JP5452452B2 - Damper and vibration control device - Google Patents

Description

  The present invention relates to a damper and a vibration control device.

  It has been proposed to dampen a structure using a rotary inertia mass damper using the rotary inertia mass. Damping means may be provided in such a rotary inertia mass damper.

  For example, in Patent Document 1, the auxiliary mass receives resistance due to the shear resistance of the viscous body by filling the viscous body between the inner peripheral surface of the holding body constituting the rotary inertia mass damper and the outer peripheral surface of the auxiliary mass. The vibration in the axial direction is attenuated by generating a damping force that attenuates the rotational kinetic energy of the auxiliary mass.

  Further, for example, in Patent Document 2 and Patent Document 3, when a viscous fluid is sealed in the gap between the inner surface of the frame constituting the rotary inertia mass damper and the rotating body, and the rotating body rotates relative to the frame, the viscosity is increased. The fluid causes a viscous force in the direction opposite to the rotational direction to act on the rotating body, and a rotational torque reaction force is applied to the rotating body to attenuate the axial vibration.

  However, the configuration in which the rotational resistance around the shaft is attenuated by the viscous body or the viscous fluid directly or via the rotating body or the like with the viscous body or the viscous fluid as described above increases as the moving speed (vibration speed) in the axial direction increases. The frictional resistance is reduced and the axial resistance is reduced.

JP 2006-125110 A JP 2010-77726 A JP 2010-90555 A

  In view of the above, the present invention prevents or suppresses a decrease in the axial resistance force as the axial movement speed (vibration speed) of the shaft portion increases in a damper or a vibration control device using rotational inertial mass. It is a problem to do.

  The invention of claim 1 is provided with a shaft portion having a first shaft portion and a second shaft portion, a housing in which the shaft portion is movably inserted in the axial direction, and the housing. A rotational inertial mass generating unit that generates rotational inertial mass by converting a linear linear displacement of the shaft portion relative to the housing into rotation of a mass body; and An attenuating portion for attenuating the axial displacement relative to the housing by applying an axial resistance force to the second shaft portion; and rigidity K1 of the first shaft portion and rigidity of the second shaft portion. A damper in which K2 is set such that K1 ≧ K2.

  According to the first aspect of the present invention, there is provided a rotary inertia mass generating portion that generates a rotary inertia mass by converting a linear displacement in the axial direction of the first shaft portion constituting the shaft portion into rotation of the mass body, and a shaft. And an attenuating portion that applies axial resistance to the second shaft portion constituting the portion and attenuates linear displacement in the axial direction relative to the casing of the second shaft portion. The first shaft portion rigidity K1 and the second shaft portion rigidity K2 are set such that K1 ≧ K2.

  In this way, even if the rotary inertia mass generation unit and the attenuation unit are arranged in series on the same shaft, the rotation inertia mass generation unit and the attenuation unit are generated in the same manner as the configuration in which the rotation inertia mass generation unit and the attenuation unit are arranged in parallel. The vibration of the shaft portion of the damper having the portion can be damped.

  In addition, when the rigidity K1 of the first shaft portion and the rigidity K2 of the second shaft portion are not set to K1 ≧ K2, the attenuation portion does not exhibit a damping effect.

  Here, the configuration in which the rotational resistance around the shaft is applied to the shaft portion directly or via a rotating body or the like with a viscous body or viscous fluid, the frictional resistance decreases as the moving speed (vibration speed) in the axial direction increases. , Axial resistance decreases.

  On the other hand, the resistance in the axial direction is increased according to the moving speed (vibration speed) in the second axial direction by providing a resistance in the axial direction with respect to the second shaft portion. That is, the axial direction of the shaft portion is compared with a configuration to which the present invention is not applied, for example, a configuration in which a rotational resistance is applied to the shaft portion directly or via a rotating body with a viscous body or a viscous fluid. As the moving speed (vibration speed) increases, the axial resistance force is prevented or suppressed.

  According to a second aspect of the present invention, the rotating mass generator is configured such that the first shaft portion that constitutes one side of the shaft portion penetrates, and the rotating body that is rotatably held in the housing; and the first shaft portion Screwing means for converting linear displacement of the shaft portion in the axial direction into rotation around the axis of the rotating body, and integral with the rotating body. The mass body rotating around an axis.

  According to the invention of claim 2, the linear displacement of the shaft portion with respect to the housing is such that the rotating body into which the first shaft portion is inserted is rotationally displaced by the screwing means. Then, the rotary inertia mass body is rotated around the axis integrally with the rotary body, thereby generating a rotary inertia mass.

  According to a third aspect of the present invention, there is provided guide means provided on the casing for guiding the linear displacement of the shaft portion and preventing the shaft portion from rotating about the axis.

  In the invention of claim 3, the shaft portion is prevented from being twisted by the guide means for guiding the linear displacement of the shaft portion and preventing the shaft portion from rotating about the axis.

  According to a fourth aspect of the present invention, the damper according to any one of the first to third aspects is provided between the first part and the second part of the structure that is relatively moved by a disturbance, and the first part is provided. The shaft portion of the damper is directly or indirectly connected to the second portion, and the casing of the damper is directly or indirectly connected to the second portion.

  In invention of Claim 4, the damper of any one of Claims 1-3 is provided.

  Here, in the configuration in which the rotational resistance is provided around the shaft directly or via a rotating body or the like with a viscous body or viscous fluid, the frictional resistance increases as the moving speed (vibration speed) in the axial direction increases. , Axial resistance decreases.

  On the other hand, the damper according to any one of claims 1 to 3 is configured to provide resistance in the axial direction with respect to the second shaft portion, whereby the moving speed in the second axial direction ( The resistance force in the axial direction increases with the vibration speed. Therefore, even if the relative movement speed between the first part and the second part, that is, the linear displacement speed (vibration speed) of the shaft portion is increased, a high vibration control effect can be obtained.

  The invention according to claim 5 includes a spring element arranged in series with the damper.

  In the invention of claim 5, the rotational inertial mass is amplified by appropriately setting the specifications of the damper and the spring element. In other words, a large rotational inertial mass can be obtained with a small mass body. Therefore, since the performance of the vibration control device is improved, the structure is effectively damped.

