JP2000205333A - Vibration relaxation unit and seat using it - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve vibration absorption ability and shock relaxation ability by arranging a compression coil spring and a super viscous elastic body in parallel between a bottom member and a ceiling member, and fixing both end parts of at least either of the compression coil spring and the super viscous elastic body to both the bottom member and the ceiling member. SOLUTION: In this vibration relaxation unit 7, a bottomed cylinder shaped bottom member 8 is slidably inserted in a similar bottomed cylinder shaped ceiling member 9 having a little larger inner diameter than the outer diameter of the bottom member 8, and between the bottom member 8 and the ceiling member 9, a compression coil spring 10 and a round bar-like super viscous elastic body 11 are concentrically arranged in parallel. At this time, both end parts of the super viscous elastic body 11 are fixed to both the bottom member 8 and the ceiling member 9, and both end parts of the coil spring 10 are pressure connected to the bottom member 8 and the ceiling member 9. Hereby, vibration and shock can be absorbed by deformation of the compression coil spring and the super viscous elastic body, and further large vibration damping effect can be realized.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for transporting a load placed between an outdoor unit or an engine drive generator of an engine driven compression air conditioner and an installation surface, or on a bed of a vehicle or a ship. A vibration mitigation unit arranged between the mounting surface and a vibration eliminator, and a built-in vibration mitigation unit, such as a motorcycle or a motor vehicle such as a scooter, a land vehicle such as a small snowmobile, a watercraft, The present invention relates to a seat used for a watercraft such as a high-speed boat.

[0002]

2. Description of the Related Art Conventionally, as a device for reducing vibration, there is a cushion unit using, for example, hydraulic pressure. In this method, a piston having an orifice penetratingly formed therein is slidably disposed in a cylinder sealed by a cylinder cap, and a piston rod that penetrates the cylinder cap oil-tightly is connected to the piston. A hydraulic shock absorber filled with hydraulic oil therein, and a spring arranged on the outer periphery of the hydraulic shock absorber and having one end fixed to the cylinder and the other end fixed to the piston rod. Have been.

[0003] In the above-mentioned hydraulic shock absorber, when the hydraulic oil passes through the throttle as the piston slides, the hydraulic oil generates heat and absorbs the sliding energy at the throttle portion, whereby the vibration can be absorbed. Become. In addition, the elastic force of the spring supports the static load, prevents the piston from bottoming on the bottom of the cylinder or the cap, and enables vibration absorption while supporting the static load.

[0004] As a material capable of absorbing vibration, there is a mat having a compression coil spring built in a skin member, and a sheet having a foamed urethane foam built in a skin member. This seat can be used for motorcycles and motor vehicles such as motorcycles and scooters, as well as land vehicles such as small snowmobiles, hydroplanes,
It is arranged on a watercraft such as a high-speed boat to reduce engine vibration to passengers and passengers, unevenness of road surface, and vibration due to waves on the water surface.

Further, there has been proposed a motorcycle seat in which a cushion body in which a foam such as urethane and a superabsorbent elastic body are layered is wrapped with a skin and mounted on a bottom plate (JP-A-2-286481). reference).

[0006] The applicant of the present invention in Japanese Patent Application No. Hei 7-132398 has set a storage elastic coefficient corresponding to the elastic modulus of a superabsorbent elastic material to be smaller than that of a metal spring (for example, 0). 0.05 to 0.4 MPa), while the loss elastic modulus is overwhelmingly larger than that of the metal spring, and the loss coefficient obtained by dividing the loss elastic coefficient by the storage elastic coefficient is set to 0.35 to 0.5. Propose that.

In this method, the vibration of the vehicle is attenuated during the transmission of the seat because of the large loss elastic modulus. In addition, since the sheet has a small storage elastic modulus, it is necessary to reduce the resonance frequency, increase the area higher than the resonance frequency, and increase the area where the vibration transmissibility is 1 or less, so that the sheet can reliably reduce the vibration transmission. Can be.

Here, in land vehicles, the vehicle may jump from the road surface when passing through large unevenness on the road surface, and in water vehicles, when running through a large wave on the water surface, may jump from the water surface and land or land. . At this time, the person on the seat is pressed against the seat by its own inertia when the vehicle jumps,
Further, at the time of landing or landing, it is pressed against the sheet by its own inertia of the falling motion. For this reason, it is required that a large impact force is not applied to the occupant or the occupant due to the inertia of the seat.

