JPS5828035A - Vibro-isolating track and its vibro-isolating device - Google Patents

Abstract

PURPOSE:To prevent generation of resonance further increase a vibro-isolating effect, by arranging upper and lower resilient members of mutually different spring constant to the upper and the lower of a supporting mount and holding said resilient members with tightening tools in top and bottom ends of a main shaft and flange part. CONSTITUTION:A flange part 6 is constituted to the central part of a main shaft 5, inserted through a supporting mount 1, and an upper side plate 15, inserted with an upper half part 14 of the main shaft 5, is adapted to the flange part 6. Then plural layers of resilient materials 7 are laminated on the upper side plate 15 and held by a tightening tool 17 to form an upper resilient member 7a. While a lower side plate 23 is inserted with the main shaft 5 from the lower and adapted to the flange part 6, then plural layers of resilient materials 7 is laminated to the lower of said plate 23, and held by a tightening tool 17 to form a lower resilient member 7b. A spring constant of said upper resilient member 7a and lower resilient member 7b is arragned to values different from each other.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibration isolator and a vibration isolator track that utilizes the special properties of this vibration isolator.

Conventional tracks simply consist of a large number of sleepers arranged in parallel on crushed stone or concrete slabs, rails laid on top of the sleepers, and the rails directly fixed to the sleepers. The disadvantage of such a rigidly structured track is that vibrations and noises of all frequencies, from high to low, that occur while the train is running are directly transmitted to the ground through the rail sleepers, which has a great negative impact on the surrounding area. was there. In particular, when a train passes through a structure that is prone to resonance, such as an elevated tunnel, the vibrations and noise are amplified, and the negative impact on the surrounding area is enormous. There is also a demand that vibration and noise countermeasures must be taken as soon as possible for the health of live line residents when passing through densely populated residential areas. It is also important to note that the speed of the X trains (especially the Shinkansen) is scheduled to be increased, and drastic countermeasures will be taken up as an urgent issue in the near future. 1. Anti-vibration rubber was laid under the slab to reduce the noise and vibration of the rigid track (-), but since there is no change in the tension constant, the drawback is that if resonance occurs, it cannot be suppressed. Although the anti-vibration effect was weak, it had the disadvantage that only hard materials with no fear of resonance could be used.Additionally, if anti-vibration rubber was placed under one slab, vibrations would be transmitted through the slab and the anti-vibration effect would be poor. There were also disadvantages of the slab being thin and the slab breaking due to bending.

The present invention has been made in view of the drawbacks of the conventional example.
The purpose is to provide a vibration isolating device in which the resonance constant changes depending on the amplitude and does not cause resonance, and a vibration isolating track that utilizes this feature.

The present invention will be described in detail below according to illustrated embodiments. First, the seventh invention of the vibration isolator will be explained according to FIGS. 1 to 9. The support base (1) is composed of a square-shaped elastic material attachment part and an active material attachment part (2) (an attachment piece part (3) extending from the bottom of the side plate). 2) A sliding hole <4) is bored in the center of the top plate. The main shaft (5) is composed of a bolt, and a nut constituting a snap part (6) is screwed into the center of the shaft. Of course, Jin's brim (6) is the main shaft (
5) may be removed integrally. In this embodiment, the elastic material (7) is made of synthetic rubber or a soft synthetic resin molded product, and includes a wavy elastic plate (8) having V grooves alternately formed on its surface, an outer spring (9), and an inner tin ring. (10) (Inner and outer spring (9) (1
The spring constants of 0) may be different from each other.
Also, the free lengths may be made different. 1) Furthermore, in the center of the wavy elastic plate (8), there are spring storage holes (12) arranged at equal intervals around the main shaft insertion hole (11) and the main shaft insertion hole (11). ).

