JP2011226649A - Damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide damping technique for efficiently reducing vibrations in a natural vibration mode of a structure.SOLUTION: A damping device includes a spring 311, at least one attenuator 316, a transfer body 312 connected to the spring 311 and the attenuator 316, two support means 313A, 313B for applying force of the spring 311 and the attenuator 316 to the structure 300, in which both of them are mounted to the structure 300 or one of them is mounted to the structure 300 and the other forms a part of the structure 300, and a support member 314 supporting the transfer body 312 movably in a direction of the force applied between two points of the structure 300, and reduces the vibration caused on the structure 300 by applying the force between two points of the structure 300.

Description

  The present invention relates to a vibration damping device that reduces a mode generated in a structure by applying a compression force or an extension force between two points of the structure.

  Conventionally, as shown in FIG. 17, the vibration reducing device disclosed in Patent Document 1 reduces vibration of a vehicle panel 80 by anti-phase vibration, and includes two plate-like piezoelectric elements 811 and 812. A vibration plate 81, a spacer 82, and a mass body 83 attached to the vibration plate 81.

  The piezoelectric elements 811 and 812 are formed so as to generate a force that expands and contracts in the direction along the surface when a voltage is applied, and the two piezoelectric elements 811 and 812 are bonded together with the electrode 84 interposed therebetween. A diaphragm 81 is formed. The spacer 82 is provided to leave a space between the vibration plate 81 and the panel 80. With the configuration described above, a vibration mode having substantially the same magnitude as the vibration mode of the panel 80 and having a reverse phase can be applied to the panel 80.

Since the vibration reducing device of Patent Document 1 uses the diaphragm 81, it is suitable for damping a planar structure such as a panel 80 of a vehicle. Not suitable for shaking.
Note that the piezoelectric element used in the structure damping device described in Patent Document 2 and the piezoelectric element used in the vibration damping device described in Patent Document 3 are the diaphragm described in Patent Document 1, Similarly, since it is a planar element, it is expected that it is not suitable for damping a structure having a beam or a column.

  For a beam or column of a structure, a variable bending stiffness control device as described in Patent Document 4 is known. In this control device, as shown in FIG. 18, a restraint member 92 is provided along the pillar 91 of the structure 90 so as to be substantially parallel to the pillar, and the connection state between the restraint member 92 and the pillar 91 is changed in an auxiliary manner. It is configured to control the rigidity of the entire object. That is, this control device changes the expansion / contraction rigidity of the column, and assists the bending rigidity of the column by providing a jack between the upper beam 93 and the lower beam 94.

JP-A-6-10988 JP 2002-61708 A JP 2006-189697 A Japanese Patent Laid-Open No. 01-263333

  However, the control device of FIG. 18 does not take into account the mode shape of the natural vibration. Therefore, the variable bending stiffness can be controlled by using a jack with beams and columns positioned at both ends. Cannot be applied when reducing the natural vibration (when focusing on the mode shape and reducing the natural vibration).

  Another object of the present invention is that a large structure can be damped by a spring and an attenuator, and high-efficiency damping is possible not only for vibration modes with short nodes but also with vibration modes with long nodes. To shake.

The gist of the present invention is (1) to (4).
(1)
At least one spring and at least one attenuator;
At least one transmission body coupled to the spring and the attenuator;
Two support means for applying force from the spring and the attenuator to the structure, both attached to the structure or one attached to the structure and the other part of the structure When,
A support member that supports the transmission body so as to be movable in the direction of a force applied between two points of the structure;
With
In the vibration damping device that reduces vibration generated in the structure by applying the force between the two points of the structure,
The two points are present between the curve top of the distance derivative of the mode shape function with the position in the direction connecting the two points as a variable and the curve bottom existing next thereto, or the end point of the structure and next thereto. A vibration damping device selected between the curve top and the curve bottom.

(2)
The vibration damping device according to (1), wherein the two points are selected such that a point where the distance differentiation is zero is located between the two points.

