JP2015137656A - Vibration control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration control device having an improved structure of which vibration control effect is further improved on the basis of a vibration control device of cantilever type conventional structure.SOLUTION: This invention relates to a vibration control device 10 in which one side of a longitudinal plate-like spring member 14 is applied as a base part 28 fixed to a vibrator body 12, the other side of the spring member 14 is applied as a mass fixing part 30, a mass member 16 is fixed to the mass fixing part 30 and at the same time there is provided an attenuation body 18 protruded from the mass fixing part 30 and abutted against the vibrator body 12. These elements have the conditions expressed in the following equation. Namely, 2≤W/(X+H/2)≤60.8≤H/X≤2.5 where, W=width size of the mass member 16, X=height size from a fixing surface of the mass member 16 to the abutting surface of the attenuation body 18 against the vibrator body 12, H=height size of the mass member 16.

Description

  The present invention relates to a vibration damping device that is attached to, for example, a floor of a building and used to reduce sound and vibration associated with an impact.

  Conventionally, a floor impact sound or the like may be a problem in a building such as a house. In particular, in multi-storey apartments, sound and vibration due to impact input to the floor due to walking or jumping on the upper floor are likely to be propagated to the ceiling below the floor, which may cause discomfort to the residents below the floor. there were.

  Therefore, as a means for reducing the impact sound of the floor, for example, it has been proposed to attach a vibration damping device to the back surface of the floor. For example, as described in Japanese Patent Application Laid-Open No. 2010-230031 (Patent Document 1), the vibration damping device is attached to a vibrating body such as a floor while one end side of a spring member having a longitudinal plate shape is provided. It is a cantilever-like structure in which a mass member is attached to the other end side.

  Then, the resonance frequency of the vibration damping device is tuned so as to match the vibration frequency of the floor to be damped. As a result, when an impact force such as walking or jumping is exerted on the floor, the vibration energy of the floor is converted into the vibration energy of the vibration damping device, and the vibration damping effect is exhibited, and the impact sound is reduced. .

  However, as a result of studies by the present inventor, it has been found that there is a case where it is difficult to obtain a satisfactory vibration damping effect even when tuning that matches the resonance frequency of the vibration damping device with the vibration frequency of the floor is performed with high accuracy.

JP 2010-230031 A

  The present invention has been made in the background of the above-described circumstances, and the problem to be solved is that in the vibration damping device having a conventional structure having a cantilever shape as shown in Patent Document 1, the vibration damping effect thereof. It is an object of the present invention to provide a vibration damping device having an improved structure and improved.

  Hereinafter, the aspect of this invention made | formed in order to solve such a subject is described. In addition, the component employ | adopted in each aspect as described below is employable by arbitrary combinations as much as possible.

  First, in view of the problems in the vibration damping device having the conventional structure as described above, the present inventors have conducted many experiments and examinations. As a result, when the vibration damping device is mounted on the conventional structure, the floor material is originally damped. It has been understood that the vibration state may deteriorate in a frequency range different from the power vibration, and this is one of the main reasons why it is difficult to stably obtain a sufficient damping effect. And it came to the knowledge that such a deterioration of a vibration state originates in the vibration suppression apparatus producing the vibration of another mode different from the vibration which should be controlled.

  That is, generally, since the vibration of the flooring of the building has a vertical vertical vibration mode, the spring member of the vibration damping device is horizontally oriented from the base fixed to the flooring toward the mass mounting part at the tip. It is attached so as to extend. At that time, the spring member having a long plate shape is attached in a state in which the plate surface extends in the horizontal direction so that the plate thickness direction to be bent is the vertical direction. However, the input position of the vibration load to the flooring is not fixed, and when the load input position deviates from the center between the support points, the vibration displacement direction is inclined from the vertical vertical direction. In addition, since flooring spreads horizontally in two dimensions and is supported around it, vertical vibrations in multiple directions do not overlap to create a simple vertical vibration mode, but a vibration mode inclined from the vertical vertical direction. It turned out that it is easy to produce.

  When the vibration in the inclined direction is applied from the floor material to the vibration damping device, not only simple vibration deformation in the bending direction but also vibration deformation in the torsional direction is caused to the spring member. . Since the spring member has vibration characteristics such as a natural frequency different from the original bending direction in the torsion direction, vibration may be amplified by a resonance action in the torsion direction in the vibration damping device. There was a possibility that the vibration state of the flooring material would be deteriorated by becoming an excitation source for the flooring material.

