JP2012237422A - Spring - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a spring for which the use for upward movement and/or the use for downward movement can be selected appropriately, and for which the spring constant can be adjusted suitably to a low value with the selected use.SOLUTION: In a cross section in the axial direction of a body part 10, a middle part between an inner circumferential part 10A and an outer circumferential part 10B forms a protrusion with respect to a straight line connecting the inner circumferential part 10A and the outer circumferential part 10B, and that protrusion is formed with a curving shape. When a load P which moves a first flange part 11 upward is applied, the body part 10 undergoes elastic deformation and the inner circumferential part 10A of the body part 10 moves upward. When a load P which moves the first flange part 11 downward is applied, the body part 10 undergoes elastic deformation and the inner circumferential part 10A of the body part 10 moves downward. With the deformation of the spring 1, whether moving upward or moving downward, a tensile mode wherein tension is applied with respect to the radial direction of the body part 10 can be exhibited, and in this case a bending deformation can be achieved.

Description

  The present invention relates to a spring used for suppressing vibration transmission, and more particularly to improvement of a spring shape suitable for use in a high frequency band.

  In various fields such as the automobile industry, precision equipment industry, home appliances, and architecture, technology for suppressing vibration transmission is required, and elastic members are used in the technology for suppressing vibration transmission. For example, in a suspension device that is a device that suppresses impact transmission from a road surface to a vehicle body in a vehicle such as an automobile, an elastic member is used between the shock absorber and the vehicle body.

  Specifically, the suspension device includes a shock absorber and a suspension spring. The shock absorber has a piston part connected to the vehicle body side and a cylinder part connected to the wheel side and slidably guiding the piston part. The cylinder part is connected to the wheel side via a suspension arm or the like. The piston portion has a rod at its upper end, the upper end of the rod is connected to the vehicle body side, and a valve is fixed to the lower end of the rod. The valve of the piston part slides on the inner surface of the cylinder part, and the rod slides on the seal of the rod guide part provided around the rod. The piston portion and the upper end portion of the suspension spring are connected to the vehicle body side via an upper seat.

  Since the shock absorber cannot follow vibrations in a high frequency band or a fine amplitude region, a shock absorbing function cannot be realized for those vibrations. For example, when stick slip occurs between the seal of the rod guide portion and the rod, smooth operation cannot be performed. As a result, the ride comfort becomes worse. Therefore, an elastic member is provided between the shock absorber and the vehicle body as described above in order to prevent the ride comfort from deteriorating. In this case, the vibration in the vertical direction of the vehicle body (axial direction of the shock absorber) from the rod of the piston part acts as a shear stress on the elastic member, so it is necessary to ensure steering stability.

  As a result, the elastic member has a soft spring characteristic in the high frequency band in the axial direction of the shock absorber (the dynamic spring constant in the axial direction of the shock absorber is low), and in a direction other than the axial direction of the shock absorber. Suppression is required (high rigidity).

  Conventionally, for example, a rubber member has been used as the elastic member as disclosed in Patent Document 1, but in the case of a rubber member, the dynamic spring constant is high, and the ratio of the spring constant in the axial vertical direction / axial direction is high. The above problem cannot be solved because there is a limit to the increase.

  Therefore, it is conceivable to use a metal spring having a low dynamic spring constant as the elastic member, and there is a disc spring as a metal spring that can satisfy the above characteristics (for example, Patent Document 2). The disc spring is normally premised on a usage pattern in which the load fluctuates in a vertical direction from a state where a predetermined load is applied as a normal load. In the disc spring, by adjusting the ratio of the height H to the plate thickness t (= H / t), the spring constant at the normal load and the minute amplitude in the vertical direction can be set low.

  FIG. 31 shows a state in which the disc spring 200 is installed between the first member 111 and the second member 112, (A) is a state before the operation, and (B) is a state in which the first member 111 is the disc spring 200. A state when moving in the same direction as the protruding direction (when moving upward), (C) is an axis representing a state when the first member 111 moves in the direction opposite to the protruding direction of the disc spring 200 (when moving downward). FIG. In FIG. 31, the right part of the disc spring 200 is shown, and the protruding direction of the disc spring 200 is the direction seen from the second member 112. The disc spring 200 includes a main body 210 having a substantially conical shape and having a hole 210 </ b> A. Flange portions 211 and 212 are formed on the inner peripheral portion and the outer peripheral portion of the main body portion 210. The flange portion 211 on the inner peripheral portion side protrudes toward the inner side of the inner peripheral portion, and the flange portion 212 on the outer peripheral portion side protrudes toward the outer side of the outer peripheral portion. The flange portions 211 and 212 are completely fixed to the first member 111 and the second member 112. The shapes of the first member 111 and the second member 112 correspond to the shapes of the flange portions 211 and 212.

  For example, when an example (conventional example) of a disc spring 200 shown in FIG. 31A is used and a load is applied with H / t set to 7, the characteristics shown in FIG. 32 are obtained. In this case, the plate thickness t is 0.6 mm, the outer diameter φ is 131.4 mm, the inner diameter φ is 28.8 mm, the outer diameter φ of the outer peripheral flange portion 212 is 161.4 mm, and the inner diameter of the flange portion of the inner peripheral portion 211. φ is set to 13 mm. In the present application, the load deflection characteristic is obtained by a finite element method (FEM). In the present application, the inner side indicates the radial center side direction, and the outer side indicates the direction opposite to the radial center side direction. In the present application, the diameter dimensions such as the inner diameter and the outer diameter are the dimensions at the center of the plate thickness, and the load P applied to the disc spring is shown as an absolute value in all the graphs showing the load values. In the present application, the sign of the deflection amount when moving upward is positive, and the sign of the deflection amount when moving downward is negative. As shown in FIG. 32, when used in a load range of 1200 N ± 50 N, the load can be supported with a low spring constant of 500 N / mm or less.

Patent 2662164 Japanese Examined Patent Publication No. 62-30924

  When the disc spring 200 is provided in the shock absorber, since the load from the vehicle body is received by the suspension spring, the initial state of the disc spring 200 is an unloaded state. In this state, since a high load is applied in the up and down direction, the disc spring 200 is used in both swings. It is essential to provide the disc springs 200 with the flange portions 211 and 212 in the usage mode in which both swings.

  In the disc spring 200, as shown in FIG. 31B, when the first flange portion 11 moves upward as the first member 111 moves upward, as shown by the arrow in the figure, the main body portion 210 moves in the radial direction. It becomes the tension mode in which tension is applied to. On the other hand, as shown in FIG. 31C, when the first flange portion 211 moves downward as the first member 111 moves downward, the main body portion 210 moves in the radial direction as shown by the arrow in the figure. It becomes a compression mode in which compression is applied to.

  FIG. 33 is a graph showing characteristics obtained by changing H / t in the conventional example. In this case, the size and the mating member other than H / t are not changed. As shown in FIG. 33, the spring constant in the compression mode can be set low by setting H / t small, but the spring constant in the tension mode during upward movement is adjusted by adjusting H / t. However, it cannot be set as low as the spring constant in the compression mode during the downward movement, and is significantly different from the spring constant in the compression mode. Therefore, the disc spring 200 cannot be used as an upward moving spring.

