friction damper

Abstract

This reduces localized wear between plate materials and easily suppresses the decrease in frictional force due to frictional heat. [Solution] A friction damper is disposed between a pair of members that move relative to each other in a predetermined direction, and suppresses the relative movement by the frictional force between plate materials that slide together as a result of the relative movement, comprising: a first plate material provided on one of the pair of members and a second plate material provided on the other of the pair of members, a plurality of plate materials stacked in a thickness direction intersecting the predetermined direction; a fastening member that penetrates each through hole of the plurality of plate materials and fastens the plurality of plate materials from both sides in the thickness direction; and an interposing member interposed between the end of the fastening member in the thickness direction and the plurality of plate materials, wherein the interposing member has a flat washer portion that receives the tightening axial force of the fastening member and a ring portion disposed between the flat washer portion and the plurality of plate materials.

Description

Technical Field

[0001] The present invention relates to a friction damper.

Background Art

[0002] In building structures and the like, a friction damper is known that is disposed between a pair of members that move relative to each other in a predetermined direction and suppresses relative movement (attenuates vibration) by the frictional force between pressure contact plates that slide with the relative movement. For example, the friction damper of Patent Document 1 includes a bolt and a nut as fastening members for fastening plate materials, and further, a flat washer is interposed between the nut and the plate material (pressure contact plate).

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In a friction damper such as that of Patent Document 1, since the tightening force (axial force of the fastening member) by the bolt and the nut easily acts in a narrow region near the bolt and the nut, frictional heat is likely to be generated in that portion, and there is also a problem that the pressure contact surface of the plate material is likely to wear. As a result, it may be difficult to obtain a desired frictional force.

[0005] The present invention has been made in view of the above problems, and an object thereof is to reduce local wear between plate materials and easily suppress a decrease in frictional force due to frictional heat.

Means for Solving the Problems

[0006] The main invention for achieving the above object is A friction damper is positioned between a pair of members that move relative to each other in a predetermined direction, and suppresses the relative movement by the frictional force between the plate materials that slide against each other as a result of the relative movement, A plurality of plates are stacked in a thickness direction intersecting the predetermined direction, including a first plate provided on one of the pair of members and a second plate provided on the other of the pair of members, A fastening member that penetrates each of the through holes in the plurality of plate materials and fastens the plurality of plate materials from both sides in the thickness direction, The end of the fastening member in the thickness direction and the interposing member interposed between the plurality of plate materials, Equipped with, The aforementioned intervening member is The flat washer portion that receives the tightening axial force of the fastening member, A ring portion is disposed between the flat washer portion and the plurality of plate materials, of Yes, The flat washer portion and the ring portion are friction-joined or engaged. This friction damper is characterized by the following features.

[0007] Other features of the present invention will be revealed in the specification and drawings described below. [Effects of the Invention]

[0008] According to the present invention, localized wear between plate materials can be reduced, and the decrease in frictional force due to frictional heat can be easily suppressed. [Brief explanation of the drawing]

[0009] [Figure 1] This is a schematic elevation view of a building frame 1 equipped with a friction damper 10. [Figure 2] This is a view taken along arrow AA in Figure 1. [Figure 3A] This is an enlarged view of the fastening structure 20 in Figure 2. [Figure 3B] This is a view from arrow BB in Figure 3A. [Figure 4] Figure 4A is an explanatory diagram of a conventional friction damper 100. Figure 4B is a view taken along the arrow DD in Figure 4A. [Figure 5] It is an explanatory view of the friction damper 10a of a modification of the first embodiment. [Figure 6] It is an explanatory view of the friction damper 10b of the second embodiment. [Figure 7] It is an explanatory view of the friction damper 10c of a first modification of the second embodiment. [Figure 8] It is an explanatory view of the friction damper 10d of a second modification of the second embodiment. [Figure 9] It is an explanatory view of the friction damper 10e of a third modification of the second embodiment.

MODE FOR CARRYING OUT THE INVENTION

[0010] From the descriptions of the specification and drawings described later, at least the following matters will become clear.

