JP2002242988A - Axial force type vibration control device usable for earthquake and wind in common - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an axial force type vibration control device usable for earthquake and wind in common capable of reducing vibration of a structure by deforming metal vibration absorbing material which shows little work hardening from plasticization by an axial force. SOLUTION: An energy absorbing member has both end parts of a long and narrow axial force loading part in a center rounded for preventing stress concentration, and has rectangular attachment parts large enough to transmit load formed at both outside parts. Both surfaces of the attachment part and both end surfaces of the upper and lower axial force loading parts are restricted by a load transmitting frame and a spacer to prevent in-plane buckling and out-plane buckling. The load-transmitting frame is comprised of a male type frame, a female type frame and recessed plate attached to the female frame.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to an energy absorbing member having a material strength having a high strain rate sensitivity, a stable strength against a temperature rise in an energy absorbing process, and a work hardening by plasticization. It belongs to the technical field of an axial force type vibration damping device that uses a metal-based vibration absorbing material that hardly occurs and has a sufficiently large deformation performance and reduces the vibration of a structure by deforming the material by an axial force. The present invention relates to an axial force type vibration damping device that can be used substantially for both earthquakes and winds, and exhibits a necessary and sufficient vibration damping (or vibration damping, the same applies hereinafter) effect.

[0002]

2. Description of the Related Art Conventionally, vibration damping devices for absorbing vibrations of building structures can be roughly divided into (a) a vibration damping device for reducing the shaking caused by an earthquake, and (b) a wind damping device. Vibration damping device that absorbs vibration and improves comfort
Types are used.

[0003] In the field of the hysteretic vibration damping device for the above-mentioned (a) seismic force, conventionally, a large number of vibration damping devices using an extremely low yield point steel as an energy absorbing member have been used.

[0004] A lead-filled type vibration damping device using lead is also provided.
For example, Japanese Patent No. 2647609, Japanese Patent No. 26501
No. 53 is known.

Further, recently, as a superplastic material suitable for an energy absorbing member of a vibration damper, for example, Japanese Unexamined Patent Publication No. 11-2
It is also known to use a zinc-aluminum alloy (Zn-Al alloy) for damping disclosed in Japanese Patent No. 22463. It is known that this superplastic material does not cause work hardening and strain deterioration, and thus has a property of maintaining stable vibration resistance for a long period of time.

Next, as shown in (b) above, a vibration damping device installed for the purpose of reducing the vibration of a high-rise building mainly due to wind is used as an energy absorbing member such as a viscous body or a viscous material (hereinafter referred to as a summary). Vibration damping devices using viscous materials) are well known and used. Vibration damping devices using these viscous materials generally have excellent deformation performance.

[0007]

(I) The hysteresis system of the hysteresis system using the above-mentioned extremely low yield point steel, once subjected to a plastic strain history due to an earthquake or the like, processes the extremely low yield point steel itself. Hardening increases the yield load. Therefore, after the second time,
The energy absorption performance becomes unstable, for example, the elastic region of the extremely low yield point steel becomes longer, and the energy absorption performance decreases. Extremely low yield point steel also suffers from deterioration of its mechanical properties when subjected to plastic strain, making it difficult to grasp its performance during continuous use and failing to maintain the initial vibration damping performance. There are problems such as the need to replace the absorbing member (extremely low yield point steel).

(II) In the case of a lead-filled type vibration damping device using lead, the room temperature strength of lead itself is low, and therefore, the same level of vibration damping performance as a vibration damping device using extremely low yield point steel is realized. Requires a large amount of lead. However, since lead has a large specific gravity, the weight of the entire vibration damping device eventually increases, handling becomes poor, and the load on the structure is large. Furthermore, since lead is a toxic metal, its use is not preferred for environmental protection. In addition, for lead-filled vibration damping devices using lead, a mechanism has been proposed in which lead is sealed to cause equal volume deformation. However, since there is elastic deformation of the stiffening member, complete It is difficult to achieve volume deformation. In addition, lead conducts heat with respect to heat generation due to energy absorption,
The ability to dissipate is poor, and the strength is significantly reduced during repeated deformation. For this reason, it is easy to cause sagging, a gap occurs between the loading member that did not exist in the initial stage of encapsulation, and a problem such as a slip type plastic strain history and unstable vibration resistance performance was pointed out. I have.

