TW202603285A - Vibration attenuation device - Google Patents

Abstract

An vibration damping device includes an inner component and an outer component, the inner component and the outer component being configured to reciprocate relative to each other in a first direction, wherein the inner component is disposed inside the outer component in a second direction perpendicular to the first direction, and includes a magnetic material disposed opposite to the outer component in the second direction, the outer component including a magnetic element configured to attract the end component in an equilibrium state, the end component and the magnetic element being restricted from moving in the second direction without contacting each other.

Description

Vibration attenuation device

This invention relates to a vibration attenuation device using magnetic force.

The invention comprises "a base, an upper annular permanent magnet, a lower annular permanent magnet, a connecting rod, and a central permanent magnet, wherein a metal conductor sleeve is connected to the upper surface of the base, the metal conductor sleeve being a hollow metal cylinder, the base sealing the lower end face of the metal conductor sleeve, and the upper and lower annular permanent magnets having the same shape and both being hollow." The device is circular, with an upper and lower ring-shaped permanent magnet embedded within an upper and lower ring-shaped bushing, respectively. The upper and lower ring-shaped bushings are connected to the upper and lower ends of the inner wall of the metal conductor sleeve, respectively. The upper and lower ring-shaped permanent magnets and the metal conductor sleeve are coaxially arranged in the axial direction, and the upper and lower ring-shaped permanent magnets are aligned with each other. The opposing faces of the toroidal permanent magnets have opposite magnetic polarities. The axis of the connecting rod is coaxial with the central axis of the metal conductor sleeve. The central permanent magnet is a hollow ring, coaxially fitted onto and fixed to the connecting rod. The upper end of the connecting rod passes through the central hole of the upper toroidal permanent magnet. The central permanent magnet is located between the upper and lower toroidal permanent magnets. A single-degree-of-freedom magnetic vibration damping device that allows the magnets to move axially between the upper and lower ring permanent magnets together with the connecting rod, wherein the magnetic polarities of the faces of the central permanent magnet and the upper ring permanent magnet are opposite, and the magnetic polarities of the faces of the central permanent magnet and the lower ring permanent magnet are also opposite (see, for example, reference 1).

The single-degree-of-freedom magnetic vibration damping device disclosed in Reference 1 "does not require energy supply, has high reliability, and can generate static and dynamic magnetic forces. The static magnetic force is achieved by the attraction between opposite poles of permanent magnets, while the dynamic magnetic force is achieved by a vortex current damper generated by the relative motion between the metal conductor sleeve and the permanent magnet. The strength of the static magnetic force is only related to displacement, and the device of the present invention also has magnetic force when it is stationary, so it can be regarded as a rigid force. The vortex current damper is only related to relative velocity and only exists when the magnetic mechanism is in motion, so it can be regarded as a viscous damping force." Furthermore, this single-degree-of-freedom magnetic vibration damping device, "by being configured in parallel with passive vibration damping structures such as rigid coil springs or air springs, can effectively suppress the increase in amplitude at the natural frequency without affecting the high-frequency attenuation performance of the passive vibration damping system, thereby improving the passive vibration damping performance of the original system." [Prior Art Documents] [Patent Documents]

[Patent Document 1] Japanese Patent No. 6317822

[Problem to be solved by the invention] The single-degree-of-freedom magnetic vibration damping device disclosed in Patent Document 1 has the problem that "the magnetic polarities of the faces of the upper and lower ring permanent magnets are opposite" and "the central permanent magnet is located between the upper and lower ring permanent magnets and can move axially between the upper and lower ring permanent magnets together with the connecting rod". Therefore, when the central permanent magnet moves in either direction in a self-balancing state, the movement is limited by the presence of the upper or lower ring permanent magnets along its extension line.

To address the aforementioned problems, this invention provides a vibration damping device that suppresses the limitation of movement of a component under magnetic force in a vibration damping device utilizing magnetic force. [Technical Means for Solving the Problem]

The vibration damping device of this invention comprises an inner component and an outer component, the inner component and the outer component being configured to reciprocate relative to each other along a first direction. The inner component is disposed inside the outer component in a second direction perpendicular to the first direction, and includes an end component made of magnetic material with magnetic poles arranged opposite to the outer component in the second direction. The outer component includes a magnetic element configured to attract the end component in an equilibrium state. The end component and the magnetic element are restricted from moving in the second direction without contacting each other. [Effects of the Invention]

According to the invention described above, a magnetic force in the direction of adsorption is generated between the inner component and the outer component, and the movement paths of the inner component and the outer component do not intersect, so their movement is not restricted.

The following describes appropriate embodiments of the vibration damping device of the present invention with reference to the drawings. In addition, although the embodiments described below are appropriate specific examples of the present invention and are subject to various technical limitations, the scope of the present invention is not limited to these types unless specifically limited by the description in the following description.