[0011] (Aspect 1) A friction damper disposed between a pair of members that relatively move in a predetermined direction, and that suppresses the relative movement by the frictional force between plate materials that slide with the relative movement, the friction damper including a first plate material provided on one of the pair of members, and a second plate material provided on the other of the pair of members, a plurality of plate materials overlapped in a plate thickness direction intersecting the predetermined direction, a fastening member passing through each through hole of the plurality of plate materials and fastening the plurality of plate materials from both sides in the plate thickness direction, an interposed member interposed between an end portion of the fastening member in the plate thickness direction and the plurality of plate materials, the interposed member having a washer portion that receives the fastening axial force of the fastening member, and a ring portion disposed between the washer portion and the plurality of plate materials.

[0012] According to the friction damper of Aspect 1, local wear between the plate materials can be reduced, and a decrease in the frictional force due to frictional heat can be easily suppressed.

[0013] (Aspect 2) The friction damper according to Aspect 1, wherein it is desirable that the washer portion and the ring portion are frictionally joined or engaged.

[0014] According to the friction damper of Embodiment 2, displacement between the flat washer portion and the ring portion can be suppressed as compared with the case where the flat washer portion and the ring portion are separate bodies.

[0015] (Embodiment 3) The friction damper according to Embodiment 1, wherein it is desirable that the flat washer portion and the ring portion are integrally formed.

[0016] According to the friction damper of Embodiment 3, there is no possibility that the flat washer portion and the ring portion are displaced. Further, the number of members constituting the friction damper can be reduced, and simplification of assembly and configuration can be achieved.

[0017] (Embodiment 4) It is desirable that the interposed member is provided at one end portion of the fastening member in the plate thickness direction, and a disc spring is provided between the other end portion of the fastening member in the plate thickness direction and the plurality of plate materials.

[0018] According to the friction damper of Embodiment 4, stabilization of the magnitude of the force (pressing force) for pressing a plurality of plate materials against each other can be achieved.

[0019] (Embodiment 5) The friction damper according to Embodiment 4, wherein it is desirable that the inner diameter of the ring portion is 1 / 2 or more of the outer diameter of the disc spring.

[0020] According to the friction damper of Embodiment 5, the tightening axial force by the fastening member (for example, bolt and nut) can be transmitted to a position away from the vicinity of the fastening member (outside the vicinity of the fastening member). Therefore, wear in the vicinity of the fastening member of each plate material can be reduced.

[0021] (Embodiment 6) The friction damper according to Embodiment 4, wherein it is desirable that the inner diameter of the ring portion is larger than the inner diameter of the disc spring.

[0022] According to the friction damper of embodiment 6, each plate material can be pressed together at a position away from the vicinity of the fastening member.

[0023] (Aspect 7) In the friction damper according to embodiment 4, it is desirable that the inner diameter of the ring portion is smaller than the outer diameter of the disc spring.

[0024] According to the friction damper of embodiment 7, the ring portion and the disc spring can be used to sandwich the same part (position) of each plate material. In addition, each plate material can be pressed together at a position away from the vicinity of the fastening member.

[0025] (Pattern 8) In the friction damper according to Embodiment 1, it is preferable that the interposing member is provided in a pair on both sides in the thickness direction of the plate material so as to sandwich the plurality of plate materials.

[0026] According to the friction damper of embodiment 8, it is possible to press (press-fit) multiple plate materials at the same position from both sides in the thickness direction.

[0027] (Aspect 9) A friction damper according to embodiment 8, preferably having a disc spring between the end of the fastening member in the thickness direction and at least one of the pair of interposing members.

[0028] According to the friction damper of embodiment 9, the same portion of multiple plate materials can be pressed from both sides in the thickness direction.

[0029] (Aspect 10) The friction damper according to embodiment 9, wherein the outer diameter of the disc spring may be smaller than the inner diameter of the ring portion.

[0030] According to the friction damper of embodiment 10, by providing a pair of interposing members on both sides in the thickness direction of the plate, the degree of freedom in the size and number of parallel disc springs can be greatly increased, and a small disc spring can be used.

