JPH08326843A - Vibration damping support device - Google Patents

Abstract

PURPOSE: To lower the dynamic spring constant of a vibration damping support device without use of a large size elastic member. CONSTITUTION: The upper end parts of elastic members 15A, 15B secured to the upper surfaces of horizontal parts 14c of brackets 14A, 14B, are slightly projected upward from the upper surface of brackets 13, passing through openings 13A, 13B, and a shaft 16 which is fixed so as to extend in the y-axial direction between the openings 13A, 13B is extended through the upper end parts of the elastic members 15A, 15B. That is, the brackets 13 secured to a high pressure pipe line 10A and a low pressure pipe line 10B, and the elastic members 15A, 15B extended in the z-axial direction are coupled with each other by the shaft 16 so as to allow them to rotate around the y-axis orthogonal to the z-axis while the brackets 14A, 14B and the elastic members 15A, 15B which are secured no the support member side, are coupled with each other, being restrained from rotating around any of the axes.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of an anti-vibration supporting device for supporting a support on a support while isolating the support from vibration, and more particularly to flexural elasticity between a member on the support side and a member on the support side. In the anti-vibration support device in which an elastic body that exerts an anti-vibration effect is interposed, the dynamic spring constant of the anti-vibration support apparatus can be reduced without using a large elastic body.

[0002]

2. Description of the Related Art As a conventional technique of this kind, for example, Japanese Patent Laid-Open No. 1-210680 (first prior art) and Japanese Patent Laid-Open No.
The one disclosed in Japanese Laid-Open Patent Publication No. 204369 (second conventional example) is known. That is, the first conventional example is an anti-vibration supporting device for supporting a pipe, in which an outer frame is fixed to a wall surface close to the pipe, and the outer frame is moved vertically through at least two points. While supporting the rod as much as possible, a pipe is attached to the end of the rod, and an equal stress flat plate that has a relatively small rigidity and the stress is constant at any position against the bending moment is installed on the left and right sides of the rod. A structure in which the free end is pin-coupled to one of the rod and the outer frame and the fixed end is fixed to the other of the rod and the outer frame in a state of being symmetric and having its plane orthogonal to the rod. Have With this structure, even if the pipe moves slowly in the vertical direction due to thermal expansion or the like, the movement of the pipe is absorbed by the elastic deformation of the iso-stress flat plate having a relatively small rigidity, and the pipe suddenly moves due to an earthquake or the like. Even if such an excessive load is applied, the energy is absorbed by the iso-stress flat plate, and large shaking of the pipe is prevented.

The second conventional example is an apparatus for preventing bending vibration of a vehicle body of a railway vehicle, in which a vibration-proof rubber that works in a compression direction is provided under the floor of the vehicle body of the railway vehicle, and a weight, etc. It is possible to prevent bending vibration on the vehicle body side because the weight and the like supported via the anti-vibration rubber acts as a dynamic vibration absorber.

[0004]

However, in the first conventional example described above, although a certain degree of anti-vibration effect can be expected, the structure is complicated. Therefore, for example, a device for supporting piping of a building or the like. As applicable,
It is difficult to apply as a device that supports something with a small space around it, such as under-floor piping of a vehicle, and if it were to be applied, the iso-stress flat plate for absorbing vibration would be small. However, the dynamic spring constant becomes large, and it becomes difficult to obtain a good vibration damping effect from a region where the frequency of vibration is low.

Further, even in the second conventional example, when it is applied as a device for supporting an underfloor pipe or the like having a small space around it, the volume of the vibration-proof rubber is small. As a result, the dynamic spring constant becomes large, so that it is difficult to obtain a good anti-vibration effect in the region where the vibration frequency is low. The present invention has been made by paying attention to the unsolved problem of such a conventional technique, and even when supporting a vibrating body arranged in a space with a small space margin, It is an object of the present invention to provide a vibration isolation support device that can obtain a good vibration isolation effect from a region where the frequency of vibration is low.

[0006]

In order to achieve the above object, the invention according to claim 1 has an elastic member interposed between a vibrating member side member and a supporting member side member so as to be elastically deformed in a bending direction by a vibration input. In a vibration-damping support device including a body, one end side of the elastic body is allowed to rotate around at least one axis orthogonal to the interposing direction of the elastic body, and the one of the vibrating body side member and the support body side member And the other end of the elastic body is connected to the other of the vibrating body side member and the supporting body side member while restraining rotation about an axis parallel to the axis allowing the rotation. .

According to a second aspect of the present invention, in the vibration-damping support device according to the first aspect of the present invention, the other end side of the elastic body is not parallel to the axis that allows rotation of the one end side. Further, the elastic body is coupled to the other of the vibrating body side member and the supporting body side member in a state in which the elastic body is allowed to rotate about an axis orthogonal to the interposing direction. The invention according to claim 3 is the vibration-damping support device according to claim 1 or 2, wherein the elastic body is provided with a plurality of shafts, and a shaft that allows the rotation of one elastic body, The axis that allows the rotation of the other elastic body is oriented in a different direction.

Further, the invention according to claim 4 is the vibration-damping support device according to any one of claims 1 to 3, wherein the vibration direction of the vibrating body side member, the interposing direction of the elastic body, and The direction in which the axis of the elastic body is allowed to rotate is perpendicular to each other. Further, the invention according to claim 5 is the vibration isolating support device according to the invention according to claim 4, wherein the vibrating body side member is a member fixed to a pressure pipe through which a fluid causing pulsation passes, The vibrating direction of the vibrating body side member is the direction of the bisector of the bending angle in the bent portion of the pressure pipe.

According to a sixth aspect of the invention, in the vibration-damping support device according to the fourth aspect of the invention, the vibrating body side member is a member fixed to a pressure pipe through which a fluid causing pulsation passes. In this case, the vibration direction of the vibrating body side member is set to a direction in which a straight line portion continuous to the bent portion of the pressure pipe is displaced according to the expansion / contraction of the bending angle of the bent portion.

On the other hand, the invention according to claim 7 is the vibration-damping support device according to claim 3, wherein the plurality of elastic bodies are arranged along a circle and the plurality of elastic bodies are rotated. The direction of the axis that allows is intersected at the center of the circle. The invention according to claim 8 is the vibration-damping support device according to any one of claims 1 to 7, wherein the vibrating body-side member is a member fixed to a pressure pipe through which a fluid causing pulsation passes. In some cases, the vibrating body side member was fixed to a portion of each portion of the pressure pipe that was apart from the bent portion.

Further, the invention according to claim 9 is the vibration isolating support device according to any one of claims 1 to 7, wherein the vibrating member is fixed to a pressure pipe through which a fluid causing pulsation passes. In the case of the other member, the member on the vibrating body side is fixed to a part of each part of the pressure pipe that corresponds to a node of the natural vibration mode or a part in the vicinity thereof.

[0012]

In the invention according to claim 1, one end side and the other end side of the elastic body are connected to the vibrating body side member and the supporting body side member in a state where the rotation is appropriately permitted or restricted. Therefore, the elastic body is in a so-called “cantilevered beam” state fixed to the other of the vibrating body side member and the supporting body side member when viewed from the direction along the axis that allows rotation.

Then, the dynamic spring constant of the elastic body with respect to the vibration inputted to bend the elastic body from the direction orthogonal to the axis permitting its rotation is as follows. Compared with the case where the support-side members are firmly coupled, the size is significantly reduced, so that the vibration transmissibility between the vibrator-side member and the support-side member is reduced.

Further, in the invention according to claim 2, the other end of the elastic body is coupled to the other of the vibrating body side member and the supporting body side member in a state in which the elastic body is allowed to rotate, and the elastic body is formed. Since the axis that allows the rotation of the other end side is not parallel to the axis that allows the rotation of the one end side and is orthogonal to the intervening direction of the elastic body, this elastic body allows the rotation of the one end side. When viewed from the direction along the axis, it becomes a "cantilever beam" fixed to the other of the vibrating body side member and the supporting body side member, and when viewed from the direction along the axis that allows rotation of the other end side, The state becomes a “cantilever” fixed to one of the vibrating body side member and the supporting body side member.

