TW201839288A - Damper - Google Patents

Abstract

A damper which can successfully generate damping force and easily adjust the damping force is provided. The damper includes a cylinder 10, a rod 50, elastomer particles 90, and a magnetic field generating unit 20. The rod 50 which is reciprocally movable in an axial direction or rotatable around an axis projects outside from the cylinder 10. The elastomer particles 90 have characteristics of a permanent magnet and elasticity and a plurality of elastomer particles 90 are filled in the cylinder 10. The magnetic field generating unit 20 generates a predetermined magnetic field in the cylinder 10.

Description

   Damper   

The invention relates to a damper.

Patent Document 1 discloses a conventional damper. This damper has a structure in which a granular body, that is, a steel ball is filled in a space surrounded by a cylinder body and a pair of covers, and the piston is filled with the granular body relative to the cylinder with the movement of the rod. Relative displacement. A pair of lid bodies are often provided with potential energy by a pair of springs in a direction in which the volume of the space in which the granular bodies are housed decreases. An electromagnet is provided on the outer periphery of the cylinder. If this damper displaces the rod so that the piston is relatively displaced with respect to the cylinder, the granular bodies flow along with the movement of the piston, and are generated by the friction between the granular bodies or between the granular bodies and the piston, etc. Attenuation. Specifically, if the force required for the granular body to flow is larger than the force of the lid body being added with potential energy from the spring, the lid body will be displaced to a position where this force and the lid body are balanced by the force of potential force added from the spring. If the cover body is displaced, the volume in the shell filled with the granular body is increased, and a void is generated in the cylinder body. As a result, the damper promotes the flow of the granular body, and the piston pushes the granular body away and moves to generate a damping force. In addition, if a current flows to the electromagnet of the damper, the binding force of the granular body in the direction along the direction of the magnetic field lines of the electromagnet can be enhanced. As a result, the friction between the granular bodies is increased, and the damping force of the damper is also increased. Therefore, by controlling the magnitude of the current flowing through the electromagnet, the damper can change the characteristics of the generated damping force.

    [Prior technical literature]         [Patent Literature]    

Patent Document 1: Japanese Patent Laid-Open No. 2011-21648

However, the damper of Patent Document 1 is a steel ball filled with granular bodies inside the cylinder. Steel balls are not flexible. Therefore, the granular bodies compressed by a pair of lids may cause sintering of adjacent granular bodies. As a result, the damper will not be able to make the granular body flow in the cylinder, which may hinder the movement of the piston, so that no damping force can be generated.

The present invention has been completed in view of the above-mentioned conventional actual situation, and the problem to be solved is to provide a damper that can generate the damping force well and can easily adjust the magnitude of the generated damping force.

The damper of the present invention includes a housing, a rod, particles, and a magnetic field generating section. A rod that can move freely back and forth in the axial direction or can rotate freely about the shaft is protruded from the shell to the outside. The particles have the characteristics and elasticity of a permanent magnet, and a plurality of particles are filled in the shell. The magnetic field generating unit generates a predetermined magnetic field inside the casing.

This damper will elastically deform a plurality of particles with the characteristics and elasticity of a permanent magnet filled in the housing when the rod moves back and forth or rotates around the axis. The damper generates a damping force by the frictional force of the particles or the elastic reaction force of the particles. In addition, since the particles have elasticity, it is difficult for the particles to sinter each other because the adjacent particles are elastically deformed to each other. In addition, by using the magnetic field generated in the housing by the magnetic field generating portion and the characteristics of the permanent magnets possessed by each particle, the binding force between the plurality of particles can be enhanced. As a result, the frictional force between the plurality of particles becomes larger, and the damping force of the damper also increases accordingly.

Therefore, the damper of the present invention can generate a damping force well, and the damping force can be easily adjusted.

The magnetic field generating portion of the damper of the present invention can freely change the strength of the magnetic field generated in the casing. In this case, if the damper changes the strength of the magnetic field generated by the magnetic field generating unit, the binding force between the particles will change, and the magnitude of the damping force can be easily changed to the desired magnitude.

The damper of the present invention may include a piston, which is arranged in the housing and connected to a rod capable of freely reciprocating in the axial direction, and can move back and forth in the housing together with the rod. In this case, the piston moves the particles filled in the casing away. Therefore, this damper can produce a greater damping force than would be the case without a piston.

The damper of the present invention may include a rotor, which is arranged in the housing and connected to a rod that can rotate freely about an axis, and can be rotated together with the rod in the housing. In this case, when the rod and the rotor are rotated around the axis, the particles filled in the casing are elastically deformed. The friction force of the particles generated by this time or the elastic reaction force of the particles can generate a damping force in a direction opposite to the direction in which the rod and the rotor rotate.

The piston may have the characteristics of a permanent magnet. In this case, in this damper, since the friction between the piston having the characteristics of a permanent magnet and the particles abutting on the surface of the piston becomes larger, the damping force of the damper can be further increased.

The rotor may have the characteristics of a permanent magnet. In this case, since the friction between the rotor having the characteristics of a permanent magnet and the particles abutting on the surface of the rotor becomes larger in this damper, the damping force of the damper can be further increased.

1, 11, 21, 31, 41, 51‧‧‧ dampers

10, 110‧‧‧ Cylinder block (shell)

10A, 110A‧‧‧ Open end

20, 120, 220, 320‧‧‧‧ Magnetic field generation unit

30, 130, 230‧‧‧ Pistons

30A‧‧‧Central Section

30B‧‧‧ both ends

40, 140, 240‧‧‧ rotor

40A, 140A, 240A‧‧‧ Central

40B‧‧‧First end

40C‧‧‧ 2nd end

40D‧‧‧The first plane

40E‧‧‧The second plane

45, 145‧‧‧magnets

50, 150, 250, 350‧‧‧ par

60‧‧‧Sealed Bearing

70, 170‧‧‧ lever guide

70A‧‧‧through hole

70B‧‧‧ 锷 部

80‧‧‧thrust bearing

90‧‧‧ elastomer particles (particles)

90A‧‧‧Neodymium particles

110A‧‧‧ open end

171‧‧‧1st rod guide

171A‧‧‧The first through hole

171B‧‧‧The first abutment

172‧‧‧ 2nd Rod Guide

172A‧‧‧The second through hole

172B‧‧‧The second abutment

173‧‧‧3rd rod guide

173A‧‧‧3th through hole

173B‧‧‧The third contact section

174‧‧‧4th bar guide

174A‧‧‧4th through hole

174B‧‧‧The fourth abutment

Fig. 1 is a sectional view showing a damper according to the first embodiment.