Here, in the first aspect of the present invention, one side of the elongated spring-shaped spring member is a base fixed to the vibrating body, while the other side of the spring member is a mass mounting portion, In the vibration damping device in which a mass member is fixed to the mass attachment portion and a damping body that protrudes from the mass attachment portion and comes into contact with the vibrating body is provided, the following (Equation 1) and ( It is characterized in that all of the conditions shown in Equation 2) are provided.
2 ≦ W / (X + H / 2) ≦ 6 (Formula 1)
0.8 ≦ H / X ≦ 2.5 (Formula 2)
However, W is the width dimension of the mass member, X is the height dimension from the mounting surface of the mass member to the contact surface of the damping body to the vibrating body, and H is the height dimension of the mass member.

  In the vibration damping device having the structure according to the first aspect, by satisfying the above (Equation 1), the width dimension which is the dimension of the mass member in the direction orthogonal to the elastic central axis of the spring member is vibrated. The height of the center of gravity of the mass member with respect to the support point of the damping body that is in contact with the body as a reference position is appropriately set in consideration of the reference value, and the torsional vibration of the spring member accompanying the oscillation of the mass member is set. Can be suppressed. That is, if the width dimension W of the mass member is set to be smaller than 2 with respect to the height dimension (X + H / 2) of the center of gravity of the mass member, the height dimension of the mass member itself becomes too large compared to the width dimension. Therefore, it tends to cause torsional vibration of the spring member due to easy rolling in the width direction. On the other hand, if the width dimension W of the mass member is set to be greater than 6 with respect to the height dimension (X + H / 2) of the center of gravity of the mass member, the width dimension of the mass member itself becomes too large compared to the height dimension. Therefore, the torsional vibration of the spring member tends not to be settled and tends to increase due to an increase in the inertial force when the lateral roll occurs. In addition, if it deviates from the range of 2 ≦ W / (X + H / 2) ≦ 6, the mass member becomes too large in the height direction compared to the width direction, or conversely in the width direction compared to the height direction. There is also a problem that the space for disposing the mass member becomes inefficient because it becomes too large.

  Further, by satisfying the above (Formula 2), the height dimension (H) of the mass member itself relative to the height dimension (X) from the reference position to the mounting surface of the mass member can be appropriately set. In combination with Equation (1), the torsional vibration of the spring member accompanying the rocking of the mass member can be more effectively suppressed. Note that the height dimension (X) from the reference position to the mounting surface of the mass member can be understood as substantially representing the height dimension of the attenuation body. That is, when the value of H / X is smaller than 0.8, the height of the damping body becomes too large compared to the size of the mass member, and it is difficult to obtain a damping effect by the damping body against the torsional vibration of the spring member. As a result, the torsional vibration of the spring member may increase. On the other hand, when the value of H / X is larger than 2.5, the height dimension of the mass member becomes too large compared to the size of the attenuation body, and the swinging shape of the mass member located below the attenuation body is increased. There is a possibility that torsional vibration of the spring member may increase due to the fact that a sufficient damping force against swinging is difficult to be exhibited.

  Therefore, by satisfying the conditions of (Equation 1) and (Equation 2) together, torsional deformation in the long plate spring member is suppressed, and as a result, the peak of the torsional vibration mode in the vibration damping device is obtained. It can be suppressed. As a result, a problem that the vibration state of the vibrating body is reduced due to an unintended torsional mode vibration amplification action can be effectively suppressed, and the vibration device is originally intended to bend in the bending direction of the spring member. By virtue of the vibration damping effect against the vertical vibration, good vibration damping performance for the vibration member is exhibited.

In this embodiment, it is more preferably set so as to satisfy the following expression.
1 ≦ W / (X + H) ≦ 5

  A second aspect of the present invention is the vibration damping device according to the first aspect, wherein a plurality of reinforcing ribs protruding in the height direction and extending in the longitudinal direction are separated from each other in the width direction in the spring member. In addition, the height dimension of the reinforcing rib is smaller in the mass attaching portion than in the base portion.

  According to the second aspect, for example, the spring rigidity in the torsional direction can be effectively increased by the reinforcing rib protruding in the height direction as compared with a spring member having a flat plate shape or the like. Therefore, problems caused by torsional mode vibration in the damping device can be achieved by suppressing the amount of torsional deformation of the spring member or by tuning the natural frequency in the torsional direction of the damping device to a high frequency range that does not matter. Can be more effectively prevented.

  In particular, the height of the reinforcing rib on the base side on which a large bending moment acts when the torsional vibration is generated with the swing of the mass member mounted on the mass mounting portion located on the distal end side of the spring member from the distal end side. As a result, the torsional vibration can be efficiently suppressed without unnecessarily increasing the size of the reinforcing rib. In addition, by suppressing the size of the reinforcing rib on the distal end side, it is possible to advantageously ensure the degree of freedom in tuning the spring characteristics in the bending direction of the spring member according to the required frequency characteristics of the damping action. In addition, it is desirable that the ratio between the height of the reinforcing rib on the base side and the height of the reinforcing rib on the tip side satisfies the requirements shown in the following third aspect.