(3)
At least one spring and at least one attenuator;
At least one transmission body coupled to the spring and the attenuator;
Two support means for applying force from the spring and the attenuator to the structure, both attached to the structure or one attached to the structure and the other part of the structure When,
A support member that supports the transmission body so as to be movable in the direction of a force applied between two points of the structure;
With
In the vibration damping device that reduces vibration generated in the structure by applying the force between the two points of the structure,
One of the two points is selected between a point where the distance derivative of the mode shape function with the position in the direction connecting the two points as a variable is zero and the curve top closest to the zero point. Select the other point near the point on the curve top opposite to the point where the distance derivative is zero, or one of the two points is zero when the distance derivative is zero A vibration damping device, characterized in that it is selected between the curve bottom closest to the point and the other point is selected in the vicinity of the opposite side of the curve bottom where the distance differentiation is zero.

(4)
At least one spring and at least one attenuator;
At least one transmission body coupled to the spring and the attenuator;
Two support means for applying force from the spring and the attenuator to the structure, both attached to the structure or one attached to the structure and the other part of the structure When,
A support member that supports the transmission body so as to be movable in the direction of a force applied between two points of the structure;
With
In the vibration damping device that reduces vibration generated in the structure by applying the force between the two points of the structure,
The two points are in the vicinity of the curve top of the distance derivative of the mode shape function with the position in the direction connecting the two points as a variable and the curve bottom near the adjacent point, or near the end point of the structure and the adjacent point. A vibration control device that is selected near the curve top or the curve bottom.

  According to the present invention, the large structure can be damped by the spring and the attenuator as in the first mode. In this case as well, as in the first mode, of course, the vibration mode in which the distance between the nodes is short, High-efficiency vibration control can be performed even in vibration modes with long knot intervals.

(A) is a plan view showing a vibration damping device using an actuator, (B) is a side view, and (C) is a front view. (A) is a diagram showing an example in which two transmitter elements are connected and used as one transmitter, (B) is a diagram showing an example in which three transmitter elements are connected and used as one transmitter. is there. It is a figure which shows the example which used the sliding bearing as a supporting member. It is a figure which shows the example using the support by a leaf | plate spring as a support member, (A) is a top view, (B) is a side view, (C) is a front view. It is a figure which shows the example which uses a hydraulic jack. It is a figure which shows the example which comprised the damping device so that extension force might be applied to a transmission body, (A) is a side view of a damping device, (B) looked at the arrow q1, q1 direction in (A). Explanatory drawing (C) is explanatory drawing which looked at the arrow q2, q2 direction in (A). It is a model figure which shows the example which applied the damping device using an actuator to the structure fixed to both ends. (A), (B), (C), (D) are the mode shape function φn (x) and the differential function dφn (x) when n = 1, 2, 3, 4 in the model diagram of FIG. ) / Dx. (A), (B), (C), (D), (E), (F) is a figure which shows the example of selection of two points | pieces about the primary mode shown to FIG. 8 (A). It is a model figure which shows the example which applied the damping device using an actuator to the structure (cantilever) of one end fixation and one end freedom. (A), (B), (C), (D) are the mode shape function φn (x) and the differential function dφn (x) when n = 1, 2, 3, 4 in the model diagram of FIG. ) / Dx. (A), (B) is explanatory drawing which shows the example of selection of 2 points | pieces about the primary mode shown to FIG. 11 (A). (A) to (E) are explanatory views of an example in which the direction of the driving force of the actuator is orthogonal to the direction of the force applied to the transmission body. It is a block diagram which shows the damping device using an actuator. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows embodiment of this invention, (A) shows the example whose damping device consists of one spring, one transmission body, a pair of support means, one support member, and an attenuator. (B) is a figure which shows the example which uses a wire as a transmission body and uses a pulley as a supporting member. It is a figure which shows other embodiment of this invention, (A) is explanatory drawing of the example in which the direction of a spring and a damper is orthogonal to the direction of the force applied to a transmission body, (B) is (A). (C) is a figure using a link mechanism in place of the wire and pulley in the vibration damping device of (A). It is explanatory drawing of the prior art which reduces the vibration of the panel of a vehicle by the vibration of a reverse phase. It is a figure which shows the damping device considered in order to eliminate the inconvenience in the damping technology of FIG.

Before describing an embodiment of the present invention, a vibration damping device using an actuator will be described.
1A, 1B, and 1C are a plan view, a side view, and a front view showing a vibration damping device using an actuator, and this vibration damping device applies vibration to the structure to the structure. The generated vibration can be reduced. In FIG. 1, for convenience of explanation, only a part of the structure 100 (here, H steel) is shown.
The vibration control device 11 includes one actuator 111, one transmission body (in this embodiment, a rod-like body) 112, a pair of support means 113A and 113B, and one support member 114. In FIG. 1A, the support member 114 is not shown, and in FIG. 1C, the actuator 111, the transmission body 112, the support means 113B, and the support member 114 are not shown.