FIG. 2 is a schematic diagram of a granular body filled in the outer shell of the damper of Embodiment 1. FIG.

FIG. 3 is a graph showing the magnitude of the magnetic flux density near the central axis of the cylinder when the magnitude of the current flowing through the magnetic field generating portion of the damper of Embodiment 1 is changed for each predetermined magnitude; and (A) shows the magnitude of the magnetic flux density in the direction of the central axis of the cylinder, and (B) shows the magnitude of the magnetic flux density in the direction (radiation direction) orthogonal to the central axis of the cylinder.

FIG. 4 is a diagram showing a case where a magnitude of a current (hereinafter, referred to as a frequency) is changed for each predetermined magnitude when a magnitude of a current flowing through a magnetic field generating section of the damper of Embodiment 1 is changed for each predetermined magnitude; A graph showing the relationship between the displacement of the rod relative to the cylinder and the damping force during the change. The above-mentioned speed is the speed when the rod is reciprocated in the direction of the central axis of the cylinder, and (A) shows the flow in When the magnitude of the current flowing through the magnetic field generating section is 0A, (B) shows the magnitude of the current flowing through the magnetic field generating section is 2A, (C) shows the magnitude of the current flowing through the magnetic field generating section is 4A, (D) ) Shows the case where the magnitude of the current flowing through the magnetic field generating section is 6A.

FIG. 5 is a graph showing the relative frequency when the magnitude of the current flowing through the magnetic field generating portion of the damper of the first embodiment is 0, 3, and 6A, and the frequency is changed every 1 Hz between 1 and 5 Hz. A graph of the magnitude of the attenuation energy of frequency.

FIG. 6 shows the amount of displacement and attenuation of the rod relative to the cylinder when the magnitude of the current flowing through the magnetic field generating portion of the damper of Embodiment 1 is changed at each predetermined size at a frequency of 1 Hz. (A) shows the case where the magnitude of the current flowing through the magnetic field generating section is 0, 1, 2, 3A, and (B) shows the magnitude of the current flowing through the magnetic field generating section, 3, 4, and In the case of 5, 6A, (C) shows the case where the magnitude of the current flowing through the magnetic field generating section is 0, 3, and 6A.

FIG. 7 shows the displacement and damping force of the rod relative to the cylinder when the magnitude of the current flowing through the magnetic field generating portion of the damper of Embodiment 1 is changed at each predetermined size at a frequency of 3 Hz. (A) shows the case where the magnitude of the current flowing through the magnetic field generating section is 0, 1, 2, 3A, and (B) shows the magnitude of the current flowing through the magnetic field generating section, 3, 4, and In the case of 5, 6A, (C) shows the case where the magnitude of the current flowing through the magnetic field generating section is 0, 3, and 6A.

FIG. 8 shows the displacement and damping force of the rod relative to the cylinder when the magnitude of the current flowing through the magnetic field generating portion of the damper of Embodiment 1 is changed at each predetermined size at a frequency of 5 Hz. (A) shows the case where the magnitude of the current flowing through the magnetic field generating section is 0, 1, 2, 3A, and (B) shows the magnitude of the current flowing through the magnetic field generating section, 3, 4, and In the case of 5, 6A, (C) shows the case where the magnitude of the current flowing through the magnetic field generating section is 0, 3, and 6A.

FIG. 9 shows the magnitude of the attenuation energy when the magnitude of the current flowing through the magnetic field generating section is changed between 1 and 6A when the frequency of the damper of Embodiment 1 is 1, 3, and 5 Hz. Graph.

FIG. 10 is a cross-sectional view showing a damper according to the second embodiment, and (A) is a cross-sectional view showing the center axis direction of the rotor, and (B) is a cross-sectional view taken along line A-A in FIG. 10 (A).

11 is a cross-sectional view showing a damper according to Embodiments 3 and 4, and (A) shows a state where a magnet is provided in a piston, and (B) shows a state where a magnet is provided in a rotor.

FIG. 12 is a cross-sectional view showing a damper of another embodiment, and (A) shows a state where a magnetic field generating section is provided in a piston, and (B) shows a plurality of magnetic field generating sections configured in a ring shape in a rotor Situation.

Embodiments 1 to 4 of the damper according to the present invention will be described with reference to the drawings.

    <Embodiment 1>    

As shown in FIG. 1, the damper 1 according to the first embodiment includes a cylinder 10 that is a housing, a piston 30, a rod 50, a pair of rod guides 70, elastomer particles 90 that are a plurality of particles, and a magnetic field generator 20.

The cylinder 10 has a cylindrical shape which is open at both ends. The piston 30 includes a central portion 30A and both end portions 30B. The central portion 30A has a cylindrical shape. Both end portions 30B are in a conical trapezoidal shape in a direction separated from both end surfaces of the central portion 30A and gradually decreasing in outer diameter. A predetermined gap is formed between the outer peripheral surface of the piston 30 and the inner peripheral surface of the cylinder block 10. The piston 30 is disposed in the cylinder block 10.

The rod 50 is formed in a cylindrical shape. The rod 50 is continuous to the front end of both end portions 30B of the piston 30 and extends in both directions of the piston 30. The rod 50 extends along the central axis direction of the cylinder block 10 and protrudes from the open end portions 10A at both ends of the cylinder block 10 toward the outside of the cylinder block 10. That is, the piston 30 is connected to the rod 50. The lever guide 70 is formed in a disc shape having a flange portion 70B on the outer periphery, and is connected to each of the open end portions 10A so as to close each of the open end portions 10A of both end portions of the cylinder block 10. The rod guides 70 are formed at the center of the disc shape and penetrate through the disc-shaped plate thickness direction, and are provided with through holes 70A. The inner diameter of the through-hole 70A is slightly larger than the outer diameter of the rod 50. The through-hole 70A penetrates the central axis direction of the cylinder block 10 in a state where the rod guide 70 is fixed to each of the open end portions 10A at both ends of the cylinder block 10. The rod 50 is inserted through the through-holes 70A of the rod guides 70 reciprocally. Both the rod 50 and the piston 30 can move freely in the cylinder body 10 along the central axis direction of the cylinder body 10. The cylinder 10, the piston 30, the rod 50, and the pair of rod guides 70 are non-magnetic bodies.

