JP2013152011A - Rotating inertia mass damper, brace damper and brace frame - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotating inertia mass damper which is compact and light-weighted, can obtain a large inertial mass effect, has a simple structure and can be inexpensively manufactured, and a brace damper and a brace frame comprising the same.SOLUTION: A rotating inertia mass damper includes a first ball screw mechanism 20 having a first nut 23 screwed with a first screw shaft 21 via a first ball screw 22, a second ball screw mechanism 30 having a second nut 33 screwed with a second screw shaft 31 via a second ball screw 32, and a rotation weight 40 which couples both screw shafts together and rotates integrally. While the first screw shaft and the second screw shaft relatively displace axially with respect to the first nut and the second nut by relative vibration occurring between two members to be damped, all of the first screw shaft, the second screw shaft and the rotation weight can rotate integrally. The first ball screw 22 and the second ball screw 32 are the same in orientation and have their leads Land Ldifferent from each other. The rotating inertial mass damper is disposed in a frame as a brace.

Description

  The present invention relates to a rotary inertia mass damper, a brace damper thereby, and a brace frame.

  A rotary inertia mass damper is a device that generates the amount of rotation of a weight member in proportion to the relative displacement at both ends of the damper. It is a device with

  As a specific example of this type of rotary inertia mass damper, as shown in Patent Document 1, a type called a damping piece combining a ball screw mechanism and a rotary weight (flywheel) is known. According to this, the mass effect is 1000 times greater than the actual weight mass.

For example, in a damper having a configuration in which a rotating weight (disk-shaped flywheel) is rotated by a set of ball screw mechanisms, a change in the angular momentum generated in the rotating weight due to the rotating inertia moment I _θ and the rotating angular acceleration A of the rotating weight. An axial inertial resistance force P is obtained. In that case, when the ball screw lead (thread pitch) L _d , the axial displacement x of the damper, and the rotation angle θ of the weight,

Thus, the burden force (control force) P of the damper is expressed by the following equation.

Here, assuming that the rotating weight (flywheel) is an annular disk and its outer diameter D ₁ , inner diameter D ₂ , thickness t, and density ρ, the rotational inertia mass moment I _θ and damper burden force P of the rotating weight are Each is expressed by the following equation depending on the mass m of the rotating weight.

This type of large-capacity rotary inertial mass damper generally has D ₁ / L _d > 15.

It becomes. This indicates that an inertial mass effect (ratio of burden force to relative acceleration) that is 1000 times or more the actual mass m of the rotating spindle can be obtained.

JP-A-11-201224

As described above, a rotary inertia mass damper using a ball screw mechanism is widely used because it can obtain a relatively large inertial mass effect even if it is small, but it can obtain a larger inertial mass effect. It is also desired to develop a rotary inertia mass damper that is possible and a rotary inertia mass damper that is further reduced in size with the same inertia mass effect. To that end, the outer diameter D ₁ of the rotary weight is increased as much as possible, or a ball It is considered effective to make the screw lead L _d as small as possible.

However, the very large outer diameter D ₁ of the rotary weight is not preferable because the size of the apparatus.
Also, when simply reducing the lead L _d, the diameter of the ball bearing disposed in the screw groove becomes small, strength per one If load resistance decreases (the bearing diameter decreases sharply decreases, the same load-bearing it is necessary to increase the length of the ball nut in order to obtain, since it can not be made compact), from the viewpoint of securing the load force P of the damper is also difficult to too small screw lead L _d.

  The present invention has been made in view of the above circumstances, and it is not necessary to increase the outer diameter of the rotary weight, and it is not necessary to reduce the lead of the ball screw, so that an effective and appropriate rotation capable of obtaining a large inertial mass effect can be obtained. It is an object of the present invention to provide an inertia mass damper, and also to provide an effective and appropriate brace damper and a brace frame by the rotary inertia mass damper.

  According to a first aspect of the present invention, the first member and the second member are interposed between a first member and a second member, which are structures to be controlled, which generate relative vibrations in directions away from each other. A rotary inertia mass damper for reducing the relative vibration generated therebetween, wherein a first nut is screwed to a first screw shaft via a first ball screw, and the first member is A first ball screw mechanism coupled to the second member, and a second ball screw coupled to the second member, the second nut being screwed to the second screw shaft via the second ball screw. The first nut in the first ball screw mechanism can be non-rotatably connected to the first member, and the second nut in the second ball screw mechanism can be connected to the second member. It is possible to connect non-rotatably to the front The tip end of the first screw shaft in the first ball screw mechanism and the tip end of the second screw shaft in the second ball screw mechanism are arranged to face each other with a space therebetween, and a rotating weight is arranged between them. By connecting a weight with respect to the first screw shaft and the second screw shaft, the first screw shaft and the second screw shaft are caused by the relative vibration generated between the first member and the second member. The first screw shaft, the second screw shaft, and the rotary weight can be rotated together integrally while being relatively displaced in the axial direction with respect to the first nut and the second nut, and the first nut The first ball screw in the ball screw mechanism and the second ball screw in the second ball screw mechanism are formed as ball screws having the same axis and the same direction and different leads.