  Further, in the load deflection diagram in the compression mode at the time of downward movement, when H / t is set large, the change in the absolute value of the load P shifts from a monotonous increase to a decrease at a predetermined deflection amount or more. In this case, even if the load P is removed after applying a load P larger than the peak of the absolute value of the load in the load deflection diagram, the main body 210 cannot return to its original shape and remains in a deformed state. It becomes. Therefore, when the disc spring 200 is used as a spring for downward movement, the spring constant can be set to a low value, but since the selection of H / t according to the load is limited, the spring constant is It cannot be adjusted accordingly. On the other hand, it is possible to adjust H / t appropriately by limiting the maximum load so that the change in the absolute value of the load P does not turn to decrease. In this case, the low spring constant is the high load region. Limited to.

  Therefore, according to the present invention, it is possible to appropriately select at least one of the upward movement and the downward movement as well as the axial constant / axial spring constant ratio can be selected. It aims at providing the spring which can adjust the spring constant in an application to a low value suitably.

  The spring of the present invention has an inner peripheral part and an outer peripheral part, and is provided in a body part that can be elastically deformed, and an inner peripheral part and an outer peripheral part of the main body part, and is fixed to respective mating members of the inner peripheral part and the outer peripheral part. The main body portion has a convex shape with respect to a straight line connecting the inner peripheral portion and the outer peripheral portion at the central portion between the inner peripheral portion and the outer peripheral portion in the axial cross section. Is characterized by having a curved shape.

  In the spring of the present invention, when a double swing load is applied to the spring, for example, one flange portion moves upward or downward according to the movement of the mating member. Here, in the spring of the present invention, the main body portion has a convex shape with respect to a straight line connecting the inner peripheral portion and the outer peripheral portion at the central portion between the inner peripheral portion and the outer peripheral portion in the axial cross section. The shape has a curved shape.

  Therefore, when one flange portion moves upward (when moving upward), the main body portion having the above shape is appropriately elastically deformed, so that the peripheral portion (inner peripheral portion or outer peripheral portion) on the one flange portion side of the main body portion. ) Can move upward in response to the upward movement of one of the flange portions. Such deformation of the spring is a tension mode in which tension is applied in the radial direction in the main body. Moreover, when one flange part moves downward (at the time of a downward movement), the main-body part which makes the said shape can be elastically deformed suitably, and can move below according to the downward movement of one flange part. In such a spring deformation, the main body portion is in a tension mode in which tension is applied in the radial direction.

  In this way, when a double swinging load is applied, the spring can exhibit a similar deformation mode called a tensile mode both when the one flange portion moves upward and when it moves downward. Therefore, since the compression mode does not occur during the downward movement, H / t can be selected according to the load, and the spring constant can be adjusted unlike the downward movement of the disc spring.

  Here, in the spring of the present invention, the main body portion having the curved convex shape as described above has a central portion between the inner peripheral portion and the outer peripheral portion along a straight line connecting the inner peripheral portion and the outer peripheral portion. Unlike the disc springs that are formed, bending deformation can be performed in the tension mode during upward movement and downward movement. Therefore, both the upward movement and the downward movement are easily elastically deformed, and the spring constant can be set low. In this case, the spring constant can be set substantially constant without depending on the load direction or the magnitude of the load. Furthermore, since the stress at the same load can be set equal to or less than that of the disc spring, it can have fatigue durability equal to or more than that of the disc spring. Thus, at least one of the use for upward movement and the downward movement can be appropriately selected, and the spring constant in the selected use can be appropriately adjusted to a low value. In addition, the spring constant ratio in the vertical direction / axial direction can be increased.

  Various configurations can be used for the spring of the present invention. For example, a cylindrical part is provided in the inner peripheral part and the outer peripheral part, the cylindrical part protrudes in a direction opposite to the convex protruding direction of the main body part, and the flange part passes through the cylindrical part and the inner peripheral part and the outer peripheral part. The aspect provided in the part can be used.

  In the above aspect, the main body portion can be fixed to the inner peripheral portion side and the outer peripheral portion counterpart member via the inner peripheral portion side and the outer peripheral portion side cylindrical portions, so that the inner peripheral portion side and the outer peripheral portion The attachment position to the mating member can be adjusted by appropriately setting the height of at least one cylindrical portion on the side. Moreover, when one flange part moves upward or downward, the main body part can be elastically deformed, and the boundary part between the main body part and the cylindrical part and the cylindrical part can be elastically deformed. Therefore, the spring constant can be set further lower.

  The main body can have various curved shapes. In this case, the optimum shape can be set according to the application of the spring. In the present application, regarding the description of the shape of the main body, in the axial cross section of the main body, a coordinate system using the axial direction as the vertical axis and the radial direction as the horizontal axis is set, and the positive direction of the vertical axis is the axis. Set to the upper direction of the direction, the positive direction of the horizontal axis is set to the direction from the inner end to the outer end in the radial direction, the gradient of the shape of the main body part in the axial cross section in each of the convex contour lines of the main body part The case where the inclination of the tangent line at the position is set and the shape of the main body is set to be convex downward is used.

  For example, when the spring of the present invention is used as a spring for moving (upward moving) the moving direction of the mating member on the inner peripheral side of the main body in the direction opposite to the convex protruding direction of the main body, the axial direction The gradient of the shape of the main body in the cross section monotonously increases from the inner peripheral edge toward the outer peripheral edge, the gradient of the shape of the inner peripheral edge of the main body is negative, and its absolute value is the shape of the outer peripheral edge of the main body. A location that is larger than the absolute value of the gradient and where the gradient of the shape of the main body portion is 0 can be used such that it is located closer to the inner peripheral end than the center position between the inner peripheral end and the outer peripheral end. In this embodiment, since the bending stress in the radial direction can be made uniform by making the bending moment in the radial direction uniform, the maximum stress among the stresses distributed in the main body portion should be set low. Can do. Therefore, as shown in FIG. 30, the spring constant at the time of upward movement can be appropriately adjusted to a low value.

  For example, when the spring of the present invention is used as a spring for moving (downward moving) the movement direction of the mating member on the inner peripheral side of the main body portion in the protruding direction of the shape of the main body portion, the main body portion in the axial cross section The gradient of the shape decreases from the inner peripheral end toward the outer peripheral end, turns to increase on the inner peripheral end side from the center position of the inner peripheral end and the outer peripheral end, and the shape gradient of the inner peripheral end of the main body portion becomes It is negative and its absolute value is larger than the absolute value of the gradient of the shape of the outer peripheral end of the main body, and the portion where the gradient of the shape of the main body is zero is located on the outer peripheral end side from the center position. Can be used. In this mode, since the bending moment in the circumferential direction can be made uniform by making the bending moment in the circumferential direction uniform, the maximum stress among the stresses distributed in the main body is set low. can do. Therefore, as shown in FIG. 30, the spring constant during the downward movement can be appropriately adjusted to a low value.

  For example, when the spring is used for both upward movement and downward movement, the gradient of the shape of the main body portion in the axial cross section monotonously increases from the inner peripheral end toward the outer peripheral end, and the gradient of the shape of the inner peripheral portion of the main body portion. Is negative, and its absolute value is larger than the absolute value of the gradient of the shape of the outer peripheral portion of the main body, and the portion where the gradient of the shape of the main body is zero is from the center position between the inner peripheral edge and the outer peripheral edge. Also, an aspect located on the outer peripheral end side can be used. In this aspect, since the larger bending moment of the absolute value of the bending moment in the radial direction and the circumferential direction in each part is made uniform, the maximum principal stress can be made uniform. The maximum stress among the distributed stresses can be set low. Therefore, as shown in FIG. 30, the spring constant can be appropriately adjusted to a low value at both the upward movement and the downward movement.