  According to the first aspect of the present invention, a configuration to which the present invention is not applied, for example, a configuration in which a rotational resistance is provided around the shaft directly or via a rotating body or the like in the shaft portion with a viscous body, a viscous fluid, or the like. As compared with the above, it is possible to prevent or suppress the axial resistance force from decreasing as the moving speed (vibration speed) of the shaft portion increases.

  According to the second aspect of the present invention, the rotation inertia mass can be easily generated by the rotation inertia mass rotating around the axis integrally with the rotation body provided in the housing.

  According to the invention described in claim 3, twisting of the shaft portion is prevented.

  According to invention of Claim 4, even if a vibration speed becomes high, a high damping effect is acquired.

  According to the fifth aspect of the present invention, it is possible to improve the vibration control effect as compared with the configuration having no spring element.

It is a front view in which the damping damper concerning a first embodiment of the present invention is provided in the frame of a structure. It is sectional drawing along the axial direction which shows the internal structure of the damping damper which concerns on 1st embodiment of this invention. (A) is an arrow view along the AA line of FIG. 2, (B) is an arrow view along the BB line of FIG. (A) is a figure of the state which the structure moved horizontally to the left side from the state of FIG. 1, (B) is a figure of the state which the structure moved horizontally to the right side from the state of FIG. It is sectional drawing along the axial direction which shows the internal structure of the damping damper which concerns on 2nd embodiment of this invention. (A) is the model figure which modeled the damping damper of 1st embodiment of this invention, (B) is the model figure which modeled the damping damper of 2nd embodiment of this invention, (C FIG. 4 is an analysis model diagram in numerical analysis of the vibration control damper of the first embodiment and the vibration control damper of the second embodiment. (A) is a graph for demonstrating the relationship between the axial direction moving speed and axial direction resistance value in the damping damper of 1st embodiment of this embodiment, (B) is this invention. The relationship between the axial movement speed and the axial resistance value of a damping damper configured to apply rotational resistance to the shaft part directly or via a rotating body with a viscous body or viscous fluid that is not applied. It is a graph to show. It is an analysis model figure of the damping device which connected the spring in series with respect to the damping damper of 1st embodiment, or the damping damper of 2nd embodiment. (A) is explanatory drawing explaining the arrangement | positioning position in the case of providing a spring in the damping damper concerning 1st embodiment of this invention, (B) is a spring in the damping damper concerning 2nd embodiment of this invention. It is explanatory drawing explaining the arrangement position in the case of providing. It is a front view in which the toggle damping device which concerns on embodiment of the modification of this invention is provided in the frame of the structure.

<First embodiment>
The damper which concerns on 1st embodiment of this invention is demonstrated about a damping device.

  As shown in FIG. 1, a damping damper 100L and a damping damper 100R are installed in a frame 24 composed of a left column 20L, a right column 20R, an upper beam 22A, and a lower beam 22B constituting the structure 10. Are arranged side by side. Further, the left vibration control damper 100 </ b> L and the right vibration control damper 100 </ b> R are arranged symmetrically in the frame 24. In the following description, when it is necessary to distinguish between left and right, either L or R is added after the symbol, and when it is not necessary to distinguish, L and R are omitted.

  The vibration control damper 100L and the vibration control damper 100R are configured such that a shaft portion 120 is inserted in a cylindrical housing 110 so as to be movable in the axial direction.

  In the damping damper 100L, an attachment portion 128L provided at one end portion of the shaft portion 120L (one end portion of a shaft 122L described later) is rotatable to an attachment portion 40L attached to a corner portion of the upper beam 22A and the column 20L. Is attached to the other end portion of the casing 110R (the other end portion of an outer cylinder 144L described later) and is rotatable to the attachment portion 30 attached to the substantially central portion in the left-right direction of the lower beam 22B. It is connected to.

  Similarly, the damping damper 100R has an attachment portion 128R provided at one end portion of the shaft portion 120R (one end portion of the shaft 122R described later) attached to the attachment portion 40R attached to the corner portion of the upper beam 22A and the column 20R. An attachment portion 118R, which is rotatably connected and provided at the other end portion of the casing 110R (the other end portion of an outer cylinder 144R described later), is attached to the attachment portion 30 attached to a substantially central portion in the left-right direction of the lower beam 22B. It is connected rotatably.

  Here, the installation (arrangement) configuration of the damping damper 100 as shown in FIG. 1 is an example, and if horizontal deformation of the frame 24 (see FIGS. 4A and 4B) can be suppressed. It may be installed (arranged) in any way. Furthermore, you may install in the frame of any layer (floor) of the structure 10. FIG. Moreover, you may install in site | parts other than a frame. That is, the structure 10 may be installed (arranged) so as to obtain a vibration control effect by providing the vibration control damper 100 between the first part and the second part where the structure 10 is relatively moved by a disturbance such as an earthquake. Further, a toggle mechanism may be applied as described in JP 2008-002165 A and the like. An example of the toggle mechanism will be described later with reference to FIG.

  Next, the damping damper 100 will be described in detail. Since the left and right damping dampers 100R and 100L have the same structure, L and R will be omitted in the description.

  As shown in FIG. 2, as described above, the damping damper 100 has the shaft portion 120 inserted into the cylindrical housing 110 so as to be movable in the axial direction.

  The damping damper 100 has a rotary inertia mass damper portion 150 and an oil damper portion 180, and these are joined in series. Further, a part where the rotary inertia mass damper part 150 and the oil damper part 180 are joined is a joint part 140.

  First, the rotary inertia mass damper unit 150 will be described.

  The rotary inertia mass damper unit 150 includes a rotating body 152, a holder 112 that configures the casing 110, and a shaft 122 that configures the shaft unit 120.

  A female screw groove 122 </ b> A is formed on the outer peripheral surface of the shaft 122. The shaft 122 is inserted into a cylindrical rotating body 152 formed on the inner peripheral surface of a male screw 152A that is screwed into the female screw groove 122A. A mounting portion 128 is provided at one end of the shaft 122.

  The rotating body 152 is held in a cylindrical holder 112 having both ends opened so as to be rotatable about its axis. The shaft 122 is configured to penetrate the holder 112 and the rotating body 152.

  The rotating body 152 includes a cylindrical portion 154D, a first disc portion 154A, and a second disc portion 154B and a third disc portion 154C having a diameter larger than that of the cylindrical portion 154D.

