JP5986894B2 - Variable rigidity dynamic vibration absorber - Google Patents

Description

  The present invention relates to a variable rigidity dynamic vibration absorber.

  Patent Document 1 discloses a conventional variable stiffness dynamic vibration absorber. This variable rigidity type dynamic vibration absorber is composed of a vibration absorber body attached to a vibration body, a pair of long rigid bodies having the same rigidity, and a rotation that rotates these rigid bodies in opposite directions in a plane-symmetric state. An apparatus and a weight member supported by each rotatable rigid body are provided. Each rigid body is supported by the vibration absorber main body via a bearing member, and its axis is arranged in parallel on the same orthogonal plane with respect to the linear vibration direction of the vibrating body. Each rigid body supports a weight member via a bearing member. Each rigid body is formed in a cylindrical shape with a portion supported by the vibration absorber body via the bearing member and a portion supporting the weight member via the bearing member. A flat plate shape is formed between the portions.

  This variable rigidity dynamic vibration absorber can change the natural frequency by rotating a pair of rigid bodies in an accurate plane-symmetric state while maintaining an accurate parallel relationship. This variable stiffness type dynamic vibration damping device can control the vibration by matching the natural frequency with the vibration frequency of the vibrating body.

Japanese Patent No. 4257432

  However, in the variable stiffness type dynamic vibration damping device of Patent Document 1, it is difficult to form a flat plate between the portions formed in the columnar shape in the processing of the rigid body, it is difficult to ensure the necessary dimensional accuracy, and the manufacturing cost is low. Get higher. In particular, the rigid body having such a shape is likely to warp in post-processing such as quenching after processing, and it is difficult to ensure dimensional accuracy. For this reason, it is difficult to make the rigidity of the pair of rigid bodies the same (the spring constant of the portion formed in a flat plate shape of each rigid body). For this reason, as shown in FIG. 15, this variable stiffness type dynamic vibration absorber has a portion (arrowed portion) that is divided into two forks in the frequency analysis result in the impact test. As described above, this variable stiffness type dynamic vibration damping device has a possibility that the vibration damping effect is weakened or there is a frequency range where vibration cannot be suppressed. Further, in this variable stiffness type dynamic vibration absorber, the bearing member must be disassembled when the rigid body is replaced. Since the bearing member has to be preloaded to ensure the accuracy of the natural frequency, this variable stiffness type dynamic vibration absorber requires time and effort to replace the rigid body.

  The present invention has been made in view of the above-described conventional situation, and solves the problem of providing a variable-rigidity dynamic vibration damping device that has a wide frequency range in which vibration can be controlled and can be well controlled. It should be a challenge.

The variable stiffness type dynamic vibration absorber of the present invention includes a vibration absorber body attached to a vibrating body,
A pair of rigid bodies having the same rigidity and formed long,
Each of the rigid bodies has a rigid body support tool that detachably supports an end of the rigid body and is rotatably attached to the vibration absorber body, and each virtual center line extending in the longitudinal direction of the rigid body Arranged in parallel on the same orthogonal plane with respect to the linear vibration direction of the vibrating body, and the rigid bodies are in opposite directions to each other in a plane-symmetric state with these virtual center lines or virtual parallel lines parallel to these virtual center lines as rotation axes A rotating device for rotating
A weight main body and each rigid body detachably supported in a rotatable state with the virtual center line or the virtual parallel line as a rotation axis, and a weight support tool rotatably attached to the weight main body. A weight member;
It is characterized by having.

  The variable stiffness type dynamic vibration absorber attached with a rigid body with the same rigidity can finely and accurately adjust the natural frequency, and can satisfactorily suppress the vibration in the entire frequency range that can be controlled. Can do. Further, in this variable stiffness type dynamic vibration absorber, since the rigid body is detachable with respect to the rotating device and the weight member, only the rigid body can be replaced when a problem occurs in the rigid body. Further, by changing to a rigid body having a different rigidity, the range of the natural frequency that can be adjusted can be changed, and the frequency range in which vibration can be controlled can be easily changed.

  Therefore, the variable stiffness type dynamic vibration damping device of the present invention has a wide frequency range in which vibration can be controlled and can be well controlled.

It is sectional drawing which shows the variable rigidity type | mold dynamic vibration absorber of Example 1. FIG. It is arrow XX sectional drawing of FIG. FIG. 3 is a sectional view taken along the line YY in FIG. 2. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an exploded cross-sectional view showing a variable rigidity dynamic vibration absorber of Example 1. 3 is a plan view showing a flat spring of Example 1. FIG. It is a graph which shows the frequency analysis result of the impact test which changed rotation angle (alpha) of the flat spring of the variable rigidity type | mold dynamic vibration absorber of Example 1. FIG. It is a graph which shows the relationship between the rotation angle (alpha) of the flat spring of the variable rigidity type | mold dynamic vibration absorber of Example 1, and a natural frequency. It is a graph which shows the relationship between the rotation angle (alpha) of a flat spring, and a natural frequency at the time of replacing | exchanging the plate | board thickness of a flat spring. It is a graph which shows transition of the natural frequency at the time of changing the attachment number n of an additional mass thing. It is a graph which shows the damping effect by the presence or absence of an attenuation body. It is a graph which shows the damping vibration waveform at the time of changing the additional amount of an attenuation body, (A) is when there is no attenuation body, (B) is when the damping force of an attenuation body is small, (C) is an attenuation body. The case where the damping force is large is shown. It is sectional drawing which shows the variable rigidity type | mold dynamic vibration damper apparatus of Example 2. FIG. It is arrow XX sectional drawing of FIG. FIG. 14 is a cross-sectional view taken along line YY in FIG. 13. It is a graph which shows the frequency analysis result in the impact test of the variable rigidity type | mold dynamic vibration absorber of patent document 1. FIG.

