TW201821710A - Device and method for impact semi-active mass vibration adsorption - Google Patents

Abstract

The present invention relates to a device and a method for impact semi-active mass vibration adsorption, wherein the device particularly installed on a controllable structure, e.g. buildings, bridge towers and other constructions easily vibrating due to dynamic force, includes a mass control block fitted on a controllable structure, a controller and a moveable unit having an elastic element at one end thereof for connection with the mass control block and a moveable joint connecting with the controller and subject to operative control by the controller so as to engage with or separate from the elastic element in due course. In such a case, the amount of the negative work the mass control block exerts to the controllable structure can be amplified and the amount of positive works to the controllable structure be significantly decreased by switching the separation or connection status of the movable joint and the elastic element, so as to solve the issue of bad vibration adsorption effect of a tuned mass damper resulted from frequency detuning effect on control performance of the tuned mass damper, as well as the tuned mass damper is able to work without supply of a large quantity of energy for main purpose of promoting the safety of the controllable structure.

Description

Impact type semi-active mass shock absorbing device and method

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

According to mass damper, it is a structural and mechanical shock absorption technology field, which is used to reduce the vibration response of structures under dynamic loads, such as displacement, velocity and acceleration. Its characteristics are as follows: a light mass relative to the structure is installed at a specific part of the structure, and the structure and the mass are connected in a specific way and generate mutual force. The main focus of its design is to make its mutual production force effectively reduce the vibration response of the main structure; the secondary focus is (1) to let the mass and its connection system absorb the energy of the main structure and effectively dissipate it, and (2) Prevent the mass from reacting too much to endanger the main structure.

Mass damper technology can be roughly divided into three categories: (1) passively tuned mass damper, (2) active mass damper, and (3) semi-active mass damper. There are also fourth types that mix any or all of the previous two. (4) Hybrid mass damper.

The first type of passive mass damper is a designed spring and energy dissipating damper connected in parallel between the main structure and the mass block, and the mutual force is generated by the relative movement of the mass block and the main structure. Because its mutual control force can not be actively controlled, it must be completely determined by the external force characteristics and the dynamic properties of the mass-spring-dissipation damper, so it is called a passive mass damper. Passive mass damper is the earliest proposed mass damper technology. It was known from the beginning that when the mass-spring subsystem has a natural vibration frequency similar to that of the main structure, it can exert a very significant shock absorption effect. Because the frequency tuning is the main parameter of the damping effect, the passive mass damper is also called Tuned Mass Damper (TMD). Many types of changes have been proposed, such as replacing the spring with a single pendulum suspension to allow the mass to oscillate greatly, and replacing the liquid column damper (LCD) of the mass-spring-dissipation damper with a water column. The main disadvantages of tuned mass dampers are twofold: (1) requires a large space for the device to allow mass mass movement-limiting the usability, and (2) detunning-effect-reducing the shock absorption effect. The off-frequency phenomenon refers to the ratio of the natural vibration frequency of the subsystem and the main structure beyond the valid range, which may occur when the design is poor, the use condition changes, and the main structure enters an inelastic state under strong earthquakes. Therefore, in recent years, some new ideas have been proposed. Among them, the technique of expanding the effective frequency range by using multi-mass blocks with different natural frequencies is the most representative. Since the seismic force is a transient dynamic force, the tuned mass damper does not control the maximum displacement of the structure, so the tuned mass damper is mainly used for wind resistance of super high-rise structures.

The development of the second type of active mass damper, active mass damper and tuned mass damper, has no obvious correlation. The basic composition of an active mass damper is a mass, an actuator, a controller, a motion sensor, an energy supply unit, and a supporting slide device. Its working principle is: when the structure is subjected to dynamic load and generates movement (displacement, speed, acceleration), the necessary physical quantity of motion is converted into an electronic signal by the motion sensor, and the controller according to the control law and the sensor formulated in advance The signal determines the control force that should be generated on the main structure, and this control force is generated by the reaction force of the actuator that pushes / pulls the mass. Therefore, the controller generates an actuator control command according to the control force demand. The actuator generates a control force on the main structure during the acceleration / deceleration of the mass. The main application of active mass dampers in earthquakes or wind is not to provide better shock absorption effects than tuned mass dampers, but to reduce the amount of mass displacement, allowing applications in space-constrained situations. It is also an important advantage that it does not have the problem of off-frequency effects. The control force determined according to the control law needs to be provided by energy supply units, such as hydraulic pumps, high-voltage power supplies and other equipment, so the active mass damper has dependence on external energy. Active mass dampers require many components such as inductors, controllers, precision-controlled actuators, and huge energy supplies. Due to their relatively high installation costs, their reliability is also questioned. Therefore, in practice, the active mass damper is mainly to improve the usability and comfort of the structure, rather than to improve the safety.