Example 1, <Vibration Attenuation Device 100> Figure 1 is a schematic diagram showing the main structure of the vibration attenuation device 100 according to Example 1. The vibration attenuation device 100 shown in Figure 1 has an inner component 10 that can move in the z-direction and a fixed outer component 20. The vibration attenuation device 100, for example, connects the inner component 10 to other structures and uses magnetic force to suppress the displacement of the structures in the z-direction. The vibration attenuation device 100 is used for vibration attenuation purposes such as damping in automobiles, seismic devices in buildings, or vibration damping devices in machinery. In addition, although the example of the inner component 10 moving in the z direction is used in Embodiment 1, the vibration damping device 100 can be constructed such that the inner component 10 and the outer component 20 can move in opposite directions in the z direction.

The vibration damping device 100 is, for example, formed in a cylindrical shape by an outer component 20. The outer component 20 surrounds the inner component 10 in a direction perpendicular to the z-direction. The outer component 20 has a magnetic element 21. In a cross-section parallel to the z-direction, the magnetic element 21 has paired magnetic poles 21a and 21b arranged along the z-direction. In FIG. 1, the magnetic elements 21A and 21B are arranged such that the S pole is located at one end in the z1 direction and the N pole is located at one end in the z2 direction. In addition, the magnetic elements 21A and 21B can be a single magnetic element or separate magnetic elements. Alternatively, the z-direction may be referred to as the first direction and the direction perpendicular to the z-direction may be referred to as the second direction.

The inner component 10 is disposed inside the outer component 20 in a direction perpendicular to the z-direction (xy-direction). The inner component 10 has a first end 13 and a second end 12 disposed separately in the z-direction. The first end 13 and the second end 12 are each made of a magnetic material. In FIG1, although the first end 13 and the second end 12 are each made of a magnet, they can also be soft magnetic materials such as iron or nickel. That is to say, even if the first end 13 and the second end 12 do not have magnetic force or have almost none, they can still be attracted to the magnetic element 21.

The first end 13 and the second end 12 are connected in the z-direction by a connecting member. The connecting member 11 is a member used to maintain a fixed distance between the first end 13 and the second end 12. The connecting member 11 can be a non-magnetic material such as resin, or it can be a metal containing a magnetic material. Furthermore, the inner member 10 has structures in its z-direction end that respectively support the first end 13 and the second end 12, and each structure can also be connected in the z-direction by the connecting member 11. Furthermore, the structures that respectively support the first end 13 and the second end 12 can be integrally formed with the connecting member 11, or they can be separate components connected by means of screws or welding. Alternatively, the first end 13 and the second end 12 may be referred to together as the end member. In other words, the first end 13 and the second end 12 constitute the end component.

The first end 13 and the second end 12 are configured to be attracted to the magnetic poles 21a or 21b of the magnetic element 21 in the equilibrium state shown in FIG. 1. The front end 13a of the first end 13 is configured to be attracted to the magnetic pole 21a of the magnetic element 21, which is the N pole in the example shown in FIG. 1. The front end 12a of the second end 12 is configured to be attracted to the magnetic pole 21b of the magnetic element 21, which is the S pole in the example shown in FIG. 1.

Although the structures supporting the inner component 10 and the outer component 20 are not shown in Figure 1, the vibration damping device 100 can also be configured to support the inner component 10 and the outer component 20 respectively. Alternatively, since the inner component 10 is configured to be able to adhere to the outer component 20, a spacer or bearing can be provided to maintain a specified distance between the inner component 10 and the outer component 20, so that the front end 13a of the first end 13 and the front end 12a of the second end 12 do not contact the magnetic poles 21a and 21b. The distance between the inner component 10 and the outer component 20 in a direction perpendicular to the z-direction can also be dynamically controlled. By dynamically controlling the distance between the end components (first end 13 and second end 12) and the magnetic element 21 in a direction perpendicular to the z-direction, the magnetic force of attraction can be controlled. In this way, the attenuation force of the vibration attenuation device 100 can be controlled.

Figure 2 is an enlarged view of the first end 13 of Figure 1 and the magnetic pole 21a of the magnetic element 21. In Figure 2(a), the magnetic force generated at the first end 13 is schematically illustrated. Figure 2(b) schematically shows the distribution of magnetic field lines of the magnetic element 21. The operating principle of the vibration damping device 100 will be explained below using Figures 1 and 2.

The front end 13a of the first end 13 of the inner component 10 is positioned opposite the magnetic pole 21a of the magnetic element 21 in the x-direction. The front end 13a of the first end 13 is the N pole and is subjected to a magnetic force in the attraction direction along the direction of the magnetic field lines generated from the magnetic pole 21a of the magnetic element 21 as shown in FIG. 2(b). Therefore, as shown in FIG. 2(a), a magnetic force fa is generated at the z2 side end of the end face of the front end 13a, and a magnetic force fb is generated at the z1 side end of the end face of the front end 13a. These magnetic forces fa and fb can be decomposed into components xa and xb in the x-direction and components za and zb in the z-direction. FIG. 2(a) shows the equilibrium state (initial position) of the vibration damping device 100, where the components za and zb in the z-direction are equal. Furthermore, the x-direction components xa and xb are equal to the magnetic force generated between the front end 13a of the first end 13 located on the x2 side as shown in Figure 1 and the magnetic pole 21a of the magnetic element 21A.

