JP2017015133A - Rotational inertia mass damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotational inertia mass damper which can suppress minute vibration at walking or the like, and can prevent damage resulting from energy at a huge earthquake.SOLUTION: A screw nut 5 is rotatably supported to a first structure 2a, and a flywheel 6 is coaxially fixed to the screw nut. A spline nut 10 is fixed to a position which is separated coaxially from the screw nut of the first structure 2b. A screw shaft 7 extending toward the spline nut at its one end is screwed into the screw nut. A spline shaft 11 which is fixed to a second structure 3 at its one end, and opposes one end of the screw shaft at the other end is slidably supported to the spline nut in an axial direction. An overload adjusting mechanism 15 which makes the spline shaft and the screw shaft non-rotatable with respect to each other, and makes the spline shaft and the screw shaft relatively rotatable in the axial direction when an external force exceeding a prescribed limit value acts thereon in the axial direction is arranged between the other end side of the spline shaft and one end side of the screw shaft.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a rotary inertia mass damper.

On large span floors such as office buildings and large facilities, minute vibrations are generated even during normal walking. For this reason, a floor vibration control system may be introduced for the purpose of improving habitability.
One of the systems is a technology that suppresses shaking using a tuned pendulum, but a large and heavy weight is required to achieve a high effect, and the need for a compact and lightweight floor damping system is increasing. .

As a compact and lightweight floor damping system, for example, a rotary inertia mass damper disclosed in Patent Document 1 is known.
The rotary inertia mass damper disclosed in Patent Document 1 rotates with a ball screw having a base end fixed to one of two members that are relatively displaced in the direction of approaching and separating from each other, and a screw of the ball screw. A ball nut rotatably supported with respect to the other of the two members, a flywheel that rotates together with the ball nut about the rotation center of the ball screw, and a housing that holds the ball nut; A ball support screw that is slidably supported in the direction of the screw axis with respect to the ball screw, the ball screw being freely displaceable in the direction of the screw axis with respect to the slide support member, and having a central axis about the screw center axis It is a device provided with a ball spline that regulates the rotation of.

  When the vibration energy of the minute vibration is applied to the ball screw as an axial force, the ball screw is linearly moved because the ball spline is provided and its rotation is restricted, and the ball nut rotates. The flywheel rotates synchronously with the rotation of the ball nut, and an inertial force is generated by the rotating body of the flywheel. The axial kinetic energy transmitted to the ball screw is converted into rotational energy in the rotational direction, and the The vibration energy of vibration is absorbed.

Japanese Patent No. 5410825

However, the rotary inertia mass damper described in Patent Document 1 is for minute vibrations such as walking, and cannot follow huge vibrations during an earthquake.
In addition, since energy during a huge earthquake is transmitted to the rotary inertia mass damper through the floor, a part of the rotary inertia mass damper may be damaged.
Therefore, the present invention has been made paying attention to the unsolved problems of the above conventional example, and can control minute vibrations such as walking and prevent damage to energy during a huge earthquake. It is an object of the present invention to provide a rotary inertia mass damper that can be used.

  In order to achieve the above object, in a rotary inertia mass damper according to an embodiment, a screw nut is freely rotatable in a first structure body among a first structure body and a second structure body that are relatively displaced in directions close to and away from each other. The flywheel is fixed coaxially to the screw nut, the spline nut is fixed at a position spaced coaxially to the screw nut of the first structure, and the screw shaft has one end extending toward the spline nut. Is engaged with the spline nut, one end is fixed to the second structure, and the other end of the spline shaft is opposed to one end of the screw shaft. Of the spline shaft and screw shaft when an external force exceeding the specified limit value is applied in the axial direction between the screw shaft and one end of the screw shaft. Wearing the overload adjusting mechanism where the movement of the relative.

  According to the rotary inertia mass damper according to the present invention, when it is installed in an office building or a large facility, when a minute vibration occurs during normal walking in the facility, the first inertial body and the second structural body Relative displacement is transmitted through the spline shaft, overload adjustment mechanism and screw shaft, and inertial mass generated by rotation of the flywheel and axial reaction force proportional to the relative acceleration between the screw shaft and screw nut are generated. Thus, minute vertical vibrations in the facility can be attenuated.

