JP6215436B2 - Damper device - Google Patents

Description

  The present invention relates to a damper device used for the purpose of damping vibrations and shocks.

  A damper device is generally used as a device for damping the vibration of a structure. For example, Patent Document 1 discloses a technique related to a rotary inertia mass damper. The rotary inertia mass damper is interposed between two members that are close to and away from each other in a building or the like. A force corresponding to the relative acceleration in the displacement direction generated between the two members is generated by the rotary inertia mass damper, and vibration is suppressed.

  In addition, unlike a heavy-weight building or the like as described above, there is also a damper device that is used for buffering vibrations and shocks of equipment of about several tens of kg. The damper device is fixed to each other via a spring having elasticity between the shock absorbing device and another sufficiently robust device. And by using the said damper apparatus, the vibration and impact which a buffer object apparatus receives, and the collision with another apparatus can be avoided.

JP 2010-255752 A

  Since the damper device according to Patent Document 1 is configured for the purpose of suppressing vibrations of buildings that are considerably heavy, even if used for suppressing vibrations of equipment of about several tens of kg, it does not operate normally. Also lacks responsiveness.

  Therefore, there is a demand for a damper device having a simple configuration that can suppress vibration of equipment of about several tens of kg.

  In addition, for the purpose of suppressing vibrations of equipment of about several tens of kg, it is conceivable to employ a damper device using a spring as described above. The damper device has a damping force function for suppressing the elastic displacement of the spring in order to converge the elastic displacement of the elastic spring in a shorter time.

  However, the damping force of the damper device is selected according to the mass of the shock absorbing device, the amount of expansion / contraction displacement of the spring, and the periodic vibration, and is fixed at the set value. Therefore, it has been difficult to obtain an optimal vibration suppression effect for different vibration modes.

  Then, an object of this invention is to provide the damper apparatus of a simple structure which can suppress the vibration suppression of about several dozen kg of apparatus. More preferably, an object of the present invention is to provide a damper device that can exhibit an optimum vibration suppression effect for different vibration modes.

  In order to achieve the above object, a damper device according to the present invention includes a first inner member having a columnar shape, a second inner shape that is cylindrical and is disposed to face the first inner member. And the elastic member disposed between the first inner member and the second inner member, and the elastic member disposed between the first inner member and the second inner member. A cylindrical outer member surrounding the first inner member, the second inner member, and the elastic member, and the first inner member and the second inner member. A protrusion provided on at least one outer surface portion of the material, and a spiral groove formed through the side surface of the outer member to guide the protrusion. The spiral movement is possible along the groove.

  The damper device according to the present invention includes a cylindrical first inner member, a cylindrical second member disposed opposite to the first inner member, and the first inner member. And the elastic member disposed between the second inner member and the elastic member disposed between the first inner member and the second inner member. A cylindrical outer member surrounding at least one inner member, the second inner member, and the elastic member, and at least one outer surface portion of the first inner member and the second inner member. And a spiral groove formed through the side surface of the outer member to guide the protrusion, and the protrusion can be spirally moved along the groove. It is.

  Therefore, the linear motion generated by the approach and separation of the first inner member and the second inner member can be converted into the rotational motion of the outer member, and vibrations and impacts that cause the approach and separation can be suppressed. Furthermore, the vibration and impact are buffered by the expansion / contraction displacement of the elastic member connected and fixed to the first inner member and the second inner member. In addition, a spiral groove is formed in the outer member, and the protrusion moves along the groove, thereby realizing a rotary inertia mass damper device. Therefore, it is possible to suppress the vibration suppression of the equipment of about several tens of kg by a damper device with a simple configuration.