[0031] Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. In the following, identical or equivalent components, members, etc., shown in each drawing will be denoted by the same reference numerals, and redundant explanations may be omitted as appropriate.

[0032] ===First Embodiment=== <<About friction damper 10>> Figure 1 is a schematic elevation view of the building frame 1 equipped with a friction damper 10. Figure 2 is a view taken along arrow AA in Figure 1. Figure 3A is an enlarged view of the fastening structure 20 in Figure 2. Figure 3B is a view taken along arrow BB in Figure 3A. For simplification, thin washers, friction plates, sliding plates, etc., placed between each plate material are not shown.

[0033] The friction damper 10 is incorporated into the brace 7 of the H-shaped steel of the column-beam frame 1, which is the building frame 1. The brace 7 is divided at appropriate positions at predetermined intervals from each other to form a pair of brace segments 71 and 72. The brace segments 71 and 72 are able to move relative to each other in the spanning direction at predetermined intervals. This spanning direction corresponds to the direction of relative movement (predetermined direction). The friction damper 10 is positioned between the brace segments 71 and 72 of the brace 7, and when an external force such as an earthquake occurs, the frictional force between the plate materials suppresses the relative movement of the brace segments 71 and 72 in the brace spanning direction.

[0034] As shown in Figure 2 and other figures, the friction damper 10 includes a first plate 11, a second plate 12, a third plate 13, fastening members 60 (high-strength bolts 61b, nuts 61n), a bush 62, a disc spring 63, and an intervening member 65. These members together constitute the fastening structure 20 shown in Figures 2 and 3A.

[0035] The first plate 11 and the third plate 13 are fixed (bolted in this case) to the web 71w of one of the brace fragments 71. The second plate 12 uses the same web 72w of the other brace fragment 72. The first plate 11, the second plate 12, and the third plate 13 are stacked in the thickness direction.

[0036] The first plate 11 has a first through-hole 11a, the second plate has a second through-hole 12a, and the third plate 13 has a third through-hole 13a, all formed through the thickness direction of the plates, and high-strength bolts 61b are passed through these through-holes 11a, 12a, and 13a in a skewer-like manner. The first through-hole 11a and the third through-hole 13a are circular, while the second through-hole 12a is an elongated hole that is longer in the relative movement direction.

[0037] The fastening member 60 is a member that fastens the first plate material 11, the second plate material 12, and the third plate material 13 together. The fastening member 60 in this embodiment is equipped with a high-strength bolt 61b (hereinafter also simply referred to as bolt 61b) and a nut 61n.

[0038] A nut 61n is screwed onto the tip of the bolt 61b. The bolt 61b also has a bolt head 61h on the opposite side of the tip. In this embodiment, the bolt head 61h and the tip of the bolt 61b (the end on the nut 61n side) correspond to the ends of the fastening member 60 in the thickness direction (one end and the other end), respectively.

[0039] The second plate member 12 is fastened between the first plate member 11 and the third plate member 13 by bolts 61b and nuts 61n, and a pressing force is applied in the thickness direction of the plates. Due to this pressing force, the first plate member 11 and the second plate member 12, and the second plate member 12 and the third plate member 13 come into contact with each other, and when sliding, a frictional force corresponding to the pressing force is generated. This frictional force becomes the damping force of vibration of the column-beam frame 1. In addition, a bush 62 and a disc spring 63 are interposed between the nut 61n and the third plate member 13, and the elastic force of the disc spring 63 helps to stabilize the magnitude of the pressing force.

[0040] To allow the aforementioned sliding in the brace-connecting direction, the second through-hole 12a of the second plate member 12 is formed as a long elongated hole along the brace-connecting direction (relative movement direction), as previously described. That is, this second through-hole 12a allows the second plate member 12 to slide relative to the first plate member 11 and the third plate member 13 in the brace-connecting direction as the brace-connecting fragments 71 and 72 of the column-beam frame 1 move relative to each other in the brace-connecting direction. The length L12a of the second through-hole 12a in the relative movement direction (brace-connecting direction) is longer than the diameter D11a of the first through-hole 11a (L12a > D11a). The length of this second through-hole 12a (elongated hole) in the brace-connecting direction is determined considering the amount of relative movement between the brace-connecting fragments 71 and 72 expected during an earthquake.