Further, when an external force exceeding a predetermined limit value is applied in the axial direction, the cylindrical clamping surface of the overload adjustment mechanism moves the one end of the screw shaft and the other end of the spline shaft relative to each other in the axial direction so Since no axial displacement is input to the screw shaft via the load adjusting mechanism, and the screw nut and the flywheel do not rotate, damage to the rotary inertia mass damper can be prevented.
it can.

It is a figure showing the outline of the rotation inertia mass damper of a 1st embodiment concerning the present invention. It is a figure which shows the coupling and clamping bolt which comprise the overload adjustment mechanism of the rotation inertia mass damper of 1st Embodiment. It is the III-III arrow directional view of FIG. It is the IV-IV line arrow directional view of FIG. FIG. 5 is a view taken along line VV in FIG. 2.

  Next, a first embodiment of the present invention will be described with reference to the drawings. In the following description of the drawings, the same or similar parts are denoted by the same or similar reference numerals. However, it should be noted that the drawings are schematic, and the relationship between the thickness and the planar dimensions, the ratio of the thickness of each layer, and the like are different from the actual ones. Therefore, specific thicknesses and dimensions should be determined in consideration of the following description. Moreover, it is a matter of course that portions having different dimensional relationships and ratios are included between the drawings.

The first embodiment described below exemplifies an apparatus and method for embodying the technical idea of the present invention, and the technical idea of the present invention is the material, shape, and structure of component parts. The arrangement is not specified below. The technical idea of the present invention can be variously modified within the technical scope defined by the claims described in the claims.
Hereinafter, an embodiment of a rotary inertia mass damper according to an aspect of the present invention will be described with reference to the drawings as appropriate.

[Configuration of Rotating Inertia Mass Damper]
A rotary inertia mass damper 1 according to the first embodiment shown in FIG. 1 is formed between a first structure 2 and a second structure 3 that are relatively displaced in the direction of approaching and separating from each other, for example, by a column beam, a floor, or a spring of a building. Is intervened.
The rotary inertia mass damper 1 is connected to the screw nut 5 disposed on the first structure 2 side, the flywheel 6 that rotates together with the screw nut 5, the screw shaft 7 that is screwed to the screw nut 5, and the second structure 3. The spline shaft 11 and an overload adjusting mechanism 15 that transmits the displacement generated between the first structure 2 and the second structure 3 from the spline shaft 11 to the screw shaft 7 are provided.

Here, the 1st structure 2 is comprised by the 1st unit body 2a and the 2nd unit body 2b which are mutually arrange | positioned in parallel at predetermined intervals, and are displaced to the same direction.
The screw nut 5 is rotatably supported on the first unit body 2 a of the first structure 2 via a bearing 4. The bearing 4 includes an inner ring (not shown) that rotates integrally with the screw nut 5, an outer ring (not shown) fixed to the first unit body 2a, and a plurality of rolling elements (not shown) interposed between the inner ring and the outer ring. ) And. A substantially disc-shaped flywheel 6 is coaxially fixed to the inner ring of the bearing 4.

A screw shaft 7 is screwed onto the screw nut 5. A large number of rolling members (not shown) are interposed between the screw groove of the screw nut 5 and the screw groove of the screw shaft 7, and the screw nut 5 and the screw shaft 7 constitute a ball screw mechanism.
A cylindrical screw shaft side connecting portion 8 is coaxially formed on one end side of the screw shaft 7, and a single key groove 9 extending axially from the tip is formed on the outer periphery of the screw shaft side connecting portion 8. Is formed.

A spline nut 10 is fixed to the second unit body 2b of the first structure 2 coaxially with the screw nut 5, and a spline shaft 11 is supported on the spline nut 10 so as to be slidable in the axial direction.
A fixed portion 12 is integrally formed coaxially with one end of the spline shaft 11, and the fixed portion 12 is fixed to the second structure 3.

The other end of the spline shaft 11 (referred to as a spline shaft side connecting portion 11a) faces the screw shaft side connecting portion 8 of the screw shaft 7, and the outer periphery of the spline shaft side connecting portion 11a extends axially from the tip. An extending key groove 13 is formed.
As shown in FIGS. 2 to 5, the overload adjusting mechanism 15 includes a coupling 16, a first key 17, a second key 18, a first tightening bolt 19a, and a second tightening bolt 19b.

