WO1992002743A1 - Vibration-damping apparatus - Google Patents

Abstract

This invention relates to a vibration-damping apparatus (dynamic damper) for damping vibration in tower-like structures and multistored buildings. More specifically, in a pendulum type vibration-damping apparatus comprising a weight (1), a spring (9), a damper (8), suspension members (2, 3, 4) and a fitting frame (7), the present invention provides a vibration-damping apparatus characterized in that upper suspension frames (5, 6) and lower suspension frames (5', 6') each consisting of a quadrilateral are disposed between the fitting frame (7) and the weight (1), the upper suspension frames (5, 6) and the lower suspension frames (5', 6') are supported by four joint materials (5a, 5b) so as to suspend the weight (1) in multiple stages and the fitting angles of the lower suspension frame quadrilaterals with respect to the upper suspension frame quadrilaterals are made unequal lest the suspension members (2, 3, 4) overlap. In a dynamic damper consisting of a vibration system and an oil damper (8), the present invention provides also a vibration-damping apparatus characterized in that an oil damper (8) of the type whose damping force is proportional to the square of a speed beyond a certain speed level is employed.

Description

 Name of Invention

 Technical field

 The present invention relates to a vibration control device (Dynamic ♦ Dano, ·) applied to the vibration control of tower-like structures (pylons, observation towers, etc.) and high-rise buildings.

 Background art

 Conventionally, as shown in Fig. 12, it is composed of a weight 1, a hanging member 2, a damper 8, and a spring 9 which can be attached as required. However, it was directly attached to the structure 7. In other words, in the case of single suspension (single-stage suspension), the period was adjusted by changing the length of the suspended material.

 In the event that the hanging material is broken and the weight falls, no measures have been taken to relieve the city on the floor.

Further, the vibration damping device configured as shown in FIG. 16 has the following features. In FIG. 16, reference numeral 71 denotes a vibrating body. The vibrating body 71 is suspended from a suspension frame 73 by a suspension member 79 having no bending rigidity. Further, the suspension 73 is suspended by the structure 74 by the suspension member 79 having no bending rigidity. A damper 76 is interposed between the structure 74 and the lower end section of the suspension frame 73, and the vibrating body 71 and the lower end section of the suspension frame 73. Lower end of the above structure 74 and suspension frame 7 3 A spring 77 was interposed between the gate, the vibrating body 71 and the lower end of the suspension frame 73 as necessary.

 When vibration is generated in the structure 74 by the above-described configuration, the vibration of the structure 74 is transmitted to the vibrator 71 via the damper 76, the spring 77, and the suspension frame 73. The vibration is transmitted and the vibrating body 71 vibrates. The vibration of the structure 74 is suppressed by the vibration of the vibrating body 71.

 In the damping device having the structure shown in Fig. 16, the point of action of the damper and the spring is located at the bottom of the suspension member 79, so the vibrator and the suspension frame are large. Vibrating. For this reason, the damper 76 and the spring 77 need to have a large stroke.

 Further, an oil damper used for a conventional vibration damping device (dynamic damper) generally has a speed proportional damping force characteristic. there were .

 Disclosure of invention

 The present invention solves the problems described below and provides a vibration damping device for a compact tower-like structure, a high-rise building, and the like, and further provides a damper having a small stroke. An object of the present invention is to provide a vibration damping device using a vibration damping member such as a spring.

(1) In the conventional method, in order to increase the period of the pendulum, the length of the pendulum (the length of the hanging material) becomes longer, and the problem of space (particularly in the vertical direction) is reduced. Was born. That is, for example, the length of a pendulum with a period of 6 seconds is about 9 m, and for a normal high-rise building, a height of three stories is required. Therefore 3 It is necessary to crush the space corresponding to the floor in order to install the damping device.

 (2) As a method of adjusting the frequency of the pendulum, if the vibration is in one direction, it can be dealt with by changing the length of the pendulum, but the frequency in two directions can be adjusted. It is not possible to change the length of the pendulum if it is different.

 (3) In the conventional method, a spring with a stroke of the same length as the amplitude of the pendulum is required. For example, if the amplitude of the pendulum is 1.2 m, the stroke of the spring will be ± 1.2 «(+: bow stretch, —: compression).

 (4) Similarly, in the conventional method, it is necessary to provide a stroke with a stroke of the same length as the pendulum amplitude.

 (5) In the conventional method, the period of the pendulum is adjusted by changing the length of the hanging material.However, changing the length of the hanging material is not the same as changing the length of the hanging material. You have to prepare a lot of different hanging materials. And it takes a lot of time and effort to replace it. Also, it is difficult to fine-tune the period of the pendulum.