The front end 13a of the first end 13 and the front end 12a of the second end 12 of the inner component 10 generate component forces as shown in FIG. 2(a). Therefore, the magnetic forces are equal in the z-direction and in the direction perpendicular to the z-direction (x-direction in FIG. 2), and thus remain stationary. When the vibration damping device 100 is in this stationary state, it is called an equilibrium state. If the magnetic forces generated between the inner component 10 and the outer component 20 are ideally equal, the inner component 10 and the outer component 20 can maintain an equilibrium state even without any support structure. However, since the vibration damping device 100 is connected to the external structure and bears external forces, it must at least have a structure that restricts the movement of the inner component 10 and the outer component 20 in the direction perpendicular to the z-direction. The inner member 10 and the outer member 20 can be supported by bearings or other support components, thereby restricting their movement in a direction perpendicular to the z-direction, or one of them can be fixed. In either case, the inner member 10 and the outer member 20 are configured to be able to move relative to each other at least in the z-direction.

Furthermore, in Figure 2(a), in a balanced state, the width center of the front end 13a of the first end 13 of the inner component 10 in the z-direction coincides with the position of the front end face of the magnetic element 21B of the outer component 20 in the z-direction. However, for example, when the inner component 10 is affected by external forces such as gravity, the balanced state will shift towards the direction of gravity. At this time, the gravitational load on the inner component 10 is equal to the magnetic force generated by the first end 13 and the second end 12 in the z-direction, and this position becomes a balanced state.

Figure 3 is a schematic diagram of the inner component 10 of the vibration damping device 100 shown in Figure 1 moving in the z-direction. Figure 3(a) shows the inner component 10 moving in the z1 direction, and Figure 3(b) shows the inner component moving in the z2 direction. The inner component 10 is configured such that the first end 13 and the second end 12 are attracted to the magnetic poles 21a and 21b of the magnetic element 21. Therefore, regardless of whether the inner component 10 moves in the z1 or z2 direction, it will be subjected to a magnetic force on the side opposite to the direction of movement. That is, when the inner component 10 moves in a self-balancing state in the z1 direction, it is subjected to a magnetic force in the z2 direction; and when it moves in a self-balancing state in the z2 direction, it is subjected to a magnetic force in the z1 direction. Thus, since the vibration damping device 100 generates a magnetic force opposite to the direction of movement when the inner component 10 moves, for example, when the structure connected to the inner component 10 is displaced, a magnetic force opposite to the direction of displacement is generated, thereby generating a force that returns the inner component 10 to an equilibrium state. In this way, the vibration damping device 100 can dampen the vibrations generated by the structure connected to the inner component 10.

Figure 4 is a schematic diagram showing the relationship between the moving distance of the inner component 10 of the vibration damping device 100 in Embodiment 1 and the generated magnetic force. The moving distance refers to the change in the relative distance between the inner component 10 and the outer component 20 in the z-direction. A larger moving distance indicates that the magnetic poles 21a and 21b of the magnetic elements 21A and 21B are far apart from the front end 13a of the first end 13 and the front end 12a of the second end 12 in the z-direction. The equilibrium state of the vibration damping device 100 is represented by a moving distance of 0. The load in Figure 4 is expressed as an absolute value. In other words, as shown in Figures 1 and 3, when the inner component 10 moves in the z1 direction, a load will be generated in the z2 direction depending on the distance of movement, as shown in Figure 4. When the inner component 10 moves in the z2 direction, a load will be generated in the z1 direction depending on the distance of movement, as shown in Figure 4.

The magnetic force is inversely proportional to the square of the distance between the object and the magnetic force. Therefore, as shown in Figure 4, when the inner component 10 moves relative to the outer component 20 in the z direction, the greater the distance moved, the smaller the magnetic force required to restore the inner component 10 to its equilibrium state.

Figure 5 is a schematic diagram of the main structure of a modified vibration damping device 100A according to Embodiment 1. As shown in Figure 5, the front end 13a of the first end 13 and the front end 12a of the second end 12 of the inner component 10 of the vibration damping device 100A become narrower as they extend outward in a direction perpendicular to the z-direction. As shown in Figure 5(a), the front end 13a of the first end 13 and the front end 12a of the second end 12 can be formed into sharp edges 13c and 12c, or as shown in Figure 5(b), the edges 13c and 12c can remain flat. In other words, the front end 13a of the first end 13 and the front end 12a of the second end 12 of the inner component 10 can also have trapezoidal inclined portions 13d and 12d, whose width decreases towards the z-direction of the end. Furthermore, as shown in FIG5(c), the front ends 13a and 12a can also form a stepped structure. At this time, a plurality of end faces 13e located on the inner side relative to the edge portion 13c can be provided. That is to say, the front ends 13a and 12a can also be formed into a stepped structure.

