JP2012002274A - Spring - Google Patents

Abstract

A spring capable of reducing vibration transmissibility even in a low frequency band near the resonance frequency of the system is provided.
A friction generating portion is formed in a main body portion of a spring. The friction generating part 21 protrudes toward the base 112, and a gap h is formed between the lower end part of the friction generating part 21 and the base 112. The spring 1 bends greatly in the low frequency band near the resonance frequency of the system unlike the high frequency band. For example, when the contact portion of the first cylindrical portion 11 moves a predetermined amount in the direction of the pressing force (when the spring 1 is bent by a predetermined amount), as shown in FIG. To touch. In the spring 1, the spring constant becomes discontinuous and large in a low frequency band near the resonance frequency of the system. Friction is generated by sliding of the friction generating portion 21 with respect to the base 112, and hysteresis loss is generated.
[Selection] Figure 1

Description

  The present invention relates to a spring that suppresses transmission of high-frequency vibration from a mating member, and more particularly to improvement of the shape of the spring.

  In various fields such as the automobile industry, precision equipment industry, home appliances, and architecture, a technology for suppressing vibration transmission is required. Vibration transmission suppression technology is applied to engines, motors rotating at high speeds, washing machine dewatering tanks, buildings, and the like. As a technique for suppressing vibration transmission, it is effective to set the resonance frequency of a system constituted by an object and a support part to be sufficiently lower than a predetermined frequency band. As a technique, it is conceivable to reduce the spring constant of the support part. In this case, when a coil spring or a leaf spring is used as the support part, if the spring constant is reduced, a large deflection is required to support a high load. Is required, and the spring becomes large.

  Therefore, a method using a disc spring between the object and the support has been proposed (for example, Patent Documents 1 and 2). Since the load characteristic of the disc spring can be designed as a curve shown in FIG. 7, it is possible to set a substantially flat region A that can support a high load and set a small spring constant.

  When the disc spring is deformed so as to have a substantially flat shape when a load is applied, the inner peripheral edge and the outer peripheral edge of the disc spring slide against the mating member to generate friction. For this reason, when the use range of the disc spring is set to the range of the substantially flat region A in FIG. 7, the hysteresis shown in FIG. 8A is generated in the actual load curve. As a result, the substantial dynamic spring constant in the usage range of the disc spring is the inclination of the diagonal line l connecting the point P and the point Q in FIG. In this case, when the amplitude of the use range is reduced, the slope of the diagonal line l increases as shown in FIG. 8B, and the dynamic spring constant increases. In a system to which a disc spring is applied in this way, when a small amplitude vibration such as a high frequency vibration is input, the dynamic spring constant of the disc spring increases, so that the resonance frequency of the system increases, resulting in a high frequency vibration. There was a problem that it was not possible to suppress the transmission.

  In order to solve the above problems, the present applicant has proposed a spring 200 shown in FIG. 9 (for example, Patent Document 3). 9A and 9B show the configuration of the spring 200, where FIG. 9A is a perspective view and FIG. 9B is a cross-sectional view of the right side portion of the spring 200. FIG. 8B shows a state in which the spring 200 arranged on the base 112 (mating member) supports the object 111 (mating member). The spring 200 includes a main body 210 having a hole 210A formed at the center. The main body 210 has the same shape as a disc spring and has a function as a disc spring.

  A first cylindrical portion 211 protruding toward the object 111 is provided on the inner peripheral portion of the main body portion 210, and a second cylindrical portion protruding toward the base 112 is provided on the outer peripheral portion of the main body portion 210. 212 is provided. A first corner 213 is formed at the boundary between the main body 210 and the first cylindrical portion 211, and a second corner 214 is formed at the boundary between the main body 210 and the second cylindrical portion 212. Yes.

  In the spring 200, the corner portions 213 and 214 can be elastically deformed so as to change the angle according to the pressing force from the counterpart members 111 and 112 when a load is applied. In this case, the lengths of the cylindrical portions 211 and 212 are set so that the portions on the counterpart members 111 and 112 side of the cylindrical portions 211 and 212 are non-deformable portions. As a result, the spring 200 can prevent the cylindrical portions 211 and 212 from sliding with respect to the mating members 111 and 112, so that no hysteresis occurs in the load characteristics of the spring 200. Therefore, the spring 200 can support a high load and reduce the dynamic spring constant. As a result, the resonance frequency of the system can be lowered, and the vibration transmissibility of high-frequency vibration can be reduced.