(Of course, the elastic material (7) is not limited to the case of this embodiment, and may be a sponge-like material. It is also possible to use only the wave-like elastic plate (8) or the springs (10) and (9).) First, the main shaft ( 5) Upper plate (15) on the upper half (14)
The corrugated elastic plate (8) is then inserted into the upper half (4) of the main shaft (5) and bonded to the upper plate (15). Next, attach the outer spring (9) to the rear wavy elastic plate (8) disposed inside the spring storage hole (12).
) is pushed through the upper half (14) K, the outer spring (9) is stored in the spring storage hole (12) of the upper wavy elastic plate (8), and then the intermediate play is inserted into the upper half (14). (16
) and adhere the upper wavy elastic plate (8). At this time, a gap (X) may be provided between each wave-like elastic plate (8), or they may be brought into close contact with each other. The effect of the gap (X>
) and tighten the elastic member (7) with the collar part (6) to form an upper elastic member (7a). The Time of Jin ~ Main Axis (5)
An initial pressure may be applied to the upper elastic member (7a) in accordance with the excitation force applied to the upper elastic member (7a).
Only the top layer of 7) has the inner and outer springs (9) and (10) double-layered, but of course they can be double-layered across the entire layer depending on the excitation force.Conversely, they can also be single-layered. good. Further, in this embodiment, the elastic material (7) is stacked in three layers, but it may be stacked in 17 layers or more. In this way, attach the upper elastic material (7a) to the ten-half part (]4) of the main shaft (5).
Insert the lower half (18) of the rear shaft main shaft (5) into the sliding hole (4) of the support base (1), and one flange (6) fits into the sliding hole (4). Do it like this. Then the lower plate (
23) Assemble the wavy elastic plate (8) A outer spring (9) \ wavy elastic plate (8) \ middle play (16) into the lower half (18) in the same manner as above in this order, and install the 8 bullets. (7) is laminated in several layers. In this case, of course, there may be seven layers or one or more layers depending on the load. After that, the lower half (18
) is screwed onto the lower end of the lower elastic member (7b) to tighten the lower elastic member (7b) with the collar (16). In case B, initial pressure can also be applied if necessary. The vibration isolator ff1(A) is assembled in this way, but the spring constants of the upper elastic material (7a) and the lower elastic material (7b) are different in ξ. (In this embodiment, the lower elastic member (7) has a larger spring constant).

Next, change in the spring constant of this vibration isolator (A) and the natural frequency ωn% 41. The δ transmissibility t will be explained separately. If the σ constant of the size 1 elastic material (7) is K, then
The natural frequency ωn is generally expressed as C or less.

15 When the period of the excitation force Wdnωt is ω, the vibration transmissibility t is generally expressed as follows.

As shown in Figure 1 and 1, when the thickness (S) of the collar (6) and the thickness of the support base (1) are equal and the initial pressure is applied, the change in the force constant is shown. The result will be as shown in Figure s. That is, 1
The spring constants of the upper and lower elastic members (7a) and (7b) are KIJ,
If it is KL, it will bend at the 1st layer point 0 and act as an independent spring. That is, 1 upper elastic material (7a)
When it is pressed down and bent, the brim (6) protrudes beyond the support base (1), and when the lower elastic member (7b) separates from the support base (1), the vibration direction of the excitation force reverses. Then, when the lower elastic member (7b) is compressed, the upper elastic member (7a) moves to the support base (
1) Do not separate from the upper and lower elastic members (7:X)
(7b)): It works independently for each direction of rotation. Next, these KU% KL (
Substituting into equations 1) and (2), the natural frequency ωn1
A legend.

If the delivery rate t is different in the vertical direction, then . Now, the period ω of the excitation force is the natural frequency ωn of either one
, and even if one side resonates, the other acts as a vibration absorber), and as a result, resonance is completely suppressed.

(An example of calculation in the case of is described later.)The larger the difference between the spring constant KO of the upper elastic member (7a) and the spring constant of the lower elastic member (7b), the greater this effect will be. It is desirable that one is 0 times or more larger than the other.

Upper elastic material Lower elastic material K: KU = K.