  The invention according to claim 2 is the rotary inertia mass damper according to claim 1, wherein the rotary weight is integrally connected to the first screw shaft and the second screw shaft so as not to rotate relative to each other. A transmission member, and a weight body that is mounted so as not to rotate relative to the outer periphery of the torque transmission member and to be axially displaceable, and the weight body is connected to the first nut or the second nut. It is connected so that it can rotate but cannot be displaced in the axial direction.

  The invention according to claim 3 is the rotary inertia mass damper according to claim 1 or 2, wherein the rotary weight is transmitted between the first screw shaft and the second screw shaft. When the torque exceeds a predetermined limit value, the rotary weight is connected to the first screw shaft and the second screw shaft via a torque limiting mechanism that limits torque transmission by rotating relative to the first screw shaft and the second screw shaft. Features.

  The invention according to claim 4 is a brace damper provided with the rotary inertia mass damper according to claim 1, 2 or 3 in the form of a brace in the frame of a building, wherein the first of the rotary inertia mass dampers The base end of the first connecting member is integrally connected to one nut, and the base end is integrally connected to the second connecting member to the second nut. Each of the distal ends of the second connection members is configured to be connectable to the frame.

  The invention according to claim 5 is a brace frame in which the brace damper according to claim 4 is installed in the frame of a building, and the tip of the first connection member or the second connection member and the frame A fail-safe mechanism for limiting an excessive input to the rotary inertia mass damper is interposed therebetween.

  A sixth aspect of the present invention is the brace frame according to the fifth aspect, wherein the fail-safe mechanism is a steel damper that yields when the excessive input occurs.

The rotary inertia mass damper of the present invention uses a combination of two ball screw mechanisms having different ball screw leads, and sets the difference between the two leads to a small value, thereby reducing the displacement of each ball screw mechanism relative to the damper stroke. It has a displacement amplification function that can greatly expand, and such a displacement expansion function is also a speed increasing function that increases the rotational speed of the ball screw. Even if the outer diameter and the overall length of the damper are not increased, an effect equal to or greater than that obtained can be obtained, and a large inertial mass effect can be obtained.
In particular, the rotary inertia mass damper of the present invention can directly fix the ball nut of each ball screw mechanism in a state in which the relative rotation is restricted with respect to the structure to be controlled. Since the mechanism does not need to be accommodated in the casing, the overall configuration is extremely simple, a sufficiently small size and light weight can be achieved, and it can be manufactured at low cost.

The brace damper and the brace frame of the present invention are the above-described rotary inertia mass mass as well as providing an excellent vibration control effect because the rotary inertia mass damper is installed in the form of a brace in the building frame. When installing the damper, there are fewer dimensional constraints in the axial direction of the material, and even if the overall length of the damper is slightly increased due to the extra length, it is difficult to cause a problem.
In particular, by joining the rotary inertia mass damper to the frame via a fail-safe mechanism such as a steel damper, the burden force can be peaked even when an unexpected excessive input is applied. Therefore, it is not necessary to provide an overload prevention mechanism in the rotary inertia mass damper itself, and the structure can be greatly simplified as compared with a conventional damper equipped with the mechanism, and a fail-safe mechanism can be realized at a low cost.

It is a longitudinal section showing an embodiment of a rotation inertia mass damper of the present invention. It is a figure which shows other embodiment of the rotation inertia mass damper of this invention, Comprising: (a) is a longitudinal cross-sectional view, (b) is a cross-sectional view. It is a longitudinal cross-sectional view which shows further another embodiment of the rotary inertia mass damper of this invention. It is a longitudinal section showing an embodiment of a brace damper of the present invention. It is a figure which shows embodiment of the brace frame of this invention. It is a figure which shows an example of the steel material damper as a fail safe mechanism in embodiment of the brace frame of this invention, (a) is a front view, (b) is a side view. It is a figure which shows the other example of the steel material damper as a fail safe mechanism in embodiment of the brace frame of this invention, (a) is a front view, (b) is a side view. It is a longitudinal cross-sectional view which shows schematic structure of the rotary inertia mass damper of the prior invention used as the foundation of this invention.

Prior to the description of the embodiments of the present invention, the rotary inertia mass damper of the prior invention, which is the basis of the present invention, will be described with reference to FIG.
This was previously proposed by the present applicant as Japanese Patent Application No. 2010-141838, and two sets of ball screw mechanisms having different ball screw leads, that is, the first ball screw mechanism 20 and the second ball screw mechanism 30 are connected to the casing 10. It is incorporated in a state of being coaxially opposed to each other, and one rotary weight 40 is rotated by the first ball screw mechanism 20 and the second ball screw mechanism 30 so that the damper itself has a displacement expanding function and a speed increasing function. It is what has.