The coupling 16 is formed as a member having a substantially C-shaped cross section by inserting one slit 20 along the axial direction of the cylindrical member, and the screw shaft side coupling portion 8 formed on one end side in the axial direction of the coupling 16. A first cylindrical clamping surface 21 that clamps the outer periphery, and a second cylindrical clamping surface 22 that clamps the outer periphery of the spline shaft side coupling portion 11a formed on the other axial end side of the coupling 16 are provided.
A bolt head locking hole 23 a and a screw hole 23 b are formed at a position passing through the slit 20 on one end side (first cylindrical holding surface 21) of the coupling 16 in the axial direction of the coupling 16. A bolt head locking hole 24a and a screw hole 24b are also formed on the other end side (second cylindrical holding surface 22) at a position passing through the slit 20.

The coupling 16 is elastically deformed at a position 180 degrees (half circumference) away from the position where the slit 20 of the coupling 16 is inserted in the circumferential direction, and the first cylinder clamping surface 21 and the second cylinder clamping surface due to elastic deformation. Deformation promotion grooves 25 are formed so that the diameter reduction operation of 22 is facilitated.
As shown in FIGS. 3 and 4, a single key groove 26 is formed on the first cylindrical holding surface 21 of the coupling 16 along the axial direction from one end. As shown in FIG. 1, the key groove 26 is formed at a position facing the key groove 9 formed on the outer periphery of the screw shaft side coupling portion 8, and the first key 17 is placed inside the key grooves 9 and 26. Is installed.

As shown in FIGS. 3 and 5, a single key groove 27 is formed in the second cylindrical holding surface 22 of the coupling 16 along the axial direction from the other end. As shown in FIG. 1, the key groove 27 is formed at a position facing the key groove 13 formed on the outer periphery of the spline shaft side connecting portion 11a. Is installed.
Then, the first tightening bolt 19a is attached to the bolt head locking hole 23a and the screw hole 23b formed in the first cylindrical clamping surface 21 of the coupling 16, and the head of the first tightening bolt 19a is locked to the bolt head locking position. By screwing the screw part into the screw hole 23b in contact with the hole 23a, the screw shaft side connecting part 8 is clamped with a predetermined tightening force due to the reduced diameter of the first cylindrical clamping surface 21.

Further, the second tightening bolt 19b is mounted in the bolt head locking hole 24a and the screw hole 24b formed in the second cylindrical clamping surface 22 of the coupling 16, and the head of the second tightening bolt 19b is locked to the bolt head locking. The spline shaft side coupling portion 11a is clamped with a predetermined tightening force due to the reduced diameter of the second cylindrical clamping surface 22 by abutting the hole 24a and screwing the screw portion into the screw hole 24b.
In the overload adjusting mechanism 15 having the above-described configuration, the coupling 16 is screwed with the first key 17 mounted in the key grooves 9 and 26 and the second key 18 mounted in the key grooves 13 and 27. Since the shaft side connecting portion 8 and the spline shaft side connecting portion 11a are sandwiched, the screw shaft side connecting portion 8 and the spline shaft side connecting portion 11a are connected so as not to be relatively rotatable.

  Here, the cylindrical clamping surface according to the present invention corresponds to the first cylindrical clamping surface 21 and the second cylindrical clamping surface 22, and the clamping bolt according to the present invention corresponds to the first clamping bolt 19a and the second clamping bolt 19b. The shaft side keyway according to the present invention corresponds to the keyways 9 and 13, the clamping surface side keyway according to the present invention corresponds to the keyways 26 and 27, and the key according to the present invention corresponds to the first key 17 and the first keyway. It corresponds to 2 key 18.

[Operation of rotary inertia mass damper]
Next, an operation when the rotary inertia mass damper 1 of the first embodiment is installed on a large span floor such as an office building or a large facility will be described.
When minute vibrations occur even during normal walking in an office building or a large facility, the rotary inertia mass damper 1 responds to the relative acceleration in the displacement direction generated between the first structure 2 and the second structure 3. By generating a strong damping force, it is possible to dampen minute vibrations generated in office buildings and large facilities.