@Figure 4 shows the case where an initial pressure T is applied to the upper elastic member (7a). 1 Figure 7 shows the case where an initial pressure TL is applied to the lower elastic member (7b). Figure g shows the case where T is applied to both. In the example in which the excitation force is T,
Or, when it becomes 11 or more, it will be deflected by W-TIJ (TL), and the actual deflection can be reduced. In addition, Figure 1 of the imperial edict ~ fl'7 Figure g is the spring (9)
This is a case where (10) and the wavy external plate (8) work integrally.

Figure 9 and Figure 1θ Figure 01 A gap XusχL is provided between the upper and lower wavy external plates (8), and 1 spring (9) (1
A case is shown in which G) and the wavy external plate (8) do not necessarily work integrally. Here, the second part and the lower spring (9
) The individual or combined spring constant of (10) is KUS% I(
LS, and the gene constant of the wavy elastic plate (8) is ICIJGλ
Let's call it KLG. 7L, lower elastic material (7a) with excitation force
When compressed, only some of the springs (9) and (10) deflect and the spring constant shows KIJS. Here, the hysteresis is long because the springs (9) and (10) are bent. When the upper elastic member (7a) is further compressed and the upper elastic member (7a) stiffens to Xu-0, the upper and lower wavy elastic plates (8) are also compressed, and the deflection-spring constant tk is the sum of both (KO”= Kus +
Kuc ) and become stronger. In addition, here, due to the influence of the wavy elastic plate (8), the curved surface exhibits hysteresis. The same thing as described above occurs when the direction of the excitation force is reversed and an increasing component of K is applied to the lower elastic member (7b).

Below are the margins: upper elastic material, lower elastic material, and if an initial pressure T (TL) is applied in advance, the actual deflection will be smaller, as shown in Figures - g. In this way, since the spring constant changes depending on the amount of deflection, the KIISN K
When the amplitude reaches the region of KL even if LST resonates, ωn
From equation (2), if the resonance is suddenly suppressed, then .

Figures 1 to 2 are graphs of changes in the spring constant in the second invention in which the wall thickness (S) of the collar portion (6) is thinner than the wall thickness of the support base (1). this house! //Figure~M/Figure and 1st g
The setting method for the parts shown in Figures 1 to 1 is different. First, we will explain the case of S 1/Figure 1 to 1. First, tighten the upper and lower fasteners (17). Elastic material (7a)
(7b) is given an initial pressure T, and the collar (6) is attached to the support base (
1) Be located within. Let the gaps at this time be Xx2. Upper and lower elastic materials (7a) (7b)
are balanced and attracted to each other, so the N spring constant is K. , iK, +, tonashi) It becomes a very strong spring.

Another thing is the spring (9) (10)! :Since it works integrally with the wavy elastic plate (8), KIJ=KIJ
For S ten, 6, KL = KLS + KIG. Here, when the excitation force resonates and the amplitude increases and exceeds X0, the upper and lower elastic plates (7a) (7b) are alternately separated from the support base (1) \ spring constant is K. , KL, and decreases. Here, hysteresis will be drawn in the KU+ and KL regions. In the case of resonance, K1. lX K As soon as it enters the L region, ωn becomes significantly smaller. Upper elastic material prevents Hiro resonance Lower elastic material 1st stage KU+1 Same as left 2
K, K.

In the case of Fig. 73 to Fig. 1, the fi, string-like elastic plate) and the suffling (9X1) do not work integrally.

First, in the case of the first diagram, the gap between the wavy elastic plates (8) is XU.
This is the case when %XL is larger than XI and X2.

That is, Xl(X.

X2 (X) If the amplitude of the excitation force is within Xu%xL, the spring (9)
The deflection is only (1G), and the spring constant is as follows.