It is a figure which shows the structure of the damper which concerns on embodiment. It is a figure which shows the structure of the damper which concerns on embodiment. It is a figure which shows the structure of the damper which concerns on embodiment. It is an exploded view which shows the structure of the damper which concerns on embodiment. It is a figure which shows a mode that the pin 13U is fixed with respect to the 1st inner member 12. FIG. It is a figure which shows a mode that the pin 13U is fixed with respect to the 1st inner member 12. FIG. It is a figure which shows the other structure aspect of the damper apparatus which concerns on this invention. It is an exploded view which shows the other structure aspect of the damper apparatus which concerns on this invention. It is a figure which shows a mode that the inclination of the spiral winding in the groove | channel 33R is changing. It is an enlarged view which shows a mode when the inclination of the winding of the spiral in the groove | channel 33R is large. It is an enlarged view which shows a mode in case the inclination of the spiral of the groove | channel 33R is small. It is sectional drawing which shows a mode that the damper apparatus used as the comparison object of this invention is arrange | positioned. It is a figure used when explaining operation | movement and an effect of the damper apparatus which concerns on this invention. It is a figure used when explaining operation | movement and an effect of the damper apparatus which concerns on this invention. It is a figure used when explaining operation | movement and an effect of the damper apparatus which concerns on this invention. It is an enlarged view used when explaining operation | movement and an effect of the damper apparatus which concerns on this invention. It is an enlarged view used when explaining operation | movement and an effect of the damper apparatus which concerns on this invention. It is a figure used when explaining operation | movement and an effect of the damper apparatus which concerns on this invention.

  Hereinafter, the present invention will be specifically described with reference to the drawings showing embodiments thereof.

<Embodiment>
1-4 is a figure which shows the structure of the damper apparatus which concerns on embodiment of this invention. Here, FIG. 2 is a diagram illustrating a state in which the structure of FIG. 1 is viewed from the side. FIG. 3 is a diagram illustrating a state in which the structure of FIG. 1 is viewed from above (or downward). Further, FIG. 4 is an exploded view of the structure of FIG. Hereinafter, based on the said FIGS. 1-4, the structure of the damper apparatus which concerns on this Embodiment is demonstrated.

  1-4, the damper device according to the present embodiment includes a columnar first inner member 12, a columnar second inner member 22, a cylindrical outer member 31, a weight 32, and elasticity. It has the spring 41 which is a member.

  A base end portion 11 is fixed to the upper portion of the first inner member 12. Here, the first inner member 12 and the base end portion 11 may be integrally formed. Further, a rod-shaped shaft 14 is fixedly disposed at the lower portion of the first inner member 12 (that is, the end of the first inner member 12 on the side where the second inner member 22 is disposed). Yes. Here, the first inner member 12 and the shaft 14 may be integrally formed. Further, a pin (which can be grasped as the first protrusion) 13U which is a protrusion is disposed on the outer surface portion of the first inner member 12. Here, the pin 13 </ b> U is detachable with respect to the first inner member 12.

  FIG. 5 is a view showing a state in which the first inner member 12 and the pin 13U are removed. FIG. 6 is an enlarged view showing a state in which the pin 13U is attached to the first inner member 12.

  The pin 13U is a screw type pin and includes a head portion 13a and a screw portion 13b. Further, a hole through which the pin 13U is inserted is formed in the side surface portion of the first inner member 12. Here, when the pin 13U is attached to the first inner member 12, the hollow cylindrical member 5 is interposed between the pin 13U and the first inner member 12.

  That is, when the pin 13U is attached to the first inner member 12, the screw portion 13b of the pin 13U is inserted into the hollow portion of the cylindrical member 5, and then the screw portion 13b is drilled in the first inner member 12. Through the hole. Then, the pin 13U is fixed to the first inner member 12 by screw tightening. As shown in FIG. 6, in a state where the pin 13U is fixed to the first inner member 12, the cylindrical member 5 is disposed between the first inner member 12 and the head 13a of the pin 13U. Yes.

  Actually, as shown in FIGS. 1 and 2, the pin 13 </ b> U is fixed to the first inner member 12 in a state where the first inner member 12 and the outer member 31 are assembled. Therefore, although not shown in FIG. 6, a groove 33 </ b> R provided in the outer member 31 exists on the outer peripheral portion of the cylindrical member 5.

  Further, as shown in FIG. 3, the pins 13U are fixed to the first inner member 12 at four locations. Here, the height positions of the arranged pins 13U are uniform, and the pins 13U are arranged evenly (every 90 °) along the outer peripheral portion of the first inner member 12.

  As can be seen from FIGS. 1, 2, and 4, in the assembled state of the damper device according to the present embodiment, the first inner member 12 and the second inner member 22 face each other with an interval in the vertical direction. Be placed.

  A base end portion 21 is fixed to the lower portion of the second inner member 22. Here, the second inner member 22 and the base end portion 21 may be integrally formed. Further, from the upper part of the second inner member 22 (that is, the end of the second inner member 22 on the side where the first inner member 12 is disposed) toward the inside of the second inner member 22, A guide hole 24 that guides the shaft 14 is disposed inside the second inner member 22. Further, a pin (which can be grasped as the second protrusion) 13 </ b> D which is a protrusion is disposed on the outer surface portion of the second inner member 22. Here, the pin 13 </ b> D is detachable with respect to the second inner member 22.

