure. Continue to calculate the control force according to the active control law control law, and judge the direction of the mutual production force generated by the restoration mass block and the main structure connection. When the estimated mutual force direction is the same as the demand control force direction, the mass block and the main structure are restored. Spring connection between the two. Under this logic, the spring between the mass and the main structure approximates the natural vibration frequency of the mass to the fundamental vibration frequency of the structure and is typically slightly larger than the fundamental vibration frequency of the main structure. According to the active control law, the control law must immediately take the displacement and velocity response of the controlled structure at equal intervals, and substitute these reactions into the control law to obtain the spring between the coupling or the uncoupling and the mass. Its control law usually leads to the following: If the active joint state is "on", then when V _s ×( V _s - V _c ) 0 is switched to "off"; if the active joint state is "off", it is switched to "on" when V _s × F _c >0; where V _s is the moving speed of the structure and V _c is the mass The speed of motion, F _c is the force of the spring on the structure, and the positive direction and the speed of the structure are defined the same. According to this control law, the mass can be guaranteed to perform negative work on the controlled structure, but it does not necessarily exert the maximum energy dissipation effect.

Such a semi-active mass damper combines the variable tunability of a passive tuned mass damper into a variable variability in an active mass damper. However, because its control law is directly modified from the active mass damper, it is not derived from the vibration characteristics, and the damping effect is similar to that of the passive tuning mass damper.

Today, the inventor has been researching and improving the existing structure for many years of research, design and development and practical production experience in this related industry, providing an impact semi-active mass damper device and method to achieve better practical value. Target person.

The main object of the present invention is to provide an impact type semi-active mass damper device and method, in particular to a control mass having twice or more natural vibration frequency of a controlled structure, and capable of overcoming the frequency deviation that may occur in a conventional tuned mass damper. Phenomenon, and can improve the damping effect of the mass damper for its purpose.

The main purpose and effect of the method for using the impact type semi-active mass damper device and method of the present invention are achieved by the following specific technical means: the impact type semi-active mass damper device is mainly installed on the controlled structure, and includes a control mass, an activity unit, a vibration sensing unit and a controller; wherein the control mass is slidably disposed on the controlled structure, and the active unit is coupled at one end, the active unit includes An elastic member coupled to the control mass and a movable joint that is separated/coupled from the elastic member, and the movable joint is coupled to the controller, and the controller is coupled to receive the signal of the vibration sensing unit, and at an appropriate timing The control movable joint is separated from the elastic element and combined with the actor; thereby, the switching of the separation/combination state can amplify the negative work done by the control mass on the controlled structure and reduce the amount of positive work, which can overcome the traditional tuning quality. The off-frequency phenomenon that may occur in the damper achieves the purpose of improving the safety of the controlled structure.

A preferred embodiment of the impact type semi-active mass damper device and method of the present invention, wherein the controlled structure refers to a structure such as a building, a pylon, and other structures susceptible to vibration by dynamic forces.

A preferred embodiment of the impact type semi-active mass damper device and method of the present invention, wherein the vibration sensing unit is mainly used for sensing a vibration reaction of the controlled structure and the control mass, and includes a connection to the controlled structure a structural vibration sensor, and a control mass vibration sensor coupled to the control mass; the structural vibration sensor can measure an acceleration response or a velocity response of the controlled structure at the movable joint, and control the mass vibration induction The device can measure the absolute acceleration response or absolute velocity response of the control mass or its relative acceleration relative to the controlled structure or relative velocity.

A preferred embodiment of the impact type semi-active mass damper device and method of the present invention, wherein the connection between the controller and the vibration sensing unit and the movable joint can be wired or wirelessly transmitted.

A preferred embodiment of the impact type semi-active mass damper device and method of the present invention further includes a fixing unit, one end of which is fixed to the controlled structure and the other end is fixed to the control mass when the control When the mass has a relative motion with the controlled structure, a force that causes the control mass to return to the equilibrium position and a force to dissipate the energy may be generated; further the fixed unit includes a fixed resilient member that generates a position that causes the control mass to return to equilibrium. And a dissipative component that dissipates energy.

A preferred embodiment of the impact type semi-active mass damper device and method of the present invention, wherein the fixed resilient member can be a spring, an upwardly curved track or a single pendulum suspension device, or one of its similar functional devices.

