JP5787142B2 - Spring member - Google Patents

Description

  The present invention relates to a spring member that uses a disc spring, and more particularly to a spring member that can handle both a tensile force and a compressive force with a simple configuration.

  As is well known, a disc spring is used in various devices as a spring member that is compact and has a large load resistance. In particular, as shown in Patent Document 1, since a plurality of disc springs are used in combination in series or in parallel, deformation performance and load resistance can be increased, so that there is an advantage that predetermined performance can be obtained at a lower cost and more compact than a coil spring. is there.

  On the other hand, since the disc spring alone can only deal with compressive force, in order to make a spring element that can cope with not only compressive force but also tensile force, for example, as shown in Patent Document 2, It is necessary to use a combination of a disc spring group and a disc spring group to cope with the tensile force.

  FIG. 9 shows an example of such a spring member. A piston 2 that can be displaced in both directions is disposed in a cylinder 1, and a disc spring 3 as shown in FIG. The piston 2 is housed and configured as two sets of disc spring groups 3 </ b> A and 3 </ b> B that are stacked in series on each side of the piston 2 (eight in the illustrated example).

  In this spring member, one (the right side of the piston 2 in the illustrated example) of the disc spring group against the compression force generated between the rod 4 connected to the piston 2 and the clevis 5 provided at one end of the cylinder 1. The entire 3A is pressed by the piston 2 in one direction (rightward in the illustrated example) and elastically compressed, and the other (the same, the left) disk spring group 3B is moved to the piston for the tensile force. It is possible to cope with this by pressing in the opposite direction (same as the left side) and elastically compressing by 2. On the other hand, in the spring member configured so as to correspond to both the compressive force and the tensile force by combining the two sets of disc spring groups 3A and 3B in this way, a large number of disc springs 3 are required, and the entire configuration of the spring member is required. There were limits to simplification, compactness, and low cost.

  On the other hand, the applicant of the present application has already filed an application relating to the invention of a spring member that can cope with both compression force and tensile force while the overall configuration is sufficiently simple, compact and low cost (Japanese Patent Application No. 2011-022631). ). As shown in FIG. 10, the spring member 10 has the rod 4 in the direction of the axis O1 with respect to the whole spring element in which the pressing plates 12 (12a, 12b) are disposed on both ends of the pair of disc spring groups 3A. Are inserted in such a manner that they can be displaced relative to each other, and force bolts as stoppers 13 (13a, 13b) are screwed into positions on the outside of the push plates 12a, 12b of the rod 4, respectively.

  As shown in FIGS. 10 and 11, the spring member 10 presses the inner surfaces of the annular lid bodies 14 (14 a, 14 b) provided on the both ends of the cylinder 1 by the pressing plates 12 a, 12 b, respectively. The entire spring element is accommodated in the cylinder 1 in a possible state. When a tensile force is applied, as shown in FIG. 11A, the push plate 12a on the back side (right side in the drawing) of the cylinder 1 is drawn into the cylinder 1 and the whole disc spring group 3A is elastic. Compressed. On the contrary, when a compressive force is applied, as shown in FIG. 11B, the push plate 12b on the front side (the left side in the figure) of the cylinder 1 is drawn into the cylinder 1, and the whole disc spring group 3A is elastic. Compressed. As a result, since one set of disc spring groups 3A can cope with both tension and compression, the required number of disc springs 3 can be reduced, and simplification, compactness, and low cost can be achieved. .

JP 2010-38228 A JP 2000-243424 A

  Here, FIG. 12 shows a result of an experiment for confirming a load-deformation relationship using the spring member 10 shown in FIGS. In addition, the load of the vertical axis | shaft of FIG. 12 is tension | tensile_strength and negative | negative is compression, and the dashed-dotted line in the figure has shown the rigidity (theoretical rigidity) calculated only from the disc spring. Further, in the experiment, a precompression load of 10 kN is applied in order to eliminate the gap between the adjacent disc springs 3, and accordingly, as shown in FIG. 12, about 10 kN of the precompression load in the load direction near the origin. A slip occurred.

  From the result of FIG. 12, the rigidity of the spring member 10 is almost as theoretical on the compression side, but is reduced by about 15% on the tension side (decreases by 0.85 times on the compression side). confirmed. This is because the tensile strain (elongation deformation) of the rod 4 and the cylinder 1 is added on the tension side, and thus the spring stiffness is different between the tension side and the compression side, which deviates from the theory of a linear spring. . For this reason, it is desired that the spring rigidity on the tension side and the compression side be made uniform so that the linear condition can be satisfied, and there remains room for improvement in this respect.