The third type of semi-active mass damper is to calculate the control force according to the control law of the active control method. When the direction of the actual mutual force is opposite to the direction of the required control force, the spring connection between the mass and the main structure is released, and the mass is released instantly. Spring strain energy to the main structure. Continue to calculate the control force according to the control law of the active control law, and determine the direction of the mutual production force that will be generated by the restoration of the connection between the mass and the main structure. Spring coupling. Under this logic, the spring between the mass and the main structure brings the natural vibration frequency of the mass close to the basic vibration frequency of the structure, and is usually slightly higher than the basic vibration frequency of the main structure. According to the active control law, the control law must capture the displacement and velocity responses of the controlled structure in real time at equal intervals, and substitute these reactions into the control law to obtain the spring between the connection or decoupling and the mass. Its control law usually leads to the following:

If the status of the movable joint is "ON", then Switch to "Off"

If the status of the movable joint is "Off", then Switch to "On" when

among them, Is the speed of movement of the structure, Is the speed of the mass, For the force of the spring on the structure, the positive direction and the speed of the structure are defined the same. According to this control law, it can ensure that the mass does negative work on the controlled structure, but it may not exert the maximum energy dissipation effect.

This type of semi-active mass damper combines the frequency tunability of a passive tuned mass damper with the changeable characteristics of an active mass damper. But because its control law is directly modified from the active mass damper, it is not derived based on the vibration characteristics, and the damping effect is similar to that of the passively tuned mass damper.

Today, the inventor upholds many years of rich research, design and development and actual production experience in this related industry, and then researches and improves the existing structure to provide an impact semi-active mass vibration damping device and method in order to achieve better practical value. Purpose.

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

The main purpose and effect of the use method of the impact semi-active mass shock absorbing device and method of the present invention are achieved by the following specific technical means:

An impact-type semi-active mass vibration damping device is mainly installed on a controlled structure, and includes a control mass, a movable unit, a vibration sensing unit, and a controller. The control mass is slidably disposed on the control mass. On the controlled structure, a movable unit is connected at one end, the movable unit includes an elastic element connected to the control mass at one end, and a movable joint which is timely separated / combined with the elastic element, and the movable joint should be connected with the controller. The controller is connected to receive the signal of the vibration sensing unit, and controls the movable joint and the elastic element to separate / combine the actor at an appropriate timing; thereby, the switching of the separation / combination state can enlarge the control mass to the controlled structure. The negative work done and the amount of positive work done can overcome the off-frequency phenomenon that may occur in traditional tuned mass dampers and achieve the purpose of improving the safety of the controlled structure.

According to a preferred embodiment of the impact type semi-active mass vibration damping device and method of the present invention, the controlled structures are, for example, buildings, bridge towers, and other structures that are susceptible to vibration due to dynamic forces.

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

According to a preferred embodiment of the impact type semi-active mass vibration damping device and method of the present invention, the connection between the controller and the vibration sensing unit and the movable joint can be wired or wireless transmission.

A preferred embodiment of the impact type semi-active mass vibration damping device and method of the present invention further includes a fixing unit, one end of which is fixed on the controlled structure and the other end is fixed on the control mass. When the mass moves relative to the controlled structure, it can generate a force that causes the control mass to return to its equilibrium position and a force that dissipates energy; further, the fixed unit includes a fixed resilient member that can generate a force that causes the control mass to return to its equilibrium position. And a dissipative element that dissipates energy.

According to a preferred embodiment of the impact type semi-active mass shock absorbing device and method of the present invention, the fixed rebound member may 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 semi-active mass vibration damping device and method of the present invention, wherein the function of the energy dissipating element is to dissipate the energy from the control mass to the controlled structure, which may be frictional force, viscous damping force, viscous The sources of elastic force, hydraulic pressure, and plastic hysteresis can be divided into passive or semi-active energy dissipators.