  The actuator 111 is a piezoelectric material (element) in FIG. 1 and generates a pressing force in the X-axis direction (± X direction) shown in FIGS. In addition to piezoelectric materials, hydraulic actuators and electromagnetic actuators (linear motors, rotary motors using a rotation-linear conversion mechanism) can also be used as actuators.

As shown in FIGS. 1A and 1B, the support means 113A and 113B attached to the two points P ₁ and P ₂ of the structure 100 function as brackets, and support the actuator 111 and the transmission body 112 from both ends thereof. To do. In this embodiment, the point P ₁ is the center point of the surface where the support means 113A is in contact with the structure 100, and the point P ₂ is the center point of the surface where the support means 113B is in contact with the structure 100. Note that the point P ₁ is an end point on the surface in contact with the structure 100 on the actuator 111 side of the support means 113A, and the point P ₂ is on the surface in contact with the structure 100 on the transmission body 112 side of the support means 113B. It can also be an end point.

  The support member 114 is a device (linear bush) provided with a linear bearing provided between the actuator 111 and the structure 100, and supports the transmission body 112 from the structure 100 side without being restricted in the direction of the driving force. . In the vibration damping device using the actuator, the support member (reference numeral 114 in FIG. 1) is provided for preventing buckling or displacement of the transmission body 112, but there is no danger of buckling or displacement. In such a case, it may not be provided.

In FIG. 1, the actuator 111 is provided with a mounting jig 115 made of metal, and the mounting jig 115 is pressed against the actuator 111. The jack bolt provided on the support means 113A adjusts the difference between the total length of the length between the support means 113A and 113B and the length of the transmission body 112, the actuator 111, and the mounting jig 115, and supports the jack bolt. A predetermined stretching force is applied between the means.
If the actuator 111 is not a push-pull type, a drive command of 20% to 80% is given as a drive command for the actuator, if a state in which a bias component of a constant value (for example, 50% of the maximum capacity) is added to the non-actuated state In this case, it corresponds to the pushing / pulling force of ± 30%.

  FIG. 2A is a diagram showing a mode in which two transmitter elements 112A and 112B (see the transmitter 112 shown in FIGS. 1A and 1B) are connected and used as one transmitter. . In FIG. 2A, a coupling tool 116 is provided for connection with the transmission element 112A, 112B, and a support member 114 is provided between the transmission element 112A, 112B and the structure 100, respectively. ing.

  FIG. 2 (B) is a diagram showing a mode in which three transmitter elements 112A, 112B, and 112C are connected and used as one transmitter, and the transmitter elements 112A and 112B are connected, and the transmitter elements 112B and 112C are used. For the connection, a connecting tool 116 is provided. Further, support members 114 are provided between the transmission element 112A, 112B, 112C and the structure 100, respectively.

  In the vibration damping device 11 in FIG. 1 and the vibration damping device 11 in FIGS. 2A and 2B, an example in which a linear bearing is used as the support member 114 is shown. Various configurations that can be movably supported can be employed. For example, a sliding support can be used as the support member 114 as shown in FIG. This sliding support is a member that has been surface-treated with a material having excellent sliding properties (indicated by hatching in FIG. 3), and is configured to support the transmission body 112 by this member. Further, for example, the support member 114 may be a metal or ceramic that is not particularly subjected to a surface treatment with a material having excellent sliding properties.

  Further, as the sliding support member 114, a leaf spring as shown in the plan view of FIG. 4A, the side view of FIG. 4B, and the front view of FIG. In FIG. 4, the sliding support member 114 includes a leaf spring H and a leaf spring fixing portion S and a leaf spring fixing portion B provided at both ends of the leaf spring H, and the leaf spring fixing portion S is attached to the structure 100. The leaf spring fixing portion B is attached to the transmission body 112. The leaf spring H can support the transmission body 112 so as to be movable in the center axis method.