  One end portion side of the rotating body 152 extends to the outside of the holder 112, and the above-described first disk portion 154A is formed at the extended tip portion. A third disk portion 154 </ b> C is formed at the other tip of the rotating body 152. In addition, the second disk portion 154B and the third disk portion 154C are arranged in the holder 112.

  Concave portions 112B and 112C into which the second disc portion 154B and the third disc portion 154C are fitted are formed at both end portions in the axial direction of the holder 112 corresponding to the second disc portion 154B and the third disc portion 154C. Further, bearings (ball bearings) 153 are provided in the recesses 112B and 112C. With such a configuration, the rotating body 152 rotates around the axis but is restricted from moving in the axial direction.

  As shown in FIGS. 2 and 3A, a plurality of disk-shaped mass bodies 158 are fastened to the first disk portion 154 </ b> A of the rotating body 152 with bolts 159. A circular opening 158A is formed at the center of the mass body 158, and the shaft 122 passes through the opening 158A. Since the inner diameter of the opening 158A is sufficiently larger than the outer diameter of the shaft 122, the opening 158A and the shaft 122 are not in contact with each other. Further, the axis of the rotating body 152 (the first disk portion 154A, the second disk portion 154B, the third disk portion 154C, and the column portion 154D), the axis of the mass body 158, and the axis of the shaft 122 are on the same axis. is there.

  With this configuration, when the shaft 122 moves in the axial direction, the rotary inertia mass damper unit 150 is screwed into the female screw groove 122A on the outer peripheral surface of the shaft 122 and the male screw 152A of the rotary body 152, thereby rotating the rotary body 152. Rotates around the axis, and the mass body 158 fastened by the rotating body 152 and the bolt 159 rotates around the axis (the rotating body 152 and the mass body 158 rotate together).

  That is, the rotary inertia mass damper unit 150 has a mechanism for converting the linear displacement in the axial direction of the shaft 122 into the rotary displacement of the mass body 158 (and the rotary body 152) that is the rotary inertia mass.

  The configuration (structure) of the rotary inertia mass damper portion described here is an example, and is not limited to the present embodiment, and a desired type or characteristic can be arbitrarily adopted. .

  Next, the oil damper portion 180 will be described. Note that the oil damper portion 180 of the present embodiment is a double cylinder type oil damper.

  As shown in FIG. 2, the oil damper portion 180 has a cylindrical portion 184 having a double structure of an inner cylinder 182 and a cylindrical outer cylinder 114 constituting the housing 110. A mounting portion 118 is provided at the other end of the outer cylinder 142.

  A piston rod 124 that constitutes the shaft portion 120 is inserted into an inner cylinder 182 that constitutes the cylinder portion 184. A piston valve 186 is provided at the tip of the piston rod 124. A base valve 188 is provided at the bottom of the inner cylinder 182. The piston valve 186 is formed with an orifice 186A serving as an oil path. The base valve 188 is formed with an orifice 188A serving as an oil path.

  The inner cylinder 182 is filled with oil E. In addition, between the piston rod 124 of the outer cylinder 114, it seals with the oil seal 189 so that the oil E may not leak.

  The oil E filled in the inner cylinder 182 passes through the orifice 188A of the base valve 188 and is guided to the gap between the outer cylinder 114 and the inner cylinder 182. Then, when the piston valve 186 moves in the inner cylinder 182 in the axial direction due to the linear displacement of the piston rod 124 in the axial direction, the damping function is caused by resistance when passing through the orifice 186A of the piston valve 186 and the orifice 188A of the base valve 188. Is demonstrated.

  Basically, the oil E hardly compresses or expands, so the damping force (damping value) exerted by the oil damper portion 180 is determined by the size of the orifice 186A of the piston valve 186 and the orifice 188A of the base valve 188. . That is, if the orifices 186A and 188A are small, the resistance when the piston valve 186 moves is large and the damping force is large, and if the orifices 186A and 188A are large, the resistance is small and the damping force is small.

  Note that the oil damper portion 180 of the present embodiment is provided with a so-called relief mechanism (not shown) that has a relief valve (not shown) to make the pressure peak and the damper load force to reach a relief load.

  Next, the joint 140 will be described.

  In the damping damper 100 of this embodiment, the rotary inertia mass damper portion 150 and the oil damper portion 180 are arranged in series so that the shaft 122 and the piston rod 124 are on the same axis. A joint portion between the rotary inertia mass damper portion 150 and the oil damper portion 180 is a joint portion 140. The joint portion 140 has a cylindrical tube portion 116.

  Here, the cylindrical holder 112 of the rotary inertia mass damper part 150 and the cylindrical outer cylinder 114 of the oil damper part 180 are connected by a cylinder part 116 constituting the casing 110. That is, the housing 110 includes a holder 112, an outer cylinder 114, and a cylinder portion 116.

  In the cylindrical portion 116, the other end portion of the shaft 122 of the rotary inertia mass damper portion 150 and one end portion of the piston rod 124 of the oil damper portion 180 are joined. In this embodiment, a disc-shaped flange 126 is provided at the other end of the shaft 122, a disc-like flange 126 is provided at one end of the piston rod 124, and these flanges 126 are joined together. . That is, the shaft portion 120 is integrated by joining the shaft 122 and the piston rod 124 arranged on the same axis line via the flange 126 provided at the joining portion.

  Thus, the holder 112 of the rotary inertia mass damper portion 150 and the outer cylinder 114 of the oil damper portion 180 are joined by the cylinder portion 116, and the shaft 122 of the rotary inertia mass damper portion 150 and the piston rod of the oil damper portion 180 are joined. The rotational inertia mass damper portion 150 and the oil damper portion 180 are arranged in series and integrated by joining the end portions of 124 via the flange 126.

  In the present embodiment, a plurality of ribs 119 are formed on the inner wall of the cylindrical portion 116 of the joint portion 140 along the axial direction. A plurality of grooves 126A are formed on the outer peripheral surface of the flange 126 along the axial direction with which the rib 119 is engaged. Thus, the shaft portion 120 can move in the axial direction with respect to the housing 110, but is prevented from rotating around the shaft (see FIG. 3B).

  Here, the specifications of the shaft 122 of the rotary inertia mass damper portion 150 and the piston rod 124 of the oil damper portion 180 are set so as to satisfy the following [Equation 1].