(III) Next, a superplastic material "zinc-aluminum alloy (Zn-Al alloy)" disclosed in the above-mentioned Japanese Patent Application Laid-Open No. 11-222643 is used as an energy absorbing member of the vibration damping device. If so, the following considerations must be overcome. That is, this kind of superplastic material is
Since it does not cause work hardening or strain deterioration, stable vibration resistance performance is maintained for a long time. However, on the other hand, a superplastic material having a fine grain structure, “room-temperature high-speed superplastic alloy,” loses the stability of the metallographic structure. Processing method involving large heat input cannot be performed. In addition, the superplastic material "room-temperature high-speed superplastic alloy" has a problem that, when local buckling occurs, "strain concentration" is more likely to occur than the low yield point steel, and the conventional buckling stiffening method cannot be used. . Further, although not so much as lead, superplastic materials have a reduced material strength due to heat generation during energy absorption, and thus heat dissipation measures are an important issue.

(IV) Next, the vibration damping device using the above "viscous material" has a very large temperature dependency of various characteristics, and the heat generation in the energy absorption process causes the rigidity at a temperature rise of several tens of degrees Celsius. In addition, since the damping characteristics and the like are significantly reduced, the damping characteristics are rapidly reduced. For example, in summer and winter, the temperature at which the "viscous material" is exposed varies greatly, so that the damping performance also varies greatly. Therefore, the place where the viscous vibration damping device is installed on the structure is not suitable around the outer wall where the temperature changes drastically, and is limited to a place near the living space where the temperature changes little.
The “viscous material” generally has a small material strength, so that the device itself becomes large. Inevitably, there is a problem that the effective installation space of the structure is further limited.

(V) It should be noted that, in the current vibration suppression technology, a history-based vibration suppression device for an earthquake and a viscous vibration suppression device for a wind must be selectively used for different purposes. There is no single type of vibration control device that can be used substantially for both earthquake and wind, and can exhibit a sufficiently large vibration control effect. It is for the following reasons. For example, a vibration suppression device using extremely low yield point steel,
When designed to plasticize against an external earthquake force,
As a result of giving priority to the purpose of ensuring the deformation performance of the hysteretic energy absorbing material, in extremely small amplitude regions such as wind load for the purpose of improving comfort, use ultra low yield point steel as it is in the elastic region. Therefore, the energy absorbing ability can hardly be exhibited. Conversely, for example, when a vibration damping device using extremely low yield point steel is designed to plasticize against wind for the purpose of habitability, when plasticizing after experiencing an earthquake with a larger amplitude, As described above, in addition to the problem that the deformation performance of the hysteretic energy absorbing material is limited, in terms of function,
Since the strength is increased by the work hardening, only the elastic behavior is exhibited against the external wind force, and problems such as an inability to exhibit an effective energy absorbing ability are caused. Therefore, there is a problem that the energy absorbing member must be replaced. In other words, hysteretic vibration damping devices using ultra-low yield point steel etc. provide both wind external force for the purpose of improving the livability of the building and seismic external force for the purpose of reducing the seismic response of the building. It is impossible to combine functions.

On the other hand, in the case of a vibration damping device using a “viscous material”, since the material strength has a strain rate dependency and the deformation performance is better than that of the hysteresis material, the livability is low. Although it can exhibit energy absorption performance against both wind external force for the purpose of improvement and external force during a large earthquake, it has the following disadvantages. In a large-amplitude region at the time of a large earthquake, heat resistance at the time of energy absorption causes a sudden decrease in proof strength, and vibration control performance is unstable. In addition to the low stress level compared with the extremely low yield point steel, the required number of vibration damping devices becomes extremely large when targeting earthquakes due to the problem of reduced proof stress as described above. Is very difficult to secure. In other words, it is extremely difficult for a viscous vibration control device to have both a wind external force for improving the livability of the building and an earthquake external force for reducing the seismic response of the building. It is. In addition, the conventional axial force type vibration damping device is a so-called friction type, and it is, of course, very difficult to use the same for both earthquake and wind.