A preferred embodiment of the impact type semi-active mass damper device and method of the present invention, wherein the function of the energy dissipating component is to dissipate the energy of the control mass to the controlled structure, which may be friction force, viscous damping force, viscosity The source of elastic force, hydraulic pressure and plastic hysteresis can be divided into passive or semi-active energy dissipators.

(A) ‧ ‧ controlled structures

(1) ‧ ‧ control quality block

(2) ‧‧‧ activity unit

(21)‧‧‧Flexural components

(22)‧‧‧Activity joints

(221)‧‧‧Rigid outer casing

(222)‧‧‧through holes

(223)‧‧‧Piezoelectric brakes

(3) ‧‧‧Vibration sensing unit

(31)‧‧‧Structural vibration sensor

(32)‧‧‧Control quality vibration sensor

(4) ‧ ‧ controller

(5) ‧‧‧Fixed units

(51) ‧‧‧Fixed rebounds

(52) ‧ ‧ energy dissipating components

First figure: Schematic diagram of the structure of the present invention.

Second figure: Schematic diagram of the implementation of the movable joint of the present invention (piezoelectric type).

Third figure: Schematic diagram of the control law flow of the present invention.

Fourth figure: Schematic diagram of the reaction under the condition of speed weight=0 of the invention.

Figure 5: Schematic diagram of the reaction under the condition of speed weight > 0 of the present invention.

For a more complete and clear disclosure of the technical content, the object of the invention and the effects thereof achieved by the present invention, as will be described in detail below, please refer to the drawings and drawings. The actual application of technology and means, please refer to the first figure, which is a schematic diagram of the impact type semi-active mass damper device, which is mainly equipped with an impact type semi-active mass damper device on the controlled structure (A), The utility model comprises: a control mass (1), which is a rigid object arranged to slide on the controlled structure (A); An activity unit (2) is disposed between the control mass (1) and the controlled structure, and includes an elastic element (21) having one end coupled to the control mass (1) and a movable joint ( 22), the movable joint (22) is a separate/combined switch, which is connected with the other end of the elastic element (21), and can instantly control the switching/separating/binding action of the elastic element (21); a vibration sensing The unit (3) is a vibration reaction for sensing the controlled structure (A) and the control mass (1), and includes a structure vibration sensor coupled to the controlled structure (A) ( 31), and a control mass vibration sensor (32) coupled to the control mass (1); a controller (4) corresponding to the structure vibration sensor (31) and the control mass vibration The sensor (32) is coupled to and receives the sensing signal, and the controller (4) is coupled to the movable connector (22), and controls the movable connector (22) to separate/couple the action switcher according to the sensing signal.

Referring to the first figure, the impact type semi-active mass damper of the present invention is installed on the controlled structure (A), and the controlled structure (A) refers to buildings, pylons, and the like. A structure that is susceptible to vibration by dynamic forces, thereby reducing the vibration response of the controlled structure (A), thereby achieving the purpose of improving the safety of the controlled structure (A). First, the characteristics and implementation functions and functions of the various components of the present invention are explained in detail:

(1) The control mass (1) is mainly a rigid object that is slid over the controlled structure (A), and its mass is between 0.5 and 15% of the total mass of the controlled structure (A).

(2) The active unit (2) is interposed between the control mass (1) and the controlled structure (A), and includes an elastic element (21) having a switching function and a movable joint (22). One end of the elastic element (21) is connected to the control mass (1), and the other end is a semi-free end, so-called half The free end is switched to form a separation/combination via the movable joint (22) [ie free/constrained semi-free end state]. Continued, the movable joint (22) is an on/off [separation/bonding] switching, one end is connected to the controlled structure (A), and the other end is passed by the semi-free end of the elastic element (21), when the movable joint (22) When switching to the "on" state, the semi-free end of the elastic member (21) is in a free state, and the controlled structure (A) can be relatively moved, so when the control mass (1) is controlled to the controlled structure (A) When the relative position is changed, the elastic member (21) is not deformed without internal force, and therefore, the elastic member (21) is in an unstressed state; otherwise, when the movable joint (22) is switched to the "off" state, the elastic member (21) The semi-free end is in a restrained state, and the controlled structure (A) cannot be relatively moved, so when the relative position of the control mass (1) to the controlled structure (A) is changed, the elastic member (21) ) will deform and have internal force. Further, the movable joint (22) can be any quick-acting braking device such as a friction type, an electromagnetic type, a plug type, a piezoelectric type, etc., and must be a control signal switcher that can accept the controller.