  A preferred embodiment of the present invention will be described.

  The rigid body of the present invention may be a flat spring. In this case, the flat spring can ensure the necessary dimensional accuracy and can be easily processed into a uniform spring constant as a whole. For this reason, it is easy to make the pair of rigid bodies (flat springs) attached to the variable rigidity type dynamic vibration absorber have the same rigidity. The variable stiffness type dynamic vibration absorber equipped with a pair of rigid bodies (flat springs) having the same rigidity can adjust the natural frequency finely and accurately, and is excellent in the entire frequency range where vibration can be controlled Can be controlled.

Variable stiffness type dynamic vibration absorber of the present invention, the thickness of the rigid body can be replaced with a flat leaf spring you differences. In this case, the rigidity of the flat spring can be easily changed by the difference in the plate thickness. For this reason, by replacing with a flat spring having a different plate thickness, the range of the natural frequency of the variable rigidity dynamic vibration absorber can be easily changed, and the frequency range in which vibration can be controlled can be changed. it can.

  The variable stiffness type dynamic vibration absorber of the present invention may include an additional mass that can be attached to and detached from the weight member. In this case, the range of the natural frequency of the variable stiffness type dynamic vibration absorber can be easily changed by attaching and detaching the weight member of the additional mass, and the frequency range in which vibration can be controlled can be changed.

  The variable rigidity dynamic vibration damping device of the present invention may include an attenuation body interposed between the vibration absorber body and the weight member. In this case, stable vibration suppression can be performed against changes in the vibration of the vibrating body. In addition, fatigue failure of the flat spring can be reduced.

  Next, Embodiments 1 and 2 embodying the variable rigidity dynamic vibration damping device of the present invention will be described with reference to the drawings.

<Example 1>
As shown in FIGS. 1 and 2, the variable stiffness type dynamic vibration absorber of the first embodiment supports a vibration absorber body 10, a flat spring 30 that is a pair of elongated rigid bodies, and each flat spring 30. A rotating device 50, a weight member 70 supported by the flat spring 30, and a damping body 90 interposed between the vibration absorber body 10 and the weight member 70. The vibrating body 1 vibrates linearly in a direction perpendicular to the planar mounting surface 1A to which the variable stiffness type dynamic vibration absorber is mounted (vibrates in the direction of arrow V shown in FIG. 1).

  The vibration absorber body 10 is attached to the attachment surface 1 </ b> A of the vibration body 1. When the vibration absorber body 10 is attached to the vibrating body 1, the flat base portion 11 that forms the contact surface 11 </ b> A that contacts the mounting surface 1 </ b> A of the vibrating body 1, and the opposite direction of the contact surface 11 </ b> A from both sides of the base portion 11. And plate-like side wall portions 12A and 12B extending in the direction. Both side wall portions 12A and 12B have two pairs of through-holes 13 provided at opposing positions. Two sets of through-holes 13 provided in each of the side wall portions 12A and 12B are provided side by side on a plane parallel to the contact surface 11A. A pair of through-holes 13 provided at opposing positions pass through both ends of one flat spring 30. Each through hole 13 includes a first hole portion 13A, a second hole portion 13B, and a third hole portion 13C from the inside to the outside of the vibration absorber body 10. The first hole portion 13A, the second hole portion 13B, and the third hole portion 13C have a circular cross-sectional shape orthogonal to the through direction of the through hole 13. The inner diameter gradually increases in the order of the first hole 13A, the second hole 13B, and the third hole 13C.

  As shown in FIG. 5, each flat spring 30 has a long flat plate shape. Each flat spring 30 is quenched. Each flat spring 30 has the same plate thickness and is processed into a uniform spring constant (same rigidity) as a whole. Each flat spring 30 has insertion holes 30 </ b> A and 30 </ b> B that are provided in two in the longitudinal direction at three locations, both ends and the center. The shaft portion of the fixing bolt 61 can be inserted into each insertion hole 30A, 30B.

As shown in FIGS. 1 to 4, the rotating device 50 includes a first support 51 that is a rigid body support that detachably supports one end of each flat spring 30, and the other of the flat springs 30. And a second support member 52 which is a support member for a rigid body that detachably supports the end portion of the support member . That is, the rotating device 50 includes two sets of the first support 51 and the second support 52 for each flat spring 30.

  Each first support 51 includes a first support member 53, two bearing-type bearing members 55, a fastening member 57, a pressing member 59, two fixing bolts 61, and a gear 63. Each second support 52 includes a second support member 54, two bearing-type bearing members 55, a fastening member 57, a pressing member 59, and two fixing bolts 61.