  In the embodiment shown in FIG. 1, the embodiment shown in FIGS. 2A and 2B, and the embodiment shown in FIG. 3, a piezoelectric material is used as the actuator 111. However, in the vibration damping device using the actuator, Without limitation, a hydraulic jack can be used as shown in FIG. In FIG. 5, the actuator 111 (hydraulic jack) is attached to the supporting means 113A by bolting or the like, and the attachment jig 115 is not used.

In the above-described vibration damping device 11, the case where a compressive force is applied to the transmission body 112 has been described, but the vibration damping device 11 can be configured such that an extension force is applied to the transmission body 112. 6A is a side view of the vibration damping device 11, FIG. 6B is an explanatory view when the directions of the arrows q ₁ and q ₁ are viewed in FIG. 6A, and FIG. 6C is the arrow q ₂ in FIG. , Q ₂ direction.

In FIG. 6A, the end of the transmission body 112 is gripped by the transmission body gripping tool 117, and the pushing force of the actuator is converted into the extension force of the transmission body 112.
When a compressive force is applied to the transmission body 112, a rod-shaped body must be used as the transmission body 112, and there is a risk of buckling. However, in FIGS. 6A to 6C, the transmission body 112 expands. Since force is applied, there is no risk of buckling even if a rod-like body is used as the transmission body 112. In FIGS. 6A to 6C, a rod-shaped body is used as the transmission body 112, but a wire can also be used.

  FIG. 7 is a model diagram showing an embodiment in which a vibration damping device using an actuator is applied to a structure that is fixed at both ends (an example in which a cross-section fixed at both ends is a uniform beam). Hereinafter, the operation of the vibration damping device of FIG. 7 will be described including the operation of the vibration damping device 11 described in FIGS. 1 to 6. In FIG. 7, the entire vibration damping device 11 is not shown, and only the support means 113A and 113B are shown.

In this embodiment, both ends of the structure 100 are fixed. Support means 113A and 113B are attached to two points P ₁ and P ₂ on the structure 100, and an actuator and a transmission body (not shown) are provided between the support means 113A and 113B. FIG. 7 shows a state in which a force is applied to the transmission body so as to spread the support means 113A and 113B, whereby moments M and −M act on the structure.

The behavior when the structure 100 undergoes natural vibration is generally represented by a mode shape function φ _n (x).
Here, φ _n (x) is a function whose length is defined in the X-axis direction of the structure, and in a beam having a uniform cross section fixed at both ends in this embodiment,
φ _n (x)
= Coshk _n x-cosk _n x
-[(Cosk _n L-coshk _n L) / (sink _n L-sinhk _n L)]
X (sinhk _n x-sink _n x) (1)
It is. Further, the differentiation of φ _n is expressed as follows.
dφ _n (x) / dx
_{= K n sinhk n x + k} n sink n x
-[(Cosk _n L-coshk _n L) / (sink _n L-sinhk _n L)]
_{× (k n coshk n x-} k n cosk n x) ··· (2)
In the above equations (1) and (2), k _n (n = 1, 2, 3, 4,...) Is
k ₁ = (2.267) ^1/2 × π / L
k ₂ = (6.249) ^1/2 × π / L
k ₃ = (12.25) ^1/2 × π / L
k ₄ = (20.25) ^1/2 × π / L
It becomes.
Here, L is the length of the beam.

8 (A), (B), (C), and (D), the mode shape function φ _n (x) when n = 1, 2, 3, 4 is indicated by a solid line, and dφ _n (x) / dx is indicated by a broken line. Further, a point at which dφ _n (x) / dx is maximized is indicated by a white circle, and a point at which dφ _n (x) / dx is minimized is indicated by a black circle. In FIG. 7, the total length of the structure 100 is a unitless numerical value 4.0, and the amplitude is also indicated by a unitless numerical value.
Note that the end points indicated by white triangles can be handled in the same manner as the points of dφ _n (x) / dx = 0 (can be point candidates when selecting P ₁ and P ₂ ).
In the case of the attachment mode of the actuator 111 shown in FIG. 7, if two arbitrary points on the beam are P ₁ and P ₂ , Δ (φ _n ′) can be defined as a function indicating the influence on the mode.
Δ (φ _n ′) = dφ _n (P ₁ ) / dx−dφ _n (P ₂ ) / dx (3)

The top of the peak (curve top, white circle point) x ₁ of the differential dφ _k (x) / dx of the shape function φ _k of the _k-th mode to be controlled, and the lowest point (curve) If the bottom, black circle point) x ₂ , then Δ (φ _k ′) selects P ₁ as the point x ₁ (white circle point), and P ₂ becomes the local minimum point (black dot) ) becomes the maximum when you select to x _2.