  As shown in FIG. 12, the spring member 10 using the disc spring 3 has a hysteresis characteristic in which the gradient is different between when it is applied and when it is unloaded, but this origin-oriented hysteresis characteristic is absorbed. Since the energy is small and no residual displacement occurs, this is not a big problem.

  In view of the above circumstances, the present invention provides a suitable and appropriate spring member that can cope with both compressive force and tensile force while using a disc spring, the overall configuration being sufficiently simple, compact, and low cost. Another object of the present invention is to provide a spring member capable of adjusting spring rigidity on the tension side and compression side.

  In order to achieve the above object, the present invention provides the following means.

  The spring member of the present invention is a spring member that is interposed between two members that are relatively displaceable in the direction of separating from each other, and elastically expands and contracts due to the relative displacement generated between the two members. A rod element inserted so as to be relatively displaceable in the axial direction with respect to the cylinder element, and a spring element assembled to the distal end portion of the rod element and accommodated in the cylinder element. The two members can be connected to the cylinder part and the cylinder element, respectively, and the spring element has push plates on both ends of a pair of disc spring groups formed by stacking a plurality of disc springs in series and / or in parallel. The rod elements are respectively inserted so as to be capable of relative displacement in the axial direction with respect to the whole spring element, and the rod elements are respectively positioned at positions outside the pressing plates. A stopper is provided, and the entire spring element is assembled between the stoppers in an elastically displaceable manner on both axial sides of the rod element, and the base end of the rod element is the cylinder element. The tip of the rod element is inserted into the cylinder element in a state of extending outward from the cylinder element, and the push plates are respectively against the inner surfaces of the lids provided at both ends of the cylinder element. The whole spring element is accommodated in the cylinder element in a state where it can be pressed, and an elastic body is interposed between one push plate on the tip end side of the rod element and the inner surface of one lid body. It is characterized by being.

  In the spring member of the present invention, when the rigidity of the rod element between the pair of stoppers is kn, the axial rigidity of the cylinder element is ks, and the axial rigidity of the elastic body is ke, ke = 1 / ( 1 / kn + 1 / ks), the rigidity ke of the elastic body is set.

  In the spring member of the present invention, when the spring member is compressed, the rod element is relatively displaced to one side in the axial direction with respect to the cylinder element, and one pressing plate is pressed to one lid side, The elastic body is elastically deformed by being sandwiched between the two lid bodies, and the other pressing plate is pressed toward the inside of the cylinder element by the stopper, so that the whole spring element is elastically compressed. When the spring member is pulled, the rod element is displaced relative to the cylinder element on the other side in the axial direction, the other pressing plate is pressed against the other lid, and the one pressing plate is pressed by the stopper to the cylinder element. And the whole spring element is elastically compressed.

  As a result, one set of disc spring groups is compressed and functions as a spring member having a certain spring rigidity both during tension and compression, so two sets of disc spring groups are required like conventional spring members. Therefore, even if it has the same spring rigidity as the conventional one, the required number of disc springs can be halved and the required length of the entire spring member can be halved. As a result, the structure can be simplified and miniaturized sufficiently. The price can be reduced.

  In addition, when the spring member is compressed, the elastic body is elastically deformed by being sandwiched between one push plate and one lid body, and elastic force is generated. Therefore, by adjusting the rigidity of the elastic body, The rigidity of the whole spring member can be changed. Therefore, the tension-side spring stiffness can be freely changed, and the tension-side and compression-side spring stiffness can be easily adjusted.

  Further, by setting the rigidity ke of the elastic body so that ke = 1 / (1 / kn + 1 / ks), it becomes possible to obtain the same rigidity as the whole spring member during tension and compression. Therefore, it is possible to make the spring member satisfying the linear condition by surely matching the spring rigidity on the tension side and the compression side.