  Moreover, the aspect with the same position of the axial direction of an inner peripheral end and an outer peripheral end can be used. In this aspect, the spring constant can be set low even when the amount of deflection during upward movement or downward movement increases. Furthermore, for example, as the shape of the main body, an arc shape or an elliptical shape can be used. Further, the main body portion may have a linear shape formed in a part of the curved shape. The main body portion may have a plurality of linear shapes, and in this case, adjacent linear shape boundary portions may be curved, and may be substantially curved as a whole.

  According to the spring of the present invention, it is possible to appropriately select at least one use for upward movement and downward movement, and it is possible to appropriately adjust the spring constant in the selected use to a low value. Can be obtained.

The structure of the spring which concerns on one Embodiment of this invention is represented, (A) is a top view, (B) is an axial sectional view of a spring. 1A and 1B show an operation state of the right side portion of the spring shown in FIG. 1, in which FIG. 1A is a state when the spring is moved upward, and FIG. 2B is an axial sectional view showing a state when the spring is moved downward. It is an axial direction sectional view showing composition of a right part of an example of a spring concerning one embodiment of the present invention. FIG. 4 is a load deflection diagram obtained by changing the ratio of the height H to the plate thickness t (= H / t) in the example of the spring shown in FIG. 3 (first invention example). FIG. 5 is a diagram of a load, a maximum principal stress, and a spring constant with respect to a deflection amount when H / t is set to 6.3 in the first example of the present invention. FIG. 5 is a diagram of a load and a spring constant with respect to a deflection amount in a direction perpendicular to an axis when H / t is set to 6.3 in the first example of the present invention. It is an axial direction sectional view showing composition of a right part of a suitable example (example of the 2nd present invention) of a spring concerning one embodiment of the present invention. FIG. 8 is a load deflection diagram when H / t is set to 6.3 in the preferred example (second invention example) and the first invention example of the spring shown in FIG. 7. It is a diagram of the load with respect to the amount of deflection, maximum principal stress, and spring constant when H / t is set to 6.3 in the second example of the present invention. FIG. 6 is a diagram of a load, a maximum principal stress, and a spring constant with respect to a deflection amount when H / t is set to 5.5 in the first example of the present invention. The disk model used in order to obtain the suitable shape of the main-body part of the spring which concerns on one Embodiment of this invention is represented, (A) is a perspective view, (B) is a schematic side view. 12 is a graph showing an example of stress distribution on the upper surface side in the axial cross section obtained from the disc model shown in FIG. 11. 12 is a graph showing an example of a stress distribution on the lower surface side in an axial direction cross section obtained from the disc model shown in FIG. 11. It is the graph which showed the largest largest principal stress of the largest principal stress in the upper surface side and lower surface side of the disc obtained from the graph of FIG. It is a graph showing an example of the bending moment distribution in the axial direction cross section obtained based on the graph of FIG. It is a figure for demonstrating the suitable example (3rd example of this invention) of the shape of the main-body part of the spring for an upward movement which concerns on this embodiment. It is an axial direction sectional view showing the composition of the right side portion of the suitable example of the shape of the main-body part of the example of the 3rd present invention. It is a diagram of the load with respect to the amount of deflection, the maximum principal stress, and the spring constant when the second cylindrical portion is not provided in the shape of the third example of the present invention. In the third example of the present invention having no second cylindrical portion, the load with respect to the deflection amount of the first example of the present invention when the maximum principal stress is set equal to the maximum principal stress when a load of 1500 N is applied downward, the maximum principal It is a diagram of stress and spring constant. It is a figure for demonstrating the modification (modification of FIG. 16) of the example of 3rd this invention. It is a diagram of the load with respect to the amount of deflection, the maximum principal stress, and the spring constant of the modification of the third example of the present invention. It is a figure for demonstrating the suitable example (4th example of this invention) of the shape of the main-body part of the spring for a downward movement which concerns on this embodiment. It is an axial direction sectional view showing composition of a right part of a suitable example of a shape of a main part of the example of the 4th present invention. It is a diagram of the load with respect to the amount of deflection, the maximum principal stress, and the spring constant when the second cylindrical portion is not provided in the shape of the main body portion of the fourth invention example. It is a diagram of the load with respect to the amount of deflection, maximum principal stress, and spring constant when H / t is set to 9 in the fourth example of the present invention. It is a figure for demonstrating the suitable example (5th example of this invention) of the shape of the main-body part of the spring for both the upward movement and downward movement which concerns on this embodiment. It is an axial direction sectional view showing composition of a right part of a suitable example of shape of a main part of the example of the 5th present invention. It is a diagram of the load with respect to the amount of deflection, the maximum principal stress, and the spring constant when the second cylindrical portion is not provided in the shape of the fifth example of the present invention. 1 is an axial sectional view showing a schematic configuration of a suspension device that is an application example of a spring according to an embodiment of the present invention. It is a graph showing an example of the load deflection | distribution diagram of the spring for an upward movement which concerns on this invention, the spring for a downward movement, and the spring for both movements for an upward movement and a downward movement. The operation state of the right part of the disc spring is represented, (A) is a state before the operation, (B) is a state when the spring is moved upward, and (C) is an axial sectional view showing the state when the spring is moved downward. is there. FIG. 32 is a diagram of a load and a spring constant with respect to a deflection amount when H / t is set to 7 in the example (conventional example) of the disc spring shown in FIG. 31. It is a load deflection diagram obtained by changing H / t in the conventional example. It is a diagram of the load with respect to the amount of deflection, maximum principal stress, and spring constant when H / t is set to 1.5 in the conventional example.

(1) Configuration of Embodiment Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows a configuration of the spring 1, (A) is a top view of the spring 1, and (B) is an axial sectional view of the spring 1. 2 shows the operation state of the right side of the axis center of the spring 1 shown in FIG. 1, (A) shows the state when the spring 1 is moved upward, and (B) shows the state when the spring 1 is moved downward. It is an axial direction sectional view. The broken line part of FIG. 2 has shown the shape of the spring 1 before operation | movement.

  The spring 1 is made of spring steel or reinforcement plastic. For example, as shown in FIG. 1A, the spring 1 includes a main body 10 having an inner peripheral portion 10A and an outer peripheral portion 10B, and the inner peripheral portion 10A and the outer peripheral portion 10B have a circular shape. The shapes of the inner peripheral portion 10A and the outer peripheral portion 10B of the main body portion 10 are not limited to circular shapes, and may be elliptical shapes, for example. In this case, unlike the case where the shape of the outer peripheral portion of the main body 10 is a plate extending in the longitudinal direction, space saving can be achieved. You may form a slit in the main-body part 10, the following flange parts 11 and 12, and the following cylindrical parts 13 and 14. FIG. In this aspect, weight reduction can be achieved.

  The main body 10 extends, for example, in a direction that intersects the direction of the pressing force from the first member 111 and the second member 112. The main body 10 is a spring that can be elastically deformed. For example, as shown in FIG. 1B, the main body 10 has an axial cross section with respect to a straight line S connecting the inner periphery 10A and the outer periphery 10B at the center between the inner periphery 10A and the outer periphery 10B. And has a shape such that the convex shape is curved. For example, in the form shown in FIGS. 1 and 2, the protruding direction is a downward direction. The main body 10 can have, for example, an arc shape or an ellipse shape in the axial cross section.

