JP2012246939A - Vibration isolation mount, and spring constant adjustment method - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration isolation mount which uses nonlinear springs and yet obtains a stable spring constant irrespective of a value of a load to be vibration-isolated.SOLUTION: The vibration isolation mount 1 is provided in which an upper plate 5 positioning a vibration isolation object to a positioning seat 11 is stably supported by a base plate 3 at a plurality of points via the arrangement of the nonlinear springs 7a, 7b, 7c, 7d. The vibration isolation mount includes a position changing functioning part which adjust a combined spring constant by changing the stable supporting position between the positioning seat 11 and nonlinear springs 7a, 7b, 7c, 7d. The position changing functioning part includes the positioning seat 11 which is fixed to the upper plate 5 in such a manner that the fastening position can be changed, and is configured by including a plurality of screw holes 15a, 15b, 17a, 17b, 19a, 19b, 21a, 21b enabling the fastening position of the positioning seat 11 to be changed.

Description

  The present invention relates to an anti-vibration mount and a method for adjusting a spring constant.

  In general, when a vibration-proof mount is configured by using a non-linear spring such as a disc spring or a leaf spring, the spring constant can be reduced at a high load while being compact (low spring stroke). This feature cannot be embodied by a linear spring and can only be obtained by using a non-linear spring.

  However, when a non-linear spring is used for an anti-vibration mount, a problem not found in a linear spring occurs.

  In general, the load of the vibration isolation target supported by the vibration isolation mount varies due to individual differences. For this reason, in the case of a non-linear spring whose spring constant strongly depends on the load, as shown in FIG. 17, the spring constant varies greatly due to individual differences of vibration isolation targets, and the vibration isolation performance (low spring constant) to be achieved is obtained. There is no fear.

  On the other hand, if a non-linear spring is designed for each anti-vibration object (load), the cost becomes remarkably high, resulting in a new problem that a general-purpose anti-vibration mount cannot be constructed.

  In order to deal with such a problem, there is a structure in which a vibration isolator to be supported is sandwiched between the same nonlinear springs, a tightening force is applied to these two nonlinear springs with a bolt or the like, and the spring constant is adjusted (Patent Documents 1 and 2).

  This structure is based on the principle of applying a forced displacement to two non-linear springs and flexing both non-linear springs connected in parallel to adjust the spring constant.

  However, in this structure, the load cannot be supported unless the load to be damped is sufficiently small, and there is a restriction that a nonlinear spring having an excessively high load supporting capacity and a large shape must be used. There was a problem in terms of cost and shape.

  In addition, it is necessary to sandwich the object to be anti-vibrated between the nonlinear springs by some method, and when the object to be anti-vibrated has a high load and a large shape, the anti-vibration mount structure for realizing the sandwiching structure is complicated. There was also a problem.

  As the non-linear spring on one side that sandwiches the object of vibration isolation, a linear spring or a non-linear spring having different load deflection characteristics can be used, but the above problem cannot be solved.

  As another countermeasure, Patent Document 2 has a structure in which a linear spring is connected to a nonlinear spring lower portion, and a tightening force is applied from the nonlinear spring lower portion to the linear spring with a bolt or the like.

  This structure adjusts the spring constant of the nonlinear spring by sharing a part of the load supported by the nonlinear spring with the linear spring. The combined spring constant of the linear spring and the nonlinear spring connected in parallel is It becomes the spring constant of the anti-vibration mount.

  Therefore, a linear spring having a low spring constant, being as compact as a non-linear spring, and capable of supporting the same load is required.

  However, when a high load is supported, there is no linear spring having such a feature, so this structure cannot be used to support a high load.

  As a method of adjusting the spring constant other than the above, there is a method described in Patent Document 3.

  In this structure, the nonlinear spring itself is tightened by a tightening mechanism such as a bolt. In this structure, since the spring constant of the tightening mechanism affects the spring constant of the nonlinear spring in parallel connection, a spring constant equal to or less than the spring constant of the tightening mechanism cannot be achieved.

  Therefore, in order to achieve a low spring constant, it is necessary to maintain a tightening force as a tightening mechanism and to have a low spring constant.

  However, when a high load is supported by a non-linear spring, there is a problem that a simple bolt or the like cannot achieve both a tightening force and a low spring constant.