(VI) Therefore, an object of the present invention is to provide an axial force type vibration damping device which overcomes all the problems when using the above-mentioned "superplastic material" for an energy absorbing member of the vibration damping device. is there. The next object of the present invention is excellent in deformability,
An axial force type vibration damping device that hardly causes work hardening due to plasticization and uses a metal-based vibration absorbing material that has high strain rate sensitivity as an energy absorbing member, and is devised to maximize the material characteristics. A multi-purpose or multi-functional, vibration-damping performance that works effectively and stably against two types of vibrations caused by wind force and seismic force in building structures, and does not require replacement of energy absorbing members even when subjected to strain history. It is to provide a vibration damping device.

A further object of the present invention is to provide a vibration damping device which has a stable vibration damping function on both sides of minute deformation due to wind and large deformation due to earthquake, which was impossible in the past.

[0015]

Means for Solving the Problems As means for solving the above-mentioned problems of the prior art, an axial force type vibration damping device which can be used for both earthquakes and winds according to the first aspect of the present invention comprises: Material strength has high strain rate sensitivity,
A metal-based vibration-absorbing material that has stable strength against temperature rise in the energy absorption process, hardly causes work hardening due to plasticization, and has a sufficiently large deformation performance. Axial vibration type vibration damping device for reducing vibration of a flat plate, wherein a flat energy absorbing member prevents stress concentration at corners at both ends of a central elongated axial load portion.
Processing is performed, and both outer portions of the corner portion are formed in a fixing portion having a sufficiently large width and length for load transmission, and both surfaces of the fixing portion and upper and lower end surfaces of the axial load portion are load transmitting frames. The movable transmission frame is divided into a male frame and a female frame divided by a concave gap allowing mutual deformation during axial deformation. And a concave plate attached to the female frame, which is capable of coping with deformation due to axial force.

According to a second aspect of the present invention, there is provided the axial force type vibration damping device according to the first aspect, wherein the energy absorbing member has a flat plate shape as a whole, and a central elongated axial force load portion. And a fixing portion on both outer sides thereof, and the corner portions at both ends of the axial force load portion are subjected to R processing to prevent stress concentration.

According to a third aspect of the present invention, in the axial force type vibration damping device according to the first aspect, the male frame constituting the load transmitting frame is one of the fixing portions of the energy absorbing member. And having a flat plate portion having a shape similar to the axial load portion, having a rib at the center of the outer surface of the flat plate portion,
The joint flange is provided at the outer end, and the concave plate is a flat plate having substantially the same shape and size as the other fixing portion of the energy absorbing member, and is formed at the center of one end at the end of the male frame. The female frame has a flat portion having substantially the same shape and the same size as the other fixing portion of the energy absorbing member and the concave plate, and the female frame has a concave portion in which the projected portion can enter. It has a notch into which the rib enters, and a rib formed so as to overlap with the rib, and a joint flange is provided at an outer end of the flat plate.

According to a fourth aspect of the present invention, in the axial force type vibration damping device according to the first aspect, the energy absorbing member is made of a zinc-aluminum alloy.

[0019]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of an axial force type vibration damping device which can be used for both earthquakes and winds according to the first and second aspects of the present invention will be described with reference to the drawings.

FIG. 1 shows an application example in which the axial force type vibration damping device 4 of the present invention is incorporated in a brace 3 installed in the plane of a ramen frame surrounded by beams 1 and columns 2.

Energy is absorbed by the axial force type vibration damping device 4 utilizing the axial force (compression force / tensile force) acting on the brace 3 due to the earthquake or wind load, and the vibration is attenuated (absorbed).
What is done is no different from the conventional axial force type vibration damping device.

FIGS. 2 and 3 show a specific structure of the axial force type vibration damping device 4, and FIG. 4 is an exploded view. The vibration damping device 4 has, as the energy absorbing member 6, a material strength having a high strain rate sensitivity, a stable strength against a temperature rise in an energy absorbing process, and almost no work hardening due to plasticization. Metal vibration absorbing material having sufficiently large deformation performance (hereinafter simply referred to as energy absorbing material).
In this configuration, the energy absorbing material 6 is deformed by an axial force to absorb energy and attenuate the vibration of the structure.