In order to provide a more complete and clear disclosure of the technical content, the purpose of the invention and the effect achieved by the present invention, it is described in detail below, and please also refer to the disclosed drawings and numbers:

First of all, the actual application technology and means of the present invention, please refer to the first figure, which is a schematic diagram of the impact semi-active mass damping device of the present invention, which is mainly equipped with an impact semi-active mass reduction device on the controlled structure (A). Seismic device, which includes:

A control mass (1), which is a rigid object sliding on the controlled structure (A);

A movable unit (2) is disposed between the control mass (1) and the controlled structure, and includes an elastic element (21) connected at one end to the control mass (1) and a movable joint ( 22), the movable joint (22) is a disconnection / combination switch, which is connected to the other end of the elastic element (21), and can control the disconnection / combination of the switch and the elastic element (21) in real time;

A vibration sensing unit (3) for sensing the vibration response of the controlled structure (A) and the control mass (1) includes a structure connected to the controlled structure (A). A vibration sensor (31), and a control mass vibration sensor (32) connected to the control mass (1);

A controller (4) is connected to the structure vibration sensor (31) and the control mass vibration sensor (32) respectively to receive a sensing signal, and the controller (4) is connected to the movable joint (22). , And control the movable joint (22) disconnection / combination action switcher according to the induction signal.

Please refer to the first figure again. The impact semi-active mass vibration damping device of the present invention is installed on a controlled structure (A), and the controlled structure (A) refers to a building, a bridge tower, and others. The structure which is susceptible to dynamic force and vibration, thereby reducing the vibration response of the controlled structure (A), thereby achieving the purpose of improving the safety of the controlled structure (A). First, explain in detail the characteristics of the components of the present invention and the effectiveness and functions of implementation:

(1) Control mass (1) is mainly a rigid object sliding on the controlled structure (A), and its mass is between 0.5 ~ 15% of the total mass of the controlled structure (A).

(2) The movable unit (2) is located between the control mass (1) and the controlled structure (A), and includes an elastic element (21) with 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 becomes a semi-free end. The so-called semi-free end is switched to form a separation / combination [ie, free / constrained semi-free end state] by the movable joint (22). ]. Continued, the movable joint (22) is switched on / off [detached / combined], one end is connected to the controlled structure (A), and the other end passes through the semi-free end of the elastic element (21). When the movable joint (22) ) When switched to the "on" state, the semi-free end of the elastic element (21) is in a free state, and can relatively move the controlled structure (A). Therefore, when the control mass (1) controls the controlled structure (A), When the relative position of) is changed, the elastic element (21) will not deform without internal force. Therefore, the elastic element (21) is in a state of no force; otherwise, when the movable joint (22) is switched to the "off" state, the elastic element (21) The semi-free end is in a constrained state and cannot move relative to the controlled structure (A). Therefore, when the relative position of the control mass (1) to the controlled structure (A) changes, the elastic element (21) ) Will deform and have internal forces. Further, the movable joint (22) can be any braking device with fast response, such as friction type, electromagnetic type, pin type, piezoelectric type and other braking devices, and must be a switcher who can accept the control signal of the controller.

Please refer to the second figure, which is an example of a piezoelectric movable joint (22) [braking device], which includes a rigid outer casing (221), and an elastic element (21) is provided in the rigid outer casing (221). ) A through-hole (222) is provided, and a piezoelectric brake (223) is provided on the rigid outer casing (221) corresponding to the elastic element (21) of the through-hole (222). The piezoelectric brake (223) External power; use the piezoelectric brake (223) to control whether it is energized or not. When it is energized, let the piezoelectric brake (223) deform the elastic element [to form a "close" action] or loosen the elastic element (21) ) [Forms an "on" action].

(3) The vibration sensing unit (3) is mainly used to sense the vibration response of the controlled structure (A) and the control mass (1), and includes a structure vibration sensor connected to the controlled structure (A). (31) and a control mass vibration sensor (32) connected to the control mass (1). The structure vibration sensor (31) can measure the acceleration response or speed response of the controlled structure (A) at the movable joint (22); the control mass vibration sensor (32) can measure the control mass (1). Absolute acceleration response or absolute speed response or its relative acceleration or relative speed response to the controlled structure (A).

