Damping device, vibration control device, wall structure, wooden house, and friction damper

Abstract

To provide a damping device, a vibration control device, a wall body structure, a wooden house and a friction damper for realizing a combination of a plurality of kinds of dampers.SOLUTION: The damping device 200 in which the first damping device end portion 201 which is one end portion is disposed on the first pillar side and the second damping device end portion 202 which is the other end portion is disposed on the second pillar side includes the oil damper 210 which applies a damping force and the friction damper 220 which applies a damping force, and in the displacement in which the first damping device end portion 201 and the second damping device end portion 202 approach or separate from each other, the oil damper 210 functions when the displacement is equal to or less than a predetermined value, and the oil damper 210 and the friction damper 220 function when the displacement exceeds the predetermined value.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present disclosure relates to a damping device, a vibration control device, a wall structure, a wooden house, and a friction damper. [Background technology]

[0002] For example, in the wall structure of a wooden house, a diagonal brace-type vibration control device is sometimes installed between vertically extending columns to improve earthquake resistance. For example, Patent Document 1 discloses a vibration control device configured by combining linear braces (reinforcement members) and dampers. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2008-144387 Summary of the Invention [Problem to be solved by the invention]

[0004] For example, if an oil damper is used as the damper, it can be said that the oil damper is particularly effective against small earthquakes that occur frequently, as it has excellent durability against repeated earthquakes and is effective in damping even small earthquakes. However, in order to make an oil damper able to withstand a large earthquake, it is necessary to make the oil damper larger, which may make the oil damper unsuitable for the wall structure of a wooden house where the space available for installation is limited.

[0005] Furthermore, if a friction damper is used as the damper, it can be said that the friction force (damping force) can be easily set to match the large earthquake shaking, so that the friction damper can be particularly effective against large earthquakes. However, if the friction force of a friction damper is set to match the vibrations of a large earthquake, the damping effect will be less pronounced for small earthquakes, so friction dampers may not be suitable for areas where small earthquakes occur frequently.

[0006] As such, each type of damper has its own unique properties, but by combining multiple types of dampers, it may be possible to combine the advantages of different types of dampers. Depending on the combination, it is possible to provide a damping device that can respond to a wide range of earthquake shaking and that also takes into account repeated durability.

[0007] The present disclosure has been made in consideration of the above circumstances, and aims to provide a damping device, a vibration control device, a wall structure, a wooden house, and a friction damper that combine multiple types of dampers. [Means for solving the problem]

[0008] In order to solve the above-mentioned problems, the damping device, vibration control device, wall structure, wooden house, and friction damper of the present disclosure employ the following measures. The damping device according to the first aspect of the present disclosure is a damping device in which one end, a first end, is arranged on the side of one structural member and the other end, a second end, is arranged on the side of another structural member, and comprises a main damper that applies a damping force and an auxiliary damper that applies a damping force, and when the first end and the second end are displaced toward or away from each other along an axis, the main damper functions if the displacement is equal to or less than a predetermined value, and when the displacement exceeds the predetermined value, the main damper and the auxiliary damper function.

[0009] According to the damping device of this embodiment, when the first end and the second end move closer to or farther apart along the axis, the main damper functions if the displacement is equal to or less than a predetermined value, and both the main damper and the auxiliary damper function if the displacement exceeds the predetermined value. Therefore, the damping performance of the device can be exhibited for small earthquake vibrations by the damping force of the main damper, and for large earthquake vibrations by the larger damping force obtained by adding the damping force of the auxiliary damper. Therefore, for example, small earthquakes that occur frequently can be handled by the main damper, and large earthquakes that occur infrequently can be handled by the main damper and the sub-damper. This allows for a combination of multiple types of dampers that utilize the unique properties of the dampers, for example by using a damper for the main damper that has excellent durability against repeated shaking and is effective against small earthquake vibrations, and a damper for the sub-damper that has a large damping force and is particularly effective against large earthquake vibrations, thereby making it possible to provide a damping device that can handle small to large earthquake vibrations and that also takes into consideration repeated durability.

[0010] A damping device according to a second aspect of the present disclosure is the damping device of the first aspect, wherein the main damper is an oil damper having a cylinder and a rod that moves relative to the cylinder.

[0011] According to the damping device of this aspect, the main damper is an oil damper, which is excellent in durability against repeated vibrations and is also effective against small earthquake vibrations.

[0012] A damping device according to a third aspect of the present disclosure is the damping device of the second aspect, wherein the auxiliary damper is a friction damper.

[0013] According to the damping device of this aspect, the sub-damper is a friction damper, so that it is easy to set a large damping force.

[0014] A damping device according to a fourth aspect of the present disclosure is the damping device of the third aspect, wherein the amount of movement of the rod corresponds to the displacement, the friction damper has a slidable member and a sliding member that slides along the axis while in contact with the slidable member, the slidable member is connected to the rod and includes a linkage mechanism that links the oil damper and the friction damper, and the linkage mechanism slides the sliding member against the slidable member when the displacement exceeds a predetermined value.

[0015] According to the damping device of this aspect, the interlocking mechanism causes the sliding member to slide relative to the slidable member when the displacement exceeds a predetermined value, so that when the displacement exceeds the predetermined value, the rod of the oil damper and the friction damper can be connected in parallel, thereby allowing the friction damper to provide additional damping force when the displacement exceeds the predetermined value.

[0016] In the damping device according to the fifth aspect of the present disclosure, in the fourth aspect, the sliding member is a rod-shaped sliding rod extending along the axis, and the sliding member is a cylindrical part through which the sliding rod is inserted along the axis and whose inner surface contacts the outer surface of the sliding rod.

[0017] According to the damping device of this aspect, the sliding member is a tubular part through which the sliding rod is inserted along the axis and whose inner surface contacts the outer surface of the sliding rod, so that a damping force can be applied by the frictional force generated between the tubular part and the sliding rod inserted therein.

[0018] A damping device according to a sixth aspect of the present disclosure is the fifth aspect, wherein the friction damper includes a holding unit that holds the tubular part, and the interlocking mechanism includes a frame body fixed to the cylinder, and the frame body sandwiches the holding unit that holds the tubular part with a gap in the axial direction.

[0019] According to the damping device of this aspect, the frame sandwiches the holding unit holding the tubular part with a gap in the axial direction, so that when the holding unit moves within a range where the gap does not become zero, the holding unit does not come into contact with the frame, and the tubular part does not slide against the sliding rod. On the other hand, when the gap becomes zero and the holding unit moves together with the frame, the holding unit moves relative to the sliding rod, and the tubular part held by the holding unit slides against the sliding rod, generating a frictional force.

[0020] A damping device according to a seventh aspect of the present disclosure is the sixth aspect, wherein the holding unit has a holding member having a through hole formed therein into which the tubular part is fitted along the axis, and a pressing member that presses the tubular part toward the holding member.

[0021] According to the damping device of this aspect, the holding unit has a holding member having a through hole formed therein into which the tubular part is fitted along the axis, and a pressing member that presses the tubular part against the holding member, so that the tubular part can be held with a simple configuration. Furthermore, because the pressing member presses the tubular part, the tubular part can be prevented from slipping out of the through hole of the holding member.

[0022] A damping device according to an eighth aspect of the present disclosure is the seventh aspect, wherein the tubular part has a tapered tubular portion whose outer diameter decreases and a slit along the axis, and the tapered tubular portion of the tubular part is fitted into the through hole of the holding member.

[0023] According to the damping device of this aspect, the tubular part has a tapered tubular portion whose outer diameter decreases and a slit along the axis. The tapered tubular portion of the tubular part is fitted into the through hole of the holding member. Contact between the tapered tubular portion and the through hole converts the force pushing the tubular part toward the holding member (through hole) into a radial force that changes the inner diameter of the tubular part. This allows the contact force of the tubular part with the inserted sliding rod to be changed, thereby adjusting the frictional force generated between the tubular part and the sliding rod. Furthermore, the wedge effect caused by the shape of the tapered tubular portion allows the inner circumferential surface of the tubular part to contact the outer circumferential surface of the sliding rod with a strong force even with a small pushing force.

[0024] According to a ninth aspect of the present disclosure, in the damping device of the eighth aspect, the tapered tubular portion of the tubular part has an inclination gradient of 1 degree or more and 10 degrees or less.

[0025] According to the damping device of this embodiment, the tapered tubular portion of the tubular part has an inclination gradient of 1 degree or more and 10 degrees or less, so that the amount of radial deformation of the tubular part relative to the amount of depression of the tubular part can be reduced and the wedge effect can be efficiently exerted.

[0026] The damping device according to the tenth aspect of the present disclosure is any one of the fifth to ninth aspects, wherein the portion of the tubular part that contacts the outer surface of the sliding rod is a metal-based oil-free bearing in which a solid lubricant is dispersed in metal.

[0027] According to the damping device of this aspect, the portion of the tubular part that comes into contact with the outer peripheral surface of the sliding rod is a metal-based oil-free bearing, which improves durability against repeated sliding between the tubular part and the sliding rod. Furthermore, even if the portion of the tubular part that comes into contact with the outer peripheral surface of the sliding rod is a metal-based oil-free bearing, sufficient frictional force can be ensured by pressing it against the outer peripheral surface of the sliding rod with a strong force that utilizes the wedge effect. Furthermore, for example, by combining a cylindrical part having a tapered cylindrical portion (a structure that generates a wedge effect) with a metal-based oil-free bearing, it is possible to provide a friction damper that takes into consideration strong frictional force and durability.

[0028] In the damping device according to the eleventh aspect of the present disclosure, in the tenth aspect, the frame body has a bushing through which the sliding rod is inserted in the direction of the axis, and the bushing holds the sliding rod in the radial direction centered on the axis.

[0029] In the damping device according to this aspect, the bushing holds the sliding rod in the radial direction, thereby preventing the sliding rod from vibrating or deflecting in the radial direction and stabilizing the input of the load along the axial direction transmitted by the sliding rod, thereby preventing a decrease in the rigidity of the damping device and, in turn, preventing a gradual rise in the yield strength (damping force) that the damping device can exert.

[0030] A damping device according to a twelfth aspect of the present disclosure is, in any of the fifth to ninth aspects, a damping device in which the friction damper comprises a holding unit that holds the tubular part, and the interlocking mechanism comprises two side members that extend along the axis, are connected to the cylinder, and are arranged facing each other so as to sandwich the cylinder, a first frame member that is arranged between the two side members, and through which the sliding rod is inserted along the axis and is connected to each of the side members, and a second frame member that is arranged between the two side members, and through which the sliding rod is inserted along the axis and is connected to each of the side members, and the first frame member and the second frame member are arranged at a distance in the direction of the axis, and sandwich the holding unit that holds the tubular part with a gap in the direction of the axis.

[0031] According to the damping device of this aspect, the first frame member and the second frame member are arranged apart in the axial direction and sandwich the friction unit including the holding unit and the tubular part held by the holding unit with a gap in the axial direction, so that when the holding unit moves within a range where the gap does not become zero, the holding unit does not come into contact with the first frame block and the second frame block, and the tubular part does not slide against the sliding rod. On the other hand, when the gap becomes zero and the holding unit moves together with the first frame block and the second frame block, the holding unit moves relative to the sliding rod, and the tubular part held by the holding unit slides against the sliding rod, generating a frictional force. Furthermore, the cylinder of the oil damper is connected to the first frame block and the second frame block by the two side members, so they can be integrated with a simple structure.

[0032] In the damping device according to the thirteenth aspect of the present disclosure, in the twelfth aspect, each of the side members contacts only a portion of the base end side of the cylinder of the oil damper, and contacts the outer surface of the cylinder in a single line along the axial direction.