JP-A-63-96335 JP-A-7-293621 Japanese translation of PCT publication No. 5-501441 JP-A-7-217687

  The problem to be solved is that in a vibration proof mount using a non-linear spring, it is difficult to obtain a stable spring constant if there is variation in the load to be damped.

  In order to obtain a stable spring constant by means of an anti-vibration mount using a non-linear spring, the present invention stably supports the anti-vibration object receiving part for positioning the anti-vibration object on the positioning part with respect to the base member at a plurality of points by the non-linear spring An anti-vibration mount comprising a position changing function unit for adjusting a composite spring constant of the non-linear spring by changing a stable support position between the positioning unit and the non-linear spring; and To do.

  An anti-vibration target receiving part for positioning an anti-vibration object on a positioning part is a method for adjusting a spring constant of an anti-vibration mount that is stably supported at a plurality of points by a non-linear spring with respect to a base member, wherein the positioning part and the non-linear spring The feature of the method for adjusting the spring constant of the anti-vibration mount is to change the stable support position between them.

  Since the vibration isolating mount of the present invention has the above-described configuration, the composite spring constant of the nonlinear spring can be adjusted by changing the stable support position between the positioning unit and the nonlinear spring by the position changing function unit.

  For this reason, even if there is variation in the load of the vibration isolation target positioned at the positioning portion, the composite spring constant of the vibration isolation mount can be stabilized and vibration isolation can be achieved with equivalent characteristics.

  Since the method for adjusting the spring constant of the vibration-proof mount of the present invention has the above-described configuration, the composite spring constant of the nonlinear spring can be adjusted by changing the stable support position between the positioning portion and the nonlinear spring.

  For this reason, even if there is variation in the load of the vibration isolation target positioned at the positioning portion, the composite spring constant of the vibration isolation mount can be stabilized and vibration isolation can be achieved with equivalent characteristics.

(A) is a plan view of the vibration-proof mount, and (B) is a cross-sectional view thereof (center-of-gravity deviation 0%). Example 1 (A) is a plan view of an anti-vibration mount, (B) is a cross-sectional view thereof (center of gravity deviation 20%) (Example 1) (A) is a plan view of an anti-vibration mount, and (B) is a cross-sectional view thereof (center of gravity deviation 40%) (Example 1) (A) is a plan view of an anti-vibration mount, (B) is a cross-sectional view thereof (center of gravity deviation 50%) (Example 1) (A) is a plan view of an anti-vibration mount, (B) is a cross-sectional view thereof (center of gravity deviation 60%) (Example 1) It is a conceptual diagram which shows the support position of a vibration isolating object. Example 1 (A) is a graph showing the relationship between the shared load and the deflection of the nonlinear spring on the right in FIG. 6, and (B) is a graph showing the relationship between the shared load and the deflection of the left nonlinear spring in FIG. Example 1 It is a graph which shows the relationship between the change of a stable support position, and bending. Example 1 It is a graph which shows the change of the spring constant according to the change of the stable support position. Example 1 (A) is a plan view of the vibration-proof mount, and (B) is a cross-sectional view thereof (center-of-gravity deviation 0%). (Example 2) (A) is a plan view of an anti-vibration mount, (B) is a cross-sectional view thereof (center of gravity deviation 20%) (Example 2) (A) is a plan view of an anti-vibration mount, (B) is a cross-sectional view thereof (center of gravity deviation 40%) (Example 2) (A) is a plan view of an anti-vibration mount, (B) is a cross-sectional view thereof (center of gravity deviation 50%) (Example 2) (A) is a plan view of an anti-vibration mount, (B) is a cross-sectional view thereof (center of gravity deviation 60%) (Example 2) (A) is a plan view showing the arrangement of the non-linear springs, and (B) is a sectional view thereof (center of gravity deviation 0%). (Example 3) (A) is a plan view showing the arrangement of the non-linear springs, and (B) is a cross-sectional view thereof (center of gravity deviation 30%). (Example 3) It is a graph which shows the fluctuation | variation of the spring constant of a non-linear spring by the load dispersion | variation in vibration isolating object. (Conventional example)

  Position for adjusting the composite spring constant of the nonlinear spring by changing the stable support position between the positioning portion of the vibration isolation target and the nonlinear spring for the purpose of obtaining a stable spring constant by the vibration isolating mount using the nonlinear spring. Realized by providing a change function section.