A third aspect of the present invention is the vibration damping device described in the second aspect, wherein in the reinforcing rib, the maximum height dimension h0 on the base side and the minimum height on the mass attachment part side are provided. The dimension h1 has a condition shown by the following formula.
0.2 ≦ h1 / h0 <1 (Formula 3)

  According to the third aspect, the rigidity at the base portion of the spring member can be relatively increased, and the rigidity at the mass attachment portion can be relatively decreased. Therefore, the floor material and the spring member can be firmly fixed. The vibration deformation of the spring member can also be realized stably.

  According to a fourth aspect of the present invention, in the vibration damping device described in the second or third aspect, the spring member has a groove-shaped cross-sectional shape having a concave groove extending in a longitudinal direction. The reinforcing rib is constituted by both side wall portions.

  According to the fourth aspect, a spring member having a structure integrally provided with reinforcing ribs can be easily manufactured with good productivity by press working or the like.

  According to a fifth aspect of the present invention, in the vibration damping device according to the fourth aspect, the both side walls of the concave groove are inclined outwardly so as to gradually widen toward the opening side of the concave groove. In addition, a flange-like portion is formed to extend outward from both edge portions on the opening side of the both side wall portions, and the mass member is placed on the flange-like portion. is there.

  According to the fifth aspect, the mass member can be stably supported by the flange-like portions on both sides, and the springs can be provided by the both side walls of the concave grooves inclined in the direction of expansion toward the groove openings. The cross-sectional secondary moment in the member can be more effectively ensured, and the effect of suppressing torsional deformation can be improved.

  According to a sixth aspect of the present invention, in the vibration damping device according to any one of the second to fifth aspects, a connection portion is provided between the base portion and the mass attachment portion of the spring member. The reinforcing rib extends in the longitudinal direction at a substantially constant height in the base portion and the mass mounting portion, and the height of the reinforcing rib changes in the longitudinal direction at the connecting portion. It is.

  According to the sixth aspect, by providing the connecting portion between the base portion and the mass attachment portion, for example, the height of the reinforcing ribs at the base portion and the mass attachment portion is made substantially constant and fixed to the vibration member. While ensuring the rigidity of a base part stably, it becomes possible to obtain the support strength of the mass member in a mass attachment part stably.

  In the connecting portion in this aspect, for example, one or more stepped portions are provided in the middle portion in the longitudinal direction, and the height of the reinforcing rib is changed in the longitudinal direction on both sides of the stepped portion. It is also possible to make the difference gradually by changing in the longitudinal direction. In particular, when the height dimension of the reinforcing rib is gradually changed, it is desirable to satisfy the requirements shown in the following seventh aspect.

According to a seventh aspect of the present invention, in the vibration damping device according to the sixth aspect, an end edge portion in the height direction of the reinforcing rib in the connecting portion extends in the longitudinal direction at an inclination angle θ satisfying the following formula: It is inclined.
0 ° <θ ≦ 90 °

  In addition, in this aspect, the inclination angle θ of the reinforcing rib in the longitudinal direction of the spring member is constant in the length direction of the connecting portion, and is different partially or stepwise or continuously in the length direction. May be.

  According to an eighth aspect of the present invention, in the vibration damping device according to any one of the first to seventh aspects, the center of gravity position of the mass member is set closer to the mass attachment portion than the base portion. It is what.

  According to the eighth aspect, the mass member can be stably fixed to the spring member near the position of the center of gravity while avoiding deformation inhibition of the spring member by the mass member. In other words, in order to avoid the spring member being unnecessarily restrained by the mass member, it is necessary to fix the mass member to a position where the base portion of the spring member is disengaged toward the distal end side. According to this aspect, the mass member can be easily fixed to the spring member at a substantially center of gravity while avoiding the restraint of the spring member by the mass member without requiring a special bracket or the like. .

  According to a ninth aspect of the present invention, in the vibration damping device according to any one of the first to eighth aspects, the spring member has a groove-shaped cross-sectional shape having a concave groove extending in a longitudinal direction. In the middle part of the longitudinal direction of the spring member, the bottom wall portion of the groove is inclined so that the depth dimension of the groove is gradually changed, while the opening edge of the groove is entirely formed. It extends on the same plane.

  According to the ninth aspect, by attaching a slope to the bottom wall portion side of the groove-shaped spring member, the outer surface of the bottom wall portion can be mounted and fixed on the vibrating body at the base portion. In such a mounting state, it is also possible to efficiently secure a space for disposing the damping body between the mass mounting portion and the vibrating body.