[0041] The bush 62 is a member that acts as a guide when the disc spring 63 is compressed and deformed, and has a cylindrical portion 621 and a flange portion 622.

[0042] The cylindrical portion 621 is the part that is inserted into the disc spring 63. For this reason, the outer diameter of the cylindrical portion 621 is formed to be slightly smaller than the inner diameter (D63i) of the disc spring 63. Also, a bolt 61b is inserted inside the cylindrical portion 621. For this reason, the inner diameter of the cylindrical portion 621 is formed to be slightly larger than the diameter of the bolt 61b.

[0043] The flange portion 622 is a disc-shaped part positioned between the disc spring 63 and the nut 61n, and is connected to the cylindrical portion 621.

[0044] The outer diameter of the flange portion 622 is larger than the outer diameter of the nut 61n. In other words, even after being tightened with the bolt 61b and nut 61n, the flange portion 622 protrudes outward from the outer circumference of the nut 61n.

[0045] Here, assuming that the outer diameter of the flange portion 622 and the outer diameter of the nut 61n are approximately the same, the height of the disc spring 63 would be measured at the end face of the disc spring 63 on the nut 61n side. However, as shown in Figures 2 and 3A, the end face of the disc spring 63 is slanted (inclined), making it difficult to accurately measure the height.

[0046] In contrast, as in this embodiment, if the flange portion 622 of the bush 62 protrudes outward from the nut 61n, the height can be measured at the portion of the flange portion 622 that protrudes outward from the nut 61n. Therefore, by subtracting the thickness of the flange portion 622 from the measured value, the height of the disc spring 63 can be determined. Thus, it becomes easier to accurately measure the height of the disc spring 63.

[0047] Furthermore, the outer diameter of the flange portion 622 is larger than the inner diameter (D63i) of the disc spring 63. This allows the tightening force (tightening axial force) from the bolt 61b and nut 61n to be transmitted to the disc spring 63.

[0048] The disc spring 63 is compressed between the flange portion 622 of the bush 62 and the third plate material 13 by tightening with the bolt 61b and nut 61n, thereby applying a pressing force between each plate material. In this embodiment, the disc spring 63 is composed of 12 individual disc springs stacked in parallel, but it is not limited to 12; the number of springs can be set to generate the desired pressing force. Alternatively, the disc spring 63 may be composed of only one individual disc spring.

[0049] As shown in Figures 2 and 3A, the intervening member 65 is interposed between the bolt head 61h of the bolt 61b and the first plate material 11. The intervening member 65 also includes a flat washer portion 66 and a ring portion 67.

[0050] The flat washer portion 66 is a circular plate-shaped part and is provided on the bolt head 61h side. The flat washer portion 66 receives the tightening force (axial force) of the fastening member 60 from the bolt head 61h.

[0051] Furthermore, a through hole 66a, slightly larger in diameter than the bolt 61b, is formed through the plate thickness direction in the flat washer portion 66. The bolt 61b is passed through this through hole 66a. Although there is a gap between the through hole 66a and the bolt 61b, it is preferable for this gap to be as small as possible.

[0052] The ring portion 67 is an annular part with a thin thickness in the thickness direction of the plate, and is provided between the flat washer portion 66 and the first plate material 11. For convenience, the area where the ring portion 67 is provided is shown in Figure 3B with hatching (cross-hatching). The inner diameter D67i of the ring portion 67 is greater than the minimum outer diameter D61h of the bolt head 61h (D67i > D61h). Note that the minimum outer diameter D61h of the bolt head 61h is the shortest length of the diagonal in the bolt head 61h.

[0053] The flat washer portion 66 and the ring portion 67 may be formed as separate parts. If they are separate parts, it is desirable that they be friction-joined (friction-pressure-welded). Alternatively, it is desirable that they engage with each other by providing engaging parts on the contact surfaces. This can suppress misalignment.