That is, the rotary inertia mass damper of the prior invention shown in FIG. 8 is interposed between two members (a first member and a second member, both not shown) that are structures to be controlled. The first casing 12 is connected to the first member (left side in the drawing) through the clevis 11 so as not to rotate, and the other (shown in the drawing). A second casing 14 that is non-rotatably connected to the second member on the right side) via a clevis 13, and the second casing 14 is axially connected to the first casing 12 via a slide mechanism 15. A casing 10 that is mounted so as to be relatively displaceable and relatively non-rotatable to form an entire outer shell is configured.
In the casing 10, a first ball screw mechanism 20 connected to the first casing 12 and a second ball screw mechanism 30 connected to the second casing 14 are accommodated. A rotary weight 40 is connected to the one ball screw mechanism 20 and the second ball screw mechanism 30.

The first ball screw mechanism 20 includes a first screw shaft 21 and a first nut 23 screwed to the first screw shaft 21 via a first ball screw 22, and the first nut 23 is a first nut 23. It is installed in a state where it is fixed with respect to one casing 12 so as not to rotate but to displace axially.
Similarly, the second ball screw mechanism 30 includes a second screw shaft 31 and a second nut 33 screwed to the second screw shaft 31 via a second ball screw 32, and the second nut. 33 is installed in a state in which it is fixed to the second casing 14 so that it cannot rotate but cannot be displaced in the axial direction.

  The first screw shaft 21 in the first ball screw mechanism 20 and the second screw shaft 31 in the second ball screw mechanism 30 are arranged to face each other with a gap in the center portion of the casing 10 in a state where the axes are aligned. Between the first screw shaft 21 and the second screw shaft 31, a cylindrical (horizontal disk-shaped) rotary weight 40 is disposed, and both ends thereof are the tips of the first screw shaft 21 and the second screw shaft 31, respectively. The outer peripheral surface of the rotary weight 40 is supported via a bearing 41 so as to be rotatable and axially displaceable with respect to the first casing 12.

As a result, the first screw shaft 21, the second screw shaft 31, and the entire rotary weight 40 connecting them can be integrally rotated, and the first member and the second member, which are the structures to be controlled, can be obtained. When the relative vibration in the direction of separation between them occurs, the entire length of the casing 10 changes so as to expand and contract, and the first nut 23 and the second nut 33 are separated from each other while maintaining a coaxial state. The first screw shaft 21, the second screw shaft 31, and the entire rotary weight 40 are rotated with relative displacement in the axial direction with respect to the first nut 23 and the second nut 33. It has become.
In this case, the first screw shaft 21, the rotary weight 40, and the second screw shaft 31 are not shown in contact with the casing 10 and can be displaced in the axial direction without any trouble inside the casing 10. As described above, a clearance corresponding to at least an operation amount (relative displacement amount S ₁ described later) of the first ball screw mechanism 20 is secured between the first nut 23 and the rotary weight 40, and the first nut 23 and It is necessary to ensure twice the clearance between the casing 12 and the casing 12. Similarly, a clearance corresponding to at least the operation amount of the second ball screw mechanism 30 (same relative displacement amount S ₂ ) is secured between the second nut 33 and the rotary weight 40, and the second nut 33 and It is necessary to secure a clearance twice that of the second casing 14.

The first ball screw 22 in the first ball screw mechanism 20 and the second ball screw 32 in the second ball screw mechanism 30 are formed in the same direction (both are right-hand screws in the illustrated example). The lead L _{d1 of the} screw 22 and the lead L _d2 of the second ball screw 32 are different from each other (L _D1 > L _{d2 in the} illustrated example), so that the inertial inertial mass damper itself has a displacement expansion function. It is supposed to have a speed increasing mechanism.

That is, for example, if a displacement x occurs at both ends of the damper and the first nut 23 fixed to the first casing 12 is displaced to the right by L _{d1 for} one lead, the first screw shaft 21 and the rotary weight 40 and the entire second screw shaft 31 rotate once, and accordingly, the second nut 33 is displaced to the right by L _{d2 for} one lead, so that the total length of the damper changes by L _d1 -L _d2 .
In this case, when the damper stroke is S, the operation amount of the first ball screw mechanism 20 (the relative displacement amount of the first screw shaft 21 with respect to the first nut 23) S ₁ and the operation amount of the second ball screw mechanism 30 (first The relative displacement amount (S ₂ ) of the second screw shaft 31 with respect to the two nuts 33 is expressed by the following equations, respectively, and both are enlarged with respect to the damper stroke S.
In other words, the first ball screw mechanism 20 and the second ball screw mechanism 30 operate greatly according to the respective leads L _d1 and L _d2 , but the damper stroke S which is the expansion / contraction amount of the damper as a whole is determined by the first ball screw mechanism. operation amount S ₁ of mechanism 20 to become the difference (absolute value) between the operation amount S ₂ of the second ball screw mechanism 30.