  The first support member 53 has a first shaft portion 53A and a first connecting portion 53B provided continuously on one side thereof. The first shaft portion 53A has a cylindrical shape, is inserted from the outside into the through hole 13 of the one side wall portion 12A, and is fitted inside the inner rings of the two bearing type bearing members 55. The two bearing-type bearing members 55 are arranged between the outer peripheral surface of the first shaft portion 53A of the first support member 53 and the inner peripheral surface of the second hole portion 13B of the through hole 13 of the side wall portion 12A. The first support member 53 is rotatable around the central axis of the through hole 13 of the one side wall portion 12A. The bearing type bearing member 55 can adjust the preload by the screwing condition of the tightening member 57 screwed into the third hole portion 13C of the through hole 13 of the side wall portion 12A.

  The first connecting portion 53B of the first support member 53 is exposed outside the one side wall portion 12A. The first connecting portion 53B has a flat surface 53C on which one end of the flat spring 30 inserted through the first shaft portion 53A overlaps. In the first connecting portion 53B, when one end portion of the flat spring 30 is overlapped on the flat surface 53C, the fixing bolt 61 is screwed into a position corresponding to the two insertion holes 30A aligned with the end portion of the flat spring 30. A screw hole 56 is provided.

  The pressing member 59 has the same width as the flat spring 30 and has the same length as the flat surface 53C of the first connecting portion 53B. The holding member 59 is overlaid on one end of the flat spring 30 that is overlaid on the flat surface 53C of the first connecting portion 53B. The holding member 59 has an insertion hole 59 </ b> A of the same size at a position corresponding to the two insertion holes 30 </ b> A arranged at the end of the flat spring 30.

  One end of the flat spring 30 is inserted through the insertion hole 59A of the pressing member 59 and the insertion hole 30A of the flat spring 30 while being sandwiched between the flat surface 53C of the first connecting portion 53B and the pressing member 59. The fixing bolts 61 are screwed into the screw holes 56 of the first connecting portion 53B, thereby being fixed and supported by the first support member 53. One end of the flat spring 30 can be removed from the first support member 53 by loosening these fixing bolts 61 and extracting them from the screw holes 56.

  The gear 63 is coupled to the outer end of the first coupling portion 53 </ b> B of the first support member 53. The gear 63 rotates with the rotation of the first support member 53. The gears 63 connected to the two first connecting portions 53B located outside the one side wall portion 12A are engaged with each other. One gear 63 is also engaged with a gear 67 connected to the rotation shaft 65 </ b> A of the motor 65. For this reason, when the motor 65 is driven, the gears 63 rotate in the opposite directions, and the flat springs 30 supported by the first support members 53 rotate in the opposite directions in a plane-symmetric state.

  The second support member 54 has a second shaft portion 54A and a second connecting portion 54B provided continuously on the other side. The second shaft portion 54A has a cylindrical shape, is inserted from the outside into the through hole 13 of the other side wall portion 12B, and is fitted inside the inner rings of the two bearing type bearing members 55. The two bearing type bearing members 55 are disposed between the outer peripheral surface of the second shaft portion 54A of the second support member 54 and the inner peripheral surface of the second hole portion 13B of the through hole 13 of the side wall portion 12B. The second support member 54 is rotatable around the central axis of the through hole 13 of the other side wall 12B. The bearing type bearing member 55 can adjust the preload by the screwing condition of the fastening member 57 screwed into the third hole portion 13C of the through hole 13 of the side wall portion 12B.

  The 2nd connection part 54B of the 2nd support member 54 is exposed outside the other side wall part 12B. The second connecting portion 54B has a flat surface 54C on which the other end of the flat spring 30 inserted through the second shaft portion 54A overlaps. In the second connecting portion 54B, the fixing bolt 61 is screwed into a position corresponding to the two insertion holes 30A aligned with the end of the flat spring 30 when the other end of the flat spring 30 is overlapped on the flat surface 54C. A screw hole 58 is provided.

  The pressing member 59 has the same width as the flat spring 30 and has the same length as the plane of the second connecting portion 54B. The holding member 59 is overlaid on the other end of the flat spring 30 overlaid on the flat surface 54C of the second connecting portion 54B. The holding member 59 has an insertion hole 59 </ b> A of the same size at a position corresponding to the two insertion holes 30 </ b> A arranged at the end of the flat spring 30.

  The other end of the flat spring 30 is inserted through the insertion hole 59A of the pressing member 59 and the insertion hole 30A of the flat spring 30 while being sandwiched between the flat surface 54C of the second connecting portion 54B and the pressing member 59. The fixing bolts 61 are screwed into the screw holes 58 of the second connecting portion 54B, thereby being fixed and supported by the second support member 54. The other end of the flat spring 30 can be removed from the second support member 54 by loosening these fixing bolts 61 and extracting them from the screw holes 58.