Referring to the second figure, a piezoelectric movable joint (22) [brake device] is illustrated, which comprises a rigid outer casing (221), and a resilient member (221) is provided in the rigid outer casing (221). a through hole (222), and a piezoelectric actuator (223) is disposed on the elastic member (21) corresponding to the through hole (222) on the rigid outer casing (221), the piezoelectric brake (223) External power; controlled by energization of the piezoelectric actuator (223), when the power is turned on, the piezoelectric brake (223) is deformed to clamp the elastic member [forms an "off" action] or the power is released from the elastic element (21) ) [Forms an "open" action].

(3) The vibration sensing unit (3) is mainly for sensing the vibration reaction of the controlled structure (A) and the control mass (1), and comprises a structure vibration sensor connected to the controlled structure (A) (31) and a control mass vibration sensor (32) coupled to the control mass (1). The structural vibration sensor (31) can measure an acceleration response or a velocity response of the controlled structure (A) at the movable joint (22); the control mass vibration sensor (32) can measure the control mass (1) An absolute acceleration reaction or an absolute velocity reaction or its reaction with respect to the relative acceleration or relative velocity of the controlled structure (A).

(4) The function of the controller (4) is to continuously receive the sensing signal of the structure vibration sensor (31) and the control mass vibration sensor (32) in an instant; then, determining the movable joint (22) according to the control logic The command is turned on/off and the control command is immediately transmitted to the active connector (22) in the active unit (2) to cause a corresponding on/off action. Further, the connection between the controller (4) and the two vibration sensors and the movable joint (22) may be wired or wireless.

In addition to the above-described members, the impact type semi-active mass damper device of the present invention further comprises a fixing unit (5), one end of which is fixed to the controlled structure (A) and the other end is fixed to On the control mass (1), when the control mass (1) has a relative motion with the controlled structure (A), a force that causes the control mass (1) to return to the equilibrium position and a force to dissipate the energy may be generated; further The stationary unit (5) includes a fixed resilient member (51) that produces a position that causes the control mass to return to equilibrium, and an energy dissipating member (52) that dissipates energy. The following is a detailed explanation:

(5) The fixing unit (5) comprises a fixed resilient member (51) and an energy dissipating member (52), one end of the fixing unit (5) is fixed on the controlled structure (A), and the other end is fixed to the On the control mass (1), when the control mass (1) has a relative motion with the controlled structure (A), a force that causes the control mass (1) to return to the equilibrium position and the force to dissipate the energy can be generated. Further, the fixed resilient member (51) may be a spring, an upwardly curved track or a single pendulum suspension, or the like, or a similar functional device. And the function of the energy dissipating component (52) is to dissipate the control mass and the controlled structure Material energy can be friction, viscous damping force, viscoelastic force, hydraulic pressure, plastic hysteresis force source, and can be divided into passive and semi-active energy dissipators.

However, the reason why the fixing unit (5) is provided in the present invention is that: (1) the fixed resilient member (51) is used to control the displacement amount of the control mass (1) to prevent it from being excessively large and losing usability. (2) The energy dissipating element (52) is used to dissipate the mechanical energy in the system and to avoid excessive displacement of the control mass (1).

The assembly technique and features of the structural device of the present invention will be apparent from the above description. However, the technical methods and principles for carrying out the device of the present invention will be described below. First, the natural vibration frequency of the control mass (1) is calculated by the following formula:

The prior art tuned mass damper technique requires that the ratio of the natural vibration frequency of the control mass (1) to the fundamental automatic vibration frequency of the controlled structure (A) is close to 1, usually between 0.9 and 1.0. good. Once the frequency ratio is slightly less than or greater than the optimal ratio, the energy dissipation effect will be greatly reduced, or even no damping effect at all. This phenomenon is called the Detuning effect, and the loss of the energy dissipation effect is due to the fact that the natural frequency of the control mass (1) is not compatible with the basic natural frequency of the controlled structure (A). When the controlled structure (A) is used for positive work, the amount of positive work is equivalent to the amount of negative work, and the energy dissipation effect is naturally lost.

