JPH0655942A - Liquid sealed radiator support device - Google Patents

Abstract

PURPOSE:To obtain vehicle body damping operation more effectively by supporting a radiator elastically while preventing deterioration of durability in a support mount. CONSTITUTION:A mount means 3 is interposed between a projecting shaft body 4 projecting from a side end surface of a radiator 1 and a support cylinder part of a vehicle body side support base. The mount means 3 is composed basically of an inner cylinder body 6 in which the projecting shaft body is embedded internally, an outer cylinder body 7 embedded internally in the support cylinder part and an elastic body 8 to connect both to each other, and the inner cylinder body 6 is made eccentric upward by a prescribed quantity to the outer cylinder body 7 in a no-load condition before being installed. Through-spaces 9 and 10 are formed in the elastic body in both upper and lower positions sandwiching the inner cylinder body 6 between them, and the inner cylinder body is supported with a main elastic body part 8a between both the through-spaces. Liquid chambers 11 and 12 are formed respectively between both upper and lower side edges of the elastic body and the outer cylinder body 7, and the respective liquid chambers 11 and 12 and the respective through-spaces are partitioned respectively by means of partition wall parts 8b and 8c. Flap parts 16 projecting in both the through-spaces and the liquid chambers 11 and 12 are arranged in the second partition wall part 8c, and the inner cylinder body 6 is arranged in a concentrical form in the outer cylinder body 7 in an installed condition, and a stopper part fixed to the inner cylinder body 6 is brought into contact with the second partition wall part 8c.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a liquid-sealed radiator supporting device for supporting a radiator via a liquid-filled mount.

[0002]

2. Description of the Related Art Conventionally, as a radiator supporting device,
It is known that an elastic mount such as a bush type is interposed between the left and right side portions of the radiator and the vehicle body frame to support the radiator (for example, the actual opening 63-
54515 and JP-A-58-161616). This type of engine is a dynamic system that uses the radiator as an inertial mass by elastically supporting the radiator on the vehicle body in order to suppress resonance of the front portion of the vehicle body especially in a low rotation state such as when the engine is idling. It constitutes a damper, and the elastic mount is composed only of a rubber elastic body.

[0003]

However, the elastic mount constituted only by the rubber elastic body has a relatively narrow resonance frequency region and exhibits a peak damping effect in the narrow frequency region. Therefore, there is a problem that it is not possible to exert a sufficient damping effect on all the regions of the vibration acting on the vehicle body during the idle rotation. Moreover, when the mounting position of the elastic mount is deviated at the time of assembling, the resonance frequency region may be deviated and the desired vibration damping effect may not be obtained. . In addition, in the elastic mount composed of a solid rubber elastic body, the elastic body is compressed by its own weight in the mounted state where the radiator's own weight is loaded, and the inner cylindrical body is eccentric. It may not be possible to exert it.

Further, in order to suppress the resonance amplitude due to the above-mentioned vibration, the damping function of the elastic mount is adjusted to be increased, that is,
Although it is necessary to increase and adjust the damping coefficient or loss coefficient, the elastic mount composed only of rubber elastic bodies has a limit to the increase adjustment range, and the degree of freedom in designing the radiator support device is relatively small. There is a problem that it is small and it is not always possible to perform optimum elastic support. Moreover, when the rubber elastic body is changed to a material having a higher damping function, that is, a material having a higher loss coefficient (tan δ) (for example, isobutylene isoprene rubber; IIR), the higher the loss coefficient, the higher the rubber elasticity. In addition to increasing the amount of heat generated inside the body, a synergistic effect with the heat effect from the radiator side makes it more susceptible to heat deterioration and settling, resulting in deterioration of durability.

The present invention has been made in view of the above circumstances. An object of the present invention is to prevent the deterioration of the durability of the supporting mount while suppressing the vibration of the vehicle body by elastically supporting the radiator. To get more effectively.