JP-A-5-172171 JP 2002-54685 A JP 2009-275738 A

  However, in the spring 200, since the resonance frequency of the system is set low, there is a possibility that the transmission rate of vibration is increased in a low frequency band near the resonance frequency of the system. As a result, there is a limit in reducing the amplitude of the object in the low frequency band near the resonance frequency of the system. Therefore, a more suitable spring is desired in order to reduce the vibration transmissibility even in a low frequency band near the resonance frequency of the system.

  Accordingly, an object of the present invention is to provide a spring capable of reducing the vibration transmissibility even in a low frequency band near the resonance frequency of the system.

  The spring of the present invention includes a main body portion having a hole, a cylindrical portion provided on an inner peripheral portion and an outer peripheral portion of the main body portion, and a corner portion formed at a boundary portion between the main body portion and the cylindrical portion. The cylindrical portion has an abutting portion that protrudes from the inner circumferential portion and the outer circumferential portion toward the mating member and abuts against the mating member, and the corner portion has a pressing force at which the angle is applied from the mating member. The main body is formed with a friction generating portion that protrudes toward one of the mating members, and in an initial state, between the friction generating portion and one of the mating members. A predetermined gap is provided, and when the abutting portion of the cylindrical portion moves a predetermined amount in the direction of the pressing force, the friction generating portion contacts one of the mating members.

  In the spring of the present invention, the corner portion can be elastically deformed when a load is applied. Therefore, by appropriately setting the distance between the corner portion of the cylindrical portion and the mating member, the mating member of the cylindrical portion when the load is applied. The deformation | transformation of the site | part of the vicinity can be prevented. Therefore, a high load can be supported and the dynamic spring constant can be reduced. As a result, the resonance frequency of the system can be lowered, and the vibration transmissibility of high-frequency vibration can be reduced.

  Thus, in the spring of the present invention, the above effect can be obtained in a high frequency band as in the spring 200 of the comparative example. Here, in the spring of the present invention, since the friction generating portion protruding toward one of the mating members is formed in the main body portion, the following effects can be obtained in a low frequency band near the resonance frequency of the system. it can.

  That is, in the spring of the present invention, unlike the case of the high frequency band, in the low frequency band near the resonance frequency of the system, it bends greatly. When it moves a predetermined amount (when the spring is bent by a predetermined amount), it can contact one of the mating members. In this case, since the spring constant becomes discontinuous and large, it is possible to prevent the resonance phenomenon of the system composed of the counterpart member as the object and the spring as the support portion, and as a result, suppress the increase in the amplitude of the object. be able to. In addition, since the amount of energy absorbed by the spring per unit deflection increases, the amplitude can be reduced. Furthermore, friction is generated by sliding the friction generating portion with respect to one of the mating members, and hysteresis loss is generated. Therefore, vibration energy can be consumed, and as a result, the amplitude can be further reduced.

  From the above, in the spring of the present invention, the vibration transmissibility can be reduced even in a low frequency band near the resonance frequency of the system.

  Various configurations can be used for the spring of the present invention. For example, a mode in which a slit is formed in the main body portion and the friction generating portion is formed by being bent from an end portion of the slit can be used. In this aspect, formation of a friction generating part becomes easy.

  The friction generating part is formed at the end of the cylindrical part on the inner peripheral side of the main body part, and the protruding direction of the friction generating part is opposite to the protruding direction of the cylindrical part on the inner peripheral part side. And the aspect which is the direction which goes to an outer peripheral part side can be used. The friction generating part is formed at the end of the cylindrical part on the outer peripheral side of the main body part, and the protruding direction of the friction generating part is opposite to the protruding direction of the cylindrical part on the outer peripheral part side, and the inner peripheral part An aspect that is a direction toward the side can be used. In these aspects, since the friction generating part is formed at the end of the cylindrical part on the main body part side, the movement amount until the friction generating part comes into contact with the opposite partner member and the movement amount of the contact part of the cylindrical part. (The amount of spring deflection) becomes equivalent, and as a result, the design of the spring becomes easy. Further, since the friction generating portion can be arranged to be inclined with respect to one of the mating members, the friction generating portion can smoothly slide with respect to one of the mating members.