Then, the dynamic spring constant of the elastic body with respect to the vibration input from a plurality of directions is significantly larger than that in the case where both ends of the elastic body of the same size are firmly coupled to the vibrating body side member and the supporting body side member, respectively. Therefore, the vibration transmissibility between the vibrating body side member and the supporting body side member is further reduced. In the invention according to claim 1 or 2, the dynamic spring of the elastic body responds to the vibration input to bend the elastic body from a direction orthogonal to the axis that allows the elastic body to rotate. Since the constant becomes small, if a plurality of elastic bodies are provided and the directions in which the axes permitting the rotation of the elastic bodies are directed are made different, as in the invention according to claim 3, the vibration isolating support device is provided in each direction. The dynamic spring constant of can be easily adjusted.

Further, in the invention according to claim 4, the input direction of the vibration and the direction in which the dynamic spring constant of the elastic body is reduced coincide with each other, and these directions are substantially the same as the bending direction of the elastic body. Because of the coincidence, the dynamic spring constant of the elastic body against the vibration input to bend the elastic body becomes the minimum under the condition that the size of the elastic body is constant. Here, if the vibrating body is pressure piping that allows pulsating fluid to pass therethrough, and the rigidity of the pressure piping is sufficiently rigid, and if the pressure piping has a bent portion in the middle, pressure due to the pulsation The direction of vibration generated in the pipe is the direction of the bisector of the bending angle of the bent portion. Therefore, according to the invention of claim 5, the dynamic spring constant of the elastic body against the vibration input to bend the elastic body supporting the high-rigidity pressure pipe is minimum under the condition that the size of the elastic body is constant. Becomes

On the other hand, when the rigidity of the pressure pipe is not sufficiently rigid, the direction of the vibration generated in the pressure pipe due to the pulsation is such that the linear portion continuous to the bent portion is displaced according to the expansion / contraction of the bending angle of the bent portion. It is the direction to do. Therefore, claim 6
According to the invention, the dynamic spring constant of the elastic body against the vibration input to bend the elastic body supporting the low-rigidity pressure pipe is minimized under the condition that the dimension of the elastic body is constant.

Further, in the invention according to claim 7, each of the directions in which the dynamic spring constant of each elastic body is reduced is the tangential direction of a circle along which the elastic bodies are arranged. If the vibration generated in the vibrating body is vibration in the rotation direction such as torque fluctuation, the center axis of the circle along which each elastic body is arranged is the center axis of the vibration in the rotation direction. If they coincide with each other, the dynamic spring constant of the anti-vibration support device becomes small against the vibration in the rotation direction, and the vibration transmissibility is reduced.

Here, as described in the operation of the invention according to claim 5 and claim 6, the vibration generated in the pressure pipe due to the pulsation is generated in the vicinity of the bent portion of the pressure pipe. If the vibrating body side member, to which one end side or the other end side of the elastic body is coupled, is fixed to a portion of the pressure pipe that is away from the bent portion, the vibration input to this elastic body can be small, as in the invention according to. .

Further, in the invention according to claim 9, the vibrating body side member, to which one end side or the other end side of the elastic body is coupled,
Since the pressure pipe is fixed at a position corresponding to the node of the natural vibration mode or in the vicinity thereof, the vibration on the pressure pipe side is prevented from being amplified by the natural vibration mode and input to the elastic body.

[0021]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 3 are views showing a configuration of a first embodiment of the present invention. In this embodiment, the vibration-damping support device according to the present invention is a pipe support device for supporting a pressure pipe for a vehicle on a vehicle body. It has been applied to.

First, the structure will be described. FIG. 1 is a plan view showing a schematic structure of a vehicle. In this vehicle, the driving force of an engine 2 mounted on the front side of a vehicle body 1 is hydraulically adjusted to the left and right. It is a four-wheel drive vehicle that is also distributed to the rear wheels 3RL and 3RR. In the following description, it is assumed that an xyz orthogonal coordinate system is used in which an axis oriented in the vehicle left-right direction is an x-axis, an axis oriented in the vehicle front-rear direction is a y-axis, and an axis oriented in the vehicle up-down direction is a z-axis.

That is, the driving force of the engine 2 is transmitted to the front-wheel-side drive shaft 5 via the transmission 4, and from the front-wheel-side drive shaft 5 the left and right front wheels 3FL.
And 3FR. Therefore, this four-wheel drive vehicle is based on an FF (front engine / front drive) vehicle. Further, a rotary drive type hydraulic pump 6 is disposed in the front part of the vehicle body 1,
The rotational force of the front wheel drive shaft 5 is input to the hydraulic pump 6.

On the other hand, the inner ends of the left and right rear wheel drive shafts 7L and 7R connected to the left and right rear wheels 3RL and 3RR are connected to the output side of the differential gear mechanism that constitutes the final reduction gear 8. The input shaft 8a of the differential gear mechanism that constitutes the final reduction gear 8 extends toward the front of the vehicle, and the tip end of the input shaft 8a is the output shaft of the hydraulic motor 9 disposed in the rear portion of the vehicle body 1. Are linked to.

The high pressure side (discharging side) of the hydraulic pump 6
And the suction side of the hydraulic motor 9 communicate with each other through a high pressure pipe 10A as pressure pipe, and the low pressure side (suction side) of the hydraulic pump 6 and the discharge side of the hydraulic motor 9 are low pressure pipe 10B as pressure pipe. The hydraulic pump 6, the hydraulic motor 9, the high-pressure pipe 10A, and the low-pressure pipe 10B are in communication with each other and are filled with hydraulic oil as a fluid.

Further, the high pressure pipe 10A and the low pressure pipe 10B
Are arranged parallel to each other along the bottom surface of the floor of the vehicle body 1, and are supported on the bottom surface of the floor of the vehicle body 1 at two locations in the longitudinal direction via pipe support devices 11A and 11B as vibration isolation support devices. There is. These pipe support devices 11A,
In 11B, one of the pipe support devices 11A is a high pressure pipe 10A.
And a portion of the low-pressure pipe 10B extending in the y-axis direction,
It has the same structure except that the other pipe support device 11B supports the portions of the high-pressure pipe 10A and the low-pressure pipe 10B extending in the x-axis direction.

Therefore, the concrete structure of the pipe support device 11A will be described. As shown in FIG. 2 which is a perspective view thereof,
The pipe support device 11A includes a high pressure pipe 10A and a low pressure pipe 1.
A bracket 12 having two parallel semi-cylindrical recesses 12A and 12B for simultaneously holding the straight portion of 0B from the lower side is provided, and a flat plate-shaped bracket 13 is horizontally provided on the upper surface side of the bracket 12. It is fixed by welding or screwing. The bracket 12 and the high-pressure pipe 1
0A and low-pressure pipe 10B are, for example, recesses 12A and 12B.
The high-pressure pipe 10A and the low-pressure pipe 10B are firmly fitted to the above, or they are welded to each other so that they are substantially integrated.

Further, the flat plate-shaped bracket 13 horizontally extends further outward in the x-axis direction from the central portion through which the high-pressure pipe 10A and the low-pressure pipe 10B pass, and vertically penetrates each of the left and right ends thereof. Moreover, rectangular openings 13A and 13B having sides parallel to the x-axis and the y-axis are formed. On the other hand, on the bottom surface of the floor of the vehicle body 1, the bracket 1
Brackets 14A, 1 so as to be close to both left and right ends
4B is fixed. These brackets 14A, 14
B is a flat plate portion 14a fixed to the bottom surface of the floor of the vehicle body 1 using bolts and the like, and the bracket 1 of the flat plate portion 14A.
A vertical portion 14b continuously extending from the end portion facing the 3 side to a lower portion separated from the bracket 13 by a predetermined distance, and the vertical portion 1b.
The opening 13 of the bracket 13 continues to the lower end of 4b.
The horizontal portion 14c extends horizontally so as to face the A and 13B from below, and the short edge portion 14c extends upward from the inner end portion of the horizontal portion 14c.

Elastic members 15A and 15B made of synthetic rubber are fixed to the upper surfaces of the horizontal portions 14c of the brackets 14A and 14B, respectively. That is, these elastic bodies 15A and 15B have a U-shape when viewed from the y-axis direction, and the bottom surface of the elastic bodies 15A and 15B is, for example, vulcanized and bonded when the open side of the U-shape faces upward. Horizontal part 14c
It is fixed on the upper surface. In this embodiment, the edge 1
By fixing the inner surface of 4d to the side surfaces of the elastic bodies 15A and 15B, the brackets 14A and 14B and the elastic bodies 15A and 1B are also fixed.
It makes the bond of 5B stronger.