As shown in an exploded view in FIG. 4, the energy absorbing member 6 in the form of a flat plate is made of the above-described energy absorbing member, and stress is concentrated on the corners a at both ends of the central elongated load portion b. The outer sides of the corners a are formed in rectangular fixing portions c and d having a sufficiently large width and length for transmitting a load. In this energy absorbing member 6, the outer surface buckling and the in-plane buckling of both surfaces of the fixing portions c and d and the upper and lower end surfaces of the axial load portion b are restrained by the load transmitting frame 7 and the spacer 14. The structure receives the action of the axial force.

The load transmitting frame 7 is divided into a male frame 8 and a female frame 16 which are bipartitely configured to allow mutual deformation (axial deformation) when the shaft is deformed left and right (back and forth in the axial direction). It is composed of a combination of a concave plate 15 attached to the female frame 16.

As is apparent from FIG. 4, the male frame 8 has flat plate portions 9, 10 formed in a shape similar to the fixing portion c and the axial load portion b on the left side of the energy absorbing member 6.
And a rib 12 arranged outwardly at the center of the outer surface of the flat plate portions 9 and 10, and a joint flange 11 provided at a right angle to the outer end of the flat plate portion 9.

The flat plate portion 9 has the same number of bolt holes 9a at positions corresponding to the bolt holes 6a prepared in the fixing portion c of the energy absorbing member 6 (in the illustrated example, two bolt holes 9a at the upper side and two bolt holes at the lower side). Four, but not limited to this).
The flat plate portion 10 is formed to be wider by the width of the spacer 14 than the width of the axial load portion b of the energy absorbing member 6, and the bolts of the spacers 14 The same number of bolt holes 10a are provided in an arrangement corresponding to the holes 14a.

The spacer 14 has substantially the same shape as the concave portions 6c formed above and below the axial load portion b of the energy absorbing member 6, and has substantially the same plate thickness.

The concave plate 15 has a flat shape of substantially the same shape and size as the fixing portion d on the right side of the energy absorbing member 6.
A concave portion 15b having substantially the same shape and size as the convex portion 13 is formed in the center of the left end, into which the convex portion 13 formed at the tip of the flat plate portion 10 of the male frame 8 enters.

The female frame 16 has a fixing portion d on the right side of the energy absorbing member 6 and therefore a flat plate portion 17 having substantially the same shape and size as the concave plate 15 and the rib 12 of the male frame 8 enter. A notch 17b formed at the center of the left end, a rib 19 formed in a hook shape so as to ride on the rib 12 of the male frame 8, and a right angle to the outer end of the flat plate portion 17. Fitting flange 18 provided
It is composed of

The flat plate portion 17 and the concave plate 15 of the female frame 16 are provided with bolt holes 15a and bolt holes 17a at positions corresponding to the bolt holes 6b prepared in the right fixing portion d of the energy absorbing member 6. Are provided in the same number.

Each of the components described above is a steel structure having necessary and sufficient strength and rigidity, and is similarly prepared on the opposite side so as to sandwich the energy absorbing member 6 of FIG. Construct a damping device. However, the illustration is omitted in FIG. 4 for convenience.

In the vibration damping device shown in FIGS. 2 and 3, the spacer 14 is disposed on the concave portion 6c so as to be in contact with the upper and lower edges of the axial force load portion b of the energy absorbing member 6;
The flat portions 9 and 10 of the male frame 8 are arranged so as to be applied to the planes of the fixing portion c and the axial load portion b of the energy absorbing member 6.

The concave plate 15 is arranged so that the convex portion 13 at the tip of the flat plate portion 10 of the male frame 8 can enter the concave portion 15b.
To the fixing section d. Further, the concave plate 15
The flat portion 17 of the female frame 16 is applied so as to overlap the outer surface of the
Is arranged at a position overlapping with the rib 12.

In this manner, the above-described components are arranged on both sides of the energy absorbing member 6 and the respective bolt holes 9a are formed.
And 6a, 10a and 14a, and 17a and 15a and 6b
Are adjusted to be concentric with each other, and bolts 9b, 10b, and 17c are passed through them, and nuts 9c,
The axial force type vibration damping device 4 is configured by screwing and strongly tightening 10c and 17d.

