JPH1086725A - Magnetic floating type suspension unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a magnetic floating type suspension unit constituted economically simply to improve the vibration elimination performance by utilizing the damping characteristic of a magnetic spring. SOLUTION: A magnetic spring is constituted from at least two permanent magnets 2, 4 spaced from each other relatively movably and having repulsion magnetic poles opposed to each other. Also, one 4 of two permanent magnets 2, 4 is mounted to a pedestal of a seat or the like and a distance between the permanent magnets 2, 4 separated from each other is varied through a rotary lever 42 to the external force inputted to the other permanent magnet to vary the spring constant or damping coefficient in the internal motion system so that the vibration elimination is easily controlled.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a magnetic levitation suspension unit provided with a magnetic spring having a plurality of permanent magnets.

[0002]

2. Description of the Related Art Conventionally, an automobile seat or an ambulance bed is provided with an anti-vibration unit for suppressing vibration transmitted from a vehicle body floor. It is used. Recently, there has been proposed an active suspension seat in which an actuator is attached to a vehicle seat and active vibration is actively controlled to improve a seating feeling.

[0003]

However, a vibration isolation unit using a metal spring, an air suspension, an air damper, or the like, requires 4 to 20 of the vibration transmitted from the vehicle body floor.
It was not possible to further improve the feeling of sitting or use by lowering the frequency of vibration of Hz. In addition, the active suspension seat is not only heavy and expensive, but also requires that the actuator be operated at all times. When the actuator is turned off, vibration is transmitted directly to the occupant via the actuator, and the feeling of sitting is impaired. there were.

The present invention has been made in view of the above-mentioned problems of the prior art, and is a magnetic levitation having an inexpensive and simple configuration in which the vibration isolation performance is improved by utilizing the damping characteristics of a magnetic spring. It is intended to provide a suspension unit.

[0005]

Means for Solving the Problems In order to achieve the above object, the present invention according to claim 1 of the present invention comprises at least two permanent magnets which are relatively movably separated from each other and have repulsive magnetic poles opposed to each other. Forming a magnetic spring, attaching one of the at least two permanent magnets to the pedestal, and changing a distance between the at least two permanent magnets via a rotating lever with respect to an external force input to the other permanent magnet. The magnetic levitation suspension unit is characterized in that a spring constant or a damping coefficient in the internal motion system is changed by the following.

According to a second aspect of the present invention, one end of a link linked to the rotary lever is pivotally connected to a permanent magnet attached to a pedestal, and the link is swung by rotation of the rotary lever. The distance is changed by means of

[0007]

Embodiments of the present invention will be described below with reference to the drawings. In the case of a magnetic spring structure having at least two permanent magnets spaced apart from each other and having the same magnetic pole facing each other, since the separated permanent magnets are not in contact with each other, ignoring friction loss of the structure itself, its static characteristics are input. Non-linear output (return) on the same line as time (going), and static magnetic field (position of magnets) with small input by utilizing the degree of freedom peculiar to non-contact pair and the instability of levitation control system , Negative decay is likely to occur.

The present invention has been made in view of this fact, and changes the geometrical dimension between two permanent magnets on the input side (going) and the output side (returning) by a mechanism in the movement stroke or an external force. By converting it into a repulsive force in the motion system, the repulsive force on the output side is made larger than the repulsive force on the input side from the equilibrium position of the two permanent magnets.

The basic principle will be described below. FIG. 1 is a schematic diagram showing an equilibrium position of two permanent magnets 2 and 4 on an input side and an output side. FIG. 2 shows a load applied to one of the permanent magnets and a balance between the two permanent magnets. 9 shows basic characteristics of a magnetic spring structure showing a relationship with a displacement amount from a position.