  As described with reference to FIGS. 5 and 6, the structure of the pin 13D is the same as that of the pin 13U, and the method of attaching the pin 13D to the second inner member 22 is the same as that of the first inner member. 12 is the same as the method of attaching to 12.

  That is, when the pin 13D is attached to the second inner member 22, the screw portion 13b of the pin 13D is inserted into the hollow portion of the cylindrical member 5, and then the screw portion 13b is drilled in the second inner member 22. Through the hole. Then, the pin 13D is fixed to the second inner member 22 by screw tightening.

  In practice, as shown in FIGS. 1 and 2, the pin 13 </ b> D is fixed to the second inner member 22 in a state where the second inner member 22 and the outer member 31 are assembled. Therefore, although not shown in FIG. 6, a groove 33 </ b> L provided in the outer member 31 exists on the outer peripheral portion of the cylindrical member 5.

  Further, as shown in FIG. 3, the pins 13 </ b> D are fixed to the second inner member 22 at four locations. Here, the height positions of the disposed pins 13D are uniform, and the respective pins 13D are disposed evenly (every 90 °) along the outer peripheral portion of the second inner member 22.

  As can be seen from FIGS. 1, 2, and 4, in the assembled state of the damper device according to the present embodiment, the spring 41, which is an elastic member, is arranged between the first inner member 12 and the second inner member 22. Established. That is, one end of the spring 41 is connected to the lower part of the first inner member 12, and the other end of the spring 41 is connected to the upper part of the second inner member 22.

  Here, the shaft 14 is disposed at the center of the lower surface of the first inner member 12, but in the configuration example shown in FIGS. 1, 2, and 4, one spring 41 is provided outside the shaft 14. It is arranged. However, two or more springs 41 may be disposed outside the shaft 14. As shown in FIGS. 7 and 8, the spring 41 may be disposed between the first inner member 12 and the second inner member 22 so that the shaft 14 is inserted into the spring 41. good. That is, the spring 41 may be disposed between the first inner member 12 and the second inner member 22 so as to surround the shaft 14 from the outside (see FIGS. 7 and 8).

  As can be seen from FIGS. 1, 2, and 4, in the assembled state of the damper device according to the present embodiment, the outer member 31 is near the lower portion of the first inner member 12, near the upper portion of the second inner member 22 and the spring. 41 is enclosed from the outside.

  The external material 31 is cylindrical. When the damper device is assembled, the lower region of the first inner member 12 (the first inner member 12 on the side where the shaft 14 is disposed) is inserted from one end of the hollow portion of the outer member 31. Is done. In contrast, the upper region of the second inner member 22 (the second inner member 22 on the side where the guide hole 24 is formed) is inserted from the other end of the hollow portion of the outer member 31. Here, in the assembled state of the damper device, the spring 41 disposed between the first inner member 12 and the second inner member 22 is disposed in the outer member 31 (FIGS. 1, 2, and 3). 4, 7, 8).

  As shown in FIGS. 1, 2, and 4, a ring-shaped weight 32 is disposed on the outer side surface portion (side surface portion of the cylinder) of the outer member 31. Specifically, a weight 32 is disposed in the central region in the length direction of the cylindrical outer member 31. Here, the weight 32 is disposed so as to surround the central region of the outer member 31, and is fixed to the outer member 31. The weight 32 may be detachable from the outer member 31 (even in this case, the weight 32 is fixedly attached to the outer member 31).

  As shown in FIGS. 1, 2, and 4, spiral grooves 33 </ b> R and 33 </ b> L are formed on the side surface of the outer member 31. The grooves 33R and 33L are formed so as to penetrate the side surface portion of the outer member 31, and the pins 13U and 13D penetrate the grooves 33R and 33L from the inner side to the outer side of the outer member 31. . The grooves 33R and 33L guide the movement of the pins 13U and 13D. That is, the pins 13U and 13D can spirally move along the grooves 33R and 33L.

  The groove 33R (hereinafter referred to as the first groove portion 33R) is formed on the side surface portion of the outer member 31 on the first inner member 12 arrangement side with the weight 32 interposed therebetween. On the other hand, the groove 33L (hereinafter referred to as the second groove portion 33L) is formed on the side surface portion of the outer member 31 on the second inner member 22 arrangement side with the weight 32 interposed therebetween. The pin 13U is inserted through the first groove 33R, and the pin 13D is inserted through the second groove 33L.