9 (A), (B), (C), (D), (E), and (F) are shown in FIG. 8 (A) in which two points P ₁ and P ₂ are selected for the primary mode. Will be explained.
9 (A) is two points P _1, P _2, hatched between (the area between the curve top d.phi ₁ / dx (open circles) and d.phi ₁ / dx curve bottom present in the next (closed circles) Shows the case of selecting. In FIG. 9A, a point where dφ ₁ / dx becomes zero is selected between P ₁ and P ₂ so as not to be located.

FIG. 9 (B) the two points P _1, P _2, hatched between (the area between the curve top d.phi ₁ / dx (open circles) and d.phi ₁ / dx curve bottom present in the next (closed circles) And a point where the distance differential dφ ₁ / dx is zero is selected between P ₁ and P ₂ .

FIG. 9C shows two points P ₁ and P ₂ between a point where dφ ₁ / dx is zero and a curve top (white circle) of dφ ₁ / dx closest to the zero point (this region). And the other point P ₂ is selected in the vicinity of the opposite side of the point where dφ ₁ / dx of the curve top of dφ ₁ / dx becomes zero.

Figure 9 (D), the two points _{P 1, P 2, dφ 1} / dx curve top near the d.phi ₁ / dx hatched curve bottom near (curve top and near the curve bottom near the region of that present in the next Shows the case of selecting.

FIG. 9E shows two points P ₁ and P ₂ between the end point of the structure 100 (the white triangle at the left end in the figure) and the curve top (white circle) of dφ ₁ / dx existing next to it (this circle) The area is indicated by hatching).
FIG. 9 (F) shows two points P ₁ and P ₂ in the vicinity of the end point of the structure 100 (the white triangle at the left end in the figure) and the vicinity of the curve top (white circle) of dφ ₁ / dx existing next to it. The area is indicated by hatching).

  In the case of FIG. 9 (D), the influence on the mode is the largest and the vibration damping efficiency is the highest, but there are cases where it cannot be implemented due to some restrictions of the structure, in which case FIGS. One of C), (E), and (F) is selected.

FIG. 10 is a model diagram showing an embodiment in which a vibration damping device using an actuator is applied to a one-end fixed structure (cantilever). Hereinafter, the operation of the vibration damping device of FIG. 10 will be described.
10 is the same as FIG. 7 except that one end of the structure 100 is fixed and the other end is free.
The nth-order mode shape function φ _n (x) for the structure 100 of FIG.
φ _n (x)
= Coshk _n x-cosk _n x
− [(Cos _{k n} L + coshk _n L) / (sink _n L + sinhk _n L)]
X (sinhk _n x-sink _n x) (4)
It is represented by Further, the differentiation of φ _n is expressed as follows.
dφ _n (x) / dx
_{= K n sinhk n x + k} n sink n x
− [(Cos _{k n} L + coshk _n L) / (sink _n L + sinhk _n L)]
_{× (k n coshk n x-} k n cosk n x) ··· (5)
k ₁ = (0.356) ^1/2 × π / L
k ₂ = (2.232) ^1/2 × π / L
k ₃ = (6.252) ^1/2 × π / L
k ₄ = (12.25) ^1/2 × π / L

In FIGS. 11A, 11B, 11C, and 11D, the mode shape function φ _n (x) when n = 1, 2, 3, 4 is indicated by a solid line, and dφ _n (x) / dx is indicated by a broken line. Further, a point at which dφ _n (x) / dx is maximized is indicated by a white circle, and a point at which dφ _n (x) / dx is minimized is indicated by a black circle. In FIG. 11, the total length of the structure 100 is a unitless numerical value 4.0, and the amplitude is also indicated by a unitless numerical value. Note that the end points indicated by white triangles can be handled in the same manner as the points of dφ _n (x) / dx = 0 (can be point candidates when selecting P ₁ and P ₂ ).
In the present embodiment, Δ (φ _n ′) in the expression (3) can be defined as a function indicating the influence on the mode. In the case of the k-th order mode, Δ (φ _k ′) selects P ₁ as a point x ₁ (white circle point), and P ₂ becomes a minimum point (black circle point) x ₂ adjacent to it. Maximum when selected.