Figure 6 is a schematic diagram showing the relationship between the moving distance of the inner component 10 of the vibration damping device 100A in the modified example shown in Figure 5 and the generated magnetic force. In the case of the vibration damping device 100A, since the width of the front end 13a of the first end 13 of the inner component 10 is narrower, the magnetic force of the edge portion 13c of the front end 13a has a greater influence, while the magnetic force of the inclined portion 13d has a smaller influence. Therefore, when moving in the z-direction from the equilibrium state shown in Figure 5, the magnetic force generated by the edge portion 13c will become the main source of influence.

Therefore, for example, assuming that the edge portion 13c of the front end 13a of the first end 13 moves slightly in the z1 direction, the edge portion 13c will generate a force that pulls it back to the equilibrium state due to the magnetic force generated in the z2 direction. In contrast, the magnetic force generated by the inclined portion 13d is smaller than the magnetic force generated by the edge portion 13c, and the magnetic force that cancels out the magnetic force pulling the edge portion 13c back to the z2 direction is smaller. Therefore, the force that pulls the front end 13a of the first end 13 back to the equilibrium state is greater than when the front end 13a has a plane along the z direction as shown in FIG2.

On the other hand, as shown in Figure 2, when the front end 13a has a plane along the z-direction, the magnetic force fa increases and the magnetic force fb decreases when the front end 13a moves in the z1 direction. In this case, the z-direction component of the magnetic force fa (that is, the force towards the z1 direction) is greater than the z-direction component of the magnetic force fb (that is, the force towards the z2 direction). The force that pulls the front end 13a back to the z2 direction decreases because the z-direction components of the magnetic force fa and the magnetic force fb cancel each other out.

Therefore, in the vibration damping device 100A of the modified example shown in FIG5, as shown by the solid line in the chart of FIG6, the reduction in load caused by the movement of the inner component 10 in the z direction becomes gentle.

As shown in Figure 5, with the widths of the front end 13a of the first end 13 and the front end 12a of the second end 12 gradually narrowing, it is preferable that the edges 13c and 12 are located closer to the magnetic poles of the magnetic element 21 compared to the front ends 13a and 12a, which are formed as flat surfaces as shown in Figure 1. With this structure, the vibration damping device 100A shown in Figure 5 can suppress the reduction of magnetic force acting on the inner component 10, and at the same time, as shown in Figure 6, make the reduction of load generated when the inner component 10 moves in the z direction more gradual.

Figure 7 is a schematic top view (viewed from the z-direction) of the vibration damping devices 100 and 100A of Embodiment 1. Figure 7(a) shows the outer component 20 configured to cover the inner component 10 from the x and y directions. As shown in Figure 7(a), the vibration damping devices 100 and 100A can also be configured such that the outer component 20 is formed into a rectangular tube, and the inner component 10 is disposed inside it. The structures shown in Figures 1 and 5 show the cross-sectional structure of the A-A section of Figure 7(a), showing the cross-sectional structure parallel to both the z and x directions. In addition, the cross-sectional structure of the vibration damping devices 100 and 100A shown in Figure 7(a) that is parallel to both the z and y directions is the same as that shown in Figures 1 and 5.

Figure 7(b) is a schematic diagram of another embodiment of the vibration damping devices 100 and 100A in a top view (viewed from the z direction). The outer component 20 does not necessarily need to cover the inner component 10 in the entire circumference, and it is also possible to have a structure in which the magnetic elements 21 are arranged only at both ends in the x direction.

Furthermore, the outer component 20 can be circular or other shapes when viewed from above. That is, as long as the magnetic poles 21a and 21b configured as magnetic elements 21 are facing each other in a direction that is perpendicular to the z-direction of the front end 13a and the second end 13b of the first end 13.

Figure 8 is another example of a top view (viewed from the z-direction) of the vibration damping devices 100 and 100A of Embodiment 1. The inner component 10 may also contain a magnetic material that is triangular in shape in the top view. Furthermore, the magnetic material is not limited to being triangular in the top view, and may also be other shapes such as rectangles.

In Figures 7(a) and (b), the magnetic elements 21 of the outer component 20 have the same polarity of magnetic pole 21a in top view, but the orientation of the magnetic elements 21 is not restricted by this. As shown in Figure 8, the four magnetic elements 21 arranged on the four sides of the rectangular outer component 20 are respectively arranged such that the two sides facing each other on the left and right have N poles, and the two sides facing each other on the top and bottom have S poles. The magnetic poles of the magnet in the inner component 10 are arranged corresponding to the magnetic elements 21 of the outer component 20.

Figure 9 is a schematic diagram of the main structure of a modified vibration damping device 100B of Embodiment 1. The vibration damping device 100B is constructed by using paired magnetic poles of a magnet for the front ends 13a of the first end 13 and the front ends 12a of the second end 12 of the inner member 10. A magnetic element 21 with an outer member 20 is arranged corresponding to the magnetic poles of the front ends 13a of the first end 13 and the second end 12a of the second end 12. With this configuration, the width of the first end 13 and the second end 12 of the inner member 10 in the x-direction is reduced, thereby making the overall width of the vibration damping device 100B more compact.