[0006]

In order to achieve the above object, the invention according to claim 1 is one in which both sides of a radiator are supported by a vehicle body through mounting means, and both ends of the radiator are supported. While the first support portion protruding outward from the position is provided, the vehicle body is provided with the second support portion facing the first support portion. The mount means is connected to one of the first support portion and the second support portion and an inner cylinder body that is externally inserted into the inner cylinder body and is connected to the other of the first support portion and the second support portion. An outer cylinder body, an elastic body connecting the outer cylinder body and the inner cylinder body, a plurality of liquid chambers defined inside the elastic body, a liquid enclosed in the liquid chamber, And a throttling passage that communicates the liquid chambers with each other. Then, the plurality of liquid chambers are arranged such that liquid is generated from one liquid chamber to another liquid chamber through the throttle passage by input vibration acting on the elastic body from the vehicle body side. is there.

According to a second aspect of the present invention, in the invention according to the first aspect, the mounting means has both side positions in a vibration input direction which is a direction which sandwiches the inner cylinder and is orthogonal to a cylinder axis of the inner cylinder. First and second through-holes penetrating the elastic body in parallel with the cylinder axis, and a stopper portion protruding from the inner cylinder toward the second through-hole toward one side in the vibration input direction,
The elastic body includes first and second liquid chambers formed between both ends of the elastic body in the vibration input direction and the outer cylindrical body. In addition, the elastic body divides the main elastic body portion that is partitioned into the first and second through spaces to elastically support the inner cylindrical body, the first through space and the first liquid chamber. While being provided with a first partition wall and a second partition wall partitioning the second through space and the second liquid chamber, the second partition wall is orthogonal to the cylinder axis and orthogonal to the vibration input direction. A pair of flaps is formed so as to project from both sides in the direction of the arrow to the second through space side and the second liquid chamber side, respectively. Then, while the inner cylindrical body is supported by the main elastic body portion at a position eccentric with respect to the outer cylindrical body in a non-loaded state before being mounted on the radiator, the mounted state in which the weight of the radiator acts on the inner cylindrical body. The outer cylinder is supported at a concentric position, and in the mounted state, the tip of the stopper is arranged so as to be able to transmit vibration to the opposing second partition.

[0008]

With the above construction, in the invention according to claim 1,
For example, vibrations during idle rotation of the engine are transmitted from the second support portion on the vehicle body side to the elastic body via the inner cylinder body or the outer cylinder body of the mount means, and the elastic body is bent. As a result, the liquid in the liquid chamber flows through the throttle passage, so that the input vibration absorbs the vibration due to the spring action of the elastic body of the elastic mount and the damping action based on the flow resistance of the liquid through the throttle passage between the plurality of liquid chambers. Vibration is absorbed by and damped by. For this reason, the resonance frequency range is wider than in the case of the mounting means constituted only by the elastic body, and vibration can be suppressed over the entire frequency range of the vibration during the idle rotation. Further, due to the damping action based on the flow resistance of the liquid, the vibration acceleration of the vibration system having the radiator as a mass at the time of input of a large impact force is reduced, and the excitation force acting on the radiator is reduced. . As a result, the durability of the radiator itself and the connection with the radiator hose can be improved.

According to the second aspect of the invention, in addition to the operation of the first aspect of the invention, the first support portion and the second support portion are provided.
By supporting the own weight of the radiator on the vehicle body side by interposing the mounting means between the mounting portion and the support portion, the inner cylinder of the mounting means is positioned at the concentric position with the outer cylinder.
It is set to the initial setting state for surely exhibiting a predetermined elastic support characteristic in the assembled state. When the radiator as a mass is vibrated in the vibration input direction, the inner cylinder moves relatively in the vertical direction, and the tip of the stopper portion presses the second partition wall portion toward the second liquid chamber side. The liquid in the two liquid chamber flows to the first liquid chamber side through the throttle passage, and a flow resistance is generated during this flow. Therefore, the input vibration is absorbed by the spring action of the main elastic body portion that supports the inner cylindrical body, and is also damped by the flow resistance of the liquid when passing through the throttle passage. Moreover, in this case, as a result of the stopper portion pressing the portion between the two flap portions of the second partition wall portion, the both flap portions are swung about the axis parallel to the cylinder axis of the inner cylindrical body to cause the second liquid. The portion protruding toward the chamber moves in the second liquid chamber, and the liquid is forced to flow in the liquid chamber. The forced flow of the liquid further promotes the damping action of the input vibration.