[0010] As shown in FIG. 1, respectively x ₀ the equilibrium position and the spring constant of the input side of the permanent magnet 4 with respect to the permanent magnet _2, k ₁ and then, x _1, the equilibrium position and the spring constant of the output side respectively k When _2, the area conversion between x ₀ ~x ₁ is performed, the following relation is established at each equilibrium position. −k ₁ / x ₀ + mg = 0 −k ₂ / x ₁ + mg = 0 k ₂ > k ₁

Accordingly, the static characteristics indicate negative damping characteristics as shown in FIG. 2, the potential difference at the position x ₁ and the position x ₀ can be considered as potential energy of oscillation.

Further, the model shown in FIG. 1 was manufactured, and the relationship between the load and the amount of displacement was actually measured while changing the time for applying the load. As a result, a graph as shown in FIG. 3 was obtained. this is,
When the two permanent magnets 2 and 4 approach the closest position, a large repulsive force acts. Also, when the amount of displacement from the equilibrium position changes minutely, friction loss occurs due to the damper effect of the magnetic spring. Is interpreted as the appearance of a damping term.

In FIG. 3, (a) is a graph in the case where a constant load is applied, and the time during which the load is applied in the order of (a), (b) and (c) is shortened. That is, the static characteristics differ depending on how the load is applied, and the impulse increases as the load application time increases.

Further, in the rare earth magnet, the strength of magnetization does not depend on the magnetic field. In other words, since the internal magnetic moment is hardly affected by the magnetic field, the magnetization intensity hardly changes on the demagnetization curve, and the value of the saturation magnetization is almost maintained. Therefore, in the rare-earth magnet, input and output can be considered using a charge model that assumes that magnetic charges are uniformly distributed on the end face.

FIG. 4 shows the concept, in which a magnet is defined as a set of magnets of the minimum unit, and the relationship between the forces between the unit magnets is classified into three and calculated. (A) withdrawing (r, since the same also m, defines the two types in one ^{1) f (1) = (} m 2 / r 2) dx 1 dy 1 dx 2 dy 2 f x (1) = f (1 _{^{) cosθ f z (1) =}} f (1) sinθ (b) repulsion _{^{f x (2) = f (}} 2) cosθ f z (2) = f (2) sinθ (c) rebound f _x ⁽³⁾ = f _{^{(3) cosθ f z (3}} ) = f (3) sinθ ^{_{Accordingly, -f x = 2f x (1}} ) -f x (2) -f x (3) -f z = 2f z (1) -f z ⁽²⁾ −f _z ⁽³⁾ Here, Coulomb's law is expressed as follows. Can be determined force by integrating the -f _x, the -f _z in the range of dimensions of the magnet.

As shown in FIG. 5, this state is completely deviated from the state where the opposing magnets are completely wrapped for each magnetic gap (the amount of x-axis movement = 0 mm) (the amount of x-axis movement = 5).
0 mm) is calculated in the graph of FIG. However, it is defined as "the internal magnetic moment is constant", but when the magnetic gap is small, the disturbance is generated around the magnet, so the correction is made.

The above calculation results are also substantially coincident with the actually measured values. The force moving from the point a to the point b in FIG. 2 is represented by the load in the x direction, and the output is represented by the load in the z direction. <Output relationship is statically clear.

FIG. 7 shows that the magnet shown in FIG. 5 is kept at a separation distance of 3 mm, moved from a completely displaced state to a completely wrapped state, and further moved from this state to a completely displaced state. It is the graph showing the relationship at the time of doing. This graph shows that the absolute value of the load in the x direction is the same and the output direction is reversed, and the output direction is reversed. When approaching the fully wrapped state, resistance or attenuation occurs, and the state shifts from the completely wrapped state to a completely deviated state The case indicates that it will be accelerated. By utilizing this characteristic for a non-contact damper, it becomes possible to reduce vibration energy in low, medium, and high frequency regions (0 to 50 Hz) that can be perceived by a person who could not be achieved by the conventional damper, that is, to improve the vibration transmission rate. Was.

Further, as shown in FIG. 8, when the rotation angle of the facing magnet was changed, a graph as shown in FIG. 9 was obtained. Naturally, as the facing area decreases, the maximum load decreases, indicating that the output can be changed via area conversion by applying a predetermined input.