 (6) The weight of the pendulum type vibration damping device is hung by the hanging material, and if the hanging material breaks and the weight falls down In some cases, the floor may be severely impacted and the floor may be broken. In addition, most of the weight of the pendulum type vibration damper is concentrated on the weight, and the weight is held when the vibration damper is installed or when the maintenance is performed. Chige

-'Work is important.

(7) When changing the suspension height of the weight / suspension frame. The setting of the damper and the spring becomes difficult. Also, it has disadvantages such as the height being uneven and the aesthetic feeling being worsened.

 (8) In the conventional method, when shortening the period of the pendulum, simply reducing the length of the suspending material makes the inner suspending frame contact with the outer suspending frame. As a result, the adjustment range was limited. Also, if the period of the pendulum is lengthened, the suspension height of the suspension frame will be uneven, which will make it difficult to set the damper and spring. There was a drawback.

 (9) In the damping device having the structure shown in Fig. 16, the damping, the 'and the spring must have a large stroke. There is a disadvantage.

 00) A conventional dynamic damper that has a damping force characteristic of a general speed proportional type, a dynamic damper that uses a ', installs the weight amplitude and that The ratio of the obtained structure amplitudes is constant irrespective of the magnitude of the amplitude. Also, the larger the ratio between the weight amplitude and the structure amplitude, the greater the damping effect.

Therefore, recently, in order to improve the livability of high-rise buildings, etc., vibrations of about 10 cm, which are caused by winds of about 10 to 20 mZs, are usually reduced. Demand for vibration damping devices to suppress the vibration has begun.However, to increase the damping effect, the ratio of the amplitude of the weight Z and the amplitude of the structure is large, for example, about 5-6. The design to be used is generally made. In this case, if a conventional velocity proportional oil damper is used, the ratio of the amplitude of the weight to the amplitude of the structure is constant, and large winds such as a large earthquake or 40 m / s or more occur. At times, the amplitude of the weight is very large because the building vibrates about 1 m with one side amplitude. PT JP

(E.g., 5 to 6 m at one amplitude), making it virtually impossible to design. As a countermeasure against this, it is possible to suppress the amplitude by hitting the stump with a one-sided radiation of about 1 to 2 m, but in this case, the impulse The reaction was applied to the building side, which had an adverse effect.

 In order to solve the above problems, the vibration damping device of the present invention has the following features.

 (1) In a pendulum type vibration damping device consisting of a weight, a spring, a damper, a hanging member, and a mounting frame, an upper suspension is provided between the mounting frame and the gate. In addition to providing a hanging frame and a lower hanging frame, it is also necessary to have a connecting material for joining the upper hanging frame and the lower hanging frame, and to hang the β-weight forward in multiple stages. Features.

 (2) In the vibration damping device of the above means (1), the upper suspension frame and the lower suspension frame are formed in a quadrilateral, and the upper suspension frame and the lower suspension frame are connected by four joints. In addition to being supported by the hanging material, the mounting angle of the lower hanging frame quadrilateral with respect to the upper hanging frame quadrilateral has been changed so that the hanging materials do not overlap. And

 (3) The vibration damping device of the means (2) is characterized in that a spring for adjusting the frequency of the pendulum is provided between the suspension frames.

 (4) The vibration control device of the above-mentioned means (2) is characterized in that the vibration control device is installed between the dambor and the suspension frame.

(5) In the vibration damping device of the above means (2), a spring for adjusting the frequency of the pendulum and a damper are provided between the suspension frames. (6) The vibration damping device according to the above means α) is characterized in that a hanger horizontal support device for adjusting the frequency of the pendulum is provided.

 (7) In the vibration damping device of the above-mentioned means (1), a foot for lowering the impact when the weight falls and a jack for maintenance are provided at the lower part of the weight. It is characterized by having a device.

 (8) In the vibration control device of the above means (1), a slide jig is installed between the end of the hanging material and the hanging frame and the weight, and the position of the hanging point is determined. In addition to being movable, the length of the pendulum is changed by the turnbuckle attached to the hanging material, and the period of the pendulum is adjusted.

 (9) In the vibration damping device of the above-mentioned means (1), a suspension mechanism shall be installed on the suspension frame, and a turnbuckle shall be installed on the suspension material. The feature of this is that the length of the pendulum is changed, and the period of the pendulum is adjusted.

 AO) a structure in which vibration is suppressed, a plurality of first hanging members having bending rigidity, one end of which is supported by the structure to be rotatable; and A suspending frame supported at the other end of the suspending member in a rotationally self-supporting manner; one end of the suspending frame is supported in the rotating self-supporting manner, and the other end is pivotally supported by the vibrating body. A plurality of the second suspended members, between the vicinity of the one end side of the first suspended member and the structure, and between the vicinity of the one end side of the second suspended member and the suspension frame. And a variable stroke mechanism provided.