[Anti-vibration mount structure]
1 to 5 relate to the first embodiment, FIG. 1A is a plan view of an anti-vibration mount, FIG. 1B is a cross-sectional view thereof (center of gravity deviation 0%), and FIG. FIG. 3B is a plan view of the vibration isolation mount, FIG. 3A is a plan view of the vibration isolation mount, and FIG. 4A is a plan view of the vibration-proof mount, FIG. 4B is a cross-sectional view thereof (center of gravity deviation 50%), FIG. 5A is a plan view of the vibration-proof mount, and FIG. It is a figure (60% center of gravity deviation).

  As shown in FIG. 1, the anti-vibration mount 1 is formed in a circular shape in a plan view, and the upper plate 5 as the anti-vibration target receiving portion has four nonlinear springs 7a, 7b, 7c and 7d are stably supported at a plurality of four points. The non-linear springs 7a, 7b, 7c, and 7d may be any one that has a spring constant that decreases in accordance with a shared load due to an increase in the load between the upper plate 5 and the base plate 3, and in the present embodiment, a disc spring-like shape. The upper and lower convex edge portions are formed in a circular shape. The non-linear springs 7a, 7b, 7c, and 7d can be formed of a leaf spring or the like.

  The base plate 3 and the upper plate 5 are made of, for example, an aluminum alloy. A rubber cover 9 is fitted around the outer peripheries of the base plate 3 and the upper plate 5.

  In the center of the upper plate 5, a positioning seat 11 is fastened and fixed by bolts 13a and 13b as a positioning portion for positioning a vibration-proof object.

  The vibration isolating mount 1 has a position change for adjusting the composite spring constant of the nonlinear springs 7a, 7b, 7c, 7d by changing the stable support position between the positioning seat 11 and the nonlinear springs 7a, 7b, 7c, 7d. A functional part is provided.

  In this embodiment, the position changing function unit includes the positioning seat 11 and a plurality of screw holes 15a, 15b, 17a, 17b, 19a, 19b, 21a, 21b that can change the fastening position of the positioning seat 11. It is configured with.

  The displacement dimension of the screw holes 15a and 15b from the center C of the upper plate 5 is 6 mm as an example. Similarly, the screw holes 17a and 17b are 12 mm, the screw holes 19a and 19b are 15 mm, and the screw holes 21a and 21b are 18 mm.

  On the other hand, the distance between the center C and each of the nonlinear springs 7a, 7b, 7c, 7d is 30 mm.

  In FIG. 1, the positioning seat 11 is fastened and fixed by bolts 13 a and 13 b with the center aligned with the center C of the upper plate 5, and the center of gravity deviation is set to 0%, and the upper plate 5 and the positioning seat 11 are four pieces. The non-linear springs 7a, 7b, 7c and 7d are stably supported.

  The fastening position of the positioning seat 11 with respect to the upper plate 5 by the bolts 13a, 13b is changed by changing the screw holes 15a, 15b, 17a, 17b, 19a, 19b, 21a, 21b.

  In FIG. 2, the positioning seat 11 is fastened and fixed to the screw holes 15a and 15b by bolts 13a and 13b, set to a center of gravity deviation of 20% (6/30 × 100%), and is stably supported.

  In FIG. 3, the positioning seat 11 is fastened and fixed to the screw holes 17 a and 17 b by bolts 13 a and 13 b, set to a deviation of the center of gravity of 40% (12/30 × 100%), and is stably supported.

  In FIG. 4, the positioning seat 11 is fastened and fixed to the screw holes 19a and 19b by bolts 13a and 13b, set to 50% (15/30 × 100%) center of gravity deviation, and is stably supported.

In FIG. 5, the positioning seat 11 is fastened and fixed to the screw holes 21a and 21b by bolts 13a and 13b, set to a center of gravity shift of 60% (18/30 × 100%), and is stably supported.
[Spring constant adjustment method]
FIG. 6 is a conceptual diagram showing the support position of the vibration-proof object, FIG. 7A is a graph showing the relationship between the shared load and the deflection of the nonlinear spring on the right in FIG. 6, and FIG. 6B is the left in FIG. FIG. 8 is a graph showing the relationship between the change in the stable support position and the deflection, and FIG. 9 is a graph showing the change in the spring constant according to the change in the stable support position. It is a graph.