The upper ends of the elastic bodies 15A and 15B, which are bifurcated, pass through substantially the central portions of the openings 13A and 13B and project slightly above the upper surface of the bracket 13.
Two parallel shafts 16 extending in the y-axis direction are fixed between the inner surfaces of the openings 13A, 13B which are parallel to the x-axis direction. It penetrates the bifurcated upper end in the y-axis direction.

At the upper ends of the elastic bodies 15A and 15B, as shown in FIG. 3 (a), a pipe 17 made of a resin containing oil or fat such as silicon is embedded so as to face the y-axis direction, and 16 penetrates the inside of the pipe 17, whereby each of the bifurcated upper ends of the elastic bodies 15A and 15B can smoothly rotate around the axis of the shaft 16. However, for example, by providing the shaft 16 with a protrusion or a lock nut so as to come into contact with the end surface of the pipe 17, the elastic bodies 15A, 15B
Relative displacement between the shaft 16 and the shaft 16 in the direction along the y-axis is prevented. The elastic bodies 15A, 1
In order to make the rotation of the upper end portion of 5B smooth, for example, as shown in FIG.
A pipe 18 having a plurality of semi-cylindrical projections 18a on the inner surface thereof as shown in FIG. 3C may be used, or FIG.
As shown in FIG. 3, instead of the pipe 17, a pipe 19 having a plurality of grooves 19a filled with lubricating oil such as grease may be used as shown in FIG.

Due to this structure, the high-pressure pipe 10
The static load of A and the low-pressure pipe 10B is the elastic body 15A interposed along the z-axis direction between the bracket 13 as the vibrating body side member and the upper surfaces of the horizontal portions 14c of the brackets 14A and 14B as the supporting body side members. , 15B to be supported on the lower surface of the floor of the vehicle body 1. Further, in this embodiment, the z-axis direction is the interposing direction of the elastic bodies 15A and 15B, and the bracket 13 and the elastic body 15 as the vibrating body side member.
With A and 15B, by the shaft 16 and the pipe 17,
The brackets 14A, 1A, 1A and 1B, which are joined together in a state in which rotation around the y-axis orthogonal to the z-axis direction is allowed, are provided as support-side members.
4B and the elastic bodies 15A and 15B are coupled in a state in which rotation about any axis is restricted.

Next, the operation of this embodiment will be described. That is,
The hydraulic pump 6 rotates integrally with the front wheel side drive shaft 5, and the hydraulic motor 9 rotates the rear wheel side drive shafts 7L, 7R.
Therefore, when a rotation speed difference occurs between the front wheel side drive shaft 5 and the rear wheel side drive shafts 7L, 7R while the vehicle is traveling, hydraulic oil having a pressure corresponding to the rotation speed difference is passed through the high pressure pipe 10A. It is supplied from the hydraulic pump 6 to the hydraulic motor 9 side, and a driving force is generated in the hydraulic motor 9 by the supplied hydraulic oil. Then, the driving force is transmitted to the rear wheels 3RL and 3RR through the final reduction gear 8 and the rear wheel side drive shafts 7L and 7R, so that the driving force of the engine 2 is distributed to the rear wheels 3RL and 3RR. Becomes
This vehicle runs in four-wheel drive. The hydraulic oil supplied to the hydraulic motor 9 is returned to the hydraulic pump 6 through the low pressure pipe 10B again, where the pressure is increased again and is supplied to the hydraulic motor 9 side through the high pressure pipe 10A. That is,
When in the four-wheel drive state, the hydraulic oil is sent from the hydraulic pump 6 to continue circulating in the high-pressure pipe 10A and the low-pressure pipe 10B.

The high-pressure pipe 10A and the low-pressure pipe 10B
Pulsation (pressure fluctuation) due to the structure of the hydraulic pump 6 and the hydraulic motor 9 is generated in the hydraulic fluid passing through, and the pulsation causes vibration in the high-pressure pipe 10A and the low-pressure pipe 10B. Therefore, the vibrations generated in the high-pressure pipe 10A and the low-pressure pipe 10B are transmitted to the vehicle body 1 side through the pipe supporting device 11A or 11B, so that the pipe supporting device 11A
And 11B are required to have a function of reducing the vibration generated in the high pressure pipe 10A and the low pressure pipe 10B.

Here, such pipe supporting devices 11A and 11B are mainly required to satisfy the following four conditions. The first condition is a condition for anti-vibration ability.
That is, in the four-wheel drive vehicle as in this embodiment, when the rear wheels 3RL and 3RR are driven by hydraulic pressure, the hydraulic pump 6 generates a high hydraulic pressure of several hundred kgf / cm ² . The level of pulsation generated in the high pressure pipe 10A and the like also increases. Therefore, since the vibration level input to the pipe support devices 11A and 11B is also high, the pipe support devices 11A and 11B are required to have a high vibration isolation capability in order to suppress the vibration input to the vehicle body 1.

The second condition is a condition in the image stabilization direction. That is, in the four-wheel drive vehicle as in this embodiment, the high-pressure pipe 10A and the low-pressure pipe 10B are often arranged in a bent shape in a horizontal plane as shown in FIG. When pulsation occurs in the hydraulic oil passing through the high-pressure pipe 10A and the low-pressure pipe 10B, horizontal vibration is likely to occur in the pipe. Therefore, the pipe support device 11A is required to have a high vibration damping capability against vibration in the x-axis direction,
The pipe support device 11B is required to have high vibration isolation capability against vibration in the y-axis direction.

The third condition is a condition for a vibration proof frequency. That is, since the frequency of the pulsation generated by the hydraulic pump 6 and the hydraulic motor 9 is proportional to the vehicle speed, the frequency is 0 Hz.
Will gradually rise from. Therefore, the pipe support devices 11A and 11B are required to be able to exhibit the vibration isolation capability from an extremely low frequency (for example, a frequency lower than the human audible frequency). However, since the high-pressure pipe 10A and the like are relatively lightweight, it is necessary to set the dynamic spring constant of the elastic bodies 15A and 15B to a value as low as possible in order to exert the vibration damping performance from low frequencies.

The fourth condition is a dimensional constraint condition.
That is, the high-pressure pipes 10A and the like are arranged under the floor of the vehicle body 1. In the space under the floor, it is necessary to provide a protector for a stone bounce or the like while traveling and to clear the minimum ground clearance. Due to the priority conditions, the high dimensions of the pipe support devices 11A and 11B are very limited.

In other words, the elastic members 15A and 15B of the pipe support devices 11A and 11B are made as thin as possible in the x-axis and y-axis directions (first condition) and large in the z-axis direction. Without (the fourth condition), there is a demand for lowering the dynamic spring constant in the bending direction (x-axis direction in the pipe support device 11A, y-axis direction in the pipe support device 11B) (second and third conditions). There is.

Therefore, the elastic bodies 15A and 15B of this embodiment are
The behavior when the vibration is input will be described in detail. That is, as shown in FIG. 4, an exciting force F is applied horizontally from the upper end surface side of a cubic rubber-like elastic body having a width a, a depth b, and a height c, with its bottom surface fixed to the floor surface. Think about giving. First, assuming that the bracket is fixed to the upper end surface of the elastic body and the exciting force F is input to the bracket in the horizontal direction, the elastic body is deformed by shearing deformation as shown in FIG. Then, two types of deformation are conceivable: bending deformation as shown in FIG. Then, assuming that the elastic modulus of the elastic body is G and the deformation amount of the upper end surface when the elastic body is sheared as shown in FIG. 5A is x ₁ , the spring constant k ₁ (= F / x ₁ ) is given by the following equation (1).

K ₁ = Gab / c (1) The equation (1) is derived as follows. That is, γ = Gγ, where γ is the angle of the elastic body at the time of shear deformation in FIG. 5A and τ is the shear stress generated at that time. Then, the cross-sectional area of the elastic body in the horizontal direction is A (= a
When b), if the angle gamma a minute range, because can be approximated as _{γ ≒ x 1 / c, F} = τA = GAγ = GAx 1 / c _{becomes, k 1 = F / x 1} = GA / c = It becomes Gab / c and the above equation (1) is obtained.