  Here, the spiral winding direction of the first groove 33R is opposite to the spiral winding direction of the second groove 33L. In the configuration example of FIGS. 1, 2, and 4, the first groove portion 33R is a right-handed winding (Z winding), and the second groove portion 33L is a left-handed winding (S winding).

  Further, the inclination of the grooves 33R and 33L may be constant, but in the present embodiment, the inclination of the spiral winding of the grooves 33R and 33L is changed (see FIGS. 1, 2 and 4). 9 is an enlarged view of the first groove portion 33R, FIG. 10 is an enlarged view of a portion A surrounded by a round dotted line in FIG. 9, and an enlarged view of a portion B surrounded by a round dotted line in FIG. FIG. As can be seen from FIGS. 9 to 11, the inclination of the winding of the first groove part 33 </ b> R in the A part is larger than the inclination of the winding of the first groove part 33 </ b> R in the B part. 9 to 11 show enlarged views of the first groove portion 33R, the winding inclination also changes in the second groove portion 33L (see FIGS. 1, 2, and 4).

  The assembled damper device shown in FIGS. 1 and 2 is fixedly disposed between the device and the fixing portion (bottom surface, wall surface, etc.) and between the device and the device. Here, the said fixed arrangement | positioning is realizable by fixing the base end parts 11 and 12 to an apparatus etc.

  It is assumed that vibration and impact occur in a state where the damper device is fixedly disposed on the device or the like. Then, the vibration and impact act on the base end portions 11 and 21 and are buffered by the expansion and contraction displacement of the spring 41 connected and fixed to the first inner member 12 and the second inner member 22. At this time, the first inner member 12 and the second inner member 22 perform linear motions such that they are close to and away from each other. In the linear motion, the shaft 14 disposed in the first inner member 12 slides along the guide hole 24 in the linear direction drilled in the second inner member 22.

  Then, with the linear motion, the pin 13U fixed to the first inner member 12 spirally rotates along the first groove portion 33R, and the pin 13D fixed to the second inner member 22 It spirally rotates along the groove 33L.

  That is, when vibration or impact is generated, the first inner member 12 and the second inner member 22 perform linear motions such that they are close to and away from each other, and the linear motion causes the outer member 31 to rotate. In other words, the linear motion of the first inner member 12 and the second inner member 22 is converted into the rotational motion of the outer member 31.

  As described above, in the damper device according to the present embodiment, the outer member 31 is such that the spring 41 is disposed between the first inner member 12 and the second inner member 22. The components 12, 22, 41 are enclosed from the outside. Of the first inner member 12 and the second inner member 22, pins 13U and 13D are disposed on at least one outer surface portion, and the pins 13U and 13D are disposed on the side surface portion of the outer member 31. Helical grooves 33R and 33L are formed.

  Therefore, the linear motion generated by the proximity and separation of the first inner member 12 and the second inner member 22 can be converted into the rotational motion of the outer member 31, and vibration and impact that cause the proximity and separation can be suppressed. Can do. Furthermore, the vibration and impact are buffered by the expansion and contraction of the spring 41 connected and fixed to the first inner member 12 and the second inner member 22.

  In the damper device according to the present embodiment, spiral grooves 33R and 33L are formed in the outer member 31, and the pins 13U and 13D move along the grooves 33R and 33L. The device is realized. Therefore, it is possible to suppress the vibration suppression of the equipment of about several tens of kg by a damper device with a simple configuration.

  In the damper device according to the present embodiment, the weight 32 is disposed on the outer surface portion of the outer member 31. Therefore, the moment of inertia in the rotational movement of the outer member 31 can be made larger than that in the case of the outer member 31 alone. Therefore, the damping force that suppresses the linear motion of the first inner member 12 and the second inner member 22 can be increased. Here, by adopting the weight 32 that can be removed from the outer member 31, the weight 32 having a different weight and diameter can be attached to and detached from the outer member 31, and the damping force can be adjusted.

  Further, unlike the configuration example shown in FIGS. 1, 2, and 4, the outer member 31 is provided with only one spiral groove 33R (or 33L), and only the first inner member 12 is provided. Only the pin 13U is arranged, and the second inner member 22 is not provided with the pin 13D (or only the second inner member 22 is provided with only the pin 13D, The inner member 12 may have a configuration in which the pin 13U is not disposed.