In this case, when the rotational inertia moment I _θ of the rotary weight 40 and the damper displacement x are given, the damper burden force P is

This is obtained by replacing L _d (the denominator in parentheses) in the above equation (1) with L _d1 −L _d2 , that is, a damper by a single ball screw mechanism in which the lead L _d is L _d1 −L _d2. Thus, the effect of sufficiently expanding the damper load force P is obtained, and the effect becomes more prominent as the lead difference L _d1 −L _d2 is smaller.

As a specific example, for example, when L _d1 = 25 mm and L _d2 = 20 mm, it is equivalent to the case of using a single ball screw mechanism with a small lead with a lead L _d = L _d1 −L _d2 = 5 mm. .
In this case, when the damper stroke S = 60 mm, the relative displacement amount S ₁ of the first screw shaft 21 with respect to the first nut 23 = 300 mm and the relative displacement amount S ₂ of the second screw shaft 31 with respect to the second nut 33 according to the above formula. = 240 mm.
In this case, assuming that the length of the rotating weight 40 (thickness t as a disk) is 600 mm, the outer diameter D ₁ of the rotating weight 40 is 350 mmφ, and the inner diameter (the first screw shaft 21 and the second screw shaft 31 pass through. If D ₂ = 150 mmφ, the mass m of the rotary weight 40 is 0.37 ton and the rotary moment of inertia I _{θ is} 6.71 × 10 ⁻³ ton · m ^2. Is over 10,000 tons from the following formula.

Such a large inertial mass [psi, the read L _d is to be realized by the rotational inertia mass damper according to the prior common single ball screw mechanism is limited to be about 16 mm, the required outside of the rotary spindle 40 Since the diameter is 630mmφ, it can be considerably more compact, lighter, and less expensive.

As described above, the rotary inertia mass damper shown in FIG. 8 uses a combination of two sets of ball screw mechanisms having different ball screw leads, and sets the difference between the two leads to be small. It has a displacement amplification function that can greatly increase the operation amount (relative displacement amount S ₁ , S ₂ of each ball screw shaft with respect to each ball nut) with respect to the damper stroke S. At the same time, it is a speed increasing function for increasing the rotational speed of both ball screws. Therefore, a large inertial mass effect can be obtained without actually reducing the leads L _d1 and L _d2 of both the ball screw mechanisms and without excessively increasing the outer diameter D ₁ and the total length of the damper 40 of the rotary weight 40. It is sufficiently effective in this respect.

However, since the configuration shown in FIG. 8 is a configuration in which the entire first ball screw mechanism 20, the second ball screw mechanism 30, and the rotary weight 40 are accommodated in the casing 10, the configuration as a damper is slightly complicated. In addition, it is not always easy to reduce the size and weight, and there is still room for improvement in that respect.
That is, the rotary inertia mass damper shown in FIG. 8 needs to have a configuration in which the entire casing 10 is combined with the first casing 12 and the second casing 14 through the slide mechanism 15 so as to be axially displaceable and relatively non-rotatable. There is. Further, the first nut 23 and the second nut 33 need to be firmly fixed to the casing 10 in a non-rotatable state, and the rotary weight 40 can be rotated with respect to the casing 10 and can be axially displaced. It is necessary to support the bearing 41. Furthermore, since clearances corresponding to the relative displacement amounts S ₁ and S ₂ are necessary on both sides of both the first ball screw mechanism 20 and the second ball screw mechanism 30, it is also necessary to allow a sufficient length of the casing 10. is there

  Therefore, in the present invention, the casing is omitted as shown in FIG. 1 in order to realize further simplification and miniaturization of the configuration while following the basic configuration of the rotary inertia mass damper of the prior invention shown in FIG. Is the main focus.

  That is, in the rotary inertia mass damper A of the present embodiment shown in FIG. 1, the casing 10 and related elements in the rotary inertia mass damper of the prior invention shown in FIG. The first nut 23 can be directly connected to a first member (not shown) which is one structure to be controlled, and the second nut 33 in the second ball screw mechanism 30 is connected to the other structure. It can be directly connected to a second member (not shown).