[0033] According to the damping device of this aspect, each side member contacts only a partial area on the base end side of the cylinder of the oil damper, and contacts the outer circumferential surface of the cylinder along a single line along the axial direction, so that the cylinder is supported over a partial area on the base end side, and by minimizing the area of ​​the support point of the cylinder, the possibility of the cylinder being deformed by contact with the side member is reduced. Also, because the end of the rod (the end housed inside the cylinder) does not reach the inside of the base end side of the cylinder, even if the cylinder is deformed over a partial area due to contact with the side member, it is unlikely to affect the damping performance of the oil damper.

[0034] A damping device according to a fourteenth aspect of the present disclosure is the thirteenth aspect, wherein each of the side members is in surface contact with an outer circumferential surface of the first frame member and an outer circumferential surface of the second frame member.

[0035] According to the damping device of this embodiment, each side member is in surface contact with the outer peripheral surfaces of the first frame block and the second frame block, and therefore can stably support the first frame block and the second frame block.

[0036] In the damping device according to the fifteenth aspect of the present disclosure, in the fourteenth aspect, the cross-sectional shapes of the first frame member and the second frame member perpendicular to the axis are circular and centered on the axis, the cross-sectional shape of the cylinder of the oil damper perpendicular to the axis is circular and centered on the axis, the cross-sectional shape of the side member perpendicular to the axis is convex outward in the radial direction and centered on the axis, and in the range of contact with the cylinder of the oil damper, the cross-sectional shape is a bow shape with two bends formed, and in the range of contact with the first frame member and the second frame member, the cross-sectional shape is an arc shape that follows the outer peripheral surfaces of the first frame member and the second frame member.

[0037] According to the damping device of this aspect, the cross-sectional shape of the side member perpendicular to the axis is convex outward in the radial direction centered on the axis, and in the area where it contacts the cylinder of the oil damper, it has a bow shape with two bends, and in the area where it contacts the first frame block and the second frame block, it has an arc shape that follows the outer peripheral surfaces of the first frame block and the second frame block.Therefore, by changing the cross-sectional shape of the side member, it is possible to change the way the side member contacts the cylinder of the oil damper and the way the side member contacts each frame block.

[0038] A damping device according to a 16th aspect of the present disclosure is the 15th aspect, wherein the first frame member is arranged between the second frame member and the tip of the cylinder of the oil damper in the direction of the axis, and the cross-sectional shape of the side member perpendicular to the axis changes continuously within the range from the tip of the cylinder of the oil damper to the first frame member.

[0039] According to the damping device of this embodiment, the cross-sectional shape of the side member perpendicular to the axis changes continuously within the range from the tip of the oil damper cylinder to the first frame block, so that the cross-sectional shape of the side member can be changed within a range that does not affect either the cylinder or the first frame block.

[0040] The damping device according to the 17th aspect of the present disclosure is, in any of the 12th to 16th aspects, such that the cross-sectional shape of the holding unit perpendicular to the axis is circular and centered on the axis, the cross-sectional shapes of the first frame member and the second frame member perpendicular to the axis are circular and centered on the axis, and the cross-sectional shape of the cylinder of the oil damper perpendicular to the axis is circular and centered on the axis.

[0041] According to the damping device of this embodiment, the cross-sectional shape perpendicular to the axis of the holding unit is circular and centered on the axis, the cross-sectional shapes perpendicular to the axis of the first frame member and the second frame member are circular and centered on the axis, and the cross-sectional shape perpendicular to the axis of the oil damper cylinder is circular and centered on the axis, so that the shape of the device as a whole has a sense of unity, creating an excellent aesthetic appearance.

[0042] The damping device according to the 18th aspect of the present disclosure is any of the 12th to 17th aspects, wherein the holding unit has a holding member having a through hole formed therein that is fitted along the axis of the tubular part, a pressing member that presses the tubular part toward the holding member, and three or more screw members that fasten the holding member and the pressing member, and the screw members are arranged at equal angular intervals in the circumferential direction centered on the axis.

[0043] According to the damping device of this embodiment, the holding unit has three or more screw members that fasten the holding member and the pressing member, and the screw members are arranged at equal angular intervals in the circumferential direction around the axis, so that the tubular part can be pressed down evenly in the circumferential direction.

[0044] A damping device according to a 19th aspect of the present disclosure is any of the 2nd to 18th aspects, wherein the oil damper is of a type having bilinear characteristics in which the yield strength rises at a gradient of 0.8 kN / mm or more from the stop position of the rod to a predetermined displacement, and the yield strength is maintained approximately constant after the predetermined displacement.

[0045] According to this embodiment, the oil damper is a type with bilinear characteristics in which the strength rises at a gradient of 0.8 kN / mm or more from the stop position to a predetermined displacement, and the strength remains approximately constant after the predetermined displacement, so that it can exert a damping force from the early stages even in the event of a small earthquake.

[0046] A vibration damping device according to a twentieth aspect of the present disclosure includes a damping device according to any one of the second to nineteenth aspects and a brace connected to the first end and extending along the axis.

[0047] A wall structure according to a twenty-first aspect of the present disclosure includes the vibration damping device according to the twentieth aspect, the one structural member, and the other structural member.

[0048] A wooden house according to a twenty-second aspect of the present disclosure includes the wall structure according to the twenty-first aspect.

[0049] A wall structure according to a 23rd aspect of the present disclosure comprises a damping device according to any one of the 12th to 18th aspects, a brace connected to the first end and extending along the axis, the first wooden structural member extending in the vertical direction, and the second wooden structural member extending in the vertical direction and positioned horizontally spaced apart from the first structural member, and when viewed in a depth direction perpendicular to the vertical and horizontal directions, the two thin plate-shaped side members face each other in a direction perpendicular to the axis and the depth direction.

[0050] According to the wall structure of this embodiment, the two thin plate-shaped side members face each other in a direction perpendicular to the axial direction and the depth direction, so that when a moment around the axis along the depth direction occurs in the vibration control device (particularly the damping device), the two side members can balance the tension / compression (a tensile load acts on one side member and a compressive load acts on the other side member).

[0051] A wooden house according to a twenty-fourth aspect of the present disclosure includes the wall structure according to the twenty-third aspect.

[0052] The damping device according to the 25th aspect of the present disclosure is a damping device in which one end, a first end, is arranged on the side of one structural member and the other end, a second end, is arranged on the side of another structural member, and when the first end and the second end are displaced toward or away from each other along an axis, the yield strength increases from the stop position to a first predetermined displacement, the yield strength remains approximately constant from the first predetermined displacement to a second predetermined displacement, and the yield strength increases from the second predetermined displacement onwards.

[0053] According to the damping device of this aspect, when the first end and the second end are displaced toward or away from each other along the axis, the bearing capacity increases from the stop position to the first predetermined displacement, and the bearing capacity remains substantially constant from the first predetermined displacement to the second predetermined displacement, so that the damping capacity can be exerted from the early stage against small earthquakes. Furthermore, the bearing capacity increases again after the second predetermined displacement, so that the damping capacity can be exerted even greater against large earthquakes.

[0054] A friction damper according to a 26th aspect of the present disclosure comprises a rod-shaped sliding rod extending along an axis, a tubular part through which the sliding rod is inserted along the axis and whose inner surface contacts the outer surface of the sliding rod, and a holding member that holds the tubular part, wherein the tubular part has a slit along the axis and a tapered tubular portion whose outer diameter decreases, and the holding member has a through hole into which the tapered tubular portion of the tubular part is fitted.

[0055] According to the friction damper of this aspect, the tubular part has a slit along the axis and a tapered tubular part whose outer diameter decreases, and the holding member has a through hole into which the tapered tubular part of the tubular part is fitted. Therefore, the force pushing the tubular part toward the holding member (through hole) can be converted into a radial force that changes the inner diameter of the tubular part through contact between the tapered tubular part and the through hole. This allows the contact force of the tubular part with the inserted sliding rod to be changed, thereby adjusting the friction force generated between the tubular part and the sliding rod. Furthermore, the wedge effect caused by the shape of the tapered tubular part allows the inner circumferential surface of the tubular part to contact the outer circumferential surface of the sliding rod with a strong force even with a small pushing force.

[0056] A friction damper according to a twenty-seventh aspect of the present disclosure is the twenty-sixth aspect, further comprising a pressing member that presses the tubular part toward the holding member.

[0057] According to the friction damper of this aspect, the friction damper is provided with a pressing member that presses the tubular part toward the holding member, and therefore the tubular part can be prevented from slipping out of the through hole.

[0058] A friction damper according to a 28th aspect of the present disclosure is the 26th or 27th aspect, wherein the portion of the tubular part that contacts the outer peripheral surface of the sliding rod is a metal-based oil-free bearing in which a solid lubricant is dispersed in metal.

[0059] According to the friction damper of this aspect, the portion of the tubular part that comes into contact with the outer peripheral surface of the sliding rod is a metal-based oil-free bearing, which improves durability against repeated sliding between the tubular part and the sliding rod. Furthermore, even if the portion of the tubular part that comes into contact with the outer peripheral surface of the sliding rod is a metal-based oil-free bearing, sufficient frictional force can be ensured by pressing the tubular part against the outer peripheral surface of the sliding rod with a strong force that utilizes the wedge effect. As described above, by combining a metallic oil-free bearing with the wedge effect, it is possible to provide a friction damper that takes durability into consideration.

[0060] A friction damper according to a 29th aspect of the present disclosure is any one of the 26th to 28th aspects, wherein the tapered tubular portion of the tubular part has an inclination gradient of 1 degree or more and 10 degrees or less.

[0061] According to the friction damper of this embodiment, the tapered cylindrical portion of the tubular part has an inclination gradient of 1 degree or more and 10 degrees or less, so that the amount of radial deformation of the tubular part relative to the amount of depression of the tubular part can be reduced and the wedge effect can be efficiently exerted.

[0062] The friction damper according to a thirtieth aspect of the present disclosure is any one of the twenty-sixth to twenty-ninth aspects, further including a spacer that regulates the amount by which the tubular part is pushed into the through hole.

[0063] The friction damper according to this aspect includes a spacer that regulates the amount by which the tubular part is pushed into the through hole, thereby preventing the tubular part from being pushed into the through hole more than necessary. [Effects of the Invention]

[0064] According to the present disclosure, a combination of multiple types of dampers can be realized. [Brief explanation of the drawings]