The meaning of each symbol in [Equation 1] is described below.
kD _{. M} : rigidity of the shaft of the rotary inertia mass damper part k _C : rigidity of the piston rod of the oil damper part

Further, the rigidity k _D. of the shaft of the rotary inertia mass damper portion _{. M} and the rigidity k _C of the piston rod of the oil damper portion can be obtained by the following [Equation 2] and [Equation 3].

The meaning of each symbol in [Equation 2] and [Equation 3] is described below.
E: Young's modulus A _{D.E. M} : Area of the cross section orthogonal to the axial direction of the shaft of the rotary inertia mass damper portion L _{D. M} : Axial length of the shaft of the rotary inertia mass damper part A _C : Area of a cross section perpendicular to the axial direction of the piston rod of the oil damper part L _C : Axial length of the piston rod of the oil damper part

That is, as shown in [Equation 1], the damping damper 100 of the present embodiment has the rigidity kD.D of the shaft 122 of the rotary inertia mass damper portion 150 _{. M} and the rigidity k _C of the piston rod 124 of the oil damper portion 180 are the same, or the rigidity k of the shaft 122 _{D.D. M} is set to be larger than the rigidity k _C of the piston rod 124.

  Here, the above-mentioned “rigidity” refers to the degree of difficulty in deformation (axial expansion / contraction) with respect to the axial direction.

  In addition, the shaft of the rotary inertia mass damper portion in the above formulas ([Expression 1] to [Expression 3]) is the D.D. Refers to the M part. That is, the shaft 122 portion that does not include the attachment portion 128 and the flange 126 is indicated.

  Further, the piston rod of the oil damper portion refers to a portion C in FIG. That is, the piston rod 124 portion that does not include the piston valve 186 and the flange 126 is indicated.

  Next, the operation and effect of this embodiment will be described.

  As shown in FIG. 4A, in the vibration control device, when the structure 10 moves horizontally to the left side due to vibration (disturbance) such as seismic motion, the frame 24 is horizontally deformed (deformed into a parallelogram) leftward. . That is, the upper beam 22A moves horizontally to the left (the upper beam 22A and the lower beam 22B move relative to each other).

  Therefore, in the frame 24, the distance between the attachment portion 30 and the attachment portion 40L is increased, and the distance between the attachment portion 30 and the attachment portion 40L is shortened. Thus, due to the change in the distance between the attachment portion 30 and the attachment portions 40L and 40R, the overall length of the vibration control damper 100L is expanded, and the total length of the vibration control damper 100R is contracted.

  As shown in FIG. 4B, when the structure 10 moves horizontally to the right, the frame 24 is horizontally deformed (deformed into a parallelogram) to the right. That is, the upper beam 22A moves horizontally to the right (the upper beam 22A and the lower beam 22B move relative to each other).

  Therefore, in the frame 24, the distance between the attachment portion 30 and the attachment portion 40L is shortened, and the distance between the attachment portion 30 and the attachment portion 40R is increased. Thus, due to the change in the distance between the attachment portion 30 and the attachment portions 40L and 40R, the overall length of the damping damper 100R contracts, and the overall length of the damping damper 100L extends.

  That is, when the frame 24 vibrates left and right due to a disturbance (vibration) such as an earthquake, the distance between the attachment portion 30 and the attachment portions 40R and 40L changes, and the overall lengths of the damping dampers 100L and 100R expand and contract.

  By the expansion and contraction (change in the total length) of the damping damper 100, the rotating body 152 of the rotary inertia mass damper portion 150 rotates around the axis, and the mass body 158 integrated with the rotating body 152 rotates around the axis (rotating body). 152 and the mass body 158 rotate together. As a result, inertial mass is generated, so that a force opposite to the linear displacement is generated, and input due to disturbance is reduced.

  Further, the oil damper portion 180 generates a damping force against the linear displacement of the shaft portion 120 in the axial direction.

  That is, the seismic damper 100 according to this embodiment is a damper having the effect of “rotational inertia mass (M) + viscosity (C)”, and exhibits a seismic control effect.

  Here, as shown in FIG. 2, in the vibration damper 100 according to the present embodiment, the rotary inertia mass damper portion 150 and the oil damper portion 180 are arranged in series on the same axis. FIG. 6A shows a model of this. However, as an analysis model, as shown in FIG. 6B, the model is equivalent to a configuration in which a rotary inertia mass damper portion 150 and an oil damper portion 180 are arranged in parallel. That is, similarly to the configuration in which the rotary inertia mass damper portion 150 and the oil damper portion 180 are arranged in parallel, the axial vibration of the shaft 122 of the rotary inertia mass damper portion 150 is attenuated by the damping force of the oil damper portion 180. .

In addition, when [Equation 1] is not satisfied, the rigidity k of the shaft 122 of the rotary inertia mass damper portion 150 is obtained _{. M} and the rigidity k _C of the piston rod 124 of the oil damper portion 180 are the same, or the rigidity k of the shaft 122 of the rotary inertia mass damper portion 150 _D.D. If so towards the _M increases not set each parameter, i.e. the stiffness k _D. of shaft 122 of the rotary inertial mass damper 150 _When the rigidity k _C of the piston rod 124 of the oil damper portion 180 is larger than _M , the oil damper portion 180 does not exhibit a damping effect, or even if it exhibits a damping effect, the effect is limited (sufficiently) Does not exert a significant damping effect).

  This is because the shaft 122 of the rotary inertia mass damper portion 150 is deformed, and the piston rod 124 of the oil damper portion 180 cannot be moved in the axial direction, or even if it moves, the operation amount is small.

Therefore, as in this embodiment, the rigidity k of the shaft 122 of the rotary inertia mass damper portion 150 is satisfied so as to satisfy [Equation 1] _. By setting each specification so that the rigidity k _C of the piston rod 124 of the oil damper portion 180 is larger than that of _M, the shaft 122 of the rotary inertia mass damper portion 150 is not deformed, and the oil damper is reliably The piston rod 124 of the part 180 can be moved in the axial direction. That is, the axial vibration of the shaft 122 of the rotary inertia mass damper portion 150 can be attenuated by the damping force of the oil damper portion 180.

  Thus, even if the rotary inertia mass damper portion 150 and the oil damper portion 180 are arranged in series, by setting each specification so as to have the relationship of [Equation 1], the rotary inertia mass damper portion 150 and the The oil damper portion 180 can be handled as a configuration arranged in parallel, that is, similar to the configuration in which the rotary inertia mass damper portion 150 and the oil damper portion 180 are arranged in parallel, the shaft 122 of the rotary inertia mass damper portion 150 Axial vibration can be attenuated.