1st stage K =:kBs+kLs Next, as the amplitude increases, the collar (6) moves to the support base (1
), and only the springs (9) and (10) of the upper and lower elastic members (7a) and (7b) are bent, and the spring constants change to S and kLS. Therefore, even if resonance occurs in the previous stage, resonance is suppressed in this stage. When the elastic plate (7) further bends, the upper and lower wavy elastic plates (8) come into close contact with each other, and the spring (9)
(10) and the wavy elastic plate (8) work together to increase the spring constant to Ku ("Kus + Kuc) % Kt. Usually cvmlth ha l K7 stage (K = Kus 10 KL
(s)) is effective when the load is excessive and the amplitude reaches up to stage C and resonance occurs.

The first left diagram is χ, 〉X.

1 when xt <XI In this case, the behavior of the upper elastic member (7a) is different from the case in Figure @/7. That is, before the collar portion (6) projects beyond the support base (1), the upper and lower wavy elastic plates (8) come into close contact with each other, so the spring constant changes as follows.

Upper elastic material Lower elastic material 1st stage q K=Ku-1-, 5K=Kts 3rd stage K: Ku K:=Kl FIG. 1A shows the reverse case where x2>xL Xl <Xu.

The change in spring constant is upper elastic material lower elastic material 1st stage K” KUS +KLS Same as left,
2 K:KIS K:=Kl +
Kus, 7 K=KuK:KL Fig. 77 is the opposite of Fig. 1. In this case, Xl > XU X2 > xL. υ) The change in the spring constant is K as follows.

Upper elastic material Lower elastic material 1st stage K-KUS 10KLS Same as left 2
K = Ku ten KLSK: Kl + KIJ.

, 7 K: Ku K: K
As shown above, the spring constant is 3 in both vertical vibrations.
Even when an excitation force that is approximately equal to KutKts changes in stages and resonates, this can be suppressed.

Figures 1g to 2.2 are for the case where the initial pressure TU>TL.

First, to explain Fig. 19, one excitation force W picture ωt is T
U TLN Upper and lower elastic material (7a) until it overcomes TL
(7b) is not an admiral. Next, when the rolling component overcomes the Tu-TL, it begins to bend and the parts 4 of the collar (6) and the support base (1) begin to bend.
“The spring constant decreases to Ku when the amplitude exceeds the gap X. Regarding the rising component, when the amplitude exceeds T [
The deflection in b) becomes Kl from the beginning. That is, upper elastic material lower elastic material 1st stage Excitation force≦Tυ-TL Not deflected (Ill, not deflected 2 K: Ku, LK = KL3
K:K.

Figures 20 to 2.2 show the case where the spring (10) and the wavy elastic material (8) do not work together.
The case shown in the figure will be explained. In this case, the gap X is larger than the gap Xu between the υ wave-like elastic members (8).

That is, X <

3 K=I(uSK ding-
■(Ltl K=KU On the other hand, in the figure here, when X>X, 1 or less margin Upper elastic material Lower elastic material 1st stage Excitation force <Tu-'r and does not bend tt <
TL deflection 2 K:KUS
+KLS K=:KLs3
K:Kl +KLS
K:=Klg
K: KLI, and the spring constant changes one after another as the deflection increases. Note that the broken line portion in the figure is hysteresis caused by the wavy elastic plate (8) K that occurs when the excitation force decreases. Here, drawing nohysteresis after the second or third stage of Wf has the following effects. For example, when ω/ωnb/ resonates in the previous stage, as soon as the amplitude spreads to the next stage, the spring constant changes and the wavy elastic material (
8) The internal friction acts to produce internal damping, and even if the changed ①/ω is less than ρ, a significant vibration damping effect is achieved.

Note) In the fourth embodiment, the upper and lower elastic members (7a) (.

The spring constants KL in 7b) may be equal or different. Further, when the main shaft (5) is not provided with the rib portion (6) and a gap is provided between each wave-like elastic plate (8), the spring constant increases midway as shown in FIG. 23. That is, the upper elastic material and the lower elastic material on the 7th floor - "US 10 KLS Same left f
il, l tt K = Ku +KLS
K: KL +KUS No. 23 shows the case where the upper end of the main shaft (5) is pulled horizontally and a bending moment is applied around the boxwood part (6) -lc. In this case, only both ends of the elastic material (7) is tensioned or compressed, and the central part is in a neutral state.) The spring constant is `` when compressed.