  On the other hand, as described above, the weight 32 is disposed in the central region of the outer member 31, and the first groove portion 33R and the second groove portion 33L are formed in the outer member 31 with the weight 32 interposed therebetween. The inner member 12 is provided with a pin 13U, the second inner member 22 is provided with a pin 13D, the pin 13U is inserted through the first groove 33R, and the pin 13D is inserted through the second groove 33L. By adopting, the following effects can be achieved.

  That is, the force exerted on the outer member 31 is distributed between the pin 13U and the pin 13D, and a damper device having high vibration and impact resistance can be provided. In addition, the number of pins 13U and 13D can be increased from the viewpoint of dispersion of the force. Here, when the plurality of pins 13U and the plurality of pins 13D are disposed, they are equally disposed along the circumference of the first inner member 12 and along the circumference of the second inner member 22. It is desirable to do.

  The spiral winding direction of the first groove portion 33R and the spiral winding direction of the second groove portion 33L may be the same direction. However, in the damper device according to the present embodiment, the spiral direction of the first groove portion 33R is the same. The winding direction and the spiral winding direction of the second groove portion 33L are opposite to each other.

  Thus, the first groove portion 33R and the second groove portion 33L are made the outer member 31 by reversing the spiral winding direction of the first groove portion 33R and the spiral winding direction of the second groove portion 33L. Even if it arrange | positions, the strength reduction of the said outer member 31 can be suppressed.

  In addition, a configuration without the shaft 14 and the guide hole 24 can be adopted. However, in the damper device according to the present embodiment, the rod-like shaft 14 is provided in the first inner member 12, and the second inner member is provided. A guide hole 24 for guiding the shaft 14 is provided in the interior 22.

  As described above, by adopting the configuration in which the shaft 14 and the guide hole 24 are provided, it is possible to smoothly guide the linear motion generated by the proximity and separation of the first inner member 12 and the second inner member 22, and the operation It is possible to provide a stable damper device.

  Further, in the damper device according to the present embodiment, as described with reference to FIGS. 9 to 11, the inclination of the spiral winding in the grooves 33R and 33L is changed. Therefore, it is possible to provide a damper device that can exhibit an optimum vibration suppression effect for different vibration modes. In other words, the damping force that suppresses the linear motion can be adjusted by the inclination angle of the grooves 33R and 33L, and therefore can be arbitrarily set within the expansion movable range of the first inner member 12 and the second inner member 22. It is possible to provide a damper device that can freely obtain a damping force pattern. Hereinafter, details of the effect will be described in detail with reference to the drawings.

  FIG. 12 is a cross-sectional view showing a state in which a damper device to be compared with the damper device according to the present invention is attached. As shown in FIG. 12, a spring 141 and a damper device 101 to be compared are disposed and fixed between a base 102 that receives vibration and impact and a buffer target device 103.

  FIGS. 13, 14 and 15 are diagrams showing the waveforms obtained from the configuration shown in FIG. Specifically, FIG. 13 is a waveform in which the displacement amount of the base 102 is shown on the vertical axis and the passage of time is shown on the horizontal axis. FIG. 14 is a waveform in which when the damping force of the damper device 101 is high, the amount of displacement of the buffer target device 103 is plotted on the vertical axis and the passage of time is plotted on the horizontal axis. FIG. 15 is a waveform in which when the damping force of the damper device 101 is low, the amount of displacement of the buffer target device 103 is plotted on the vertical axis and the passage of time is plotted on the horizontal axis.

  When the damping force of the damper device 101 is high, the operation of the damper device 101 is as follows.

  With respect to a high displacement amount of the base 102 (displacement amount W1 surrounded by a dotted circle in FIG. 13), the damping amount function of the damper device 101 suppresses a displacement amount (indicated by a dotted circle in FIG. 14). The enclosed displacement W3) is obtained. On the other hand, when the displacement amount of the base 102 converges with time (displacement amount W2 surrounded by a dotted circle in FIG. 13), the damping force effect of the damper device 101 suppresses expansion and contraction of the spring 141. The displacement amount is approximately the same as the displacement amount W2 of the base 102 (displacement amount W4 surrounded by a dotted circle in FIG. 14).