  Thus, each flat spring 30 is detachably supported at both ends by the first support member 53 and the second support member 54. The rotating device 50 passes through the center of the cross section in the short direction of each flat spring 30 and extends a virtual center line extending in the long direction on the same orthogonal plane with respect to the linear vibration direction of the vibrating body 1 (of the vibration absorber body 10). Each flat spring 30 is arranged in parallel on the same plane parallel to the contact surface 11A, and when the motor 65 is driven, each flat spring 30 rotates this virtual center line or a virtual parallel line parallel to the virtual center line. Rotate in opposite directions in a plane-symmetric state as a moving axis.

The weight member 70 includes two weight main bodies 71 having two hollow portions 72, and two weight members 70 that are disposed in the respective hollow portions 72 and that are detachably connected to the central portion of each flat spring 30 to support the weight member 70. The third support 73 is attached to the third support 73, which is a weight support, and a third opening 72C, which will be described later, provided to insert the third support 73 into each cavity 72, and the third support 73 is positioned. And a lid member 75.

  The weight main body 71 has a rectangular parallelepiped shape. Each hollow portion 72 has a substantially cylindrical shape, and is provided side by side so that the flat springs 30 supported at both ends by the first support member 51 and the second support member 52 are inserted along the respective central axes. Yes. The weight main body 71 is continuous with each of the hollow portions 72 and continuously with each of the two first opening portions 72A opened in the direction opposite to the base portion 11 of the vibration absorber main body 10 and each of the hollow portions 72. Two second openings 72B opened on one side wall 12A side of the vibration absorber main body 10 and two pieces opened on the other side wall 12B side of the vibration absorber main body 10 in succession to each cavity 72. The third opening 72C.

  Each first opening 72 </ b> A is formed to have a size through which a later-described pressing member 79 that sandwiches the central portion of the flat spring 30 and the fixing bolt 61 can pass. Each second opening 72B is formed in a round hole having a diameter slightly larger than the width dimension of the flat spring 30, and the flat spring 30 is inserted therethrough. The third opening 72 </ b> C is formed in a round hole having a size that allows the third support member 73 to be inserted into the cavity 72.

  Each third support 73 includes a third support member 77, two bearing-type bearing members 55, a pressing member 59, and two fixing bolts 61. The third support member 77 has a third connecting portion 77A and a third shaft portion 77B provided continuously on both sides thereof. Each third shaft portion 77B has a cylindrical shape, and each third shaft portion 77B is fitted inside the inner ring of the bearing type bearing member 55. One of the bearing type bearing members 55 is disposed between one outer peripheral surface of the third shaft portion 77 </ b> B and the inner peripheral surface of the cavity portion 72.

  Each lid member 75 has a substantially disk-like outer shape, and is attached by screwing into the inner peripheral surface of the third opening 72 </ b> C of the weight main body 71. When the lid member 75 is attached to the third opening 72C, a peripheral edge facing the inside of the weight main body 71 protrudes in an annular shape, and a recess 75A is formed at the center. The lid member 75 is continuous to the center of the recess 75A, and has an opening 75B that opens to the other side wall 12B side of the vibration absorber body 10 when attached to the third opening 72C. . The opening 75B is formed in a round hole having a diameter slightly larger than the width dimension of the flat spring 30, and the flat spring 30 is inserted therethrough. The other of the bearing type bearing member 55 is disposed between the other outer peripheral surface of the third shaft portion 77B and the inner peripheral surface of the concave portion 75A of the lid member 75. The third support member 77 is positioned in the cavity 72 by screwing the lid member 75 into the inner peripheral surface of the third opening 72C. At this time, the bearing type bearing member 55 can adjust the preload by the screwing condition of the lid member 75. The third support member 77 is rotatable within the cavity 72 of the weight member 70.

  The third connecting portion 77A has a flat surface 77C where the central portions of the flat springs 30 inserted through the third shaft portions 77B on both sides overlap. The third connecting portion 77A is a screw into which the fixing bolt 61 is screwed into a position corresponding to the two insertion holes 30B arranged in the central portion of the flat spring 30 when the central portion of the flat spring 30 is overlapped on the flat surface 77C. A hole 78 is provided.

  The holding member 79 has the same width as the flat spring 30 and has a length slightly shorter than the plane of the third connecting portion 77A. The holding member 79 is overlaid on the central portion of the flat spring 30 that is overlaid on the plane of the third connecting portion 77A. The holding member 79 has an insertion hole 79 </ b> A having the same size at a position corresponding to the two insertion holes 30 </ b> B arranged in the center of the flat spring 30.

  The central portion of the flat spring 30 is sandwiched between the flat surface 77C of the third connecting portion 77A of the third support member 77 and the pressing member 79, and the insertion hole 79A of the pressing member 79 and the insertion hole 30B of the flat spring 30 The two fixing bolts 61 inserted through are screwed into the screw holes 78 of the third connecting portion 77 </ b> A to be fixed to the third support member 77. Thus, the weight member 70 is detachably supported at the center of the flat spring 30 in a state in which the flat spring 30 is rotatable about the virtual center line as a rotation axis. The central portion of the flat spring 30 can be removed from the third support member 77 by loosening these fixing bolts 61 and extracting them from the screw holes 78.