  When the stable support position of the positioning seat 11 is changed as shown in FIGS. 2 to 5, the vibration-proof object 23 corresponds to the four nonlinear springs 7a, 7b, 7c, and 7d as shown in FIG. Will be biased.

  For example, when looking only at the relationship between the two nonlinear springs 7a and 7b, the vibration-proof object 23 approaches the nonlinear spring 7a (left in the figure) and moves away from the nonlinear spring 7b (right in the figure). When this is seen in the bending change of FIG. 7, the shared load of the non-linear spring 7b (right) decreases as shown in (A), and the shared load of the non-linear spring 7a (left) increases as shown in (B). It becomes.

  With such a change in the shared load, the load deflection curve of the vibration-proof mount 1 having the nonlinear springs 7a, 7b, 7c, and 7d changes as shown in FIG. 8 according to the center-of-gravity shift amount of FIGS. The amount of deflection can be changed with respect to the same vibration-proof target load by increasing the amount of deviation of the center of gravity.

  Therefore, the combined spring constant of the vibration proof mount 1 with respect to the load change of the vibration proof object corresponds to FIG. 8 and changes as shown in FIG. As can be seen from FIG. 9, if the center of gravity is shifted according to the load variation of the vibration isolation target, the change curve of FIG. 9 can be selected, and the combined spring constant of the vibration isolation mount 1 can be made constant. .

In this case, it is possible to increase the allowable range of load variation of the vibration isolation target.
[Effect of Example 1]
In the vibration isolating mount of the first embodiment of the present invention, the upper plate 5 for positioning the vibration isolating object on the positioning seat 11 is stably supported on the base plate 3 at a plurality of points by the non-linear springs 7a, 7b, 7c, 7d. The anti-vibration mount 1 includes a position changing function unit that adjusts a composite spring constant by changing a stable support position between the positioning seat 11 and the nonlinear springs 7a, 7b, 7c, and 7d.

  The position change function unit includes a positioning seat 11 fixed to the upper plate 5 so that the fastening position can be changed, and a plurality of screw holes 15a, 15b, 17a, 17b, 19a that can change the fastening position of the positioning seat 11. , 19b, 21a, 21b.

  Accordingly, the screw holes 15a, 15b, 17a, 17b, 19a, 19b, 21a, 21b are selected, the fastening position of the positioning seat 11 is changed, and the positioning seat 11 and the nonlinear springs 7a, 7b, 7c, 7d are changed. When the stable support position is changed, the vibration-proof object 23 is biased with respect to the four nonlinear springs 7a, 7b, 7c, and 7d as shown in FIG.

  This bias increases or decreases the shared load of the nonlinear springs 7a, 7b, 7c, and 7d, and the composite spring constant of the vibration-proof mount 1 can be adjusted.

  For this reason, when there is a load variation in the vibration isolating object 23, the fastening position of the positioning seat 11 is selected as shown in FIGS. 2 to 5 according to this variation, and the vibration isolating mount having a constant spring constant as shown in FIG. 1 can be obtained.

  FIGS. 10 to 14 relate to the second embodiment, FIG. 10A is a plan view of an anti-vibration mount, FIG. 10B is a sectional view thereof (center of gravity deviation 0%), and FIG. FIG. 12B is a plan view of the vibration-proof mount, FIG. 12A is a plan view of the vibration-proof mount, and FIG. 12B is a cross-sectional view of the vibration mount. 13A is a plan view of the vibration-proof mount, FIG. 13B is a cross-sectional view thereof (center of gravity deviation 50%), FIG. 14A is a plan view of the vibration-proof mount, and FIG. It is a figure (60% deviation of the center of gravity).

  Note that the basic configuration is the same as that of the first embodiment, and the same components are denoted by the same reference numerals, the corresponding components are denoted by A, and redundant description is omitted.