  Further, since the opening edge of the concave groove extends on the same plane throughout, it is possible to easily form a support surface that stably supports the mass member at the opening edge. Become.

  As is apparent from the above description, in the vibration damping device having the structure according to the present invention, the torsional deformation in the long plate-like spring member is suppressed, so that vibration is caused by an unintended torsional mode vibration amplification action. The trouble that the vibration state of the body deteriorates is prevented. As a result, the vibration damping action with respect to the originally intended vibration is efficiently exhibited, and a further excellent vibration damping effect is achieved for the vibration member.

1 is a front view of a vibration damping device as a first embodiment of the present invention. The top view of the damping device shown in FIG. III-III sectional drawing of FIG. IV-IV sectional drawing of FIG. The cross-sectional view of the base part of the spring member which comprises the damping device shown in FIG. The cross-sectional view of the mass attachment part of the spring member which comprises the damping device shown in FIG. The graph which shows the specific example combined with the reference example which measured the vibration characteristic of the frequency in the damping device of the structure shown by FIG.

  Embodiments of the present invention will be described below with reference to the drawings.

  FIG. 1 shows an architectural dynamic damper 10 as an embodiment of a vibration damping device structured according to the present invention. In addition, the virtual line in FIG. 1 shows the flooring 12 of the building as a vibrating body to which the dynamic damper 10 is mounted. Further, in the following description, the vertical direction means the vertical direction in FIG. 1 that is substantially vertical in the vertical direction when mounted on the back surface of the flooring 12 unless otherwise specified.

  1-4, the dynamic damper 10 of this embodiment includes a leaf spring 14 as a spring member, a mass member 16 attached to the leaf spring 14, and a contact rubber 18 as a damping body. Have.

  The leaf spring 14 has a longitudinal plate shape extending in the substantially horizontal direction and extending in the left-right direction in FIG. The leaf spring 14 is preferably formed of a metal such as iron, steel, or aluminum alloy, but may be formed of a synthetic resin or the like. The leaf spring 14 of the present embodiment is made of metal, and is formed by stamping and pressing a flat plate.

  Further, the leaf spring 14 has a groove-shaped cross-sectional shape in which a groove 20 extending in the longitudinal direction opens downward. That is, at the center portion in the width direction of the leaf spring 14, an upper bottom portion 22 is provided as a bottom wall portion, and both side wall portions 24, 24 rising downward from both edge portions in the width direction of the upper bottom portion 22 are formed. Has been.

  In other words, the leaf spring 14 is formed with a pair of reinforcing ribs that protrude upward and extend in the longitudinal direction, and is opposed to the both sides of the leaf spring 14 in the width direction (left and right direction in FIG. 3) with a predetermined distance therebetween. Has been. In the present embodiment, the upper end edges of these reinforcing ribs are connected to each other to form the concave groove 20. That is, the pair of reinforcing ribs are constituted by the both side wall portions 24, 24, and the upper end edge portions of the both side wall portions 24, 24 are connected by the upper bottom portion 22 to constitute the concave groove 20.

  And these both side wall parts 24 and 24 incline with the inclination | tilt angle (alpha) (refer FIG. 5) to both outer sides so that it may spread gradually toward the groove opening side from the upper bottom part 22. FIG. Further, flange-like portions 26, 26 that extend in the substantially horizontal direction toward the outside of the groove 20 are formed at the edge portions on the groove opening side of the both side wall portions 24, 24.

  In addition, the edge part by the side of the groove opening in both the side wall parts 24 and 24 is extended on the same plane over the full length. As a result, the flange-like portions 26, 26 spreading from the end edges of the side wall portions 24, 24 are spread out on the same plane. Further, the opening surface of the concave groove 20 of the leaf spring 14 is widened with one horizontal plane, and the flange-like portions 26 and 26 are concave grooves with a substantially constant width dimension over the entire length in the longitudinal direction of the leaf spring 14. It spreads in the width direction of 20.

  Further, the depth dimension of the concave groove 20 of the leaf spring 14 is changed in the longitudinal direction of the leaf spring 14, and the depth dimension on the right side is made smaller than the depth dimension on the left side in FIG. ing. Accordingly, the side wall portions 24 and 24 of the concave groove 20 constituting the reinforcing ribs also have a right-side height dimension smaller than the left-side height dimension in FIG.