FIG. 10 is a graph showing the relationship between the inter-magnet distance and the load when a neodymium magnet is used as the permanent magnet. The repulsive force increases as the mass increases. Here, the repulsive force F is represented by F∝Br ² × (geometric dimension) Br: strength of magnetization, and the geometric dimension is a separation distance of an opposing magnet, an opposing area, a magnetic flux density, and a magnetic field. Means the size determined by the strength of If the magnet material is the same, the strength of the magnetization (Br) is constant, so that the repulsive force of the magnet can be changed by changing the geometric dimensions.

FIG. 11 shows a specific magnetic spring model in which the geometrical dimensions of two opposing permanent magnets 2 and 4 are changed using a rotating lever. In FIG. 11, the base 6 and the top plate 8 extending in parallel to each other
They are connected to each other by a pair of left and right X-links 10 composed of books 10a and 10b. Links 10a, 10
b has one end pivotally attached to the base 6 and the top plate 8, respectively, and the other end of the links 10a and 10b has an upper slider 12 slidably attached to the top plate 8 and a slideable base 6. Are pivotally attached to the lower sliders 14 attached to the respective sliders.

The permanent magnet 2 is fixed to a base 6, and the same (repulsive) magnetic poles as the permanent magnet 2 oppose the permanent magnet 4.
Is fixed to a mounting base 34 slidably mounted on a frame 32 erected on the base 6. Mounting stand 34
The other end of the link 36 is pivotally connected to the first support base 3 fixed to one side of the lower slider 14.
It is pivoted to 8. A second support 40 is fixed to the opposite side of the lower slider 14, and a pin 44 is attached to the other end of the lever 42 having one end pivotally attached to the second support 40. The pin 44 is loosely inserted into a long hole 36 a formed in an intermediate portion of the link 36, and is attached to a lower end of an arm 46 pivotally attached to the top plate 8. Therefore, the lever 42 can rotate around the pivotally connected end with the second support 40, and the link 36 swings with the rotation of the lever 42, and the separation distance between the permanent magnets 2 and 4 changes. I do.

In the above configuration, when an input is applied to the base 6 and the base 6 moves toward the top plate 8, the lever 42 rotates in the direction of the arrow in the figure, and the two permanent magnets 2, 4 approach each other. I do. Since the permanent magnets 2 and 4 face the same magnetic pole, the repulsive force gradually increases with the rotation of the lever 42, and when the permanent magnets 2 and 4 pass the closest position, the permanent magnets 2 and 4 Depart from each other. While the base 6 makes one reciprocation with respect to the top plate 8, the magnetic spring of FIG. 11 shows a negative damping characteristic as shown in FIG. The position where the maximum repulsion occurs can be appropriately adjusted by changing the length of the lever 42 according to the input. In FIG. 11, two permanent magnets 2 and 4 are configured to be opposed to each other. However, a plurality of sets of magnetic springs may be provided by further facing two or more permanent magnets.

Therefore, the base 6 is fixed to a vehicle or the like, and the top plate 8
When a seat or a pedestal such as a bed or a bed of a stretcher is placed on the top, the magnetic spring of FIG. 11 functions as a magnetic levitation suspension unit, attenuates periodic external force in a minute vibration region, and As described above, low frequency can be improved by using the negative damping of the magnetic spring, and the resonance point can be set regardless of the weight of the person sitting on the seat or the person lying on the bed due to the nonlinear characteristics of the permanent magnet. Can be almost matched.

Next, the dynamic characteristics of the magnetic spring will be described with reference to a simplified basic model shown in FIG.
The input F in FIG. 12 is a force caused by a geometric dimensional change such as the area conversion of the permanent magnet. In FIG. 12, if the spring constant is k, the damping coefficient is r, and the harmonic vibration input to the mass m is F (t), the state equation is as follows:

(Equation 1) It is expressed as

Here, assuming that the equilibrium position is x ₀ and the displacement from the equilibrium position is y,

(Equation 2)

Here, if k / x ₀ ² = k ′,

(Equation 3)

[0028] The harmonic vibration ^F (t) = Fe iωt Distant, y
= Xe ^iωt ,

(Equation 4) Here, φ indicates a phase delay.