  The inner peripheral portion 10A of the main body portion 10 has a first flange portion 11 that protrudes inward in the radial direction, for example. The outer peripheral part 10B of the main-body part 10 has the 2nd flange part 12 which protrudes toward the outer side of radial direction, for example. For example, the positions in the height direction of the inner peripheral end 10A and the outer peripheral end 10B of the main body 10 are the same. The first flange portion 11 is fixed to the first member 111 by using screw means or the like, and the second flange portion 12 is fixed to the second member 112 by using screw means or the like. For example, a hole 11 </ b> A for providing screw means is formed in the inner peripheral portion of the first flange portion 11. In addition, when using means other than the screw means (for example, welding), the hole 11A may not be provided. The protruding directions and shapes of the flange portions 11 and 12 are not limited to those shown in FIG. 1 and can be variously modified, and can be set as appropriate according to the mating member and the interference.

  The spring 1 can be formed by bending each part by press molding. Moreover, each part can be formed by welding.

(2) Operation | movement of embodiment Operation | movement of the spring 1 is demonstrated with reference to drawings. As shown in FIG. 1, the main body portion 10 of the spring 1 has an axial cross section with respect to a straight line S where the central portion between the inner peripheral portion 10A and the outer peripheral portion 10B connects the inner peripheral portion 10A and the outer peripheral portion 10B. Since the protrusion has a protruding shape and the protrusion has a curved shape, the spring 1 exhibits the following deformation modes when moving upward and downward.

  For example, as shown in FIG. 2A, when a load P that moves the first flange portion 11 upward is applied, the main body portion 10 having the above shape is appropriately elastically deformed, whereby the inner peripheral portion 10A of the main body portion 10 is obtained. Can move upward relative to the outer peripheral portion 10 </ b> B of the main body portion 10 as the first flange portion 11 moves upward. Such deformation of the spring 1 is a tensile mode in which tension is applied in the radial direction in the main body 10 as indicated by arrows in the figure.

  On the other hand, as shown in FIG. 2 (B), when a load P that causes the first flange portion 11 to move downward is applied, the main body portion 10 having the above shape is appropriately elastically deformed, whereby the inner peripheral portion of the main body portion 10. 10A can move downward relative to the outer peripheral portion 10B of the main body portion 10 as the first flange portion 11 moves downward. Such deformation of the spring 1 is a tensile mode in which tension is applied in the radial direction in the main body 10 as indicated by arrows in the figure.

  In this way, when the swinging load is applied, the spring 1 can exhibit a similar deformation mode called the tension mode when the first flange portion 11 is moved upward or downward. In addition, the body portion 10 having a curved convex shape as described above has a disc spring in which the central portion between the inner peripheral portion and the outer peripheral portion is formed along a straight line connecting the inner peripheral portion and the outer peripheral portion. Unlike the above, bending deformation can be performed in the tensile mode during upward movement and downward movement. Such a spring 1 can obtain the following characteristics, for example.

  FIG. 3 is an axial sectional view showing the configuration of the right side portion of an example of the spring 1 according to the embodiment of the present invention. In the example of the spring 1 shown in FIG. 3, the main body 10 has an arc shape having a constant curvature in the axial cross section. The height H of the arc shape is a distance from the center position of a straight line connecting the inner peripheral end 10A and the outer peripheral end 10B to the arc. FIG. 4 is a load deflection diagram obtained by changing the ratio (= H / t) of the height H to the plate thickness t in the example (first invention example) of the spring 1 shown in FIG. In addition, about the 1st example of this invention and the 2nd example of this invention, the inner and outer diameter of a main-body part and a flange part, plate | board thickness, and the other party member are the same as the said example (conventional example) of a disc spring.

  In the first example of the present invention, the spring constant can be changed by changing H / t as shown in FIG. Further, in this case, the relationship between the absolute value of the load and the amount of deflection is substantially linear in the upward movement and the downward movement, unlike the disc spring.

  FIG. 5 is a diagram of the load, the maximum principal stress, and the spring constant with respect to the deflection amount when H / t is set to 6.3 in the first example of the present invention. FIG. 34 is a diagram of the load, the maximum principal stress, and the spring constant with respect to the deflection amount when H / t is set to 1.5 in the conventional example. In this case, the inner and outer diameters, plate thicknesses, and mating members of the main body portion and the flange portion of the first invention example and the conventional example are the same as described above.

  In the conventional example, as shown in FIG. 33, the load characteristic on the compression side shows that when H / t exceeds about 1.5, the change in the absolute value of the load P is monotonously increased to decreased when the predetermined deflection amount is exceeded. And migrate. In this case, even if the load is removed after applying a load P larger than the peak of the absolute value of the load P, the main body 210 remains in a deformed state and does not return to its original shape. For this reason, in the conventional example, the upper limit value of H / t at which a high load can be applied and the spring constant can be set low is about 1.5. In this case, conventionally, as shown in FIG. 34, the spring constant can be set to 500 N / mm or less only in the load range of about the downward movement side 250N to the downward movement side 100N, and in the other ranges, the spring constant is set. Is expensive.

  On the other hand, in the first example of the present invention, as shown in FIG. 5, the spring constant becomes substantially constant regardless of the load direction and the load magnitude, and the spring constant is 500 N / mm at any load. A low spring constant can be set. In this case, in the first example of the present invention, unlike the disc spring 200 in which H / t capable of applying a high load and setting a low spring constant is limited to about 1.5, The range of / t can be set wide. Furthermore, the maximum principal stress at the same load is lower than that of the conventional example, and the fatigue durability is equal to or higher than that of the conventional example.

  FIG. 6 is a diagram of the load and the spring constant with respect to the deflection amount in the direction perpendicular to the axis when H / t is set to 6.3 in the first example of the present invention. As can be seen from FIGS. 5 and 6, in the first example of the present invention, the spring constant in the axis vertical direction can be set to a value that is 40 times or more higher than the spring constant in the axis direction. Therefore, in the first invention example, unlike the rubber member, the spring constant ratio in the axial vertical direction / axial direction can be increased.

  As described above, in the present embodiment, for example, in a usage pattern in which a heavy load is swung, the spring constant is set low by adjusting the ratio of the height H to the plate thickness t (= H / t). Can do. In particular, since the position in the height direction of the inner peripheral end 10A and the outer peripheral end 10B of the main body 10 is the same, the spring constant should be set low even when the amount of deflection during upward movement or downward movement increases. Can do. Further, unlike the rubber member, the spring constant ratio in the axis vertical direction / axis direction can be increased.

(3) Preferred example of embodiment (3-1) Example of providing a cylindrical portion The present invention is not limited to the above embodiment, and various modifications are possible. For example, as shown in FIG. 7, the first cylindrical portion 13 and the second cylindrical portion 14 can be provided on the inner peripheral portion 10 </ b> A and the outer peripheral portion 10 </ b> B of the main body portion 10. In this case, the cylindrical portions 13 and 14 can protrude in a direction opposite to the protruding protruding direction of the main body portion 10 (upward direction in FIG. 7). For example, the first flange portion 11 can be provided on the inner peripheral portion 10 </ b> A of the main body portion 10 via the first tubular portion 13. For example, the second flange portion 12 can be provided on the outer peripheral portion 10 </ b> B of the main body portion 10 via the second tubular portion 14. For example, the cylindrical portions 13 and 14 are cylindrical portions having the same height G. In this case, for example, since the position in the height direction of the inner peripheral end 10A and the outer peripheral end 10B of the main body portion 10 is the same, the main body side end portions 11C and 12D of the flange portions 11 and 12 (the upper ends of the cylindrical portions 13 and 14). The positions in the height direction of each other are set equal.