In that case, it is necessary to firmly fix the first nut 23 and the second nut 33 in a non-rotatable state by fastening the bolts to the first member and the second member, respectively. In addition, it is necessary to ensure a clearance that does not restrain the displacement of the first screw shaft 21 and the second screw shaft 31 in these connecting portions. For this purpose, the operation amount of the first ball screw mechanism 20 between the first nut 23 and the first member (the relative displacement amount S ₁ of the first screw shaft 21 with respect to the first nut 23) corresponds to at least twice. A clearance is ensured and corresponds to at least twice the operation amount of the second ball screw mechanism 30 between the second nut 33 and the second member (the relative displacement amount S ₂ of the second screw shaft 31 with respect to the second nut 33). It is necessary to ensure clearance.
Alternatively, instead of directly fixing the first nut 23 and the second nut 33 to the first member and the second member as described above, an appropriate connecting member (shown by a broken line) is used if necessary. Or by using an appropriate clevis or ball joint. In that case, the clearances described above with respect to the connecting portion for the first member and the second member using the connecting member, clevis, and ball joint are used. Can also be secured.

Also in the rotary inertia mass damper A of the present embodiment, the first screw shaft 21 rotates while being displaced relative to the first nut 23 in the axial direction according to the lead L _d1 of the first ball screw 22, and The second screw shaft 31 rotates relative to the second nut 33 while being relatively displaced in the axial direction according to the lead L _d2 of the second ball screw 32, and the first screw shaft 21, the second screw shaft 31, and their The entire rotary weight 40 connected between them is rotated together.
Thus, according to the rotary inertia mass damper A of the present embodiment, the casing 10 is omitted in addition to the above-described effects obtained by functioning similarly to the rotary inertia mass damper of the prior invention shown in FIG. As a result, the overall configuration can be further simplified, miniaturized, and the cost can be reduced.

  Incidentally, since the casing 10 in the rotary inertia mass damper of the prior invention shown in FIG. 8 is omitted, naturally the bearing 41 for supporting the rotation of the rotary weight 40 is also omitted, but the rotary weight 40 is rotated. There is no particular problem in making it happen.

FIGS. 2A and 2B show a rotary inertia mass damper B which is another embodiment of the present invention.
This is because the rotary weight 40 has a double structure composed of a torque transmission member 40a and a weight main body 40b, and the torque transmission member 40a is integrally connected to the first screw shaft 21 and the second screw shaft 31 so as not to be relatively rotatable. The weight main body 40b is attached to the outer periphery of the weight main body 40b so as not to be rotatable relative to the axial direction, and the weight main body 40b is attached to the first nut 23 with a bearing 42 and a connecting member 43 as shown in FIG. It is set as the structure connected via the shaft so that rotation was possible and the axial direction relative displacement was impossible.

In the case of the rotary inertia mass damper A of the embodiment shown in FIG. 1, the rotary weight 40 is displaced relative to both the first nut 23 and the second nut 33 in the axial direction. It is necessary to ensure a clearance corresponding to the relative displacement amount S ₁ between the nut 23 and a clearance corresponding to the relative displacement amount S ₂ between the nut 23 and the second nut 33. On the other hand, according to the rotary inertia mass damper B of the present embodiment shown in FIG. 2, only the torque transmission member 40 a is displaced in the axial direction, and the weight body 40 b is relatively displaced with respect to the first nut 23 and the second nut 33. Therefore, it is sufficient to secure a clearance corresponding to the damper stroke S between the second nut 33 and the entire length of the damper can be further reduced accordingly.
In the embodiment shown in FIG. 2, the torque transmission member 40a has a hexagonal cross section as shown in FIG. 2B, and the weight body 40b is non-rotatably fitted thereto. It is only necessary to connect in a state in which relative rotation is impossible and axial relative displacement is possible, and so long as the weight main body 40b is attached to the torque transmission member 40a as appropriate.
In addition, instead of connecting the weight main body 40b to the first nut 23 as shown in (a), it may be connected to the second nut 33. In this case, the weight main body 40b and the first nut may be connected. A clearance corresponding to the damper stroke S may be ensured between the first and second members.

FIG. 3 shows a rotary inertia mass damper C which is still another embodiment of the present invention.
This is based on the rotary inertia mass damper A shown in FIG. 1, but the rotary weight 40 is connected to the first screw shaft 21 and the second screw shaft 31 via the torque limiting mechanism 45. It is.
The torque limiting mechanism 45 normally transmits torque between the rotary weight 40 and the first screw shaft 21 and the second screw shaft 31 to rotate them integrally, but transmits them between them. When the torque to be exceeded exceeds a predetermined limit value, the rotary weight 40 is rotated relative to the first screw shaft 21 and the second screw shaft 31 at that time (idling while maintaining a constant torque). This mechanism limits torque transmission.