However, the impact type semi-active mass damping method of the present invention aims to magnify the negative work performed by the control mass (1) on the controlled structure (A) as much as possible, and to minimize the amount of positive work. To achieve this, the present invention limits the natural frequency of the control mass (1) to be greater than or equal to twice the fundamental natural frequency of the controlled structure (A), ie, the following formula holds: the natural vibration frequency of the control mass 2× the basic natural frequency of the controlled structure; the control mass (1) is connected with two elastic objects, one of which is an elastic element (21) that can be switched between on and off, and the other is a fixed fixed back. Bullet (51). The invention limits the elastic modulus of the elastic element (21) to at least three quarters of the total elastic coefficient, and therefore, the effective natural vibration frequency of the control mass (1) is controlled when the elastic element (21) is in the "off" state. Controlling the structure (A) more than twice the natural frequency; conversely, when the elastic element (21) is in the "on" state, the effective automatic vibration frequency of the control mass (1) may only be left to the fundamental natural frequency of the control structure. Half, or less.

Further, assume that the currently active joint is in the "on" state and that the controlled structure (A) is moving to the right, while the control mass (1) is moved to the left relative to the controlled structure (A). At this time, if the state of the movable joint (22) is switched to "OFF", the elastic member is deformed, a leftward force is applied to the controlled structure (A), and a rightward force is applied to the control mass (1). The speed of movement of the controlled structure (A) to the right is thus reduced; and the relative leftward movement speed of the control mass (1) relative to the controlled structure (A) is also reduced, even gradually changing to relatively rightward motion. The internal force of the elastic element (21) in the initial movement to the right is still reducing the speed of movement of the controlled structure (A), that is, negative work, and increasing the control mass (1) to the controlled structure (A) The relative speed of movement to the right. The internal force of the elastic element (21) gradually returns to zero as the relative movement speed changes, and begins to become the same force for the controlled structure (A) as the direction of movement of the controlled structure (A), that is, to start doing Positive work. Switching the active joint state to "on" at the instant of the positive work on the controlled structure (A) will avoid applying positive work to the controlled structure (A). At this time, the control mass (1) is absorbed by the control structure (A) by a large amount of kinetic energy, and can exert greater impact force and shock absorption interaction force at the timing of the next combination. In order to amplify the amount of negative work, the negative work must be completed as soon as possible, so the present invention limits the natural mass of the control mass (1) to be greater than or equal to twice the fundamental natural frequency of the controlled structure (A).

In the above description, the main factor affecting the negative function of the controlled structure (A) is the timing of switching the state of the movable joint (22). The basic logic of this method is: as much as possible to be controlled Structure (A) applies negative work and avoids applying positive work. To achieve the object of the present invention, the vibration sensing unit (3) is used to continuously measure the velocity and acceleration response of the controlled structure (A), and to control the relative motion direction of the mass (1) relative to the controlled structure (A). . Since the velocity response can be obtained by integrating the acceleration reaction, or the acceleration reaction can be derived from the velocity reaction, the structure vibration sensor (31) can measure one of the reactions. As for the relative motion direction of the control mass (1) relative to the controlled structure (A), which may be obtained by integrating the relative acceleration, or may be derived from the relative displacement, the control mass vibration sensor (32) may be an accelerometer or Speedometer or displacement meter.

When the controller (4) continuously collects the vibration reaction by the structure vibration sensor (31) and the control mass vibration sensor (32), and according to the control logic, the active joint state should be switched to "on" or "off". The control logic is called Control Law; the control law of the impact semi-active mass damping method of the present invention is as follows: If the active joint state is "on", then ( C _V V _S - A _S ) × V _CS When 0 is set to “Off”; if the active joint status is “Off”, it switches to “On” when V _S × D _CS >0; in the above formula, V _S is the speed of the controlled structure, to the right Positive; A _S is the motion acceleration of the controlled structure, positive to the right; V _CS is the moving speed of the control mass relative to the controlled structure, positive to the right; D _CS movable joint is switched off to control the mass relative The amount of displacement of the controlled structure corresponds to the amount of deformation of the elastic element. When V _S × D _CS > 0 means that the controlled structure will be positively operated; C _V is the speed weight and may be a constant greater than or equal to 0.

