Structural construction

Abstract

This reduces localized wear between plate materials and easily suppresses the decrease in frictional force due to frictional heat. [Solution] A circular plate portion, and an annular projection that protrudes out of the plane from the outer peripheral edge of the circular plate portion, A circular washer characterized by having the following features.

Description

Technical Field

[0001] The present invention relates to a fastening structure.

Background Art

[0002] In building structures and the like, a fastening structure is known in which a plurality of plate materials to be joined are pressed and fastened by a tightening force. For example, the fastening structure of the friction damper of Patent Document 1 includes a bolt and a nut as fastening members for fastening the plate materials to each other, and furthermore, 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 fastening structure such as that of Patent Document 1, since the tightening force (axial force of the fastening member) by the bolt and the nut tends to act 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 the 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 aspect of the present invention for achieving the above object is A fastening structure in which multiple plate materials are fastened together in the thickness direction with fastening members, The fastening member has a circular washer interposed between the end in the thickness direction of the plate and the plurality of plate materials, The aforementioned circular washer is The aforementioned fastening member has a circular plate portion that receives the tightening axial force, An annular projection extending from the outer edge of the circular plate portion toward the side of the plurality of plate materials, It has, The circular washers are provided in pairs so as to sandwich the plurality of plate materials. This fastening structure 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 4A] This is a plan view of the circular washer 65. [Figure 4B] This is a cross-sectional view of a circular washer 65. [Figure 4C] This is a perspective view of a circular washer 65. [Figure 5] Figure 5A is an explanatory diagram of a conventional friction damper 100. Figure 5B is a view taken along the arrow DD in Figure 5A. [Figure 6] This is an explanatory diagram of a modified example of the first embodiment of the friction damper 10a (fastening structure 20a). [Figure 7] This is an explanatory diagram of the friction damper 10b (fastening structure 20b) of the second embodiment. [Figure 8] This is an explanatory diagram of the friction damper 10c (fastening structure 20c) of the first modified example of the second embodiment. [Figure 9] This is an explanatory diagram of a friction damper 10d (fastening structure 20d) of a second modified example of the second embodiment. [Figure 10] It is an explanatory view of the friction damper 10e (fastening structure 20e) of the third modification of the second embodiment.

Mode for Carrying Out the Invention

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

[0011] (Aspect 1) A circular washer having a circular plate portion and an annular convex portion protruding in the out-of-plane direction from the outer peripheral edge portion of the circular plate portion.

[0012] According to the circular washer of Aspect 1, by using it in a fastening structure for fastening a plurality of plate materials with a fastening member, 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) A circular washer used in a fastening structure for fastening a plurality of plate materials with a fastening member, the circular washer having a circular plate portion for receiving the fastening axial force of the fastening member and an annular convex portion protruding from the outer peripheral edge portion of the circular plate portion toward the side of the plurality of plate materials.

[0014] According to the circular washer of Aspect 2, local wear between the plate materials can be reduced, and a decrease in the frictional force due to frictional heat can be easily suppressed.

[0015] (Aspect 3) A fastening structure for fastening a plurality of plate materials in the plate thickness direction with a fastening member, having a circular washer interposed between an end portion of the fastening member in the plate thickness direction and the plurality of plate materials, the circular washer having a circular plate portion for receiving the fastening axial force of the fastening member and an annular convex portion protruding from the outer peripheral edge portion of the circular plate portion toward the side of the plurality of plate materials.

[0016] According to the fastening structure of Aspect 3, it is possible to transmit the fastening axial force to the outside of the fastening member. Thereby, wear in the vicinity of the fastening member can be reduced.

[0017] (Aspect 4) In the fastening structure described in Embodiment 3, it is preferable that the circular washer is interposed between one end of the fastening member in the thickness direction and the plurality of plate materials, and that a disc spring is interposed between the other end of the fastening member in the thickness direction and the plurality of plate materials.

[0018] According to the fastening structure of Embodiment 4, it is possible to stabilize the magnitude of the force (pressure force) that presses multiple plate materials together.

[0019] (Appendix 5) In the fastening structure described in Embodiment 3 or Embodiment 4, it is preferable that a pair of circular washers are provided so as to sandwich the plurality of plate materials.

[0020] According to the fastening structure of Embodiment 5, multiple plate materials can be pressed (press-fitted) at the same position from both sides in the thickness direction. Furthermore, if disc springs are provided, the degree of freedom in terms of size and the number of parallel springs can be greatly increased (smaller disc springs can be used).

[0021] (Aspect 6) A fastening structure according to any one of embodiments 3 to 5, characterized in that it is provided on a friction damper.

[0022] According to the fastening structure of embodiment 6, localized wear when the friction damper operates can be reduced.

[0023] The following description will explain how the circular washer and fastening structure of this embodiment can be applied to a friction damper, with reference to the drawings. In the following, identical or equivalent components and parts shown in each drawing will be denoted by the same reference numerals, and redundant explanations may be omitted as appropriate.

[0024] ===First Embodiment=== <<Regarding the friction damper 10 and fastening structure 20>> 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.

[0025] 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.