12 (A) and 12 (B), the mode of selection of the two points P ₁ and P ₂ for the primary mode shown in FIG. 11 (A) will be described.
FIG. 12 (A) shows two points P ₁ and P ₂ as an end point (white triangle) (in this case, a minimum value of dφ ₁ (x) / dx) and dφ ₁ / A case is shown in which it is selected between the curve top (white circle) of dx (which is also an end point in this case) (this region is indicated by hatching).

FIG. 12 (B) shows two points P ₁ and P ₂ near the end point (white triangle) of the structure and the curve top (white circle) of dφ ₁ / dx existing next to it (the vicinity of the end point and the vicinity of the curve top). The area is indicated by hatching).
Here, two examples of a simple uniform cross-section beam have been shown. If a mode shape function is obtained from a finite element analysis even for a complicated structure, appropriate P ₁ and P ₂ can be derived by the same method. it can.

In ordinary structures, the order of vibration modes that require damping is often low, but the present invention is also effective when the vibration mode is high.
The vibration mode that requires damping is not limited to one for one structure, and may be two or three or more. For example, it is possible to attach two two vibration control devices having the same configuration to two different predetermined points on the structure in the same direction connecting the two predetermined points. For example, for a certain beam or column of a structure, vibration suppression is necessary for the i-th order mode shape function φ _Ai , and at the same time for a j-th order mode shape function φ _Bj for the other beams or columns of the structure. Vibration suppression may be required. In addition, the i-order mode shape function φ _Ai may be controlled for two opposing sides of the rectangular frame, and the j-order mode shape function φ _Bj may be controlled for the remaining two opposing sides. .

FIGS. 13A to 13E are explanatory views of the embodiment in the case where the direction of the driving force of the actuator is orthogonal to the direction of the force generated in the transmission body 212.
In FIG. 13A, the vibration damping device 21 provided in the structure 200 includes an actuator 211, a transmission body 212 made of a wire, support means 213A and 213B, and a support member 214 made of a pulley. FIG. 13B shows a state where the supporting means 213A and 213B are attached to P ₁ and P ₂ .
FIG. 13C shows an embodiment in which a spring 216 for preventing sagging is provided along with the actuator 211, and FIG. 13D shows an embodiment in which an attenuator 217 is further provided.
FIG. 13E shows an embodiment using a link mechanism in place of the wire and pulley in the vibration damping device 21 of FIG. The transmission body 212 is two link rods, and the support member 214 is a fulcrum. One end of each link rod is attached to a link shaft provided in the actuator, and the other end of the link rod is connected to a link shaft provided in the support means 213A and 213B. Although not shown in FIG. 13 (E), there may be a case where a spring is added to the actuator 211 or an attenuator.

  FIG. 14 is a functional block diagram of a vibration damping device using an actuator. In FIG. 14, the vibration of the structure 100 is detected by the vibration sensor 118, and the control device 119 generates a drive signal for the actuator 111 based on information from the vibration sensor. In FIG. 14, the control device acquires temperature information T from a thermometer (not shown), and may correct a change in size due to thermal expansion / contraction of the transmission body or the like.

Embodiments of the present invention will be described below.
In the above description, an actuator is used as a vibration suppression source of the vibration damping device. However, a spring and an attenuator can be used instead of the actuator.

In FIG. 15A, the vibration damping device 31 includes one spring 311, one transmission body (rod-like body in this embodiment) 312, a pair of support means 313 A and 313 B, and one support member 314. And an attenuator 316.
The support means 313A and 313B are attached to the two points P ₁ and P ₂ of the structure 300, one end of the transmission body 312 is attached to the support means 313B, and the other end passes through the hole of the support means 313A. Connected to. A spring 311 and an attenuator 316 are installed between the gripper and the support means 313A. In this embodiment, the point P ₁ is the center point of the surface where the support means 313A is in contact with the structure 300, and the point P ₂ is the center point of the surface where the support means 313B is in contact with the structure 300.
The support member 314 is a linear bearing provided between the transmission body 312 and the structure 300, and supports the transmission body 312 without restraining it in the axial direction of the transmission body. In the drawing of the support means 313B, the clearance between the support means 313A and the gripping tool is adjusted by an adjustment bolt at one end of the transmission body 312 on the right side, the compression force of the spring 311 is set to a predetermined value, and the transmission body 312 is expanded and contracted. Can give power.
The attenuator 316 performs vibration suppression by consuming vibration energy transmitted through the transmission body.