As shown in FIG. 2, the plurality of elastomer particles 90 are spherical. These elastomer particles 90 are elastomers made of silicone rubber having a durometer type A hardness (hereinafter referred to as hardness) of 60. The elastomer particles 90 include neodymium (Nd) particles 90A. The amount of the neodymium (Nd) particles 90A contained in the elastomer particles 90 is about 60 wt.% (17.78 vol.%). The neodymium (Nd) particles 90A are magnetic. That is, the elastomer particles 90 have magnetic properties and elasticity. The elastomer particles 90 thus formed are magnetized to be magnetic. That is, the elastomer particles 90 have the characteristics of a permanent magnet. The elastomer particles 90 are filled in a space surrounded by the cylinder body 10 and a pair of rod guides 70 (ie, inside the cylinder body 10) at a filling rate of 60%. The filling rate is expressed by the following formula (1). Furthermore, the filling volume refers to the volume of the space in which the elastomer particles 90 are filled.

The magnetic field generating section 20 is a cylindrical wire having a predetermined width in the radial direction and a plurality of turns of coaxially wound metal wires covering the surface with an insulating film, and is bundled into a cylindrical shape having an inner diameter slightly larger than the outer diameter of the cylinder 10. In addition, the metal wires of the magnetic field generating unit 20 have a configuration (not shown) in which both ends of the metal wires are drawn out so that a current flows. The magnetic field generating section 20 is inserted into the cylinder 10 such that the cylindrical inner side of the magnetic field generating section 20 is along the outer peripheral surface of the cylinder 10 and is disposed on the outer peripheral surface of the cylinder 10.

In the thus formed damper 1, when the piston 30 moves back and forth along the central axis of the cylinder 10, the elastomer particles 90 move through a predetermined gap between the outer peripheral surface of the piston 30 and the inner peripheral surface of the cylinder 10. At this time, between the inner peripheral surface of the cylinder body 10 and the elastomer particles 90 abutting the inner peripheral surface of the cylinder body 10, between adjacent elastomer particles 90, and between the outer peripheral surfaces of the rod 50 and the piston 30, A frictional force is generated between the elastomer particles 90 abutting on the outer peripheral surface of the rod 50 and the piston 30. In addition, the elastomer particles 90 on the moving side of the piston 30 are pressed by the piston 30. At this time, the elastic reaction force generated by the elastomer particles 90 squeezed by the piston 30 will press the piston 30 back. That is, the damper 1 generates a damping force based on the frictional force or elastic reaction force thus generated.

In addition, if a current of a predetermined magnitude is passed through a metal wire drawn from the magnetic field generating section 20 of the damper 1, a magnetic field is generated around the magnetic field generating section 20. At this time, a predetermined magnetic field is generated such that the magnetic field lines extend in the direction of the central axis of the cylinder 10 by using the magnetic field generated in the cylinder 10 by the magnetic field generating unit 20. Thereby, the bonding force between the elastomer particles 90 filled in the cylinder 10 can be further enhanced. Accordingly, since the frictional force between the elastomer particles 90 increases, the damping force of the damper 1 also increases accordingly. In addition, the intensity of the magnetic field generated in the cylinder 10 can be freely changed by changing the magnitude of the current flowing through the metal wire drawn from the magnetic field generating section 20. Accordingly, if the damper 1 changes the strength of the magnetic field generated by the magnetic field generating unit 20, the binding force between the elastomer particles 90 changes, and the magnitude of the damping force can be easily changed to a desired magnitude.

Next, FIGS. 3 (A) and (B) show the magnetic field near the central axis of the cylinder 10 when the magnitude of the current flowing through the magnetic field generating section 20 of the damper 1 is changed for each predetermined magnitude. The result of the measurement of the density. Specifically, the magnetic flux density is measured by changing the magnitude of the current flowing through the magnetic field generating section 20 of the damper 1 every 1 A between 1 and 6 A (amperes). FIG. 3 (A) shows the magnitude of the magnetic flux density in the direction of the central axis of the cylinder 10, and FIG. 3 (B) shows the magnitude of the magnetic flux density in the direction (radiation direction) orthogonal to the central axis of the cylinder 10.

As shown in FIG. 3 (A), regardless of the magnitude of the current flowing through the magnetic field generating section 20, which is 1 to 6 A, the magnetic flux density in the center axis direction of the cylinder 10 is in a pair of rods. The vicinity of each of the guides 70 is the smallest, and becomes larger toward the center in the direction of the central axis of the cylinder 10. In addition, the larger the magnitude of the current flowing through the magnetic field generator 20, the larger the magnitude of the magnetic flux density.

In addition, as shown in FIG. 3 (B), the direction orthogonal to the central axis of the cylinder 10 (radiation direction) regardless of the magnitude of the current flowing through the magnetic field generating section 20 is 1 to 6A. The magnetic flux densities increase with a predetermined degree of strength as they move from the vicinity of one rod guide 70 to the vicinity of the other rod guide 70. Specifically, the direction of the magnetic field line extending from the vicinity of the rod guide 70 to the center of the center axis direction of the cylinder 10 includes the direction (radiation direction) separating from the center axis of the cylinder 10. ingredient. In addition, a component located in a direction (radiation direction) approaching the central axis of the cylinder block 10 is included in a direction in which a magnetic field line extends from a vicinity of the other rod guide 70 to a center of the central axis direction of the cylinder block 10. . In addition, the magnetic flux density in the center of the central axis direction of the cylinder 10 is substantially zero regardless of the magnitude of the current flowing through the magnetic field generating section 20. That is, the direction in which the magnetic field lines located in the center of the center axis direction of the cylinder block 10 extend is substantially parallel to the center axis direction of the cylinder block 10. In addition, in the case where the magnitude of the current flowing through the magnetic field generating section 20 is relatively large, the degree of increase in the magnetic flux density becomes larger.