  The weight body 71 has a flat side surface opposite to the side surface facing the base portion 11 of the vibration absorber body 10, and a plurality of rectangular parallelepiped-shaped additional masses 95 can be attached to the side surface. . Each additional mass 95 has the same shape and the same mass. The attenuation body 90 is made of rubber and is sandwiched between the base portion 11 of the vibration absorber body 10 and the weight body 71.

  In the variable stiffness dynamic vibration absorber having such a configuration, the flat spring 30 is connected to the first support member 53, the second support member 54, and the third support member 77 by the fixing bolt 61. As shown in FIG. 4, when the fixing bolt 61 is loosened and extracted from the screw hole, the flat spring 30 can be extracted from the second support member 54 side. At this time, it is not necessary to remove or move the first support member 53, the second support member 54, and the weight member 70 from the vibration absorber body 10. That is, it is not necessary to disassemble each bearing type bearing member 55. In this variable stiffness type dynamic vibration absorber, the flat spring 30 is inserted from the second support member 54 side, and the first support member 53, the second support member 54, and the third support member 77 are respectively fixed by the fixing bolts 61. Can be linked. As described above, the variable stiffness type dynamic vibration absorber can easily replace only the flat spring 30 when a fault occurs in the flat spring 30.

  Next, characteristics of the variable stiffness type dynamic vibration absorber will be described.

  First, the frequency analysis result of the variable stiffness type dynamic vibration absorber when the impact test was performed with the plate thickness of 1 mm and the hardened flat spring 30 attached and the rotation angle α of the flat spring 30 changed was performed. As shown in FIG. The flat spring 30 drives the motor 65 and can rotate in opposite directions in a plane-symmetric state. The rotation angle α of the flat spring 30 is 0 deg. , The flat spring 30 is perpendicular to the vibration direction of the vibrating body 1 and the rotation angle α is 90 deg. In this case, the flat spring 30 is parallel to the vibration direction of the vibrating body 1. In this variable stiffness type dynamic vibration absorber, as the rotation angle α of the flat spring 30 increases, the peak value moves in a direction in which the frequency is large, and the natural frequency increases. FIG. 7 shows the relationship between the rotation angle α of the flat spring 30 and the natural frequency. In this variable stiffness type dynamic vibration absorber, the natural frequency smoothly changes as the rotation angle α of the flat spring 30 increases.

  In this variable stiffness type dynamic vibration absorber, the flat spring 30 has the required dimensional accuracy and is processed to have a uniform spring constant as a whole, so that the rigidity of the pair of flat springs 30 attached can be the same. it can. For this reason, in this variable stiffness type dynamic vibration damping device, the natural frequency continuously changes as the rotation angle α of the flat spring 30 increases, and the natural frequency can be finely and accurately adjusted. The vibration can be satisfactorily suppressed over the entire frequency range.

  FIG. 8 shows the relationship between the rotation angle α of the flat spring 30 and the natural frequency when the plate thickness t of the flat spring 30 is changed to 1.0 mm, 1.5 mm, 2.0 mm, and 2.5 mm. It can be seen that, in this variable stiffness type dynamic vibration absorber, when the plate thickness t of the flat spring 30 is increased, the adjustable natural frequency range is increased.

  This variable stiffness type dynamic vibration absorber can be easily replaced with a flat spring 30 having different stiffness. For this reason, this variable stiffness type dynamic vibration absorber can change the range of the natural frequency that can be adjusted by replacing the plate spring 30 with a different plate thickness, and the frequency range that can be damped can be easily set. Can be changed.

  Next, the transition of the natural frequency when the number n of the additional mass objects 95 is attached to the weight main body 71 is shown in FIG. This variable stiffness type dynamic vibration absorber can adjust the natural frequency range according to the machining specifications by changing the number n of the additional masses 95 attached to the weight main body 71. That is, the variable stiffness type dynamic vibration absorber can easily change the range of the natural frequency by attaching and detaching the additional mass 95, and can change the frequency range in which vibration can be controlled.

  Next, FIG. 10 shows the damping effect due to the presence or absence of the attenuation body 90. Moreover, when there is no attenuation body 90, the attenuation | damping vibration waveform and attenuation ratio when attenuation | damping of the attenuation body 90 is small and large are shown to FIG. In this variable stiffness type dynamic vibration absorber, when the damping body 90 is sandwiched between the base portion 11 and the weight main body 71 of the vibration absorber body 10, the vibration damping effect is slightly reduced, but even if the tuning is slightly shifted, it is not shifted. The vibration suppression effect substantially the same as the case can be ensured (robustness is ensured), and the resonance amplitude can also be reduced. That is, stable vibration suppression can be performed with respect to changes in the vibration of the vibrating body 1. Further, fatigue failure of the flat spring 30 can be prevented.

  As described above, the variable stiffness type dynamic vibration damping device of the first embodiment has a wide frequency range in which vibration can be controlled, and can perform good vibration control.

<Example 2>
As shown in FIGS. 12 to 14, the variable stiffness type dynamic vibration absorber of the second embodiment supports a flat plate spring 130 that is a pair of rigid bodies formed in a long shape with a vibration absorber body 110, and each flat plate spring 130. The rotating device 150, a weight member 170 supported by the flat spring 130, and a damping body 190 interposed between the vibration absorber main body 110 and the weight member 170 are provided. The vibrating body 1 vibrates linearly in a direction orthogonal to the flat mounting surface 1A to which the variable stiffness type dynamic vibration absorber is mounted (vibrates in the direction of arrow V shown in FIG. 12).