Since the superabsorbent elastic body proposed by the applicant of the present invention has a small storage elastic modulus, the superabsorbent elastic body is largely deformed even when an inertial force acts, so that it is possible to prevent the generation of an impact force. it can.

[0010]

However, the above-mentioned conventional hydraulic shock absorber requires a structure and parts for preventing oil leakage, and also requires a process for filling oil. However, there is a problem that the cost of the vibration mitigation unit increases as a result.

The hydraulic shock absorber has a longer overall length because the piston rod projects from the cylinder cap in addition to the length of the cylinder. Therefore, there is a problem in that the height of the transported object and the outdoor unit is increased, and a large arrangement space is required. In addition, there is also a problem that the seat height becomes abnormally large when built in the seat.

In addition, there is a problem that the vibration cannot be absorbed only by the compression coil spring, particularly when the vibration has a frequency close to the resonance point.

Further, foamed urethane has a large storage elastic modulus and cannot be largely displaced by a static load from the seat. As a result, the impact when the vehicle body jumps due to unevenness of the road surface or the hull due to the waves is reduced. There is a problem that the displacement cannot be alleviated by the displacement, and a large load acts on the occupant and the occupant as a reaction force. Further, there is a problem that the loss coefficient cannot be increased with urethane foam, and as a result, the loss elastic modulus is small and the function of absorbing vibration due to internal heat generation is small.

Further, when the urethane and the superabsorbent elastic body are merely layered, the superabsorbent elastic body has a small storage elastic modulus and a large loss elastic modulus. It makes it difficult for the sinking person to return to the original position early due to the repulsive force of the superabsorbent elastic body. For this reason, there is a problem that a person who sinks into the sheet cannot quickly recover the view position before jumping.

Note that a sinusoidal strain ε = ε ₀ e is applied to the polymer sample.
^{Given iWt} (i = (-1) ^1/2 , ω = 2π × frequency, t = time), the sinusoidal stress is of the same frequency but divided into distortion and in-phase and 90 ° advanced. σ =
(Σ ′ + iσ ″) occurs. When this σ is expressed by the following equation, σ = Е ^* (w) ε = [Е ′ (w) + i (Е ″ (w)] ε ₀ e ^iWt (1) Е ^* (w) The modulus Е ″ (w) is the storage modulus or the storage modulus referred to in the present application, and Е ″ (w) is the loss modulus or the loss modulus referred to in the present application.The storage modulus is specifically a test based on JIS K7198. Is the real part of the complex modulus measured by (JIS K7198)
Is referred to as the dynamic storage modulus Е ′), and the magnitude of the in-phase stress component when a unit of sine strain is applied. Similarly, the loss modulus is the imaginary part of the complex modulus (in JIS K7198, the dynamic loss modulus 弾 性 ′).
'), The phase when the unit sine distortion is applied is 90 °
It can be obtained as the magnitude of the advanced stress component.

The present invention has been made in view of the above problems, and provides a vibration damping unit that is compact, has high vibration absorbing ability and shock absorbing ability, and can quickly recover from deformation due to load. That is the task.

[0017]

According to the first aspect of the present invention, a compression coil spring and a super-viscous elastic body are disposed in parallel between a bottom member and a ceiling member, and the coil spring and the super-viscous elastic body are arranged in parallel. Characterized in that at least one of both ends is fixed to both the bottom member and the ceiling member.

According to a second aspect of the present invention, a urethane foam is incorporated in a skin member, a gap is provided in the urethane, and a compression coil spring is provided between the bottom member and the ceiling member in the gap. And a super-viscous elastic body are arranged in parallel, and a vibration damping unit is provided in which at least one end of the coil spring and the super-viscous elastic body are fixed to both the bottom member and the ceiling member. Is a sheet characterized by the following.

[0019]

According to the vibration damping unit according to the first aspect of the present invention, the compression coil spring and the super-viscous elastic body are arranged in parallel between the bottom member and the ceiling member. Since at least one end of the viscous elastic body is fixed to both the bottom member and the ceiling member, vibrations and shocks can be absorbed by deformation of the compression coil spring and the super viscous elastic body. It can be performed early due to the elasticity of the coil spring.