It is a figure which shows the spring member which concerns on one Embodiment of this invention. It is a figure which shows the operation state at the time of the tensile force and the compressive force acting on the spring member which concerns on one Embodiment of this invention. It is a figure which shows the example of a shape of the disk spring single-piece | unit which the spring member which concerns on one Embodiment of this invention comprises. It is a figure which shows the structural example (example of the combination pattern of a disc spring) of the disc spring group which the spring member which concerns on one Embodiment of this invention comprises. It is a figure which shows an example of the load-deformation characteristic in the spring member which concerns on one Embodiment of this invention. It is a figure which shows the modification of the spring member which concerns on one Embodiment of this invention. It is a figure which shows the example of a design of a load-deformation characteristic. It is a figure which shows an example in the case of applying the spring member which concerns on one Embodiment of this invention to a damping mechanism. It is a figure which shows the conventional spring member. It is a figure which shows the conventional spring member. It is a figure which shows the operation state at the time of a tensile force and a compressive force acting on the spring member shown in FIG. It is a figure which shows an example of the load-deformation characteristic in the spring member shown in FIG.

  Hereinafter, a spring member according to an embodiment of the present invention will be described with reference to FIGS. 1 to 5. In the present embodiment, the same components as those of the conventional spring member 10 shown in FIGS. 10 and 11 will be described with the same reference numerals.

  As shown in FIGS. 1 and 2, the spring member A of the present embodiment includes a cylinder element 1 (hereinafter simply referred to as a cylinder 1) and a rod that is inserted into the cylinder 1 so as to be capable of relative displacement in the direction of the axis O <b> 1. An element 4 (hereinafter simply abbreviated as a rod 4) and a spring element 11 assembled at the tip of the rod 4 and housed in the cylinder 1 are configured.

  The spring element 11 is provided with push plates 12 (12a, 12b) on both ends of a set of disc spring groups 3A in which a plurality of disc springs 3 (eight in the illustrated example) are stacked in series. It is. Further, the rod 4 is inserted into the whole spring element 11 so as to be relatively displaceable in the direction of the axis O1, and the rod 4 is provided as a stopper 13 (13a, 13b) at a position outside each push plate 12, respectively. These spring bolts are screwed together, and the entire spring element 11 is assembled between these stoppers 13 so as to be elastically displaceable on both sides of the rod 4 in the axis O1 direction.

  Then, with the base end portion of the rod 4 extending outward (leftward in the illustrated example) from the cylinder 1, the distal end portion is inserted into the cylinder 2, so that each push plate 12 is moved to each cylinder. 1 is disposed in a state where it can be pressed against the inner surface of an annular lid body 14 (14 a, 14 b) provided at both ends, and the entire spring element 11 is accommodated in the cylinder 1.

  Further, in the spring member A of the present embodiment, a rubber is interposed between one inner push plate 12a (the right push plate in the drawing) of the cylinder 1 and one inner lid body 14a. An elastic body 15 such as is interposed. That is, the spring member A is provided such that the other pressing plate 12b on the front side of the cylinder 1 (the pressing plate on the left side in the drawing) can be directly pressed against the other lid body 14b on the front side. One push plate 12a on the back side is provided on one lid body 14a on the back side so as to be indirectly pressable via an elastic body 15. Further, the elastic body 15 is formed in an annular shape, and its inner hole is formed with an inner diameter larger than the outer diameter of the force-applying nut that is the one stopper 13a on the back side. Accordingly, the spring member A is configured such that one stopper 13a abuts the outer surface of one pressing plate 12a through the inner hole of the elastic body 15. Further, the elastic body 15 of the present embodiment is integrally fixed to the one pressing plate 12a.

  When the spring element 11 is accommodated in the cylinder 1, the spring element 11 may be accommodated in the cylinder 1 and then the lid 14 may be attached to the cylinder 1 and bolted. Alternatively, the cylinder 1 Are divided into two in the circumferential direction (or more divided) and attached to the outside of the spring element 11 to connect them together, or the cylinder 1 is divided into two in the length direction and What is necessary is just to connect integrally, after accommodating the spring element 11 inside.

In any case, as shown in the illustrated example, the disc spring 3 that is in contact with the pressing plate 12 is arranged so that the large diameter side (the surface of the large diameter dimension D shown in FIG. 3) faces the pressing plate 12. preferable.
Further, since the rod 4 functions as a member that guides the deformation and displacement of each disc spring 3, the hardness of the rod 4 is preferably HRC 55 or more, and the peripheral surface in contact with the disc spring 3 is preferably a smooth cylindrical surface. .