That is, when the flywheel 6 rotates θ due to the axial displacement x input from the spline shaft 11 to the screw shaft 7 via the overload adjusting mechanism 15, the axial force (reaction force) F is expressed by the following equation (1). It can be expressed as

Where I _θ is the rotational moment of inertia of the entire rotating part, α is the angular acceleration of the flywheel, L _d is the lead (screw pitch) of the screw shaft 7, D is the outer diameter of the flywheel 6, and m is the flywheel The mass of the wheel 6, ψ is the inertial mass in the axial direction, and x ″ is the relative acceleration between the screw shaft 7 and the screw nut. Here, the inertial mass ψ in the axial direction is several hundred times to several times the mass m of the flywheel 6. 1000 times the value is obtained.

  As described above, the rotary inertia mass damper 1 according to the first embodiment installed in an office building or a large-scale facility causes the spline shaft 11 via the overload adjusting mechanism 15 when minute vibration occurs during normal walking in the facility. When the axial displacement x is input to the screw shaft 7, an axial force (reaction force) proportional to the relative acceleration x ″ of the screw shaft 7 and the screw nut 5 with respect to the inertial mass Ψ generated by the rotation of the flywheel 6. ) The occurrence of F suppresses minute vertical vibrations in the facility.

Next, the operation of the rotary inertia mass damper 1 when an earthquake occurs will be described.
In the overload adjusting mechanism 15 of the first embodiment, the first tightening bolt 19a screwed to the coupling 16 reduces the diameter of the first cylindrical holding surface 21, and the second tightening bolt 19b reduces the second cylindrical holding surface 22. By the diameter, the first cylindrical clamping surface 21 clamps the screw shaft side coupling portion 8 with a predetermined clamping force, and the second cylindrical clamping surface 22 clamps the spline shaft side coupling portion 11a with a predetermined clamping force. .

The predetermined tightening force described above causes the screw shaft side connecting portion 8 and the spline shaft side connecting portion 11a to move relative to each other in the axial direction when an earthquake having a predetermined seismic intensity that may damage the rotating screw nut 5 or the flywheel 6 occurs. When it moves and falls below an earthquake of a predetermined seismic intensity, it is set to a force that disables the axial relative movement of the screw shaft side connecting portion 8 and the spline shaft side connecting portion 11a.
The rotary inertia mass damper 1 provided with such an overload adjustment mechanism 15 causes the first cylinder when an earthquake having a predetermined seismic intensity or more occurs and a relative displacement occurs between the first structure 2 and the second structure 3. The screw shaft side coupling portion 8 sandwiched by the sandwiching surface 21 and the spline shaft side coupling portion 11a sandwiched by the second cylindrical sandwiching surface 22 move relative to each other in the axial direction, and the overload adjustment mechanism 15 is moved from the spline shaft 11. The axial displacement is not input to the screw shaft 7 through the screw nut 5, and the screw nut 5 and the flywheel 6 do not rotate.
Thereby, when an earthquake of a predetermined seismic intensity or more occurs, the first cylindrical clamping surface 21 and the second cylindrical clamping surface 22 of the overload adjusting mechanism 15 are axially connected to the screw shaft side coupling portion 8 and the spline shaft side coupling portion 11a. The rotation inertia mass damper 1 is prevented from being damaged.

[Effect of rotational inertia mass damper]
Next, the effect of the rotary inertia mass damper 1 of the first embodiment described above will be described.
When the rotary inertia mass damper 1 installed in an office building or a large facility generates minute vibrations during normal walking in the facility, the relative displacement between the first structure 2 and the second structure 3 is expressed by the spline shaft 11. The inertial mass transmitted through the overload adjusting mechanism 15 and the screw shaft 7 and generated by the rotation of the flywheel 6 and the axial force (reaction force) proportional to the relative acceleration x ″ of the screw shaft 7 and the screw nut 5. ) By generating F, minute vertical vibrations in the facility can be attenuated.

  Further, when an earthquake of a predetermined seismic intensity or more occurs, the first cylindrical clamping surface 21 and the second cylindrical clamping surface 22 of the overload adjusting mechanism 15 cause the screw shaft side coupling portion 8 and the spline shaft side coupling portion 11a to move in the axial direction. Relative movement is performed, and no axial displacement is input from the spline shaft 11 to the screw shaft 7 via the overload adjusting mechanism 15, and the screw nut 5 and the flywheel 6 do not rotate, thereby preventing the rotary inertia mass damper 1 from being damaged. Can do.