[0054] Furthermore, the flat washer portion 66 and the ring portion 67 may be integrally formed by welding or other means. When the flat washer portion 66 and the ring portion 67 are integrally formed, there is no risk of misalignment. In addition, the number of components required to form the friction damper 10 can be reduced, making it easier to simplify the manufacturing process of the friction damper 10.

[0055] Figure 4A is an explanatory diagram of a conventional friction damper 100. Figure 4B is a view from the direction of arrow DD in Figure 4A. For each component of the friction damper 100 in Figures 4A and 4B, the parts that are common with the configuration of the friction damper 10 described above will be given the same reference numerals, etc., and a detailed explanation of the basic configuration of the friction damper 100 will be omitted.

[0056] In this friction damper 100, a flat washer 40 is interposed between the bolt head 61h and the first plate material 11. The flat washer 40 is a circular plate-shaped washer (a washer without a protrusion) with a through hole 40a formed in the center.

[0057] Generally, forces such as pressure are transmitted along the shortest distance. In other words, the force f applied from the bolt head 61h is easily transmitted perpendicular to the first plate material 11. Therefore, as shown in Figure 4B, the force generated by the bolt 61b (fastening member 60) is easily transmitted near the bolt on each plate material 11, 12, and 13, and is particularly easily transmitted in the region that overlaps with the bolt head 61h in the plate thickness direction. In Figure 4B, the region where the force f applied from the bolt head 61h acts particularly strongly is indicated by hatching (cross-hatching). As shown in Figure 4B, in the conventional friction damper 100, the force f transmitted from the bolt head 61h tends to act near the first through hole 11a of the first plate material 11 and near the second through hole 12a of the second plate material 12, which could lead to increased surface pressure in those areas, causing heat generation or localized wear.

[0058] In contrast, in this embodiment, as shown in Figure 3B, the region in which the force f applied from the bolt head 61h of the friction damper 10 acts in particular is the ring portion 67 that is in contact with the first plate material 11 when the friction damper 10 is viewed from the bolt head 61h side (hatched area in Figure 3B).

[0059] In other words, the friction damper 10 transmits the force f applied from the bolt head 61h to the first plate material 11 via the intervening member 65 (flat washer portion 66, ring portion 67). This makes it possible to make the force f applied from the bolt head 61h act more easily in the outer region away from the vicinity of the bolt 61b. That is, in Figure 3A, the force f is more likely to act in the region where the ring portion 67 and the first plate material 11 overlap in the plate thickness direction (hatched region in Figure 3B).

[0060] Furthermore, in the friction damper 10, the area where a force f is easily applied from the bolt head 61h to the first plate material 11 is the region where the ring portion 67 and the first plate material 11 overlap when viewed from the bolt head 61h side. For this reason, the area of ​​the region in the friction damper 10 where a force f is applied from the bolt head 61h to the first plate material 11 (the area of ​​the hatched region in Figure 3B) is larger than the area in the conventional friction damper 100 where a force f is applied from the bolt head 61h (the hatched region in Figure 4B). Therefore, the force per unit area due to the force f applied from the bolt head 61h in the friction damper 10 of this embodiment is smaller than the force per unit area due to the force f applied from the bolt head 61h in the conventional friction damper 100.

[0061] In this way, by making the force f applied from the bolt head 61h more likely to be directed outward from the vicinity of the bolt 61b, and by reducing the force per unit area due to force f, wear near the first through hole 11a of the first plate material 11 and near the second through hole 12a of the second plate material 12 can be reduced.

[0062] In this embodiment of the friction damper 10, since a disc spring 63 is provided on the side where the nut 61n is located in the plate thickness direction (the tip side of the bolt 61b), the force applied from the nut 61n side is easily acted upon a wide area of ​​the third plate material 13 via the disc spring 63. For example, the force is easily acted upon the outer circumference of the disc spring 63.

[0063] Therefore, it is desirable that the region where the ring portion 67 of the interposing member 65 and the first plate material 11 overlap overlaps with the outer circumference of the disc spring 63. In this embodiment, as shown in Figure 3A, the outer diameter D63e of the disc spring 63 and the outer diameter D67e of the ring portion 67 are approximately the same. This allows the force (elastic force) from the disc spring 63 to be applied to each plate material more efficiently.