  The spring member A according to the present embodiment is interposed between two members (not shown) that can be relatively displaced in a direction to be separated from each other in the same manner as a normal spring member, for example, as a component of a vibration damping mechanism. One of these two members is connected to the base end of the rod 4 and the other is connected to the clevis 5 provided in the cylinder 1. Yes. When relative displacement or relative vibration occurs between the two members, the entire spring element 11 is elastically compressed in both directions, so that the entire spring member A has a predetermined spring rigidity. Is elastically expanded and contracted on both sides in the direction of the axis O1.

  That is, when the spring member A is interposed between the two members in the state shown in FIG. 1, a relative displacement occurs in the direction in which the two members are separated from each other, and the spring member A as shown in FIG. When a tensile force is applied to both ends of the rod 4, the rod 4 is displaced in the direction of pulling out from the cylinder 1 and the entire spring member A is expanded. At that time, the back side push plate 12a is drawn into the cylinder 1 by the back side stopper 13a, and the whole disc spring group 3A is displaced in one direction (left direction in the figure) by the push plate 12a. At the same time, the front-side pressing plate 12b is pressed against the front-side lid 14b, whereby the entire spring element 11 is elastically compressed.

  Conversely, when relative displacement occurs in the direction in which the two members approach each other and a compressive force acts on both ends of the spring member A as shown in FIG. The whole spring member A is degenerated by being displaced in the pushing direction. At this time, the front-side pressing plate 12b is pushed into the cylinder 1 by the front-side stopper 13b, and the whole disc spring group 3A is displaced in the reverse direction (right direction in the drawing) by the pressing plate 12b. Then, the elastic body 15 is pressed by the back-side push plate 12a, and the elastic body 15 is elastically deformed and the back-side push plate 12a is pressed against the back-side cover body 14a, whereby the spring element 11 is pressed. The whole is compressed elastically.

  As described above, according to the spring member A of the present embodiment, the pair of disc spring groups 3A can be compressed to cope with both the tensile force and the compressive force in both the tension state and the compression state. Unlike the conventional spring member shown in FIG. 9, two sets of disc spring groups 3A and 3B are not required, and therefore the required number of disc springs 3 can be halved even if the spring stiffness is equivalent to the conventional one. The required length of the spring member A as a whole can also be halved. As a result, the structure can be sufficiently simplified, downsized, and reduced in cost.

  Of course, by adjusting the spring rigidity of the disc spring 3 as a single unit and the number of these, it is possible to deal with a wide range of arbitrary deformation performance and proof stress. For this purpose, the shape and dimensions of the disc spring 3 alone (large diameter dimension D, small diameter dimension d, total height H, rise h, plate thickness t) are arbitrarily set according to the elastic characteristics of the steel material. Should be set.

  Further, the number and arrangement pattern of the disc springs 3 may be arbitrarily designed in various patterns as shown in FIG. 4, for example, so that desired spring rigidity can be obtained as the whole disc spring group 3A. In this case, if the disc springs 3 are arranged in parallel, the proof stress (load) can be increased. If the disc springs 3 are arranged in series, the deformation performance can be increased. The number of sheets necessary for a predetermined load may be arranged in parallel, and the number of sheets necessary for the predetermined deformation may be arranged in series.

  In any case, the deformation performance δ of the disc spring alone is preferably δ ≦ 0.75 h with respect to the rise h of the disc spring alone. Further, the proof stress p of the disc spring alone may be a reaction force when the deformation is δ, and the relationship of load F-deformation (deflection) δ can be made closer to linear. Specifically, the deformation amount x and the burden force F of the whole spring member A are preferably set so that the number of in-line pieces ≧ x / δ and the number of parallel pieces ≧ F / p.

  On the other hand, in the spring member A of the present embodiment, as shown in FIG. 2B, when a compressive force is applied, the elastic body 15 is pressed by the push plate 12a on the back side, and the elastic body 15 is elastic. While being deformed, a compressive force is transmitted to the inner lid 14 a via the elastic body 15.

  As described above, the elastic body 15 is provided so that the elastic body 15 contracts only during compression, so that the displacement amount δ of the spring member A as a whole is full length rod displacement + disc spring displacement + cylinder displacement + joining member during tension. It is expressed by displacement (displacement of the clevis 5 etc.), and at the time of compression, it is expressed by displacement inside the left side (the left side in the figure) + disc spring displacement + elastic body displacement + joining member displacement.