The axial force type vibration damping device 4 having the above-described structure is joined to the joint flanges 11 and 18 at both ends by bolts with the joint flanges 5 and 5 of the brace 3 shown in FIG. Incorporated into brace 3.

When the axial force type vibration damping device 4 is installed as described above, an earthquake or wind load acts as an axial force (compression force / tensile force) on the energy absorbing member 6 through the brace 3.
It is possible to make full use of the energy absorbing ability and exhibit a vibration damping function that can be used for both earthquake and wind (the invention according to claim 1).

As described above, the energy absorbing member 6 used in the axial force type vibration damping device 4 has a material strength having a high strain rate sensitivity, and the strength is stable with respect to a temperature rise in the energy absorbing process. It is a metal-based vibration-absorbing material that hardly causes work hardening due to plasticization and has sufficiently large deformation performance (hereinafter, abbreviated as material M). Specifically, the zinc-aluminum alloy described above is used. Can be applied (the invention according to claim 4).

The "material M" used for the energy absorbing member 6 of the axial force type vibration damping device 4 is a metal material having a high strain rate dependency of strength, and does not deteriorate in strain and has a high deformation performance. Because it is an energy-absorbing material that excels in heat and has a small decrease in strength due to heat generation during the energy absorption process, it is practically impossible to achieve both “small deformation due to wind” and “large deformation due to earthquake”. Demonstrate excellent energy absorption ability. Moreover, it is possible to provide a vibration damping device that does not require replacement of the energy absorbing member 6 after the history.

The reason is that the vibration damping device incorporating the energy absorbing member 6 made of the above-mentioned "material M" has an advantage that the energy absorbing member 6 yields early and becomes plastic in a low strain rate and small deformation region such as wind. Exhibits an energy absorbing effect. on the other hand,
In a high strain rate / large deformation region such as an earthquake, the strength increases due to the strength strain rate sensitivity of the energy absorbing member 6, so that yielding and plasticization can be delayed, and an extremely large energy absorbing ability is exhibited. In addition, unlike the conventional hysteresis type vibration damping device, there is almost no problem that, once plasticized, work hardening occurs. Therefore, this damping device
Demonstrates energy absorption capacity according to the external force level input to the building structure. This concept is illustrated in FIG. In the case of the “material M”, any mechanism such as compression-tension, shear, torsion, or bending deformation may be used as a mechanism for applying a plastic strain to the energy absorbing member 6. Further, it can be seen that the configuration of the vibration damping device may be any of an axial force type, a shear panel type, a stud type and the like, and is not particularly limited.

The above-mentioned "material strength has high strain rate sensitivity" is specifically desirably a material having a strain rate sensitivity index m of 0.3 or more. Here, m = (Lnσ ₂ /
Lnσ ₁ ) / (Lnv ₁ / Lnv ₂ ). σ ₁
Is a flow stress of the material M at the time of the strain rate v _1,
σ ₂ is the flow stress of “Material M” when the strain rate is v ₂ , and has a relationship of v ₂ > v ₁ . FIG. 6 shows this state.

The above-mentioned “material whose strength is stable against a temperature rise in the energy absorption process” means that, when compared at the same deformation rate, the rate of decrease in the material strength at around 100 ° C. is near room temperature. (Approximately 20 ° C.) means that the strength is within 30% of the material strength.

"Material that hardly causes work hardening due to plasticization" means that there is almost no increase in material strength due to plastic strain history.

Further, "material having sufficient deformation performance"
Is a material having a ductility of 100% or more in a static tensile test at room temperature. If the material has such a large ductility, large deformation can be allowed as the energy absorbing member 6.

The energy absorbing member 6 that satisfies all of the above conditions is specifically Zn, which is a room-temperature high-speed superplastic material.
-Al alloy (JP-A-11-222643) can be exemplified.

The first drawback of the "material M" having the above energy absorption characteristic is that, since welding cannot be performed, a force transmission mechanism by welding cannot be used. Room-temperature high-speed superplastic alloys such as Zn-Al alloys are characterized by having a fine crystal grain structure, and the stability of the metal structure is lost due to welding heat input, and as a result, energy absorption capacity cannot be exhibited. . Second, since the material is not work-hardened, it is weak against buckling and stress concentration, and special consideration is required. Because it is a material that does not work harden, stable vibration resistance performance lasts for a long time, but on the contrary, if buckling deformation or stress concentration occurs extremely, local deformation concentrates, which is truly superplasticity This is because even materials are destroyed.