[0064] Also, in FIG. 3A (and FIG. 3B), it is desirable that the inner diameter D67i of the ring portion 67 is at least 1 / 2 of the outer diameter D63e of the disc spring 63. Thereby, the tightening force (the force f applied from the bolt head 61h) by the bolt 61b and the nut 61n can be transmitted to the outside rather than the vicinity of the bolt 61b. Thus, the wear in the vicinity of the bolt 61b of each plate material can be reduced.

[0065] Also, it is desirable that the inner diameter D67i of the ring portion 67 is larger than the inner diameter D63i of the disc spring 63 (D67i > D63i) and smaller than the outer diameter D63e (D67i < D63e). Thereby, a pressure contact force can be applied to a position away from the vicinity of the bolt 61b by the disc spring 63 and the interposed member 65 (ring portion 67).

[0066] Note that the same effect can be obtained even if the interposed member is composed of a bush portion and a ring portion. However, as in the present embodiment, the flat washer portion 66 and the ring portion 67 can be manufactured more simply.

[0067] <Modified Example> FIG. 5 is an explanatory view of a friction damper 10a according to a modified example of the first embodiment.

[0068] The fastening structure 20a of the friction damper 10a shown in FIG. 5 is a configuration in which the first plate material 11 and the second plate material 12 are fastened by a fastening member 60 (a configuration without the third plate material 13). Thus, a configuration with two plate materials (one sliding surface) may be used. Note that this is not limited thereto, and for example, a configuration in which the second plate material 12 and the third plate material 13 are fastened by a fastening member 60 (a configuration without the first plate material 11) may be used. In this case, the third plate material 13 corresponds to the first plate material.

[0069] Also, although not shown, more plate materials may be further added to increase the number of sliding surfaces. For example, a friction damper having five plate materials (pressure contact plates) and four sliding surfaces (four surfaces) may be used.

[0070] Even in these cases, by using the interposed member 65, the same effect as in the above-described embodiment can be obtained.

[0071] Furthermore, the positions of the bolt head 61h and nut 61n of the fastening member 60 may be reversed. In other words, the tip of the bolt 61b may be passed from the bush 62 side (disc spring 63 side), with the bolt head 61h on the disc spring 63 side and the nut 61n on the intervening member 65 side. In this case as well, each plate material can be fastened. Moreover, by using the intervening member 65, the same effects as in the above-described embodiment can be obtained.

[0072] ===Second Embodiment=== Figure 6 is an explanatory diagram of the friction damper 10b of the second embodiment. The friction damper 10b is provided with a fastening structure 20b.

[0073] The fastening structure 20b of the second embodiment is provided with a pair of intervening members 65. The pair of intervening members 65 are provided so as to sandwich the first plate material 11, the second plate material 12, and the third plate material 13 from both sides in the thickness direction. More specifically, in addition to the configuration of the fastening structure 20 of the first embodiment, an intervening member 65 is also provided (intervened) between the third plate material 13 and the disc spring 63. The ring portion 67 of the intervening member 65 is in contact with the third plate material 13.

[0074] Since the pair of interfacing members 65 are identical, they can press the first plate material 11, the second plate material 12, and the third plate material 13 from both sides in the thickness direction at the same position. However, the pair of interfacing members 65 do not have to be exactly the same. For example, the height (thickness) of the ring portion 67 may be different.

[0075] In this second embodiment, the same effects as in the first embodiment can be obtained.

[0076] <First variation> Figure 7 is an explanatory diagram of the friction damper 10c of the first modified example of the second embodiment.

[0077] The fastening structure 20c of this friction damper 10c is equipped with a flat washer 64 and a disc spring 63a on the nut 61n side (between the nut 61n and the third plate material 13, more specifically between the nut 61n and the intervening member 65).