[0065] [Figure 1] FIG. 1 is a front view of a wall structure according to a first embodiment of the present disclosure. [Figure 2] FIG. 1 is a front view of a vibration damping device according to a first embodiment of the present disclosure. [Figure 3] FIG. 3 is a cross-sectional view taken along line III-III shown in FIG. 2. [Figure 4] FIG. 3 is a partial enlarged view of a portion F4 shown in FIG. [Figure 5] FIG. 5 is a partial enlarged view of a portion F5 shown in FIG. [Figure 6] 1 is a front view of a friction damper included in a damping device according to a first embodiment of the present disclosure. [Figure 7] 1 is a front cross-sectional view of a friction damper included in a damping device according to a first embodiment of the present disclosure. [Figure 8] FIG. 2 is a front view of a sliding cylinder of the friction damper. [Figure 9] FIG. 9 is a plan view of the sliding cylinder shown in FIG. [Figure 10] 1 is a schematic front view of the vicinity of a friction damper provided in a damping device according to a first embodiment of the present disclosure. [Figure 11] 10 is a schematic diagram showing the movement (vibration) of the interlocking mechanism when the maximum value of the displacement is smaller than the distance G. FIG. [Figure 12] 10 is a schematic diagram showing the movement (vibration) of the interlocking mechanism and the friction unit of the friction damper when the maximum value of the displacement is greater than the distance G. FIG. [Figure 13] FIG. 1 is a graph showing the relationship between story displacement (horizontal axis) and the strength generated by the damping device (vertical axis). [Figure 14] This is a graph showing the relationship between story displacement (horizontal axis) and the strength generated by the damping device (vertical axis) over one period of shaking. [Figure 15] FIG. 11 is a partial front view of a friction damper according to a third modified example. [Figure 16] FIG. 16 is a side view of the friction damper shown in FIG. [Figure 17] FIG. 16 is a cross-sectional view taken along the line XVII-XVII shown in FIG. [Figure 18] FIG. 10 is a conceptual diagram showing deformation of a wall structure as viewed from the front. [Figure 19] 10 is a front cross-sectional view of a friction damper included in a damping device according to a fourth modification. FIG. [Figure 20] FIG. 10 is a front view of a wall structure according to a second embodiment of the present disclosure. [Figure 21] FIG. 4 is a front view of a vibration damping device according to a second embodiment of the present disclosure. [Figure 22] FIG. 4 is a side view of a vibration damping device according to a second embodiment of the present disclosure. [Figure 23] FIG. 23 is a cross-sectional view taken along the line XXIII-XXIII shown in FIG. 22. [Figure 24] FIG. 10 is a perspective view of a friction unit of a friction damper included in a damping device according to a second embodiment of the present disclosure. [Figure 25]FIG. 25 is a front cross-sectional view of the friction unit taken along the line XXV-XXV shown in FIG. 24. [Figure 26] FIG. 10 is a schematic front view of the vicinity of a friction damper of a damping device according to a second embodiment of the present disclosure. [Figure 27] FIG. 22 is a cross-sectional view taken along the line VII-VII shown in FIG. [Figure 28] FIG. 23 is a cross-sectional view taken along line VIII-VIII in FIG. [Figure 29] FIG. 24 is a cross-sectional view taken along line IX-IX shown in FIG. 23. [Figure 30] FIG. 24 is a cross-sectional view taken along the line XX shown in FIG. 23. DETAILED DESCRIPTION OF THE INVENTION

[0066] A damping device, a vibration control device, a wall structure, a wooden house, and a friction damper according to a first embodiment and a second embodiment of the present disclosure will be described with reference to the drawings.

[0067] [First embodiment] The first embodiment will be described below.

[0068] <About the wall structure> As shown in Figure 1, the wall structure 10 is a structure used, for example, in the walls of a wooden house, and comprises a frame-like structure having a first pillar 11 (first structural member) and a second pillar 12 (second structural member) extending vertically on a foundation 14, and beams 15 extending horizontally on each pillar, and a vibration control device 50 arranged from the top of the first pillar 11 to the bottom of the second pillar 12. The frame-shaped structure of the wall structure 10 is manufactured by, for example, a wood-frame construction method. However, this construction method is merely an example, and other construction methods may also be used.

[0069] The base 14 is a piece of wood extending horizontally and is provided on, for example, a foundation (not shown). The base 14 is a member that supports each pillar and transmits vertical loads to the foundation.

[0070] The first pillar 11 is a piece of wood extending in the vertical direction, and its lower end is fitted into one end side (the left side in FIG. 1) of the base 14. The first pillar 11 is a member to which a load is mainly applied in the vertical direction. The dimensions of the first pillar 11 are determined, for example, by standards (construction methods). In this embodiment, the width (horizontal dimension) is 105 mm, the height (vertical dimension) is approximately 2600 mm, and the depth is 105 mm. However, these values ​​are merely examples, and other dimensions may also be used.

[0071] The second pillar 12 is a piece of wood extending in the vertical direction, and its lower end is fitted into the other end side (the right side in FIG. 1) of the base 14. The second pillar 12 is a member to which a load is mainly applied in the vertical direction. The dimensions of the second pillar 12 are determined, for example, by standards (construction methods). In this embodiment, the width is 105 mm, the height is approximately 2600 mm, and the depth is 105 mm. However, these values ​​are merely examples, and other dimensions may also be used. The second pillars 12 are spaced apart from the first pillars 11 in the horizontal direction. The distance (center-to-center pitch) between the first pillars 11 and the second pillars 12 in the horizontal direction is determined, for example, by standards (construction methods). In this embodiment, the pitch is approximately 910 mm. However, these numerical values ​​are merely examples, and other dimensions may also be used.

[0072] The beam 15 is a piece of wood extending horizontally, into which the upper ends of the first pillar 11 and the second pillar 12 are fitted.

[0073] <About vibration control devices> The wall structure 10 according to this embodiment is configured by attaching a vibration damping device 50 to the above-described frame-shaped structure. The vibration damping device 50 will be described in detail below.

[0074] <<Summary>> As shown in Figure 1, the vibration control device 50 is a device comprising a brace 100 and a damping device 200, which are arranged along an axis C connecting a first vibration control device end 51 and a second vibration control device end 52.

[0075] When the vibration damping device 50 is attached to a frame-shaped structure, the first vibration damping device end 51 is positioned at the top of the first pillar 11, and the second vibration damping device end 52 is positioned at the bottom of the second pillar 12, and is arranged diagonally like a brace from the top of the first pillar 11 to the bottom of the second pillar 12. The positions of the first vibration damping device end 51 and the second vibration damping device end 52 may be interchanged as appropriate.

[0076] The first vibration damping device end 51 is attached to the first pillar 11 via a first bracket 301 . The first bracket 301 is fixed to the top of the first pillar 11 with a plurality of screws. The first bracket 301 rotatably supports the first vibration damping device end 51 at a first bracket fulcrum portion 301a, with the rotation axis of the first vibration damping device end 51 extending in the depth direction. The depth direction is a direction that is substantially perpendicular to the vertical and horizontal directions.

[0077] The second vibration damping device end 52 is attached to the second pillar 12 via a second bracket 302 and a connecting rod 303 . The second bracket 302 is fixed to the lower part of the second pillar 12 with a plurality of screws. The second bracket 302 rotatably supports the end of the connecting rod 303, which is connected to the second vibration damping device end 52, at a second bracket fulcrum portion 302a. At this time, the rotation axis of the connecting rod 303 is aligned with the depth direction.

[0078] <<About braces>> As shown in Figure 1, the brace 100 is a metal rod-shaped member extending from a first brace end 101 located on the first column 11 side to a second brace end 102 located on the second column 12 side. The first brace end 101 and the second brace end 102 are located on the axis C. That is, the brace 100 extends along the axis C. The brace 100 is, for example, a circular pipe with a predetermined wall thickness. However, the brace 100 does not necessarily have to be a circular pipe, and may be a pipe with a cross-sectional shape other than a circular shape, a solid bar, or a rectangular timber.

[0079] The first brace end 101 is also the first vibration damping device end 51 described above, and is connected to the first bracket 301 so as to be freely rotatable. As shown in FIGS. 1 and 2, the second brace end 102 is connected to the first damping device end 201 of the damping device 200 .

[0080] <<About the damping device>> The damping device 200 is a device that generates a desired damping force. The damping device 200 has a first damping device end 201 (first end) arranged on the first pillar 11 side and a second damping device end 202 (second end) arranged on the second pillar 12 side. The first damping device end 201 is connected to the second brace end 102 of the brace 100 . The second damping device end 202 is also the second vibration suppression device end 52 described above, and is connected to the connecting rod 303 .

[0081] As shown in FIG. 2, the damping device 200 includes a plurality of dampers that apply damping force, and an interlocking mechanism 230 that interlocks the dampers in a predetermined case.

[0082] The plurality of dampers are, for example, a main damper and a sub damper. The main damper and the sub damper are separate devices, but are configured so that their functions are linked together in a predetermined manner by the linkage mechanism 230. Specifically, the main damper and the sub-damper are configured so that their functions are linked in accordance with the amount of displacement along the axis C of the damping device 200 . More specifically, the damping device 200 is configured so that the main damper functions alone when the displacement (absolute value of the displacement) along the axis C is equal to or less than a predetermined value, and so that both the main damper and the sub-damper function when the displacement (absolute value of the displacement) along the axis C exceeds the predetermined value.

[0083] In other words, the damping device 200 is configured to exert the damping performance of the vibration control device 50 by using the damping force of the main damper for small displacements (small earthquake shaking that occurs frequently), and to exert the damping performance of the vibration control device 50 by using a larger damping force, which is the sum of the damping force of the sub-damper, for large displacements (large earthquake shaking that occurs infrequently). Therefore, it is preferable to use a damper for the main damper that has excellent durability against repeated vibrations and is effective against small earthquake vibrations, and it is preferable to use a damper for the secondary damper that has a large damping force and is particularly effective against large earthquake vibrations.

[0084] In the case of this embodiment, for example, an oil damper 210 is used as the main damper, and a friction damper 220 is used as the sub-damper.

[0085] The displacement along the axis C occurs when the upper part of the first pillar 11 and the lower part of the second pillar 12 move closer to or farther apart due to inter-story displacement that occurs in a wooden house due to earthquake shaking, for example. The inter-story displacement is the amount of horizontal displacement of the beam 15 caused by the inclination of the columns 11 and 12 relative to the foundation 14.

[0086] Here, displacement along the axis C will be explained in detail using an example in which a predetermined inter-story displacement d occurs in the beam 15 due to the columns 11 and 12 tilting by an angle θ relative to the base 14, as shown in Figure 18. The tilt θ is also called the inter-story deformation angle θ. Furthermore, due to geometric relationships, for the same inter-story deformation angle θ, the longer the columns 11 and 12 are, the larger the inter-story displacement d will be. Because the first bracket 301 is fixed to the first pillar 11, the first bracket fulcrum portion 301a of the first bracket 301 to which the first vibration damping device end portion 51 is connected moves horizontally and vertically due to the inclination of the first pillar 11. In addition, because the second bracket 302 is fixed to the second pillar 12, the second bracket fulcrum portion 302a of the second bracket 302 to which the second vibration damping device end portion 52 is connected via the connecting rod 303 moves horizontally and vertically due to the inclination of the second pillar 12. At this time, because the first bracket 301 is fixed to the upper part of the first column 11 and the second bracket 302 is fixed to the lower part of the second column 12, even for the same inter-story deformation angle θ, the amount of movement of the first bracket fulcrum part 301a, which is located above the second bracket fulcrum part 302a, is greater than the amount of movement of the second bracket fulcrum part 302a. Due to a geometric relationship, this difference in movement amount becomes greater as the inter-story deformation angle θ increases and as the first bracket fulcrum part 301a and the second bracket fulcrum part 302a are separated from each other in the vertical direction. This difference in the amount of movement causes a difference between the length of the line segment L1 (shown by a solid line in FIG. 18, coinciding with the axis C) connecting the first bracket fulcrum portion 301a and the second bracket fulcrum portion 302a before deformation and the length of the line segment L2 (shown by a two-dot chain line in FIG. 18, coinciding with the axis C) connecting the first bracket fulcrum portion 301a and the second bracket fulcrum portion 302a after deformation. In other words, the first bracket fulcrum portion 301a at the top of the column 11 becomes relatively closer to or farther from the second bracket fulcrum portion 302a at the bottom of the second column 12. The amount of separation or proximity between the first bracket fulcrum portion 301a and the second bracket fulcrum portion 302a is reflected as the amount of separation or proximity between the first vibration damping device end portion 51 and the second vibration damping device end portion 52 in the damping device 200, resulting in a displacement along the axis C.

[0087] The detailed configurations of the oil damper 210, the friction damper 220, and the interlocking mechanism 230 will be described below.

[0088] As shown in FIGS. 2 and 3, the oil damper 210 includes a cylinder 211 and a rod 212 extending in the direction of the axis C. The cylinder 211 is a cylindrical housing that houses a part of the rod 212. Since the cylinder 211 is a cylindrical housing, its cross-sectional shape (the cross-sectional shape in a cut surface perpendicular to the axis C) is circular. The rod 212 is a rod-shaped part that moves forward and backward along the axis C relative to the cylinder 211 .