(Equation 5) Therefore, the resonance frequency ω ₀ is

(Equation 6)

Here, equation (2) can be further expressed as follows.

(Equation 7) When y is x and considering the third-order term,

(Equation 8)

In equation (3), an attenuation term of −bx ² appears in the second-order term. If equation (3) is replaced with a simpler image,

(Equation 9)

Here, assuming that x = x ₀ cosωt,

(Equation 10)

[0032] That is, in the micro-vibrating region for periodic external force, constantly have involved certain repulsive force _{((b / 2) x 0} 2) is, thus attenuating a periodic external force that force .

The dynamic characteristics of the magnet alone were examined using the apparatus shown in FIG. 13, and the results shown in FIGS. 14 and 15 were obtained.

In the apparatus shown in FIG. 13, the two permanent magnets 2 and 4 are opposed to each other, and the X-link 10
Is a device that changes the separation distance via the.

In FIGS. 14 and 15, the horizontal axis represents frequency (Hz), and the vertical axis represents vibration transmissibility (G / G). In FIG. 14, (a), (b),
(C), (d), (e) and (f) are each 50 × 5
0x10mm, 50x50x15mm, 50x50x2
0mm, 75 × 75 × 15mm, 75 × 75 × 20m
The same load of 30 kg was applied using a magnet of 75 mm x 75 mm x 25 mm, whereas in FIG.
Different loads of 53 kg and 80 kg were applied using the same magnet of 0 × 50 × 20 mm.

FIGS. 14 and 15 show the non-linear characteristics of the magnetic spring. From both figures, when the load is the same, as the magnet size increases, the resonance point shifts to a lower frequency range, and when the magnet size is the same. It can be seen that the resonance point does not change even when the load changes, and that the vibration transmissibility at the resonance point changes depending on the load.

FIG. 16 is a graph showing the dynamic characteristics of a conventional passenger car seat as a comparative example. The vibration transmissibility is high as a whole, and the resonance point and the vibration transmissibility both fluctuate with the load fluctuation. I have.

By the way, in the above equation (1), when the geometrical size between the opposing permanent magnets is changed by a mechanism in the movement stroke or an external force, the spring constant k changes with time as shown in FIG. And the value of + k ′ and −k ′ are alternately taken every half cycle in a cycle T = 2π / ω. Therefore, equation (1) is expressed as follows.

[Equation 11] (I) When 0 <t <π / ω,

(Equation 12) (Ii) When π / ω ≦ t <2π / ω,

(Equation 13)

Here, assuming that the equilibrium position when 0 <t <π / ω is x ₀ and the displacement from the equilibrium position is y ₁ ,

[Equation 14]

Here, if (n−k ′) / x ₀ ² = k ₁ ′,

(Equation 15)

[0041] The harmonic vibration ^F (t) = Fe iωt Distant, y
₁ = xe ^iωt ,

(Equation 16) Here, φ indicates a phase delay.

[Equation 17] Therefore, the resonance frequency ω ₀ is

(Equation 18)

Similarly, when π / ω ≦ t <2π / ω,

[Equation 19] Therefore, divergence occurs when y ₁ <y ₂ .

Generally, the self-excited vibration system can be replaced with a spring-mass system having negative viscous damping, and vibration energy is introduced from the outside during vibration. And various resistances are generated, and energy is lost.

However, when vibration energy is introduced as an external force into the magnetic spring having a negative damping characteristic of the present invention, as described above, it diverges at y ₁ <y ₂ , and as it continues to diverge, the amplitude gradually increases. The system is destroyed, or
By adding a damping term that increases as the displacement increases to the above-mentioned equation of state, a positive damping acts and a steady oscillation is performed in a state of being balanced with the negative damping. That is, similarly to the spring constant k (t), the damping coefficient is also variable, and the equation (1) can be further rewritten as follows.