[0078] The flat washer 64 is a circular plate-shaped washer and does not have a tubular portion (the part inserted into the disc spring) like a bush. Therefore, by using the flat washer 64, a disc spring with a smaller diameter (in this case, disc spring 63a) can be used. It is desirable that the outer diameter of the flat washer 64 be larger than the inner diameter of the disc spring 63a. This allows the tightening force (tightening axial force) from the bolt 61b and nut 61n to be transmitted to the disc spring 63a. It is also desirable that the outer diameter of the flat washer 64 be larger than the outer diameter of the nut 61n (it protrudes outward from the outer circumference of the nut 61n). This makes it easier to accurately measure the height of the disc spring (in this case, disc spring 63a), similar to the case of the flange portion 622 of the bush 62 mentioned above.

[0079] As mentioned above, disc spring 63a is a disc spring that is smaller in size (inner diameter and outer diameter) than disc spring 63. In Figure 8, the outer diameter of disc spring 63a is approximately the same as the inner diameter D67i of the ring portion 67, but it is not limited to this and may be smaller than the inner diameter D67i of the ring portion 67. By providing a pair of interposing members 65 on both sides that sandwich each plate material in the thickness direction, the same effects as in the above embodiment can be obtained using the smaller disc spring 63a. Therefore, the degree of freedom in the size of the disc spring and the number of parallel springs can be greatly increased.

[0080] <Second variation> Figure 8 is an explanatory diagram of a second modified example of the friction damper 10d of the second embodiment.

[0081] The fastening structure 20d of this friction damper 10d is equipped with a bush 62a and a disc spring 63a on the nut 61n side (between the nut 61n and the third plate material 13).

[0082] The bush 62a has a flange portion 622 and a cylindrical portion 621a. The cylindrical portion 621a is formed to be thinner in the radial direction compared to the cylindrical portion 621 of the bush 62 described above. As a result, the bush 62a can be inserted into the disc spring 63a.

[0083] In this second modified example, a smaller disc spring 63a can also be used.

[0084] <Third variation> Figure 9 is an explanatory diagram of a friction damper 10e of a third modified example of the second embodiment.

[0085] The fastening structure 20e of this friction damper 10e is equipped with a bush 62b and a disc spring 63a on the nut 61n side (between the nut 61n and the third plate material 13).

[0086] The bush 62b has a flange portion 622 and a cylindrical portion 621b. The cylindrical portion 621b has a shorter length in the thickness direction compared to the cylindrical portion 621a of the bush 62a described above.

[0087] In this third modified example, a smaller disc spring 63a can also be used.

[0088] ===Other=== The embodiments described above are provided to facilitate understanding of the present invention and are not intended to limit its interpretation. The present invention can be modified and improved without departing from its spirit, and it goes without saying that the present invention includes equivalents thereof.

[0089] In the embodiment described above, the friction damper 10 was incorporated into the brace 7 of the column-beam frame 1 (between the brace segments 71 and 72), but it is not limited to this, and may be incorporated into parts other than the braces of the building (for example, intermediate columns, partition walls, etc.). It may also be incorporated into structures other than buildings. It can be installed between any two (a pair) members that move relative to each other due to external forces such as earthquakes. [Explanation of symbols]

[0090] 1 Building frame (column beam frame) 7 Brace 10, 10a~10e Friction damper 11 First plate material 11a 1st through hole 12 Second plate material 12a 2nd through hole 13 Third plate material 13a 3rd through hole 20, 20a~20e Fastening structure 40 Flat Washer 40a through hole 60 Fastening members 61b High-strength bolts (bolts) 61h Bolt head 61n nut 62, 62a, 62b bush 63,63a Disc spring 64 Flat Washer 65 Intermediate component 66 Flat Washer Metal Part 67 Ring section 71,72 Brace fragments 71w, 72w Web 100 Friction Damper 621,621a,621b Cylinder part 622 Flange section

Claims

1. A friction damper is positioned between a pair of members that move relative to each other in a predetermined direction, and suppresses the relative movement by the frictional force between the plate materials that slide against each other as a result of the relative movement, A plurality of plates are stacked in a thickness direction intersecting the predetermined direction, including a first plate provided on one of the pair of members and a second plate provided on the other of the pair of members, A fastening member that penetrates each of the through holes in the plurality of plate materials and fastens the plurality of plate materials from both sides in the thickness direction, The end of the fastening member in the thickness direction and the interposing member interposed between the plurality of plate materials, Equipped with, The aforementioned intervening member is The flat washer portion that receives the tightening axial force of the fastening member, A ring portion is disposed between the flat washer portion and the plurality of plate materials, It has, The flat washer portion and the ring portion are friction-joined or engaged. A friction damper characterized by the following features.