  As shown in FIGS. 10 to 14, the vibration isolating mount 1 </ b> A according to the present embodiment includes a plurality of spiral grooves 25 a, 25 b, 25 c, and 25 d formed on the lower surface of the upper plate 5 </ b> A. It is a ball 27 interposed between 25a, 25b, 25c, 25d and the non-linear springs 7aA, 7bA, 7cA, 7dA.

  In each of the spiral grooves 25a, 25b, 25c, 25d, positioning recesses 25aa, 25ab, 25ac, 25ad, 25ae of the ball 27, positioning recesses 25ba, 25bb, 25bc, 25bd, 25be, positioning recesses 25ca, 25cb, 25cc, 25cd, 25ce, positioning recesses 25da, 25db, 25dc, 25dd, 25de are provided.

  Each nonlinear spring 7aA, 7bA, 7cA, 7dA is provided with a ball receiving portion 29 at the top, and a ball 27 is interposed between each ball receiving portion 29 and each spiral groove 25a, 25b, 25c, 25d. Has been.

  In this embodiment, as shown in FIG. 10, the space between the upper plate 5A and the positioning seat 11 is fixed by bolts 13a and 13b, and the upper plate 5A moves relative to the base plate 3A to set the center of gravity deviation.

  Therefore, the stable support position between the positioning seat 11 and the nonlinear springs 7aA, 7bA, 7cA, 7dA is changed by moving the spiral grooves 25a, 25b, 25c, 25d of the upper plate 5A relative to the ball 27. Can do.

  In FIG. 10, since the center C1 of the upper plate 5A and the positioning seat 11 is aligned with the center C2 of the base plate 3A, the center of gravity shift is set to 0%, and there are four upper plates 5 and positioning seats 11. The non-linear springs 7aA, 7bA, 7cA and 7dA are stably supported.

  At this time, the balls 27 are fitted into the positioning recesses 25aa, 25ba, 25ca, 25da at the ends of the spiral grooves 25a, 25b, 25c, 25d, and the upper plate 5A is connected to the nonlinear springs 7aA, 7bA, 7cA, 7dA. Positioning with respect to.

  The fitting force of each ball 27 to the recesses 25aa, 25ba, 25ca, and 25da can be obtained by the urging force of the rubber cover 9A. The cover 9A can be rotated relative to the base plate 3A while maintaining the biasing force.

  The stable support positions of the upper plate 5A and the positioning seat 11 with respect to the nonlinear springs 7aA, 7bA, 7cA, 7dA are changed by moving the spiral grooves 25a, 25b, 25c, 25d relative to the balls 27.

  In FIG. 11, the distance between the center C1 of the upper plate 5A and the positioning seat 11 and the center C2 of the base plate 3A is 6 mm, and the center C2 of the base plate 3A and the nonlinear springs 7aA, 7bA, 7cA, 7dA Since the gap is 30 mm (FIG. 10), the center-of-gravity deviation is set to 20% (6/30 × 100%).

  At this time, the balls 27 are fitted into the positioning recesses 25ab, 25bb, 25cb, 25db next to the spiral grooves 25a, 25b, 25c, 25d, and the upper plate 5A is fitted to the nonlinear springs 7aA, 7bA, 7cA, 7dA. Positioning with respect to. The relative movement of each ball 27 from the recesses 25aa, 25ba, 25ca, 25da to the recesses 25ab, 25bb, 25cb, 25db can be performed with a sense of moderation by the urging force of the cover 9A.

  In FIG. 12, the distance between the center C1 of the upper plate 5A and the positioning seat 11 and the center C2 of the base plate 3A is 12 mm, and the center-of-gravity deviation is set to 40% (12/30 × 100%).

  At this time, the balls 27 are fitted into the positioning recesses 25ac, 25bc, 25cc, 25dc next to the spiral grooves 25a, 25b, 25c, 25d, and the upper plate 5A is fitted to the nonlinear springs 7aA, 7bA, 7cA, 7dA. Positioning with respect to.

  In FIG. 13, the distance between the center C1 of the upper plate 5A and the positioning seat 11 and the center C2 of the base plate 3A is 15 mm, and the center-of-gravity deviation is set to 50% (15/30 × 100%).