(Equation 20)

In the vibration system having a magnetic spring according to the present invention, an energy change / conversion system which induces continuous vibration and divergent vibration is present inside the vibration system, and a positive damping term is mechanically added to the above state equation. Thereby, the following equation of state can be obtained.

(Equation 21)

In this state equation, when r ₂ ≠ 0, when x increases, the three terms on the left side increase, and a positive damping works due to the damping term of the spring term. Therefore, as the internal excitation characteristics of the permanent magnet, when the displacement is small, the damping is a negative damping, and the positive damping works as the displacement increases, so that the vibration becomes steady at an amplitude where the positive and the negative damping balance.

When the magnitude of at least one of the mass, damping coefficient and spring constant of the vibration system changes with time, the resulting vibration is called coefficient excitation vibration. 4), (5), and (6) are coefficient excitation vibrations in which the excitation source itself vibrates, and non-vibration energy in the system is converted into vibration excitation in the system to generate vibration.

Normally, the supplied energy is obtained by converting a part of the power energy, so if the power energy has an upper limit, the supplied energy is limited, and the amplitude is suppressed when this becomes equal to the consumed energy. The potential energy of the permanent magnet is independent of the power energy of the system and can widen the gap with the energy consumption. However, if the maximum energy product per mass of the permanent magnet increases, this gap can be further increased. Can be expanded to 1
By making the supplied energy due to negative damping greater than the energy consumed due to damping during the cycle, the vibration energy is increased.

As described above, in the equation (1), the damping coefficient r and the spring constant (coefficient) k can be freely controlled. For example, in the schematic diagram of FIG. 1, the permanent magnet 4 is at the lowermost end. At this time, by maximizing the area facing the permanent magnet 2, the amplitude can be attenuated, and it can be applied to a magnetic brake, a dynamic vibration absorber and the like. In addition, since the repulsive force can be increased by maximizing the facing area after the permanent magnet 4 is separated from the lowermost end toward the uppermost end, the permanent magnet 4 can be applied to a generator, an amplifier, and the like.

Further, as can be seen from the solution of the above state equation, the coefficient excitation vibration system of the present invention reduces the fluctuation of the amplitude by moving the excitation frequency even if the natural frequency changes due to the fluctuation of the load. can do. In other words, the excitation frequency is variable, and the resonance frequency can be manually or automatically tracked to operate at a position where the resonance frequency of the frequency characteristic always decreases, and used as an anti-vibration device for an automobile seat. Thereby, the vibration insulation can be improved, and the individual performance thereof can be improved. For example, the resonance point can be lowered to 4 Hz or less. Also, it is possible to improve the low frequency by using the negative attenuation and to absorb the weight difference by specializing the nonlinear characteristics of the permanent magnet.

Here, a vibration experiment was performed using a pad combining urethane and fiber or a bed type vibration isolation unit employing the magnetic spring structure of the present invention.
The result as shown in FIG. 18 was obtained.

As can be seen from the graph of FIG. 18, the device employing the magnetic spring structure of the present invention together with the pad reduces the resonance frequency to 3 Hz, which is half or less, as compared with the device employing only the pad. It was found to be very effective. Furthermore, by performing the semi-active control, the vibration transmissibility at the resonance point could be reduced to about 1/3.

Further, the magnetic lev of FIG.
When the dynamic characteristics of the unit were examined, the results shown in FIG. 20 were obtained.

The maglev unit shown in FIG. 19 supports a sheet 78 on a base 74 via a plurality of swing levers 76 so as to be able to swing, and has two permanent magnets 80, 8 on the upper surface of the base 74.
2 are fixed at a predetermined distance, and a permanent magnetic pole 84 having the same magnetic pole facing the permanent magnets 80 and 82 is fixed to the lower surface of the sheet 78. The permanent magnetic poles 80, 8
As 2,84, one having a size of 75 × 75 × 25 mm was used.