  According to the spring of the present invention, the vibration transmissibility can be reduced not only in the high frequency band of the system, but also in the low frequency band near the resonance frequency of the system.

The structure of the spring which concerns on one Embodiment of this invention is represented, (A) is a perspective view, (B) is a sectional side view of the spring in the state arrange | positioned between members. 1 shows a state before contact of the friction generating portion with the mating member at the time of operation of the right side portion of the spring shown in FIG. 1, and (A) is a sectional side view before operation of the spring (dotted line) and at the time of operation (solid line). (B) is an enlarged side sectional view of the first corner and the second corner during the operation of the spring. It is a sectional side view showing the state after the contact of the friction generation part to the other member at the time of operation | movement of the right side part of the spring shown in FIG. (A), (B) represents the actual machine evaluation result of the load characteristic of the spring of this invention example, and the spring of a comparative example, (B) is an enlarged view of the part shown by the inside X of the broken line of (A). . It is a graph showing the actual machine evaluation result of the frequency response characteristic of the spring of this invention example, and the spring of a comparative example. It is a sectional side view of the spring in the state which represents the structure of the modification of the spring which concerns on one Embodiment of this invention, and has arrange | positioned between members. It is a graph showing the load characteristic of a disc spring. It is a graph showing the load characteristic of the actual disk spring which a hysteresis produces, (A) When the amplitude of a use range is a predetermined magnitude | size, (B) The graph when the amplitude of a use range is smaller than the case of (A) It is. The structure of the spring of a comparative example is represented, (A) is a perspective view, (B) is a sectional side view of the right part.

(1) Configuration of Embodiment Hereinafter, an embodiment of the present invention will be described with reference to the drawings. 1A and 1B show a configuration of the spring 1, in which FIG. 1A is a perspective view of the spring 1, and FIG. 1B is a side sectional view of a right portion of the spring 1 disposed between an object 111 and a base 112. .

  The spring 1 is made of, for example, spring steel or reinforcing material plastic. The spring 1 includes, for example, a main body 10 having a hole 10A formed at the center. The main body 10 is a disc spring portion that extends in a direction intersecting with the direction of the pressing force from the object 111 and the base 112 and has a function as a disc spring, for example. The main body 10 has, for example, a substantially conical shape that is inclined downward. The spring 1 is non-linear so that its load characteristic has a substantially flat region A, similar to the characteristic of the disc spring shown in FIG.

  The hole 10A has, for example, a circular shape. A first cylindrical portion 11 (cylindrical portion) that protrudes toward the object 111 is provided on the inner peripheral portion of the main body portion 10. The upper end portion of the first cylindrical portion 11 is a contact portion that contacts the object 111. A second cylindrical portion 12 (cylindrical portion) that protrudes toward the base 112 is provided on the outer peripheral portion of the main body portion 10. The lower end portion of the second cylindrical portion 12 is a contact portion that contacts the object 112. The cylindrical parts 11 and 12 are cylindrical parts, for example.

  The main body 10 is formed with a plurality of (for example, four) slits 10B around the hole 10A, and the friction generating portion 21 is bent from the end of the slit 10B. The friction generating part 21 has a rectangular plate shape, for example. The friction generating part 21 protrudes toward the base 112, and a gap h is formed between the lower end part of the friction generating part 21 and the base 112. The friction generating part 21 contacts the base 112 when the contact part of the first cylindrical part 11 moves downward by a predetermined amount.

  When the friction generating unit 21 comes into contact with the base 112, the friction generating unit 21 rotates around the lower end portion of the first cylindrical portion 11 according to the pressing force from the object 111, and the friction generating unit 21 and the main body unit 10 are rotated. It can be elastically deformed so that the angle formed is small. The friction generating part 21 is preferably formed, for example, in the vicinity of the boundary part between the first cylindrical part 11 and the main body part 10 and formed at the lower end part of the first cylindrical part 11. Moreover, it is preferable that the protrusion direction of the friction generating part 21 is a direction toward the outer peripheral part side of the main body part 10.