  In the above aspect, the main body 10 can be fixed to the inner member and the counterpart member on the outer peripheral part via the cylindrical parts 13 and 14 on the inner peripheral part side and the outer peripheral part side. The attachment position to the mating member can be adjusted by appropriately setting the height of at least one cylindrical portion on the side and the outer peripheral side. Moreover, the said aspect can acquire the following characteristics.

  FIG. 8 is a load deflection diagram when H / t is set to 6.3 in the modified example of the spring shown in FIG. 7 (second example of the present invention) and the first example of the present invention. The second example of the present invention has the same inner and outer diameters and plate thicknesses as the first example of the present invention, and H / t is also set to the same value as above.

  As can be seen from FIG. 8, the second example of the present invention having a cylindrical part has a lower absolute value of the load P and a lower spring constant than the first example of the present invention having no cylindrical part. In addition, about the 2nd example of the present invention which has a cylindrical part, when the separation distance from a main-body part becomes long, the part spaced apart from a main-body part among cylindrical parts will hardly change. Even if the height H of the cylindrical portion is increased, the effect is not substantially changed. For example, the load deflection characteristics when the height H is 10 mm, when the height H is 10 mm, and when the height H is 20 mm are substantially the same.

  FIG. 9 is a diagram of the load, maximum principal stress, and spring constant when H / t is set to 6.3 in the second example of the present invention. As can be seen from FIGS. 5 and 9, the second example of the present invention having a cylindrical part is the same as the first example of the present invention having no cylindrical part and the same H / t (= 6.3). In comparison, the spring constant is low. However, in this case, since the maximum principal stress corresponding to the load value is high and the fatigue durability is different, the second invention example cannot compare the performances of the two.

  FIG. 10 is a diagram of the load, the maximum principal stress, and the spring constant with respect to the deflection amount when H / t is set to 5.5 in the first example of the present invention. When H / t of the first example of the present invention having no cylindrical portion is set to 5.5 and the maximum principal stress corresponding to the load value is set to be the same as that of the second example of the present invention, from FIGS. As can be seen, the second example of the present invention having a cylindrical part can have a lower spring constant than the first example of the present invention having no cylindrical part. Thus, in the 2nd example of the present invention which has a cylindrical part, a spring constant can be set up lower than the 1st example of the present invention with the equivalent fatigue endurance.

(3-2) Preferred shape of main body (A) Example of acquisition method of preferred shape of main body (A-1) Determination method of gradient In this embodiment, the shape of main body 10 is appropriately set for upward movement. And at least one of the applications for the downward movement can be selected as appropriate. In this case, the spring constant is appropriately adjusted to a low value by adjusting the ratio of the height H to the thickness t (= H / t). can do.

  For example, the optimal curved shape of the main body 10 can be determined by using a bending moment distribution obtained using, for example, a disk model that undergoes axisymmetric bending. Specifically, the distribution M (r) of the bending moment with respect to the position r in the radial direction is acquired using a disc model, and a shape that cancels the distribution is selected. In this case, when the shape of the main body is expressed by setting the shape of the main body to an axisymmetric shape and setting the height h according to the position r in the radial direction from the central axis, the gradient dh / dr The height h (r) is obtained so that the absolute value of | dh / dr | is proportional to the absolute value | M | of the bending moment M. By using the height h (r) thus obtained, the shape of the main body 10 can be obtained.

The bending moment can be obtained by using a disc 300 (inner diameter D _in , outer diameter D _out ) as shown in FIGS. 11 (A) and 11 (B). In disc 300, the inner portion 300A than the inner diameter _{D in} is a rigid body, adding shear load as the load P to the center position of the inner portion 300A (the central position of the disc 300 (the axial center position)). The disc 300 has flange portions (not shown) on the inner peripheral portion and the outer peripheral portion, and uses support conditions that approximate the conditions for reproducing the load applied to the flange portion on the inner peripheral portion side. Then, the outer peripheral portion of the disc 300 is completely fixed so as not to be displaced, and the inner peripheral portion of the disc 300 is completely fixed except in a direction in which a shearing force is applied thereto. A polar coordinate system (r, θ, z) having an origin at the center position is set on such a disc 300. The disc 300 is bent by the load P, and stress is generated inside. Each component of the bending stress is obtained by obtaining each component of the bending moment as follows.

By using the disc bending theory of elasticity and the two-dimensional elasticity theory, the deflection angle φ in the disc 300 is expressed by the following mathematical formula 1. C ₁ and C ₂ are expressed by the mathematical expressions 5 and 6 by solving the simultaneous equations established from the mathematical expressions 3 and 4 in which the support conditions of the disc 300 are substituted into the mathematical expression ₁ .

なお、ｒは円板３００の原点からの距離、Ｐは荷重値、Ｄは、円板の曲げ剛性であって数２の数式で表される。

In addition, r is the distance from the origin of the disc 300, P is the load value, D is the bending rigidity of the disc, and is expressed by the mathematical formula 2.

なお、Ｅはヤング率、νはポアソン比である。

E is Young's modulus and ν is Poisson's ratio.

By using the 2-dimensional elastic theory, the bending of the radial represented by the number 7 in the formulas moment M _r and number 8 bending moment M _theta circumferential represented by formula is obtained. Dφ / dr in the mathematical expressions 7 and 8 is given by the mathematical expression 9 by differentiating the mathematical expression 1. The radial bending moment distribution necessary for determining the shape of the spring for upward movement is obtained by the equation (7). The bending moment distribution in the circumferential direction necessary for determining the shape of the spring for downward movement can be obtained by the mathematical formula (8). The gradient is determined such that its magnitude is proportional to the magnitude of the bending moment having such a distribution. Since the bending moment is proportional to the load P and the reciprocal 1 / D of the bending rigidity of the disc, the gradient distribution is determined by the inner diameter D _in and the outer diameter D _out regardless of the load P and the plate thickness t. The

The calculation of the moment distribution based on the idea of the maximum principal stress σmax necessary for determining the shape of the spring for both upward movement and downward movement will be described. With a circumferential bending moment M _theta represented by formula radial bending moment M _r and number 8, represented by the number 7 of the formula, the stress component of the top and bottom surfaces of the disc 300 sigma _r (Upper surface), σ _θ (upper surface), σ _r (lower surface), and σ _θ (lower surface) are given by mathematical expressions of several tens to thirteen. It can be seen that the stress component σ _r is proportional to the bending moment M _r in the radial direction, and the stress component σ _θ is proportional to the bending moment M _θ in the circumferential direction.

なお、Ａは板厚ｔによって決定されるパラメータ（＝６／ｔ^２）である。

A is a parameter (= 6 / t ² ) determined by the plate thickness t.

なお、Ａは、数１０の数式と同じパラメータである。

Note that A is the same parameter as the mathematical expression of Formula 10.

When a shear load is applied to the disc 300 as described above, the arbitrary maximum principal stress σmax in the axial section is expressed by the mathematical formula 14 and used as a fatigue strength parameter. Since stress component tau _R.theta 0 for axisymmetric, the maximum principal stress σmax is represented by equation number 15.