Vibration of the structure is transmitted to the vibrating body via the suspension and the suspension frame. In order to achieve this, it is necessary to attach a variable stroke device between the structure and the suspension and the suspension and the suspension frame at a position near the suspension point. This is what we did.

 (11) In a vibration system and a vibration damping device (dynamic damper) composed of an oil damper, at a speed higher than the damping speed level It is characterized by the use of an oil chamber that is of the square-proportional type. In other words, in the present invention, the large amplitude caused by a large earthquake or strong wind that occurs in the conventional dynamic dam is automatically suppressed, It is characterized by the use of an oil member that becomes a speed square proportional type when the speed exceeds a certain speed.

 The vibration damping device of the present invention configured as described above has the following operation.

 (1) The cycle of a pendulum with weights suspended in multiple stages is almost equal to the cycle of a conventional pendulum having a length obtained by adding the lengths of the multiple stages of pendulum.

 (2) By adding a spring, the frequency of the pendulum can be changed without changing the length of the pendulum.

 (3) Generally, the amplitude of each pendulum of an n-stage suspended pendulum is about 1 / n that of a conventional pendulum.

 (4) Therefore, if the dampers are placed between the individual suspension frames, a damper with a stroke of 1 / n of the amplitude of the conventional pendulum can be used. Become .

(5) Grasp the middle of the hanging material with the horizontal support bracket, and By restraining the horizontal displacement of the suspension, the suspended material below the gripped part is independent of the length of the pendulum and suspended above the gripped part. The length of the rebar is the effective pendulum length.

 (6) With the legs coming out of the lower part of the weight and slightly below the floor, even if the weight falls, the distance to the floor is very short. As a result, the impact force on the floor is greatly reduced.

 (7) Since the joints between the end of each hanging material and the hanging frame and weight can be slid up and down, the hanging material fixing position is changed. be able to . In addition, since a turn knocker is installed in a part of the hanging material, the length of the hanging material itself can be changed, and the change of the hanging material can be changed. By absorbing the length with the above-mentioned slide part, it is possible to adjust the period by changing the length of the pendulum without changing the height of the suspension frame and weight. Let's go.

 (8) Adjusting the length of the hanging material changes the length of the pendulum. At the same time, by extending and contracting the suspension frames, it is possible to avoid contact between the suspension frames and irregularities in the installation positions of the suspension frames.

 (9) By installing a damper or spring at a position close to the upper fulcrum of the hanging material, the stroke of the damper, 'yaba. Can be used.

00) At a certain speed level or higher, the damping force is proportional to the square of the speed. When the amplitude exceeds the level, the dynamic damping factor increases, and as the structure amplitude increases, the dynamic damper becomes heavier. The ratio of the weight amplitude to the structure amplitude decreases, and the amplitude of the weight of the dynamic damper can be suppressed.

5 Brief explanation of drawings

 FIG. 1 is a diagram showing a first embodiment of the present invention.

 FIG. 2 is a diagram showing a second embodiment of the present invention,

 FIG. 3 is a diagram showing a third embodiment of the present invention.

 FIG. 4 is a diagram showing a fourth embodiment of the present invention,

 ,. FIG. 5 to FIG. 7 show a fifth embodiment of the present invention.

 FIG. 8 is a diagram showing a sixth embodiment of the present invention.

 FIG. 9 is a diagram showing a seventh embodiment of the present invention.

 FIG. 10 to FIG. 11 are views showing an eighth embodiment of the present invention.

_{1 5} FIG. 12 Ru Oh a diagram showing a conventional apparatus.

 FIG. 13 is a diagram showing a structure of a vibration damping device according to a ninth embodiment of the present invention,

 FIG. 14 is a diagram showing a state in which the vibration damping device is operated, FIG. 15 is a configuration diagram showing a tenth embodiment of the present invention,

20 Fig. 16 is a diagram showing the structure of a problematic vibration damping device. <Fig. 17 is a side view of the eleventh embodiment of the present invention.

 Fig. 18 is the same plan,

 Figure 19 shows the relationship between building amplitude and weight amplitude, and the relationship between building amplitude and building decay.

Fig. 20 shows the characteristic diagram of oil FIG. 21 to FIG. 25 are views showing other embodiments of the present invention.

 BEST MODE FOR CARRYING OUT THE INVENTION Some embodiments of the present invention are shown in FIGS. 1 to 11. FIG. 1 shows a first embodiment of the present invention. It has a three-stage, two-point suspension structure, and controls vibration in one direction (the X-axis direction in Fig. 1).