Next, an example in which the case shown in FIG. 19 is applied to a trajectory will be described. 2nd left), the vibration isolator (as shown in Figure 26)
A) is the main vibration isolator (
A,) and the secondary vibration isolator (A*) placed on the side of the sleeper (19) and the main vibration isolator (Aυ support stand (1) U
, is directly fixed to the base (20), and the sleeper (19) is screwed to the main shaft (5) of the book. On the other hand, the 1st sub-vibration isolator (A,
) is fixed to the base (20) at an angle of 45 degrees and the sleeper (
The side end of 19) is screwed onto the main shaft (5). When the train passes over the rails (22), vertical and horizontal excitation forces are applied to the sleepers (19) via the rails (22). That is, each time a wheel of row 2t reaches above the sleeper (19), a rolling component and a -horizontal component are added to the sleeper (19), and once the wheels have passed, the rolling component and -horizontal component are canceled. However, the main vibration isolator (A,) and the sub-vibration isolator m (A2) of the present invention are integrated. Therefore, the excitation force in the vertical direction and the excitation force in the horizontal direction are absorbed. Now, if we consider vertical vibration, the composite spring constant # of the upper and lower elastic members (7a) and (7b) is 1!
IKUi, K14yi is the following passage.

'u if direction top! Igua, F-2 (Klt-
10, ``'uk, >・-・(''), and the lower elastic material (
The composite spring constant KU4* of 7b) is K, , = 2 (K
l, -1-(1,7Kla, ) ・ ・
・(4) becomes.

(Calculation example/in the case of the figure on the left) Determine each spring constant as follows \ Installed on sleepers / books) Main and sub-vibration isolators (Aυ (A2) Kuas K Lt
Calculate riωnz t.

(tri', constant of each upper and lower elastic member (7a) (7b) of main and sub-vibration isolator (AI) (At)) 1 (Ul
=2,857 (kg 7cm) K, ==8
．． 57 (IKU Nishikiji 1,428 K...
::=4,285,', KU,,22 (2,857
+f1.7X1,42B):: 7,713KLQ--
72(8,57(!to0.7X4,285) -
-23,139'Vm+tx-10, Go(')kg. g=980 (gravitational force [(velocity) and elasticity of the lower part of the soil (7a) (7b)'s unique &!'r-'tb number ω□
ωηake＼ Now, if the period of the excitation force is ω: 47, the tl of the combined lower elastic member (7b) becomes and resonates.

On the other hand, when the upper elastic material (7a) is composed of 1, it becomes 1 and suppresses the tendency of the lower elastic material (7b) to resonate.

(Calculation Example 2) Next, a case will be described in which the vibration isolator (A) shown in Figure 1, No. 79 is applied to the orbit.

The following describes the upper elastic material (7a).

(a) When the excitation force Wmax≦Tu-'I'L, 1. Upper elasticity - Oh (78) is not effective. In other words, one upper and lower elastic member (7a) (
If we give 7b) a constant initial pressure (T) that matches the load, we can obtain the reaction force (Tu-Tt) of the elastic material (7) that is equal to the load when one load passes through it. , resulting in the change of the elastic material (7) with respect to the instantaneous acceleration of the load (
) ζ deflection) ＼ The amplitude is significantly relaxed (l) When the excitation force Wmax > Tu-TI, within the range of 1 gap X, the upper and lower elastic members (7a) (7b) Since they both expand and contract, the composite spring constant is K = K + KL, which is -L・6°,', K :=7,713+23,139=30,
85211+L voice C According to formula (2), the natural frequency 61.1B is (c) When the amplitude due to the excitation force Wmax exceeds X, only the upper elastic material is deflected, resulting in a composite spring constant K -υp- 7,713 If the amplitude exceeds the gap X due to the resonance of the upper elastic member (7a), the period ω of the input vibration force is 55 rad/sea.
It is close to. Assuming ω:55, KU4. ,.