  The vibration absorber main body 110 is attached to the attachment surface 1A of the vibrator 1. When the vibration absorber body 110 is attached to the vibrating body 1, the flat base portion 111 that forms the contact surface 111 A that contacts the mounting surface 1 A of the vibrating body 1, and the contact surface 111 A from one end of the base portion 111. And a side wall portion 112 extending in the opposite direction. The side wall portion 112 is provided with two through holes 113 arranged on a plane parallel to the contact surface 111A. Each through hole 113 includes a first hole 113A, a second hole 113B, and a third hole 113C from the side where the weight member 170 is disposed toward the opposite side. The first hole 113A, the second hole 113B, and the third hole 113C have a circular cross-sectional shape that is orthogonal to the through direction of the through hole 113. The inner diameter gradually increases in the order of the first hole 113A, the second hole 113B, and the third hole 113C.

  Each flat spring 130 has a long flat plate shape. Each flat spring 130 is quenched. Each flat spring 130 has the same plate thickness, and is processed into a uniform spring constant (same rigidity) as a whole. Each flat spring 130 has one insertion hole 130A at each end. The shaft portion of the fixing bolt 161 can be inserted into each insertion hole 130A.

The rotating device 150 has two sets of first support members 151 that are support members for rigid bodies that detachably support the end portions of the flat springs 130. Each first support 151 includes a first support member 153, two bearing-type bearing members 155, a fastening member 157, a pressing member 159, one fixing bolt 161, and a gear 163.

  The first support member 153 has a first shaft portion 153A and a first connecting portion 153B provided continuously on one side thereof. The first shaft portion 153A is a side surface of the side wall portion 112, and protrudes from the opposite side surface where the weight member 170 is located, a second shaft 153Y continuous with the first shaft 153X, and a second shaft The third shaft 153Z is continuous with 153Y. The first shaft 153X, the second shaft 153Y, and the third shaft 153Z are concentric columnar shapes. Further, the outer diameter gradually increases in the order of the first shaft 153X, the second shaft 153Y, and the third shaft 153Z. The second shaft 153Y and the third shaft 153Z are inserted into the through holes 113 of the side wall portion 112, and the second shaft 153Y is fitted inside the inner rings of the two bearing type bearing members 155.

  The two bearing type bearing members 155 are disposed between the outer peripheral surface of the second shaft 153 </ b> Y of the first support member 153 and the inner peripheral surface of the second hole portion 113 </ b> B of the through hole 113 of the side wall portion 112. The first support member 153 is rotatable around the central axis of the through hole 113 of the side wall portion 112.

  The tightening member 157 includes an annular screw-in member 157A, and a cylindrical push-in member 157B that is disposed between the screw-in member 157A and the bearing-type bearing member 155 and pushes in the bearing-type bearing member 155. The screw member 157A can be screwed into the first shaft 153X of the first support member 153. Since the tightening member 157 can adjust the distance that the push-in member 157B pushes the bearing-type bearing member 155 depending on the screwing condition of the screw-in member 157A, the preload of the bearing-type bearing member 155 can be adjusted.

  The first connecting portion 153B of the first support member 153 protrudes from the side surface of the side wall portion 112 toward the weight member 170 side. The first connecting portion 153B has a flat surface 153C where one end of the flat spring 130 overlaps. The first connecting portion 153B has a screw hole 156 into which the fixing bolt 161 is screwed at a position corresponding to the insertion hole 130A at the end of the flat spring 130 when one end of the flat spring 130 is overlapped on the flat surface 153C. Provided.

  The holding member 159 is wider than the flat spring 130 and has the same length as the flat surface 153C of the first connecting portion 153B. The holding member 159 is overlaid on one end of the flat spring 130 that is overlaid on the flat surface 153C of the first connecting portion 153B. The holding member 159 has an insertion hole 159A having the same size at a position corresponding to the insertion hole 130A at the end of the flat spring 130.

  One end of the flat spring 130 is inserted through the insertion hole 159A of the pressing member 159 and the insertion hole 130A of the flat spring 130 while being sandwiched between the flat surface 153C of the first connecting portion 153B and the pressing member 159. The fixing bolts 161 are screwed into the screw holes 156 of the first connecting portion 153B, thereby being fixed and supported by the first support member 153. One end of the flat spring 130 can be detached from the first support member 153 by loosening these fixing bolts 161 and extracting them from the screw holes 156.

  The gear 163 is connected to the first shaft 153X of the first support member 153. The gear 163 rotates with the rotation of the first support member 153. The gears 163 connected to the two first shafts 153X located outside the side wall 112 are engaged with each other. One gear 163 also meshes with a gear 167 connected to the rotating shaft 165A of the motor 165. For this reason, when the rotating shaft 165A of the motor 165 rotates, the gears 163 rotate in the opposite directions, and the flat springs 130 supported by the first support members 153 rotate in the opposite directions in a plane-symmetric state.