Next, FIGS. 4 (A) to (D) show the magnitude of the speed (hereinafter referred to as the frequency) when the magnitude of the current flowing through the magnetic field generating section 20 of the damper 1 is changed for each predetermined magnitude. The relationship between the displacement of the rod 50 with respect to the cylinder 10 and the damping force when the predetermined size changes, wherein the above-mentioned speed is the speed when the rod 50 is reciprocated in the direction of the central axis of the cylinder 10. Specifically, in each case where a current having a magnitude of 0, 2, 4, and 6 A flows through the magnetic field generating section 20 of the damper 1, the magnitude of the frequency is changed every 1 Hz between 1 and 5 Hz (hertz). Determine the attenuation force. The area enclosed by each curve corresponds to the amount of energy absorbed by the vibration energy of the rod 50 and the piston 30 that the damper 1 moves back and forth. That is, the larger the area enclosed by the curve, the larger the amount of energy absorbed by the damper 1 (that is, the larger the attenuation force generated). In addition, the smaller the area enclosed by the curve, the smaller the amount of energy (hereinafter, referred to as attenuation energy) absorbed by the damper 1 (that is, the smaller the generated attenuation force). As shown in FIGS. 4 (A) to (D), as the frequency becomes larger, the area enclosed by the curve also increases. That is, the damper 1 has a larger attenuation energy as the frequency becomes larger (that is, a larger attenuation force is generated).

Next, FIG. 5 shows the relationship between the magnitude of the frequency and the magnitude of the attenuation energy when the magnitude of the current flowing through the magnetic field generating section 20 is a predetermined magnitude. Specifically, in each case where a current having a magnitude of 0, 3, and 6 A flows through the magnetic field generating section 20 of the damper 1, the attenuation energy when the magnitude of the frequency is changed by 1 Hz between 1 and 5 Hz is measured. As shown in FIG. 5, regardless of whether the magnitude of the current flowing through the magnetic field generator 20 is 0, 3, or 6A, the attenuation energy increases as the frequency becomes larger. That is, it can also be seen from FIG. 5 that the damping force generated by the damper 1 is larger as the frequency becomes larger.

Next, Figs. 6 (A) to (C) show that the frequency of the rod 50 relative to the cylinder when the magnitude of the current flowing through the magnetic field generating section 20 of the damper 1 is changed for each predetermined magnitude at a frequency of 1 Hz. The relationship between the displacement of the body 10 and the damping force. Specifically, FIG. 6 (A) shows that the magnitude of the current flowing through the magnetic field generating section is 0, 1, 2, 3A, and FIG. 6 (B) shows the magnitude of the current flowing through the magnetic field generating section is 3, 4, or 3. In the case of 5, 6A, FIG. 6 (C) shows the case where the magnitude of the current flowing through the magnetic field generating section is 0, 3, and 6A. As shown in FIGS. 6 (A) to (C), as the magnitude of the current flowing through the magnetic field generating section 20 increases, the area enclosed by the curve also increases. That is, as the magnitude of the electric current flowing through the magnetic field generating section 20 becomes larger (that is, the magnetic field generated in the cylinder 10 becomes stronger), the damping energy becomes larger.

Next, Figs. 7 (A) to (C) show that the frequency of the rod 50 relative to the cylinder when the magnitude of the current flowing through the magnetic field generating section 20 of the damper 1 is changed for each predetermined magnitude at a frequency of 3 Hz. The relationship between the displacement of the body 10 and the damping force. Specifically, FIG. 7 (A) shows a case where the magnitude of the current flowing through the magnetic field generating section is 0, 1, 2, 3A, and FIG. 7 (B) shows a magnitude of the current flowing through the magnetic field generating section is 3, 4, In the case of 5, 6A, FIG. 7 (C) shows the case where the magnitude of the current flowing through the magnetic field generating section is 0, 3, and 6A. As can also be seen from FIGS. 7 (A) to (C), as the magnitude of the current flowing through the magnetic field generating section 20 increases, the area enclosed by the curve also increases. That is, it can also be seen from FIGS. 7 (A) to (C) that the damper 1 becomes larger as the current flowing through the magnetic field generating section 20 becomes larger (that is, the magnetic field generated in the cylinder 10 becomes stronger). ), And the greater the attenuation energy.

Next, Figs. 8 (A) to (C) show that at a frequency of 5 Hz, the magnitude of the current flowing through the magnetic field generating section 20 of the damper 1 is changed with each predetermined magnitude. The relationship between the displacement of the body 10 and the damping force. Specifically, FIG. 8 (A) shows a case where the magnitude of the current flowing through the magnetic field generating portion is 0, 1, 2, 3A, and FIG. 8 (B) shows a magnitude of the current flowing through the magnetic field generating portion is 3, 4, or 3. In the case of 5, 6A, FIG. 8 (C) shows the case where the magnitude of the current flowing through the magnetic field generating section is 0, 3, and 6A. As can also be seen from FIGS. 8 (A) to (C), as the magnitude of the current flowing through the magnetic field generating section 20 increases, the area enclosed by the curve increases. That is, it can also be seen from FIGS. 8 (A) to (C) that the damper 1 becomes larger as the current flowing through the magnetic field generating section 20 becomes larger (that is, the magnetic field generated in the cylinder 10 becomes stronger). ), And the greater the attenuation energy.

FIG. 9 shows the relationship between the magnitude of the current flowing through the magnetic field generating unit 20 and the magnitude of the attenuation energy when the magnitude of the frequency is a predetermined magnitude. Specifically, in each of the cases where the frequency of the damper 1 is 1, 3, and 5 Hz, the attenuation energy when the magnitude of the current flowing through the magnetic field generating section 20 between 0 and 6 A is changed every 1 A is measured. As shown in FIG. 9, regardless of whether the frequency is 1, 3, or 5 Hz, the attenuation energy increases as the magnitude of the current flowing through the magnetic field generating section 20 becomes larger.