 In Fig. 1, 1 is a weight, 2, 3 and 4 are hanging materials, 5 and 6 are upper hanging frames, 5a and 6a are connecting materials, and 5 'and 6' are lower hanging materials. 7 indicates a structure (mounting frame), 8 indicates a dam, and 9 indicates a spring.

 The weight 1 is suspended by the suspending member 2 and the upper suspending frame 5. The upper suspending frame 5 is in a horizontal state. A highly rigid connecting member 5a protruding downward from both ends of the upper suspension frame 5 and a lower suspension frame 5 'are provided. The lower suspension frame 5 ′ is suspended by the suspension member 3 and the upper suspension frame 6. The upper suspension frame 6 is in a horizontal state. A connecting member 6a protruding downward from both ends of the upper suspension frame 6 and a lower suspension member 6 'can be provided. The lower suspension member 6' is a suspension member 4 and is attached to the structure (mounting frame) 7. It is suspended.

The height of the hanging material mounting part of the connecting materials 5a and 6a should be almost the same as the mounting point of the hanging material 2 with respect to the weight 1, and the hanging materials 2, 3, 4 The upper suspension frames 5 and 6 restrict the movement in the y-axis direction perpendicular to the X2 plane in Fig. 1 so that the z-components overlap each other. (Not shown). Assuming now that the lengths of the hanging members 2, 3, and 4 are £ ',-' £ 3, the period T of the first embodiment is

g ： 重力 の 加速度 で 表 わ さ れ る 。

g: Expressed by the acceleration of gravity.

In the conventional type shown in FIG. 12, the length of the pendulum needs to be (£ = £, + £ 2 + ^ 3). Therefore, if £, = 2 | 11, £ ₂ = 3 | 11, £ ₃ 4 | «1, then £ is 9 m. The period T is given by equation (1).

(2 + 3 + 4) X 100

 Τ 2 Γ 6.02 (sec)

 980

It becomes. On the other hand, in the device of the first embodiment, the length of each pendulum is 4 m or less, and the length of the pendulum can be reduced to half or less of the conventional 9 m. Therefore, if the floor height of the floor on which the vibration damping device is installed is 9 m in the conventional type, it can be reduced to 4 mm.

 Fig. 2 shows a second embodiment of the present invention in the case of a three-stage four-point suspension.

In this example, as shown in Fig. 2, the suspension members 2, 3, 4 and the upper suspension frames 5, 6 are combined by shaking 45 '. The levels of the suspension frames 5 and 6 are arranged in the same horizontal plane, so that the required space in the height direction is kept small. The device according to the second embodiment functions as a damper for vibrations in any direction of 360 'in a plane.

 The period T of the device of the second embodiment is also expressed by equation (1), where the lengths of the hanging members 2, 3, and 4 are £ ^;:, £ 3.

(£, + £ _z + £ ₃ )

 Τ 2 JT (1)

 g ε: Gravitational acceleration If at-z-jg a-S ei, the period of the pendulum in Fig. 2 is 6.02 seconds according to equation (1). This is the same as the period of a 9 m long pendulum of a normal single suspension. In this way, the length of the pendulum, which previously required a length of 9 m, can be reduced to 1/3 of 3 m by dividing it into three.

 FIG. 3 shows a third embodiment of the present invention, which is a three-stage four-point suspension system having a spring.

In the third embodiment, as shown in Fig. 3, the suspension members 2, 3, 4 and the upper suspension frames 5, 6 are swung by 45 '(Fig. 3 (b)). The level of the rims 5 and 6 are arranged in the same horizontal plane to minimize the required space in the height direction. The device according to the third embodiment functions as a damper for vibrations in any direction of 360 'in the plane, and adjusts the frequency in each direction. Of suspension frames 5 ', 6' and weight 1 Springs 9 and 10 are installed between them.

Now, can the length of the hanging Ri material 2, 3, 4 jg zi jg ss spring of the spring constant K _x, when you and K _y is the period T of the pendulum of FIG. 3 in due Ri meter Ki to the following equation .

M

 T 2% T == 2π (2)

 K D X Κ D y

Where the period of the pendulum in the direction T τ X, y (sec)

I o

 : Weight of weight

M D 'g M Dg

 K D X I KV X Ten K D V K Ten

g:! gravitational acceleration Now, jg - je z - fs - S m, MD = 102 kg - sec z / cm, Κ χ = 50 kg / cm, when you and K _y = 100 kg Bruno cm, formula (2 ) Therefore, T _x and T _y are as follows. 0 102 X 980

 K 50 + 161.1 kg / cm

 900

102 X 980

K _{D y} = 100 + 211.1 kg / cm

900 102

 . T x 2 π 5 (sec)

 161.1

102

 Τ = 2π4.4 (s e c)

 211.1

Also, if the amplitude of the conventional type (FIG. 12) is 1.2 m, the amplitude of each pendulum of this embodiment is 1.2 m X l / 3 = 0.4 m, and the required spring strut is 1/3 (± 0.4ηι) of conventional type (± 1.2m)

10 is enough.