On the other hand, when the elastic body is bent and deformed as shown in FIG. 5B, the deformation amount of its upper end surface is x _2, and the spring constant k ₂ (= F / x ₂₎ at the time of such bending deformation. )
Is expressed by the following equation (2). k ₂ = Gba ³ /0.4 c ³ (2) The equation (2) is derived as follows. In other words, regarding an elastic body that is flexurally elastic as shown in FIG. 5B, considering the local coordinate systems x ′ and y ′ as shown in FIG. 6, the longitudinal elastic modulus is E, the second moment of area is I, and the elasticity is when the deformation amount of the elastic body when the concentrated load F and the moment M on the upper end face of the body loaded y and '(x'), from the equation of the elastic ^{line, EI = d 2 y '/} dx' 2 = −Fx ′ + M (3) The boundary conditions are: x = 0 (upper end), dy ′ / dx ′ = 0, ... (4) x = c (lower end), y ′ = dy ′ / dx ′ = 0 (5) .

[0043] Integrating this equation, EIdy '/ dx' = - (F / 2) x '2 + Mx' + C 1 ...... (6) EIy = - (F / 6) x '3 + (M / 2) x ′ ² + C ₁ x ′ + C ₂ (7) is obtained. However, C ₁ and C ₂ are integration constants. Here, from the equations (4) and (6), C ₁ = 0 (8). Further, from the above formulas (5) and (6), since-(F / 2) c + Mc = 0, M = Fc / 2 (9). Then, equation (5), (7) from the equation, and equation (9), - a ^{(F / 6) c 3 +} Fc 3/4 + C 2 = 0 ^{_{So, C 2 = -Fc 3/12}} ...... (10) Become. Then, the equation (8), (9) and (10), is transformed by substituting the equation (7), y '= {- (F / 6) x' 3 + (FC / 4) ^{x '2 -Fc 3/12}} / EI ...... (11) is obtained. Then, since the maximum displacement of the elastic body occurs at x ′ = 0, y ′ _max = y ′ (0) = − Fc ³ / 12EI (12) Here, the relationship between the shear modulus G and longitudinal elastic modulus E, and equation for secondary moment I of the rectangular cross-section, respectively, E ≒ G / 0.4 ...... ( 13) I = ba 3/12 ...... ( 14), substituting each of these equations into equation (12) above yields y ′
by replacing the absolute value of _max to _{x 2, x 2 = 0.4 Fc} 3 / Gba 3 next, by substituting this expression into k ₂ = F / x _2, above (2) is obtained.

Then, as is apparent from the above equations (1) and (2), in order to reduce the spring constant when elastically deforming as shown in FIG. It is understood that the height c of the elastic body may be increased or the width a and the depth b of the elastic body may be decreased.
And it is not desirable to satisfy the condition 4.

On the other hand, the elastic bodies 15A, 1 of this embodiment are
5B, the upper end of the elastic body is allowed to rotate around the y-axis (in the case of the pipe supporting device 11A) or the x-axis (in the case of the pipe supporting device 11B). As shown in (c), the same deformation occurs when a concentrated load is applied to the free end of the cantilever. If the horizontal displacement of the upper end of the elastic body is x ₃ , the spring constant k ₃ (= F / F of the elastic body when deformed as shown in FIG. 5C).
x ₃ ) is given by the following equation (15).

K ₃ = Gba ³ /1.6 c ³ (15) This equation (15) can be derived in the same way as the above equation (2) if the moment M = 0. Therefore, the equation of elastic line is as follows. Eid ² y '/ dx' ² = -Fx 'However, the boundary conditions are x' = c and y '= dy' / dx '= 0.

Solving this and obtaining the absolute value x ₃ of the maximum displacement at x ′ = 0, x ₃ = −Fc ³ / 3EI is obtained. Then, in this equation, the above equation (13) and (1
By substituting the equation 4), x ₃ = 1.6 Fc ³ / Gba ³ , and by substituting this equation for k ₃ = F / x ₃ , the above equation (15) is obtained.

As can be seen by comparing the above equations (2) and (15), the elastic deformation shown in FIG. 5C is made as compared with the elastic deformation shown in FIG. 5B. In this case, the spring constant becomes 1/4. In other words, the spring constant can be greatly reduced if the deformation as shown in FIG. 5C is possible without changing the material of the elastic body and the size thereof.

Furthermore, the above equations (1), (2) and (1
When the ratios of the spring constants k ₂ and k ₃ of the bending spring to the spring constant k ₁ of the shear spring are calculated from the equation 5), k ₂ / k ₁ = (a / c) ² /0.4 (16) k ₃ / k ₁ = (a / c) ² /1.6 (17), and based on these equations (16) and (17), the aspect ratio (a / c) of the elastic body and the spring constant ratio (k ₂ / k ₁ , k ₃
The relationship with / k ₁ ) is shown in FIG. According to this, the value of the spring constant ratio (k ₂ / k ₁ ) is 1 or less,
That is, in order for the bending spring shown in FIG. 5B to be softer than the shear spring shown in FIG. 5A, the aspect ratio (a / c) of the elastic body must be about 0.63 or less. No, this means that the elastic body must be molded to a certain length. On the other hand, the spring constant ratio (k ₃ /
In order that the value of k ₁ ) is 1 or less, that is, the bending spring shown in FIG. 5C becomes softer than the shear spring shown in FIG. 5A, the aspect ratio (a / c) of the elastic body is about It may be 1.26 or less, which means that the bending spring can be softened even if the height c of the elastic body cannot be sufficiently secured.
That is, when the aspect ratio (a / c) of the elastic body is about 1.26 or less, the cantilever state as shown in FIG. 5C minimizes the spring constant in the bending direction. You can do it.

In the structure of this embodiment, since the upper ends of the elastic bodies 15A and 15B are rotatable around the shaft 16, horizontal vibration is generated in the high pressure pipe 10A and the low pressure pipe 10B, and the bracket 13 and bracket 1
Even if horizontal relative displacement occurs between 4A and 14B,
Since the elastic bodies 15A and 15B whose upper ends are free ends are bent and deformed as shown in FIG. 8, the dynamic spring constant thereof becomes extremely small, and the vibration transmission between the high pressure pipe 10A and the low pressure pipe 10B and the vehicle body 1 is transmitted. It is possible to reduce the vibration rate, suppress the vibration on the vehicle body 1 side, and reduce the vehicle interior vibration and noise.

Moreover, the fact that the horizontal dynamic spring constant of the elastic bodies 15A and 15B can be made sufficiently small means that the pipe supporting devices 11A and 11B supporting the high pressure pipe 10A and the low pressure pipe 10B whose vibration frequency rises from 0 Hz. Is very advantageous in that it can reduce vibration from the low frequency band. FIG. 9 is a frequency characteristic diagram showing a simulation result of the vibration isolation performance performed by the present inventors. That is, as shown in FIG. 10, the elastic body 15A in a state of fixing a bottom surface on the base, the upper end face of the 15B, secure the mass m _0, its mass m ₀ in the x-axis direction of the excitation force f ₀
Consider the case of giving. When the spring constants of the elastic bodies 15A and 15B are k ₀ , the damping coefficient is c ₀ , and the displacement of the mass m ₀ during vibration in the x-axis direction is x ₀ , the following differential equation holds.

M ₀ · d ² x ₀ / dt ² + c ₀ · dx ₀ / dt + k ₀ x ₀ = f _{0 When} this is Laplace-transformed and rearranged, F ₀ (s) = (m ₀ s ² + c ₀ s + k ₀ ) X ₀ (s) (18) is obtained. If the force transmitted to the base is f ₁ , then f ₁ = k ₀ x ₀ + c ₀ · dx ₀ / dt. If this is Laplace transformed, F ₁ (s) = (k ₀ + c ₀ s) X ₀ (s) (19), and from these equations (18) and (19), the excitation force f ₀
And the transfer function between the transfer force f ₁ is F ₁ (s) / F ₀ (s) = (c ₀ s + k ₀ ) / (m ₀ s ² + c ₀ s + k ₀ ) ... (20) And the simulation result shown in FIG.
It shows the amplitude of the transfer function of equation (20),
The simulation is performed after setting the spring constant when the rotation around the y-axis is free to a value of 1/4 of the spring constant when the rotation around the y-axis is restricted.