When the larger bending moment of any at the radius r of the radial bending moment M _r and circumferential bending moment M _theta and Mmax, Mmax is expressed by equation number 16. By using Mmax, the maximum principal stress σmax is expressed by the following mathematical formula (17). In this case, the maximum principal stress σmax is different between the upper surface side and the lower surface side of the disc 300. For example, when the load P is positive, the maximum principal stress σmax on the upper surface side has a distribution shown in FIG. 12, and the maximum principal stress σmax on the lower surface side has a distribution shown in FIG.

なお、Ａは、数１０の数式と同じパラメータである。

Note that A is the same parameter as the mathematical expression of Formula 10.

The larger maximum principal stress σmax ′ of the maximum principal stresses σmax on the upper surface side and the lower surface side is expressed by Equation (18). σmax ′ is obtained from the graphs shown in FIGS. 12 and 13 as shown in FIG. The bending moment distribution Mmax ′ corresponding to σmax ′ is obtained by adopting the larger moment of the absolute values of the bending moments in the radial direction and the circumferential direction as shown in the mathematical expression (19). Mmax ′ is obtained as shown in FIG. Focusing on the bending moment distribution Mmax ′, the gradient is determined such that the magnitude thereof is proportional to the absolute value of the bending moment Mmax ′ having the above distribution. Since the bending moment distribution Mmax ′ is expressed by | M _r | and | M _θ |, the gradient distribution is the inner diameter D _in , regardless of the load P and the plate thickness t, as in the case of M _r and M _θ. And the outer diameter _Dout .

(A-2) Method for determining height Since the shape of the main body of the spring is set to a convex shape, for example, downward, the slope changes once during the course from the inner end to the outer end of the main body. Thus, the sign is determined. In this case, when the sign changes at a position where the gradient becomes 0, the curve continuously changes. Therefore, when the slope is used as a spring for upward movement or a spring for downward movement, the mathematical formula 20 When the position is changed at a position r (= r ′) that satisfies the above and is used as a spring for both upward movement and downward movement, the gradient is always larger than 0, and therefore the number 21 at which the gradient is the smallest position is given. The position is changed at a position r (= r ′) satisfying the mathematical formula.

なお、Ｍは、上方移動用のばねの場合にはＭ_ｒ、下方移動用のばねの場合にはＭ_θである。

Note that M is M _{r in} the case of a spring for upward movement, and M _θ in the case of a spring for downward movement.

As described above, the bending moment M (M _r in the case of an upward movement spring, M _{θ in} the case of a downward movement spring, Mmax ′ in the case of both upward and downward movement springs) When the gradient is obtained on the basis of the shape to obtain the shape of the main body, the relationship between the gradient and the moment is expressed by the mathematical formula of Formula 22. On the other hand, the height position h is obtained by integrating the gradient, and is expressed by Equation 23. The height position h is obtained from the mathematical formulas of Formula 22 and Formula 23, and the height position h is represented by a position r on an arbitrary axial cross section as shown by the mathematical formula of Formula 24. At the time of designing the shape of the main body, h (r) can be adjusted (ie, the height H can be adjusted) by adjusting the proportionality constant α. Therefore, since H / t can be adjusted as appropriate, the spring constant can be adjusted according to the specifications of the spring. Note that the height H used for obtaining a suitable shape of the main body is, for example, the absolute value of the minimum value hmin of h (r) | hmin when the shape of the main body 10 is set to be convex downward. |, And hmin is expressed by the mathematical formula 25.

なお、αは、０より大きな任意の比例定数である。

Α is an arbitrary proportional constant larger than 0.

  In order to obtain the shape of the main body portion, a moment distribution Mmax ″ which is a modified example thereof may be used instead of the bending moment distribution Mmax ′. Since Mmax ′ is always larger than 0, when r = r ′. Mmax ′ is given in the entire range of r. The moment Mmax ”expressed by the mathematical formula 26 will be described. Since the gradient at the position where r = r ′ is 0, the main body is obtained by making the gradient proportional to the magnitude of the moment of the moment distribution Mmax ″. Changes continuously.

(B) Preferred shape example of main body portion With respect to a preferred shape example of the main body portion, for example, the inner and outer diameters, plate thicknesses, and mating members of the main body portion and the flange portion are the same as the above example (conventional example) of the disc spring. , Bending moment M obtained using a disk model subjected to axisymmetric bending (M _r for a spring for upward movement, M _θ for a spring for downward movement, and for upward and downward movement In the case of a dual-purpose spring, the distribution of Mmax ′) is obtained as shown in FIG. By using a curve created so that the magnitude of the gradient is proportional to the magnitude of the bending moment M having the distribution shown in FIG. 15, the optimum curved shape of the main body 10 can be obtained.

  An example of a preferred shape of the main body when using a spring for upward movement, a spring for downward movement, and a spring for both upward and downward movement will be described. In the present application, the symbol C indicates the center position between the inner peripheral end 10A and the outer peripheral end 10B of the main body portion 10, the reference symbol Q indicates a location where the sign of the shape of the main body portion 10 changes, and the reference symbol L Indicates data on the gradient of the inner peripheral end 10A of the shape of the main body 10, and symbol M indicates data on the gradient of the outer peripheral end 10B of the shape of the main body. In the following preferred shape examples of the main body portion, for example, by providing the second cylindrical portion 14 on the outer peripheral portion 10B of the main body portion 10, the inner peripheral end 10A of the main body portion 10 (the main body side end of the first flange portion 11). The position in the height direction of the main body side end portion 12D of the second flange portion 12 is set equal.

(B-1) When Using Spring for Moving Up FIG. 16 is a graph showing a preferred example (third invention example) of the shape of the main body 10 obtained. 16, the magnitude of the gradient, the height distribution when decided gradient distribution in proportion to the magnitude of the magnitude of the radial bending moment M _r with a distribution shown in FIG. 15. In the example shown in FIG. 16, H / t is set to 6.3, and the size and the mating member other than H / t are the same as the above example (conventional example) of the disc spring.

  With respect to the shape of the cross section in the axial direction of the main body 10, for example, as shown in FIGS. 16 and 17, when the shape of the main body 10 is convex downward, the gradient of the shape of the main body 10 in the cross section in the axial direction is It increases monotonously from the peripheral end 10A toward the outer peripheral end 10B, the gradient of the shape of the inner peripheral end 10A of the main body 10 is negative, and its absolute value is the absolute value of the gradient of the shape of the outer peripheral end 10B of the main body 10 The position Q at which the sign of the gradient of the shape of the main body 10 changes is located closer to the inner peripheral end 10A than the center position C. The characteristics of the main body 10 are the same even when the plate thickness, outer diameter, and inner diameter are changed.

In the third invention example, by a radial bending moment M _r uniformly, since it is possible to achieve uniform stress component sigma _r, the maximum and becomes the stress of the stress is distributed in the body portion Can be set low. Therefore, the spring constant during the upward movement can be appropriately adjusted to a low value.

  FIG. 18 is a diagram of a load, a maximum principal stress, and a spring constant with respect to a deflection amount when the second cylindrical portion is not provided in the shape of the third example of the present invention. In the third example of the present invention, as shown in FIG. 18, for example, the amount of deflection when the load P in the tensile direction is 1500 N is 4.2 mm, and when converted to an average spring constant in the range of 0 to 1500 N, it is about 360 N / mm. It is. In the first example of the present invention, even if H / t is adjusted as shown in FIG. 4, the amount of deflection cannot be set large, so the spring constant is high. The constant can be set low.