  Here, FIG. 7A is a graph for explaining the relationship between the axial movement speed of the shaft portion 120 and the axial resistance value in the vibration damper 100 of the present embodiment to which the present invention is applied. is there. FIG. 7 (B) shows a shaft portion of a damping damper having a configuration in which a rotational resistance is applied to the shaft portion directly or via a rotating body with a viscous body or a viscous fluid to which the present invention is not applied. It is a graph which shows the relationship between the moving speed of an axial direction, and the resistance value of an axial direction.

  As shown in FIG. 7B, the damping damper having a configuration in which a rotational resistance is applied to the shaft portion directly or via a rotating body or the like with a viscous body or a viscous fluid has an axial movement speed (vibration speed). ) Becomes faster, the frictional resistance decreases, and the axial resistance decreases.

  On the other hand, as shown in FIG. 7 (A), the damping damper 100 to which the present invention is applied has an axial resistance force that increases in accordance with the moving speed (vibration speed) in the axial direction (linear or Almost linear).

  Therefore, the vibration damping damper 100 of the present embodiment has an axial movement of the shaft portion 120 as compared with a configuration in which a rotational resistance is applied to the shaft portion directly or via a rotating body with a viscous body or a viscous fluid. It is prevented or suppressed that the axial resistance force decreases as the speed (vibration speed) increases. Therefore, the damping damper 100 of the present embodiment has a speed (vibration speed) of the shaft portion 120 as compared with a configuration in which a rotational resistance is applied to the shaft portion directly or via a rotating body with a viscous body or a viscous fluid. High vibration control effect can be obtained even if) is faster.

  Also, since a relief valve is provided with a function that causes the pressure to reach a peak with a relief valve, the so-called relief mechanism is provided, so that the axial resistance force exceeds a predetermined value (point P or more in the figure). It is prevented.

  In addition, it is extremely difficult to provide such a relief mechanism in a vibration control damper that is configured to give rotational resistance around the shaft directly or via a rotating body with a viscous body or viscous fluid. It is said that.

  Moreover, the damping damper 100 of this embodiment can be easily configured by arranging and connecting a rotary inertia mass damper in series to an existing oil damper.

  Further, since the plurality of ribs 119 formed on the inner wall of the cylindrical portion 116 of the joining portion 140 are engaged with the plurality of grooves 126A formed on the outer peripheral surface of the flange 126, the shaft portion 120 is in contact with the housing 110. Although it can move in the axial direction, it can be prevented from rotating around the axis (see FIG. 3B). Therefore, twisting of the shaft portion 120 due to rotation of the rotating body 152 or the like is prevented.

  Now, the shaft of the rotary inertia mass damper portion in the above formulas ([Equation 1] to [Equation 3]) is the D. of FIG. The portion M is indicated, and the shaft 122 portion not including the attachment portion 128 and the flange 126 is indicated. Further, the piston rod of the oil damper portion refers to a portion C in FIG. 2, and refers to a piston rod 124 portion that does not include the piston valve 186 and the flange 126.

However, to be precise, the mounting portion 128, the flange 126, and the piston valve 186 are also provided with the rigidity k _D. of the shaft of the rotary inertia mass damper portion _{. M} (rigidity K1) and the rigidity k _C (rigidity K2) of the piston rod of the oil damper portion are affected. However, in the case of this embodiment, even if it is approximately calculated by the above mathematical formulas ([Formula 1] to [Formula 3]), no significant problem occurs. However, in the case of designing more accurately, the rigidity k _{D.D including the} mounting portion 128, the flange 126, and the piston valve 186 is included. _M it is desirable to determine by calculating (stiffness K1) and the piston rod stiffness _{k C} (stiffness K2).

  Also, when the shaft diameter or cross-sectional shape of the shaft differs in the axial direction (for example, a shaft that gradually becomes thicker from one side to the other or a shaft that has a circular cross-section on one side and a square cross-section on the other side (a cylinder and The shape in which the prisms are connected))) and the like are also determined by the calculation formulas other than the above formulas ([Formula 1] to [Formula 3]).

  In short, the rigidity K1 of the first shaft portion in the rotation inertia mass generating portion where the rotation inertia mass is generated is equal to or greater than the rigidity K2 of the second shaft portion in the attenuation portion that attenuates by applying a resistance force in the axial direction. It only has to be set.

<Second embodiment>
Next, the damping damper 200 of the second embodiment will be described. In addition, the same code | symbol is attached | subjected to the member similar to 1st embodiment, and the overlapping description is abbreviate | omitted.

  As shown in FIG. 5, the damping damper 200 is inserted into a cylindrical casing 210 so that the shaft portion 220 is movable in the axial direction.

  An attachment portion 128 is provided at one end portion of the shaft portion 220 (one end portion of a piston rod 224, which will be described later), and rotates to the attachment portion 40 (see FIG. 1) attached to the corner portion between the upper beam 22A and the column 20. An attachment portion 30 (FIG. 1) is attached so that the attachment portion 118 is connected to the other end portion of the casing 210 (the other end portion of the holder 212 to be described later) and attached to a substantially central portion in the left-right direction of the lower beam 22B. Reference) is rotatably connected.

  The damping damper 200 has a rotary inertia mass damper portion 250 and an oil damper portion 280, and these are joined in series. Further, a part where the rotary inertia mass damper part 250 and the oil damper part 280 are joined is a joint part 240.

  The rotary inertia mass damper portion 250 is substantially the same as the rotary inertia mass damper portion 150 of the first embodiment. The rotary inertia mass damper portion 250 includes a rotating body 152, a holder 212 that constitutes the casing 210, and a shaft 222 that constitutes the shaft portion 220.

  A female screw groove 222 </ b> A is formed on the outer peripheral surface of the shaft 222. The female screw groove 222A is inserted into a cylindrical rotating body 152 formed on the inner peripheral surface of a male screw 152A that is screwed into the female screw groove 222A. The rotator 152 is held inside the two cylindrical holders 212 so as to be rotatable about its axis. Further, the shaft 222 passes through the rotating body 152.