Figure 10 is a schematic diagram of the main structure of a vibration attenuation device 100C, a variation of the vibration attenuation device 100 of Embodiment 1. The vibration attenuation device 100C is configured to eliminate the first end 13 and the second end 12, which are arranged on the x1 side of the inner member 10 as shown in Figure 1. The inner member 10 eliminates the first end 13 and the second end 12, which are symmetrically arranged on one side in the x direction, by restricting its movement in the x direction and configuring it to move in the z direction. Even with this configuration, since the inner member 10 still exerts a force to return it to an equilibrium state when it moves in the z direction, it performs the same function as the vibration attenuation device 100 shown in Figure 1.

Based on the vibration damping devices 100, 100A, 100B, and 100C described above, a structure can be obtained in which an inner component 10 and an outer component 20, which are capable of reciprocating relative to each other in the z-direction, are brought back to an equilibrium state by magnetic force. Since the outer component 20 of the vibration damping devices 100, 100A, 100B, and 100C is positioned so as not to interfere with the movement direction of the inner component 10, regardless of whether the inner component 10 moves relative to the outer component 20 in the z1 or z2 direction, the load that returns to the equilibrium state can be applied to the inner component 10 by magnetic force, thereby attenuating the displacement caused by vibration.

The single-degree-of-freedom magnetic vibration damping device disclosed in Patent 1 is configured such that the magnetic force increases as the displacement in either the vertical or horizontal direction increases. However, this single-degree-of-freedom magnetic vibration damping device is configured such that "the polarities of the magnetic poles of the opposing surfaces of the upper and lower ring permanent magnets are opposite" and "the central permanent magnet is positioned between the upper and lower ring permanent magnets and moves axially between the upper and lower ring permanent magnets together with the connecting rod". Therefore, when the central permanent magnet moves from its equilibrium state in either the vertical or horizontal direction, the magnetic force in the direction of movement will increase, and an external force greater than the magnetic force is required to pull it back to the equilibrium state. Furthermore, since there are upper or lower ring-shaped permanent magnets on the extension line of the movement path of the central permanent magnet, the amount of movement is limited. On the other hand, regarding the vibration damping devices 100, 100A, 100B and 100C of Embodiment 1, there are no outer components 20 on the movement path of the inner component 10, so the inner component 10 and the outer component 20 do not restrict each other's movement.

Example 2 describes the vibration damping device 200 of Example 2. The vibration damping device 200 of Example 2 is a combination of the vibration damping device 100 of Example 1 and the elastic member 30. Furthermore, components having the same function and effect as those in Example 1 will be given the same reference numerals, and their descriptions will be omitted.

Figure 11 is a schematic diagram of the main structure of the vibration damping device 200 according to Embodiment 2. The vibration damping device 200 is formed by further combining the vibration damping device 100 with an elastic member 30. The elastic member 30 is, for example, made of a helical spring and connected to the inner member 10, configured to apply a load in the opposite direction to the direction of movement when the inner member 10 moves in the z direction. The elastic member 30 is also fixed to the support 31 and configured to expand and contract with the movement of the inner member 10.

Figure 12 is a schematic diagram showing the relationship between the moving distance of the inner component 10 and the generated load in the vibration damping device 100 shown in Figure 1, and a schematic diagram showing the relationship between the expansion and contraction of the elastic component 30 and the generated load. As shown in Figure 12(a), since the inner component 10 in the vibration damping device 100 shown in Figure 1 only has magnetic force, the generated load decreases in inverse square of the distance as the moving distance increases. As shown in Figure 12(b), when the elastic component 30 shown in Figure 11 expands and contracts in the z-direction, it generates a load that is opposite to the expansion and contraction direction and proportional to the expansion and contraction.

Figure 13 is a schematic diagram showing the relationship between the movement distance of the inner component 10 of the vibration damping device 200 in Embodiment 2 and the generated magnetic force. Since the vibration damping device 200 applies the load generated by the magnetic force and the expansion and contraction of the elastic component 30 to the inner component 10 in response to the displacement of the inner component 10, the reduction in the load borne by the inner component 10 is suppressed compared with the magnetic force alone shown in Figure 12(a). Therefore, when the inner component 10 is displaced in the z direction, the force that pulls the inner component 10 back to the equilibrium state will gradually weaken when the displacement is still small. However, as the displacement increases, the force that pulls the inner component 10 back to the equilibrium state increases due to the action of the elastic component 30.

In other words, the force that pulls the vibration damping device 200 back to equilibrium changes less compared to the vibration damping device 100 in Embodiment 1, as described in Embodiment 2.

Figure 14 is a schematic diagram showing the relationship between the movement distance of the inner component 10 and the generated magnetic force when the vibration damping device 100 in the vibration damping device 200 shown in Figure 11 is replaced with the vibration damping device 100A shown in Figure 5. The two-point chain in Figure 14 shows the relationship between the displacement and the load of the inner component 10 of the vibration damping device 200 shown in Figure 11, while the solid line in Figure 14 shows the relationship between the displacement and the load when the inner component 10 shown in Figure 11 is replaced with the inner component 10 of the vibration damping device 100A shown in Figure 5. As shown in Figure 6, the vibration damping device 100A in Figure 5 has a relatively gentle load change relative to the displacement of the inner component 10. Therefore, when used in combination with the elastic component 30, the change in the force that pulls the device back to the equilibrium state becomes smaller, and the load change tends to be flat.