[0089] The friction damper 220 includes a sliding rod 221 (sliding member) and a friction unit Uf. The friction unit Uf has a sliding cylinder 222 (sliding member, cylindrical part) and a holding unit Uh that holds the sliding cylinder 222. The holding unit Uh has a holding block 223 (holding member) into which the sliding tube 222 is fitted, a pressing block 224 (pressing member) that presses the sliding tube 222 toward the holding block 223, and a plurality of fastening members 225 that fasten the holding block 223 and the pressing block 224 together. The slidable rod 221, the holding block 223 and the pressing block 224 are made of, for example, metal.

[0090] The interlocking mechanism 230 includes a connection block 231, a main damper side member 232, a sub-damper side member 233, a first frame block 234 (first frame member), and a second frame block 235 (second frame member). Each part constituting the interlocking mechanism 230 is made of, for example, metal.

[0091] The base end of the oil damper 210 is connected to the connecting block 231 of the interlocking mechanism 230. Here, the "base end of the oil damper 210" refers to the end of the cylinder 211 on the side where the rod 212 does not protrude. On the other hand, the end of the cylinder 211 on the side where the rod 212 protrudes is referred to as the "tip end of the cylinder 211." This connecting block 231 is also a component that is connected to the second brace end portion 102 of the brace 100, and its upper end is the first damping device end portion 201 described above.

[0092] One end of each of two main damper side members 232 extending in the direction of the axis C is connected to the side surface of the connecting block 231. As shown in Figure 4, the other ends of the two main damper side members 232 are located closer to the second damping device end 202 than the tip of the rod 212 of the oil damper 210 when it is at least in the stopped position, and are connected to the side of the first frame block 234 arranged between them (the two main damper side members 232). The stop position means the initial position, the position before the earthquake, the position where the displacement along axis C is zero, the position of the center of shaking / vibration, or the position where the inter-story displacement is zero, etc.

[0093] 4 and 5, in addition to the main damper side member 232, one end of each of two auxiliary damper side members 233 extending in the direction of the axis C is connected to the side surface of the first frame block 234. In other words, the main damper side member 232 and the auxiliary damper side member 233 are connected and integrated by the first frame block 234. The other ends of the two sub-damper side members 233 are connected to the side surfaces of the second frame block 235 disposed between them. At this time, a space for providing the friction unit Uf of the friction damper 220 is secured between the two opposing sub-damper side members 233 and between the first frame block 234 and the second frame block 235.

[0094] As described above, the connecting block 231, the two main damper side members 232, the two sub-damper side members 233, the first frame block 234, and the second frame block 235 included in the interlocking mechanism 230 are connected to one another and can therefore be regarded as a single unit in the damping device 200. Therefore, the respective members included in the interlocking mechanism 230 do not need to be separate members as described above, and may be appropriately integrated (made into a single component). Furthermore, the interlocking mechanism 230 is connected to the cylinder 211 of the oil damper 210 via the connecting block 231, and therefore can be regarded as an integrated part of the damping device 200. The method of connecting the members included in the interlocking mechanism 230 is not particularly limited, and any connection method such as welding or fastening can be appropriately selected.

[0095] The end of the rod 212 protruding from the cylinder 211 of the oil damper 210 is connected to a slidable rod 221 . The sliding rod 221 is a rod-shaped part that extends along the axis C and has a diameter of, for example, about 15 mm to 30 mm. This sliding rod 221 is also a component that is connected to the connecting rod 303, and its tip is the second damping device end portion 202 described above. The sliding rod 221, the rod 212, and the connecting rod 303 are connected to one another and can therefore be regarded as a single unit in the damping device 200. Therefore, the sliding rod 221, the rod 212, and the connecting rod 303 do not have to be separate bodies as described above, and may be appropriately integrated (made into a single component).

[0096] The slidable rod 221 is inserted along the axis C while in contact with a sliding bush 234b pressed into the through hole 234a of the first frame block 234 and a sliding bush 235b pressed into the through hole 235a of the second frame block 235. The sliding bush 234b and the sliding bush 235b are components that hold the slidable rod 221 in the radial direction while smoothly moving it in the direction of the axis C, and are, for example, self-lubricating sliding bearings. By providing the sliding bush 234b and the sliding bush 235b, the radial vibration and deflection of the slidable rod 221 are prevented, and the input of the load along the direction of the axis C transmitted by the slidable rod 221 is stabilized. This prevents the rigidity of the damping device 200 from decreasing, and in turn prevents the rise of the yield strength (damping force) that the damping device 200 can exert from becoming gradual.

[0097] Between the two opposing sub-damper side members 233 and between the first frame block 234 and the second frame block 235, a friction unit Uf (a holding unit Uh that holds the sliding cylinder 222) is provided. The friction unit Uf can be regarded as an integrated unit in the damping device 200. Therefore, the members included in the friction unit Uf do not have to be separate bodies as described above, and may be appropriately integrated (made into one part). The friction unit Uf is inserted through the sliding rod 221. However, the friction unit Uf cannot move freely relative to the sliding rod 221, but moves while generating friction between the friction unit Uf and the sliding rod 221 when a certain force is applied.

[0098] As shown in FIGS. 8 and 9, the sliding cylinder 222 is a member through which the slidable rod 221 is inserted, and includes a cylinder main body 222a and a friction material 222b.

[0099] The cylindrical main body 222a is a cylindrical component having a predetermined inner diameter and extending along the axis C with the axis C as its center. The dimension of the cylindrical main body 222a along the direction of the axis C is, for example, about 15 mm to 30 mm. The cylindrical body 222a is made of, for example, metal. The cylindrical body 222a has a tapered cylindrical portion 222a1 whose outer diameter is tapered. The cylindrical body 222a is formed with a vertical slit 222a2 extending along the direction of the axis C. That is, the shape of the cylindrical body 222a when viewed from above in the direction of the axis C is C-shaped with two opposing ends.

[0100] The friction material 222b is a cylindrical part / portion having a predetermined inner diameter and centered on the axis C and extending along the axis C, and is provided on the inner circumferential surface of the cylindrical main body 222a. Therefore, the outer diameter of the friction material 222b is approximately the same as the inner diameter of the cylindrical main body 222a. The friction material 222b is, for example, a metal-based oil-free bearing in which a solid lubricant is dispersed in metal. By using a metal-based oil-free bearing for the friction material 222b, it is possible to improve durability against repeated sliding between the friction material 222b and the sliding rod 221. The type of friction material 222b can be changed as appropriate depending on the required friction force (damping force). The friction material 222b is formed with a vertical slit 222b2 extending along the direction of the axis C. That is, the shape of the friction material 222b in plan view from the direction of the axis C is C-shaped with two opposing ends. The position of the vertical slit 222b2 corresponds to the position of the vertical slit 222a2 of the tube main body 222a, for example. The inner diameter of the friction material 222b is approximately the same as the outer diameter of the slidable rod 221, and the inner peripheral surface of the friction material 222b is in contact with the outer peripheral surface of the slidable rod 221 inserted into the sliding cylinder 222 with a predetermined contact force. As a result, when the sliding cylinder 222 moves along the axis C relative to the slidable rod 221, friction occurs between the sliding cylinder 222 (friction material 222b) and the slidable rod 221. The force required to move the sliding cylinder 222 relative to the slidable rod 221 (force resisting the frictional force) becomes the damping force of the friction damper 220.

[0101] As shown in FIGS. 6 and 7, the sliding cylinder 222 through which the slidable rod 221 is inserted is held by a holding unit Uh having a holding block 223, a pressing block 224, and a fastening member 225. The form will be specifically described below.

[0102] The sliding cylinder 222 is fitted into a through hole 223 a formed in the holding block 223 . The through hole 223a is a hole formed along the axis C, and has a tapered hole portion 223a1 with a tapered inner diameter and a straight hole portion 223a2 with a substantially constant inner diameter. The slidable rod 221 is inserted through the through hole 223a without contacting the rod 221. However, as described above, the sliding cylinder 222 fitted into the through hole 223a is in contact with the slidable rod 221.

[0103] The inclination gradient of the tapered hole portion 223a1 is approximately the same as the inclination gradient of the tapered tube portion 222a1 of the tube main body 222a. At this time, the minimum diameter of tapered hole portion 223a1 is smaller than the minimum diameter of tapered tubular portion 222a1, and the maximum diameter of tapered hole portion 223a1 is larger than the minimum diameter of tapered tubular portion 222a1 and smaller than the maximum diameter of tapered tubular portion 222a1. The tapered tube portion 222a1 of the tube main body 222a is fitted into the tapered hole portion 223a1 having such dimensions.

[0104] When the tapered tubular portion 222a1 is fitted into the tapered hole portion 223a1, the sliding tube 222 is pushed into the through-hole 223a (tapered hole portion 223a1), but since the vertical slit 222a2 is formed in the tube main body 222a and the vertical slit 222b2 is formed in the friction material 222b, the inner diameters of the tube main body 222a and the friction material 222b are deformed in a direction that reduces the inner diameters due to contact between the tapered tubular portion 222a1 of the tube main body 222a and the tapered hole portion 223a1 of the holding block 223. At this time, due to a wedge effect caused by the shape of the tapered tubular portion 222a1, the inner peripheral surface of the sliding tube 222 (friction material 222b) can be brought into contact with the outer peripheral surface of the slidable rod 221 with a strong contact force with a small pushing force. As a result, even if a metal-based oil-free bearing is used for the friction material 222b, sufficient friction can be generated between the friction material 222b and the sliding rod 221. Furthermore, by adjusting the amount of pressing of the sliding cylinder 222 into the through-hole 223a (tapered hole portion 223a1), the contact force of the inner circumferential surface (friction material 222b) of the sliding cylinder 222 with the sliding rod 221 can be adjusted, and the friction force for generating a desired damping force can be set in the friction damper 220.

[0105] Here, the inclination gradient of the tapered tubular portion 222a1 that generates the wedge effect is set to, for example, 1 degree or more and 10 degrees or less. By setting the inclination gradient to about 1 degree, the amount of radial deformation of the tube main body 222a relative to the amount of pressing of the sliding tube 222 can be reduced, allowing for fine adjustment of the contact force (frictional force). On the other hand, by setting the inclination gradient to about 10 degrees, the wedge effect resulting from the shape of the tapered tube portion 222a1 can be efficiently exerted. In this embodiment, the inclination gradient of the tapered tube portion 222a1 is set as described above, taking into consideration the balance between these lower and upper limit values.

[0106] The sliding cylinder 222 fitted into the through hole 223a is pressed toward the holding block 223 by a pressing block 224. The pressing block 224 is fixed to the holding block 223 by a fastening member 225. This prevents the sliding cylinder 222 from slipping out of the through hole 223a of the holding block 223. In other words, it prevents the amount of pressing of the sliding cylinder 222 into the through hole 223a from becoming smaller than a set value. The pressing block 224 is formed with a through hole 224a, through which the slidable rod 221 is inserted without contact.

[0107] The fastening member 225 is, for example, a bolt, and is inserted from the pressure block 224 side toward the holding block 223, with the head housed in a countersink formed in the pressure block 224 and the tip of the shaft (external thread) screwed into an internal threaded hole formed in the holding block 223. The fastening member 225 may be inserted from the holding block 223 side toward the pressing block 224. In this case, a counterbore is formed in the holding block 223, and an internally threaded hole is formed in the pressing block 224.

[0108] In this manner, the sliding cylinder 222 is held by the holding unit Uh.

[0109] The nominal length L of the bolt serving as the fastening member 225 is preferably set to be twice the diameter of the slidable rod 221 or more. The reasons for this are explained below.