  That is, when the damper device 101 having a high damping force is used, a good buffering effect can be obtained for a large displacement amount W1 of the base 102, but for a small displacement amount W1 of the base 102. A good buffering effect cannot be obtained.

  On the other hand, when the damping force of the damper device 101 is low, the operation of the damper device 101 is as follows.

  For the high displacement amount W1) of the base 102, since the movable amount of the damper device 101 is in a stretchable saturation state, the stretchable displacement of the shock absorbing device 103 is like the displacement amount W5 surrounded by a dotted circle in FIG. Will be saturated. On the other hand, when the displacement amount of the base 102 converges with time (displacement amount W2 surrounded by a dotted circle in FIG. 13), the displacement amount of the buffer target device 103 is suppressed by the expansion / contraction displacement of the spring 41 ( A displacement amount W6) surrounded by a dotted circle in FIG.

  That is, when the damper device 101 having a low damping force is used, a good buffering effect can be obtained for a small displacement amount W1 of the base 102, but for a large displacement amount W1 of the base 102. A good buffering effect cannot be obtained.

  Thus, the damper device 101 cannot exhibit the optimum vibration suppression effect for different vibration modes. The performance of the damper device that can obtain a buffering effect such that the displacement amount of the buffer target device 103 becomes the displacement amount W3 and the displacement amount W6 with respect to the displacement amount (displacement amount W1 and displacement amount W2) of the base 102 serving as a reference. Is required.

  Next, the operation and effect of the damper device according to the present embodiment in which the inclination of the spiral winding in the grooves 33R and 33L is changed will be described.

  FIG. 16 is a view for explaining the operation and effect of the damper device according to the present embodiment, and is an enlarged view of the first groove portion 33R. In the following, the description will be given focusing on the movement of the pin 13U in the first groove 33R, but the movement of the pin 13D in the second groove 33L is the same.

  The pin 13U rotates the outer member 31 along the first groove portion 33R, and the amount of rotation depends on the spiral inclination angle of the first groove portion 33R. For example, as shown in FIG. 16, in the region of the first groove 33R having a large spiral inclination angle, the rotation amount α is obtained according to the inclination angle θ1 of the first groove 33R with respect to the displacement amount δ of the pin 13U. Similarly, as shown in FIG. 17, in the region of the first groove portion 33R having a small spiral inclination angle, the rotation amount β is obtained according to the inclination angle θ2 of the first groove portion 33R with respect to the displacement amount δ of the pin 13U. Here, angle θ1> angle θ2.

  As can be seen from FIGS. 16 and 17, even if the displacement amount δ is the same, since the spiral inclination angle of the first groove portion 33 </ b> R is different, the rotation amount α of the outer member 31 and the rotation amount β of the outer member 31 are different. . Therefore, the rotational inertia obtained when the outer member 31 is rotated gives a low damping force in the region of the first groove 33R having a large helical inclination angle when acting as a damping force given to the displacement amount δ of the pin 13U. In the region of the first groove portion 33R where the spiral inclination angle is small, the operation gives a high damping force.

  It is assumed that the damper device according to the present embodiment is disposed and fixed between a base that receives vibration and shock and a buffer target device. For example, it is assumed that the base end portion 11 of the first inner member 12 is fixed to the buffer target device, and the base end portion 21 of the second inner member 22 is fixed to the base (the reverse is also possible).

  FIG. 18 is a diagram showing a change in the amount of displacement of the buffer target device as a waveform when the damper device according to the present embodiment is applied. In FIG. 18, the amount of displacement of the buffer target device is the vertical axis, and the passage of time is shown on the horizontal axis.

  When the damper device according to the present embodiment is applied, the rotation amount β with respect to the displacement amount δ increases in a region where the spiral inclination angle of the first groove portion 33R in the outer member 31 is small (see FIG. 17). Therefore, in the region where the spiral inclination angle of the first groove 33R is small, the damping force of the damper device according to the present embodiment is high. Therefore, in the region where the spiral inclination angle of the first groove portion 33R is small, the amount of displacement of the buffered device that is suppressed (see FIG. 13) with respect to the high displacement amount of the base (the displacement amount W1 surrounded by the dotted circle in FIG. 13). A displacement amount W7) surrounded by 18 dotted circles is obtained.