In addition, the overload adjusting mechanism 15 adjusts the screwing state of the first tightening bolt 19a and the second tightening bolt 19b, so that the tightening force with respect to the screw shaft side connecting portion 8 of the first cylindrical clamping surface 21 and the second tightening bolt 19b are adjusted. The clamping force of the cylindrical clamping surface 22 with respect to the spline shaft side connecting portion 11a can be easily adjusted.
Further, the structure in which the screw shaft side connecting portion 8 and the spline shaft side connecting portion 11a cannot be rotated relative to each other includes a key groove 26 formed on the first cylindrical holding surface 21 of the coupling 16 and a key formed on the screw shaft side connecting portion 8. The first key 17 is mounted between the groove 9 and the second key between the key groove 27 formed on the second cylindrical holding surface 22 of the coupling 16 and the key groove 13 formed on the spline shaft side connecting portion 11a. By mounting 18, it can be easily realized.

DESCRIPTION OF SYMBOLS 1 Rotation inertia mass damper 2 1st structure 2a 1st unit body 2b 2nd unit body 3 2nd structure 4 Bearing 5 Screw nut 6 Flywheel 7 Screw shaft 8 Screw shaft side connection part 9 Key groove 10 Spline nut 11 Spline shaft 11a Spline shaft side connecting portion 12 Fixing portion 13 Key groove 15 Overload adjusting mechanism 16 Coupling 17 First key 18 Second key 19a First tightening bolt 19b Second tightening bolt 20 Slit 21 First cylinder holding surface 22 Second cylinder Clamping surface 23a Bolt head locking hole 23b Screw hole 24a Bolt head locking hole 24b Screw hole 25 Deformation promoting grooves 26, 27 Key groove

Claims (5)

A screw nut is rotatably supported by the first structure body among the first structure body and the second structure body that are relatively displaced in directions that are close to and away from each other.
The flywheel is fixed coaxially to the screw nut,
A spline nut is fixed at a position spaced coaxially with respect to the screw nut of the first structure,
A screw shaft having one end extending toward the spline nut is screwed onto the screw nut,
One end of the spline nut is fixed to the second structure, and the other end of the spline shaft that is opposed to the one end of the screw shaft is supported slidably in the axial direction.
When the spline shaft and the screw shaft cannot be relatively rotated between the other end side of the spline shaft and the one end side of the screw shaft, and an external force exceeding a predetermined limit value is applied in the axial direction. A rotary inertia mass damper equipped with an overload adjustment mechanism that enables relative movement of the spline shaft and the screw shaft in the axial direction. The overload adjustment mechanism is
A coupling having a cylindrical clamping surface capable of reducing the diameter;
A diameter reducing means for reducing the diameter of the cylindrical clamping surface to clamp the one end of the screw shaft and the other end of the spline shaft;
2. The rotary inertia mass damper according to claim 1, further comprising a relative non-rotatable means provided between the one end of the screw shaft and the other end of the spline shaft and the cylindrical clamping surface. . The coupling is made into a member having a substantially C-shaped cross section by inserting a slit along the axial direction of the cylindrical member, and its inner surface is the cylindrical clamping surface,
As the diameter reducing means, a bolt head locking hole and screw hole formed at a position passing through the slit of the coupling, and a tightening bolt are provided, and the head of the tightening bolt is connected to the bolt head locking hole. The rotary inertia mass damper according to claim 2, wherein the cylindrical clamping surface is reduced in diameter by being brought into contact with the screw and screwing a screw portion of the tightening bolt into the screw hole.   The relative non-rotatable means is formed on an outer periphery of the one end of the screw shaft, an axial key groove provided on an outer periphery of the other end of the spline shaft, and the cylindrical clamping surface facing the axial key groove. 4. The rotary inertia mass according to claim 2, comprising: a holding surface side key groove, and a key mounted between the shaft side key groove and the holding surface side key groove. 5. Damper.   5. The external force exceeding the predetermined limit value is an earthquake force having a predetermined seismic intensity that may cause damage when the screw nut or the flywheel rotates. The rotary inertia mass damper according to item.

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