(4) The function of the controller (4) is to continuously and continuously receive the sensing signals of the structural vibration sensor (31) and the control mass vibration sensor (32); then, determine the moving joint (22) according to the control logic. On / off command, and the control command is immediately transmitted to the movable joint (22) in the active unit (2) to cause the 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 components, the impact semi-active mass vibration damping device of the present invention further includes 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) and the controlled structure (A) have relative movement, the force that causes the control mass (1) to return to the equilibrium position and the power to dissipate energy can be generated; further, The fixed unit (5) includes a fixed resilient member (51) for generating a control mass to return to an equilibrium position, and an energy dissipating element (52) for dissipating energy. The following further details:

(5) The fixed unit (5) includes a fixed resilient member (51) and an energy dissipating element (52). One end of the fixed unit (5) is fixed on the controlled structure (A), and the other end is fixed on the fixed structure (A). On the control mass (1), when the control mass (1) and the controlled structure (A) are in relative motion, the force that causes the control mass (1) to return to its equilibrium position and the power to dissipate energy can be generated. Further, the fixed rebound member (51) may be a spring, a curved upward track or a single pendulum suspension device, or a similar functional device. The function of the energy dissipating element (52) is to dissipate the energy of the control mass and the controlled structure. It can be the source of friction, viscous damping, viscoelastic, hydraulic, and plastic hysteresis. Passive and semi-active energy absorbers.

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

From the above description, the assembly technology and characteristics of the structural device of the present invention can be known. However, the technical method and principle of implementing 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 tuned mass damper technology in the prior art requires that the ratio of the natural vibration frequency of the control mass (1) to the basic 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, its energy dissipation effect will be greatly reduced, or there will be no shock absorption effect at all. This phenomenon is called the detuning effect, and the loss of its energy dissipation and damping effect comes from the dissonance between the natural frequency of its control mass (1) and the basic natural frequency of the controlled structure (A). The possibility that the controlled structure (A) does positive work, when the amount of positive work is equal to the amount of negative work, the energy dissipation effect is naturally lost.

However, the impact semi-active mass vibration damping method of the present invention aims to enlarge the negative work performed by the control mass (1) on the controlled structure (A) as much as possible, and reduce the amount of positive work as much as possible. To achieve this, the present invention limits the natural frequency of the control mass (1) to be greater than or equal to twice the basic natural frequency of the controlled structure (A), that is, the following formula holds:

;

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 resilient member (51). The invention limits the elastic coefficient of the elastic element (21) to at least three-fourths of the total elastic coefficient. Therefore, when the elastic element (21) is in the "off" state, the effective natural vibration frequency of the control mass (1) is affected by The basic natural frequency of the control structure (A) is more than twice; on the contrary, when the elastic element (21) is in the "on" state, the effective automatic vibration frequency of the control mass (1) may be only the basic natural frequency of the controlled structure. Half or less.

To further explain, it is assumed that the movable joint is currently in the "on" state, and the controlled structure (A) moves to the right, and the control mass (1) moves 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 element will deform, applying a leftward force to the controlled structure (A) and a rightward force to the control mass (1). As a result, the speed of the controlled structure (A) moving to the right is reduced; and the speed of the relative mass of the control mass (1) relative to the controlled structure (A) is also reduced, or even gradually turned to the right. The internal force of the elastic element (21) at the beginning of the relative rightward movement is still reducing the movement speed of the controlled structure (A), that is, negative work is performed, and the control mass (1) is added to the controlled structure (A). Relative right speed of movement. The internal force of the elastic element (21) gradually returns to zero with the change of the relative movement speed, and starts to become the force acting on the controlled structure (A) in the same direction as the movement of the controlled structure (A). Positive work. At the moment when the positive work of the controlled structure (A) is about to start, switching the state of the movable joint to "ON" can avoid applying positive work to the controlled structure (A). At this time, the control mass (1) controlled structure (A) absorbs a large amount of kinetic energy, and can exert a greater impact force and a damping mutual restraining force at the next combination timing. In order to amplify the amount of negative work, the negative work must be completed as soon as possible. Therefore, the present invention limits the natural frequency of the control mass (1) to be greater than or equal to twice the basic natural frequency of the controlled structure (A).

In the above description, the main factor affecting the negative functional force on the controlled structure (A) is the switching timing of the state of the movable joint (22). The basic logic of this method is to apply negative work to the controlled structure (A) as much as possible and avoid applying positive work. In order to achieve the purpose of the invention, the vibration sensing unit (3) is used to continuously measure the speed and acceleration response of the controlled structure (A), and the relative movement direction of the control mass (1) relative to the controlled structure (A). . Because the velocity response can be obtained by integrating the acceleration response, or the acceleration response can be derived by differentiating the velocity response, the structure vibration sensor (31) can measure one of the responses. As for the relative movement direction of the control mass (1) relative to the controlled structure (A), it can be obtained by integrating the relative acceleration, or by differentiating the relative displacement, so the control mass vibration sensor (32) can be an accelerometer or Speedometer or displacement meter.