Calculating t in the area is 1 The sea resonance will be suppressed.

Next, consider the lower elastic member (7b) K. The track is rolled down by one wheel each time nine trains pass, and returns to its original position once the wheel has passed, and the general button will vibrate within the range of the gap X. Therefore, as a countermeasure against resonance, if only the lower elastic member (7b) side is taken into account, then the lower elastic member (7b) should only be able to suppress the splash when the lower elastic member (7b) returns. Become. In addition, 1 vibration is mainly caused by the upper elastic material (
7a), but at this time the lower elastic member (71
)) If the spring constant K[ of the upper elastic member (7a) is increased, the difference in VC transition will be large as when it works as a composite spring Ku+L1.As a result, the natural vibration frequency will change greatly. As a result, the anti-vibration effect is enhanced.

Note that, as an example of use, a case where the present invention is applied to a track is shown; however, the present invention is not necessarily limited to this, and may be applied depending on the case so as to change the excitation frequency. Also, the spring (9) (1
0) is brought into direct contact with the support base (1) so that even when the upper and lower elastic members (7a) (7b) are separated from the support base (1), these springs (9) (10) will expand. Alternatively, as shown in FIG. 29, a thin contact piece (24) may be extended from the wavy elastic plate (8) to make contact in the same manner. Conversely, this contact piece (24) may be provided between the gaps (XIJ) and (XL) so that they touch each other between the corrugated elastic plates (8) of the earthwork. Furthermore, the gap (Xu) (XL) is made of upper and lower elastic materials (7a).
It may be provided only in the seat (7b).

In the present invention, the upper elastic material and the lower elastic material, which have different spring constants from each other, are separated by the wall thickness of the support base, etc. Since the vibration isolator is held between the two sides, when an excitation force is applied to the vibration isolator, the reduction component and the soil elevation component are separately applied to the two lower elastic materials, resulting in individual natural frequency-vibration transmission. You will have to take the rate.

As a result, even if one side resonates, the other side works to absorb the distortion and prevents the A resonance. Furthermore, since the upper and lower elastic members 1 are held independently, there is an advantage that if necessary, the fasteners can be tightened and then loosened to reapply the initial pressure. In addition, in the invention of Part 1 and 2), the thickness of the collar is made thinner than the thickness of the support base, and initial pressure is applied to the upper and lower elastic members, so the excitation force is added and the amplitude of vibration increases. As it decreases, the collar protrudes from the support base and retracts, causing a change in the spring constant each time.For example, even if the collar resonates when vibrating within the support base, as soon as the collar protrudes from the support base, the spring constant changes. The natural frequency changes and resonance is suppressed. Furthermore, in the third invention, since a vibration isolator is disposed between the railroad ties and the foundation, vibrations and noise generated when the train is running are immediately absorbed by the vibration isolator and transmitted to the A foundation. Never. In particular, high vibration isolation effects can be obtained in structures that are prone to resonance, such as bridges and tunnels. Furthermore, as mentioned above, the spring constant of the vibration isolator changed between rolling down and raising.
Since it changes during the deflection, even if it is likely to resonate at 7 of the miscellaneous frequencies ranging from low to high frequencies (
Normally, if the vibration at the frequency that exhibits the maximum amplitude is suppressed, the vibration at other frequencies will be suppressed.

) Since the natural frequency changes immediately and resonance is suppressed, a high vibration damping effect can be achieved. Also)
Since the sub-vibration isolators are arranged at both ends symmetrically and inclined symmetrically along the display direction of the sleepers, it exhibits a strong resistance against vibration force in the horizontal direction and a vibration-isolating effect.