[0110] It is assumed that in the initial state in which sliding tube 222 is pushed in, an axial force is acting on the bolt shank, and that this causes an axial deformation (elastic deformation) of ΔL1 in the bolt shank (the shank other than the portion threaded into the female threaded hole) that makes it longer than the unloaded length L. In other words, the length of the bolt shank when an axial force is acting is L + ΔL1, and there is a margin for pushing presser block 224 toward holding block 223 by ΔL1. Here, if the friction material 222b and / or the outer surface of the sliding rod 221 are slightly worn and the amount of depression of the sliding tube 222 must be increased by ΔL2 (<ΔL1) from the initial amount of depression in order to maintain the contact force, this ΔL2 can be compensated for by the axial deformation ΔL1. In this case, the axial deformation ΔL1 can be ensured to be large as the bolt nominal length L is longer. This is because the amount of elastic deformation allowable in the shank per unit length is determined by the bolt material, etc., and therefore the longer the bolt nominal length L, the greater the overall elastic deformation that can be achieved. Therefore, by making the bolt nominal length L at least twice the diameter of the sliding rod 221, the axial deformation ΔL1 can be ensured sufficiently.

[0111] <<About the movement of the damping device>> The damping device 200 can be roughly divided into an integrated body including the interlocking mechanism 230 and the cylinder 211 of the oil damper 210, an integrated body including the slidable rod 221 and the rod 212, and a friction unit Uf. Therefore, in the following explanation, a schematic diagram in which the boundaries between the members constituting each integrated body are omitted will be used, as shown in, for example, FIG. 10.

[0112] The interlocking mechanism 230 includes a frame body that holds the friction unit Uf in the direction of the axis C. In this embodiment, this frame is composed of a secondary damper side member 233, a first frame block 234, and a second frame block 235, and is connected to the base end of the cylinder 211 of the oil damper 210 via the main damper side member 232 and the connecting block 231.

[0113] 10 , when the damping device 200 is at the stop position, a predetermined distance G is provided as a gap between the frame and the friction unit Uf in the direction of the axis C. In detail, when the damping device 200 is at the stop position, a predetermined distance G is provided as a gap between the first frame block 234 and the presser block 224 and between the second frame block 235 and the holding block 223. When the damping device 200 in the stopped position is displaced along the axis C (i.e., when the first damping device end 201 and the second damping device end 202 shown in Figure 2 move closer to or away from each other along the axis C), the interlocking mechanism 230 having the first damping device end 201 and the cylinder 211 of the oil damper 210 connected to the interlocking mechanism 230 will move along the axis C relative to the sliding rod 221 having the second damping device end 202 and the rod 212 connected to the sliding rod 221. In the damping device 200 shown in FIGS. 11 and 12, for ease of explanation, only the position of the interlocking mechanism 230 is moved.

[0114] As shown in FIG. 11, when the maximum value of the displacement along the axis C (amplitude along the axis C) is smaller than the distance G, the interlocking mechanism 230 moves within a range where it does not come into contact with the friction unit Uf. In FIG. 11, the displacement is designated as A1.

[0115] At this time, in order to move the interlocking mechanism 230, a force is required to move the cylinder 211 of the oil damper 210 connected to the interlocking mechanism 230 relative to the rod 212. This causes the oil damper 210 to apply a damping force.

[0116] As shown in FIG. 12, when the maximum value of the displacement along the axis C is greater than the distance G, the interlocking mechanism 230 comes into contact with the friction unit Uf and then moves together with the friction unit Uf while maintaining contact with the friction unit Uf. 12, the displacement is A2. At this time, the amount of movement of the friction unit Uf from the stop position is A2-G. Specifically, the contact between the interlocking mechanism 230 and the friction unit Uf means the contact between the second frame block 235 of the interlocking mechanism 230 and the holding block 223 of the friction unit Uf, or the contact between the first frame block 234 of the interlocking mechanism 230 and the pressing block 224 of the friction unit Uf (see Figures 5 and 10).

[0117] Until the interlocking mechanism 230 comes into contact with the friction unit Uf, a damping force is applied only by the oil damper 210, using the same principle as described above. In other words, until the interlocking mechanism 230 comes into contact with the friction unit Uf, the damping performance of the damping device 200 is exerted mainly by the oil damper 210. After the interlocking mechanism 230 comes into contact with the friction unit Uf, the friction unit Uf moves together with the interlocking mechanism 230 relative to the slidable rod 221 connected to the rod 212 of the oil damper 210. At this time, in order to move the interlocking mechanism 230, a force to move the friction unit Uf (i.e., a force that resists the friction force generated by the friction F) is required in addition to a force to move the cylinder 211 of the oil damper 210 connected to the interlocking mechanism 230 relative to the rod 212. This results in an additional damping force being applied by the friction damper 220. In other words, after the interlocking mechanism 230 comes into contact with the friction unit Uf, the damping performance of the damping device 200 is exerted by the oil damper 210 and the friction damper 220.

[0118] The oil damper 210 used in this embodiment is preferably of a type having bilinear characteristics, for example. The bilinear characteristic is a characteristic in which the strength rises sharply between the stop position of the rod 212 and a predetermined displacement, and then maintains the strength at an approximately constant level after the predetermined displacement (including cases where the strength gradient is gentler than the gradient at the time of rise). The rise in the proof stress (kN) is set to a gradient of, for example, 0.8 kN / mm or more relative to the displacement (mm) along the axis C of the rod 212. Expressed in relation to the story drift angle θ (rad), the rise in the proof stress (kN) is set to a gradient of 1.5 kN at 1 / 500 rad. Note that this proof stress gradient is exerted at least when the beam 15 is displaced (vibrated) in the horizontal direction with an amplitude of approximately 2.8 mm and a frequency of approximately 2 Hz. However, these numerical values ​​are merely examples, and other numerical values ​​may be used.

[0119] FIG. 13 is a graph showing the relationship between the inter-story displacement (horizontal axis) and the yield strength (vertical axis) generated in the damping device 200 when an oil damper 210 having a bilinear characteristic is used. In this graph, it is assumed that the interlocking mechanism 230 is configured to come into contact with the friction unit Uf when the inter-story displacement exceeds d2. As described above, the inter-story displacement has a predetermined relationship with the displacement along the axis C of the damping device 200.

[0120] First, when inter-story displacement occurs due to earthquake shaking, the oil damper 210 functions independently in the range from the stop position to d2. In other words, the damping force of the damping device 200 is provided solely by the oil damper 210. At this time, the bearing capacity rises sharply when the inter-story displacement is in the range from zero (stop position) to d1. On the other hand, when the inter-story displacement is in the range from d1 to d2, the bearing capacity remains approximately constant. These behaviors are due to the bilinear characteristics of the oil damper 210.

[0121] When the inter-story displacement further increases and exceeds d2, the interlocking mechanism 230 comes into contact with the friction unit Uf, and the friction damper 220 additionally functions. In other words, the damping force of the damping device 200 is provided by the oil damper 210 and the friction damper 220. At this time, the bearing force rises again in the range exceeding d2. This is due to the damping force of the friction damper 220 that is additionally applied.

[0122] 13 represents the profile of the strength when only the oil damper 210 functions over the entire range of story displacement. This is not included in this embodiment, but is shown for reference.

[0123] As described above, the damping device 200 is divided into two types, with the inter-story displacement d2 as the boundary, namely, whether only the oil damper 210 functions or whether both the oil damper 210 and the friction damper 220 function. Considering that the value of the inter-story displacement (d2 in FIG. 13) when the interlocking mechanism 230 comes into contact with the friction unit Uf depends on the distance G between the first frame block 234 and the presser block 224, the value of d2 can be adjusted by adjusting the distance G. In other words, if the value of the inter-story displacement that can occur due to a relatively frequent small earthquake shaking (earthquake shaking that is mainly to be handled by the oil damper 210) is set in advance to d2, it is possible to determine the distance G so as to target the value of the inter-story displacement d2. Taking into account the bilinear characteristics of the oil damper 210, the distance G is set to, for example, 1 mm or more and 5 mm or less.

[0124] Figure 14 shows the relationship between the inter-story displacement (horizontal axis) and the strength (vertical axis) generated by the damping device 200 within the range of one period of vibration when an oil damper 210 with bilinear characteristics is used. As is clear from this, the yield strength increases in the range where the damping force is additionally applied by the friction damper 220 (shown by the dashed square in FIG. 14).

[0125] [Variation 1] In the above description, the oil damper 210, which is a type of fluid damper, is used as the main damper, and the friction damper 220, which is a type of hysteretic damper, is used as the sub-damper, but other types or combinations of dampers may also be used. For example, a hysteretic damper that has excellent durability against repeated vibrations and starts to work with small earthquake vibrations may be combined with another hysteretic damper that is effective against large earthquake vibrations, or a fluid damper that has excellent durability against repeated vibrations and starts to work with small earthquake vibrations may be combined with a viscoelastic damper that is effective against large earthquake vibrations.

[0126] [Variation 2] In the above description, the oil damper 210 is of a type having a bilinear characteristic, but this characteristic is not essential, and for example, a normal oil damper may be used. In either case, oil dampers generally have excellent durability against repeated use and are effective against small earthquake vibrations, so by using oil dampers to absorb the relatively frequent small earthquake vibrations, small earthquake vibrations can be effectively suppressed.

[0127] [Variation 3] The friction damper 220 generates a friction force between the slidable rod 221 and the sliding cylinder 222, but is not limited to this configuration as long as it has a structure that can generate friction. For example, as shown in Figures 15 to 17, a sliding plate 421 (sliding member) having a long hole 421a formed along the direction of axis C may be sandwiched between two clamping plates 422 (sliding members) and held in place by bolt and nut type fastening members 423, thereby generating frictional force between the sliding plate 421 and each clamping plate 422. In this case, the slide plate 421 is connected to the rod 212 of the oil damper 210 , and the clamping plate 422 is enclosed by the frame of the interlocking mechanism 230 .

[0128] Each of the holding plates 422 has a plate body 422a and a friction material 422b provided on the surface of the plate body 422a, and the friction material 422b comes into contact with the sliding plate 421. The contact force of the friction material 422b against the slid plate 421 is adjusted by the fastening force of the fastening member 423 transmitted via the plate body 422a.

[0129] [Variation 4] As shown in FIG. 19, the friction damper 220 may include a spacer 226 . The spacer 226 is, for example, a cylindrical part having a predetermined inner diameter and outer diameter and extending along the axis C with the axis C as its center. The spacer 226 is made of, for example, metal. A step surface 223a3 is formed at the boundary between the tapered hole portion 223a1 and the straight hole portion 223a2 of the through hole 223a, and one end face of the spacer 226 contacts the step surface 223a3. In contrast, the end of the sliding tube 222 contacts the other end face of the spacer 226. This prevents the sliding tube 222 from being pushed more than necessary into the through hole 223a of the holding block 223. In other words, the amount of pushing of the sliding tube 222 into the through hole 223a is regulated, preventing the amount of pushing from exceeding a set value. The inner diameter of the spacer 226 is set to a dimension that does not contact the sliding rod 221. This is to prevent the spacer 226 from applying a frictional force to the sliding rod 221 that is not anticipated in the design. The outer diameter of spacer 226 is set to a dimension that is equal to or smaller than the inner diameter of tapered hole portion 223a1 of through hole 223a and larger than the inner diameter of straight hole portion 223a2 of through hole 223a, in order to bring one end face of spacer 226 into contact with step surface 223a3 of through hole 223a.

[0130] The amount of pressing of the sliding tube 222 into the through hole 223a may be adjusted by preparing a plurality of types of spacers 226 having different dimensions along the direction of the axis C, or by adjusting the dimensions of the spacers 226.

[0131] [Variation 5] The friction damper 220 described in this embodiment does not necessarily have to be used in combination with another damper (for example, the oil damper 210), and for example, the friction damper 220 can also be used alone.