When the controller (4) continuously collects the vibration response from the structural vibration sensor (31) and the control mass vibration sensor (32), and decides according to the control logic that the state of the movable joint should be switched to "on" or "off" "This control logic is called Control law; the control law of the impact semi-active mass vibration damping method of the present invention is as follows:

If the status of the movable joint is "ON", then Switch to "Off"

If the status of the movable joint is "Off", then Switch to "On" when

In the above formula, The speed of movement of the controlled structure is positive to the right; Is the acceleration of the movement of the controlled structure, it is positive to the right; To control the moving speed of the mass relative to the controlled structure, it is positive to the right; After the movable joint is switched off, the displacement amount of the control mass relative to the controlled structure is equivalent to the deformation amount of the elastic element. when Indicates that positive work will be performed on the controlled structure; Is the speed weight, which can be a constant greater than or equal to zero.

The main difference between the control law of the present invention and the conventional semi-active control law is that the acceleration response of the structure is considered, which can improve the shock absorption effect even higher. 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 it is sensing the trend of speed change during its movement, so an acceleration sensor may not be needed, as long as The controller (4) performs a primary difference based on the speed sensing value or a secondary differential operation from the displacement meter. Similarly, the speed response of the controlled structure (A) can also be obtained by integrating the acceleration response once or by using the displacement response once.

Please refer to the fourth to fifth figures as shown in the actual embodiment description. Here, the settings and speed weights of the fixed unit (5) are not used ( The case where) is zero indicates the operation situation of the impact semi-active mass shock absorbing device of the present invention under the action of a dynamic external force on the controlled structure (A) to help understand its shock absorption performance. Proceed as follows:

Step 1-Before the external force acts, the controlled structure (A) and the impact-type semi-active mass damping device are both in a stationary state, and the movable joint (22) is in an "off" state at this time. When the external force acts, the controlled structure (A) starts to move to the right ( > 0), the control mass (1) is in a stationary state due to inertia, so the control mass (1) starts to move leftward relative to the controlled structure (A) ( <0), its relative displacement relative to the controlled structure (A) is also to the left, so it is negative ( <0). Therefore, according to the control law, the movable joint (22) should still be kept in the "off" state, and the speed of the control mass (1) is gradually increased. Currently between points in time AB. The displacement of the controlled structure (A) is increasing from near the origin to the right, the speed is at the maximum to the right and falling, 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) on the controlled structure (A) is negative to the left.

Step 2-After a period of time, the movement speed of the control mass (1) exceeds the controlled structure (A), and the displacement of the control mass (1) relative to the controlled structure (A) (elastic element) will eventually return to zero( = 0). With reference to time point B, the controlled structure (A) and the control mass (1) both move to the right (the speed is positive), and the speed of the control mass (1) is relatively large. At the next point in time, the displacement of the control mass (1) relative to the controlled structure (A) becomes a positive value ( ＞ 0), it meets the condition that the control law will switch the movable joint (22) to "ON", so 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, while the controlled structure (A) moves to its right when its elastic restoring force (mainly from the deformation of the column force) Left, so the acceleration of the controlled structure (A) is negative ( <0). This is the time between BC. With time, 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 from negative to zero ( = 0). Therefore, it meets the condition that the control law switches the movable joint (22) to "OFF", so the control mass (1) and the controlled structure (A) are integrated again.

Step 4- The structure continues to move to the left due to inertia ( <0), but the control mass (1) moves to the right to push the elastic element to deform, so that the elastic element (21) exerts a rightward force on the controlled structure (A), so it does Negative work, this is between time points CD. Since the natural vibration frequency of the control mass (1) is higher than that of the controlled structure (A), before the controlled structure (A) changes its movement direction again, the movement speed of the control mass (1) has been reversed. And move to the left at a faster speed, so that the speed of the control mass (1) relative to the controlled structure (A) is negative ( <0), even at the time point D, the relative displacement of the control mass (1) relative to the controlled structure (A) is changed from positive to negative ( <0). At this time, the condition that the control law switches the movable joint (22) to "ON" is met. Therefore, by opening the movable joint (22), positive work on the controlled structure (A) can be avoided. Thereafter, the controlled structure (A) moves to the left of 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 controlled structure (A) moves to the left with its elastic restoring force (mainly from the deformation of the column force) To the right, the acceleration of the controlled structure (A) is positive ( > 0). This is between the time points DE. Over time, 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 from negative to zero ( = 0). Therefore, the condition that the movable joint (22) is switched to "off" is again met with the control law, so the control mass (1) and the controlled structure (A) are integrated again.