  In this way, each flat spring 130 is supported by the first support member 153 so that one end thereof is detachable. The rotating device 150 passes through the center of the cross-section of each flat spring 130 in the short direction and extends a virtual center line extending in the long direction on the same orthogonal plane with respect to the linear vibration direction of the vibrating body 1 (of the vibration absorber body 110). When the motor 165 is driven, each flat spring 130 is symmetrical with respect to the virtual center line or a virtual parallel line parallel to the virtual center line as a rotation axis. Rotate in opposite directions.

The weight member 170 is provided side by side on the side wall portion 112 side, two first cavities 172A in which the flat springs 130 are accommodated, and two cavities 170 that communicate with each of the first cavities 172A via the communication port 172C. The weight main body 171 having the second cavity portion 172B and the weight body 171 that is housed in each of the second cavity portions 172B and is detachably connected to the other end of each flat spring 130 to support the weight member 170 And two second supports 173 which are supports.

  The weight main body 171 has a rectangular parallelepiped shape. The weight main body 171 has two first opening portions 174A that are continuous with each of the first hollow portions 172A and open in a direction opposite to the base portion 111 of the vibration absorber main body 110. Further, the weight body 171 includes two second openings 174B in which the first cavities 172A are opened on the side surface on the side wall 112 side of the vibration absorber body 110, and the second cavities 172B on the opposite side surface. It has the 3rd opening part 174C opened. Each first cavity 172A and each second cavity 172B are substantially cylindrical.

  Each first opening 174 </ b> A is formed to have a size that allows the flat spring 130, a pressing member 159 to be described later that sandwiches both ends of the flat spring 130, and the fixing bolt 161 to pass therethrough. The first connecting portion 153B of each first support 151 passes through each second opening 174B and is disposed in the first cavity 172A.

  Each second support 173 includes a second support member 175, two bearing-type bearing members 155, a fastening member 157, a pressing member 159, and one fixing bolt 161. The second support member 175 has a second shaft portion 175A and a second connecting portion 175B provided continuously on one side thereof. The second shaft portion 175A includes a first shaft 175X protruding from the weight main body 171, a second shaft 175Y continuous with the first shaft 175X, and a third shaft 175Z continuous with the second shaft 175Y. The first shaft 175X, the second shaft 175Y, and the third shaft 175Z are concentric cylinders. Further, the outer diameter gradually increases in the order of the first shaft 175X, the second shaft 175Y, and the third shaft 175Z. The second shaft 175Y and the third shaft 175Z are inserted into the second cavity 172B of the weight main body 171 and the second shaft 175Y is fitted inside the inner ring of the two bearing type bearing members 155. .

  The two bearing type bearing members 155 are disposed between the outer peripheral surface of the second shaft 175 </ b> Y of the second support member 175 and the inner peripheral surface of the second cavity portion 172 </ b> B of the weight main body 171. The second support member 175 is rotatable around the central axis of the second cavity 172B of the weight body 171.

  The tightening member 157 includes an annular screw-in member 157A, and a cylindrical push-in member 157B that is disposed between the screw-in member 157A and the bearing-type bearing member 155 and pushes in the bearing-type bearing member 155. The screw member 157A can be screwed into the first shaft 175X of the second support member 175. Since the tightening member 157 can adjust the distance that the push-in member 157B pushes the bearing-type bearing member 155 depending on the screwing condition of the screw-in member 157A, the preload of the bearing-type bearing member 155 can be adjusted.

  The second connecting portion 175B of the second support member 175 passes through the communication port 172C and is disposed in the first cavity portion 172A. The second connecting portion 175B has a flat surface 175C on which the other end of the flat spring 130 overlaps. The second connecting portion 175B has a screw hole 176 into which the fixing bolt 161 is screwed into a position corresponding to the insertion hole 130A at the end of the flat spring 130 when the other end of the flat spring 130 is overlapped with the flat surface 175C. Provided.

  The holding member 159 is wider than the flat spring 130 and has the same length as the flat surface 175C of the second connecting portion 175B. The holding member 159 is overlaid on one end of the flat spring 130 that is overlaid on the flat surface 175C of the second connecting portion 175B. The holding member 159 has an insertion hole of the same size at a position corresponding to the insertion hole at the end of the flat spring 130.

  The other end of the flat spring 130 is inserted through the insertion hole 159A of the pressing member 159 and the insertion hole 130A of the flat spring 130 while being sandwiched between the flat surface 175C of the second connecting portion 175B and the pressing member 159. The fixing bolts 161 are screwed into the screw holes 176 of the second connecting portion 175B, thereby being fixed and supported by the second support member 175. The other end of the flat spring 130 can be removed from the second support member 175 by loosening these fixing bolts 161 and extracting them from the screw holes 176.

  The weight main body 171 has a flat surface opposite to the base 111 of the vibration absorber main body 110, and a plurality of rectangular parallelepiped-shaped additional masses (not shown) can be attached to this surface. Each additional mass has the same shape and the same mass. The attenuation body 190 is made of rubber, and is sandwiched between the base 111 of the vibration absorber main body 110 and the weight main body 171.