 FIG. 4 shows a fourth embodiment of the present invention, which is a three-stage, four-point suspension system having a spring and a damper. The device of the fourth embodiment functions as a damper for vibrations in any direction of 360 in the plane, and adjusts the frequency in each direction.

 I5 springs 9 and 10 are installed between the lower suspension frames 5 'and 6' and the weight 1 for the purpose of I5.

 Also, dangnos, · 8 and 11 are installed between the lower suspension frames 5 'and 6' and the weights.

 Now, if the amplitude of the pendulum of the conventional type (Fig. 12) is 1.2m,

Ζ 0 Correspondingly, the amplitude of the pendulum according to the present invention is only 1/3 of 0.4 m. Therefore, in the case of the conventional type, a large damper with a stroke of ± 1.2 m is required, but in the case of the pendulum according to the present invention, the pendulum according to FIG. From there, you have to use ± 1.2m X l / 3 = ± 0.4m.

5 to 7 show a fifth embodiment of the present invention. 74 PT

15 Fig. 5 (a) shows an example of a two-stage suspension, weight 1 and suspensions 2 and 3, suspension frame 5 and horizontal support bracket 14 for suspension, and way. It consists of a support that protrudes from g. In addition, when the hanging members 2 and 3 are one (one bundle), the hanging member horizontal support brackets 14 are the same as shown in Fig. (B). When the hanging members 2 and 3 are plural, the same. It is supported as shown in Fig. (C), and the other end is supported by a support base 12 or a suspension frame 5 so as to be able to move up and down by bolts. The hanging member is fixed to the bolt 15 via the metal fittings 16, 17 or 18, 19, 20, 21. In this case, the hanging members 2 and 3 may be completely fixed to the bracket 14, or may be supported only in the horizontal direction, and may be free (not supported) in the vertical direction. .

 Fig. 6 shows that the horizontal supports 14 of the hanging members shown in Fig. 5 are divided into two steps, and the period of the pendulum in two directions (X, Y directions) in the plane can be adjusted separately. This is what we did.

 FIG. 6 (a) shows only the hanging member 2 and the metal fitting 14 in FIG. 5, and the metal fitting 14 is connected to the X direction as shown in FIG. 5 (a). 14 Divided into two sets of Y14 for Y direction. Figure (b) shows the X direction X14, which is free to swing in the X direction but free to swing in the Y direction. (C) is the Y direction Y14, which is free in the Y direction but restricted in the X direction.

By attaching the hanging member horizontal support bracket 14 as shown in Fig. 5 to restrain the horizontal displacement of the hanging members 2 and 3, the pendulum is shown in Fig. 7. Vibration like this. That is, The length of the hanging members 2 and 3 above the bracket 14 is the effective length of the pendulum, and the period of the pendulum corresponding to the length can be obtained. Although FIG. 7 shows the movement of only the weight 1, the movement of the suspension frame 5 with respect to the structure 7 in FIG. 5 is also the same.

It is five.

 Similarly, in the example shown in Fig. 6, by changing the mounting position (height direction) of the X-direction bracket and the Y-direction bracket, the X and Y directions are different. be able to .

 FIG. 8 shows a sixth embodiment of the present invention. Two-stage swing,. A weight 1, hanging members 2 and 3, a hanging frame 5, legs 34, and a jacket 35. The suspension frame is composed of an upper suspension frame, a lower suspension frame, and a connecting member.

 FIG. 9 shows a seventh embodiment of the present invention.

This figure constitutes a double-suspended pendulum, and the weight 1 and the hanging members _15, 2 and 3, the hanging frame 5, and the length of the hanging members are changed. It is composed of a hook 44 and a slide jig 45 between the hanging material end, the weight and the hanging frame. Here, the slide jig is fixed to the weight and the suspension frame by the bolt 46, but the slide jig is fixed to the weight and the suspension frame. According to the ingredients

A large number of bolt holes are set up and down with a small pitch at Z0, and the fixing position can be changed according to the length (£) of the hanging material. I can do it. In the present invention, the jig for changing the length of the hanging material and the jig for the slide portion are provided in this embodiment if they have the function. It is not limited.

zs For the slide jig 45 and the turn knock hole 44, The variable length is almost the same, and if the length of the hanging material () is set to the measurement surface length, it is set so that it becomes 1/2 of the variable length. Combing is also short, and combing is also possible. In other words, when changing the period of the pendulum to a long period, the turn knocker 44 is extended so that (£) becomes longer, and the extended amount is used. Lower the jig 45. Conversely, when changing to the shorter cycle side, shorten the turnbuckle 44 to shorten (£) the power and increase the slide jig 45 by the reduced amount. Thus, the cycle can be adjusted without changing the suspension height (L) of the weight and the suspension frame.