Further, since it is integrated as an anti-vibration unit, handling and assembly can be facilitated. Further, since the super-viscous elastic body is used without using the hydraulic oil, maintenance can be facilitated. Also, without using a cylinder, each part of the entire super-viscous elastic body generates internal friction and generates heat.
It can be made compact, so that the ratio of vibration damping effect / volume can be increased, and a large damping effect can be realized with a smaller size than when oil is used.

According to the seat according to the second aspect of the present invention, since the void is provided in the urethane foam disposed in the leather member, and the vibration damping unit is provided in the void, the vehicle is provided. The vibration damping unit can be easily incorporated into the seat. Therefore, it is possible to recover the visibility position early after the jump landing and landing while securing the vibration absorption function, with the limited sheet size.

That is, since the super-viscous elastic body has a larger loss elastic modulus, that is, a loss elastic coefficient than urethane foam, it is possible to reliably attenuate vibration. In addition, the super-viscous elastic body has a lower storage elastic modulus and lower elasticity than urethane foam, but the elasticity of the coil spring is large, so it can compensate for this and jump while absorbing vibration. Early and later visual field recovery can be enabled.

[0023]

Embodiments of the present invention will be described below with reference to the accompanying drawings. FIGS. 1 and 2 are views for explaining a vibration damping unit according to a first embodiment of the present invention. FIG. 1 is a front view of a main part of an outdoor unit to which the vibration damping unit is applied. 2 is a sectional front view of the vibration damping unit.

In FIG. 1, reference numeral 1 denotes an outdoor unit for housing an engine of an engine-driven compression type air conditioner.
Has a bottom plate 3 on which the engine and the like are installed and a side plate 4 surrounding the bottom plate 3. The outdoor unit 1 is installed on a base 6 fixed to a floor 5 with four sets of vibration damping units 7 of the present embodiment interposed therebetween.

The vibration damping unit 7 slidably inserts the bottomed cylindrical bottom member 8 into the similarly bottomed cylindrical ceiling member 9 having an inner diameter slightly larger than the outer diameter of the bottom member 8. A compression coil spring 10 and a round rod-shaped super-viscous elastic body 11 are concentrically arranged in parallel between the bottom member 8 and the ceiling member 9. Both ends of the super-viscous elastic body 11 are fixed to both the bottom member 8 and the ceiling member 9, and both ends of the coil spring 10 are pressed against the bottom member 8 and the ceiling member 9.

Mounting plates 12 and 13 are fixed to the bottom member 8 and the ceiling member 9 by welding or the like. The mounting plates 12 and 13 are attached to the bottom plate 3 and the base 6 of the outdoor unit 1.
Is fixed by bolts or the like.

Specifically, the super-viscous elastic body 11 is made of, for example, an ultra-soft urethane elastomer as a matrix resin and a resin microballoon in the matrix resin in an amount of 1 to 5%.
(% By weight) is used. When a resin microballoon is mixed with the ultra-soft urethane elastomer, if the mixing amount (% by weight) of the resin microballoon with respect to the urethane elastomer is 1% or less, the mixture is separated into two layers after casting and curing. Amount (weight%) is 5
% Or more, the viscosity after mixing is so high that air enters during casting.

The ultra-soft urethane elastomer used as the matrix resin is, for example, a mixture of a trifunctional polyol and a difunctional polyol (polyether-based polyol, polyester-based polyol), triallyl isocyanurate, MDI (diphenylmethane diisocyanate). ) / TDI (tolylene diisocyanate) prepolymer, bismuth-based catalyst, tin-based catalyst, phthalic acid-based plasticizer, etc. are mixed, and the hardness of a soft material manufactured by Kobunshi Keiki Co., Ltd. is measured. It is a urethane elastomer having a hardness of 15 or less according to Asker C hardness tester which is a durometer.

The resin microballoon mixed into the matrix resin is an outer shell of vinylidene chloride-based resin (vinylidene chloride acrylonitrile copolymer) (average particle size: 40 to 60 microns, particle size range: 10 to 100 microns).
Butene gas is contained inside.

In the outdoor unit 1, the vibration from the engine can be absorbed by the vibration reduction unit 7.
Looking at this vibration absorbing action in detail, first, when a downward load acts on the vibration damping unit 7 due to the vibration,
The compression coil spring 10 and the super-viscous elastic body 11 are compressed and deformed, and the deformation absorbs the load. Thereafter, the repulsive force of the super-viscous elastic body 11 and the larger compression coil spring 10 Due to the resilience, the compressive deformation is quickly recovered and restored, and the load acting next is absorbed. By repeating this operation, the vibration from the engine is reliably absorbed.