  In the variable stiffness type dynamic vibration absorber having such a configuration, the flat spring 130 is connected to the first support member 153 and the second support member 175 by the fixing bolt 161. When the fixing bolt 161 is loosened and extracted from the screw holes 156 and 176, the flat spring 130 can be extracted from the first opening 174A. At this time, the first support member 153, the second support member 175, and the weight member 170 need not be removed from the vibration absorber body 110 or moved. That is, it is not necessary to disassemble each bearing type bearing member 155. Further, in this variable stiffness type dynamic vibration absorber, the flat spring 130 can be inserted from the first opening 174A and can be connected to the first support member 153 and the second support member 175 by the fixing bolt 161, respectively. In this way, this variable stiffness type dynamic vibration absorber can easily replace only the flat spring 130 when a fault occurs in the flat spring 130 or the like.

  In this variable stiffness type dynamic vibration absorber, the flat springs 130 ensure the necessary dimensional accuracy and are processed to have a uniform spring constant as a whole, so that the rigidity of the pair of flat springs 130 attached can be the same. it can. For this reason, in this variable stiffness type dynamic vibration damping device, the natural frequency smoothly changes as the rotation angle of the flat spring 130 increases, and the natural frequency can be adjusted finely and accurately, thereby damping the vibration. Can be satisfactorily controlled in the entire frequency range.

  This variable stiffness type dynamic vibration absorber can be easily replaced with a flat spring 130 having different rigidity. For this reason, this variable stiffness type dynamic vibration absorber can change the range of the natural frequency that can be adjusted by replacing the plate spring 130 with a different plate thickness, and the frequency range in which vibration can be controlled can be easily achieved. Can be changed.

In this variable rigidity type dynamic vibration absorber, when the damping body 190 is sandwiched between the base 111 and the weight main body 171 of the vibration absorber main body 110, the vibration damping effect is slightly reduced, but even if the tuning is slightly shifted, it is not shifted. The vibration suppression effect substantially the same as the case can be ensured (robustness is ensured), and the resonance amplitude can also be reduced. That is, stable vibration suppression can be performed with respect to changes in the vibration of the vibrating body 1. In addition, fatigue failure of the flat spring 130 can be prevented.

  As described above, the variable stiffness type dynamic vibration damping device of the second embodiment also has a wide frequency range that can be damped and can be damped well.

  Further, in this variable stiffness type dynamic vibration absorber, the flat spring 130 is shortened, and only one end of the flat spring 130 is supported by the first support member 153, and the weight member 170 is provided at the other end of the flat spring 130. Since it is made to support, compactness can be achieved.

The present invention is not limited to the embodiments described with reference to the above description and drawings. For example, the following embodiments are also included in the technical scope of the present invention.
(1) In Examples 1 and 2, the rigid body is a flat spring, but the rigid body may have an elliptical shape, a rhombus shape, or a hollow section in the short direction.
(2) In Examples 1 and 2, the flat spring rotates around the virtual center line of the flat spring or the virtual parallel line close to the virtual center line (passing through the flat spring) as the rotation axis, but the virtual parallel separated from the flat spring The flat spring may rotate with the wire as the axis of rotation.
(3) In Examples 1 and 2, the attenuation body is provided, but the attenuation body may not be provided.
(4) In Examples 1 and 2, a plurality of additional masses having the same shape and the same mass could be stacked and attached to the weight body. You may attach to.
(5) In Example 1, both ends and the center of the flat spring are fixed with two fixing bolts. However, both ends and the central of the flat spring may be fixed with one fixing bolt.

  The present invention can be used for automobiles, automobile brakes, rolling mills, paper machines, textile machines, machine tools, and the like.

DESCRIPTION OF SYMBOLS 1 ... Vibrating body 10, 110 ... Vibration absorber main body 30, 130 ... Flat spring (rigid body)
50, 150 ... Rotating device 70, 170 ... Weight member 90, 190 ... Attenuator 95 ... Additional mass

Claims (5)

A vibration absorber body to be attached to the vibrating body;
A pair of rigid bodies having the same rigidity and formed long,
Each of the rigid bodies has a rigid body support tool that detachably supports an end of the rigid body and is rotatably attached to the vibration absorber body, and each virtual center line extending in the longitudinal direction of the rigid body Arranged in parallel on the same orthogonal plane with respect to the linear vibration direction of the vibrating body, and the rigid bodies are in opposite directions to each other in a plane-symmetric state with these virtual center lines or virtual parallel lines parallel to these virtual center lines as rotation axes A rotating device for rotating
A weight main body and each rigid body detachably supported in a rotatable state with the virtual center line or the virtual parallel line as a rotation axis, and a weight support tool rotatably attached to the weight main body. A weight member;
A variable-rigidity dynamic vibration absorber characterized by comprising:   The variable stiffness type dynamic vibration absorber according to claim 1, wherein the rigid body is a flat spring. Variable stiffness type dynamic vibration absorber according to claim 1, wherein the exchange in flat plate spring plate thickness of the rigid body you differences.   The variable stiffness type dynamic vibration absorber according to any one of claims 1 to 3, further comprising an additional mass that can be attached to and detached from the weight member.   The variable stiffness type dynamic vibration absorber according to claim 1, further comprising an attenuation body interposed between the vibration absorber body and the weight member.

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