  When the shaft 222 moves in the axial direction in the same manner as the rotary inertia mass damper portion 250 of the first embodiment, the rotary inertia mass damper portion 250 includes the female screw groove 222A on the outer peripheral surface of the shaft 222 and the male screw 152A of the rotating body 152. And the rotating body 152 rotates around the axis, and the mass body 158 fastened by the rotating body 152 and the bolt 159 rotates around the axis (the rotating body 152 and the mass body 158 are integrated with each other). Rotate).

  That is, the rotary inertia mass damper unit 250 has a mechanism for converting the linear displacement in the axial direction of the shaft 222 into the rotary displacement of the mass body 158 (and the rotary body 152) that is the rotary inertia mass.

  Note that the holder 212 is configured such that a part thereof bulges outward in accordance with the mass body 158.

  In the present embodiment, the other end of the shaft 222 is disposed in the space 252 on the other end of the holder 212. The other end portion of the shaft 222 moves in the axial direction in the space 252. The mounting portion 118 described above is provided outside the other end of the space 252, that is, on the other end of the holder 212.

  As in the first embodiment, the configuration (structure) of the rotary inertia mass damper portion 250 is an example, and is not limited to the present embodiment, and arbitrarily adopts a desired type and characteristics. can do.

  Next, the oil damper portion 280 will be described. Note that the oil damper portion 280 of the present embodiment is a PSA-P (viscous damping device) type oil damper.

  The oil damper portion 280 has a cylindrical outer cylinder 214 that constitutes the casing 210. A piston rod 224 is inserted into the outer cylinder 214, and a piston valve 282 is provided on the piston rod 224. A mounting portion 128 is provided at one end of the piston rod 224.

  An oil seal 288 is sealed between the opening of the outer cylinder 214 and the piston rod 224 so that the oil E does not leak.

  A communication tube (narrow tube) 284 configured to communicate between both end portions on the outer peripheral surface is provided on the outer side of the outer cylinder 214. A buffer 286 is provided on the outer peripheral surface of one end of the outer cylinder 214. Then, as the piston rod 224 moves in the axial direction, the piston valve 282 moves, whereby oil E flows through the communication pipe 284. A damping resistance is exhibited by the viscous resistance force of the oil E flowing through the communication pipe 284.

  Next, the joint portion 240 will be described.

  In the damping damper 200 of this embodiment, the rotary inertia mass damper portion 250 and the oil damper portion 280 are arranged in series so that the shaft 222 and the piston rod 224 are on the same axis. A joint portion between the rotary inertia mass damper portion 250 and the oil damper portion 280 is a joint portion 240. The joint portion 140 has a cylindrical tube portion 116 that constitutes the housing 210.

  A cylindrical holder 212 of the rotary inertia mass damper portion 250 and a cylindrical outer cylinder 214 of the oil damper portion 280 are connected to the cylindrical portion 116 constituting the casing 210. That is, the housing 210 includes a holder 212, an outer cylinder 214, and a cylinder portion 116.

  In the cylindrical portion 116, one end portion of the shaft 222 of the rotary inertia mass damper portion 250 and the other end portion of the piston rod 224 of the oil damper portion 280 are joined. Also in this embodiment, a disc-shaped flange 126 is provided at one end of the shaft 222, and a disc-shaped flange 126 is provided at the other end of the piston rod 224, and these flanges 126 are joined together. Yes. That is, the shaft portion 120 is integrated by joining the shaft 222 and the piston rod 224 arranged on the same axis via the flange 126 provided at the joining portion.

  Thus, the holder 212 of the rotary inertia mass damper portion 250 and the outer cylinder 214 of the oil damper portion 280 are joined by the cylinder portion 116, and the shaft 222 of the rotary inertia mass damper portion 250 and the piston rod of the oil damper portion 280 are joined. Since the end portions of 224 are joined to each other via the flange 126, the rotary inertia mass damper portion 250 and the oil damper portion 280 are arranged in series and integrated.

  Also in this embodiment, a plurality of ribs 119 are formed on the inner wall of the cylindrical portion 116 along the axial direction, and a plurality of grooves are formed on the outer peripheral surface of the flange 126 along the axial direction with which the ribs 119 are engaged. 126A is formed. Thus, the shaft portion 120 can move in the axial direction with respect to the housing 110, but is prevented from rotating around the shaft (see FIG. 3B).

  Also in this embodiment, the shaft 222 of the rotary inertia mass damper portion 250 and the piston rod 224 of the oil damper portion 280 have the relationship of [Equation 1] (to Equation 3) described in the first embodiment. Each specification is set as follows.

That is, the damping damper 200 of the present embodiment has the rigidity kD.D of the shaft 222 of the rotary inertia mass damper portion 250 _{. M} and the rigidity k _C of the piston rod 224 of the oil damper portion 280 are the same, or the rigidity k of the shaft 222 of the rotary inertia mass damper portion 250 _D.D. Each item is set so that _M is larger.

  Note that the shaft of the rotary inertia mass damper part is the D. of FIG. Refers to the M part. That is, it indicates the portion of the shaft 222 that does not include the flange 126. Further, the piston rod of the oil damper portion refers to a portion C in FIG. That is, it refers to the piston rod 224 portion that does not include the attachment portion 128, the flange 126, and the piston valve 282. In other words, the C1 portion that does not include the attachment portion 128 and the piston valve 282 and the C2 portion that does not include the piston valve 282 and the flange 126 are C portions.

  Next, the operation of the vibration control damper 200 of this embodiment will be described.

  Similar to the first embodiment, due to the expansion and contraction (change in the total length) of the damping damper 200, the rotating body 152 of the rotary inertia mass damper portion 250 rotates around the axis, and the mass body 158 integrated with the rotating body 152 has the shaft. Rotating around (rotating body 152 and mass body 158 rotate together). As a result, inertial mass is generated, so that a force opposite to the linear displacement is generated, and input due to disturbance is reduced.

  Further, the oil damper portion 280 generates a damping force against the linear displacement of the shaft portion 220.

  That is, the damping damper 200 of the present embodiment is a damper having the effect of “rotational inertia mass (M) + viscosity (C)”, and exhibits a damping effect.