In particular, in this embodiment, the region extending from the left end in FIG. 1 of the leaf spring 14 to a predetermined length has a maximum groove depth dimension h0 as shown in FIG. The base 28 has a deep groove shape that extends. On the other hand, the region extending from the right end of the leaf spring 14 to the predetermined length in FIG. 1 has a minimum groove depth dimension h1 as shown in FIG. The mass mounting portion 30 is formed. Such h0 and h1 preferably satisfy the following mathematical formula.
0.2 ≦ h1 / h0 <1 (Formula 3)

  Further, the intermediate portion located between the base portion 28 and the mass attachment portion 30 in the longitudinal direction of the leaf spring 14 extends from the groove depth dimension h0 of the base portion 28 to the groove depth dimension h1 of the mass attachment portion 30. The connecting portion 32 has a changing depth changing portion. Note that the entire length of the connecting portion 32 of the present embodiment is a depth changing portion, and the depth dimension is changed gradually and gradually from one end portion in the longitudinal direction to the other end portion. It has been. That is, in the base portion 28 and the mass attachment portion 30 of the leaf spring 14, the height of the side wall portions 24, 24 is substantially constant over the entire length of the leaf spring 14 in the longitudinal direction. In the connecting portion 32 located in the middle of the mass attaching portion 30, the height dimension changes in the longitudinal direction of the leaf spring 14.

  Thereby, the upper bottom part 22a of the base part 28 of the leaf | plate spring 14 is made into the attachment surface to the flooring 12 which is located in the uppermost perpendicular direction and spreads substantially horizontally. Further, the upper bottom portion 22b of the connecting portion 32 of the leaf spring 14 is an inclined surface that is inclined and widened. Furthermore, the upper bottom portion 22c of the mass attachment portion 30 of the leaf spring 14 is a mounting surface that extends substantially horizontally at a position that is lower than the upper bottom portion 22a of the base portion 28 by a predetermined distance in the vertical direction.

  Here, the inclination angle θ (see FIG. 1) of the connecting portion 32 with respect to the base portion 28 is preferably set to 0 ° <θ ≦ 90 °. In other words, it is preferable that the edge portion of the reinforcing rib 24 in the connecting portion 32 is inclined in the longitudinal direction of the leaf spring 14 with an angle of 0 ° <θ ≦ 90 °. When θ is 90 °, a step in the vertical direction is provided in the connecting portion 32, and the base portion 28 of the leaf spring 14 and the mass attaching portion 30 are connected by the connecting portion 32 having a step.

  And in the base 28 of the leaf | plate spring 14, the attachment surface 22a is overlaid on the lower surface of the flooring 12 of a building, and the leaf | plate spring 14 with respect to the flooring 12 with the fixing volt | bolt penetrated by the several bolt hole 34 is carried out. It is supposed to be fixed. Under such a mounting state, the mounting surface 22c of the mass mounting portion 30 of the leaf spring 14 is separated from the floor material 12 by a predetermined distance so as to be opposed to each other.

  Further, the contact rubber 18 is superimposed on the mounting surface 22c and fixed to the mass mounting portion 30 of the leaf spring 14 so as to protrude upward from the mounting surface 22c. The abutting rubber 18 has a substantially truncated cone shape, and a locking projection 36 having a substantially stepped columnar shape projects from the base end surface on the large diameter side. The contact rubber 18 is superimposed on the mounting surface 22c at the base end surface on the large diameter side, and the large-diameter head portion of the locking protrusion 36 is a locking hole provided in the upper bottom portion 22c of the mass mounting portion 30. The contact rubber 18 is fixed to the leaf spring 14 by being inserted and locked to the plate 38.

  The height of the contact rubber 18 is set to be larger than the height difference between the upper bottom 22a of the base 28 and the upper bottom 22c of the mass attaching portion 30 in the leaf spring 14, so that the dynamic damper 10 is mounted. Under the state, the front end surface of the contact rubber 18 is pressed against the lower surface of the flooring 12 with a predetermined pressing force.

  On the other hand, the mass member 16 is superimposed on the mass attaching portion 30 of the leaf spring 14 from the opening side of the groove 20 and fixed in contact with the flange-like portions 26 and 26. The mass member 16 can be suitably formed of a metal having a large specific gravity such as iron, and has a cylindrical shape in this embodiment. Bolt holes 40, 40 are formed in the flange-like portions 26, 26 of the mass attachment portion 30, and the bolts 40 are inserted into these bolt holes 40, 40, so that the mass attachment portion 30 can be connected to the mass attachment portion 30. The member 16 is fixed.

  The dynamic damper 10 having such a structure is substantially supported by a cantilever structure when shock vibration during walking or the like applied to the upper surface of the flooring 12 is applied to the base portion 28 in the mounted state. Therefore, the mass attaching part 30 vibrates up and down. That is, the mass member 16 is elastically supported by the floor material 12 via the leaf spring 14, and the mass member 16 can be relatively displaced up and down with respect to the floor material 12 by elastic deformation of the leaf spring 14. A mass-spring resonance system in which the leaf spring 14 and the contact rubber 18 are used as spring components and the mass of the mass member 16 is used as a mass component is configured by the dynamic damper 10 and added to the flooring 12.