The present invention has been achieved by overcoming the first and second drawbacks. In particular, the following improvements are important. 1) A force transmission mechanism other than welding was used to transmit the force from the load transmission frame 7 to the energy absorbing member 6. 2) The energy absorbing member 6 processed into a shape that avoids stress concentration causes axial deformation. 3) A versatile and high-performance axial force type vibration damping device having a mechanism and function capable of maximally restraining and stiffening the buckling of the energy absorbing member 6 generated during axial deformation.

In addition, the above-mentioned metal-based vibration absorbing material used as the energy absorbing member 6, ie, “Material M” is a harmless metal and has a specific gravity that is about half that of lead, so that it is lightweight and safe. An environmentally friendly vibration damping device can be provided.

Also, since the thermal conductivity is better than that of lead,
There is an advantage that the temperature rise of the material due to the strain is small. In particular, the above-mentioned Zn-Al alloy is much more excellent in room temperature strength and plastic deformation ability than lead, so that its properties are optimally used for a vibration damping device.

[0049]

Next, an embodiment of a vibration damping performance test performed using the vibration damping device having the above-described configuration will be described. The energy absorbing member 6 used is the above-mentioned Zn-Al alloy, and its size is width × thickness × length 45 × 15 × 200 mm.
The test conditions are as follows: The building has a natural period of 4 s (constant), and the vibration damping device is installed between braces (L = 5650 mm) provided at an angle of 45 ° on a frame with a height of 4.0 m. The working section of the alloy is 600 mm.

The interlayer deformation angle during a level 2 earthquake is 1 /
100, then ± 3.0% of maximum distortion in brace
And

FIG. 7 shows load-deformation history characteristics obtained by sine wave excitation. FIG. 8 is a table showing the test results.

The excitation frequency was set to 0.25 Hz, and the amplitude was changed. As a result, the energy absorption capacity of the vibration damping device changes from small amplitude to large amplitude according to the amplitude, and in the small amplitude range assuming wind load, plasticity is early with low stress and the energy absorption ability is exhibited. However, in a large-amplitude region assuming an earthquake, the stress becomes high, indicating an ideal property capable of exhibiting a high energy absorption capacity according to an external force. In addition, the axial strain rate acting on the braces was reduced, so that the plasticity was quickly formed, and it was confirmed that there was an energy absorbing ability even when the interlayer deformation angle was 1/3000. Even in the small-amplitude region after the large-amplitude experience, the reproducibility of the history is good, indicating that it is a vibration damping device that can be used for multiple purposes with almost no work hardening and that can be used for a long time without replacement. .

FIG. 9 is a graph showing the vibration damping effect of a very low yield point steel (open circles) and the vibration damping device using the material M of the present invention for the energy absorbing member 6 (black circles). A comparison is shown. It is clear that the vibration damping device of the present invention exerts a good vibration damping effect on both earthquake and wind.

Although the embodiments have been described with reference to the drawings, the present invention is not limited to the illustrated examples, but may be applied to design changes and application variations that are normally performed by those skilled in the art without departing from the technical idea thereof. Mention is made to include ranges.

[0055]

[Effects of the present invention] The axial force type vibration damping device which can be used for both earthquakes and winds according to the inventions according to the first to fourth aspects has an energy absorbing capability varying from small amplitude to large amplitude according to the amplitude, In a small-amplitude region where a wind load is assumed, plasticization is early performed with low stress and energy-absorbing ability is exhibited. In addition, a large amplitude assuming an earthquake results in a high stress, exhibiting an ideal performance such as exhibiting a high energy absorbing ability according to an external force. The reproducibility of the history is good even in the small-amplitude area after the large-amplitude experience. it can.

In short, it exhibits excellent deformation performance even during an earthquake, and has a response reduction effect almost equivalent to that of the hysteresis type vibration damping device. Also, in the case of wind power, the response is smaller than that of a vibration damping device having no speed sensitivity. This means that the resistance of the damping device, which is indicated by the decrease in strain rate, decreases.
Because it is plasticized at an early stage, the energy absorbing effect is effectively exhibited.