[0026] 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 a circular washer 65. These members together constitute the fastening structure 20 shown in Figures 2 and 3A.

[0027] 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.

[0028] 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.

[0029] 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.

[0030] 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.

[0031] 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.

[0032] 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.

[0033] 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.

[0034] 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.

[0035] 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.

[0036] 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.

[0037] 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.

[0038] 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.

[0039] 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.

[0040] 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.

[0041] As shown in Figures 2 and 3A, the circular washer 65 is interposed between the bolt head 61h of the bolt 61b and the first plate material 11.

[0042] <Regarding circular washer 65> Figure 4A is a plan view of the circular washer 65. Figure 4B is a cross-sectional view of the circular washer 65. Figure 4C is a perspective view of the circular washer 65.

[0043] The circular washer 65 of this embodiment comprises a circular plate portion 65b through which a through hole 65a is formed, and an annular protrusion 65t.

[0044] The circular plate portion 65b is a circular plate-shaped part. In the friction damper 10 (fastening structure 20), the circular plate portion 65b is provided on the bolt head 61h side. The circular plate portion 65b receives the tightening force (axial force) of the fastening member 60 from the bolt head 61h.

[0045] The through-hole 65a in the circular plate portion 65b is slightly larger in diameter than the diameter of the bolt 61b, and the bolt 61b is passed through the through-hole 65a. Although there is a gap between the through-hole 65a and the bolt 61b, it is preferable that the gap be as small as possible.

[0046] As shown in Figures 4B and 4C, the annular projection 65t protrudes out of plane (in the thickness direction) from the outer peripheral edge of the circular plate portion 65b. In addition, as shown in Figures 2 and 3A, in the friction damper 10, the annular projection 65t protrudes toward each plate material (first plate material 11 to third plate material 13), and in this case, it is in contact with the first plate material 11.

[0047] For convenience, Figure 3B shows the area (region) where the annular projection 65t is provided using hatching (cross-hatching). The inner diameter D65ti of the annular projection 65t is greater than the minimum outer diameter D61h of the bolt head 61h (D65ti > 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.

[0048] Figure 5A is a diagram illustrating a conventional friction damper 100. Figure 5B is a view from the direction of arrow DD in Figure 5A. For each component of the friction damper 100 in Figures 5A and 5B, 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.

[0049] 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.

[0050] Generally, forces such as pressure are transmitted along the shortest distance. That is, the force f applied from the bolt head 61h is easily transmitted perpendicular to the first plate material 11. Therefore, as shown in Figure 5B, 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 5B, 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 5B, 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.

[0051] 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 annular protrusion 65t that is in contact with the first plate material 11 when the friction damper 10 is viewed from the bolt head 61h side (hatched region in Figure 3B).

[0052] In other words, the friction damper 10 (fastening structure 20) transmits the force f applied from the bolt head 61h to the first plate material 11 via the circular washer 65 (circular plate portion 65b, annular projection portion 65t). 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 annular projection portion 65t and the first plate material 11 overlap in the plate thickness direction (hatched region in Figure 3B).

[0053] 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 annular protrusion 65t 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 5B). 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.

[0054] 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.

[0055] In the friction damper 10 of the present embodiment, on the side where the nut 61n is provided in the plate thickness direction (the tip side of the bolt 61b), since the disc spring 63 is provided, the force applied from the nut 61n side easily acts on a wide range of the third plate material 13 via the disc spring 63. For example, the force easily acts on the outer peripheral portion of the disc spring 63.

[0056] Therefore, it is desirable that the region where the annular convex portion 65t of the circular washer 65 overlaps with the first plate material 11 overlaps with the outer peripheral portion of the disc spring 63. In the present embodiment, as shown in FIG. 3A, the outer diameter D63e of the disc spring 63 and the outer diameter D65te of the annular convex portion 65t are substantially the same. Thereby, the force (resilient force) by the disc spring 63 can be more efficiently applied to each plate material.

[0057] Also, in FIG. 3A (and FIG. 3B), it is desirable that the inner diameter D65ti of the annular convex portion 65t is 1 / 2 or more 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. Therefore, the wear in the vicinity of the bolt 61b of each plate material can be reduced.

[0058] Also, it is desirable that the inner diameter D65ti of the annular convex portion 65t is larger than the inner diameter D63i of the disc spring 63 (D65ti > D63i) and smaller than the outer diameter D63e (D65ti < D63e). Thereby, the pressing contact force can be applied to a position away from the vicinity of the bolt 61b by the disc spring 63 and the circular washer 65 (the annular convex portion 65t).

[0059] The circular washer 65 as in the present embodiment can be easily formed, for example, by cutting a circular shape with one side of a relatively thick flat washer while leaving the outer peripheral edge portion to provide a concave portion (the annular convex portion 65t remains outside the concave portion). Note that this is not limited thereto, and for example, a flat washer and a thin ring may be integrally joined by welding or the like. However, as described above, providing a concave portion can be formed more easily.