  FIG. 19 is a diagram of the load, the maximum principal stress, and the spring constant with respect to the deflection amount of the first example of the present invention. In this case, the maximum principal stress corresponding to the load value in the first example of the present invention is set to be the same as that of the third example of the present invention (example shown in FIG. 18) having no cylindrical portion. In the first example of the present invention in which the main body 10 has an arc shape, as shown in FIG. 19, for example, the deflection amount when a load of 1500 N is applied so as to move downward is 3.1 mm, and 0 to 1500 N in downward movement. It is about 480 N / mm when converted to an average spring constant in the range of. Therefore, the third invention example can set the spring constant lower than that of the first invention example. Thus, in the third invention example, the spring constant can be set lower than in the first invention example having the same fatigue durability.

(B-2) When Using Spring for Moving Down FIG. 22 is a graph showing a preferred example (fourth example of the present invention) of the shape of the main body 10 obtained. Figure 22 is a height distribution when the magnitude of the gradient gave the gradient distribution in proportion to the magnitude of the circumferential direction of the bending moment M _theta having a distribution shown in FIG. 15. In the example shown in FIG. 22, H / t is set to 6.3, and the size and mating member other than H / t are the same as the above-described example (conventional example) of the disc spring.

  Regarding the shape of the axial section of the main body 10, for example, when the shape of the main body 10 is set to be convex downward as shown in FIGS. 22 and 23, the gradient of the shape of the main body 10 in the axial section is The inner circumferential end 10A decreases from the inner circumferential end 10B toward the outer circumferential end 10B, starts to increase on the inner circumferential end 10A side with respect to the center position C, the gradient of the shape of the inner circumferential end 10A of the main body 10 is negative, and its absolute value is The position Q, which is larger than the absolute value of the gradient of the shape of the outer peripheral end 10B of the main body portion 10 and changes in the positive / negative of the gradient of the shape of the main body portion 10, is located closer to the outer peripheral end 10B than the center position C. The characteristics of the main body 10 are the same even when the plate thickness, outer diameter, and inner diameter are changed.

Stress in the third invention example, by setting the circumferential bending moment M _theta uniform, consisting of can be made uniform stress component sigma _theta, the largest among the stress is distributed in the body portion Can be set low. Therefore, the spring constant during the downward movement can be appropriately adjusted to a low value.

  FIG. 24 is a diagram of the load, the maximum principal stress, and the spring constant with respect to the deflection amount when the second cylindrical portion is not provided in the shape of the fourth example of the present invention. In the fourth example of the present invention, as shown in FIG. 24, for example, the amount of deflection when the load P during downward movement is 1000 N is -5 mm, and when converted to the average spring constant in the range of 0 to 1000 N during downward movement, 200 N / mm. In the first example of the present invention, even if H / t is adjusted as shown in FIG. 4, the amount of deflection cannot be set large, so the spring constant is high. The constant can be set low.

  FIG. 25 is a diagram of the load, the maximum principal stress, and the spring constant with respect to the deflection when H / t is set to 9 in the fourth example of the present invention. In the fourth example of the present invention, as shown in FIG. 25, for example, the amount of deflection when the load P in the compression direction is 1500 N is −4.81 mm. In the first example of the present invention in which the main body 10 has an arc shape, as shown in FIG. 19, for example, when the load P in the compression direction is 1500 N, the deflection amount is −3.5 mm, and the maximum principal stress is high. . Accordingly, the fourth example of the present invention has a lower maximum principal stress and a lower average spring constant than the first example of the present invention. Thus, in the fourth example of the present invention, the spring constant during the downward movement can be set lower than in the first example of the present invention having the same fatigue durability.

(B-3) When using springs for both upward movement and downward movement FIG. 26 is a graph showing a preferred example (fifth example of the present invention) of the shape of the main body 10 obtained. In FIG. 26, the gradient magnitude is a larger value of the radial bending moment magnitude | M _r | and the circumferential bending moment magnitude | M _θ | in the distribution shown in FIG. This is the height distribution when the gradient distribution is determined so as to be proportional to a certain moment Mmax ′. In the example shown in FIG. 26, H / t is set to 6.3, and the size and mating member other than H / t are the same as the above example (conventional example) of the disc spring.

  As for the shape of the cross section in the axial direction of the main body 10, for example, as shown in FIGS. 26 and 27, when the shape of the main body 10 is set downward and convex, the gradient of the shape of the main body 10 in the cross section in the axial direction is It increases monotonously from the peripheral end 10A toward the outer peripheral end 10B, the gradient of the shape of the inner peripheral end 10A of the main body 10 is negative, and its absolute value is the absolute value of the gradient of the shape of the outer peripheral end 10B of the main body 10 The position Q at which the gradient of the shape of the main body 10 becomes 0 is located on the outer peripheral end 10B side with respect to the center position C. The characteristics of the main body 10 are the same even when the plate thickness, outer diameter, and inner diameter are changed.

In the fifth example of the present invention, the moment Mmax ′ which is the larger one of the magnitude of the bending moment | M _r | in the radial direction and the magnitude of the bending moment | M _θ | in the circumferential direction is made uniform. Thus, the maximum principal stress σmax can be made uniform, so that the maximum stress among the stresses distributed in the main body can be set low. Therefore, the spring constant during upward movement and downward movement can be appropriately adjusted to a low value.

  FIG. 28 is a diagram of a load, a maximum principal stress, and a spring constant with respect to a deflection amount when the second cylindrical portion is not provided in the shape of the fifth example of the present invention. In the fifth example of the present invention, as shown in FIG. 28, when the load P during upward movement is 1500 N, for example, as shown in FIG. Indicates stress and deflection. In the fifth example of the present invention, as shown in FIG. 28, for example, when the load P during downward movement is 1500 N, the maximum principal stress is lower than that of the first example of the present invention shown in FIG. can do. As described above, in the fifth example of the present invention, the spring constant can be set lower than that of the first example of the present invention having the same or less fatigue durability at both the upward movement and the downward movement.

  In setting the preferred shape of the main body, the proportionality constant α in the mathematical formula 22 indicating the relationship between the gradient and the bending moment may be changed for each radial position of the axial cross section. For example, in the above-described embodiment, the shape of the main body 10 is set as an example of a preferable shape of the main body 10 when using a spring for upward movement, a spring for downward movement, and a spring for both upward movement and downward movement. In any example, the inner peripheral end 10A of the main body 10 is positioned higher than the outer peripheral end 10B when set in a convex shape downward. For example, the height direction of the inner peripheral end 10A and the outer peripheral end 10B May be adjusted by changing the proportionality constant α with a predetermined position in the radial direction as a boundary.

  18, 24, and 28 in which the constant of proportionality α is constant, the diagrams of the spring constant with respect to the deflection amount of the third example of the present invention, the fourth example of the present invention, and the fifth example of the present invention are all examples. As the amount of deflection during upward movement increases, the spring constant increases. In the shape in which the inner peripheral end 10A of the main body portion 10 is positioned above the outer peripheral end 10B in this way, the length of the substantially arc shape in the vicinity of the outer peripheral end 10B of the main body portion 10 in the axial cross section is short. If the amount of deflection increases during the upward movement shown in A), the main body 10 may be difficult to deform. Therefore, the spring constant may increase as the amount of deflection during upward movement increases.