[Brief description of the drawings]

FIG. 1 is an elevation view showing an application example of a vibration damping device according to the present invention.

FIG. 2 is a front view showing an embodiment of the vibration damping device according to the present invention.

FIG. 3 is a plan view of FIG. 2;

FIG. 4 is an exploded perspective view of FIG. 2;

FIG. 5 is an explanatory diagram showing a state in which a material M exhibits an energy absorbing ability according to an input external force level.

FIG. 6 is an explanatory diagram showing a state of a flow stress of a material M.

FIG. 7 is a graph showing the story deformation angle at the earthquake level and the maximum axial strain (%) generated at that time.

FIG. 8 is a table showing an interlayer deformation angle at an earthquake level and a maximum axial strain (%) generated at that time.

9 (a) to 9 (h) are performance diagrams showing a vibration damping effect of the vibration damping device of the present invention.

[Explanation of symbols]

 Reference Signs List 6 Energy absorbing member (superplastic material) 4 Axial force type vibration damping device b Axial force load part a R processing c, d Fixing part 7 Load transfer frame 14 Spacer 8 Male frame 9 Female frame 15 Concave plate

 ──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Kotaro Toyama 1-5-1, Otsuka, Inzai City, Chiba Prefecture Inside the Technical Research Institute, Takenaka Corporation (72) Inventor Satoru Aizawa 1-5-1, Otsuka, Inzai City, Chiba Prefecture Inside Takenaka Corporation Technical Research Institute Co., Ltd. (72) Inventor Koichi Makii 1-5-5 Takatsukadai, Nishi-ku, Kobe City, Hyogo Prefecture Inside Kobe Steel, Ltd.Material Research Laboratory Co., Ltd. 1-5-5 Takatsukadai F-term in Kobe Steel, Ltd. Materials Research Laboratory Co., Ltd. (Reference) 2E002 FA02 MA12 MA13 3J048 AA04 AB01 BC09 DA06 EA38

Claims (4)

[Claims] As an energy absorbing member, the material strength has a high strain rate sensitivity, the strength is stable against a temperature rise in an energy absorbing process, and hardly causes work hardening due to plasticization. An axial-force-type vibration damping device that uses a metal-based vibration-absorbing material having large deformation performance and reduces the vibration of a structure by deforming the metal-based vibration-absorbing material. The corners at both ends of the portion are subjected to R processing to prevent stress concentration, and portions outside both sides of the corners are formed in a fixing portion having a width and length sufficiently large for load transmission, and both sides of the fixing portion and The upper and lower end faces of the axial force load portion are restrained from buckling out of the plane and buckling in the plane by the load transmission frame and the spacer, and the movable transmission frame has a concave gap that allows mutual deformation during axial deformation. Mediation It is composed of a male frame, a female frame, and a concave plate attached to the female frame, and is capable of coping with deformation due to axial force. Shaking device. 2. The energy absorbing member has a flat plate shape as a whole and includes an elongated axial load portion in the center and fixing portions on both outer sides of the central load portion, and prevents energy concentration at corners at both ends of the axial load portion.
The axial force type vibration damping device which can be used for both earthquakes and winds according to claim 1, characterized in that the vibration damping device is processed. 3. A male frame constituting a load transmitting frame has a flat plate portion having a shape similar to one of the fixing portion and the axial load portion of the energy absorbing member, and a rib is provided at a central portion of an outer surface of the flat plate portion. The joint plate is provided at the outer end, and the concave plate is a flat plate having substantially the same shape and the same size as the other fixing portion of the energy absorbing member. The female frame has a concave portion into which the convex portion formed at the tip can enter, and the female frame has a flat portion having substantially the same shape and size as the other fixing portion of the energy absorbing member and the concave plate, and A notch portion into which the rib of the mold frame enters, and a rib formed so as to overlap with the rib, wherein a flange for joint is provided at an outer end of the flat plate portion. Can be used for the earthquake and wind described in Item 1 Power-type vibration control device. 4. The axial force type vibration damping device according to claim 1, wherein the energy absorbing member is a zinc-aluminum alloy.