As described above, the compression coil spring 1
0 and the super-viscous elastic body 11 are arranged in parallel and attached and fixed to the bottom member 8 and the ceiling member 9, so that the deformation of the super-viscous elastic body 11 due to the load is promptly performed by the elastic force of the spring 10. As a result, the vibration from the engine can be reduced and the effect of absorbing the vibration can be improved.

3 and 4 show a second embodiment of the first aspect of the present invention. FIG. 3 is a schematic view showing an arrangement state of a super-viscous elastic body.
FIG. 4 is a sectional side view of a main part. The second embodiment is an example in which a vibration damping unit based on the same concept as the vibration damping unit 7 is adopted for a saddle such as a two-wheeled or three-wheeled vehicle. More specifically, as shown in FIG.
Is divided into an upper seat tube 27 and a lower seat tube 28 connected to the saddle 25, and a vibration damping unit 29 is disposed between the two seat tubes 27, 28.

In the vibration damping unit 29, as shown in FIG. 4, both ends of the ceiling member 30 and the bottom member 31 attached to the lower end of the upper sheet tube 27 and the upper end of the lower sheet tube 28, respectively, cannot be pulled out. A rod 32 having an enlarged diameter is slidably inserted therein, and a cylindrical super-viscous elastic body 33 and a compression coil spring 34 are concentrically provided between the steps 30a and 31a of the ceiling member 30 and the bottom member 31. The two ends of the super-viscous elastic body 33 and the compression coil spring 34 are fixed to the steps 30a and 31a. The exposed portions of the super-viscous elastic body 33 and the compression coil spring 34 between the upper sheet tube 27 and the lower sheet tube 28 are covered with a rubber boot 35.

In the vibration mitigation unit 29, when a load is applied by road surface vibration, the super-viscous elastic body 33 and the compression coil spring 34 are compressed and deformed by the load, and the load is absorbed by the deformation. Due to the repulsive force of the super-viscous elastic body 33 and the resilient force of the compression coil spring 34 which is larger than the above, the compression deformation is recovered and restored, and the vibration from the road surface is reliably absorbed, and the operation is performed. Ride comfort can be improved.

FIG. 5 is a sectional front view of a front fork showing a third embodiment of the present invention. Book 3
The embodiment is an example in which the invention is applied to a front fork 38 of a two- or three-wheeled vehicle. Specifically, a vibration damping unit 39 is provided between the lower end surface of the upper fork 40 fixed to the bracket 37 at the lower end of the steering shaft 36 and the bottom of the lower fork 41.
Are arranged.

In the vibration damping unit 39, a rod 45 is slidably inserted through a ceiling member 42 fixed to the lower end surface of the upper fork 40 and a bottom (bottom member) 41a of the lower fork 41. And a bottom portion 41a, a cylindrical super-viscous elastic body 43 and a compression coil spring 44 are concentrically arranged in parallel to each other.
Both ends of the compression coil spring 3 and the compression coil spring 44 are fixed to the ceiling member 42 and the bottom 41a. Reference numeral 46 denotes a rubber boot for preventing rainwater, mud, and the like from entering the sliding portion between the upper fork 40 and the lower fork 41.

In the vibration reducing unit 39, when a load is applied due to road surface vibration, the super-viscous elastic body 43 and the compression coil spring 44 are compressed and deformed by the load, and the load is absorbed by the deformation. By the repulsive force of the super-viscous elastic body 43 and the resilient force of the compression coil spring 44 which is larger than the above, the compression deformation is recovered and restored. In this way, the vibration from the road surface is reliably absorbed, and the operation is performed. Ride comfort can be improved.

FIG. 6 is a side view showing a fourth embodiment of the present invention. The fourth embodiment is an example in which the vibration damping unit 7 is used for a seat of an automobile, a train, an aircraft, or the like. Specifically, the vibration reduction unit 7 is disposed between the seat 24 and the floor 21. In the sixth embodiment, the same effects as those in the first to third embodiments can be obtained.

FIGS. 7 to 9 show a fifth embodiment of the present invention.
1 shows an embodiment. FIG. 7 is a cross-sectional side view of the saddle-ride type seat (a cross-sectional view taken along line VII-VII of FIG. 8), and FIG.
FIG. 9 is a rear view of the seat. The fifth embodiment is an example in which the vibration damping unit 51 is applied to a saddle-ride type seat of a two- or three-wheeled vehicle.