2. A friction damper according to claim 1, The intervening member is provided at one end of the fastening member in the plate thickness direction, A disc spring is provided between the other end of the fastening member in the thickness direction of the plate and the plurality of plate materials. A friction damper characterized by the following features.

3. A friction damper disposed between a pair of members that move relative to each other in a predetermined direction, wherein the relative movement is suppressed by the frictional force between plate materials that slide against each other as a result of the relative movement, A plurality of plates are stacked in a thickness direction intersecting the predetermined direction, including a first plate provided on one of the pair of members and a second plate provided on the other of the pair of members, A fastening member that penetrates each of the through holes in the plurality of plate materials and fastens the plurality of plate materials from both sides in the thickness direction, The end of the fastening member in the thickness direction and the interposing member interposed between the plurality of plate materials, Equipped with, The aforementioned intervening member is The flat washer portion that receives the tightening axial force of the fastening member, A ring portion is disposed between the flat washer portion and the plurality of plate materials, It has, The intervening member is provided at one end of the fastening member in the plate thickness direction, A disc spring is provided between the other end of the fastening member in the thickness direction of the plate and the plurality of plate materials. The inner diameter of the ring portion is at least half the outer diameter of the disc spring. A friction damper characterized by the following features.

4. A friction damper disposed between a pair of members that move relative to each other in a predetermined direction, wherein the relative movement is suppressed by the frictional force between plate materials that slide against each other as a result of the relative movement, A plurality of plates are stacked in a thickness direction intersecting the predetermined direction, including a first plate provided on one of the pair of members and a second plate provided on the other of the pair of members, A fastening member that penetrates each of the through holes in the plurality of plate materials and fastens the plurality of plate materials from both sides in the thickness direction, The end of the fastening member in the thickness direction and the interposing member interposed between the plurality of plate materials, Equipped with, The aforementioned intervening member is The flat washer portion that receives the tightening axial force of the fastening member, A ring portion is disposed between the flat washer portion and the plurality of plate materials, It has, The intervening member is provided at one end of the fastening member in the plate thickness direction, A disc spring is provided between the other end of the fastening member in the thickness direction of the plate and the plurality of plate materials. The inner diameter of the ring portion is larger than the inner diameter of the disc spring. A friction damper characterized by the following features.

5. A friction damper according to claim 4, The inner diameter of the ring portion is smaller than the outer diameter of the disc spring. A friction damper characterized by the following features.

6. A friction damper disposed between a pair of members that move relative to each other in a predetermined direction, wherein the relative movement is suppressed by the frictional force between plate materials that slide against each other as a result of the relative movement, A plurality of plates are stacked in a thickness direction intersecting the predetermined direction, including a first plate provided on one of the pair of members and a second plate provided on the other of the pair of members, A fastening member that penetrates each of the through holes in the plurality of plate materials and fastens the plurality of plate materials from both sides in the thickness direction, The end of the fastening member in the thickness direction and the interposing member interposed between the plurality of plate materials, Equipped with, The aforementioned intervening member is The flat washer portion that receives the tightening axial force of the fastening member, A ring portion is disposed between the flat washer portion and the plurality of plate materials, It has, The intervening members are provided in pairs on both sides in the thickness direction of the plates, so as to sandwich the plurality of plates. A friction damper characterized by the following features.

7. A friction damper according to claim 6, A disc spring is provided between the end of the fastening member in the thickness direction and at least one of the pair of interposing members. A friction damper characterized by the following features.

8. A friction damper according to claim 7, The outer diameter of the disc spring is smaller than the inner diameter of the ring portion. A friction damper characterized by the following features.

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