  At this time, each ball 27 is fitted into the positioning recesses 25ad, 25bd, 25cd, 25dd next to the spiral grooves 25a, 25b, 25c, 25d, and the upper plate 5A is moved to the nonlinear springs 7aA, 7bA, 7cA, 7dA. Positioning with respect to.

  In FIG. 14, the distance between the center C1 of the upper plate 5A and the positioning seat 11 and the center C2 of the base plate 3 is 18 mm, and the center-of-gravity shift is set to 60% (18/30 × 100%).

  At this time, each ball 27 is fitted into the positioning recesses 25ae, 25be, 25ce, and 25de next to the spiral grooves 25a, 25b, 25c, and 25d, and the upper plate 5A is moved to the nonlinear springs 7aA, 7bA, 7cA, and 7dA. Positioning with respect to.

  With this setting, even in the present embodiment, as in the first embodiment, even when there is a load variation in the image stabilization target 23, the position of the center C1 of the upper plate 5A and the positioning seat 11 is changed according to this variation in FIGS. The vibration isolating mount 1A having a constant spring constant can be obtained.

  FIGS. 15 and 16 relate to the third embodiment, FIG. 15A is a plan view showing the arrangement of the non-linear springs, FIG. 15B is a sectional view thereof (center of gravity deviation 0%), and FIG. The top view which shows arrangement | positioning of a nonlinear spring, (B) is the same sectional drawing (center-of-gravity deviation 30%).

  Note that the basic configuration is the same as that of the first embodiment, the same components are denoted by the same reference numerals, the corresponding components are denoted by the same reference characters B, and redundant description is omitted.

  The anti-vibration mount 1B of the present embodiment sets the center of gravity shift by relatively moving the nonlinear spring side.

  The non-linear springs 7aB and 7dB are supported between an upper support 31 and a lower support 33 fixed to the upper plate 5B and the base plate 3B, respectively.

  The position changing function unit is a slider 35 that supports any one of the nonlinear springs 7aB, 7bB, 7cB, 7dB, for example, the nonlinear springs 7bB, 7cB so as to be movable between the upper plate 5B and the base plate 3B.

  In the slider 35, nonlinear springs 7 bB and 7 cB are supported between the slider base 37 and the slider upper 39. A plurality of balls 41 and 43 are interposed between the slider base 37 and the base plate 3B and between the slider upper 39 and the upper plate 5B, respectively.

  An end of an adjustment screw 45 is rotatably coupled to the slider upper 39, the adjustment screw 45 is axially supported by the upper support 31, and a knob portion 47 is disposed so as to protrude from the upper support 31.

  Therefore, by adjusting the rotation of the adjusting screw 45, the slider 35 is moved between the upper plate 5B and the base plate 3B via the balls 41 and 43, and the nonlinear springs 7bB and 7cB are moved closer to and away from the nonlinear springs 7aB and 7dB. Can be adjusted.

  That is, stable support between the positioning seat 11B and the nonlinear springs 7aB, 7bB, 7cB, 7dB by moving the nonlinear springs 7bB, 7cB, which are any of the nonlinear springs, relative to the upper plate 5B and the base plate 3B. The position can be changed.

  In FIG. 15, before the operation of the slider 35, the center C3 of the upper plate 5B and the positioning seat 11B is located at the center of the arrangement between the nonlinear springs 7aB, 7bB, 7cB, 7dB, and the center of gravity shift is 0%.

  In FIG. 16, the non-linear springs 7bB and 7cB are changed to positions of 42 mm with respect to the center C3 of the upper plate 5B and the positioning seat 11B. Since the distance between the center C3 of the upper plate 5B and the positioning seat 11B and the nonlinear springs 7cB and 7dB is 60 mm (FIG. 15) when the center-of-gravity deviation is 0%, the center-of-gravity deviation is set to 30% in FIG.

  With this setting, in the present embodiment as well as in the first embodiment, even when there is a load variation in the vibration isolation target 23, the positions of the nonlinear springs 7bB and 7cB are selected according to this variation, and the vibration isolation with a constant spring constant is performed. The mount 1B can be obtained.

In addition, in this embodiment, the positions of the nonlinear springs 7bB and 7cB can be continuously moved relative to each other, and the center-of-gravity deviation amount can be finely adjusted.
[Others]
The numerical value of each Example is an example and another dimension can also be selected according to the setting of each part.