More specifically, a urethane worm 48 is disposed on a seat bottom plate 50, and a urethane worm 48 is covered with a skin 47, and a seat 49 is disposed and fixed on a vehicle body frame 56.
7. The front end of the sheet 49 is supported by a substrate 57 by a rotation shaft 58, and the rear end of the sheet 49 is vertically movable by a guide mechanism 59. The guide mechanism 59 has a structure in which a guide pin 60 inserted into an elongated hole 61a of a bracket 61 fixed to the seat bottom plate 50 is implanted in a cross pipe 56a.

A pair of left and right vibration damping units 51, 51 are provided near the guide mechanism 59. The vibration damping unit 51 includes a compression coil spring 54 and a super-viscous elastic body 55 between a bottom member 52 and a ceiling member 53.
And the spring 54 and the elastic body 5
5 are fixed to the bottom member 52 and the ceiling member 53. The ceiling member 53 is connected to the seat bottom plate 50.
The bottom member 52 is fixed to the substrate 57.

In the sheet 49 according to the fifth embodiment,
The urethane worm 48 and the vibration damping unit 5
By the action of 1, vibration due to unevenness of the road surface, pushing up, or vibration from the engine is absorbed. In this case, in the vibration mitigation unit 51, when a load acts on the unit 51 due to road surface vibrations or the like, the load compresses and deforms the super-viscous elastic body 55 and the compression coil spring 54. The compression deformation is recovered and restored by the repulsive force of the super-viscous elastic body 55 and the resilience of the compression coil spring 54 which is larger than the above. It is absorbed and the ride comfort of the driver can be improved. In addition, since the return is performed early, the driver's view position changed by the vibration and the impact can be quickly recovered.

In the vibration absorbing operation of the vibration damping unit 51, the rear end of the sheet 49 slightly moves up and down about the rotation shaft 58. In this case, the slot 61a of the flange 61 is formed by the guide mechanism 50.
Is guided by the guide pins 60, so that the sheet 4
9 can be prevented from rolling.

Next, a sheet according to a sixth embodiment of the present invention will be described with reference to FIGS.
FIG. 10 is a side view of the vicinity of the seat, and FIG.
-XI line sectional view, FIG. 12 is a partial sectional plan view of the sheet,
FIG. 13 is a sectional front view of the vibration damping unit used for the seat. In FIGS. 10 and 12, the left side in the figure is the front of the motorcycle.

In the figure, reference numeral 62 denotes a tandem seat in which a front seating portion 62a on which the driver of the motorcycle 72 is seated and a rear seating portion 62b on which the passenger is seated are formed continuously in a stepped manner. , A pair of seat frames 6 disposed behind a fuel tank 64 installed above the main frame 63 and extending rearward from a rear portion of the main frame 63.
The rear wheel 67 is disposed below the seat frame 65.

In the sheet 62, an upper surface of a bottom sheet 66 made of a plate-like body such as a metal or a hard synthetic resin is provided.
A cushion body 70 composed of a urethane foam cushion main body 68 and four sets of vibration damping units 69 buried in voids 68a of the urethane foam is placed.
A synthetic leather sheet skin 71 consisting of a PVC (PVC) leather surface and a wooly nylon lining,
It covers the surface of the cushion 70 and is fixed to the periphery of the bottom sheet 66. Each of the vibration damping units 69 is disposed at a position below the buttocks when the driver sits on the front seating portion 62a.

The vibration damping unit 69 has substantially the same structure as that of the first embodiment, and has a bottomed cylindrical bottom member 73 having an inner diameter slightly larger than the outer diameter of the bottom member 73. Similarly, a compression coil spring 750 and a round bar-shaped super-viscous elastic body 76 are concentrically inserted between the bottom member 73 and the ceiling member 74 so as to be slidably inserted into a cylindrical ceiling member 74 having a bottom. It has a structure arranged in parallel. Both ends of the super-viscous elastic body 76 are fixed to both the bottom member 73 and the ceiling member 74, and both ends of the coil spring 75 are pressed against the bottom member 73 and the ceiling member 74.