  For this reason, when the force P during tension and compression is the same, assuming that the rigidity is the same between tension and compression, the difference in displacement between tension and compression is 0 (the rod between the left and right stoppers). Displacement + cylinder displacement−elastic body displacement = 0). Thus, assuming that the rod stiffness between the left and right stoppers is kn, the cylinder shaft stiffness is ks, and the axial stiffness of the elastic body is ke, P / kn + P / ks−P / ke = 0, ke = 1 / (1 / Kn + 1 / ks).

  Therefore, in the spring member A of the present embodiment, the rigidity of the entire spring member A against compression is changed by adjusting the magnitude of the rigidity ke of the elastic body 15. When the rigidity ke of the elastic body 15 is set so that ke = 1 / (1 / kn + 1 / ks), as shown in FIG. 5, the same rigidity is obtained as the whole spring member A during tension and compression, The spring stiffness is surely obtained on the tension side and the compression side, and the spring member A satisfies the linear condition.

  Therefore, in the spring member A of the present embodiment, when the spring member A is compressed, the rod element 4 is relatively displaced with respect to the cylinder element 1 on one side in the axis O1 direction, and one push plate 12a is one lid. The elastic body 15 is pressed between the one pressing plate 12a and the one lid body 14a and is elastically deformed while the other pressing plate 12b is moved toward the inside of the cylinder element 1 by the stopper 13b. When pressed, the entire spring element 11 is elastically compressed. Further, when the spring member A is pulled, the rod element 4 is relatively displaced with respect to the cylinder element 1 to the other side in the direction of the axis O1, and the other pressing plate 12b is pressed against the other lid body 14b and one of the pressing elements is pressed. The plate 12a is pressed toward the inside of the cylinder element 1 by the stopper 13a, and the entire spring element 11 is elastically compressed.

  As a result, the pair of disc spring groups 3A is compressed and functions as a spring member A having a certain spring rigidity both during tension and compression, so that two sets of disc spring groups as in the conventional spring member. 3A and 3B are not required, and therefore the required number of disc springs 3 can be halved and the required length of the entire spring member A can be halved even if it has the same spring rigidity as that of the prior art. Simplification, miniaturization and cost reduction can be realized.

  Further, when the spring member A is compressed, the elastic body 15 is elastically deformed by being sandwiched between the one pressing plate 12a and the one lid body 14a, and an elastic force is generated. Therefore, the rigidity ke of the elastic body 15 is adjusted in size. By doing so, the rigidity of the whole spring member A with respect to compression can be changed. Therefore, it is possible to easily adjust so that the spring stiffness on the tension side and the compression side are made uniform.

  Furthermore, by setting the rigidity ke of the elastic body 15 so that ke = 1 / (1 / kn + 1 / ks), it is possible to obtain the same rigidity as the whole spring member A during tension and compression. Therefore, it is possible to make the spring member A satisfying the linear condition by surely matching the spring rigidity on the tension side and the compression side.

  As mentioned above, although one embodiment of the spring member concerning the present invention was described, the present invention is not limited to the above-mentioned one embodiment, and can be suitably changed in the range which does not deviate from the meaning.

  For example, as shown in FIG. 6, a disc spring may be applied as the elastic body 15 according to the present invention. When a disc spring is used as the elastic body 15, the disc spring as the elastic body 15 has a large diameter side (a surface having a large diameter D shown in FIG. 3) on the inner surface side of the lid body 14a as in the illustrated example. It is preferable to arrange so as to face.

  Further, the spring member according to the present invention preferably has a linear load-deformation characteristic as shown in FIG. 7 (a). For this purpose, the disc spring 3 and the pressing plates 12a and 12b are in contact with each other at normal times. And the pressing plate 12b and the lid body 14b, the pressing plate 12a and the elastic body 15, and the elastic body 15 and the lid body 14a are in contact with each other, there is no gap between them and the disc spring group 3A is precompressed. The spring member A may be assembled in a state where there is no load. For this purpose, the size and thickness of each part of each component may be precisely processed in advance. However, if necessary, a spacer having an appropriate thickness may be interposed between them to make fine adjustments.

However, a gap is intentionally secured between the disc spring 3 and the pressing plates 12a and 12b, the pressing plate 12b and the lid body 14b, the pressing plate 12a and the elastic body 15, and the elastic body 15 and the lid body 14a. By applying a precompression load to 11 in advance, the spring member A of the present invention can also have a non-linear characteristic.
That is, if the clearance δ0 as described above is ensured for the spring element 11, the characteristic becomes a slip type as shown in FIG. 7B, and a precompression force F0 is applied to the spring element 11. If this is the case, the characteristics are as shown in FIG. 7C, and the design may be optimized so as to correspond to the application and purpose of use of the spring member A.