Furthermore, the elastic component 30 is not limited to a helical spring; it can be a leaf spring or rubber, as long as it is a component that generates elastic force through deformation. In Embodiment 2, although the elastic component 30 is connected below the inner component 10, the arrangement of the elastic component 30 can be appropriately adjusted. For example, the elastic components 30 can be arranged at certain intervals in the direction of movement of the inner component 10, such that the load caused by the elastic component 30 only acts on the inner component 10 when the amount of movement of the inner component 10 reaches a predetermined value or higher. Furthermore, when the outer component 20 of the vibration damping device 200 is configured to be movable, the load caused by the elastic component 30 can also be applied to the outer component 20.

As shown in Figure 11, the elastic member 30 can also be disposed between the first end 13 and the second end 12 of the inner member 10. For example, the elastic member 30 can also be disposed between the first end 13 and the second end 12 of the inner member 10 and fixed to the outer member 20. In this way, when the inner member 10 moves relative to the outer member 20 in the z direction, the inner member 10 will come into contact with the elastic member 30, enabling the elastic member 30 to perform the same function as the elastic member 30 of the vibration damping device 200 shown in Figure 11.

Example 3 describes the vibration damping device 300 of Example 3. In the vibration damping device 300 of Example 3, as the magnetic elements 21A and 21B of the outer component 20 of the vibration damping device 100 of Example 1, an electromagnetic magnet is used. Furthermore, for constituent elements having the same function and effect as those in Examples 1 and 2, the same symbols will be added and their detailed descriptions will be omitted.

Figure 15 is a schematic diagram of the main structure of the vibration damping device 300 according to Embodiment 3. In Embodiment 3, the magnetic element 21 of the outer component 20 of the vibration damping device 100 is replaced with an electromagnet. The magnetic element 321, made of an electromagnet, can change the positions of the magnetic poles 21a and 21b by partial energization. In Figure 15, the portions of the magnetic element 321 indicated by solid lines are energized, while the portions indicated by dashed lines are not energized. The magnetic element 321 shown in Figure 15 is energized so that the magnetic poles are positioned corresponding to the front end 13a of the first end 13 and the front end 12a of the second end 12.

Figure 16 is a schematic diagram of the vibration damping device 300 moving in the z2 direction from the state shown in Figure 15 of the inner component 10. In Figure 16, the magnetic element 321 provided by the outer component 20 moves its energized range in the z2 direction as the inner component 10 moves. Thus, since the magnetic poles 21a and 21b of the magnetic element 321 move with the inner component 10, the vibration damping device 300 can be controlled so that the inner component 10 still experiences the same magnetic force even when it moves. Regarding the vibration damping device 100 of Embodiment 1, as shown in Figure 4, the magnetic force weakens as the amount of movement increases in the z-direction. However, according to the vibration damping device 300 of Embodiment 3, even if the inner component 10 moves in the z-direction, the magnetic force acting on the inner component 10 can remain approximately unchanged.

The magnetic element 321 of the vibration damping device 100 is configured, for example, to connect a plurality of coils 324 in the z-direction and to selectively energize coils 324 as the inner component 10 moves. For example, the magnetic element 321 is configured to arrange a plurality of coils 324 extending in the z-direction along the central axis of the winding and to control the current flowing into the plurality of coils 324. That is, the magnetic element 321 is configured such that the magnetic poles can move in the z-direction by controlling the current flowing in the plurality of coils 324. Furthermore, the magnetic element 321 is not limited to the configuration shown in Figures 15 and 16, in which a plurality of coils 324 are arranged continuously along the z-direction, and can also be appropriately modified in a manner such as arranging a plurality of coils with gaps between them.

In addition, in Figures 15 and 16, although the outer component 20 has magnetic elements 321A and 321B, it can also be an integral magnetic element 321.

Furthermore, magnetic elements 321A and 321B can suppress the magnetic force attracted to the first end 13 and the second end 12 by controlling the current flowing into the coil 324. In this way, the attenuation force of the vibration attenuation device 300 can be suppressed.

The structures shown in the above embodiments are merely examples, and without departing from their essence, parts of the structure can be omitted or changed.

Figure 17 is a schematic diagram of the main structure of a vibration damping device 100D, a variant of the vibration damping device 100 of Embodiment 1, by removing the second end 12. The vibration damping devices 100, 100A, 100B, 100C, 200, and 300 shown in Embodiments 1 to 3 can function as vibration damping devices even if either the first end 13 or the second end 12 constituting the end component is omitted. In the variant of Figure 17, the first end 13 is supported by a structure 14, which is guided, for example, by a ball bearing 15. Even in this case, the first end 13 still experiences the force shown in Figure 2(a), and thus still functions as a vibration damping device by means of magnetic force. In this case, the magnetic element 21 can also be configured without having a pair of magnetic poles along the z direction, only requiring at least one magnetic pole to be configured opposite to the first end 13 in a direction that is perpendicular to the z direction.