[0010]

Embodiments of the present invention will be described below with reference to the drawings.

1 and 2 show a liquid ring radiator apparatus according to an embodiment of the present invention, in which 1 is a radiator arranged on the front side of a vehicle body, and 2 and 2 are the width direction of the radiator 1 (see FIG. 1). (A left-right direction of) a support board for supporting a radiator, which is a part of the vehicle body fixed to both sides of the vehicle body,
Denoted by 3 are bush type mounting means interposed between the radiator 1 and the support substrate 2.

Both end surfaces 1 of the radiator 1 in the vehicle width direction
The a and 1a are provided with convex shaft bodies 4, 4, ... As a first support portion projecting outward from the respective positions of the upper and lower portions, and the respective convex shaft bodies 4 are mounted on the mounting means 3 described above. Is fitted in an inner cylinder body 6 described later and is connected to the mount means 3.

The radiator 1 of each of the support substrates 2
The outer surface 7a of the base plate 2a opposite to the side end surface 1a of the mounting means 3 is connected to the mounting means 3 by fitting the outer cylindrical body 7 of the mounting means 3 which will be described later in a position facing the respective convex shaft bodies 4. The support cylinder part 5 as 2 support parts is each formed.

As shown in detail in FIGS. 3 to 5, each of the mounting means 3 has an inner cylindrical body 6 and an outer cylindrical body 7 arranged outside the inner cylindrical body 6 at a predetermined distance. An elastic body 8 that connects the inner peripheral surface of the outer cylindrical body 7 and the outer peripheral surface of the inner cylindrical body 6 to each other and the cylinder axis X of the inner cylindrical body 6 are sandwiched between the vibration input directions (see FIGS. 3 to 5). Vertical direction: hereinafter, simply referred to as vertical direction) First through void 9 and second through void 10 penetrating the elastic body 8 at both side positions, and elasticity at both vertical positions of each of these through voids 9, 10. A first liquid chamber 11 and a second liquid chamber 11 formed between the body 8 and the inner peripheral surface of the outer cylinder body 7 and in which the liquid L is sealed.
The liquid chamber 12 and the elastic body 8 are provided at respective positions on the outer peripheral side on both sides in a direction orthogonal to the vibration input direction and orthogonal to the cylinder axis X (left and right direction in FIGS. 1 and 2; hereinafter simply referred to as left and right direction). It is basically composed of the formed orifices 13 and 13 as throttle passages.

The inner cylindrical body 6 has an inner diameter substantially the same as the outer diameter of the convex shaft body 4, and the inner cylindrical body 6 has a second through space 10 extending from the lower surface of the inner cylindrical body 6. A stopper portion 14 protruding downward is fixed along the inner cylindrical body 6.

The elastic body 8 is divided by the first through space 9 and the second through space 10 and extends on both sides in the left and right direction with the inner cylindrical body 6 interposed therebetween, and the first elastic space 8a. 1
A relatively thin first partition wall portion 8b for partitioning the through space 9 and the first liquid chamber 11, the second through space 10 and the second liquid chamber 12 described above.
And a relatively thick second partition wall portion 8c for partitioning the and.
Synthetic resin plates 15 are embedded as core materials at both left and right sides of the second partition 8c, and a pair of elastic plates covering the periphery of each plate 15 are provided on both sides in a substantially vertical direction. Flap part 1
6, 16 are formed. The space-side convex portion 1 protruding by a predetermined amount toward the second penetrating space 10 side by each flap 16
6a and a liquid chamber side convex portion 1 protruding by a predetermined amount toward the second liquid chamber 12 side
6b is formed. The flap portions 16 and 16 and the central wall portion 8d of the second partition wall portion 8c that connects the flap portions 16 and 16 to each other are the liquid chamber side convex portions 16b and
The space-side convex portions 16a, 16a are arranged such that the space therebetween is wider than the space 16b, and is substantially W-shaped.