Step 6- The structure continues to move to the right due to inertia ( > 0), but the movement of the control mass (1) to the left pushes the elastic element (21) to deform, so that the elastic element (21) exerts a leftward force on the controlled structure (A), and thus controls the controlled structure ( A) Do negative work. This 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), before the controlled structure (A) changes its movement direction again, the movement speed of the control mass (1) has been reversed. And move to the right at a faster speed, so that the speed of the control mass (1) relative to the controlled structure (A) is positive ( > 0), even at the time point F, the relative displacement of the control mass (1) relative to the controlled structure (A) is changed from negative to positive ( > 0). At this time, the condition that the control law switches the movable joint (22) to "ON" is met. Therefore, by opening the movable joint (22), positive work on the controlled structure (A) can be avoided. Thereafter, the controlled structure (A) moves to the control mass (1) to the right, and the speed of the control mass (1) is relatively large.

Step 7-The above steps 3-6 are repeated switching. After the external force disappears, for 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 dissipating element (52) in the fixed unit (5) can be used to supplement the energy dissipating effect.

Here, the settings and speed weights without the fixed unit (5) are used again ( ) Is a positive value, which illustrates the operation of the impact semi-active mass damping device of the present invention under the action of a dynamic external force on the controlled structure (A) to help understand its damping performance. At this time, when the speed and acceleration response of the controlled structure (A) take into account the timing of the connection of the movable joint (22), for ease of understanding, please refer to the fifth figure together. Compared to the state where the speed weight is zero, the activity The timing of the joint (22) switching from off to on is the same, both when the relative displacement of the controlled structure (A) is from positive to negative (time points D, H) or from negative to positive (time points F, J ). But compare the timing when the movable joint (22) is switched from on to off. When the speed weight is positive, the speed response will be switched to off in advance. As shown in the time point C in the fifth figure, if the speed weight is 0, the acceleration should be switched from negative to positive when the speed of the controlled structure (A) reaches the lowest point, such as the time point C in the fourth figure. However, because the speed response participates in the calculation and judgment, it is slightly ahead of schedule. Similarly, the time points E and G in the figure are earlier than the fourth figure.

However, the foregoing embodiments or drawings do not limit the product structure or usage of the present invention, and any appropriate changes or modifications by those with ordinary knowledge in the technical field should be regarded as not departing from the patent scope of the present invention.

From the above, the composition and use of the system of the present invention can be understood, compared with the existing structure, the present invention has the following advantages:

The impact semi-active mass damping device and method of the present invention are mainly aimed at proposing a semi-active mass damper of a control law derived based on dynamic characteristics. The use of a control mass block frequency that is more than twice the basic natural frequency of the main structure can provide a ratio The aforementioned various dampers have higher shock absorption effects; their characteristics are: the difference between the control law and the frequency of the control mass and the conventional semi-active mass damper.

In summary, the embodiments of the present invention can indeed achieve the expected use effect, and the specific structure disclosed has not only been seen in similar products, nor has it been disclosed before the application. It has fully complied with the provisions of the Patent Law. In accordance with the law, the application for an invention patent was submitted in accordance with the law, and we are kindly requested to review it and grant the patent.