Also from this simulation result, the vibration damping effect can be obtained from a low frequency band by freely rotating the upper ends of the elastic bodies 15A and 15B around the y axis or the x axis as in this embodiment. Therefore, it can be confirmed that the transmissibility can be reduced over most frequency bands as compared with the case where the rotation is restricted. Further, in the configuration of this embodiment, the vibration directions of the high-pressure pipe 10A and the low-pressure pipe 10B (see FIG.
Then, the x-axis direction), the intervening direction of the elastic bodies 15A and 15B (z-axis direction), and the direction in which the axis that allows the rotation of the upper ends of the elastic bodies 15A and 15B (the y-axis direction) are orthogonal to each other. Since the elastic bodies 15A and 15B are bent, the dynamic spring constants of the elastic bodies 15A and 15B with respect to the vibration input from the high pressure pipe 10A and the low pressure pipe 10B are set under the condition that the dimensions of the elastic bodies 15A and 15B are constant. Can be the smallest. Note that these orthogonal directions do not have to be strictly orthogonal, and may be substantially orthogonal (with a deviation of approximately ± several degrees).

With the structure of this embodiment, the dynamic spring constant in the bending direction can be reduced without increasing the height dimension of the elastic bodies 15A and 15B. Pipe support device 11 under the floor
A and 11B are extremely advantageous. At the same time, since it is not necessary to reduce the width of the elastic bodies 15A and 15B, a high hydraulic pressure of several hundred kgf / cm ² is generated by the hydraulic pump 6, and a high level vibration is generated in the high pressure pipe 10A. Even then, it is possible to exert sufficient vibration damping ability.

FIGS. 11 and 12 are views showing a second embodiment of the present invention. In this embodiment as well, similar to the first embodiment, the high pressure pipe and the low pressure pipe of the vehicle are supported on the vehicle body. The present invention is applied to the pipe support devices 11A and 11B. The same components as those in the first embodiment are designated by the same reference numerals, and their duplicate description will be omitted. That is, in the present embodiment, as shown in FIG. 11 which is an enlarged perspective view of the main part of the pipe support device 11A, the x-axis direction end of the bracket 13 fixed to the high-pressure pipe and the low-pressure pipe side is provided. , Four rectangular openings 20A to 20D and 21A to 21D are provided in the x-axis direction and the horizontal part 14c of the bracket 14A fixed to the vehicle body side so as to face each other in the z-axis direction. They are formed one by one.

A shaft 22 extending in the y-axis direction is fixed between the inner surfaces of the openings 20A to 20D formed on the bracket 13 side, and the openings 21A to 21D formed on the bracket 14A side, respectively. A shaft 23 extending in the x-axis direction is fixed between the inner surfaces of the. On the other hand, the openings 20A to 20D facing each other in the z-axis direction
And 21A to 21D, elastic bodies 24A to 24D made of a synthetic rubber having a cylindrical shape are interposed with the axial direction thereof oriented in the z-axis direction.
Metal caps 25 having through holes 25a into which the shafts 22 and 23 are rotatably inserted are fixed to both ends of 24D by vulcanization adhesion or the like. The shafts 22 and 23 pass through the through holes 25 a of each cap 25. Note that, for example, the structure similar to that described in the first embodiment with reference to FIG. 3 allows the shafts 22, 23 and the through hole 25a to rotate smoothly. Also, the shafts 22, 2
Axial relative displacement between 3 and the through hole 25a is also prevented by the same structure as in the first embodiment. The configuration on the bracket 14B side is also similar to the configuration in FIG. In addition, the configuration of the pipe support device 11B is also the y-axis direction and the y-direction.
The configuration is the same as that of the pipe support device 11A, except that the axial direction is interchanged.

Since the shaft 22 and the shaft 23 are orthogonal to each other with such a structure, the elastic bodies 24A to 24D are shown in FIG. 12 when viewed from the direction along the y-axis direction. As shown, the shaft 22 side is bent and deformed as a free end cantilever, and when viewed from the x-axis direction, the shaft 23 side is bent and deformed as a free end cantilever.

As a result, the bracket 13 and the bracket 1
4A, relative to the relative displacement in the x-axis direction, the elastic body 2
Since the end portions of the brackets 4A to 24D on the side of the bracket 13 rotate around the shaft 22 during bending deformation, the elastic body 24
The dynamic spring constants A to 24D are sufficiently reduced for the same reason as described in the first embodiment, and the bracket 13
With respect to the relative displacement between the bracket and the bracket 14A in the y-axis direction, when the elastic bodies 24A to 24D are bent and deformed, the end portion on the bracket 14A side rotates around the shaft 23. The dynamic spring constant of 24D is sufficiently reduced.

Since the x-axis and the y-axis are orthogonal to each other in the horizontal plane, the pipe support device 1 of this embodiment is
According to 1A and 11B, it is possible to exhibit a good vibration damping effect against the vibration of the high-pressure pipe and the low-pressure pipe in the xy plane. The shaft 22 and the shaft 2
3 is most advantageous to reduce the vibration in many directions in the xy plane by making them orthogonal to each other in the horizontal plane as in this embodiment, but these shafts 22 and 23 are orthogonal to each other. The elastic body 2 is not necessary
It is only necessary that they are orthogonal to the intervening direction of 4A to 24D (z-axis direction) and not parallel to each other.

Other functions and effects are similar to those of the first embodiment. FIG. 13 is a diagram showing a third embodiment of the present invention. In this embodiment as well, similar to the first and second embodiments, a pipe support device for supporting a high pressure pipe and a low pressure pipe of a vehicle on a vehicle body. The present invention is applied to 11A and 11B. The same components as those in the first and second embodiments are designated by the same reference numerals, and their duplicated description will be omitted.

That is, in the present embodiment, as shown in FIG. 13 which is an enlarged perspective view of the main part of the pipe support device 11A, the openings 20A-2 formed in the bracket 13 are formed.
Of 0D, the two openings 20 in a diagonal positional relationship
The shafts 22 of B and 20C are fixed in the x-axis direction, and a short cylindrical cap 26 is provided at the end of the two elastic bodies 24B and 24C corresponding to the openings 20B and 20C on the side of the horizontal portion 14c. It is fixed by vulcanization adhesion or the like. Then, the horizontal portion 14c has two openings 2
Only 1A and 21D are formed, and the lower surface of the cap 26 is directly fixed to the surface of the horizontal portion 14c by welding or the like. Other configurations are the same as those of the first embodiment or the second embodiment.
It is similar to the embodiment. The configuration of the bracket 14B side is the same as that of FIG. 11, and the pipe support device 11B
The configuration is also the same as the configuration of the pipe support device 11A, except that the x-axis direction and the y-axis direction are interchanged.

With such a structure, the elastic bodies 24A and 24D are arranged in the x-axis direction and in the y-direction as in the second embodiment.
The elastic bodies 24B and 24C are in a cantilever state when seen from any of the axial directions, but the elastic bodies 24B and 24C are in a cantilever state only when seen in the x-axis direction. Then, each elastic body 24A to 24
The dynamic spring constant of D as a whole has a value equivalent to that of the second embodiment with respect to vibration in the y-axis direction, but is higher than that of the second embodiment with respect to vibration in the x-axis direction.

That is, as in this embodiment, a plurality of elastic bodies 24A to 24D are provided and the elastic bodies 24A are
-24D The elastic body 2 is oriented in the direction of the axis that allows rotation of the end.
If 4A to 4D are made different, it becomes possible to easily set a desired dynamic spring constant for each arbitrary direction, which has the advantage of greatly increasing the degree of freedom in design.

Other functions and effects are similar to those of the first embodiment. 14 to 17 are views showing a fourth embodiment of the present invention. In this embodiment as well, similarly to each of the above-mentioned embodiments, a pipe support device 11A for supporting a high pressure pipe and a low pressure pipe of a vehicle on a vehicle body, The present invention is applied to 11B.
The same components as those in each of the above-described embodiments are designated by the same reference numerals, and the duplicated description will be omitted.

That is, the high-pressure pipe 10A and the low-pressure pipe 10B
Is a hydraulic pump 6 arranged at the front of the vehicle body 1 and the vehicle body 1
Since it is a pipe for communicating with the hydraulic motor 9 arranged at the rear part of the vehicle, as shown in FIG. 14 which is a plan view of the vehicle body 1,
In addition to bending in the xy plane, it also bends in the yz plane as shown in FIG. 15 which is a side view of the vehicle body 1.