In the sheet 62 according to the sixth embodiment,
The urethane worm 68 and the vibration damping unit 6
By virtue of the operation 9, vibrations due to unevenness of the road surface, thrusts, or vibrations from the engine are absorbed. In this case, in the vibration damping unit 69, when a load acts on the unit 69 due to road surface vibration or the like, the load compresses and deforms the super-viscous elastic body 76 and the compression coil spring 75. The compression deformation is recovered and restored by the repulsive force of the super-viscous elastic body 76 and the resilience of the compression coil spring 75 which is larger than the above. Thus, the road surface vibration and the like are surely reduced. It is absorbed and the ride comfort of the driver can be improved. In addition, since the return is performed early, the driver's view position changed by the vibration and the impact can be quickly recovered.

Further, since the vibration damping unit 69 is arranged at a position below the buttocks when the driver is seated, his own weight and inertia force can be effectively applied to the coil spring 75 and the super-viscous elastic body 76. As a result, the vibration can be attenuated and the visibility can be restored after jumping and landing more reliably and quickly.

FIGS. 14 and 15 show a case where the characteristics of the compression coil spring 75 and the super-viscous elastic body 76 of the vibration damping unit 69 in the sixth embodiment are determined.
It is a figure for explaining an example. That is, the elastic modulus obtained from the displacement amount when a static load is applied to the vibration damping unit 69 is higher than the static load applied to the urethane foam having a shape that fills the gap 68a in which the vibration damping unit 69 is disposed. The elastic modulus obtained from the displacement obtained when a static load is applied to the super-viscous elastic body having a shape that fills the gap is smaller than the elastic modulus obtained from the displacement obtained when the above is applied. Determine the characteristics.

A method for determining the characteristics of the vibration damping unit will be specifically described. FIG. 14 is a characteristic diagram showing the relationship between the urethane foam having a shape that fills the gap 68a and the amount of contraction ΔL of the compression coil spring 75 of the vibration damping unit 69 and the resilience F. FIG. FIG. 4 is a diagram for explaining a method of measuring the shape of urethane, the amount of displacement, and the elastic force.

In FIG. 15, as the urethane foam 20, one having the same outer diameter and the same length L as the space portion 68a and different materials U1 and U2 is prepared. Then, each of the urethane foams 20 is sandwiched between the pressing plates 14 and 15, and the contraction amount Δ
L and elasticity (load) F are measured.

In FIG. 14, a1 is urethane foam U1
A2 indicates the characteristics of the urethane foam U2, and a3 indicates the characteristics of the compression coil spring 10. The spring constants of the spring 10 and urethanes U1 and U2 are K, Ku1 and Ku2, respectively.
<K <Ku2. The measured values in FIG. 14 indicate values when the urethanes U1, U2, and the spring 10 are each used alone as an elastic body in the seat.

In the figure, A is when the user is seated on the seat, B is when the user jumps and lands or touches during running, and C is
Is when the spring 10 is in close contact, and X is the amount of shrinkage x
The relationship between the displacement amount and the repulsive force at the time of is shown. Note that Lo indicates the amount of displacement from the free length when the compression coil spring 10 is set. Fs0 is the resilience of the spring 10 when the spring 10 is set, Fsx is the resilience of the spring 10 when the displacement is X, and Fu1x is the resilience of the urethane U1 when the displacement is X. , Fu2x indicate the elasticity of the urethane U2 when the displacement amount is X, respectively.

As can be seen from FIG. 14, Fsx> Fu
When the characteristics of the compression coil spring 10 are set so that 1x and Fsx> Fu2x, the elasticity of the coil spring 10 is greater than the elasticity of the urethane foam U1 and U2 at the same displacement. large. The vibration damping unit in each of the above embodiments employs a super-viscous elastic body that is more easily deformed than urethane foam, so that the elastic force at the same displacement is smaller than that of the coil spring 1 by the super-viscous elastic body.
0 is larger, and it can be said that the deformation of the super-viscous elastic body can be quickly restored and recovered by the coil spring 10.

Next, based on FIG. 16 to FIG.
An experimental result for confirming the operation and effect of the seat 62 in the embodiment will be described. FIG. 16 is a characteristic diagram showing the relationship between the displacement of the sheet and the load (elastic force) in each combination;
FIG. 17 and FIG. 18 are schematic diagrams showing the configuration of the sheet.

In FIG. 17, reference numeral 19 denotes a sheet experimental model, which is composed of two types of urethane foams 16 and 17.
(Product name “M41”) are stacked in series, and the thicknesses T1 and T2 of the urethane foams 16 and 17 are 20 mm and 40 mm, respectively.