  In addition, the contact rubber 18 is disposed between the leaf spring 14 and the flooring 12 and is in contact with the back surface of the flooring 12. In this embodiment, the axial direction is between the leaf spring 14 and the flooring 12. Is compressed. The contact rubber 18 may be in contact with the back surface of the flooring 12 without being compressed in the axial direction (0 touch), or may be spaced downward with respect to the back surface of the flooring 12. .

  When a vibration in the vertical direction is input to the flooring 12 due to, for example, a person jumping on the upper floor, the vibrational energy of the flooring 12 is converted into vibrational energy of the dynamic damper 10 and absorbed. Thereby, the vibration of the flooring 12 is reduced and the propagation of vibration energy to the downstairs is reduced, so that the sound propagated downstairs is reduced. Although not shown in the drawing, generally, a plurality of dynamic dampers 10 are attached to the flooring 12 in a distributed manner. Preferably, when the sum total of the mass of the mass members 16 in the plurality of dynamic dampers 10 is about 5% to 20% with respect to the mass of the flooring 12, the vibration damping effect can be effectively obtained. it can.

  Here, in the vibration damping device 10 of the present embodiment, the dimensions of each part are set so as to satisfy the requirements expressed by the following formulas, thereby suppressing the vibration mode in the torsional direction to be small in the vertical direction. Thus, it is possible to efficiently exhibit the damping effect on the vertical vibration in the floor material by the bending vibration mode of the cantilever structure.

2 ≦ W / (X + H / 2) ≦ 6 (Formula 1)
0.8 ≦ H / X ≦ 2.5 (Formula 2)
However, W is the width dimension of the mass member 16 (see FIG. 2), and X is the distance from the mounting surface of the mass member 16 to the contact surface of the contact rubber 18 to the flooring 12, that is, the upper surface of the contact rubber 18. It is a height dimension, H is a height dimension of the mass member 16 (refer FIG. 1).

  That is, in the mass mounting portion 30 in the dynamic damper 10, the weight of the contact rubber 18 and the mass mounting portion 30 is sufficiently small compared to the weight of the mass member 16. The position of the center of gravity of the portion 30 in the height direction is positioned below (X + H / 2) from the contact surface of the contact rubber 18 with the flooring 12. Here, as shown in the above (Equation 1), when the value of W / (X + H / 2) is set in the range of 2 or more and 6 or less, the leaf spring 14 is stably vibrated in the vertical direction. Thus, the vibration damping action of the dynamic damper 10 can be effectively exhibited. The mass mounting portion 30 that covers and includes the mass member 16 and the contact rubber 18 has a flat shape as a whole, but when W / (X + H / 2) is larger than 6, the shape becomes too flat, This is because when the leaf spring 14 vibrates, torsional vibrations other than the vertical direction are likely to occur. On the other hand, if W / (X + H / 2) is smaller than 2, the width dimension W of the mass mounting portion 16 cannot be sufficiently secured with respect to the position of the center of gravity in the height direction of the mass mounting portion 30 in the dynamic damper 10. This is because when the leaf spring 14 vibrates, it is likely that torsional vibration other than the vertical direction is likely to occur.

  Further, as in (Expression 2) above, the value of (H / X) is set to 0.8 or more and 2.5 or less, so that the leaf spring 14 is stably vibrated in the vertical direction. The vibration damping action of the dynamic damper 10 can be effectively exhibited. When the lid is closed and the value of (H / X) is smaller than 0.8, it is difficult to secure a sufficient mass in the mass member 16, and it is likely that torsional vibrations other than the vertical direction are likely to occur when the leaf spring 14 vibrates. Because there is. On the other hand, if the value of (H / X) is larger than 2.5, the mass of the mass member 30 becomes too large, and torsional vibrations other than the vertical direction are likely to occur, and stable vertical vibrations of the leaf spring 14 are caused. It is because there is a possibility of affecting.

  Since the vibration in the torsion mode is suppressed by setting the numerical values so as to satisfy the above (Equation 1) and (Equation 2), the vibration state in the originally intended vertical vertical bending mode is suppressed. Stabilization can be achieved. Therefore, as shown in FIG. 7, it is possible to increase the gain in the vertical mode (bending mode) by reducing the gain in the natural vibration region of the torsion mode, and the original vertical direction. Therefore, it is possible to obtain a more excellent vibration damping effect against the vibration of the flooring material while suppressing the hindrance of the floor vibration due to the torsional mode resonance of the vibration damping device. In addition, in FIG. 7, the measurement data of the damping device which does not satisfy the requirements of said (Formula 1) are also shown as a reference example.