  Here, in the damping damper 200 of the present embodiment, the rotary inertia mass damper portion 250 and the oil damper portion 280 are arranged in series on the same axis (see FIG. 6B). However, as in the first embodiment, the numerical analysis model is the same model as the configuration in which the rotary inertia mass damper portion 250 and the oil damper portion 280 are arranged in parallel (see FIG. 6C). That is, similarly to the configuration in which the rotary inertia mass damper portion 250 and the oil damper portion 280 are arranged in parallel, the axial vibration of the shaft 222 of the rotary inertia mass damper portion 250 is attenuated by the damping force of the oil damper portion 280. be able to.

Also in the present embodiment, the rigidity kD _{. Of} the shaft 222 of the rotary inertia mass damper portion 250 is satisfied so as to satisfy [Equation 1] _{. M} and the rigidity k _C of the piston rod 224 of the oil damper portion 280 are the same, or the rigidity k of the shaft 222 of the rotary inertia mass damper portion 250 _{D.D. Since} each specification is set so that _M is larger, the oil damper portion 280 exhibits a damping effect.

  In addition, as in the first embodiment, the axial movement speed of the shaft portion 220 (compared to a configuration in which a rotational resistance is provided around the shaft directly or via a rotating body or the like with a viscous body or a viscous fluid) As the vibration speed increases, the axial resistance is prevented or suppressed from decreasing. Therefore, even if the speed (vibration speed) of the shaft portion 220 is increased, a high vibration control effect can be obtained.

  Moreover, the damping damper 200 of this embodiment can also be easily configured by arranging and connecting a rotary inertia mass damper in series to an existing oil damper, as in the first embodiment.

  Further, since the plurality of grooves 126A formed on the outer peripheral surface of the flange 126 are engaged with the plurality of ribs 119 formed on the inner wall of the cylindrical portion 116 of the joint portion 240, the shaft portion 220 is in contact with the housing 210. It is possible to move in the axial direction, but rotation around the axis is prevented. Therefore, twisting of the shaft portion 220 due to rotation of the rotating body 152 or the like is prevented.

<Modification>
In the above embodiment, even if the rotational inertial mass generation unit (rotational inertial mass damper unit) and the attenuation unit (oil damper unit) are arranged in series, the analysis model includes the rotational inertial mass generation unit and the attenuation unit, The seismic damper was equivalent to the configuration arranged in parallel (see Fig. 6).

  However, as shown in the analysis model diagram of FIG. 8, the analysis model includes a configuration in which the rotary inertia mass generation unit and the damping unit are arranged in parallel (the damping dampers 100 and 200 in the above embodiment), and further a spring. (Spring element) It is good also as a damping device of the structure which has arrange | positioned 300 in series.

  In this way, a system in which a rotary inertia mass generating unit that converts axial linear displacement into rotational motion of a mass body and a damping unit that generates damping resistance force are connected in parallel, and a spring element that generates elastic reaction force, Is connected to the first part and the second part, so that the vibration system composed of the rotary inertia mass and the spring element vibrates in a coupled manner. The damping parts connected in parallel absorb vibration energy.

  Further, in the vibration damping device (see FIG. 8) in which the springs 300 are arranged in series in this way, the natural frequency determined by the rotary inertia mass and the spring 300 is tuned or substantially tuned to the natural frequency of the structure 10. Thus, the rotational inertial mass can be increased as compared with the configuration in which the springs 300 are not arranged in series.

  Further, by arranging the springs (spring elements) 300 in series, the maximum value of the resistance force in the axial direction can be controlled (restricted). In other words, it has substantially the same function as a configuration including a relief mechanism that prevents the axial resistance force from exceeding a predetermined value (for example, the point P or more in FIG. 7A) without using a relief valve. be able to.

  Next, an example of an arrangement position where the springs 300 are arranged in series will be described with reference to FIGS. 9A and 9B.

  As shown in FIG. 9 (A) and FIG. 9 (B), the housing 110 of the vibration control damper 100 of the first embodiment or the housing 210 of the vibration control damper 200 of the second embodiment, the mounting portion 30, The spring 300 may be arranged at the arrangement position B1 between the two.

  Alternatively, the arrangement position B2 between the attachment portion 128 of the shaft 122 of the vibration damping damper 100 of the first embodiment or the attachment portion 128 of the shaft 224 of the vibration damping damper 200 of the second embodiment and the attachment portions 40R and 40L. The spring 300 may be disposed on the front side.

  Further, the casing 110 of the damping damper 100 of the first embodiment or the casing 210 of the damping damper 200 of the second embodiment and the mounting portion 30 are connected by a connecting member having the same function as the spring element. May be. Similarly, the attachment part 128 of the shaft 122 of the vibration damping damper 100 of the first embodiment or the attachment part 128 of the shaft 224 of the vibration damping damper 200 of the second embodiment and the attachment parts 40R and 40L are the same as the spring elements. You may connect with the connection member which has the function of.

  In the present embodiment, the vibration dampers 100 and 200 configured in a V-shaped brace are provided, but the present invention is not limited to this. For example, you may provide the damping damper 100,200 to which this invention was applied to K type brace. In other words, the mounting portion 30 may be provided on the upper beam 22A, and the mounting portions 40R and 40L may be disposed at the lower corner portion of the frame 24 and attached to the lower beam 22B and the columns 20R and 20L.

  Even when applied to such a K-type brace, the housing 110 of the vibration damping damper 100 of the first embodiment or the housing 210 of the vibration damping damper 200 of the second embodiment, the mounting portion provided on the frame, A spring 300 may be provided between them, or a connection member having the same function as the spring element may be connected between them. Similarly, between the attachment part 128 of the shaft 122 of the vibration damping damper 100 of the first embodiment or the attachment part 128 of the shaft 224 of the vibration damping damper 200 of the second embodiment, and the attachment part provided on the frame. The spring 300 may be provided, or may be connected by a connecting member having the same function as the spring element.

  Furthermore, you may provide the damping damper 100,200 to which this invention was applied to the toggle damping device which has a toggle mechanism.

  For example, as shown in FIG. 10, the toggle vibration control devices 500R and 500L are supported by the first arm 538R and 538L, one end of which is rotatably supported by the mounting portion 30, and one end of which is rotatably supported by the mounting portions 40R and 40L. Second arms 542R and 542L. The other ends of the first arms 538R and 538L and the second arms 542R and 542L are connected to the attachment portions 128R and 128L of the vibration dampers 100R and 100L so as to be rotatable at a predetermined angle. Further, the mounting portions 118R and 118L of the vibration dampers 100R and 100L are disposed at the lower corners of the frame 24 and are rotatably connected to mounting portions 510R and 510L mounted on the lower beam 22B and the columns 20R and 20L.