The main elastic body portion 8a elastically supports the inner cylindrical body 6, and the inner cylindrical body 6 is in an unloaded state before the mounting means 3 is mounted on the radiator 1 (see FIG. 3).
In the state shown in FIG. 2), the first through space 9 is located at a position eccentric to the upper cylinder 7 by a predetermined amount, and the vertical space between the first through space 9 and the second through space 10 is relatively small. Is becoming relatively large. Then, the mounting means 3 is mounted on the radiator 1 and the mounted state in which the weight of the radiator 1 is loaded (the state shown in FIG. 4).
Then, the main elastic body portion 8a is bent by the self-weight and the inner cylindrical body 6 is positioned at the concentric position with the outer cylindrical body 7. By positioning the inner cylinder body 6 at the concentric position, the tip end portion 14a of the stopper portion 14 abuts and presses against the central wall portion 8d of the second partition wall portion 8c, and the both flap portions 16, 16 are brought into contact with each other. By swinging about an axis parallel to the cylinder axis X, opposite to the above-mentioned unloaded state, the both-cavity-side convex portions 16a, 16a approach the inner cylinder body 6 side, respectively, and sandwich the stopper portion 14 from both left and right sides. It is like this.
At this time, the void-side convex portions 16a of the flap portions 16 are separated from the main elastic body portion 8a with a slight gap (see FIG. 6).

The inner cylindrical body 6 and the elastic body 8 are pre-vulcanized integrally with the intermediate cylindrical body 17 embedded in the outer peripheral side of the elastic body 8, and the outer peripheral surface of the intermediate cylindrical body 17 is It is press-fitted and integrally connected to the inner peripheral surface of the outer cylindrical body 7 through the covering thin film 8e. Then, the cylindrical wall surfaces of the intermediate cylindrical body 17 in the range corresponding to the first and second liquid chambers 11 and 12 serve as cutout window portions 17a and 17b, and are formed outside the first and second partition wall portions 8b and 8c. First and second liquid chambers 11 and 12 are formed between the inner peripheral surface 7 a of the cylindrical body 7 and the inner peripheral surface 7 a. Also,
A part of the thin film 8e between the windows 17a and 17b is cut out in the circumferential direction (see FIG. 7), and the outer peripheral surface of the intermediate cylindrical body 17 and the outer cylindrical body 7 in the cutout portion are formed. An orifice 13 is formed between the inner peripheral surface and the first liquid chamber 11 and the second liquid chamber 12 as a throttle passage that communicates with each other.

As an example of a specific specification setting, the weight of the radiator 1 is, for example, 8 to 15 Kgf, and the radiator 1
When the radiator 1 is supported by the mounting means 3 of 2 to 4, the ratio k of the mass of the vehicle body to the mass of the main body 8a of the main elastic body 8a is k2.
Is set to a value of 2.0 to 7.5 Kgf / mm, and the damping coefficient c due to the flow resistance of the liquid L based on the orifices 13 and 13 is set to a value of 0.02 to 0.09. When the ratio μ is a value in the range of 0.26 to 0.42, the loss coefficient ta
A value in the range of nδ of 0.52 to 0.84 may be set as a preferable value.

Next, the basic operation and effect of the first embodiment having the above construction will be described based on the vibration system model of FIG.

In the figure, m1 is the mass of the vehicle body B, k1
Is a spring constant for supporting the vehicle body B, x1 is an exciting force F cosωt
Is the amplitude of the vehicle body B when m is applied, m2 is the mass of the radiator 1, and x2 is the amplitude of the radiator 1 when the above-mentioned exciting force acts on the vehicle body B. The radiator 1 having the mass m2 is supported on the vehicle body B by each mounting means 3 including a spring having a spring constant k2 and a dashpot having a damping coefficient c, and the spring is the main elastic member of each mounting means 3. The liquid L, which corresponds to the body portion 8a and has the dashpot passing through both orifices 13 and 13 of the mounting means 3,
Equivalent to the flow resistance of. That is, to the main vibration system with the spring constant k1 on the vehicle body B side, a sub-vibration system with the spring constant k2 with the radiator 1 as a mass and the damping coefficient c is added.