This Maghreb unit is 53kg, 75k
Although different loads of g and 80 kg were applied, as shown in FIG. 20, the difference in the vibration transmissibility due to the change in the load could be suppressed small, and the resonance points could be substantially matched.

Further, when the riding comfort evaluation of the passenger car seat, the suspension seat A, the suspension seat B, and the maglev unit according to the present invention was examined, the result as shown in FIG. 21 was obtained. The load of the maglev unit was 53 kg, and a 75 × 75 × 25 mm permanent magnet was used. In the drawing, “fixed” indicates a state in which the seat is merely fixed to the suspension, and urethane, gel, and styrene indicate a cushion material mounted on the unit.

Here, "SAE" is used as a ride comfort evaluation constant.
paper 820309 "and a ride comfort index R (Ride Number) expressed by the following equation: R = K / (A.B.fn) The variables A, B and fn are transfer functions of the seat (T.F.). .), And shows the following values: A: Maximum value of TF B: TF value at 10 Hz fn: Resonance frequency or frequency at which A appears K: A completely different sheet Expressed ride comfort coefficient (K value is set to "1" because various seats were used.) The ISO ride comfort evaluation indicates that the ride comfort is good with a small numerical value. The higher the value, the better the ride.

As can be seen from FIG. 21, among the seats evaluated for ride comfort, the seats for passenger cars are 0.2 to 0.3 (all urethane type), 0.3 to 0.5 (spring type), and weight adjustment. The maglev unit of the present invention has better ride comfort than other seats, and has a ride comfort evaluation of 0.75 to 1.60 for a 53 kg load. A constant was obtained.

FIG. 22 shows the riding comfort evaluation constant of the maglev unit when the load is changed. As can be seen from this figure, a riding comfort evaluation constant of 0.7 or more is obtained for any load. This shows the good riding comfort of the maglev unit according to the present invention.

FIG. 23 shows dynamic characteristics of a passenger car seat, a suspension seat A, a suspension seat B, and a maglev unit according to the present invention.
In the drawing, (a) is a passenger car seat, (b) and (c) are suspension seats A with a load of 53 kg and 75 kg, respectively, and (d) and (e) are suspension seats B and 45 kg and 75 kg, respectively. (F) and (g) show the case where the cushioning material is changed in the maglev unit according to the present invention, and (h) shows the case where the maglev unit according to the present invention is semi-actively controlled. .

As can be seen from FIG. 23, the resonance point of the maglev unit is between 2 and 3 Hz, and the vibration transmissibility in the low and high frequency regions is small. Furthermore, it has been confirmed that by performing the semi-active control, the resonance point can be further reduced and the vibration transmissibility can be reduced in a wide frequency range.

[0062]

Since the present invention is configured as described above, it has the following effects. According to the first aspect of the present invention, the spring constant or the damping coefficient in the internal motion system is changed by changing the separation distance between at least two permanent magnets via the rotating lever. As a result, passive control, semi-active control or active control of the suspension unit can be easily performed.

According to the second aspect of the present invention, one end of the link interlocking with the rotary lever is pivotally connected to the permanent magnet attached to the pedestal, and the rotation of the rotary lever causes the link to swing, so that the permanent magnet is rotated. By changing the distance between the two, the position where the maximum repulsive force is generated can be adjusted by changing the lever ratio, and not only can the magnetic field as a potential field be used effectively, but also the magnetic spring Any positive, zero or negative damping characteristic can be provided;
Reduction of vibration transmissibility in high frequency range, absorption of weight difference, and
It is also effective in reducing vibration energy in a low frequency region such as lowering the resonance point.

[Brief description of the drawings]

FIG. 1 is a schematic view showing an equilibrium position between an input side and an output side of two permanent magnets in a magnetic spring according to the present invention.

FIG. 2 is a graph of basic characteristics showing a relationship between an applied load and a displacement amount of a permanent magnet from an equilibrium position in the magnetic spring of FIG.

FIG. 3 is a graph showing a relationship between an actually measured load and a displacement amount.