  Further, in the spring member A of the present embodiment, the rod 4 and the clevis 5 are connected to the two members that can be relatively displaced, but the clevis 5 is omitted and the cylinder 1 itself is directly connected to the member. That's fine.

  Furthermore, in the present embodiment, the rod element is simply the rod 4 and the cylinder element is simply the cylinder 1, but the rod element of the present invention is “the inner side of the disc spring 3 and the plate at the disc spring group 3A at both ends. 12 ”integrated with the outer stopper 13”, and the cylinder element may be “supporting the elastic force generated by the disc spring group 3 </ b> A and the elastic body 15”. The form of the rod element is arbitrary.

In addition, the spring member A of the present invention can be widely applied as a spring element for various uses and purposes, but can be suitably applied as a component of a vibration control mechanism particularly for structures such as buildings. An example is shown in FIG.
This is a V-shaped brace 22 fixed to the upper beam 21a in order to control inter-layer deformation by being installed in a frame composed of columns 20 and beams 21 (21a, 21b) in the building. Is supported so as to be relatively displaceable in the plane with respect to the beam 21b on the lower floor via the joining jig 23, and the inertia mass damper 24 and the present invention are interposed between the joining jig 23 and the beam 21b on the lower floor. Are connected in series, and an oil damper 26 is connected between the joining jig 23 and a damper mounting jig 25 fixed to the beam 21b on the lower floor. The spring member A of the invention and the oil damper 26 constitute a synchronous vibration damping mechanism.

  In such a vibration damping mechanism, when a conventional general coil spring or a conventional general spring member including two disc spring groups 3A and 3B as shown in FIG. 9 is used as a spring element, the dimension becomes long. However, by using the spring member A of the present invention as described above, the required length as the spring element can be sufficiently shortened and can be stored without any trouble. .

  Further, in the above vibration damping mechanism, it is conceivable to integrate the spring member A and the oil damper 26 of the present invention. That is, if the cylinder 1 of the spring member A of the present invention and the cylinder of the oil damper 26 are integrated, and the rod 4 of the spring member A of the present invention and the rod of the oil damper 26 are integrated, the spring element and the damping element Can be integrated in a compact manner.

1 cylinder (cylinder element)
2 piston 3 disc spring 3A disc spring group 3B disc spring group 4 rod (rod element)
5 Clevis 10 Conventional spring member 11 Spring element 12 Push plate 12a One push plate 12b The other push plate 13 Stopper 13a One stopper 13b The other stopper 14 Lid 14a One lid 14b The other lid 15 Elastic body 20 Column 21 Beam 22 V-shaped brace 23 Connecting jig 24 Inertial mass damper 25 Damper mounting jig 26 Oil damper A Spring member O1 Shaft

Claims (2)

A spring member that is interposed between two members that can be displaced relative to each other in a direction to be separated from each other, and elastically expands and contracts by a relative displacement generated between the two members,
A cylinder element, a rod element inserted so as to be axially displaceable relative to the cylinder element, and a spring element assembled to the tip of the rod element and housed in the cylinder element, The two members can be connected to the base end of the rod element and the cylinder element, respectively.
The spring elements are each provided with a push plate on both ends of a set of disc spring groups in which a plurality of disc springs are stacked in series and / or in parallel.
The rod element is inserted into the whole spring element so as to be relatively displaceable in the axial direction, and the rod element is provided with a stopper at a position outside each of the pressing plates. The entire spring element is assembled in a state where it can be elastically displaced on both axial sides of the rod element,
With the base end of the rod element extending outwardly from the cylinder element, the tip end of the rod element is inserted into the cylinder element, and the push plates are respectively connected to both end portions of the cylinder element. The entire spring element is accommodated in the cylinder element in a state where it can be pressed against the inner surface of the lid body provided in
A spring member characterized in that an elastic body is interposed between one push plate on the distal end side of the rod element and the inner surface of one lid. The spring member according to claim 1,
When the rigidity of the rod element between the pair of stoppers is kn, the axial rigidity of the cylinder element is ks, and the rigidity of the elastic body in the axial direction is ke, ke = 1 / (1 / kn + 1 / ks). A spring member in which a rigidity ke of the elastic body is set.

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