Also in this embodiment, similarly to the first embodiment, the high pressure pipe 10A and the low pressure pipe 10B are supported on the lower surface of the floor of the vehicle body 1 through the two pipe supporting devices 11A and 11B. There is a pipe support device 11A
The structure and support state of 11 and 11B are slightly different from those of the first embodiment. First, the pipe support device 11A is shown in FIG.
As shown in FIG. 5, of the two bent portions 30a and 30b of the high-pressure pipe 10A and the low-pressure pipe 10B existing in the front part of the vehicle in the yz plane, the bent portion 30b just before entering the bottom surface of the floor of the vehicle body 1 is slightly bent. The rear part is supported on the bottom surface of the floor.

The pipe support device 11A has a structure similar to that of the pipe support device described in the first embodiment. However, as shown in the enlarged view of FIG. The bracket 14 fixed to the side is provided with an inclined portion 14e parallel to the bisector direction L of the bent portion 30b and orthogonal to the yz plane, and the bracket 13 fixed to the high-pressure pipe 10A and the low-pressure pipe 10B side is also provided. The bending portion 30b is inclined so as to be parallel to the bisector direction L and orthogonal to the yz plane. Then, between the brackets 13 and 14, the elastic body 1 is cantilevered by using the shaft 16 as in the first embodiment.
5A and 15B are interposed, the elastic members 15A and 15B and the shaft 16 thereof are attached to the inclined portion 14
The direction in which the dynamic spring constant of the elastic bodies 15A and 15B is lowered by rotating the surface 90 degrees from the state of the first embodiment on the surface is the bisector direction L.

On the other hand, as shown in FIG. 14, the pipe support device 11B has two bent portions 30 of the high-pressure pipe 10A and the low-pressure pipe 10B, which are present at the rear portion of the vehicle in the xy plane.
Of the c and 30d, the bent portion 3 on the side closer to the hydraulic pump 6
0c is supported on the bottom surface of the floor. This pipe support device 11B also has the same structure as the pipe support device described in the first embodiment, but as shown in FIG. 17 which is a perspective view of the arrangement state, the recess 12A of the bracket 12 is provided. , 12B are aligned with the bent portion 30c so that the direction in which the dynamic spring constant of the elastic bodies 15A, 15B decreases becomes coincident with the bisector direction L of the bent portion 30c.

The high-pressure pipe 10A and the low-pressure pipe 10
When pulsation occurs in the pressure pipe having the bent portions 30a to 30d as in B, and the pressure pipe has sufficient rigidity, an exciting force having a frequency twice that of the pulsation is generated. It is known that this occurs in the direction of the bisector of the bending angle of the bent portion. This is also detailed in “Mechanical Society of Japan, Volume C, Volume 52, 476 (1986)“ Vibration response of piping system due to fluid vibration in pipe ”Hayama et al.”.

By the way, assuming that the bending angle of the bent portion of the pressure pipe as shown in FIG. 18A is α, the cross-sectional area is A, and the pressure is P, the force F1 acting on the bent portion in a steady flow state is It is represented by. F1 = AP (2 (1-cosα)) ^1/2 (21) When the pulsation of ± ΔP occurs in the pressure P, the force F1 fluctuates within the range of the following formula at the same frequency as the pressure pulsation.

A (P−ΔP) (2 (1-cosα)) ^1/2 ≦ F1 ≦ A (P + ΔP) (2 (1-cosα)) ^1/2 (22) The pulsating angular frequency is ω Then, the force variation ΔF1 from the steady flow state is expressed by the following equation.

ΔF1 = AΔP (2 (1-cosα)) ^1/2 sinωt (23) On the other hand, the secondary motive force of the pressure pulsation is derived from the fluctuation of the centrifugal force at the bending portion. That is, as shown in FIG. 18 (b), in the bent portion where the radius of curvature of the pipe central axis is r, the fluid of mass Δm is Δv sin ωt due to pressure pulsation.
If it is oscillating at the speed of, the centrifugal force ΔF2 ′ generated in the pipe due to the mass Δm is expressed by the following formula.

ΔF2 ′ = ΔmΔv ² sin ² ωt / r = ΔmΔv ² (1-cos2ωt) / 2r (24) If the fluid density is ρ, the fluid mass m at the bent portion is m = ρArα ...... (25) Assuming that the relationship of ΔP = ρCΔv (26) is established between the pressure pulsation amplitude ΔP and the velocity fluctuation amplitude Δv, the force ΔF2 generated in the pipe due to the centrifugal force fluctuation of the fluid mass m at the bent portion is From the equations (24) to (26), ΔF2 = AαΔP ² (1-cos2ωt) / 2ρC ² (27) From this equation (27), the secondary vibration force does not depend on the curvature of the pipe, It turns out that it depends on the bending angle of the pipe. Further, it can be seen from the above equations (23) and (27) that it is necessary to reduce the bending angle α of the pipe in both the primary and the secondary in order to reduce the vibration force of the pipe. Further, in order to disperse the exciting force, it is also effective to increase the radius of curvature of the pipe bending. However, from the comparison of the above equations (23) and (27), ΔF2 is much smaller than ΔF1 and ΔF1 is dominant as the exciting force.

The high-pressure pipe 10A and the low-pressure pipe 10
Even if a vibration parallel to the bisector direction L of the bending angle is generated in the bent portions 30a to 30d of B, with the configuration of the present embodiment, the direction of the vibration and the pipe support device 11A, 1
Since the directions in which the dynamic spring constants of the elastic bodies 15A and 15B of 1B are lowered coincide with each other, the vibration transmitted to the vehicle body 1 side can be favorably reduced. Other functions and effects are similar to those of the first embodiment.

FIGS. 19 to 21 are views showing a fifth embodiment of the present invention. In this embodiment as well, similarly to each of the above-mentioned embodiments, a pipe support for supporting the high pressure pipe and the low pressure pipe of the vehicle on the vehicle body is provided. The present invention is applied to the devices 11A and 11B. The same components as those in each of the above-described embodiments are designated by the same reference numerals, and the duplicated description will be omitted. That is, in this embodiment, as shown in FIG. 19 which is a plan view of the vehicle, the straight line portions of the high-pressure pipe 10A and the low-pressure pipe 10B immediately before and after the bent portion 30c are supported on the bottom surface of the floor of the vehicle body 1. Pipe support devices 11C and 11D are provided.

Then, the pipe supporting devices 11C and 11D
Is, as shown in FIG. 20, which is a perspective view of the arrangement,
Between the surfaces of the bracket 13 fixed to the high-pressure pipe 10A and the low-pressure pipe 10B side and the bracket 14 fixed to the vehicle body 1 side facing each other, a columnar rubber-like elastic body 31 is provided.
With the same structure as the elastic bodies 24B and 24C described in the third embodiment, only the end portion on the bracket 13 side is rotatably interposed around the shaft 22. However, in the pipe support device 11C that supports the portions of the high-pressure pipe 10A and the low-pressure pipe 10B that extend in the y-axis direction on the vehicle body 1 side, the shaft 22 faces the y-axis direction, so the dynamic spring constant of the elastic body 31 is The lowering direction is the x-axis direction. On the other hand, in the pipe support device 11D that supports the portions of the high-pressure pipe 10A and the low-pressure pipe 10B that extend in the x-axis direction on the vehicle body 1 side, since the shaft 22 faces the x-axis direction, the dynamic spring constant of the elastic body 31 is The direction of lowering is y
It is in the axial direction.

Here, the bent portion 30c as in the present embodiment.
When the high-pressure pipe 10A and the low-pressure pipe 10B having the are formed of a relatively low-rigidity material, the direction of vibration caused by the pulsation in the high-pressure pipe 10A and the low-pressure pipe 10B is indicated by an arrow in FIG. As described above, the linear portion continuous with the bent portion 30c is displaced in accordance with the expansion / contraction of the bending angle of the bent portion 30c.

Then, in the case of the structure of this embodiment, the direction in which the vibration is generated and the direction in which the dynamic spring constant of the elastic body 31 of the pipe support devices 111C and 11D is low coincide with each other. The vibration transmitted to the first side can be satisfactorily reduced. Other functions and effects are similar to those of the first embodiment. As can be seen from the description of the fourth and fifth embodiments described above, in the pressure pipe having the bent portions 10a to 10d such as the high pressure pipe 10A and the low pressure pipe 10B, the vibration caused by the pulsation does not occur. Since it mainly occurs in the bent portions 10a to 10d or in the vicinity thereof, it is also a good idea to dispose the pipe support device at a position apart from the bent portions 10a to 10d.