In this way, when the rod 50 and the piston 30 move back and forth along the central axis direction of the cylinder 10, the damper 1 elastically deforms a plurality of elastomer particles 90 having the characteristics and elasticity of a permanent magnet filled in the cylinder 10. The damper 1 generates a damping force by the frictional force between the elastomer particles 90 generated at this time or the elastic reaction force of the elastomer particles 90. In addition, since the elastomer particles 90 have elasticity, the adjacent elastomer particles 90 are elastically deformed to each other, and the elastomer particles 90 are difficult to sinter with each other. In addition, by using the magnetic field generated in the cylinder 10 by the magnetic field generating unit 20 and the characteristics of the permanent magnets of each of the elastomer particles 90, the binding force between the plurality of elastomer particles 90 can be enhanced. Accordingly, since the frictional force between the plurality of elastomer particles 90 becomes larger, the damping force of the damper 1 also increases accordingly.

Therefore, the damper 1 of the present invention can generate a damping force well, and the damping force can be easily adjusted.

The elastomer particles 90 of the damper 1 have the characteristics of a permanent magnet. Therefore, in addition to the binding force of the magnetic field generated in the cylinder 10 by the magnetic field generating section 20, the damper 1 also strengthens the plurality of elastomer particles 90 with each other by the characteristics of the permanent magnets possessed by each elastomer particle 90. The binding force, therefore, can produce a greater attenuation force.

In addition, the magnetic field generator 20 of the damper 1 can freely change the strength of the magnetic field generated in the cylinder 10. Therefore, if the damper 1 changes the strength of the magnetic field generated by the magnetic field generating unit 20, the binding force between the elastomer particles 90 changes, and the magnitude of the damping force can be easily changed to a desired magnitude.

In addition, the damper 1 is provided with a piston 30 which is arranged in the cylinder block 10 and is connected to a rod 50 which can move freely in the direction of the central axis of the cylinder block 10 and reciprocates with the rod 50 in the cylinder block 10 mobile. Therefore, the piston 30 pushes away the elastomer particles 90 filled in the cylinder 10 and moves. Therefore, the damper 1 can generate a larger damping force than in the case where the piston 30 is not provided.

    <Embodiment 2>    

As shown in FIGS. 10 (A) and (B), the damper 11 of the second embodiment is based on the shape of the casing 110, that is, the cylinder 110, the shape of the rod guide 170, and the axis of the rod 150 and the rotor 40, that is, the cylinder 110. The point of rotation of the central axis, the shape of the magnetic field generating section 120, and the arrangement of the magnetic field generating section 120 with respect to the cylinder 110 are different from the first embodiment. The other configurations are the same as those of the first embodiment, and the same reference numerals are given to the same configurations, and detailed descriptions are omitted.

As shown in FIGS. 10 (A) and (B), the cylinder 110 has a cylindrical shape with both ends open.

The rod guide 170, that is, the first rod guide 171 is disc-shaped, and is connected to the cylinder block 110 so that the other surface abuts on one end surface of the cylinder block 110 and closes one side of the cylinder block 110. A first through-hole 171A is provided at a disc-shaped center of the first rod guide 171 penetrating the plate thickness direction. A first contact portion 171B is formed in the first through hole 171A on the other surface side of the first rod guide 171 and extends in a flat plate shape from the inner peripheral surface of the first through hole 171A. The inner diameter of the first contact portion 171B is slightly larger than the outer diameter of the rod 150 described later. A sealed bearing 60 is fitted in the first through hole 171A, and one surface of the sealed bearing 60 is in contact with one surface of the first contact portion 171B.

The rod guide 170, that is, the second rod guide 172, is disc-shaped, and is connected to the cylinder block 110 so that one side abuts against the other end surface of the cylinder block 110 and closes the other side of the cylinder block 110. A second through-hole 172A is provided at a disc-shaped center of the second rod guide 172 penetrating the plate thickness direction. In addition, a second abutting portion 172B extending in a flat plate shape from the inner peripheral surface of the second through hole 172A inwardly is formed in an intermediate portion of the second through hole 172A in the through-thickness direction. The inner diameter of the second contact portion 172B is slightly larger than the outer diameter of the rod 150. In addition, the inner diameter of the second through hole 172A is from the other surface of the second abutment portion 172B to the other surface of the second rod guide 172 (hereinafter, referred to as the other side of the second through hole 172A), It is smaller than the distance from one surface of the second contact portion 172B to one surface of the second lever guide 172 (hereinafter, referred to as one side of the second through hole 172A). A sealed bearing 60 is fitted in the other side of the second through-hole 172A, and one surface of the sealed bearing 60 is in contact with the other surface of the second contact portion 172B.

The lever guide 170, that is, the third lever guide 173, is disc-shaped thicker than the first lever guide 171 and the second lever guide 172. The disk-shaped outer diameter of the third rod guide 173 is substantially the same as the inner diameter of the cylinder 110. The third rod guide 173 is in contact with the other surface of the first rod guide 171 and is inserted into one of the open end portions 110A of the cylinder 110 and is connected to the first rod guide 171. A third through-hole 173A is provided at a disc-shaped center of the third rod guide 173 penetrating the plate thickness direction. In addition, a third contact portion 173B is formed in the third through hole 173A on the other surface side of the third lever guide 173 in a flat plate shape extending inward from the inner peripheral surface of the third through hole 173A. The inner diameter of the third contact portion 173B is slightly larger than the outer diameter of the first end portion 40B of the rotor 40 described later.

The lever guide 170, that is, the fourth lever guide 174, is a disk-like shape that is thicker than the first lever guide 171 and the second lever guide 172 and is thinner than the third lever guide 173. The disc-shaped outer diameter of the fourth rod guide 174 is substantially the same as the inner diameter of the cylinder 110. The fourth rod guide 174 is a disk-shaped other surface that abuts on one surface of the second rod guide 172, is inserted into the other open end portion 110A of the cylinder block 110, and is connected to the second rod guide 172. A fourth through-hole 174A is provided at a disc-shaped center of the fourth rod guide 174 penetrating the plate thickness direction. In addition, a fourth abutting portion 174B is formed in the fourth through hole 174A on one surface side of the fourth lever guide 174 in a flat plate shape extending inward from the inner peripheral surface of the fourth through hole 174A. The inner diameter of the fourth abutting portion 174B is slightly larger than the outer diameter of the second end portion 40C of the rotor 40.