  In such toggle vibration control devices 500R and 500L, the first arms 538R and 538L and the second arms 542R and 542L can function as spring elements.

  In addition, in FIG. 10, although the damping damper 100 of 1st embodiment was applied, you may use the damping damper 200 of 2nd embodiment.

  Further, the configuration of the toggle mechanism may be a configuration other than the configuration shown in FIG.

  For example, in FIG. 10, the corners formed by the first arm 538 and the second arm 542 are configured to have a convex shape upward. However, the corner portion formed by the first arm 538 and the second arm 542 may be configured to be convex downward.

  Further, for example, one end of the first arm 538 and one end of the second arm 542 may be connected to one corner and the other corner on the diagonal line of the frame.

<Others>
The present invention is not limited to the above embodiment.

  In the above embodiment, the oil dampers 180 and 280 are double cylinder type oil dampers or PSA-P (viscous damping device) type oil dampers, but the present invention is not limited to this. A single cylinder type oil damper may be used. Or the oil damper of another structure may be sufficient.

  Furthermore, the attenuation part may be constituted by other than the oil damper. Other types of dampers, for example, elastoplastic dampers can be used. Further, for example, it may be composed of a viscous damper, a friction damper, a viscoelastic damper, or the like.

  In addition, in the structure which arrange | positioned the attenuation | damping part in series, you may give rotational resistance to an axis | shaft around a shaft directly or via a rotary body etc. with a viscous body, viscous fluid, etc. further.

  Moreover, in the said embodiment, although the shafts 122 and 222 and the piston rods 124 and 224 were joined via the flange 126, it is not limited to this. The ends of the shafts 122 and 222 and the piston rods 124 and 224 may be joined directly. Or you may form 122 A of female screw grooves in the one side of one axial part instead of the structure which connected the several axial part. That is, a configuration in which one side of one shaft portion is the first shaft portion and the other side is the second shaft portion may be employed.

  Moreover, in the said embodiment, although the rib 119 was formed in the inner wall face of the cylinder part 116 and the groove | channel 126A was formed in the outer peripheral surface of the flange 126, it is not limited to this. A groove may be formed on the inner wall surface of the cylindrical portion 116, and a rib may be formed on the outer peripheral surface of the flange 126. Or the structure which provided the guide shaft which penetrates the flange 126 in a cylinder part may be sufficient. In short, any mechanism that prevents the shafts 120 and 220 from rotating around the axis may be used. Note that a guide mechanism for preventing the shafts 120 and 220 from rotating about the axis is not necessarily required (a damper or a vibration control device having no such guide mechanism may be used).

  In the above-described embodiment, the mounting portion 128 is connected to the mounting portions 128 provided on the shaft portions 120 and 220 of the vibration control dampers 100 and 200, and the housings 110 and 210 of the vibration control dampers 100 and 200 are connected to the mounting portion 30. However, the present invention is not limited to this. It may be connected via another member, for example, an arm. Alternatively, as described above, they may be connected via a spring or other vibration control device.

  Further, if there is no restriction in the vertical arrangement of the oil damper or the like, the shaft portion side of the damping damper may be connected to the mounting portion 40 and the housing side of the damping damper may be connected to the mounting portion 30. In short, how to control the structure by installing a damping damper between the first part and the second part where the structure moves relative to each other due to a disturbance such as an earthquake, so that the damping effect can be obtained. A damper may be arranged.

  Moreover, in the said embodiment, although this invention was applied to the damping damper mainly used for the purpose of damping a structure, it is not limited to this. The present invention can also be applied to a damper used for purposes other than vibration control.

  Furthermore, it cannot be overemphasized that it can implement with a various aspect in the range which does not deviate from the summary of this invention.

  In the present specification, the descriptions of one and the other are relative, and either one may be the other.

10 Structure 30 Mounting part (second part)
40L mounting part (first part)
40R mounting part (first part)
100 Damping damper (damper, damping device)
110 Housing 119 Rib (Guide means)
120 shaft 122 shaft (first shaft)
122A Female thread groove (screwing means)
124 piston rod (second shaft)
126 Flange (guide means)
126A groove (guide means)
150 Rotating inertia mass damper part (Rotating inertia mass generating part)
152 Rotating body 152A Male thread (screwing means)
158 Mass body 180 Oil damper part (attenuation part)
200 Damping damper (damper, damping device)
210 Housing 220 Shaft 222 Shaft (first shaft)
222A Female thread groove (screwing means)
224 Piston rod (second shaft)
250 Rotational inertial mass damper (rotational inertial mass generator)
280 Oil damper (damping part)
300 Spring (spring element)
500 Toggle control device (Control device)
538 First arm (spring element)
542 Second arm (spring element)

Claims (5)

A shaft portion having a first shaft portion and a second shaft portion;
A housing in which the shaft portion is movably inserted in the axial direction;
A rotational inertial mass generating unit that is provided in the housing and generates a rotational inertial mass by converting an axial linear displacement of the first shaft portion relative to the housing into a rotation of a mass body;
An attenuating portion that is provided in the housing and attenuates an axial linear displacement of the second shaft portion relative to the housing by applying an axial resistance force to the second shaft portion;
And
The rigidity K1 of the first shaft portion and the rigidity K2 of the second shaft portion are:
K1 ≧ K2
Damper set to. The rotating mass generator is
A rotating body penetrating through the first shaft portion and rotatably held in the housing;
A screwing means that is provided on the outer peripheral surface of the first shaft portion and the inner peripheral surface of the rotating body, and converts linear displacement in the axial direction of the shaft portion into rotation around the axis of the rotating body;
The mass body that rotates integrally with the rotating body around an axis;
The damper according to claim 1, comprising:   3. The damper according to claim 1, further comprising a guide unit that is provided in the housing and guides linear displacement of the shaft portion and prevents rotation of the shaft portion around an axis. 4. The damper according to any one of claims 1 to 3 is provided between the first part and the second part of the structure that is relatively moved by a disturbance,
The vibration control device in which the shaft portion of the damper is directly or indirectly connected to the first portion, and the casing of the damper is directly or indirectly connected to the second portion.   The vibration control device according to claim 4, further comprising a spring element arranged in series with respect to the damper.