Therefore, in the modification of the third invention example example shown in FIG. 20, the proportional constant gradient with respect to the radial direction of the bending moment, M _r, differently in the inner peripheral side and outer peripheral side of the positive and negative changes in position Q of the gradient By setting, the heights of the inner peripheral end 10A and the outer peripheral end 10B can be set equal. FIG. 21 is a diagram of the load, the maximum principal stress, and the spring constant with respect to the deflection amount of the modified example of the third example of the present invention (the modified example of FIG. 16 and the sixth example of the present invention). As can be seen from FIGS. 18 and 21, in the sixth example of the present invention, the spring constant when the deflection amount of the upward movement is larger than in the third example of the present invention can be lowered. As described above, in the sixth example of the present invention, the spring constant can be lowered even when the deflection amount during the upward movement is increased by setting the positions in the height direction of the inner peripheral end 10A and the outer peripheral end 10B to be equal. Can do.

(4) Application Example of Embodiment The spring 1 can be applied to the suspension device 50 shown in FIG. 29, for example. The suspension device 50 includes, for example, a shock absorber 60, a suspension spring 70, and the spring 1. The spring 1 also functions as an upper seat of the suspension device 50, for example.

  The shock absorber 60 includes a piston part 61 and a cylinder part 62. A valve (not shown) at the lower end of the piston part 61 slides on the inner surface of the cylinder part 62. The rod of the piston part 61 slides on a seal of a rod guide part (not shown) provided around the piston part 61. A flange portion 63 that receives the wheel side end portion of the suspension spring 70 is formed on the outer peripheral portion of the cylinder portion 62. The cylinder part 62 is filled with hydraulic oil or the like, and the buffering function is realized by the hydraulic oil or the like passing through the valve during sliding and generating resistance. The suspension spring 70 is provided between the flange portion 63 and the spring 1 and is, for example, a coil spring.

  In the spring 1, the first flange portion 11 is fixed by a fixing member 71 such as screw means provided in the hole portion 11A, and the second flange portion 12 is fixed to the vehicle body 120 by a fixing member 72 such as screw means. Is done. As the spring 1, depending on the required characteristics, it is possible to use a spring for upward movement, downward movement, or both upward and downward movement springs.

  When a load from the wheel side of the vehicle is input to the vehicle body through the shock absorber 60, the shock absorber 60 may not be able to follow such vibration when the load is vibration in a high frequency band or a fine amplitude region. . In this case, the spring 1 having a low axial spring constant can be deformed as shown in FIGS. 2A and 2B to absorb vibrations in the high frequency band and the fine amplitude region. . Therefore, even when stick-slip occurs in the shock absorber 60, the spring 1 can suppress load fluctuations, so that the ride comfort is improved.

  Moreover, in the spring 1, since the main-body part 10 functions as a disk spring part, the rigidity of directions other than the axial direction of the buffer 60 can be made high. Therefore, even when the vibration in the axial direction of the shock absorber 60 acts as a shear stress on the spring 1, the spring 1 does not bend in directions other than the axial direction. As a result, steering stability can be ensured.

  DESCRIPTION OF SYMBOLS 1 ... Spring, 10 ... Main-body part, 10A ... Inner peripheral part, inner peripheral end, 10B ... Outer peripheral part, outer peripheral end, 11 ... 1st flange part (flange part), 12 ... 2nd flange part (flange part), 13 ... 1st cylindrical part (cylindrical part), 14 ... 2nd cylindrical part (cylindrical part), 111 ... 1st member (mating member), 112 ... 2nd member (mating member)

Claims (6)

A body portion having an inner peripheral portion and an outer peripheral portion and capable of elastic deformation;
A flange portion provided on the inner peripheral portion and the outer peripheral portion of the main body portion, and fixed to each mating member of the inner peripheral portion and the outer peripheral portion;
In the cross section in the axial direction, the central portion between the inner peripheral portion and the outer peripheral portion has a convex shape with respect to a straight line connecting the inner peripheral portion and the outer peripheral portion, and the convex shape is a curve. A spring having a shape that forms a shape. A cylindrical part is provided in the inner peripheral part and the outer peripheral part,
The cylindrical portion protrudes in a direction opposite to the protruding direction of the main body portion,
The spring according to claim 1, wherein the flange portion is provided on the inner peripheral portion and the outer peripheral portion of the main body portion via the cylindrical portion. In the axial section of the main body, a coordinate system is set using the axial direction as the vertical axis and the radial direction as the horizontal axis, the positive direction of the vertical axis is set as the upper direction of the axial direction, and the positive axis of the horizontal axis is set. The direction is set to a direction from the inner end to the outer end in the radial direction, and the gradient of the shape of the main body in the axial cross section is defined as the tangential slope at each position in the convex contour of the main body. When the shape of the main body is set downward and convex,
The gradient of the shape of the main body portion monotonously increases from the inner peripheral end toward the outer peripheral end, the gradient of the shape of the inner peripheral end of the main body portion is negative, and the absolute value thereof is the main body portion. The location of the shape of the outer peripheral end is larger than the absolute value of the gradient, and the position where the slope of the shape of the main body portion changes is the inner peripheral end side from the center position of the inner peripheral end and the outer peripheral end. The spring according to claim 1, wherein the spring is located at In the axial section of the main body, a coordinate system is set using the axial direction as the vertical axis and the radial direction as the horizontal axis, the positive direction of the vertical axis is set as the upper direction of the axial direction, and the positive axis of the horizontal axis is set. The direction is set to a direction from the inner end to the outer end in the radial direction, and the gradient of the shape of the main body in the axial cross section is defined as the tangential slope at each position in the convex contour of the main body. When the shape of the main body is set downward and convex,
The gradient of the shape of the main body portion decreases from the inner peripheral end toward the outer peripheral end, and turns to increase on the inner peripheral end side with respect to the center position between the inner peripheral end and the outer peripheral end. The gradient of the shape of the inner peripheral end of the main body portion is negative, the absolute value thereof is larger than the absolute value of the gradient of the shape of the outer peripheral end of the main body portion, and the positive / negative of the gradient of the shape of the main body portion changes. 3. The spring according to claim 1, wherein the place to be located is located closer to the outer peripheral end than the center position. 4. In the axial section of the main body, a coordinate system is set using the axial direction as the vertical axis and the radial direction as the horizontal axis, the positive direction of the vertical axis is set as the upper direction of the axial direction, and the positive axis of the horizontal axis is set. The direction is set to a direction from the inner end to the outer end in the radial direction, and the gradient of the shape of the main body in the axial cross section is defined as the tangential slope at each position in the convex contour of the main body. When the shape of the main body is set downward and convex,
The gradient of the shape of the main body portion monotonously increases from the inner peripheral end toward the outer peripheral end, the gradient of the shape of the inner peripheral end of the main body portion is negative, and the absolute value thereof is the main body portion. The location where the slope of the shape of the main body portion changes more than the absolute value of the gradient of the shape of the outer peripheral end of the main body is located closer to the outer peripheral end than the center position of the inner peripheral end and the outer peripheral end. The spring according to claim 1 or 2, characterized by the above.   The spring according to any one of claims 1 to 5, wherein the axial end positions of the inner peripheral end and the outer peripheral end are the same.

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