  A first corner 13 is formed at the boundary between the main body 10 and the first cylindrical portion 11, and a second corner 14 is formed at the boundary between the main body 10 and the second cylindrical portion 12. Yes. The first corner portion 13 and the second corner portion 14 can be elastically deformed so as to change the angle according to the pressing force from the object 111 and the base 112.

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

(2) Function of cylindrical part The function of the cylindrical parts 11 and 12 at the time of applying a load will be described mainly with reference to FIG. FIG. 2 shows an operating state of one spring 1 installed between the object 111 and the base 112, and (A) shows a side cross section before the operation of the spring 1 (dotted line) and during operation (solid line). FIG. 4B is an enlarged side cross-sectional view of the first corner portion 13 and the second corner portion 14 during the operation of the spring 1. 2 is a side sectional view of a portion not including the slit 10B and the friction generating portion 21, and FIG. 2 shows a state before the friction generating portion contacts the object 111 when the spring 1 operates. ing. In FIG. 2, only the right side portion of the spring 1 is shown in the same manner as in FIG.

  As shown by a dotted line in FIG. 2A, a downward load is applied from the object 111 to the spring 1 disposed between the object 111 and the base 112. Then, as shown by the solid line in FIG. 2B, the spring 1 is bent and the object 111 moves downward. The symbol d in the figure indicates the amount of deflection of the spring 1.

  The main body portion 10 extends in a direction crossing the direction of the pressing force from the object 111, and on the upper side of the spring 1, the first cylindrical portion 11 is directed from the inner peripheral portion of the main body portion 10 toward the object 111. Protrudes and abuts there. The first corner portion 13 formed at the boundary between the main body portion 10 and the first cylindrical portion 11 is elastically deformed so that the angle α changes according to the pressing force from the object 111 when a load is applied. Can do. In this case, since the first corner portion 13 is a portion formed at the boundary portion between the main body portion 10 and the first cylindrical portion 11 having the above positional relationship, such first corner portion 13 is It is possible to move to the inside (left side in the figure) of the inner periphery of the main body 10 while changing the angle α when applying a load.

  Since the first corner portion 13 can be elastically deformed when a load is applied in this way, the first cylindrical portion 11 is not deformed on the object 111 side when a load is applied (above the point S in FIG. 2B). The length of the first cylindrical portion 11 is appropriately set so as to have the above-mentioned), so that deformation of the portion of the first cylindrical portion 11 on the object 111 side can be prevented.

  On the other hand, on the lower side of the spring 1, the second cylindrical portion 11 protrudes from the inner peripheral portion of the main body portion 10 toward the base 112 and is in contact therewith. In this case, the second corner portion 14 having the same function as the first corner portion 13 changes the angle β according to the pressing force from the base 112 during elastic deformation by applying a load while changing the angle β. It can move to the outside of the outer periphery (right side of the figure).

  Since the second corner portion 14 can be elastically deformed when a load is applied in this way, the second cylindrical portion 12 is not deformed on the base 112 side when the load is applied (below the point T in FIG. 2B). By appropriately setting the length of the second cylindrical portion 12 so as to have the side), deformation of the portion of the second cylindrical portion 12 on the base 112 side can be prevented.

  As described above, since the spring 1 has the non-deformable portions in the cylindrical portions 11 and 12, it is possible to prevent the spring 1 and the counterpart member from sliding. As a result, in the load characteristics of the spring 1, the hysteresis that has been a problem with the disc spring does not occur.

(3) Operation | movement of embodiment Operation | movement of the spring 1 is demonstrated with reference to drawings. In the load characteristics of the spring 1, no hysteresis is generated as described above. Therefore, the spring 1 can support a high load and reduce the dynamic spring constant. As a result, the resonance frequency of the system can be lowered, and the vibration transmissibility of high-frequency vibration can be reduced. Thus, the spring 1 can obtain the above-described effect in a high frequency band as in the spring 200 of the comparative example.

  Here, in the spring 1, since the friction generating part 21 protruding toward the base 112 is formed in the main body part 10, the following effects can be obtained in a low frequency band near the resonance frequency of the system. .