[0060] Furthermore, a similar effect can be obtained by interposing multiple components (for example, a flat washer and a ring, a bush and a ring, etc.) between the bolt head 61h and the plate material (in this case, the first plate material 11). However, in this case, each component must be manufactured and prepared separately, and installation is time-consuming. In contrast, the circular washer 65 of this embodiment can be easily manufactured, and the number of components can be reduced, making it easier to simplify the process of forming the friction damper 10.

[0061] <Variation> Figure 6 is an explanatory diagram of a modified example of the first embodiment of the friction damper 10a (fastening structure 20a).

[0062] The fastening structure 20a shown in Figure 6 is a configuration in which the first plate material 11 and the second plate material 12 are fastened together with a fastening member 60 (a configuration without a third plate material 13). Thus, a configuration with two plate materials (one sliding surface) is also possible. However, it is not limited to this, and for example, a configuration in which the second plate material 12 and the third plate material 13 are fastened together with a fastening member 60 (a configuration without the first plate material 11) is also possible.

[0063] Furthermore, although not shown in the diagram, additional plates may be added to increase the number of sliding surfaces. For example, five plates (pressure plates) may be used to create a friction damper (fastening structure) with four sliding surfaces (four sides).

[0064] In these cases as well, the same effects as those of the above-described embodiment can be obtained by using the circular washer 65.

[0065] Furthermore, the positions of the bolt head 61h and nut 61n of the fastening member 60 may be reversed. That is, 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 circular washer 65 side. In this case as well, each plate material can be fastened. Also, by using the circular washer 65, the same effects as in the above embodiment can be obtained.

[0066] ===Second Embodiment=== Figure 7 is an explanatory diagram of the friction damper 10b (fastening structure 20b) of the second embodiment.

[0067] The fastening structure 20b of the second embodiment is provided with a pair of circular washers 65. The pair of circular washers 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, a circular washer 65 is also provided (interposed) between the third plate material 13 and the disc spring 63. The annular projection 65t of the circular washer 65 abuts against the third plate material 13.

[0068] Since the pair of circular washers 65 are made of the same material, by passing a bolt 61b through them and screwing them together with a nut 61n, the same position (apart from the bolt 61b) on each plate material (first plate material 11, second plate material 12, third plate material 13) can be pressed (pressed) from both sides in the thickness direction of the plate. Note that the pair of circular washers 65 do not have to be exactly the same. For example, the protruding height of the annular projection 65t may be different.

[0069] In this second embodiment, the same effects as in the first embodiment can be obtained.

[0070] <First variation> Figure 8 is an explanatory diagram of a friction damper 10c (fastening structure 20c) of the first modified example of the second embodiment. The fastening structure 20c 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 circular washer 65).

[0071] 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.

[0072] 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 D65ti of the annular projection 65t, but it is not limited to this and may be smaller than the inner diameter D65ti of the annular projection 65t. By providing a pair of circular washers 65 on both sides that sandwich each plate material in the thickness direction, the same effect as in the above embodiment can be obtained by using a 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.

[0073] <Second variation> Figure 9 is an explanatory diagram of a friction damper 10d (fastening structure 20d) of a second modified example of the second embodiment. The fastening structure 20d 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).

[0074] 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. This allows it to be inserted into the disc spring 63a.

[0075] In this second modified example, a smaller disc spring 63a can also be used.

[0076] <Third variation> Figure 10 is an explanatory diagram of a friction damper 10e (fastening structure 20e) of a third modified example of the second embodiment. The fastening structure 20e 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).

[0077] 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 of the second modified example.

[0078] In this third modified example, a smaller disc spring 63a can also be used.

[0079] ===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.

[0080] In the embodiments described above, the fastening structure 20 and the circular washer 65 were described in the case where they are provided on the friction damper 10. However, the invention is not limited to friction dampers and can be applied to anything that fastens multiple plate materials together by pressing them together. For example, it can be applied to joints of various plate materials such as columns, beams, and deck plates of floor slabs. [Explanation of symbols]

[0081] 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 Circular Washer 65a through hole 65b Circular plate section 65t annular protrusion 71,72 Brace fragments 71w, 72w Web 100 Friction Damper 621,621a,621b Cylinder part 622 Flange section

Claims

1. A fastening structure in which multiple plate materials are fastened together in the thickness direction with fastening members, The fastening member has a circular washer interposed between the end in the thickness direction of the plate and the plurality of plate materials, The aforementioned circular washer is The aforementioned fastening member has a circular plate portion that receives the tightening axial force, An annular projection extending from the outer edge of the circular plate portion toward the side of the plurality of plate materials, It has, The circular washers are provided in pairs so as to sandwich the plurality of plate materials. A fastening structure characterized by the following features.

2. The fastening structure according to Claim 1, One of the pair of circular washers is interposed between one end of the fastening member in the thickness direction of the plate and the plurality of plate materials. A disc spring is interposed between the other end of the fastening member in the thickness direction of the plate and the plurality of plate materials. The other of the pair of circular washers is provided between the plurality of plate materials and the disc spring. A fastening structure characterized by the following features.

3. A fastening structure according to claim 1 or 2, It is installed in the friction damper, A fastening structure characterized by the following features.

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