The structure 14 and ball bearing 15 shown in Figure 17 can also be applied to vibration damping devices 100A, 100B, 100C, 200 and 300. Furthermore, the structure of the structure 14 and ball bearing 15 can be modified appropriately, and the ball bearing 15 can be replaced with a sliding bearing or other support structure.

Furthermore, the present invention, which is described above with vibration damping devices 100, 100A, 100B, 100C, 100D, 200, and 300 as examples, can also include combinations of the features shown in Appendix 1 to Appendix 10 below. Such combinations are shown below.

[Appendix 1] A vibration damping device includes an inner component and an outer component, the inner component and the outer component being configured to reciprocate relative to each other in a first direction, wherein the inner component is disposed inside the outer component in a second direction perpendicular to the first direction, and includes an end component made of a magnetic material with magnetic poles disposed opposite to the outer component in the second direction, the outer component including a magnetic element configured to attract the end component in an equilibrium state, the end component and the magnetic element being restricted from moving in the second direction without contacting each other. [Appendix 2] The vibration damping device as described in Appendix 1, wherein the inner component comprises an end component consisting of a first end and a second end configured to be spaced apart from each other in a first direction, a connecting component connecting the first end and the second end in the first direction, a pair of magnetic poles in the magnetic element being configured along the first direction, the pair of magnetic poles being respectively configured to be opposite to the first end and the second end in a second direction in an equilibrium state; the first end and the second end being configured to be attracted to the magnetic poles of the magnetic element facing each other in the second direction in an equilibrium state. [Appendix 3] The vibration damping device as described in Appendix 1 or 2, wherein the magnetic element is composed of a plurality of magnetic elements, the plurality of magnetic elements comprising at least one pair of magnetic elements configured to be positioned opposite each other in the second direction while enclosing the inner component. [Note 4] The vibration damping device as described in any one of Notes 1 to 3, wherein the end member is made of a permanent magnet, and the magnetic poles of the magnetic element are set to be opposite in polarity to the end member. [Note 5] The vibration damping device as described in any one of Notes 1 to 3, wherein the end member is made of a soft magnetic material. [Note 6] The vibration damping device as described in any one of Notes 1 to 5, wherein the end member has a structure in which the width of the front end in the second direction in the first direction gradually decreases from the central axis to the outer side in a cross section including the central axis of the inner member. [Note 7] The vibration damping device as described in any one of Appendices 1 to 6 further comprises an elastic member that applies a load in the opposite direction to the direction of movement in response to the relative movement of the inner member and the outer member in a first direction. [Note 8] The vibration damping device as described in Appendix 7, wherein the elastic member is connected to at least one of the inner member and the outer member. [Note 9] The vibration damping device as described in any one of Appendices 1 to 8, wherein the magnetic element is an electromagnet configured as a pair of magnetic poles that can move in the first direction. [Note 10] The vibration damping device as described in Note 9, wherein the magnetic element has a plurality of coils arranged in a manner with the central axis along a first direction, and the magnetic poles move in the first direction by changing the portion of the coil that is energized among the plurality of coils.

10: Inner component 11: Connecting component 12: Second end 12a: Front end 12c: Edge 13: First end 13a: Front end 13c: Edge 13d: Inclined portion 14: Structure 15: Ball bearing 20: Outer component 21: Magnetic component 21A: Magnetic component 21B: Magnetic component 21a: Magnetic pole 21b: Magnetic pole 30: Elastic component 31: Support body 100: Vibration damping device 100A: Vibration damping device 100B: Vibration damping device 100C: Vibration damping device 200: Vibration damping device 300: Vibration damping device 321: Magnetic component; 321A: Magnetic component; 321B: Magnetic component; 324: Coil