As such a torque limiting mechanism 45, various general-purpose products that are marketed as a torque keeper can be used, and in particular, as shown in Japanese Patent Application Laid-Open No. 2010-019347, an overload of a damper is used. A mechanism that functions as a prevention mechanism, that is, a mechanism for preventing an overload of the damper by making the transmission torque peak by sliding friction using a rotating friction plate can be suitably employed.
As shown in FIG. 3, two torque limiting mechanisms 45 functioning as such an overload prevention mechanism are used to connect the rotary weight 40 to the first screw shaft 21 and the second screw shaft 31, and the torques thereof. when the transmission torque leveled off throughout the limiting mechanism 45 and T ₀ (for transmitting torque T _0/2 on one of the torque limiting mechanism 45), the damper load force (axial force) P when the displacement x , It is peaked as the following formula.

This is because the lead L _d of the ball screw mechanism in the conventional inertia mass damper provided with the torque limiting mechanism (overload prevention mechanism) shown in the above Japanese Patent Application Laid-Open No. 2010-019347 is rotated in this embodiment. This is the same as changing to a substantial lead (L _d1 −L _d2 ) in the inertial mass damper C. Since the lead (L _d1 -L _d2 ) in the present embodiment can be made sufficiently smaller than the lead L _d in the conventional damper, a large burden force P can be handled even with the same peak torque T ₀ .
Therefore, the rotational inertia mass damper C of the present embodiment can be provided with a sufficient overload prevention function by using the torque limiting mechanism 45 that is simpler and less expensive than the torque limiting mechanism required in the conventional damper. Become.
The above torque limiting mechanism 45 can be provided with the same overload prevention function by being incorporated in the rotary inertia mass damper B of the embodiment shown in FIG.

  By the way, the rotary inertia mass damper of the present invention can be installed in various patterns in the structure to be controlled in the same manner as other types of dampers. In particular, the brace damper and the brace frame using the rotary inertia mass damper according to the present invention will be described below.

FIG. 4 shows an embodiment of the brace damper D according to the present invention, which is the first of both end portions of the rotary inertia mass damper A in order to install the rotary inertia mass damper A shown in FIG. The base ends of the first connecting member 50 and the second connecting member 51 are coupled to the 1 nut 23 and the second nut 33, respectively, and the distal ends of the first connecting member 50 and the second connecting member are respectively used as a frame. On the other hand, the required length as a brace is secured as a whole so that it can be joined.
In the illustrated example, both the first connecting member 50 and the second connecting member 51 employ steel pipes, and the second connecting member 51 is longer than the first connecting member 50. However, both may be equally long. Of course, the materials, cross-sectional shapes, cross-sectional dimensions, and lengths of the first connecting member 50 and the second connecting member 51 can be installed as braces as a whole according to the specifications of the rotary inertia mass damper A, and as the brace damper. What is necessary is just to design arbitrarily as long as it has desired performance. If steel pipes are used as the first connection member 50 and the second connection member 51, the movable clearances of the first ball screw mechanism 20 and the second ball screw mechanism 30 can be secured by utilizing the hollow space in the steel pipes. It can be easily accommodated even if becomes larger.
Further, it is of course possible to use the rotary inertia mass damper B shown in FIG. 2 instead of the rotary inertia mass damper A described above.

FIG. 5 shows a brace frame according to an embodiment of the present invention, which uses the above-described brace damper D (configured by the rotary inertia mass damper A) as a set of two, and uses them as a column 1 and a beam 2. The V-type braced frame is configured by arranging the V-shaped frame in the frame configured as described above.
In the brace frame of the present embodiment, the tip end portion (upper end portion) of the second connection member 51 of the brace damper D is pin-joined to the upper-layer column beam joint portion via a clevis or a ball joint. 1 The front end (lower end) of the connecting member 50 is joined to a steel damper 60 installed at the center of the lower beam 2 via a clevis or ball joint.
It should be noted that the entire top and bottom of the illustrated example can be reversed to form a Λ-type brace frame or a K-type brace frame or the like, and the brace damper D is not necessarily used as one set. One brace damper may be installed in the frame.

  The steel damper 60 in the brace frame of the present embodiment is connected in series to the brace damper D (that is, the rotary inertia mass damper A) to give a desired spring rigidity, and at the same time, is excessive to the rotary inertia mass damper A. It functions as a fail-safe mechanism for restricting input, and has a function (fail-safe function) that stops the load force by surrendering the steel material at the time of excessive input.

As a steel damper 60 for that purpose, for example, as shown in FIGS. 6A and 6B, a shear panel 63 and a stiffening rib 64 are provided between the top plate 61 and the base plate 62, and the shear panel 63 is applied by a predetermined shear force. A plurality of vertical plates 65 made of a steel plate or a lead plate are welded at a predetermined interval between the top plate 61 and the base plate 62 as shown in FIGS. 7 (a) and 7 (b). Thus, it is possible to suitably employ a plate in which the vertical plate 65 causes bending yield.
Furthermore, it is also possible to use a laminated rubber instead of the steel damper 60 as described above, and to support the laminated rubber to the beam 2 via a sliding bearing, as the same fail-safe mechanism can be exhibited. In particular, in the case of a long-period structure, it is necessary to reduce the rigidity of the spring in series with the rotary inertia mass damper A. In such a case, it is preferable to use a laminated rubber.