  The anti-vibration mount may have a configuration in which the anti-vibration target receiving portion is stably supported at a plurality of points including the non-linear spring with respect to the base member. At least one point is supported by the non-linear spring and the other points are linear springs. Can also be supported. In this case, the position changing function unit adjusts the shared load of the non-linear spring in the same manner as in each of the above embodiments, and sets the combined spring constant with the linear spring.

1,1A, 1B Anti-vibration mount 3,3B Base plate (base member)
5,5A, 5B Upper plate (anti-vibration target receiving part)
7a, 7b, 7c, 7d, 7aA, 7bA, 7cA, 7dA, 7aB, 7bB, 7cB, 7dB Non-linear spring 11 Positioning seat (positioning part, position change function part)
11B Positioning seat (positioning part)
13a, 13b Bolt (position change function part)
15a, 15b, 17a, 17b, 19a, 19b, 21a, 21b Screw hole (position change function part)
27 balls (position change function part)
25a, 25b, 25c, 25d Spiral groove (position change function part)
35 Slider (position change function part)

Claims (10)

An anti-vibration target receiving part for positioning the anti-vibration object on the positioning part is an anti-vibration mount that is stably supported at a plurality of points by a non-linear spring with respect to the base member,
A position changing function unit for changing a stable support position between the positioning unit and the nonlinear spring to adjust a shared load of the nonlinear spring and setting a composite spring constant;
Anti-vibration mount characterized by that. An anti-vibration target receiving part for positioning the anti-vibration object on the positioning part is an anti-vibration mount that is stably supported at a plurality of points including a non-linear spring with respect to the base member,
A position changing function unit that adjusts a composite spring constant by adjusting a shared load of the nonlinear spring by changing a stable support position between the positioning unit and the nonlinear spring;
Anti-vibration mount characterized by that. The anti-vibration mount according to claim 1 or 2,
The position change function unit includes a positioning seat fixed to the vibration proof object receiving unit so that the fastening position can be changed,
Changing the stable support position by changing the fastening position of the positioning seat with respect to the vibration isolator receiving part,
Anti-vibration mount characterized by that. An anti-vibration mount according to claim 3,
The anti-vibration target receiving portion includes a plurality of fastening portions for changing the position of the positioning seat in a plurality of stages.
Anti-vibration mount characterized by that. The anti-vibration mount according to claim 1 or 2,
The position changing function unit includes a spiral groove formed in the vibration-proof object receiving portion and a ball interposed between the spiral groove and the nonlinear spring,
Changing the stable support position by moving the spiral groove of the vibration isolator receiving portion relative to the ball;
Anti-vibration mount characterized by that. The anti-vibration mount according to claim 1 or 2,
The position changing function part is a slider that supports any one of the nonlinear springs so as to be movable between the vibration-proof target receiving part and the base member,
Changing the stable support position by moving any one of the non-linear springs relative to the anti-vibration target receiving portion and the base member;
Anti-vibration mount characterized by that. The vibration-proof mount according to any one of claims 1 to 6,
The non-linear spring has a spring constant that decreases in accordance with a shared load due to an increase in load between the vibration receiving target receiving portion and the base member.
Anti-vibration mount characterized by that. A method for adjusting a spring constant of a vibration isolating mount in which a vibration isolating target receiving portion for positioning a vibration isolating object on a positioning portion is stably supported at a plurality of points by a non-linear spring with respect to a base member,
Adjusting a composite spring constant by changing a stable support position between the positioning portion and the nonlinear spring;
A method for adjusting a spring constant of an anti-vibration mount. A method for adjusting a spring constant of a vibration isolation mount in which a vibration isolation target receiving portion that positions a vibration isolation target on a positioning portion is stably supported at a plurality of points including a non-linear spring with respect to a base member,
Adjusting a composite spring constant by changing a stable support position between the positioning portion and the nonlinear spring;
A method for adjusting a spring constant of an anti-vibration mount. A method for adjusting the spring constant of the vibration-proof mount according to claim 8 or 9,
The non-linear spring has a spring constant that decreases in accordance with a shared load due to an increase in load between the vibration receiving target receiving portion and the base member.
A method for adjusting a spring constant of an anti-vibration mount.

Images