The main difference between the control law of the present invention and the conventional semi-active control law is that the structural acceleration response is considered, and the shock absorption effect can be improved more. According to this control law, the closing timing of the movable joint must take into account the acceleration of the controlled structure (A), and in fact the trend of sensing speed changes during its movement, so the acceleration sensor may not be needed, as long as The controller (4) performs a difference with the speed sensing value. The second difference operation is performed in the submeter or by the displacement meter. Similarly, the velocity response of the controlled structure (A) can also be obtained by integrating the acceleration reaction once or by the displacement reaction.

Please refer to the fourth to fifth figures, the description of the actual embodiment - here the case where the setting of the fixed unit (5) is not used, and the speed weight ( C _V ) is zero, the impact type semi-active mass damper device of the present invention is explained. The controlled structure (A) is subjected to dynamic external forces to assist in understanding its damping performance. Proceed as follows:

Step 1 - Before the external force is applied, both the controlled structure (A) and the impact semi-active mass damper are in a stationary state, and the movable joint (22) is in an "off" state. When the external force acts to cause the controlled structure (A) to start moving to the right ( V _S >0), the control mass (1) is at rest due to inertia, thus controlling the mass (1) relative to the controlled structure (A) ) starts moving to the left ( V _CS <0), and its relative displacement with respect to the controlled structure (A) is also to the left, so it is a negative value ( D _CS <0). Therefore, according to the control law, the movable joint (22) should remain in the "off" state, and the speed of the control mass (1) gradually increases. Currently at the time point AB. The displacement of the controlled structure (A) increases from near the origin to the right, the speed is at the maximum to the right and decreases, and the acceleration is just from zero to negative. The displacement of the control mass (1) relative to the controlled structure (A) is negative, so the force of the elastic element (21) against the controlled structure (A) is negative to the left.

Step 2 - After a period of time, the moving speed of the control mass (1) exceeds the controlled structure (A), and the displacement (elastic element) of the control mass (1) relative to the controlled structure (A) will eventually return to Zero ( D _CS =0). Referring to time point B, both the controlled structure (A) and the control mass (1) move to the right (the speed is positive), and the speed of the control mass (1) is relatively large. At the next time point, the displacement of the control mass (1) relative to the controlled structure (A) becomes a positive value ( D _CS >0), in accordance with the control law, the active joint (22) is switched to the "on" condition. Therefore, open the movable joint (22).

Step 3 - Since the movable joint (22) is opened, the control mass (1) continues to move to the right at a constant speed, and the elastic restoring force (mainly from the deformation of the column force) of the controlled structure (A) when moving to the right Left, the acceleration of the controlled structure (A) is negative ( A _S <0). This is between time points BC. As time changes, at time C, the controlled structure (A) moves to the left, and the controlled structure (A) returns to its neutral position, and the acceleration returns to zero by a negative value ( A _S =0) . Therefore, in accordance with the control law, the movable joint (22) is switched to the "off" condition, so that the control mass (1) and the controlled structure (A) are combined again.

Step 4 - The structure continues to move to the left due to inertia ( V _S <0), but the control mass (1) moves to the right to push the elastic element to deform, so that the elastic element (21) applies the direction to the controlled structure (A) The power of the right, then the negative work on the controlled structure (A), which is between the time points CD. Since the natural vibration frequency of the control mass (1) is higher than that of the controlled structure (A), the movement speed of the control mass (1) is reversed before the controlled structure (A) changes the direction of motion again. And moving to the left at a faster speed, so that the speed of the control mass (1) relative to the controlled structure (A) is negative ( V _CS <0), even at the time point D, the control mass (1) The relative displacement amount with respect to the controlled structure (A) is negative by positive ( D _CS < 0). At this time, the condition that the control joint (22) is switched to "on" is met in accordance with the control law. Therefore, opening the movable joint (22) can avoid positive work on the controlled structure (A). Thereafter, the controlled structure (A) moves to the left toward the control mass (1), and the speed of the control mass (1) is relatively large.