  Further, it is clear from the actual measurement result shown in FIG. 7 that the torsional vibration is effectively suppressed by satisfying the above-described requirements. In this actual measurement, the dynamic damper 10 having the structure shown in this embodiment is used, and the mass of the mass member 16 is 3.5 kg. Moreover, the material of the mass member 16 and the contact rubber 18 other than the plate spring 14 is the same, and only the shapes of the mass member 16, the contact rubber 18 and the plate spring 14 are changed. In addition, as a comparative example, the following results are also shown in [Table 1], in which the same measurement is performed for a damping device that does not satisfy the requirements.

  In [Table 1], those satisfying the numerical ranges of (Equation 1), (Equation 2), and (Equation 3) are shown in bold, and the acceleration gain in the torsion mode and the acceleration in the vertical mode are shown. The damping effect was evaluated by ◎, ○, △, × by the ratio with the gain. That is, the vertical mode acceleration gain is greater than 3 times the torsion mode acceleration gain, which is very effective, and the greater than 2 times and less than 3 times are effective, and 1 A larger value of 2 times or less was evaluated as Δ with a slight effect, and a value of 1 time or less was evaluated as x with no effect.

  As shown in [Table 1] above, in the dynamic dampers of Examples 1 to 4 that satisfy both the numerical ranges of (Expression 1) and (Expression 2), the acceleration gain in the torsion mode is suppressed to be small, and the vertical mode Since the acceleration gain is a relatively large numerical value, it is presumed that the torsional vibration of the leaf spring 14 is suppressed and the vibration is effectively vibrated in the vertical direction, and a stable vibration damping effect is obtained. On the other hand, in the dynamic dampers of Comparative Examples 1 to 6 that do not satisfy at least one of the numerical ranges of (Expression 1) and (Expression 2), the acceleration gain in the torsion mode is set to a relatively large value, and the acceleration gain in the vertical mode is set. Therefore, it is presumed that torsional vibration is likely to occur and an effective vibration control action cannot be obtained.

  In the dynamic damper 10 of the present embodiment, it is preferable to increase the rigidity of the base portion 28 attached to the flooring 12 and reduce the rigidity of the mass attachment portion 30 that is elastically deformed substantially by vibration. Here, since the leaf spring 14 of the present embodiment is integrally formed of the same material, such a difference in rigidity is realized by the respective groove depth dimensions. And it is preferable that the groove depth dimension h0 in the base part 28 and the groove depth dimension h1 in the mass attachment part 30 satisfy | fill said (Formula 3). If h1 / h0 is smaller than 0.2, the mass mounting portion 30 becomes too thin as compared with the base portion 28, so that the leaf spring 14 cannot function as a spring, and the dynamic damper 10 is controlled. This is because the vibration effect cannot be obtained.

  As mentioned above, although embodiment of this invention was explained in full detail, this invention is not limited by the specific description. For example, in the above-described embodiment, the connecting portion 32 has a depth dimension that continuously changes over the entire length in the length direction. However, as described above, θ = 90 ° and an intermediate portion in the length direction of the leaf spring. It is also possible to provide a step on the surface. Further, in the longitudinal direction of the leaf spring, a plurality of these portions where the depth dimension continuously changes and step portions may be provided.

  Moreover, in the said embodiment, although the leaf | plate spring 14 was made into the groove type cross-sectional shape and the side wall parts 24 and 24 as a reinforcement rib were integrally formed, while using flat plate shape as a leaf | plate spring, it formed separately. Vertical plate-shaped reinforcing ribs may be provided by welding or the like.

  Furthermore, instead of or in addition to the reinforcing ribs 24 and 24 spaced apart on both sides in the width direction of the leaf spring 14 as in the above-described embodiment, a reinforcing rib extending in the longitudinal direction at the intermediate portion in the width direction of the leaf spring may be adopted. .

  Furthermore, the specific shapes of the mass member and the attenuation body are not limited. For example, in addition to the circular block shape illustrated as the mass member, an arbitrary shape such as an elliptical block shape or a rectangular block shape can be adopted. In the mass member, the position of the center of gravity is preferably located on the mass mounting side of the base, so that the spring function of the leaf spring is stably exhibited, and the damping action by the dynamic damper is also effective. Can get to.