Figure 1 is a schematic diagram showing the main structure of the vibration damping device 100 of Embodiment 1. Figure 2 is an enlarged view showing the first end 13 of Figure 1 and the magnetic pole 21a of the magnetic element 21. Figure 3 is a schematic diagram showing the state of the inner component 10 of the vibration damping device 100 shown in Figure 1 moving in the z-direction. Figure 4 is a schematic diagram showing the relationship between the moving distance of the inner component 10 and the generated magnetic force in the vibration damping device 100 of Embodiment 1. Figure 5 is a schematic diagram showing the main structure of the vibration damping device 100A, a variant of the vibration damping device 100 of Embodiment 1. Figure 6 is a schematic diagram showing the relationship between the movement distance of the inner component 10 of the vibration damping device 100A in the modified example shown in Figure 5 and the generated magnetic force. Figure 7 is a schematic diagram showing one example of the state of the vibration damping devices 100 and 100A in Embodiment 1 in top view (viewed from the z-direction). Figure 8 is another example showing the state of the vibration damping devices 100 and 100A in Embodiment 1 in top view (viewed from the z-direction). Figure 9 is a schematic diagram showing the main structure of the vibration damping device 100B, a modified example of the vibration damping device 100 in Embodiment 1. Figure 10 is a schematic diagram showing the main structure of a modified vibration damping device 100C according to Embodiment 1. Figure 11 is a schematic diagram showing the main structure of a vibration damping device 200 according to Embodiment 2. Figure 12 is a schematic diagram showing the relationship between the movement distance of the inner component 10 and the generated load in the vibration damping device 100 shown in Figure 1, and the relationship between the expansion and contraction of the elastic component 30 and the generated load. Figure 13 is a schematic diagram showing the relationship between the movement distance of the inner component 10 and the generated magnetic force in the vibration damping device 200 according to Embodiment 2. Figure 14 is a schematic diagram showing the relationship between the movement distance of the inner component 10 and the generated magnetic force when the vibration attenuation device 100 in the vibration attenuation device 200 shown in Figure 11 is replaced with the vibration attenuation device 100A shown in Figure 5. Figure 15 is a schematic diagram showing the main structure of the vibration attenuation device 300 of Embodiment 3. Figure 16 is a schematic diagram showing the state in which the inner component 10 moves in the z2 direction from the vibration attenuation device 300 shown in Figure 15. Figure 17 is a schematic diagram showing the main structure of the vibration attenuation device 100D of Embodiment 1, which is a modified example of the vibration attenuation device 100 with the second end 12 removed.

100: Vibration attenuation device

10: Inner Components

11: Connecting Components

12, 13b: Second end

12a, 13a: Front-end

13: First end

20: External Components

21, 21A, 21B: Magnetic components

21a, 21b: Magnetic poles

Claims (11)

A vibration damping device includes an inner component and an outer component, the inner component and the outer component being configured to reciprocate relative to each other along a first direction, wherein the inner component is disposed inside the outer component in a second direction perpendicular to the first direction, and includes end components made of a magnetic material, the end components being composed of a first end and a second end disposed apart from each other in the first direction; the outer component includes a magnetic element configured to attract the end components in an equilibrium state, in which paired magnetic poles are disposed along the first direction, the paired magnetic poles being respectively disposed opposite to the first end and the second end in the second direction in an equilibrium state; the first end and the second end... It is configured such that the end member and the magnetic element are attracted to the magnetic poles of the magnetic element facing each other in a balanced state in a second direction, and the movement of the end member and the magnetic element in the second direction is restricted in a way that they do not come into contact with each other. The vibration damping device as claimed in claim 1, wherein the magnetic element is composed of a plurality of magnetic elements, the plurality of magnetic elements including at least one pair of magnetic elements disposed at positions opposite each other in a second direction, enclosing the inner component. The vibration damping device as described in claim 1 or 2, wherein the end component is made of a permanent magnet, the magnetic poles of which are set to be opposite in polarity to the end component. The vibration damping device as described in claim 1 or 2, wherein the end component is made of a soft magnetic material. The vibration damping device as described in claim 1 or 2, wherein the end member has a structure in which the width of the front end in the second direction in the first direction gradually decreases from the central axis to the outer side in a cross section including the central axis of the inner member. The vibration damping device as described in claim 1 or 2 further comprises an elastic component that applies a load in the opposite direction to the direction of movement in response to the relative movement of the inner component and the outer component in a first direction. The vibration damping device as claimed in claim 6, wherein the elastic member is connected to at least one of the inner member and the outer member. The vibration damping device as claimed in claim 1, wherein the magnetic element is an electromagnet configured as a pair of magnetic poles that can move in a first direction. An vibration damping device includes an inner component and an outer component, the inner component and the outer component being configured to reciprocate relative to each other along a first direction, wherein the inner component is disposed inside the outer component in a second direction perpendicular to the first direction, and includes an end component made of magnetic material disposed opposite to the magnetic poles of the outer component in the second direction; the outer component includes a magnetic element configured to attract the end component in an equilibrium state, the end component and the magnetic element being restricted from moving in the second direction without contacting each other, the magnetic element being an electromagnet configured to allow the paired magnetic poles to move in the first direction by changing the energized portion. The vibration damping device as described in claim 8 or 9, wherein the magnetic element has a plurality of coils arranged in a manner with the central axis along a first direction, and the magnetic poles are moved in the first direction by changing the portion of the coil that is energized among the plurality of coils. A vibration damping device includes an inner component and an outer component, the inner component and the outer component being configured to reciprocate relative to each other along a first direction. The inner component is disposed inside the outer component in a second direction perpendicular to the first direction and includes an end component made of a magnetic material, disposed opposite to the magnetic poles of the outer component in the second direction. The outer component includes a magnetic element configured to attract the end component in an equilibrium state. The end component and the magnetic element are restricted from moving in the second direction without contacting each other. The structure has a front end in a second direction in a cross section containing the central axis of the inner component whose width in the first direction gradually decreases from the central axis to the outer side.