In this vibration system model, when vibration is input from the vehicle body B side, the radiator 1 having a mass m2 has a spring action due to the main elastic body portion 8a, and the liquid at both orifices 13 and 13 is Since vibration occurs in the state where the damping force based on the flow resistance of L acts, the vibration damping of the vehicle body B by the dynamic damper having the radiator 1 as a mass can be performed based on both the spring action and the damping action. it can. In this case, as compared with the conventional radiator supporting device that suppresses vibration only by the spring action of the elastic body, the resonance frequency range is expanded, and the vibration suppressing action can be obtained over the entire frequency range of vibration during idle rotation.

Further, the damping action based on the flow resistance of the liquid L can reduce the vibration acceleration of the sub-vibration system having the radiator 1 as a mass when a large impact force is input, and acts on the radiator 1. The excitation force can be reduced. As a result, the durability of the radiator 1 itself and the connecting portion with the radiator hose can be improved. Further, even if the mounting position of each mounting means 3 with respect to the radiator 1 is displaced due to the expansion of the resonance frequency region and the position of the resonance peak is slightly displaced, the damping function is deteriorated as compared with the case of the conventional radiator supporting device. The degree can be reduced.

Further, when the damping function of each of the mount means 3 is increased and adjusted, that is, when the loss coefficient is increased, the flow passage lengths and flow passage cross-sectional areas of the orifices 13 and 13 are adjusted to adjust the above. It is possible to easily adjust the loss coefficient, and it is possible to increase the adjustment to a range that is difficult only by adjusting the material of the rubber in the conventional radiator supporting device. Therefore, the degree of freedom of increasing the damping function, that is, the degree of freedom in designing the radiator support device can be increased, and the radiator support having the optimum vibration damping function according to the conditions of the vehicle body side on which the radiator is mounted is provided. A device can be formed. This also allows
It is possible to easily prevent deterioration of durability due to the change of the material of the rubber in the conventional radiator supporting device.

In particular, the above spring constant k2 and damping coefficient c
Is set to a predetermined optimum value based on the ratio of the mass m1 of the vehicle body B to the mass m2 of the radiator 1 and the like, so that more effective vibration damping can be performed. That is, by adopting the spring constant k2 and the damping coefficient c as the values shown as the above-mentioned preferable example, the resonance curve has two fixed points of S point and P point like the resonance curve P2 shown by the solid line in FIG. It can be assumed that each has an extreme value in the vicinity and has substantially the same response magnification between the two fixed points. A resonance curve P1 shown by a one-dot chain line in the figure is for a case where the damping coefficient ratio μ is 0, and has two maximum values (peaks) as two resonance points. Then, as the damping coefficient ratio μ is increased, the value of the maximum value becomes smaller, and when the value exceeds a predetermined value, both peaks start to overlap with each other, and the damping coefficient ratio μ becomes ∞.
As shown by the broken line in the figure, both peaks of the resonance curve P3 overlap and one resonance point is obtained, and the response magnification becomes infinite. That is, the resonance point of the radiator 1 (η =
Peak resonance occurs in an extremely narrow region near 1.0). On the other hand, the damping coefficient ratio μ is 0.26 to
Resonance curve P2 when a value within the range of 0.42 is adopted
Has substantially equal response magnifications in the vicinity of the two fixed points of the point S and the point P, and can expand the resonance frequency region across the resonance point of the radiator 1. In addition,
The points S and P are fixed points through which all resonance curves must pass regardless of the damping coefficient ratio.

Next, the specific operation and effect of the first embodiment will be described with reference to FIG. For convenience of explanation, one mount means 3 will be described below.