  On the other hand, in the region where the spiral inclination angle of the first groove 33R in the outer member 31 is large, the rotation amount α with respect to the displacement amount δ is small (see FIG. 16). Therefore, in the region where the spiral inclination angle of the first groove portion 33R is large, the damping force of the damper device according to the present embodiment is low. Therefore, since the expansion and contraction due to the elasticity of the spring 41 is not hindered, in the region where the spiral inclination angle of the first groove 33R is large, the displacement of the base is small (the displacement W2 surrounded by the dotted circle in FIG. 13). Thus, a suppressed displacement amount (displacement amount W8 surrounded by a dotted circle in FIG. 18) of the buffer target device is obtained.

  Thus, in the damper device according to the present embodiment, the damping force obtained by the rotational inertia of the outer member 31 can be adjusted by the inclination angle of the spiral of the groove 33 in accordance with the magnitude of the displacement amount of the base. It becomes possible. Therefore, the amount of displacement of the buffer target device does not become an expansion / contraction saturation state, and does not hinder expansion / contraction due to the elasticity of the spring 41 with a high attenuation. Therefore, as described above, the damper device according to the present embodiment can exhibit an optimum vibration suppression effect for different vibration modes.

  Here, when the damping amount (inertia) of the damper device is small, the displacement amount of the linear motion of the first inner member 12 and the second inner member 22 increases, and the damping amount (inertia) of the damper device is large. In this case, the displacement amount of the linear motion of the first inner member 12 and the second inner member 22 is small. In the initial stage of impact and vibration, the amount of displacement is set to a small amount, and further, the amount of displacement increases due to the addition of impact and vibration, and the greater the amount of attenuation, the more the first inner member 12 and the second inner member 22 are. It is possible to provide a damper device that can freely obtain an arbitrary damping force pattern within the expansion and contraction movable range.

  Therefore, as the damper device, before reaching the limit of approaching / separating between the first inner member 12 and the second inner member 22 (extension or contraction, that is, expansion / contraction limit), the damper device is displaced with a larger attenuation. It is desirable to compete. That is, when the spiral inclination angles of the grooves 33R and 33L are formed with a larger spiral inclination angle (FIG. 16) and a smaller spiral inclination angle (FIG. 17) as described with reference to FIGS. The initial position is set so that the pins 13U and 13D come to the position of a larger spiral tilt angle (FIG. 16), and as the limit of expansion and contraction is approached, the pins 13U and 13D become smaller spiral tilt angles (see FIG. It is desirable to set the shapes of the grooves 33R and 33L and the initial positions of the pins 13U and 13D so as to be the position 17).

  As described above, in the damper device according to the present invention, the damping force function for suppressing the expansion and contraction displacement is realized with a simple structure for adjusting the rotation inertia and the rotation amount based on the hardness selection of the spring 41 having elasticity. Can do. Therefore, in the buffering measures by the damper device, appropriate measures can be easily taken in accordance with the mass of the target device, the amount of vibration and impact received, and the cycle.

5 Cylindrical members 11, 21 Base end portion 12 First inner member 13U, 13D Pin 13a Head portion 13b Screw portion 14 Shaft 22 Second inner member 24 Guide hole 31 External material 32 Weight 33R First groove portion 33L Second groove portion Groove 41 Spring

Claims (5)

A cylindrical first inner member;
A second inner member that is cylindrical and disposed opposite the first inner member;
An elastic member disposed between the first inner member and the second inner member;
In a state where the elastic member is disposed between the first inner member and the second inner member, the first inner member, the second inner member, and the elastic member are externally connected. An outer member that surrounds and is tubular,
Of the first inner member and the second inner member, a protrusion disposed on at least one outer surface portion; and
A spiral groove formed through the side surface of the outer member to guide the protrusion, and the protrusion is capable of spiral movement along the groove.
A damper device characterized by that. A weight disposed on the outer surface of the outer member;
The damper device according to claim 1. The weight is
Disposed in the central region of the outer member;
The protrusion is
A first protrusion disposed on the first inner member;
A second protrusion disposed on the second inner member;
The groove is
A first groove formed on the side surface of the outer member on the first inner member arrangement side across the weight;
A second groove formed on the side surface of the outer member on the second inner member arrangement side across the weight;
The first protrusion is
Inserted through the first groove,
The second protrusion is
Inserted through the second groove,
The damper device according to claim 2. The spiral winding direction of the first groove is
Opposite to the spiral winding direction of the second groove,
The damper device according to claim 3. The groove is
The inclination of the spiral turns,
The damper device according to any one of claims 1 to 4, wherein the damper device is provided.

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