The rotor 40 includes a central portion 40A, a first end portion 40B, and a second end portion 40C. The central portion 40A has a cross-sectional shape that is arranged between the other surface of the third rod guide 173 and one surface of the fourth rod guide 174 and is orthogonal to the central axis of the cylinder 110 (see FIG. 10 ( B)). In addition, a ridgeline (hereinafter, referred to as a ridge) is formed between two adjacent surfaces of the four surfaces formed in a square shape.

In addition, a first plane 40D orthogonal to the central axis of the cylinder 110 is formed at both ends in the central axis direction of the cylinder 110 of the central portion 40A.

The first end portion 40B and the second end portion 40C are each formed in a cylindrical shape, and extend from the respective centers of the two first planes 40D of the central portion 40A in mutually opposite directions. In addition, a second plane 40E orthogonal to the central axis of the cylinder 110 is formed on a side of the first end portion 40B and the second end portion 40C separated from the central portion 40A.

The rod 150 extends from the center of the second plane 40E of the first end portion 40B and the second end portion 40C, respectively. That is, the rotor 40 is connected to the rod 150. The rod 150 and the first end portion 40B and the second end portion 40C are coaxial with each other. The rotor 40 is disposed in the cylinder block 110.

The lever 150 is rotatably connected to the first lever guide 171 and the second lever guide 172 via sealed bearings 60 which are respectively embedded in the first lever guide 171 and the second lever guide 172. In addition, the first end portion 40B and the second end portion 40C are rotatably inserted in the third contact portion 173B of the third through hole 173A of the third lever guide 173 and the fourth lever guide 174, respectively. The fourth contact portion 174B of the fourth through hole 174A.

In addition, a thrust bearing 80 is disposed inside the third through hole 173A of the third rod guide 173, and the thrust bearing 80 is inserted through the second plane of the first end portion 40B of the third contact portion 173B 40E and the other side of the first rod guide 171 are clamped. In addition, a thrust bearing 80 is also arranged inside the fourth through hole 174A of the fourth lever guide 174, and the thrust bearing 80 is inserted through the second end portion 40C of the fourth abutment portion 174B. Two planes 40E and one surface of the second rod guide 172 are sandwiched. Accordingly, both the rod 150 and the rotor 40 can rotate freely around the central axis of the cylinder body 110.

The magnetic field generating unit 120 is a metal wire having a plurality of coils coaxially wound on a surface covered with an insulating film, which has a predetermined width in a radial direction and is bundled into a cylindrical shape. The damper 11 is attached to the outer peripheral surface of the cylinder 110, and the four magnetic field generating units 120 are arranged so that one end side of each ring shape is along the outer peripheral surface of the cylinder 110.

The thus formed damper 11 causes the elastomer particles 90 filled in the cylinder body 110 to flow when the rod 150 and the rotor 40 rotate around the central axis of the cylinder body 110. At this time, between the inner peripheral surface of the cylinder body 110 and the elastomer particles 90 abutting the inner peripheral surface of the cylinder body 110, the adjacent elastomer particles 90 between each other, and the surface of the central portion 40A of the rotor 40 and Friction is generated between the elastomer particles 90 abutting on the surface of the central portion 40A of the rotor 40. The elastomer particles 90 are pressed by the central portion 40A of the rotating rotor 40. At this time, the elastic reaction force generated by the elastomer particles 90 squeezed by the central portion 40A of the rotor 40 will press the central portion 40A of the rotor 40 back. That is, the damper 11 generates a damping force in a direction opposite to the rotation direction of the rotor 40 based on the frictional force or the elastic reaction force thus generated.

In addition, if a current of a predetermined magnitude is passed through the metal wires drawn from the four magnetic field generating sections 120 of the damper 11, a magnetic field is generated around the magnetic field generating section 120. At this time, a magnetic field generated in the cylinder 110 is generated by the magnetic field generating unit 120 to generate a magnetic field. Thereby, the bonding force between the elastomer particles 90 filled in the cylinder 110 can be enhanced. Accordingly, since the frictional force between the elastomer particles 90 increases, the damping force of the damper 11 also increases accordingly.

In this way, when the rod 150 and the rotor 40 rotate around the central axis of the cylinder block 110, the damper 11 elastically deforms the plurality of elastomer particles 90 having the characteristics and elasticity of the permanent magnet filled in the cylinder block 110. The damper 11 generates a damping force by the frictional force between the elastomer particles 90 and the elastic reaction force of the elastomer particles 90 generated at this time. In addition, since the elastomer particles 90 have elasticity, the adjacent elastomer particles 90 are elastically deformed to each other, and the elastomer particles 90 are difficult to sinter with each other. In addition, by using the magnetic field generated in the cylinder 110 by the magnetic field generating unit 120 and the characteristics of the permanent magnets of each of the elastomer particles 90, the binding force between the plurality of elastomer particles 90 can be enhanced. Accordingly, since the frictional force between the plurality of elastomer particles 90 becomes larger, the damping force of the damper 11 also becomes larger.

Therefore, the damper 11 of the present invention can also generate a damping force well, and the damping force can be easily adjusted.

In addition, the damper 11 includes a rotor 40 which is arranged in the cylinder block 110 and is connected to a rod 150 which can rotate freely about a central axis of the cylinder block 110 and rotates in the cylinder block 110 together with the rod 150. Therefore, when the rod 150 and the rotor 40 rotate around the central axis of the cylinder block 110, the elastomer particles 90 filled in the cylinder block 110 are elastically deformed. The damper 11 can generate a damping force in a direction opposite to the rotation direction of the rod 150 and the rotor 40 by the frictional force of the elastic particles 90 or the elastic reaction force of the elastic particles 90 generated at this time.

    <Embodiment 3>    

As shown in FIG. 11 (A), the damper 21 of the third embodiment is different from the first and second embodiments in that the piston 230 is provided with a magnet 45, which is a permanent magnet. The other configurations are the same as those of the first embodiment, and the same reference numerals are given to the same configurations, and detailed descriptions are omitted.