[Brief explanation of the drawing]

, Figure 7 is a partially cutaway front view of the sub-vibration isolator shown above.
The figure below shows the case where the spring and the wavy elastic plate work together ~ Figure 2 is a graph showing the change in spring constant for each set.
Figure 9: Longitudinal cross-sectional view when a gap is provided between the wavy elastic plates and the spring and the wavy elastic plates do not always work as a unit.
tlc // Figure is a vertical cross-sectional view of an embodiment of the second invention, the first λ
The figure is a graph showing the change in the spring constant as above. Figure 1g is a longitudinal cross-sectional view when the initial pressure conditions of the second invention are changed. Vertical cross-sectional view of an example in which a gap is provided in the material, No. 2/
, 2.2 is a graph 1 showing the change in the spring constant when the setting conditions of the same as above are changed. Fig. 23 is a graph s showing the change in the spring constant when the boxwood part is not provided. The front view when horizontal heating force is applied to the main axis of the vibration isolator, the second left figure is a perspective view of the wavy elastic plate and spring according to the present invention, the tlI, λ6 figure and the full body figure are the third invention Partially stolen front view and plan view of the left half of
Figure 9 is a vertical sectional view of a portion of another embodiment of the present invention.
(1) Hiro support base, (4) is sliding hole 1 (5) is main shaft 1 (6
) The kick part 5 (7a) is the upper elastic material s (7b) is the lower elastic material, (14) the upper half of the main shaft 9 (17) is the fastening Az (1a) is the lower half of the main shaft, ( 19) is the sleeper 5 (20) is the base X (22) is the rail. Patent applicant Yoshiaki Mori, 27- Figure 20 Figure 17 Figure 24

Claims (5)

[Claims] (1) A boxwood part is provided protruding from the outer periphery of the central part of the main shaft that receives the excitation force, and the glue part of the main shaft is slidably inserted into the sliding hole drilled in the support \ above and below the support. A fastener and a boxwood part, in which upper and lower elastic members having different spring constants are respectively arranged, the upper and lower halves of the main shaft are inserted through the upper and lower elastic members, respectively, and screwed onto both upper and lower ends of the main shaft. A vibration isolating device comprising an upper and a lower elastic material sandwiched between and. (2) A boxwood part is provided protruding from the outer periphery of the central part of the main shaft that receives the excitation force, and a sliding hole is bored in the support base which is thicker than the boxwood part, so that the collar of one main shaft can freely slide into the sliding hole. An upper elastic member and a lower elastic member are respectively arranged above and below the support base, and the upper and lower halves of the main shaft are inserted through the upper and lower elastic members and screwed onto both the upper and lower ends of the main shaft. A vibration isolating device characterized in that an upper and a lower elastic member are sandwiched between a fastener and a collar and initial pressure is applied to each of them. (3) Form an elastic plate from a highly elastic rubber plate or synthetic resin plate, 1. Punch a spring storage hole in this elastic plate, and 1. store a coil spring in the spring storage hole to form the upper and lower elastic members. The vibration isolating device according to claim 1 or 1, characterized in that: (4) A patent characterized in that a pair of elastic plates with spring storage holes are arranged above and below, a gap is provided between the elastic plates, and a spring is stored in the spring storage holes of the upper and lower elastic plates. A vibration isolator according to claim 3. (5) A flange is provided on the outer periphery of the central part of the main shaft that receives the excitation force, and the flange of the main shaft is slidably inserted into the sliding hole drilled in the first support base, and elastically extends above and below the first support base. Vibration isolation is achieved by sandwiching the elastic material between the collar and the fastener, which is attached to both the upper and lower ends of the main shaft (by inserting the second hand part and lower half of the main shaft into the elastic material) and the collar part. A device is formed, a plurality of sleepers are arranged in parallel above one base, a vibration isolator is arranged vertically between the base and the sleepers, the support is fixed to the base, and the sleepers are fixed to the main shaft. 1. A pair of other vibration isolating devices are installed on both sides of the vertically arranged vibration isolating device, dipping in the longitudinal direction of the sleepers and having their main axes tilted symmetrically. 1. The support base is fixed to the base and tilted. A vibration-proof track characterized in that the main shafts are fixed to the ends of the sleepers, and a rail is laid on each sleeper.