Step 5 - Since the movable joint (22) is opened, the control mass (1) continues to move to the left at a constant speed, and the elastic restoring force (mainly from the deformation of the column force) of the controlled structure (A) when moving to the left To the right, the acceleration of the controlled structure (A) is positive ( A _S >0). This is between the time points DE. As time changes, at time E, the controlled structure (A) moves to the right, and the controlled structure (A) returns to its neutral position, and the acceleration returns to zero by a negative value ( A _S =0) . Therefore, the condition that the control joint (22) is switched to "off" is again met, so that the control mass (1) and the controlled structure (A) are combined again.

Step 6 - The structure continues to move to the right due to inertia ( V _S >0), but the control mass (1) moves to the left to push the elastic element (21) to deform, so that the elastic element (21) to the controlled structure (A) Applying a force to the left, then doing negative work on the controlled structure (A), which is between the time points EF. Since the natural vibration frequency of the control mass (1) is higher than that of the controlled structure (A), the movement speed of the control mass (1) is reversed before the controlled structure (A) changes the direction of motion again. And moving to the right at a faster speed, so that the speed of the control mass (1) relative to the controlled structure (A) is positive ( V _CS >0), even at the time point F, the control mass (1) The relative displacement amount with respect to the controlled structure (A) is from negative to positive ( D _CS >0). At this time, the condition that the control joint (22) is switched to "on" is met in accordance with the control law. Therefore, opening the movable joint (22) can avoid positive work on the controlled structure (A). Thereafter, the controlled structure (A) moves to the right to the control mass (1), and the speed of the control mass (1) is relatively large.

Step 7 - Repeat steps 3-6 above, after the external force disappears, and then the inevitable energy dissipation in the system, the control mass (1) and the controlled structure (A) will return to the static equilibrium state. In order to accelerate the return to the static equilibrium state, the energy dissipation element (52) in the fixed unit (5) can be used to supplement the energy dissipation.

Here, the impact semi-active mass damper of the present invention is subjected to the dynamic external force of the controlled structure (A) by using the setting of the fixed unit (5) and the speed weight ( C _V ) being positive. The operation of the situation to help understand its damping performance. At this time, the speed of the controlled structure (A) and the acceleration response take into consideration the timing of the joint of the movable joint (22). For the sake of easy understanding, please refer to the fifth figure as shown in the fifth figure, compared with the state where the speed weight is zero. The timing of switching the joint (22) from off to on is the same, and the relative displacement of the controlled structure (A) is from positive to negative (time point D, H) or negative to positive (time point F, J). ). However, when the active joint (22) is switched from on to off, when the speed weight is positive, the speed response will switch to the off timing in advance. As time point C of the fifth figure, if the speed weight is 0, it should be switched to off at the time point when the speed of the controlled structure (A) reaches the lowest point and the acceleration is negative from positive to negative, as at time point C of the fourth figure. However, because the speed response participates in the calculation and judgment, it is slightly advanced. Similarly, the time points E and G in the figure are earlier than the fourth figure.

However, the above-described embodiments or drawings are not intended to limit the structure or the use of the present invention, and any suitable variations or modifications of the invention will be apparent to those skilled in the art.

As described above, the composition and use description of the system of the present invention show that the present invention has the following advantages compared with the prior art: the impact type semi-active mass damper device and method of the present invention is mainly intended to provide a basis for The semi-active mass damper of the control law derived from the characteristic characteristics, using the control mass frequency of the main structure twice or more than the natural frequency, can provide higher damping effect than the various dampers described above; its characteristics are: control law and control The difference between the frequency of the mass and the conventional semi-active mass damper.

In summary, the embodiments of the present invention can achieve the expected use efficiency, and the specific structure disclosed therein has not been seen in similar products, nor has it been disclosed before the application, and has completely complied with the provisions of the Patent Law. And the request, the application for the invention of a patent in accordance with the law, please forgive the review, and grant the patent, it is really sensible.