  Further, the mounting positions of the damping body and the mass member are not necessarily the same, and the damping body and the mass member can be mounted at different positions in the longitudinal direction of the spring member. Furthermore, a plurality of attenuation bodies and a plurality of mass members can be appropriately mounted according to required characteristics. When mounting a plurality of mass members, the distance between the outermost ends on both sides in the width direction of the mass members is adopted as the width dimension W of the mass members, while the height dimension H of the mass members is An average value in the height direction of the plurality of mass members is employed. The center of gravity of the mass member is positioned on the vertical plane including the elastic main axis of the spring member in the width direction.

  Furthermore, the mounting state on the building is not limited to the example. For example, when the flooring is inclined, it is possible to arrange the spring member so as to extend along the inclined floor surface, and to reduce the vibration of the wall material of the building. In the case of the purpose, the spring member can be arranged in the vertical direction or the vertical direction in a state of extending along the wall material extending vertically. However, the vibration damping device according to the present invention is not limited to the dynamic damper attached to the building as in the above-described embodiment, and can be employed as various types of vibration damping devices for suppressing vibration.

  Further, it is possible to additionally adjust the damping performance by forming a rubber elastic body on the surface of the leaf spring. It is also possible to use a damping effect due to flow resistance by sealing a viscous fluid inside the damping body.

  Furthermore, in the above embodiment, the leaf spring 14 has a groove-shaped cross-sectional shape, and the rigidity in the longitudinal direction of the leaf spring 14 is changed by changing the groove depth in the longitudinal direction. The rigidity may be changed by varying the width dimension and the plate thickness in the longitudinal direction, and it is not necessary to have a groove-shaped cross-sectional shape.

10: Dynamic damper (damping device), 12: Floor material (vibrating body), 14: Leaf spring (spring member), 16: Mass member, 18: Abutting rubber (damping body), 20: Concave groove, 22: Upper bottom portion (bottom wall portion), 22a: upper bottom portion (mounting surface), 22b: upper bottom portion (inclined surface), 22c: upper bottom portion (mounting surface), 24: side wall portion (reinforcing rib), 26: flange-shaped portion, 28: Base part, 30: Mass attachment part, 32: Connection part

Claims (9)

One side of the spring member having a longitudinal plate shape is a base portion fixed to the vibrating body, while the other side of the spring member is a mass attachment portion, and the mass member is fixed to the mass attachment portion. And a damping device provided with a damping body that protrudes from the mass mounting portion and abuts against the vibrating body,
A vibration damping device characterized by having all of the conditions shown in the following equations.
2 ≦ W / (X + H / 2) ≦ 6
0.8 ≦ H / X ≦ 2.5
W = Width dimension of the mass member X = Height dimension from the mounting surface of the mass member to the contact surface of the damping body to the vibrating body H = Height dimension of the mass member   In the spring member, a plurality of reinforcing ribs protruding in the height direction and extending in the longitudinal direction are formed apart from each other in the width direction, and the height dimension of the reinforcing ribs is made smaller in the mass mounting portion than in the base portion. The vibration damping device according to claim 1. 3. The vibration damping device according to claim 2, wherein in the reinforcing rib, a maximum height dimension h <b> 0 on the base side and a minimum height dimension h <b> 1 on the mass attachment part side are provided with a condition expressed by the following expression.
0.2 ≦ h1 / h0 <1   4. The vibration damping device according to claim 2, wherein the spring member has a groove-shaped cross-sectional shape having a recessed groove extending in a longitudinal direction, and the reinforcing rib is formed by both side wall portions of the recessed groove.   Both side wall portions of the concave groove are inclined to both outer sides so as to gradually widen toward the opening side of the concave groove, and toward both sides outward from the edge of the opening side of the both side wall portions. The vibration damping device according to claim 4, wherein a flange-like portion that extends is formed, and the mass member is placed on the flange-like portion.   A connecting portion is provided between the base portion and the mass attaching portion of the spring member, and the reinforcing rib extends in the longitudinal direction at a substantially constant height dimension between the base portion and the mass attaching portion. The vibration damping device according to any one of claims 2 to 5, wherein a height dimension of the reinforcing rib is changed in a longitudinal direction in the connecting portion. The vibration damping device according to claim 6, wherein an end edge portion in the height direction of the reinforcing rib in the connecting portion is inclined in the longitudinal direction at an inclination angle θ satisfying the following expression.
0 ° <θ ≦ 90 °   The vibration damping device according to claim 1, wherein a position of the center of gravity of the mass member is set closer to the mass attachment portion than the base portion.   The spring member has a groove-shaped cross-sectional shape having a groove extending in the longitudinal direction, and the bottom wall portion of the groove is inclined at an intermediate portion in the longitudinal direction of the spring member so that the depth of the groove is 9. The vibration damping device according to claim 1, wherein the dimension of the groove is gradually changed, and the opening edge of the groove extends over the same plane throughout.