 FIG. 10 to FIG. 11 show an eighth embodiment of the present invention.

 Fig. 10 (a) shows a two-stage suspended pendulum, with weight 1, suspension members 2 and 3, suspension frames 5 and 6, turn knob 54 and extension. It consists of a retractable slide mechanism 55.

 The tenth (b) shows an example in which the period of the pendulum is shortened, and when the length of the hanging members 2 and 3 is shortened by the use of the knocker 54, The case where the length of the suspension frame is shortened by the slide mechanism 55 is shown.

 Fig. 10 (c) shows an example in which the period of the pendulum is lengthened, and when the length of the hanging members 2 and 3 is increased by the turn-knocking hole 54, The case where the length of the suspension frame is increased by the slide mechanism 55 is shown.

 The turn knocker 54 of the suspension members 2 and 3 may be a normal turn back knob 44.

The slide mechanism for suspension frames 5 and 6 has a length adjustment Any mechanism that allows adjustment is fine. Fig. 11 shows one example.

 Fig. 11 (a) shows that the upper member 56 and the lower member 57 of the suspension frame can be engaged in a sheath shape, and the bolt holes 58 and 59, which have been drilled in advance, are 5 bolts. This is an example in which 60 are combined. Fig. 11 (b) shows the same way that the upper and lower members of the suspension frame can be engaged in a sheath, and they are installed outside (bolts in this figure) and bolted. This is an example.

 Referring to FIGS. 13 to 15, another set of fruits of the present invention. A vibration damping device according to the embodiment will be described. In FIG. 13, 71 is a weight. The weight 71 is vibrated in order to suppress the vibration of the structure 74. Both ends of this weight 71 are one ends of a bending-rigid hanging member 72 ′, and can be rotated in any direction by the vision joint 75. Supported. In addition, the other end of the hanging member 72 ′ is supported by a suspension frame 73 by a pinion 75 in a moving manner. The suspension frame 73 has a U-shape, and absorbs the vibration energy of the structure 74 between the vicinity of the other end of the suspension member 72 ′ and the suspension frame 73. A damper 76 and a spring 7 are provided to determine the frequency of the pendulum as required.

In addition, both ends of the suspension frame 73 are one ends of suspension members 72 having bending rigidity, and the movement of the suspension frame 73 is performed in all directions by the binding 75. Supported by. Further, the other end 5 of the hanging member 72 is supported by the structure 74 by the vision point 75. A damper 76 for absorbing vibration energy of a structure 74 and, if necessary, a vibration between the vicinity of the other end of the suspension member 72 and the suspension frame 73. 77 The spring 77 for determining the wave number is interposed.

 5 Next, the operation of the embodiment of the present invention configured as described above will be described. First, when the structure 74 vibrates, the weight 71 vibrates with the suspension point B as a fulcrum, and the suspension frame 73 vibrates with the suspension point A as a fulcrum. In other words, the weight 71 and the suspension frame 73 perform a single pendulum motion. Here, the structure

,. The relative displacement between 74 and the hanging member 72 and between the hanging frame 73 and the hanging member 72 'becomes smaller as the position is closer to the hanging point A or B. For this reason, the stroke of the damper 76 and the spring 77 attached between the structure 74 and the hanging member 72, and the hanging frame 73 and the hanging member 72 'are small. It can be done.

_{1 5} primary, you bright theory and had One other embodiment of the present onset bright with reference to Figure 15. In another embodiment, instead of the damper 76 and the spring 77 shown in FIG. 13, a vibration exciter 78 operated by automatic control is provided with a structure 74, a suspension member 72, and a suspension frame 73. This is an example in which it is arranged between hanging members 72 '. According to this other embodiment, even when the st zo stroke of the vibrator 78 is small, it is possible to give the weight 71 a large amplitude. In other words, by detecting the vibration of the structure 74 and controlling the stroke of the vibrator 78, the vibration of the structure 74 is reduced by the vibration energy of the weight 71. To reduce the amount of water absorbed.

B Referring to FIGS. 17 to 25, another alternative to the present invention is shown. A set of embodiments of a damping device is described.