22 and 23 are views showing a sixth embodiment of the present invention. In this embodiment also, similarly to the above-mentioned embodiments, a pipe support for supporting the high pressure pipe and the low pressure pipe of the vehicle on the vehicle body is provided. The present invention is applied to the devices 11A and 11B. The same components as those in each of the above-described embodiments are designated by the same reference numerals, and the duplicated description will be omitted. That is, in this embodiment, as shown in FIG. 22, which is a plan view of the vehicle, the arrangement position of the pipe support devices 11A and 11B is appropriately selected. That is, the pipe support device 1 of this embodiment
As shown in FIGS. 23 (a) and 23 (b), 1A and 11B support the node positions of the low-order natural vibration modes of the high-pressure pipe 10A and the low-pressure pipe 10B on the bottom surface of the floor of the vehicle body 1. There is. That is, the pipe support devices 11A and 11
The brackets 12 and 13 on the side of the high-pressure pipe 10A and the low-pressure pipe 10B of B are fixed to the portions of the high-pressure pipe 10A and the low-pressure pipe 10B that correspond to the node positions of the low-order natural vibration mode.

With such a structure, the high-pressure pipe 10A
23 (a) and (b) showing the node positions of the natural vibration modes of the low-pressure pipe 10B and the high-pressure pipe 10A 'and the low-pressure pipe 10B showing the two low-order vibration modes of the high-pressure pipe 10A' and the low-pressure pipe 10B '. As can be seen, it is the position where the influence of vibration is the smallest. Therefore, the vibration input to the pipe support devices 11A and 11B from the high-pressure pipe 10A and the low-pressure pipe 10B is not amplified by the natural vibration mode of the pipes, and the amplitude of the vibration input to the pipe support devices 11A and 11B. The size itself is small, and the vibration level on the vehicle body 1 side can be significantly reduced due to the synergistic effect with the vibration isolation capabilities of the pipe support devices 11A and 11B themselves.

In the structure of this embodiment, the fixing positions of the brackets 12 and 13 do not have to be exactly the node position, and the high pressure pipes 10A and 10A Low-pressure pipe 10B to pipe support device 11A
Since the amplitude of the vibration input to the and 11B is small, the vibration level on the vehicle body 1 side can be significantly reduced.

FIG. 24 is a diagram showing a seventh embodiment of the present invention, and this embodiment also applies the present invention to a pipe supporting apparatus similar to the above-mentioned respective embodiments. And FIG.24 (a) is the figure which expanded the principal part of the piping support apparatus. That is, in this embodiment, as in the fifth embodiment and the like, the high pressure pipe 10
Bracket 13 fixed to A and low pressure pipe 10B side
And a cylindrical rubber-like elastic body 31 is interposed between the surfaces facing the bracket 14 fixed to the vehicle body 1 side.

A lower end surface of the elastic body 31 is directly fixed to the upper surface of the bracket 14 by vulcanization adhesion or the like, and a metal cap 32 is fixed to the upper end surface of the elastic body 31 by vulcanization adhesion or the like. In the cap 32, a ball receiving surface 32a formed of a spherical concave surface is formed so as to open to the upper surface side. A ball 33 is fixed to the lower surface of the bracket 13 via a protrusion 33 a, and the ball 33 is attached to the ball receiving surface 32 of the cap 32.
It is slidably accommodated in a.

That is, the elastic body 31 of the present embodiment is connected to the bracket 13 via the spherical joint (universal joint) composed of the cap 32 and the ball 33. With such a configuration, the end portion of the elastic body 31 on the bracket 13 side is rotatably coupled to the bracket 13 about an arbitrary axis included in the xy plane by the relative rotation between the cap 32 and the ball 33. Therefore, the elastic body 31 is elastically deformed in a cantilever state as shown in FIG. 24 (b). Therefore, even with such a configuration,
Although the dynamic spring constant of the pipe support device can be made extremely low, since the axis of relative rotation between the cap 32 and the ball 33 extends in all directions in the xy plane,
The pipe support device of this embodiment has an advantage that the dynamic spring constant can be made extremely low for all horizontal vibrations of the bracket 13.

In the structure of this embodiment, one end side of the elastic body 31 need only be directly fixed to the bracket 14, so that the height direction of the pipe support device is higher than that of the structure of the second embodiment. There is also an advantage that the size of can be further reduced. Other functions and effects are similar to those of the first embodiment and the like. FIG. 25 (a) is a diagram showing the structure of the eighth exemplary embodiment of the present invention. That is, the vibration-damping support device 35 of the present embodiment has two disc-shaped brackets 36 and 37 that are parallel and coaxially opposed to each other, and these brackets 36 and 37 are also provided.
Between the opposing surfaces of the four cylindrical rubber-like elastic bodies 38
Are connected through.

The elastic body 38 has its axial direction in the bracket 3
The brackets 6 and 37 are interposed between the brackets 36 and 37 in a state of facing each other. In addition, each elastic body 38
Are arranged in a circle along a circle 39 concentric with the brackets 36 and 37 and spaced 90 degrees apart in the circumferential direction. A short cylindrical cap 40 made of metal is fixed to the end of the elastic body 38 on the bracket 36 side by vulcanization adhesion or the like, and the cap 40 is fixed to the bracket 36 by welding or the like.

On the other hand, the bracket 37 has four rectangular opening portions 41 which are spaced by 90 degrees in the circumferential direction along the circle 39.
Is formed, and the shaft 42 is fixed between the inner surfaces of the openings 41 so that the axial direction faces the center O of the circle 39. A metal cap 43 having a through hole 43a into which the shaft 42 is rotatably inserted is fixed to the end surface of each elastic body 38 on the bracket 37 side by vulcanization adhesion or the like. The shaft 42 passes through the through hole 43 a of each cap 43. In addition,
For example, the structure similar to that described in the first embodiment with reference to FIG. 3 enables smooth rotation between the shaft 42 and the through hole 43a.

That is, even in this embodiment, each elastic body 3
Although No. 1 is coupled to the bracket 36 so that relative displacement is impossible, it is cantilevered to the bracket 37 so as to be rotatable around the shaft 42, like the elastic body described in each of the above embodiments. It can be elastically deformed as a beam.
Moreover, when considering a cylindrical coordinate system centered on the z axis extending in the interposing direction of the elastic bodies 31 through the center O of the circle 39 (see FIG. 25B), the rotation of each elastic body 31 on the bracket 36 side. Since the axis that allows is intersecting at the center O along an arbitrary radius r direction of the cylindrical coordinate system, the direction in which the dynamic spring constant of each elastic body 31 is low is the tangential direction of the circle 39. It will be.

Then, even if a torque fluctuation centering on the z-axis is input between the brackets 36 and 37, the dynamic spring of each elastic body 31 is against the relative displacement between the brackets 36 and 37 due to the torque fluctuation. Since the constant is extremely low,
The vibration transmissibility between the brackets 36 and 37 is significantly reduced as compared with a case where the brackets 36 and 37 are directly coupled to each other via an elastic body or the like. Other functions and effects are similar to those of the first embodiment and the like.

Here, the anti-vibration support device 35 of this embodiment is
For example, if it is applied as a device that supports a shaft or the like in which torque fluctuations occur, a through hole is formed in the central portions of the brackets 36 and 37, and the shaft serving as the vibrating body is coaxial with the z axis in the through hole. Through and bracket 3
One of 6 and 37 is fixed to the shaft side, and the bracket 36
The other one of 37 and 37 may be fixed to the support side.

In the first to seventh embodiments, the vibration-damping support device according to the present invention is used to support the high-pressure pipe 10A and the low-pressure pipe 10B as pressure pipes for a four-wheel drive vehicle on the vehicle body 1. Although the case where it is applied to the devices 11A to 11D has been described, the pressure pipes that can be supported are not limited to this, and in the case of a vehicle, hydraulic pipes for a brake system, hydraulic pipes for a hydraulic power steering device, Piping between the fuel tank and the engine, piping that connects the oil cooler and the engine when they are separated,
It may be a pipe or the like that allows the refrigerant of the air conditioner to pass therethrough, or may be a pressure pipe that is used in a machine tool or a plant other than the vehicle.

Further, the vibrating body which can be supported by the anti-vibration supporting device of the present invention is not limited to the high-pressure pipe 10A and the low-pressure pipe 10B as described in the above embodiments, but other vibrating bodies can be used. But of course it doesn't matter. The end of the elastic body, which is the free end of the cantilever in each of the above embodiments, is essentially the same regardless of whether it is on the support side or the vibrating body side. , The elastic bodies 15A, 15B are turned upside down, and the brackets 14A,
Even if it is rotatably connected to 14B and fixed to the bracket 13, the same effect as that of the first embodiment can be obtained. The same applies to the other examples.