In FIG. 18, reference numeral 18 denotes another seat experimental model, which is constructed by combining the coil spring 10, the super-viscous elastic body 11, and the urethane foam 17 as follows. The coil spring 10 has a wire diameter of 2.6 mm, a coil outer diameter of 27 mm, and a free length of 5 mm.
5 mm, spring constant 5.14 N / mm (0.52 kgf /
mm), and the super-viscous elastic body 11 has an outer diameter of φ3.
The trade name “YRACS” having a height of 2 mm and a height of 55 mm is used. In FIG. 18, 12 ', 1
3 'corresponds to a bottom member and a ceiling member.

In FIG. 16, b1 represents the case of the urethane foam 16 alone, b2 represents the case of the urethane foam 17 alone, and b3 represents the coil spring 10
When four are used, b4 is the super-viscous elastic body 11
In the case of using four pieces, the coil spring 10 and the super-viscous elastic body 11 are used in combination of four sets in which the coil spring 10 and the super-viscous elastic body 11 are arranged in parallel. As shown in FIG. When the urethane foam 17 and the urethane foam 17 are superposed in series, b7 indicates the relationship between the load and the displacement when the urethane foams 16 and 17 are superposed in series as shown in FIG. Each is shown.

The following points can be seen from FIG. That is, when only the urethane foam 16 is used (b1), when only the coil spring and the viscoelastic material are used (b5), when only the coil spring is used (b3), and when only the urethane foam 17 is used (b)
In the case of 2), the displacement is small with an increase in load, and the ability to absorb vibration and impact is low. On the other hand, in the case of only the super-viscous elastic body (b4), the displacement is large with an increase in the load, and although the vibration absorbing ability is high, the recovery of the displacement is slow. In the case where the urethane foams 16 and 17 are stacked in series (b7), the displacement is small in the initial stage a of increasing the load,
Therefore, although it is inferior in absorbability of small vibration and thrust, in the case of the one corresponding to the sixth embodiment in which the vibration damping unit is embedded in the urethane foam 17 (b6), the part a in b7 is corrected to a '. It is effective and can absorb small vibrations and thrusts.

Next, based on FIG. 19 to FIG.
An experimental result for confirming the operation and effect of the sheet 49 in the embodiment will be described. FIG. 19 is a characteristic diagram showing the relationship between the displacement of the sheet and the load (elastic force) in each combination;
FIG. 20 and FIG. 21 are schematic views showing the configuration of the seat and the vibration damping unit.

FIG. 20 shows a seat 23 in which four vibration damping units 22 are arranged under a cushion body 19 made of urethane having a thickness T3 (60 mm). Various configurations are adopted as the vibration reduction unit 22. Specifically, the wire diameter is 3.2 mm and the coil outer diameter is 24 m
m, free length 55 mm, spring constant 25.392 N / mm
(2.59 kgf / mm) compression coil spring;
A combination of a super-viscous elastic body having an outer diameter of 32 mm and a height of 35 mm as described below is employed.

In FIG. 19, c1 is a case where only the two coil springs are used, c2 is a case where only the two super-viscous elastic bodies are used, and c3 is a vibration damper in which the coil spring and the super-viscous elastic body are arranged in parallel. When only two units are provided, c4 is an outer diameter of 32 mm and an inner diameter of φ32 as shown in FIG.
In the case of only two vibration damping units 22 'in which the coil spring 10 is embedded and integrated in a 10-mm super-viscous elastic body 11', c5 is the case of only the urethane foam 19, and c6 is the vibration of FIG. Two relaxation units 22 'and c
C7 when urethane foam 19 of No. 5 is stacked in series
Shows the relationship between the load and the displacement when two vibration damping units c3 and urethane foam 19 c5 are stacked in series.

The following points can be seen from FIG. That is, when only the coil spring is used (c1) and when only the coil spring and the superviscoelastic material are used (c3 and c4), the displacement is small with respect to the increase in the load, and the ability to absorb vibration and shock is low. On the other hand, in the case of only the super-viscous elastic body (c2), the displacement is large with an increase in the load, and although the vibration absorbing ability is high, the recovery of the displacement is slow. In the case of only urethane foam (c5), the displacement is small at the initial stage a of increasing the load,
Therefore, it is inferior in the absorption of small vibration and thrust. On the other hand, the case corresponding to the fifth embodiment in which the coil spring and the super-viscous elastic body are arranged in parallel or the integrated vibration damping unit and the urethane foam 19 are stacked in series (c6, c7) Has the effect of correcting the portion a in c5 to the a ′ side, and can reliably absorb small vibrations and thrusts.