The damper 21 according to the third embodiment is provided with a magnet 45 inside the piston 230. The magnet 45 has the characteristics of a permanent magnet. For example, the magnet 45 is formed in a cylindrical shape, and a central axis thereof is coaxial with the central axis of the rod 50 and the piston 230 and is disposed in the piston 230. The magnet 45 is, for example, magnetized such that one end side of the column becomes the N pole and the other end side becomes the S pole. That is, the piston 230 has characteristics of a permanent magnet.

The thus formed damper 21 is caused when the piston 230 moves back and forth in the direction of the central axis of the cylinder 10, and the elastomer particles 90 move through a predetermined gap between the outer peripheral surface of the piston 230 and the inner peripheral surface of the cylinder 10. At this time, between the inner peripheral surface of the cylinder block 10 and the elastomer particles 90 abutting on the inner peripheral surface of the cylinder block 10, the adjacent elastomer particles 90 between each other, and the outer peripheral surfaces of the rod 50 and the piston 230 and Friction is generated between the rod 50 and the elastomer particles 90 on the outer peripheral surface of the piston 230. In addition, the elastomer particles 90 on the moving side of the piston 230 are pressed by the piston 230. At this time, the elastic reaction force generated by the elastomer particles 90 squeezed by the piston 230 will press the piston 230 back. That is, the damper 21 generates a damping force based on the frictional force or elastic reaction force thus generated.

In addition, the elastomer particles 90 are attracted toward the piston 230 by the magnet 45 disposed in the piston 230. Thereby, in the damper 21, the frictional force generated between the outer peripheral surface of the piston 230 and the elastomer particles 90 abutting on the outer peripheral surface of the piston 230 becomes larger. Therefore, the damper 21 can generate a larger damping force.

As such, when the rod 50 and the piston 230 reciprocate in the direction of the central axis of the cylinder block 10, the damper 21 elastically deforms the plurality of elastomer particles 90 having the characteristics and elasticity of the permanent magnets filled in the cylinder block 10. The damper 21 generates a damping force by the frictional force between the elastomer particles 90 generated at this time or the elastic reaction force of the elastomer particles 90. In addition, by using the magnetic field generated in the cylinder 10 by the magnetic field generating unit 20 and the characteristics of the permanent magnets of each of the elastomer particles 90, the binding force between the plurality of elastomer particles 90 can be enhanced. Accordingly, since the frictional force between the plurality of elastomer particles 90 becomes larger, the damping force of the damper 21 also becomes larger.

Therefore, the damper 21 of the present invention can also generate a damping force well, and the damping force can be easily adjusted.

In addition, the piston 230 of the damper 21 has the characteristics of a permanent magnet. Therefore, in the damper 21, since the friction force between the piston 230 having the characteristics of a permanent magnet and the elastomer particles 90 abutting on the surface of the piston 230 becomes larger, the damping force of the damper 21 can be further increased.

    <Embodiment 4>    

As shown in FIG. 11 (B), the damper 31 of the fourth embodiment is different from the first to third embodiments in that the rotor 240 is provided with a magnet 145, which is a permanent magnet. The other configurations are the same as those of the second embodiment, and the same reference numerals are assigned to the same configurations, and detailed descriptions are omitted.

The damper 31 of the fourth embodiment is provided with a magnet 145 inside the rotor 240. The magnet 145 has the characteristics of a permanent magnet. For example, the magnet 145 is formed in a cylindrical shape, and a central axis of the magnet 145 is coaxial with the central axis of the rod 150 and the rotor 240 and is disposed in the rotor 240. In addition, the magnet 145 is magnetized such that one end side of a cylindrical shape becomes an N pole and the other end side becomes a S pole, for example. That is, the rotor 240 has characteristics of a permanent magnet.

The thus formed damper 31 causes the elastomer particles 90 filled in the cylinder body 110 to flow when the rod 150 and the rotor 240 rotate around the central axis of the cylinder body 110. At this time, between the inner peripheral surface of the cylinder body 110 and the elastomer particles 90 abutting the inner peripheral surface of the cylinder body 110, the adjacent elastomer particles 90 between each other, and the surface of the central portion 240A of the rotor 240 and Friction is generated between the elastomer particles 90 abutting on the surface of the central portion 240A of the rotor 240. The elastomer particles 90 are squeezed by the central portion 240A of the rotating rotor 240. At this time, the elastic reaction force generated by the elastomer particles 90 squeezed by the central portion 240A of the rotor 240 will press the central portion 240A of the rotor 240 back. That is, the damper 31 generates a damping force in a direction opposite to the direction in which the rotor 240 rotates based on the frictional force or the elastic reaction force thus generated.

In addition, the magnet particles 145 disposed in the rotor 240 attract the elastomer particles 90 toward the central portion 240A of the rotor 240. Thereby, in the damper 31, the frictional force generated between the surface of the central portion 240A of the rotor 240 and the elastomer particles 90 abutting on the surface of the central portion 240A of the rotor 240 becomes larger. Therefore, the damper 31 can generate a larger damping force.

In this way, when the rod 150 and the rotor 240 rotate around the central axis of the cylinder 110, the damper 31 elastically deforms the plurality of elastomer particles 90 having permanent magnets and elasticity filled in the cylinder 110. The damper 31 generates a damping force by the frictional force between the elastomer particles 90 and the elastic reaction force of the elastomer particles 90 generated at this time. In addition, since the elastomer particles 90 have elasticity, the adjacent elastomer particles 90 are elastically deformed to each other, and the elastomer particles 90 are difficult to sinter with each other. In addition, by using the magnetic field generated in the cylinder 110 by the magnetic field generating unit 120 and the characteristics of the permanent magnets of each of the elastomer particles 90, the binding force between the plurality of elastomer particles 90 can be enhanced. Accordingly, since the frictional force between the plurality of elastomer particles 90 becomes larger, the damping force of the damper 31 also becomes larger.

Therefore, the damper 31 of the present invention can also generate a damping force well, and the damping force can be easily adjusted.

In addition, the rotor 240 of the damper 31 has the characteristics of a permanent magnet. Therefore, since the friction force of the rotor 240 having the characteristics of the permanent magnet and the elastomer particles 90 abutting on the surface of the rotor 240 becomes larger, the damping force of the damper 31 can be further increased.