 FIG. 17 is a side view of one embodiment of the present invention, and FIG. 18 is a plan view thereof. In Figs. 17 and 18, 81 is the weight, 82 is the installation floor, 83 is the hydrostatic bearing or stove, 84 is the link 5, and 85 is the universal surge. In FIGS. 17 and 18, reference numeral 86 denotes a vision point, reference numeral 87 denotes a reaction wall, reference numeral 88 denotes a spring, reference numeral 89 denotes an oil reservoir, and reference numeral 81 denotes an installation floor. A weight that is mounted on the base 82 via a hydrostatic bearing or stove 83, and two links 84 are provided between the weight 81 and the installation floor 82. , 0 It can be mounted via a joint 85 and a joint 86.

 Further, a reaction wall 87 erected and fixed on the installation floor 82 is connected to the link 84, and a spring 88 and an oil member 89 are connected to each other.

_{15 In} one embodiment of the present invention, when the weight speed exceeds 60 cm, _s (circular frequency = 1.0 rad / sec and amplitude = 60 cm), the speed is proportional to the square of the speed. In the case of using oil dams, which are the damping characteristics of molds, the relationship between building amplitude and weight amplitude, and the relationship between building amplitude and damping effect (damping effect) on buildings.

₂ 0 coefficient shown in Figure 19. This example aims to reduce the amplitude (several on) of a building generated by winds that normally blow about 10 to 20 m, and to improve the livability, and the building amplitude is 10 cm. In this example, the amplitude of the plumb bob is linearly B and zB up to about 12 cm. At 12 cm the weight amplitude is about 60 cm. this Above, the ratio of the weight amplitude to the building amplitude starts to decrease, and when the building amplitude is 100 ci (corresponding to the amplitude during a large earthquake), the weight amplitude is suppressed to about 160 cm. At this time, the effect of the decay on the building was about 4.5% up to a building amplitude of 12 cm5, but decreased to about 2.2%, about 2.2% at a building amplitude of 100 ci. . However, even in this case, in order to suppress the weight amplitude by using the conventional dynamic dang-no, the reaction force is applied by hitting the sto-no to the building. The extinction effect is secured, though only half, compared to the adverse effects of adding

I 0 is a great advantage. By the way, in the case of the conventional dynamic dang, ', when the building amplitude reaches 100 cm, the weight mass amplitude becomes 500 cm (the same as the ratio up to a building amplitude of 12 η). ), And for both amplitudes, 1000 cn becomes 10 * immediately, making it impossible to design in practice. For this reason, it is necessary to reduce the amplitude for 1 _second, so that a large reaction force is applied to the building, and it will exert a bad shadow. become .

 As shown in Fig. 20, a general speed proportional type oil chamber has a certain speed level V. , The flow rate through the valve begins to be restricted, and automatically becomes proportional to the velocity squared.

Z 0 Normally, use at or below that level. On the other hand, in the present invention, the above-described characteristics are realized by using an oil storage beyond this level. The components should be designed to have sufficient strength so that they can cope with large earthquakes or strong winds with amplitudes exceeding the normal level of use. Fig. 21 shows the case of single pendulum type, Fig. 22 shows the case of multiple pendulum type, Fig. 23 shows the case of tilted pendulum type, Fig. 24 shows the case of inverted pendulum type, Fig. 25 Are examples in which a spring and an oil member are directly attached to the weight, and the operation s and the effect are the same as those described above.

In Fig. 21, 91 indicates a weight, 92 indicates a hanging rod or cable, 93 indicates an oil chamber, 94 indicates a ceiling, and 95 indicates a reaction wall. 22 have you in FIG, 101 weight, 102 suspended Ri bar or to case b le, 103 Oh Lee Noreda down Roh, -, 104 ceiling 105 ₀ Hanchikarakabe, 106 full-les chromatography In FIG. 23, 111 is the weight, 112 is the rod, 112 is the oil chamber, 114 is the wall, 115 is the reaction wall, and in FIG. In FIG. 25, 121 is a weight, 122 is a rod, 123 is an oil nose, 124 is a floor, 125 is a reaction wall, and 126 is a spring. Reference numeral 131 denotes a weight, 132 denotes an opening, 133 denotes an oil nose, · 134 denotes a floor, 135 denotes a reaction wall, and 136 denotes a spring.

 In addition, the speed level at which the above-mentioned square characteristic is obtained is very small, and in an extreme case, it is possible to set the speed level to zero, so that the square characteristic is obtained over the entire speed range. .

. Industrial applicability

 Since the present invention is configured as described above, the following effects can be obtained.

(1) In a multi-stage suspension damper, the required pendulum length is divided into short lengths, so that the total height of the pendulum can be reduced by multi-stage suspension. I can do it. (2) The cycle of the multi-stage suspended vibration damper can be calculated as a normal pendulum having a length obtained by simply adding the lengths of the above-mentioned divided pendulums. Therefore, in comparison with the conventional vibration damping device, the height required to obtain the same cycle as the conventional type can be reduced in the multi-stage suspension vibration damping device. Yes (the greater the number of divisions, the smaller the overall height).