In the brace frame of the present embodiment, when the rotary inertia mass damper A is installed at an inclination angle θ with respect to the horizontal, the displacement is equal to the horizontal displacement cos θ compared to the case where the rotary inertia mass damper A is installed horizontally. The effective inertial mass is reduced by a factor of cos ² θ. However, as described above, the rotary inertia mass damper A itself has a displacement magnifying mechanism (accelerating function), so that the displacement reduction due to the inclined installation can be compensated by the displacement magnifying function. Therefore, even if the rotary inertia mass damper A is small and light without increasing the overall length of the rotary inertia mass damper A, a sufficient inertia mass necessary for obtaining a desired vibration damping effect can be obtained.

Further, even if the rotary inertia mass damper A itself does not include an overload prevention mechanism (for example, a mechanism for restricting excessive torque by causing relative rotational slip when the torque exceeds a certain level), the fail safe as described above. By configuring the brace frame combined with the steel damper 60 functioning as a mechanism, an excessive input to the rotary inertia mass damper A is naturally limited. Therefore, an overload prevention mechanism (for example, shown in FIG. 3) is added to the rotary inertia mass damper A itself. It is not necessary to incorporate a torque limiting mechanism 45) in the rotary inertia mass damper C.
However, residual displacement does not occur in the conventional rotary inertia mass damper that uses friction torque as an overload prevention mechanism. However, if the yield (plastic deformation) of the steel damper 60 is used as described above, the residual displacement after the earthquake. Will occur.

According to the rotary inertia mass damper of the present invention, the following effects can be obtained.
(1) By using two sets of ball screw mechanisms with different leads, the displacement of each ball screw relative to the relative displacement at both ends of the damper (the amount of movement of the ball screw shaft relative to the ball nut) can be greatly expanded. The mechanism is also a speed increasing mechanism that increases the rotational speed of the ball screw, and the enlargement rate (speed increasing rate) increases as the lead difference decreases.
As a result, the outer diameter of the damper can be greatly reduced as compared with the prior art, and the installation space for that purpose can be reduced, which makes it difficult to hinder building plans. For example, when this rotary inertia mass damper is installed in a wall, the wall thickness can be reduced to increase the effective space, and when installed on the outer periphery of a building, the size of moving the blind box toward the indoor side is reduced. In the case of being installed adjacent to the floor through hole, the position of the floor through hole can be made sufficiently close to the beam.

(2) Combined use of two sets of ball screw mechanisms with different leads, the effect of greatly increasing the displacement of the ball screw relative to the relative displacement at both ends of the damper (the amount of movement with respect to the ball nut), The force can be greatly reduced and the burden on the structural frame can be reduced.
For example, when the lead L _d1 in the first ball screw mechanism is 25 mm and the lead _Ld2 in the second ball screw mechanism is 20 mm, the torque reaction force (composite force) generated at both ends of the damper is compared to the case where the ball screws are not connected. It can be reduced to 1/9, and it can be reduced to 1/3 or less compared to a conventional damper with a single set of ball screw mechanism with a single lead.

(3) Conventionally, bearings, cylinders, and the like were required in addition to the ball screw mechanism as components constituting the damper. However, these are unnecessary and the number of components is reduced, and the mechanism is greatly simplified. Therefore, a large capacity damper can be manufactured at low cost.
(4) Since it is not necessary to make the actual lead of the ball screw small, it is not necessary to make the ball bearing too small in diameter, so it is possible to secure an appropriate lead according to the ball screw diameter, so the problem of load resistance performance is Does not occur.
(5) Although it is necessary to connect the damper both ends to the structure to be controlled in a non-rotatable manner to constrain the rotation around the ball screw shaft and transmit torque, the transmitted torque is expanded in the same way as the conventional inertia mass damper Therefore, even when using a clevis or a ball joint, a general-purpose product can be used as it is as before, and in that respect, there is no increase in cost.
(6) This type of rotary inertia mass damper does not have static rigidity, does not retain restoring force, and can manually rotate the rotating weight, so the dimensions can be adjusted during installation on site. It can also be implemented easily.