[0132] [Effects of this embodiment] According to this embodiment, the following effects are achieved. When the displacement along the axis C is equal to or less than a predetermined value, only the main damper (e.g., oil damper 210) functions, and when the displacement exceeds the predetermined value, both the main damper and the auxiliary damper (e.g., friction damper 220) function. Therefore, for small earthquake vibrations, the damping performance of the device is exerted by the damping force of the main damper, and for large earthquake vibrations, the damping performance of the device is exerted by a larger damping force obtained by adding the damping force of the auxiliary damper. Therefore, for example, small earthquakes that occur frequently can be handled by the main damper, and large earthquakes that occur infrequently can be handled by the main damper and the sub-damper. This allows for a combination of multiple types of dampers that utilize the unique properties of the dampers, for example, by using a damper for the main damper that has excellent durability against repeated vibrations and is effective against small earthquake vibrations, and a damper for the sub-damper that has a large damping force and is particularly effective against large earthquake vibrations, thereby providing a damping device 200 that can handle vibrations from small to large earthquakes and that also takes into consideration durability against repeated vibrations.

[0133] When the main damper is an oil damper 210, it has excellent durability against repeated vibrations and is also effective against small earthquake vibrations.

[0134] When the sub-damper is the friction damper 220, it is easy to set a large damping force.

[0135] When the displacement exceeds a predetermined value, the interlocking mechanism 230 causes the sliding cylinder 222 to slide relative to the slidable rod 221, so that when the displacement exceeds the predetermined value, the oil damper 210 and the friction damper 220 can be connected in parallel. This makes it possible to apply additional damping force by the friction damper 220 when the displacement exceeds the predetermined value.

[0136] The frame holds the friction unit Uf (the holding unit Uh that holds the sliding cylinder 222) with a gap in the direction of the axis C, so when the friction unit Uf moves within a range where the gap does not become zero, the friction unit Uf does not come into contact with the frame, and the sliding cylinder 222 does not slide relative to the sliding rod 221. On the other hand, when the gap becomes zero and the friction unit Uf moves together with the frame, the friction unit Uf moves relative to the sliding rod 221, and the sliding cylinder 222 included in the friction unit Uf slides relative to the sliding rod 221, generating a frictional force.

[0137] The holding unit Uh has a holding block 223 having a through hole 223a formed therein into which the sliding tube 222 is fitted along the axis C, and a pressing block 224 that presses the sliding tube 222 toward the holding block 223 (through hole 223a), and these are fastened together with a bolt as a fastening member 225, so that the sliding tube 222 can be held with a simple configuration. Furthermore, since the pressing block 224 presses down on the sliding tube 222, the sliding tube 222 can be prevented from slipping out of the through hole 223a of the holding block 223.

[0138] The sliding cylinder 222 has a tapered cylinder portion 222a1 whose outer diameter decreases and a vertical slit 222a2 along the axis C, and the tapered cylinder portion 222a1 of the sliding cylinder 222 is fitted into the through hole 223a of the holding block 223, so that the force pressing the sliding cylinder 222 toward the holding block 223 (through hole 223a) can be converted into a radial force that changes the inner diameter of the sliding cylinder 222 by contact between the tapered cylinder portion 222a1 and the through hole 223a. This makes it possible to change the contact force of the sliding cylinder 222 with the inserted slidable rod 221, and adjust the frictional force generated between the sliding cylinder 222 and the slidable rod 221. Furthermore, due to the wedge effect caused by the shape of the tapered cylindrical portion 222a1, the inner peripheral surface (friction material 222b) of the sliding cylinder 222 can be brought into contact with the outer peripheral surface of the slidable rod 221 with a strong force with a small pushing force.

[0139] The tapered tube portion 222a1 of the sliding tube 222 has an inclination gradient of 1 degree or more and 10 degrees or less, so that the amount of radial deformation of the tube main body 222a in response to the amount of pressing of the sliding tube 222 can be efficiently controlled, and the wedge effect can be efficiently exerted.

[0140] The portion of the sliding cylinder 222 that comes into contact with the outer peripheral surface of the slidable rod 221 is a metal-based oil-free bearing, which improves durability against repeated sliding between the sliding cylinder 222 and the slidable rod 221. Even if the portion of the sliding cylinder 222 that comes into contact with the outer peripheral surface of the slidable rod 221 is a metal-based oil-free bearing, sufficient frictional force can be ensured by pressing it against the outer peripheral surface of the slidable rod 221 with a strong force that utilizes the wedge effect. Furthermore, for example, by combining a sliding tube 222 having a tapered cylindrical portion 222a1 (a structure that generates a wedge effect) with a metal-based oil-free bearing, a friction damper 220 that takes into consideration strong frictional force and durability can be provided.

[0141] The sliding bushes 234b and 235b hold the slidable rod 221 in the radial direction, and therefore prevent the slidable rod 221 from vibrating or bending in the radial direction, thereby stabilizing the input of the load along the direction of the axis C transmitted by the slidable rod 221. This makes it possible to prevent the rigidity of the damping device 200 from decreasing, and in turn to prevent the rise of the yield strength (damping force) that the damping device 200 can exert from becoming gradual.

[0142] The oil damper 210 is of a type having bilinear characteristics, and is therefore capable of exerting damping force even in the early stages of a small earthquake.

[0143] [Second embodiment] The second embodiment will be described below. The same components as those in the first embodiment are denoted by the same reference numerals and the description thereof will be omitted.

[0144] <About the wall structure> As shown in Figure 20, the wall structure 10 is a structure used, for example, in the walls of a wooden house, and comprises a frame-like structure having a first pillar 11 (first structural member) and a second pillar 12 (second structural member) extending vertically on a foundation 14, and beams 15 extending horizontally on each pillar, and a vibration control device 50 arranged from the top of the first pillar 11 to the bottom of the second pillar 12.

[0145] <About vibration control devices> The wall structure 10 according to this embodiment is configured by attaching a vibration damping device 50 to a frame-shaped structure, similar to the first embodiment. The vibration damping device 50 will be described in detail below.

[0146] <<Summary>> As shown in Figure 20, the vibration control device 50 is a device that includes a brace 100 and a damping device 200, which are arranged along an axis C connecting the first vibration control device end 51 and the second vibration control device end 52.

[0147] When the vibration damping device 50 is attached to a frame-shaped structure, the first vibration damping device end 51 is positioned at the bottom of the second pillar 12, and the second vibration damping device end 52 is positioned at the top of the first pillar 11, and is arranged diagonally like a brace from the top of the first pillar 11 to the bottom of the second pillar 12. The positions of the first vibration damping device end 51 and the second vibration damping device end 52 may be interchanged as appropriate.

[0148] The first vibration damping device end 51 is attached to the second pillar 12 via a first bracket 301 . The first bracket 301 is fixed to the lower part of the second pillar 12 with a plurality of screws. The first bracket 301 rotatably supports the first vibration damping device end 51 at a first bracket fulcrum portion 301a, with the rotation axis of the first vibration damping device end 51 extending in the depth direction. The depth direction is a direction that is substantially perpendicular to the vertical and horizontal directions.

[0149] The second vibration damping device end 52 is attached to the first pillar 11 via a second bracket 302 and a connecting rod 303 . The second bracket 302 is fixed to the top of the first pillar 11 with a plurality of screws. The second bracket 302 rotatably supports the end of the connecting rod 303, which is connected to the second vibration damping device end 52, at a second bracket fulcrum portion 302a. At this time, the rotation axis of the connecting rod 303 is aligned with the depth direction.

[0150] <<About braces>> As shown in Figure 20, the brace 100 is a metal rod-shaped member extending from a first brace end 101 located on the second column 12 side to a second brace end 102 located on the first column 11 side.

[0151] <<About the damping device>> The damping device 200 is a device that generates a desired damping force. The damping device 200 has a first damping device end 201 arranged on the second pillar 12 side and a second damping device end 202 arranged on the first pillar 11 side.

[0152] As shown in FIGS. 21 to 23, the damping device 200 includes a plurality of dampers that apply damping force, and an interlocking mechanism 230 that interlocks the dampers in a predetermined case.

[0153] The plurality of dampers are, for example, a main damper and a sub damper. In the case of this embodiment, for example, an oil damper 210 is used as the main damper, and a friction damper 220 is used as the sub-damper.

[0154] The friction damper 220 includes a sliding rod 221 and a friction unit Uf. The friction unit Uf has a sliding cylinder 222 and a holding unit Uh that holds the sliding cylinder 222. The holding unit Uh has a holding block 223 into which the sliding tube 222 is fitted, a pressing block 224 that presses the sliding tube 222 against the holding block 223, and a plurality of screw members 225' that fasten the holding block 223 and the pressing block 224 together. The holding block 223 and the pressing block 224 are cylindrical members. Because the holding block 223 and the pressing block 224 are cylindrical members, their cross-sectional shapes are circular. Furthermore, because the cross-sectional shapes of the holding block 223 and the pressing block 224 that form the outer shape of the holding unit Uh are circular, it can be said that the cross-sectional shape of the holding unit Uh as a whole is also approximately circular. The outer diameters of the holding block 223 and the pressing block 224 are smaller than the outer diameter of the cylinder 211 of the oil damper 210, for example.

[0155] The interlocking mechanism 230 includes a connection block 231, a side plate 236 (side member), a first frame block 234, and a second frame block 235.

[0156] The side plate 236 is a thin metal plate extending in the direction of the axis C. The two side plates 236 are disposed facing each other with the cylinder 211 of the oil damper 210 sandwiched between them. One end of each of the two side plates 236 is connected to a side surface of the connecting block 231 disposed between them (for example, by fastening with bolts 237). As a result, the two side plates 236 are indirectly connected to the base end of the cylinder 211 via the connecting block 231. The other ends of the two side plates 236 are located closer to the second damping device end 202 than the tip of the rod 212 of the oil damper 210 when it is at least in the stopped position, and are connected to the sides of the first frame block 234 and the second frame block 235 arranged between them (the two side plates 236) (for example, by fastening with bolts 238 and 239).

[0157] The connecting block 231 is a cylindrical member connected to the base end of the cylinder 211 of the oil damper 210 . The connecting block 231 is a cylindrical member, and therefore has a circular cross section. The outer diameter of the connecting block 231 is approximately equal to the outer diameter of the cylinder 211 of the oil damper 210, for example. The connecting block 231 is made of, for example, metal.

[0158] The first frame block 234 and the second frame block 235 are cylindrical members arranged at a distance in the direction of the axis C between two opposing side plates 236. Because the first frame block 234 and the second frame block 235 are cylindrical members, their cross-sectional shapes are circular. The outer diameters of the first frame block 234 and the second frame block 235 are approximately equal to the outer diameter of the cylinder 211 of the oil damper 210, for example. The first frame block 234 is disposed between the second frame block 235 and the tip of the cylinder 211 of the oil damper 210 in the direction of the axis C. The first frame block 234 and the second frame block 235 are made of, for example, metal.

[0159] Between the two opposing side plates 236 and between the first frame block 234 and the second frame block 235, a space for providing the friction unit Uf of the friction damper 220 is secured.

[0160] As described above, the connecting block 231, the two side plates 236, the first frame block 234, and the second frame block 235 included in the interlocking mechanism 230 are connected to one another, and can therefore be regarded as an integrated unit in the damping device 200. Therefore, the respective members included in the interlocking mechanism 230 do not need to be separate bodies as described above, and may be appropriately integrated (made into a single component).

[0161] As in the first embodiment, in order to prevent the slidable rod 221 from vibrating or bending in the radial direction, the sliding bush 234b may be provided in the first frame block 234, and the sliding bush 235b may be provided in the second frame block 235.

[0162] Between the two opposing side plates 236 and between the first frame block 234 and the second frame block 235, a friction unit Uf (a holding unit Uh that holds the sliding cylinder 222) is provided.