 (3) By adding a spring, the frequency of the pendulum can be freely adjusted while keeping the length of the pendulum constant.

 (4) By installing springs between the suspension frames, it is possible to make the springs smaller in stroke O. The stroke of the damper as an attenuator is lZn in the case of n-stage suspension, as compared with the conventional pendulum.

 (5) The length of the pendulum can be freely adjusted by moving the position of the horizontal support bracket of the hanging member.

 (6) The weight has fallen due to the small gap between the leg 34 and the floor 36 attached to the lower part of the weight. At times, the impact load on the floor 36 can be reduced.

 In addition, the jacket 35 loaded on the legs 34 makes it possible to easily lift the Eight 1 so that installation and maintenance can be performed smoothly.亍 No.

 The weight of the legs 34 and the jacks 35 attached to the lower part of the weight 1 can be counted as a part of the weight of the weight 1.

(7) The length of the hanging material is changed by the turn knockle, and the length of the hanging frame is changed by the slide jig. Without changing the suspension height (L) The cycle can be adjusted. This eliminates the need to prepare large amounts of suspension materials of different lengths without compromising the aesthetics.

 (8) The length of the hanging material is changed by the turn knocking and the length of the hanging frame is changed by the sliding mechanism. The period can be adjusted.

 (9) A rod-shaped member with bending rigidity, both ends of which are supported by pins, is used for the hanging material, and each hanging point between the structure and the hanging material, and the hanging frame and the hanging material is used. By providing a damper and a spring as needed, it is possible to provide a vibration damping device capable of producing a large amplitude with a damper or a spring having a short stroke. And can be done. In addition, if a vibration exciter that can be automatically controlled is placed in the damper, a large vibration can be applied to the vibrating body with a short-stroke vibration exciter. And can be done.

 By using oil ducts whose damping force is proportional to the square of speed above a certain speed level, it can be operated even during large earthquakes or strong winds. Thus, a vibration damping device can be obtained that can suppress the amplitude of the weight while ensuring the vibration damping effect on the building to a certain degree. As a result, the floor space required for installation can be reduced, the need for installation of a stopper is eliminated, and the structure can be economically designed.

Claims

The scope of the claims  1. In a pendulum type vibration damping device consisting of a weight, a spring, a damper, a hanging material, and a mounting frame, a quadrilateral is provided between the mounting frame and the weight. When the above-mentioned weight is suspended in multiple stages, an upper suspension frame and a lower suspension frame are provided, and the upper suspension frame and the lower suspension frame are supported by four connecting members. In addition, the mounting angle of the lower hanging frame quadrilateral with respect to the upper hanging frame quadrilateral is changed so that the hanging members do not overlap.  2. A spring for adjusting the frequency of the pendulum was installed between the hanging members. 10. The vibration damping device according to claim 1, wherein the vibration damping device is characterized in that:  3. The vibration damping device according to claim 1, wherein the damper is provided between the suspension frames.  4. The vibration damping device according to claim 1, wherein a spring for adjusting the frequency of the pendulum and a damper are provided between the suspension frames.  I 5 5. A spring or a damper for adjusting the frequency of the pendulum is provided between the weight and the suspension frame, according to any one of claims 1 to 3, characterized in that: The vibration damping device according to 1.  6. The method according to claim 1, wherein a spring and a damper for adjusting the frequency of the pendulum are provided between the weight and the suspension frame. The vibration damping device according to any one of Z 0 to 3.  7. A method according to any one of claims 1 to 6, characterized in that a hanger horizontal support device for adjusting the frequency of the pendulum is provided between the upper end and the lower end of the hanger. Damping device. 8. A structure in which vibration is suppressed, and a plurality of first structures having bending stiffness, one end of which is supported by the structure to rotate freely. , A suspension frame supported at the other end of the plurality of suspension members by rotation itself, one end of the suspension frame supported by the rotation self, and the like. A plurality of second suspension members whose ends are pivotally supported by the weight, and a plurality of second suspension members; a portion near the one end side of the first suspension members and the structure; and a second suspension member. A vibration damping device characterized by comprising a stroke varying means provided between said one end side of said material and said suspension frame.  9. The vibration damping device according to claim 8, wherein the stroke varying means includes a spring or a damper.  10. The vibration damping device according to claim 8, wherein the stroke varying means comprises a controllable exciter. 1 1. In the dynamic system consisting of a vibration system and an oil dan, the velocity squared at a velocity level above which there is a damping force in °. A vibration damper characterized by using an oil chamber that is proportional.  12. The oil dam according to claim 1, wherein the damping force is an oil dam whose decay becomes proportional to the square of the speed above a certain speed level. The vibration damping device according to any one of the above.