(A) ‧‧‧ controlled structure

(1) ‧‧‧ quality control block

(2) ‧‧‧ Activity Unit

(21) ‧‧‧ Elastic Element

(22) ‧‧‧ movable joint

(222) ‧‧‧ rigid outer casing

(222) ‧‧‧ through hole

(223) ‧‧‧ Piezoelectric brake

(3) ‧‧‧Vibration sensing unit

(31) ‧‧‧ Structure vibration sensor

(32) ‧‧‧ Controlling quality vibration sensor

(4) ‧‧‧ Controller

(5) ‧‧‧ fixed unit

(51) ‧‧‧ fixed rebound

(52) ‧‧‧ energy dissipating element

Figure 1: Schematic diagram of the architecture of the present invention

Figure 2: Schematic diagram of the movable joint of the present invention (piezoelectric)

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

Figure 4: Schematic diagram of the reaction under the condition of speed weight = 0 of the present invention

Fifth diagram: The reaction schematic diagram under the condition that the speed weight is greater than 0 according to the present invention

Claims (10)

An impact type semi-active mass shock absorbing device is mainly provided with an impact type semi-active mass shock absorbing device on a controlled structure, which includes: (1) a control mass, which is a rigidity provided to slide on the controlled structure; Object; (1) An active unit, which is arranged between the control mass and the controlled structure, and includes an elastic element connected to the control mass at one end and a movable joint, which is a disconnection / combination switch. , Which is connected to the other end of the elastic element, and can control the separation / combination of the switching and the elastic element in real time; 振动 A vibration sensing unit is used to sense the vibration response of the controlled structure and the control mass, including There is a structure vibration sensor connected to the controlled structure, and a control mass vibration sensor connected to the control mass; a controller, which corresponds to the structure vibration sensor and the control quality, respectively; The vibration sensor is connected to and receives the induction signal, and the controller is connected to the movable connector and controlled according to the induction signal The movable contact separated / combined by the switching operation. The impact-type semi-active mass vibration damping device described in item 1 of the scope of patent application, 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 vibration damping device described in item 1 of the scope of patent application, further comprising a fixing unit, one end of the fixing unit is fixed on the controlled structure, and the other end is fixed on the control mass, and The fixed unit includes a fixed resilient member capable of generating a control mass to return to an equilibrium position, and an energy dissipating element capable of dissipating energy. When the control mass and the controlled structure have a relative movement, it can generate a control quality The power of the block to restore equilibrium and the power to dissipate energy. The impact type semi-active mass vibration damping device described in item 1 of the patent application range, wherein the structure vibration sensor can measure the acceleration response and speed response of the controlled structure at the movable joint; and the control mass vibration The sensor can measure the absolute acceleration response, the absolute speed response of the control mass, its relative acceleration relative to the controlled structure, and the relative speed responder. The impact-type semi-active mass vibration damping device described in item 1 of the scope of patent application, wherein the controller and the structural vibration sensor of the vibration sensing unit, the control mass vibration sensor and the signal transmission between the movable joint It uses wired and wireless telecommunications links. The impact semi-active mass damping device as described in item 1 or 2 of the scope of patent application, wherein the movable joint is a braking device that can accept the control signal switching of the controller, and the braking device is a friction type, an electromagnetic type , Pin type, piezoelectric one. The impact semi-active mass vibration damping device described in item 2 of the scope of patent application, wherein the control mass vibration sensor uses one of an accelerometer, a speed meter, and a displacement meter. As the impact type semi-active mass shock absorbing device described in item 3 of the scope of patent application, wherein the fixed rebound member can be one of a spring, an upward curved track, and a single pendulum suspension device; and the energy dissipating element is used to dissipate the The mass and the energy of the controlled structure are further dissipated by friction, viscous damping, viscoelastic, hydraulic, and plastic hysteresis. According to the impact type semi-active mass vibration damping device described in the patent application item 6, wherein the movable joint further includes a rigid outer shell, a through hole for the elastic element to pass therethrough is formed in the rigid joint, and the rigid joint A piezoelectric brake is provided at the elastic element corresponding to the through hole on the outer casing, and the piezoelectric brake is externally connected with an electric power. An impact type semi-active mass vibration damping method includes the device described in any one of items 1 to 4 of the scope of patent application; when the controller continuously collects vibrations from the structure vibration sensor and the control mass vibration sensor Response and decide according to the control law that the state of the movable joint should be switched to "on" or "off". The method of judging the control law is: if the state of the movable joint is "on", then Switch to "Off" when the status is active; if the status of the active connector is "Off", then Switch to "On"when; Expressed as the speed of movement of the controlled structure, positive to the right; Expressed as the movement acceleration of the controlled structure, positive to the right; Expressed as the moving speed of the control mass relative to the controlled structure, positive to the right; Represents the displacement of the control mass relative to the controlled structure after the movable joint is switched off, that is, the amount of deformation of the elastic element; when Indicates that positive work will be done on the controlled structure; Is the speed weight, which can be a constant greater than or equal to zero.