  The spring 1 bends greatly in the low frequency band near the resonance frequency of the system unlike the high frequency band. For example, when the contact portion of the first cylindrical portion 11 moves a predetermined amount in the direction of the pressing force (when the spring 1 is bent by a predetermined amount), as shown in FIG. Can contact. The friction generating portion 21 can rotate around the lower end portion of the first cylindrical portion 11 according to the pressing force from the object 111 at the time of contact, and the angle formed by the friction generating portion 21 and the main body portion 10. Becomes smaller. In this way, the friction generating part 21 can slide with respect to the base 112.

  In the spring 1, the spring constant is discontinuously increased in the low frequency band near the resonance frequency of the system due to the above-described action of the friction generating portion 21, so that the spring 1 includes the base 112 as an object and the spring 1 as a support portion. The resonance phenomenon of the system can be prevented, and as a result, an increase in the amplitude of the base 112 can be suppressed. In addition, since the amount of energy absorbed by the spring per unit deflection increases, the amplitude can be reduced. Further, since friction is generated by sliding the friction generating portion 21 with respect to the base 112 and hysteresis loss is generated, vibration energy can be consumed, and as a result, the amplitude can be further reduced.

  FIG. 4 shows actual machine evaluation results of load characteristics of a specific example (invention example) of the spring 1 of the present invention and a specific example (comparative example) of the spring 200 of the comparative example, and (B) is a frame of a broken line in (A). It is an enlarged view of the part shown by inner X. FIG. 5 is a graph showing actual machine evaluation results of frequency response characteristics of the spring of the present invention and the spring of the comparative example.

  Regarding the spring of the present invention and the spring of the comparative example, the plate thickness is 0.4 mm, the height of the main body is 3.17 mm, the inner diameter of the main body (the diameter of the opening of the first cylindrical portion) is 13 mm, the main body The outer diameter (diameter of the opening of the second cylindrical portion) was set to 47 mm, and the height of the second cylindrical portion was set to 5.2 mm. About the specific example of the spring 1, the space | interval h of the clearance gap between the lower end part of a friction generation part and a base was set to 0.8 mm.

  As can be seen from FIG. 4, in the spring of the present invention having the friction generating portion, when the friction generating portion is not in contact with the base, the load having a very small hysteresis is the same as the spring of the comparative example having no friction generating portion. Although the characteristics are shown, it was confirmed that when the friction generating portion is in contact with the base, the spring constant is increased and the hysteresis is increased, unlike the spring of the comparative example. In this case, as can be seen from FIG. 5, it was confirmed that the vibration transfer rate can be reduced in the low frequency band near the resonance frequency of the system in the spring of the present invention as compared with the spring of the comparative example.

  As described above, in the present embodiment, the vibration transmissibility can be reduced not only in the high frequency band of the system but also in the low frequency band near the resonance frequency of the system.

  In particular, since the first cylindrical portion 11 can be provided on the inner peripheral portion of the main body portion 10, the amount of movement until the friction generating portion 21 contacts the base 112 and the contact portion of the first cylindrical portion 11. The amount of movement (the amount of deflection of the spring) becomes equal, and as a result, the design of the spring 1 is facilitated. Further, since the protruding direction of the friction generating part 21 can be set to the direction toward the outer peripheral part, the friction generating part 21 can be arranged to be inclined with respect to the base 112, and the contact with the base 112 at the time of contact. Sliding can be performed smoothly. Moreover, since the slit 10B is formed in the main-body part 10, and the friction generation part 21 is bent from the edge part of the slit 10B, formation of the friction generation part 21 becomes easy. Further, since the friction generating part 21 can be arranged to be inclined with respect to the base 112, the friction generating part 21 can smoothly slide on the base 112.