(7) When the rotary weight is connected to the first screw shaft and the second screw shaft via the torque limiting mechanism, the rotary weight is fixed by the first screw shaft, the second screw shaft, and the torque limiting mechanism. The torque transmitted from the rotary weight to the first ball screw mechanism and the second ball screw mechanism can be peaked, and as a result, the damper burden force (axial force) can also be peaked. Therefore, an overload prevention mechanism similar to that of a conventional damper having a single lead can be provided. Furthermore, even if the damper load force is the same as that of the conventional type, the transmission torque is proportional to the lead. Therefore, in the present invention, only a torque corresponding to the lead difference needs to be processed. Can be handled by a device with a small transmission torque). In addition, as in the conventional type, there is no residual deformation in the damper (the rotary weight causes relative rotational slip with respect to the ball screw, so a residual rotational angle may occur, but the rotary weight relatively rotates in the damper. It will not be displacement only).

Further, according to the brace damper and the brace frame of the present invention, the following effects can be obtained.
(8) By applying the above rotary inertia mass-mass damper to the brace, the dimensional constraints in the material axis direction are reduced, and even if the overall length of the damper is slightly increased due to the extra length, it is difficult to cause a problem. Further, the relative displacement amounts S ₁ and S _{2 of} the ball screw are required in the first connecting member and the second connecting member in series with the damper, but by using steel pipes as the first connecting member and the second connecting member, Since the hollow portion can be used, there is no dimensional limitation.
(9) By bracing the above rotary inertia mass damper and joining it to the frame via a fail-safe mechanism (for example, a steel damper), the burden force can reach its peak even when an unexpected excessive input is applied. . Therefore, it is not necessary to provide an overload prevention mechanism in the rotary inertia mass damper, and the structure can be greatly simplified as compared with a conventional damper equipped with the mechanism, and a fail-safe mechanism can be realized at low cost.

A Rotational inertia mass damper B Rotational inertia mass damper C Rotational inertia mass damper 20 First ball screw mechanism 21 First screw shaft 22 First ball screw 23 First nut 30 Second ball screw mechanism 31 Second screw shaft 32 Second ball Screw 33 Second nut 40 Rotating weight 40a Torque transmission member 40b Weight body 42 Bearing 43 Connecting member 45 Torque limiting mechanism D Brace damper 50 First connecting member 51 Second connecting member 60 Steel damper (fail safe mechanism)

Claims (6)

The relative vibration generated between the first member and the second member is reduced by being interposed between the first member and the second member, which are structures to be controlled that generate relative vibration in the direction of separating from each other. A rotary inertia mass damper for
A first ball screw mechanism connected to the first member, wherein the first nut is screwed to the first screw shaft via the first ball screw; A second ball screw mechanism configured to screw two nuts through a second ball screw and connected to the second member;
The first nut in the first ball screw mechanism can be non-rotatably connected to the first member, and the second nut in the second ball screw mechanism cannot be rotated with respect to the second member. Can be consolidated,
The tip of the first screw shaft in the first ball screw mechanism and the tip of the second screw shaft in the second ball screw mechanism are arranged to face each other with a space therebetween, and a rotary weight is arranged between them, By connecting the rotary weight to the first screw shaft and the second screw shaft, the first screw shaft and the second screw are caused by the relative vibration generated between the first member and the second member. The whole of the first screw shaft, the second screw shaft, and the rotating weight can be integrally rotated while the shaft is relatively displaced in the axial direction with respect to the first nut and the second nut.
In addition, the first ball screw in the first ball screw mechanism and the second ball screw in the second ball screw mechanism are formed as ball screws having the same axial center and different leads in the same direction. Rotating inertia mass damper. The rotary inertia mass damper according to claim 1,
A torque transmission member integrally connected to the first screw shaft and the second screw shaft so as not to rotate relative to the first screw shaft; and a relative rotation in the axial direction relative to the outer periphery of the torque transmission member. It consists of a weight body mounted so that it can be displaced,
A rotary inertia mass damper, wherein the weight body is connected to the first nut or the second nut so as to be rotatable and not relatively displaceable in the axial direction. The rotary inertia mass damper according to claim 1 or 2,
When the torque transmitted between the rotary weight and the first screw shaft and the second screw shaft exceeds a predetermined limit value, the rotary weight is moved to the first screw shaft and the second screw shaft. A rotary inertia mass damper, wherein the rotary inertia mass damper is connected via a torque limiting mechanism that limits torque transmission by rotating relative to two screw shafts. A brace damper provided with the rotary inertia mass damper according to claim 1, 2, or 3 in the form of a brace in a building frame,
The base end portion of the first connecting member is integrally connected to the first nut in the rotary inertia mass damper, and the base end portion is integrally connected to the second connecting member to the second nut. The brace damper is characterized in that the tip ends of the first connecting member and the second connecting member can be joined to the frame. A brace frame in which the brace damper according to claim 4 is installed in a frame of a building,
A brace comprising a fail-safe mechanism for limiting an excessive input to the rotary inertia mass damper between a front end portion of the first connection member or the second connection member and the frame. Frame. The brace frame according to claim 5,
The brace frame according to claim 1, wherein the fail-safe mechanism is a steel damper that yields when the excessive input occurs.

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