Further, the number of elastic bodies to be interposed between the brackets and the like is merely an example in the above description of each embodiment, and this is completely arbitrary, and is appropriately selected by a designer or the like according to the application target. Is.

[0094]

As described above, according to the invention of claim 1, the vibrating body side member and the supporting body side member in a state where one end side and the other end side of the elastic body are appropriately permitted to rotate or restrained from rotating. Since the elastic body is elastically deformed like a cantilever by connecting to each of the above, the dynamic spring constant of the elastic body is greatly reduced, and a good vibration damping effect is exhibited from a low frequency band. The vibration transmissibility can be reduced,
Moreover, since it is not necessary to increase the size of the elastic body, there are various effects that the elastic body can be easily applied even in a place where dimensional constraints are severe.

According to the second aspect of the invention, since the dynamic spring constant of the elastic body with respect to the vibrations input from a plurality of directions becomes low, the vibration transmissibility between the vibrating body side member and the supporting body side member is further reduced. Therefore, there is an effect that a further excellent vibration damping effect can be obtained. Further, according to the invention of claim 3, the dynamic spring constant of each direction of the vibration-proof support device can be easily adjusted, so that the degree of freedom in designing can be greatly increased.

According to the fourth aspect of the invention, the vibration input direction is made to coincide with the direction in which the dynamic spring constant of the elastic body is smaller, and these directions are also substantially coincident with the bending direction of the elastic body. Therefore, the dynamic spring constant of the elastic body against the vibration input to bend the elastic body becomes the minimum under the condition that the size of the elastic body is constant. The effect that it can be applied more easily is obtained.

According to the invention of claim 5, the vibrating body is a pressure pipe through which a fluid causing pulsation passes.
The rigidity of the pressure pipe is sufficiently rigid, and when the pressure pipe has a bent portion in the middle thereof, the vibration damping support device is good against the vibration generated in the pressure pipe due to the pulsation. On the other hand, according to the invention of claim 6, when the rigidity of the pressure pipe is not sufficiently rigid, the vibration damping support device can exhibit a good vibration damping effect against the vibration generated in the pressure pipe due to the pulsation. .

Further, according to the invention of claim 7, the direction in which the dynamic spring constant of each elastic body is reduced is directed toward the tangential direction of the circle along which the elastic bodies are arranged. Even if the vibration generated in the vibrating body is vibration in the rotation direction such as torque fluctuation, a good vibration damping effect can be obtained. Further, according to the invention of claim 8, the vibration inputted to the elastic body can be small. Therefore, by the synergistic effect with the vibration reducing effect of the vibration isolating support device of the invention of claims 1 to 7, Good anti-vibration effect is exhibited.

Further, according to the invention of claim 9, it is possible to prevent the vibration on the pressure pipe side from being amplified by the natural vibration mode and input to the elastic body.
Due to the synergistic effect with the vibration reduction effect of the vibration-damping support device of the invention according to 7, the better vibration-damping effect is exhibited.

[Brief description of drawings]

FIG. 1 is a plan view of a vehicle having a configuration according to a first embodiment.

FIG. 2 is a perspective view of a pipe support device in the first embodiment.

FIG. 3 is a diagram illustrating an elastic body used in a pipe support device.

FIG. 4 is a perspective view of an elastic body used for description.

FIG. 5 is an explanatory diagram of deformation of an elastic body.

FIG. 6 is an explanatory diagram used in a process of deriving a spring constant of an elastic body.

FIG. 7 is a graph showing a relationship between a spring constant ratio and dimensions.

FIG. 8 is a front view showing a deformed state of the elastic body of the first embodiment.

FIG. 9 is a frequency characteristic diagram showing a result of a simulation for obtaining a force transmissibility.

FIG. 10 is an explanatory diagram of a simulation performed by the present inventors.

FIG. 11 is a perspective view showing a configuration of a second embodiment.

FIG. 12 is a front view showing a deformed state of the elastic body of the second embodiment.

FIG. 13 is a perspective view showing the configuration of a third embodiment.

FIG. 14 is a plan view of the vehicle showing the configuration of the fourth embodiment.

FIG. 15 is a side view of the vehicle showing the configuration of the fourth embodiment.

FIG. 16 is a side view showing a supported state of the pipe supporting apparatus according to the fourth embodiment.

FIG. 17 is a perspective view showing a supporting state of a pipe supporting device according to a fourth embodiment.

FIG. 18 is a diagram for explaining the direction of vibration generated in the pressure pipe.

FIG. 19 is a plan view of the vehicle showing the configuration of the fifth embodiment.

FIG. 20 is a perspective view showing a supporting state of a pipe supporting device according to a fifth embodiment.

FIG. 21 is a diagram for explaining the direction of vibration generated in the pressure pipe.

FIG. 22 is a plan view of the vehicle showing the configuration of the fifth embodiment.

FIG. 23 is a diagram showing a vibration mode of pressure piping.

FIG. 24 is an enlarged view of a main part of the configuration of the sixth embodiment.

FIG. 25 is a perspective view showing the configuration of the seventh embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 vehicle body (support body) 2 engine 6 hydraulic pump 9 hydraulic motor 10A high-pressure piping (pressure piping, vibrating body) 10B low-pressure piping (pressure piping, vibrating body) 11A to 11D piping support device (vibration support device) 12, 13 bracket (Vibration body side member) 14 Bracket (support body side member) 15A, 15B Elastic body 16 Shafts 24A-24D Elastic body 30a-30d Bending part 31,38 Elastic body

Claims (9)

[Claims] 1. A vibration isolation support device comprising an elastic body interposed between a vibrating body side member and a supporting body side member so as to be elastically deformed in a bending direction by a vibration input, wherein one end side of the elastic body is provided with the elastic body. While being allowed to rotate around at least one axis orthogonal to the intervening direction of the body, it is coupled to one of the vibrator-side member and the support-side member, and the other end of the elastic body is allowed to rotate. An anti-vibration support device, which is coupled to the other of the vibrating body side member and the supporting body side member while restraining rotation about an axis parallel to the axis. 2. The vibrating body side in a state where the other end side of the elastic body is not parallel to an axis allowing rotation of the one end side but is allowed to rotate about an axis orthogonal to the interposing direction of the elastic body. The anti-vibration support device according to claim 1, wherein the anti-vibration support device is connected to the other of the member and the support-side member. 3. The elastic body according to claim 1, wherein a plurality of the elastic bodies are provided, and an axis that allows the rotation of one elastic body and an axis that allows the rotation of another elastic body face different directions. The anti-vibration support device according to claim 2. 4. The vibrating direction of the vibrating body side member, the interposing direction of the elastic body, and the direction of the axis allowing the rotation of the elastic body are orthogonal to each other. The anti-vibration support device according to any one of claims. 5. The vibrating body side member is a member fixed to a pressure pipe through which a fluid causing pulsation passes, and the vibrating direction of the vibrating body side member is divided into two halves of a bending angle at a bending portion of the pressure pipe. The anti-vibration support device according to claim 4, which is in a line direction. 6. The vibrating body side member is a member fixed to a pressure pipe through which a fluid causing pulsation passes, and a vibrating direction of the vibrating body side member is dependent on expansion / contraction of a bending angle of a bending portion of the pressure pipe. The anti-vibration support device according to claim 4, wherein the straight line portion continuous to the bent portion is displaced. 7. The anti-vibration device according to claim 3, wherein the plurality of elastic bodies are arranged along a circle, and the directions of axes of the plurality of elastic bodies that allow the rotation are intersected at the center of the circle. Support device. 8. The vibrating body-side member is a member fixed to a pressure pipe through which a fluid that causes pulsation passes, and the vibrating body-side member is provided in a portion of each portion of the pressure pipe that is apart from the bent portion. The anti-vibration support device according to any one of claims 1 to 7, which is fixed. 9. The vibrating body side member is a member fixed to a pressure pipe through which a fluid causing pulsation passes, and the vibrating body side member corresponds to a node of the natural vibration mode of each portion of the pressure pipe. Alternatively, the anti-vibration support device according to any one of claims 1 to 7, which is fixed to a portion in the vicinity thereof.