(A) ‧ ‧ controlled structures

(1) ‧ ‧ control quality block

(2) ‧‧‧ activity unit

(21)‧‧‧Flexural components

(22)‧‧‧Activity joints

(3) ‧‧‧Vibration sensing unit

(31)‧‧‧Structural vibration sensor

(32)‧‧‧Control quality vibration sensor

(4) ‧ ‧ controller

(5) ‧‧‧Fixed units

(51) ‧‧‧Fixed rebounds

(52) ‧ ‧ energy dissipating components

Claims (10)

An impact semi-active mass damper device is mainly mounted on a controlled structure with an impact semi-active mass damper device, comprising: a control mass for rigidity sliding on the controlled structure An active unit is disposed between the control mass and the controlled structure, and includes an elastic component having one end coupled to the control mass and a movable joint, wherein the movable joint is a separate/combined switch Corresponding to the other end of the elastic element, and can instantly control the switching and elastic element separation/combination action; a vibration sensing unit is used for sensing the vibration response of the controlled structure and the control mass, including a structure vibration sensor coupled to the controlled structure, and a control mass vibration sensor coupled to the control mass; a controller corresponding to the structure vibration sensor and the control quality The vibration sensor connects and receives the sensing signal, and the controller connects the movable joint, and controls the movable joint to separate/combine according to the sensing signal Switching person. The impact type semi-active mass damper device of claim 1, wherein the mass of the control mass is between 0.5 and 15% of the total mass of the controlled structure. The impact type semi-active mass damper device of claim 1, further comprising a fixing unit, one end of the fixing unit being fixed to the controlled structure and the other end being fixed to the control mass And the fixing unit includes a fixed resilient member capable of causing the control mass to return to the equilibrium position and an energy dissipating component capable of dissipating energy, when the control mass has relative motion with the controlled structure, The force that causes the control mass to return to equilibrium and the power to dissipate energy. The impact type semi-active mass damper device of claim 1, wherein the structure vibration sensor can measure an acceleration reaction and a speed response of the controlled structure at the movable joint; and the control mass vibration The inductor measures the absolute acceleration response of the control mass, the absolute velocity response, its relative acceleration relative to the controlled structure, and the relative velocity response. The impact type semi-active mass damper device of claim 1, wherein the signal transmission between the controller and the structure vibration sensor, the control mass vibration sensor, and the movable joint of the vibration sensing unit It adopts a telecommunication link of wired and wireless. The impact type semi-active mass damper device according to claim 1 or 2, wherein the movable joint is a brake device capable of controlling signal switching of the controller, and the brake device is friction type and electromagnetic type. One of the plug-in type and the piezoelectric type. The impact type semi-active mass damper device of claim 2, wherein the control mass vibration sensor uses an accelerometer, a speedometer, and a displacement meter. The impact type semi-active mass damper device of claim 3, wherein the fixed resilient member is a spring, an upwardly curved track, and a single pendulum suspension device; and the energy dissipating component is used to dissipate the The mass of the mass and the energy of the controlled structure are controlled, and friction, viscous damping force, viscoelastic force, hydraulic pressure, and plastic hysteresis force are further used to dissipate energy. The impact type semi-active mass damper device of claim 6, wherein the movable joint further comprises a rigid outer casing, wherein the rigid outer casing is provided with a through hole through which the elastic member passes, and the rigidity A piezoelectric brake is disposed on the elastic member of the outer casing corresponding to the through hole, and the piezoelectric brake is externally connected to the electric power. An impact type semi-active mass absorbing method, comprising the apparatus according to any one of claims 1 to 4; when the controller is continuously collected by the structure vibration sensor and the control mass vibration sensor Vibrate the reaction, and according to the control law, the active joint state should be switched to "on" or "off". The control law is judged as: if the active joint state is "on", then ( C _V V _S - A _S ) × V _CS 0 to "off"; if the active joint state is "off", then switch to "on" when V _S × D _CS >0; where V _S is the speed of the controlled structure, right Positive; A _S is the motion acceleration of the controlled structure, positive to the right; V _CS is the moving speed of the control mass relative to the controlled structure, positive to the right; D _CS indicates the movable joint The amount of displacement of the control mass relative to the controlled structure after switching to off, that is, the amount of deformation of the elastic member; when V _S × D _CS > 0, the positive control is performed on the controlled structure; C _V is The speed weight can be a constant greater than or equal to zero.