  FIG. 15B shows an embodiment in which a wire is used as the transmission body 312 and a pulley is used as the support member 314.

16A and 16B are explanatory views of an embodiment of the vibration damping device in which the spring 411 and the attenuator 416 are orthogonal to the length direction of the transmission body 412. FIG. In FIG. 16A, the vibration damping device 41 provided in the structure 400 includes a spring 411, a transmission body 412 made of a wire, support means 413A and 413B, a support member 414 made of a pulley, and an attenuator 416. It consists of. The transmission body 412 is stretched around the support means 413A and 413B in the longitudinal direction of the structure 400, and the spring 411, the attenuator 416, and the support member 414 are provided in the middle of the transmission body 412. FIG. 16B shows a state in which the supporting means 213A and 213B are attached to P ₁ and P ₂ .

  FIG. 16C shows an embodiment in which a link mechanism is used in place of the wire and pulley in the vibration damping device 41 of FIG. The transmission body 412 is two link rods, and the support member 414 is a fulcrum. One end of each link rod is attached to a link shaft provided in the actuator, and the other end of the link rod is connected to a link shaft provided in the support means 413A, 413B.

  The damping device using the spring and the attenuator as the damping source can exhibit the operations shown in FIGS. 7 to 12 as in the damping device using the actuator as the damping source.

11, 21, 31, 41 Damping device 100, 200, 300, 400 Structure 111, 211 Actuator 112, 212, 312, 412 Transmitter 112A, 112B Transmitter element 113A, 113B, 213A, 213B, 313A, 313B, 413A, 413B Support means 114, 214, 314, 414 Bearing member 115 Jig 116 Connecting tool 117 Transmitter gripper 118 Vibration sensor 119 Controller 216, 311, 411 Spring 217, 316, 416 Attenuator B, S Leaf spring fixing part H leaf spring M moment T temperature information x ₁ vertex x ₂ lowest point

Claims (4)

At least one spring and at least one attenuator;
At least one transmission body coupled to the spring and the attenuator;
Two support means for applying force from the spring and the attenuator to the structure, both attached to the structure or one attached to the structure and the other part of the structure When,
A support member that supports the transmission body so as to be movable in the direction of a force applied between two points of the structure;
With
In the vibration damping device that reduces vibration generated in the structure by applying the force between the two points of the structure,
The two points are present between the curve top of the distance derivative of the mode shape function with the position in the direction connecting the two points as a variable and the curve bottom existing next thereto, or the end point of the structure and next thereto. A vibration damping device selected between the curve top and the curve bottom.   2. The vibration damping device according to claim 1, wherein the two points are selected such that a point at which the distance derivative is zero is located between the two points. At least one spring and at least one attenuator;
At least one transmission body coupled to the spring and the attenuator;
Two support means for applying force from the spring and the attenuator to the structure, both attached to the structure or one attached to the structure and the other part of the structure When,
A support member that supports the transmission body so as to be movable in the direction of a force applied between two points of the structure;
With
In the vibration damping device that reduces vibration generated in the structure by applying the force between the two points of the structure,
One of the two points is selected between a point where the distance derivative of the mode shape function with the position in the direction connecting the two points as a variable is zero and the curve top closest to the zero point. Select the other point near the point on the curve top opposite to the point where the distance derivative is zero, or one of the two points is zero when the distance derivative is zero A vibration damping device, characterized in that it is selected between the curve bottom closest to the point and the other point is selected in the vicinity of the opposite side of the curve bottom where the distance differentiation is zero. At least one spring and at least one attenuator;
At least one transmission body coupled to the spring and the attenuator;
Two support means for applying force from the spring and the attenuator to the structure, both attached to the structure or one attached to the structure and the other part of the structure When,
A support member that supports the transmission body so as to be movable in the direction of a force applied between two points of the structure;
With
In the vibration damping device that reduces vibration generated in the structure by applying the force between the two points of the structure,
The two points are in the vicinity of the curve top of the distance derivative of the mode shape function with the position in the direction connecting the two points as a variable and the curve bottom near the adjacent point, or near the end point of the structure and the adjacent point. A vibration control device that is selected near the curve top or the curve bottom.

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