(3) Modifications As described above, the present invention has been described with reference to the above embodiment. However, the present invention is not limited to the above embodiment, and various modifications can be made. In the following modification, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  For example, in the above embodiment, the friction generating part 21 is formed at the lower end of the first cylindrical part 11, but as shown in FIG. 6, the friction generating part 22 is a boundary between the second cylindrical part 12 and the main body part 10. It may be formed in the vicinity of the portion, and in this case, it is preferably formed at the upper end portion of the second cylindrical portion 12. In this case, the friction generator 22 protrudes toward the object 111, and a gap h is formed between the upper end of the friction generator 22 and the object 111. The friction generating part 22 contacts the object 111 when the contact part of the first cylindrical part 11 moves downward by a predetermined amount. It is preferable to form the slit 10B in the main body 10 and bend the friction generating portion 22 from the end of the slit 10B. Moreover, it is preferable that the protruding direction of the friction generating part 22 is a direction toward the inner peripheral part side of the main body part 10. The friction generating unit 22 can exhibit the same action as the friction generating unit 21.

  The formation position of the friction generating portions 21 and 22 is set at the end portion of the cylindrical portion (the inner peripheral portion or the outer peripheral portion of the main body portion 10), but is not limited to this. You may set to the arbitrary positions of the upper surface of 10 or a lower surface. Moreover, you may set the protrusion direction of a friction generation part to the direction opposite to the direction which goes to the peripheral part different from the peripheral part in which it was provided. The number of friction generating portions may be two or more.

  The main body 10 can have, for example, a conical shape, an S shape, a step shape, or a flat shape that is inclined downward from the outer peripheral portion toward the inner peripheral portion. The cylindrical portion may be cylindrical, and the cross-sectional shape thereof may be a polygon, and the side cross-sectional shape thereof may be a curved shape.

  In the above embodiment, the first cylindrical portion 11 is protruded toward the object 111 and brought into contact therewith, and the second cylindrical portion 12 is brought into contact with the base 112. 11 may be projected toward the base 112 and brought into contact therewith, and the second cylindrical portion 12 may be projected toward the object 11 and brought into contact therewith. Further, the shapes of the first corner portion 13 and the second corner portion 14 are not limited to the illustrated shapes, and can be changed to various shapes such as a curved surface shape.

  Moreover, although the 1st cylindrical part 11 and the 2nd cylindrical part 12 were formed in the inner peripheral part and outer peripheral part of the main-body part 10, it is only in any one of the 1st cylindrical part 11 and the 2nd cylindrical part 12. It may be formed. You may fix the contact part of the 1st cylindrical part 11 and the 2nd cylindrical part 12 to a counterpart member using various fixing means.

  DESCRIPTION OF SYMBOLS 1 ... Spring, 10 ... Main-body part, 10A ... Hole part, 10B ... Slit, 11 ... 1st cylindrical part (cylindrical part), 12 ... 2nd cylindrical part (cylindrical part), 13 ... 1st corner | angular part (Corner part), 14 ... second corner part (corner part), 21, 22 ... friction generating part, 111 ... object (mating member), 112 ... base (mating member)

Claims (4)

A main body having a hole;
A cylindrical portion provided on an inner peripheral portion and an outer peripheral portion of the main body portion;
A corner portion formed at a boundary portion between the main body portion and the cylindrical portion;
The cylindrical portion has a contact portion that protrudes from the inner peripheral portion and the outer peripheral portion toward the respective mating member and comes into contact therewith,
The corner portion is elastically deformable so that the angle changes according to the pressing force applied from the counterpart member,
A friction generating portion that protrudes toward one of the counterpart members is formed in the main body portion,
In an initial state, a predetermined gap is provided between the friction generating portion and one of the mating members,
The spring according to claim 1, wherein when the abutting portion of the cylindrical portion moves a predetermined amount in the direction of the pressing force, the friction generating portion contacts one of the mating members. A slit is formed in the main body,
The spring according to claim 1, wherein the friction generating portion is formed by being bent from an end portion of the slit. The friction generating part is formed at an end of the cylindrical part on the inner peripheral side of the main body part,
The protruding direction of the friction generating part is a direction opposite to a protruding direction of the cylindrical part on the inner peripheral part side, and a direction toward the outer peripheral part side. Spring. The friction generating part is formed at an end of the cylindrical part on the outer peripheral part side of the main body part,
The protruding direction of the friction generating portion is a direction opposite to a protruding direction of the cylindrical portion on the outer peripheral portion side and a direction toward the inner peripheral portion side. Spring.

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