FIG. 4 is a schematic diagram showing the concept of input and output in a charge model assuming that magnetic charges are uniformly distributed on the end face of a permanent magnet, where (a) shows attraction, (b) shows repulsion,
(C) shows the repulsion of a part different from (b).

FIG. 5 is a schematic diagram of a case where one of the permanent magnets whose magnetic poles are opposed to each other is moved relative to the other (the facing area is changed).

FIG. 6 is a graph showing a load in the X-axis and Z-axis directions with respect to an X-axis movement amount when calculated based on FIG. 5;

FIG. 7 is a diagram showing a state in which the distance between the permanent magnets shown in FIG.
6 is a graph showing the relationship between the displacement and the load when one is moved from a completely shifted state to the other from a completely wrapped state, and further moved from this state to a completely shifted state.

FIG. 8 is a schematic diagram of a case where one of the permanent magnets having the same magnetic poles is rotated with respect to the other (the facing area is changed).

FIG. 9 is a graph showing the maximum load with respect to the facing area when the permanent magnet is rotated based on FIG.

FIG. 10 is a graph showing a relationship between a distance between magnets and a load when a neodymium magnet is used as a permanent magnet.

FIG. 11 is a front view of a magnetic spring model in which a geometric dimension is changed by appropriately changing a distance between opposed permanent magnets.

FIG. 12 is a basic model for describing characteristics of a magnetic spring.

FIG. 13 is a front view of an apparatus used for obtaining static and dynamic characteristics of a magnetic spring when the area is not converted.

14 shows dynamic characteristics of a magnetic spring obtained by using the apparatus of FIG. 13, where (a) shows 50 × 50 × 10 mm
(B) is 50 × 50 × 15m when using the magnet of
(c) when a magnet of m is used is 50 × 50 × 20.
(d) when a magnet of mm is used is 75 × 75 × 1
(E) when using a 5 mm magnet is 75 × 75 ×
(F) when a 20 mm magnet is used is 75 × 75
It is a graph at the time of using the magnet of x25mm.

FIG. 15 is a graph showing dynamic characteristics of a magnetic spring obtained by using the apparatus of FIG. 13 and changing the load using the same magnet.

FIG. 16 is a graph showing dynamic characteristics of a conventional passenger car seat as a comparative example.

FIG. 17 is a graph showing changes over time of a spring constant and a coefficient in the magnetic spring structure of the present invention.

FIG. 18 is a graph showing dynamic characteristics of a bed-type anti-vibration unit when only a pad is used, when a pad and a magnetic spring are used, and when semi-active control is further performed.

FIG. 19 is a front view of a maglev unit used for measuring dynamic characteristics of a magnetic spring.

FIG. 20 is a graph showing dynamic characteristics of the maglev unit measured using the maglev unit of FIG. 19;

FIG. 21 is a graph showing ride comfort evaluation constants measured using various seats including a maglev unit.

FIG. 22 is a graph showing a riding comfort evaluation constant of a maglev unit measured by changing a load and a cushion material.

FIG. 23 is a graph showing dynamic characteristics measured using various sheets including a Maghreb unit.

[Explanation of symbols]

 2,4 permanent magnet 6 base 8 top plate 10 X link 12 upper slider 14 lower slider 32 frame 34 mounting base 36 link 42 lever 46 arm

Claims (2)

[Claims] 1. A magnetic spring comprising at least two permanent magnets which are relatively movably separated from each other and have repulsive magnetic poles facing each other, one of the at least two permanent magnets is attached to a pedestal, and the other is input to the other permanent magnet. A magnetic levitation suspension characterized in that a spring constant or a damping coefficient in an internal motion system is changed by changing a separation distance between the at least two permanent magnets via a rotating lever in response to an external force. unit. 2. An end of a link linked to the rotating lever is pivotally connected to a permanent magnet attached to a pedestal, and the link is swung by rotation of the rotating lever to change the separation distance. The magnetic levitation suspension unit according to claim 1.