The present invention is not limited to Embodiments 1 to 4 described by the above description and drawings. For example, the following embodiments are also included in the technical scope of the present invention.

(1) In the first to fourth embodiments, the magnetic field generating section is provided on the outer peripheral surface of the cylinder block. However, for example, the magnetic field generating section may be formed in the rod and the piston. Specifically, as shown in FIG. 12 (A), the damper 41 may be provided so that the central axis of the cylindrical magnetic field generator 220 and the central axis of the rod 250 and the piston 130 are coaxial with each other. Inside the piston 130. In addition, the damper 51 shown in FIG. 12 (B) may have a plurality of magnetic field generating sections 320 formed in a ring shape, and each of the four surfaces of the central portion 140A of the rotor 140 formed in a square shape. The inner sides of the faces are mounted such that one end of the ring shape is along the four faces. In addition, both ends of the metal wires drawn from the magnetic field generating sections 220 and 320 illustrated in FIGS. 12 (A) and (B) become the inner sides of the rods 250 and 350 via the one-sided rods and the slip rings and the like. In addition, a structure (not shown) that causes a current to flow from the outside of the dampers 41 and 51 toward the magnetic field generating units 220 and 320.

(2) In Embodiments 1 to 4, the magnitude of the damping force of the damper is adjusted by passing a current through the magnetic field generating section, but the number of magnetic lines of force possessed by the elastomer particles passing through the magnetic field generating section is changed, for example. Since the induced electromotive force is generated in the magnetic field generating section, electric energy can also be taken from the kinetic energy when the elastomer particles are moved inside the cylinder through the magnetic field generating section. That is, the magnetic field generation unit may be used as a generator.

(3) In the first to fourth embodiments, the magnetic field generating section is provided on the outer peripheral surface of the casing, but it may be formed on both the outer peripheral surface of the casing and the inside of the rod and the piston (rotor). In addition, a current can be made to flow through any of these magnetic field generating sections to adjust the damping force generated by the damper, and the other can be used as a generator. In addition, a current can be passed through both of these magnetic field generating sections to adjust the damping force generated by the damper, and both of these magnetic field generating sections can be used as a generator.

(4) In the first and third embodiments, the cylindrical magnetic field generating portion has a predetermined width in the radial direction, but the radial width of the cylindrical magnetic field generating portion may be locally increased or decreased. Thereby, plural types of portions having different magnetic field strengths in the direction of the central axis of the cylinder can be formed. Thereby, the position of the central axis of the cylinder block can be used to change the magnitude of the generated damping force.

(5) In the first and third embodiments, a magnetic field generating unit is arranged on the outer peripheral surface of the cylinder block, but a plurality of cylindrical magnetic fields may be provided such that the inside of each cylindrical shape is along the outer peripheral surface of the cylinder. The generating unit is arranged in the direction of the central axis of the cylinder. In addition, a current can be passed through all of these magnetic field generating sections to adjust the attenuation force generated by the damper, or a current can be passed through any of these magnetic field generating sections to adjust the attenuation force generated by the damper. Size and use the other magnetic field generator as a generator.

(6) In Embodiments 1 to 4, the elastomer particles are elastomers made of silicone rubber having a hardness of 60. However, as long as they are elastically deformed, other materials may be used, and these materials may be used in combination. In addition, the hardness of the elastomer particles can also be about 40 ~ 90.

(7) In the first to fourth embodiments, the plurality of elastomer particles filled in the cylinder body have the same size as each other, but a plurality of types of elastomer particles having a particle diameter may be filled in the cylinder body.

(8) In the first to fourth embodiments, the elastomer particles contain neodymium (Nd) particles, but as long as they are magnetic materials, other materials may be included. In addition, such materials may be contained in combination.

(9) In the first to fourth embodiments, the magnetic field generating unit is formed by winding a plurality of coaxial wires coaxially. However, for example, a permanent magnet disposed on the outer peripheral surface of the cylinder may be used in the cylinder to use an actuator or the like. The outer surface of the body can be freely separated or approached.

(10) In Embodiments 1 and 3, a gap is formed between the outer peripheral surface of the piston and the inner peripheral surface of the cylinder, but a gap may not be formed between the outer peripheral surface of the piston and the inner peripheral surface of the cylinder. That is, the space in the cylinder can also be separated into two spaces by the piston.

(11) In Embodiments 1 to 4, the rod system protrudes from the open end of the cylinder block to the outside of the cylinder, but the rod may also protrude from one side of the piston (rotor), and the rod protrudes from one open end of the cylinder. The part protrudes toward the outside of the cylinder.

(12) In Embodiments 1 to 4, the magnetic field generating section is arranged on the outer peripheral surface of the cylinder so that the cylindrical inner side of the magnetic field generating section follows the outer peripheral surface of the cylinder. For example, each cylinder may be A plurality of magnetic field generating sections are arranged at one end of the shape along the outer peripheral surface of the cylinder.

(13) In Embodiments 2 and 4, edges are formed between two adjacent surfaces of the four surfaces formed in a square shape, but the edges are not limited to tight corners, and chamfering, or The way to connect the two faces is formed by a curved surface.

(14) In the first to fourth embodiments, the piston and the rotor are provided respectively, but the piston and the rotor may be provided without a piston and a rotor.

Claims (6)

    A damper is characterized in that it includes: a casing; a rod protruding from the casing to the outside, freely reciprocating in the axial direction or rotatable about an axis; a plurality of particles, which are filled in the casing , Has the characteristics and elasticity of a permanent magnet; and a magnetic field generating section that generates a magnetic field in the above-mentioned casing.         The damper according to claim 1, wherein the magnetic field generating unit can freely change the strength of the magnetic field generated in the casing.         The damper according to claim 1 or 2, further comprising a piston disposed in the housing, connected to the rod capable of freely reciprocating in the axial direction, and reciprocating in the housing together with the rod.         The damper according to claim 1 or 2, further comprising a rotor disposed in the housing, connected to the lever capable of rotating around an axis, and rotating together with the lever in the housing.         The damper according to claim 3, wherein the piston has the characteristics of a permanent magnet.         The damper according to claim 4, wherein the rotor has the characteristics of a permanent magnet.