[0163] As shown in Figures 24 and 25, the screw member 225' is, for example, a bolt, and is inserted from the holding block 223 side toward the pressing block 224, with the head housed in a countersink formed in the holding block 223 and the tip of the shaft (external thread) screwing into an internally threaded hole formed in the pressing block 224. The screw member 225' may be inserted from the pressing block 224 side toward the holding block 223. In this case, a counterbore is formed in the pressing block 224, and an internally threaded hole is formed in the holding block 223. In the present embodiment in which the cylindrical holding block 223 and the cylindrical pressing block 224 are employed, the number of screw members 225' is preferably three or more (four in FIG. 24). By arranging the screw members 225' at equal angular intervals in the circumferential direction around the axis C, the sliding cylinder 222 can be pressed down evenly in the circumferential direction.

[0164] <<About the movement of the damping device>> The damping device 200 can be roughly divided into an integrated unit including the interlocking mechanism 230 and the cylinder 211 of the oil damper 210, an integrated unit including the slidable rod 221 and the rod 212, and a friction unit Uf. Following Fig. 10, Fig. 26 shows a schematic diagram in which the boundaries between the members constituting each integrated unit are omitted.

[0165] The interlocking mechanism 230 includes a frame body that holds the friction unit Uf in the direction of the axis C. In this embodiment, the frame is composed of a side plate 236, a first frame block 234, and a second frame block 235, and is connected to the base end of the cylinder 211 of the oil damper 210 via a connecting block 231 connected to the side plate 236.

[0166] The operation of the damping device is the same as in the first embodiment, so only a brief explanation will be given here.

[0167] When the damping device 200 is at the stop position, a predetermined distance G is provided as a gap in the direction of the axis C between the frame body and the friction unit Uf. When the damping device 200 in the stopped position is displaced along the axis C, the interlocking mechanism 230 and the cylinder 211 of the oil damper 210 connected to the interlocking mechanism 230 move along the axis C relative to the sliding rod 221 and the rod 212 connected to the sliding rod 221.

[0168] When the maximum value of the displacement along the axis C (amplitude along the axis C) is smaller than the distance G, the interlocking mechanism 230 moves within a range where it does not come into contact with the friction unit Uf. At this time, in order to move the interlocking mechanism 230, a force is required to move the cylinder 211 of the oil damper 210 connected to the interlocking mechanism 230 relative to the rod 212. This causes the oil damper 210 to apply a damping force.

[0169] When the maximum value of the displacement along the axis C is greater than the distance G, the interlocking mechanism 230 comes into contact with the friction unit Uf and then moves together with the friction unit Uf while maintaining contact with the friction unit Uf. Until the interlocking mechanism 230 comes into contact with the friction unit Uf, a damping force is applied only by the oil damper 210, based on the same principle as described above. After the interlocking mechanism 230 comes into contact with the friction unit Uf, the friction unit Uf moves together with the interlocking mechanism 230 relative to the slidable rod 221 connected to the rod 212 of the oil damper 210. At this time, in order to move the interlocking mechanism 230, a force to move the friction unit Uf (i.e., a force that resists the friction force generated by the friction F) is required in addition to a force to move the cylinder 211 of the oil damper 210 connected to the interlocking mechanism 230 relative to the rod 212. This results in an additional damping force being applied by the friction damper 220. In other words, after the interlocking mechanism 230 comes into contact with the friction unit Uf, the damping performance of the damping device 200 is exerted by the oil damper 210 and the friction damper 220.

[0170] <<About the cross-sectional shape of the side plate>> As shown in FIGS. 21 to 23, each side plate 236 is a thin metal plate extending in the direction of the axis C along the outer circumferential surface of the cylinder 211 of the oil damper 210. 27, 28, 29, and 30, the cross-sectional shape of each side plate 236 is generally a convex shape that faces outward in the radial direction about the axis C. However, the characteristics of the cross-sectional shape of each side plate 236 may differ depending on the position in the direction of the axis C. The cross-sectional shape of each side plate 236 will now be described in detail.

[0171] As shown in FIG. 23, each side plate 236 is divided into four sections along the axis C: a cylinder base end section 236A, a cylinder tip end section 236B, a middle section 236C, and a frame side section 236D.

[0172] The cylinder base end side portion 236A is the portion from the end of the side plate 236 (the end on the connecting block 231 side) to the position of the base end of the rod 212 inside the cylinder 211. However, the "position of the base end of the rod 212" here means the position of the base end of the rod 212 when the rod 212 is fully inserted into the cylinder 211 (i.e., when the rod 212 is fully retracted; shown by the two-dot chain line in FIG. 23). Hereinafter, the position of the cylinder base end portion 236A corresponding to the end of the side plate 236 is defined as the "starting end of the cylinder base end portion 236A," and the position of the cylinder base end portion 236A corresponding to the position of the base end of the rod 212 is defined as the "ending end of the cylinder base end portion 236A."

[0173] The cylinder tip end side portion 236B is the portion extending from the end of the cylinder base end side portion 236A to the position of the tip of the cylinder 211. Hereinafter, the position of the cylinder tip side portion 236B corresponding to the end of the cylinder base side portion 236A is defined as the "starting end of the cylinder tip side portion 236B," and the position of the cylinder tip side portion 236B corresponding to the position of the tip of the cylinder 211 is defined as the "end of the cylinder tip side portion 236B."

[0174] The intermediate portion 236C is the portion from the end of the cylinder tip side portion 236B to the position of the end face of the first frame block 234. However, the "end face of the first frame block 234" here means the end face of the first frame block 234 facing the cylinder 211. Hereinafter, the position of the intermediate portion 236C corresponding to the end of the cylinder tip portion 236B is defined as the "beginning of the intermediate portion 236C," and the position of the cylinder tip portion 236B corresponding to the position of the end face of the first frame block 234 is defined as the "end of the intermediate portion 236C."

[0175] The frame-side portion 236D is a portion extending from the end of the intermediate portion 236C to the end of the side plate 236 (the end on the second frame block 235 side). Hereinafter, the position of the intermediate portion 236C corresponding to the end of the intermediate portion 236C is defined as the "beginning of the frame body side portion 236D," and the position of the cylinder tip side portion 236B corresponding to the end of the side plate 236 is defined as the "end of the frame body side portion 236D."

[0176] These parts are configured as a single part, the side plate 236, and are not structurally independent parts. Furthermore, the boundaries between these portions are not strict, and the start and end positions of each portion may be offset.

[0177] As shown in FIG. 27, the cross section of the cylinder base end side portion 236A is formed in a bow shape with two bent portions 236a1 spaced apart in the circumferential direction. Between one bent portion 236a1 and the other bent portion 236a1, a straight portion 236a2 having a substantially straight line shape is formed. The distance between the straight portion 236a2 of one side plate 236 and the straight portion 236a2 of the other side plate 236 that faces it and is substantially parallel to it is equal to the outer diameter of the cylinder 211 of the oil damper 210. Therefore, in a cross section perpendicular to the axis C, the straight portion 236a2 of each side plate 236 is in contact with the outer peripheral surface of the cylinder 211 at a point (shown by a black circle in FIG. 27). Therefore, as shown in FIGS. 22 and 23, the straight portion 236a2 of each side plate 236 is in contact with the outer peripheral surface of the cylinder 211 at a line (line Lc). Line Lc is a line that extends in the direction of the axis C. This supports the cylinder 211 over a partial range of the cylinder base-end side portion 236A, and by minimizing the area of ​​the support location, reduces the possibility of the cylinder 211 being deformed due to contact with the side plate 236. Furthermore, because the end of the rod 212 does not reach the cylinder base-end side portion 236A, even if a partial range of the cylinder 211 is deformed due to contact with the side plate 236, this is unlikely to affect the damping performance of the oil damper 210. It is not necessary for the cylinder base end portion 236A to contact the cylinder 211 over the entire range along the axis C; it is sufficient for the cylinder base end portion 236A to contact the cylinder 211 over at least some range along the axis C.

[0178] As shown in FIG. 28, the cross section of the cylinder tip end portion 236B is formed in a bow shape with two bent portions 236b1 spaced apart in the circumferential direction. Between one bent portion 236b1 and the other bent portion 236b1, a straight portion 236b2 having a substantially straight line shape is formed. For example, as shown by the two-dot chain line in Fig. 23, the cylinder tip end portion 236B is bent / curved so as to bulge slightly radially outward when viewed from the front. Therefore, as shown in Fig. 28, the distance between the straight portion 236b2 of one side plate 236 and the straight portion 236b2 of the other side plate 236 that faces it in a substantially parallel relationship is greater than the outer diameter of the cylinder 211 of the oil damper 210. Therefore, in a cross section perpendicular to the axis C, the straight portion 236a2 of each side plate 236 does not contact the outer peripheral surface of the cylinder 211 (shown by an open circle in Fig. 28). The shape shown by the two-dot chain line in FIG. 23 is an exaggerated representation of one example of the shape of the cylinder tip end side portion 236B, and is not intended to limit the actual shape.

[0179] 29 and 30, the cross-sectional shape of the frame body side portion 236D is an arc shape that follows the outer peripheral surfaces of the first frame block 234 and the second frame block 235. The distance (inner diameter) between one frame body side portion 236D and the other frame body side portion 236D facing it is equal to the outer diameter of the first frame block 234 and the outer diameter of the second frame block 235. Therefore, each side plate 236 comes into surface contact with the outer peripheral surface of the first frame block 234 and the outer peripheral surface of the second frame block 235. This allows the side plates 236 to stably support the first frame block 234 and the second frame block 235. The outer diameters of the holding block 223 and the pressing block 224 included in the holding unit Uh are set smaller than the distance (inner diameter) between one frame body side portion 236D and the other frame body side portion 236D. Therefore, each side plate 236 does not come into contact with the holding unit Uh. This is to prevent the side plate 236 from applying frictional force to the holding unit Uh that is not anticipated in the design.

[0180] The cross-sectional shape of the cylinder tip side portion 236B is bow-shaped, but the cross-sectional shape of the frame side portion 236D is arc-shaped. This is achieved, for example, by continuously deforming / changing the cross-sectional shape of the middle portion 236C along the direction of the axis C. The cross-sectional shape of the side plate 236 can be deformed / changed by, for example, drawing.

[0181] As shown in Figure 20, when the first pillar 11 and the second pillar 12 tilt due to earthquake shaking, the pillars 11 and 12 may bend, and this bending may cause a moment M around an axis along the depth direction to be generated in the vibration control device 50. Therefore, in the wall structure 10, by setting the opposing directions of the two side plates 236 arranged to sandwich the cylinder 211 of the oil damper 210 to a direction perpendicular to the direction of the axis C and the depth direction, the tension / compression caused by the moment M can be balanced by the two side plates 236 (a tensile load acts on one side plate 236, and a compressive load acts on the other side plate 236). This allows the side plates 236, which are thin plates, to counteract the moment M. Furthermore, by thinning the side plates 236, the weight and size of the vibration damping device 50 can be reduced.

[0182] [Variation 6] The cross-sectional shape of the frame body side portion 236D of the side plate 236 may be an arched shape similar to the cylinder base end side portion 236A. In this case, in a cross section perpendicular to the axis C, each side plate 236 contacts the outer circumferential surface of the first frame block 234 and the outer circumferential surface of the second frame block 235 along a line.

[0183] <<About fixing the side plates>> As shown in FIG. 29, the side plate 236 is fastened to the first frame block 234 with a bolt 238 .

[0184] The bolt 238 is, for example, a shoulder bolt, and has a threaded portion 238a, a cylindrical portion 238b, and a head portion 238c. Therefore, the diameter of the cylindrical portion 238b is larger than the nominal diameter of the threaded portion 238a. The threaded portion 238 a of the bolt 238 is screwed into an internally threaded hole 234 c formed in the first frame block 234 . The cylindrical portion 238b of the bolt 238 is inserted into a stepped hole 234d formed in the first frame block 234 and a through hole 236d1 formed in the side plate 236. The diameter of the cylindrical portion 238b is set to be approximately equal to or slightly larger than the diameters of the stepped hole 234d and the through hole 236d1. Therefore, the cylindrical portion 238b fitted into the stepped hole 234d and the through hole 236d1 is configured not to rattle relative to the stepped hole 234d and the through hole 236d1. It goes without saying that the diameter of the stepped hole 234d is larger than the nominal diameter of the female threaded hole 234c. The head 238 c of the bolt 238 is in contact with the outer circumferential surface of the side plate 236 .