The scope of application of the vibration damping unit according to the present invention is not limited to the above embodiments.
Between the engine-driven generator and the installation surface, or
It can be applied to any part where vibration should be reduced, such as being placed between the load placed on the ship's carrier and the mounting surface,
Further, the present invention is not limited to seats of motorcycles, but can be applied to seats of land vehicles such as automobiles and small snowmobiles, and seats of water vehicles such as hydroplanes and high-speed boats.

[Brief description of the drawings]

FIG. 1 is a front view of a main part of an outdoor unit to which a vibration damping unit according to a first embodiment is applied.

FIG. 2 is a sectional front view of the vibration damping unit according to the first embodiment.

FIG. 3 is a side view of a main part of a saddle portion to which a vibration damping unit according to a second embodiment is applied.

FIG. 4 is a sectional side view of a main part of the vibration damping unit according to the second embodiment.

FIG. 5 is a front view of a main part of a front fork to which a vibration damping unit according to a third embodiment is applied.

FIG. 6 is a side view of a seat to which a vibration damping unit according to a fourth embodiment is applied.

FIG. 7 is a cross-sectional side view of a saddle-ride type seat to which a vibration damping unit according to a fifth embodiment is applied.

8 is a sectional view taken along line VIII-VIII in FIG. 7;

FIG. 9 is a rear view as seen from the direction of arrow IX in FIG. 7;

FIG. 10 is a side view near a seat of a motorcycle to which a vibration damping unit according to a sixth embodiment is applied.

11 is a sectional view taken along line XI-XI in FIG.

FIG. 12 is a partial cross-sectional plan view of the sheet,

FIG. 13 is a sectional front view of a vibration damping unit used for the seat.

FIG. 14 is a characteristic diagram for explaining characteristics of urethane foam and a spring.

FIG. 15 is a view for explaining a method for measuring the characteristics of the urethane foam in FIG. 14;

FIG. 16 is a characteristic diagram showing a relationship between a load and a displacement.

FIG. 17 is a cross-sectional side view of a sheet formed by stacking two types of urethane in which the relationship between load and displacement is measured in FIG.

FIG. 18 is a cross-sectional side view showing the structure of the seat in which the relationship between load and displacement is measured in FIG.

FIG. 19 is a characteristic diagram showing a relationship between a load and a displacement.

FIG. 20 is a schematic diagram of a sheet in which the relationship between load and displacement is measured in FIG.

FIG. 21 is a cross-sectional side view of the vibration damping unit in which the relationship between load and displacement is measured in FIG.

[Explanation of symbols]

7, 29, 39, 51, 69 Vibration damping unit 8, 31, 41a, 12 ', 52, 73 Bottom member 9, 30, 42, 13', 53, 74 Ceiling member 10, 34, 44, 54, 75 Compression Coil spring 11, 33, 43, 55, 76 Super viscous elastic body 16, 20, 48, 68, 17, 19, U1, U2 Urethane foam 19, 23, 24, 49, 62 Sheet 47 Skin member

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F16F 1/12 F16F 1/12 E (72) Inventor Kazuaki Hamada 2500 Shinkai, Iwata-shi, Shizuoka Yamaha Motor F term in the company (reference) 3D014 DD03 DE02 DE08 DE13 3J048 AA01 AC05 BC02 BD08 DA01 EA13 EA16 3J059 AB07 AE04 BA01 BA54 BC05 DA26 DA43 GA02 GA36

Claims (2)

[Claims] 1. A compression coil spring and a super-viscous elastic body are arranged in parallel between a bottom member and a ceiling member, and at least one end of the coil spring and the super-viscous elastic body are connected to the bottom member. And a vibration damping unit fixed to both ceiling members. 2. A urethane foam is incorporated in a skin member, and a void is provided in the urethane.
A compression coil spring and a super-viscous elastic body are arranged in parallel between the bottom member and the ceiling member, and at least one end of the coil spring and the super-viscous elastic body are connected to both the bottom member and the ceiling member. A seat provided with a vibration damping unit fixed to the seat.