[0185] As a result, even if the bolt 238 becomes loose, as long as the threaded portion 238a of the bolt 238 is threaded into the female threaded hole 234c of the first frame block 234 and the cylindrical portion 238b of the bolt 238 is fitted into the through hole 236d1 of the side plate 236, the side plate 236 and the first frame block 234 are maintained in a restrained state in the direction of the axis C. In other words, the function of the side plate 236 is maintained.

[0186] The stepped configuration of bolt 238 and the members fastened thereto can also be applied to, for example, bolt 237 and the members fastened thereto, and bolt 239 and the members fastened thereto.

[0187] [Effects of this embodiment] According to this embodiment, the following effects are achieved. The side plate 236 contacts only a portion of the base end side of the cylinder 211 of the oil damper 210, and also contacts the outer surface of the cylinder 211 at line Lc. Therefore, the side plate 236 supports the cylinder 211 in a portion of the base end side, and by making the area of ​​the support point as small as possible, the possibility of the cylinder 211 being deformed by contact with the side plate 236 is reduced. Furthermore, since the end of the rod 212 (the end housed inside the cylinder 211) does not reach the inside of the base end side of the cylinder 211, even if the cylinder 211 is deformed in some area due to contact with the side plate 236, this is unlikely to affect the damping performance of the oil damper 210.

[0188] The side plates 236 are in surface contact with the first frame block 234 and the second frame block 235, and are therefore able to stably support the first frame block 234 and the second frame block 235.

[0189] By changing the cross-sectional shape of the side plate 236 at the middle portion 236C, the manner in which the oil damper 210 contacts the cylinder 211 and the manner in which it contacts the first frame block 234 and the second frame block 235 can be changed.

[0190] The cross-sectional shapes of the first frame block 234 and the second frame block 235 that are perpendicular to the axis C are circular and centered on the axis C, and the cross-sectional shape of the cylinder 211 of the oil damper 210 that is perpendicular to the axis C is circular and centered on the axis C, so that the shape of the device as a whole has a sense of unity, creating an excellent aesthetic appearance.

[0191] The holding unit Uh has three or more screw members 225' that fasten the holding block 223 and the pressing block 224, and the screw members 225' are arranged at equal angular intervals in the circumferential direction around the axis C, so that the sliding tube 222 can be pressed down evenly in the circumferential direction.

[0192] The two side plates 236 face each other in a direction perpendicular to the direction of the axis C and the depth direction, so when a moment around the axis along the depth direction occurs in the vibration control device 50 (particularly the damping device 200), the two side plates 236 can balance the tension / compression (a tensile load acts on one side plate 236, and a compressive load acts on the other side plate 236). [Explanation of symbols]

[0193] 10 Wall structure 11 First pillar (first structural member) 12 Second pillar (second structural member) 14 Foundation 15 Beam 50 Vibration control device 51 First vibration damping device end (first end) 52 Second vibration damping device end (second end) 100 braces 101 End of first brace 102 End of second brace 200 Damping Device 201 End of first damping device 202 End of second damping device 210 Oil damper (main damper) 211 Cylinder 212 Rod 220 Friction damper (secondary damper) 221 Sliding rod (sliding member) 222 Sliding cylinders (sliding members, cylindrical parts) 222a Tube body 222a1 Tapered tube 222a2 vertical slit 222b Friction material 222b2 vertical slit 223 Retaining block (retaining member) 223a Through hole 223a1 Tapered hole 223a2 Straight hole 223a3 Step surface 224 Presser block (presser member) 224a through hole 225 Fastening members (bolts) 225' Screw member (bolt) 226 Spacer 230 Interlocking Mechanism 231 Connecting Block 232 Main damper side member 233 Sub-damper side member 234 First frame member (first frame block) 234a Through hole 234b Sliding bush 234c female thread hole 234d stepped hole 235 Second frame member (second frame block) 235a Through hole 235b Sliding bush 236 Side plate (side member) 236A Cylinder base end part 236a1 Bend part 236a2 Straight section 236B Cylinder tip part 236b1 Bent part 236b2 Straight section 236C middle part 236D Frame side part 236d1 through hole 237 volts 238 volts 238a Threaded part 238b Cylindrical part 238c head 239 volts 301 First Bracket 301a First bracket support part 302 Second Bracket 302a Second bracket support part 303 Connecting Rod 421 Sliding plate (sliding member) 421a Long hole 422 Clamping plate (sliding member) 422a Plate body 422b Friction material 423 Fastening parts (bolts and nuts) Uf friction unit Uh holding unit

Claims

1. A damping device having one end, a first end, disposed on one structural member side and the other end, a second end, disposed on another structural member side, a main damper that applies a damping force; a secondary damper that applies a damping force; Equipped with When the first end and the second end move closer to or farther apart along an axis, When the displacement is equal to or smaller than a predetermined value, the main damper functions. When the displacement exceeds a predetermined value, the main damper and the sub damper function. Damping device.

2. The main damper is an oil damper having a cylinder and a rod that moves relative to the cylinder. The damping device of claim 1 .

3. The auxiliary damper is a friction damper. The damping device of claim 2 .

4. The amount of movement of the rod corresponds to the displacement, the friction damper has a slidable member and a sliding member that slides along the axis while contacting the slidable member, the sliding member is connected to the rod, a linkage mechanism for linking the oil damper and the friction damper, The interlocking mechanism slides the sliding member relative to the slidable member when the displacement exceeds a predetermined value. The damping device of claim 3.

5. The sliding member is a rod-shaped sliding rod extending along the axis, The sliding member is a cylindrical part through which the slidable rod is inserted along the axis, and whose inner peripheral surface contacts the outer peripheral surface of the slidable rod. The damping device of claim 4.

6. the friction damper includes a holding unit that holds the tubular part, the interlocking mechanism includes a frame body fixed to the cylinder, The frame sandwiches the holding unit holding the tubular part with a gap in the axial direction. The damping device of claim 5.

7. The holding unit includes: a holding member having a through hole formed therein into which the tubular part is fitted along the axis; and a pressing member that presses the tubular part toward the holding member; have The damping device of claim 6.

8. the tubular part has a tapered tubular portion whose outer diameter decreases and a slit along the axis, The tapered tubular portion of the tubular part is fitted into the through hole of the holding member. The damping device of claim 7.

9. The tapered tubular portion of the tubular part has an inclination angle of 1 degree or more and 10 degrees or less. The damping device of claim 8.

10. The portion of the cylindrical part that comes into contact with the outer circumferential surface of the sliding rod is a metal-based oil-free bearing in which a solid lubricant is dispersed in metal. The damping device of claim 8.

11. the frame body has a bush through which the slidable rod is inserted in the axial direction, The bushing holds the slidable rod in the radial direction around the axis. The damping device of claim 10.

12. the friction damper includes a holding unit that holds the tubular part, The interlocking mechanism includes: two side members extending along the axis, connected to the cylinder, and disposed opposite to each other so as to sandwich the cylinder; a first frame member disposed between the two side members, through which the slidable rod is inserted along the axis, and connected to each of the side members; a second frame member disposed between the two side members, through which the slidable rod is inserted along the axis, and connected to each of the side members; Equipped with The first frame member and the second frame member are are spaced apart in the direction of the axis, The holding unit holding the tubular part is sandwiched with a gap in the axial direction. The damping device of claim 5.

13. Each of the side members is in contact with only a partial range on the base end side of the cylinder of the oil damper, and is in contact with the outer circumferential surface of the cylinder along a single line along the axial direction. The damping device of claim 12.

14. Each of the side members is in surface contact with the outer circumferential surface of the first frame member and the outer circumferential surface of the second frame member.

14. The damping device of claim 13.

15. a cross-sectional shape of each of the first frame member and the second frame member perpendicular to the axis is a circle having the axis as its center; a cross-sectional shape of the cylinder of the oil damper that is perpendicular to the axis of the cylinder is a circle centered on the axis, The cross-sectional shape of the side member perpendicular to the axis is The projection is convex outward in a radial direction centered on the axis, The oil damper has a bow shape with two bent portions formed in a region where the oil damper comes into contact with the cylinder, In the area where the first frame member and the second frame member come into contact with each other, the area has an arc shape that follows the outer circumferential surface of the first frame member and the outer circumferential surface of the second frame member.

15. The damping device of claim 14.

16. the first frame member is disposed between the second frame member and a tip end of the cylinder of the oil damper in the axial direction, The cross-sectional shape of the side member perpendicular to the axis changes continuously within a range from the tip of the cylinder of the oil damper to the first frame member.

16. The damping device of claim 15.

17. a cross-sectional shape of the holding unit perpendicular to the axis is a circle centered on the axis, a cross-sectional shape of each of the first frame member and the second frame member perpendicular to the axis is a circle having the axis as its center; The cross-sectional shape of the cylinder of the oil damper, which is perpendicular to the axis, is a circle having the axis as its center. The damping device of claim 12.

18. The holding unit includes: a holding member having a through hole formed therein into which the tubular part is fitted along the axis; a pressing member that presses the tubular part toward the holding member; and Three or more screw members fastening the holding member and the pressing member and The screw members are arranged at equal angular intervals in the circumferential direction around the axis. The damping device of claim 12.

19. The oil damper is a type having a bilinear characteristic in which the yield strength rises at a gradient of 0.8 kN / mm or more from the stop position of the rod to a predetermined displacement, and the yield strength is maintained substantially constant after the predetermined displacement.

19. A damping device according to any one of claims 2 to 18.

20. A damping device according to any one of claims 1 to 18; a brace connected to the first end and extending along the axis; Equipped with Vibration control device.

21. The vibration damping device according to claim 20; the one structural member; The other structural member; Equipped with Wall structure.

22. The wall structure according to claim 21 is provided. Wooden house.

23. A damping device according to any one of claims 12 to 18; a brace connected to the first end and extending along the axis; the first structural member made of wood and extending in a vertical direction; the other structural member made of wood extending vertically and arranged horizontally spaced apart from the first structural member; Equipped with When the depth direction is perpendicular to the vertical and horizontal directions, the two thin plate-shaped side members face each other in a direction perpendicular to the axial direction and the depth direction. Wall structure.

24. The wall structure according to claim 23 is provided. Wooden house.

25. A damping device having one end, a first end, disposed on one structural member side and the other end, a second end, disposed on another structural member side, When the first end and the second end move closer to or farther apart along an axis, The yield strength increases between the stop position and the first predetermined displacement, the yield strength is substantially constant between the first predetermined displacement and the second predetermined displacement, and the yield strength increases after the second predetermined displacement. Damping device.

26. a rod-shaped sliding rod extending along an axis; a cylindrical part through which the sliding rod is inserted along the axis and whose inner circumferential surface contacts the outer circumferential surface of the sliding rod, the tubular part has a slit along the axis and a tapered tubular portion whose outer diameter decreases, a holding member having a through hole formed therein into which the tapered tubular portion of the tubular part is fitted along the axis; Friction damper.

27. A pressing member is provided to press the tubular part against the holding member.

27. The friction damper of claim 26.

28. The portion of the cylindrical part that comes into contact with the outer circumferential surface of the sliding rod is a metal-based oil-free bearing in which a solid lubricant is dispersed in metal.

27. The friction damper of claim 26.

29. The tapered tubular portion of the tubular part has an inclination angle of 1 degree or more and 10 degrees or less.

29. A friction damper according to any one of claims 26 to 28.

30. A spacer is provided to limit the amount by which the cylindrical part is pushed into the through hole.

29. A friction damper according to any one of claims 26 to 28.

Images