When vibrations of high amplitude and small amplitude are input to the mount means 3 in the vertical direction from the vehicle body side through the support cylinder portion 5, the input vibrations are transmitted to the elastic body 8 via the outer cylinder body 7. The main elastic body 8 is transmitted to the main elastic body 8a.
a is bent in the vertical direction. At this time, the main elastic body portion 8
a is the amount of bending within the range of the vertical gap of the gap between the space-side convex portion 16a and the main elastic body portion 8a, and the main elastic body 8a is located in the upper and lower first and second penetrating voids 9 and 10. Since it is partitioned and can be deformed independently, it is possible to reliably absorb the vibration of the above-mentioned high-frequency minute amplitude and perform vibration isolation.

Further, the amplitude is larger than the above-mentioned vibration such as the vibration at the time of idle rotation of the engine and the low frequency (for example, 20 to 40).
When the vibration of (Hz) is inputted, the main elastic body portion 8a bends, so that the inner cylindrical body 6 relatively moves in the vertical direction. When this relative movement is, for example, in the direction in which it is pushed downward, the tip portion 14a of the stopper portion 14 pushes down the central wall portion 8d of the second partition wall portion 8c to reduce the size of the second liquid chamber 12. Therefore, the liquid L in the second liquid chamber 12 is
The first liquid chamber 11 is forcibly flowed through 13 to the first liquid chamber 11 side, and the inflowing liquid L pushes down the first partition wall portion 8b to enlarge the first liquid chamber 11. The input vibration is damped by the flow resistance of the liquid L when passing through each orifice 13.
Therefore, the damping of the input vibration can be performed based on both the spring action of the main elastic body portion 8a and the flow resistance of the liquid L in each of the orifices 13.

Further, in this case, when the central wall portion 8d is pushed down, both flap portions 16 and 16 swing about the axis parallel to the cylinder axis X, and the respective liquid chamber side convex portions 16b are brought into contact with the second liquid. Because the swinging movement in the left and right direction is repeated in the chamber 12,
The forced flow of the liquid L in the second liquid chamber 12 occurs. Therefore, it is possible to suppress the input vibration by the spring action of the second partition wall portion 8c that causes the swinging of the flap portions 16 and 16 and the damping action based on the forced flow of the liquid L accompanying the swing. You can

Furthermore, when a large impact force larger than the vibration at the time of idle rotation is input, the relative movement of the inner cylindrical body 6 further pushes down the central wall portion 8d, so that the second liquid chamber 12 is pushed further. Greater downsizing and greater swinging of the flaps 16, 16 results. For this reason, a greater damping effect is produced than in the case of the vibration during idle rotation, and the large impact force can be absorbed.
In addition, contact between the main elastic body portion 8a and each cavity-side convex portion 16a and contact between each liquid chamber-side convex portion 16b and the inner peripheral surface of the outer cylindrical body 7 occur, so that the inner cylindrical body Further downward displacement of 6 is restricted. In this case, the displacement is not restricted by one stopper portion coming into contact with the inner peripheral surface of the outer tubular body 7, but the inner tubular body 6 and the stopper portion 14 are provided with both flap portions 16, 1.
6 is sandwiched between the space side convex portions 16a, 16a and the central wall portion 8d, and the inner peripheral surface of the outer cylindrical body 7 is formed by the two portions of the liquid chamber side convex portions 16b, 16b of the both flap portions 16, 16. Since the displacement is regulated in a state where the large impact force is dispersed by contacting with 7a, it is possible to reliably prevent the inner cylinder body 6 from being displaced by a predetermined amount or more when the large impact force is input, and at the It is possible to prevent the excessive concentration of stress.

10 and 11 show a second embodiment of the present invention. In the figure, reference numeral 18 denotes an elastic body, and this elastic body 18 has a main elastic body portion 18a for elastically supporting the inner cylindrical body 6,
The first thin wall that divides the first through space 9 and the first liquid chamber 11
A thick second partition wall portion 18c that defines the second liquid chamber 12 between the partition wall portion 18b and the inner peripheral surface 7a of the outer cylindrical body 7;
The central wall portion 18d of the partition wall portion 18c and the main elastic body portion 18a
And a connecting portion 18e for connecting the vicinity of the inner cylindrical body 6 of FIG.

Numeral 19 is a stopper portion fixed to the inner cylindrical body 6 and embedded in the connecting portion 18e,
20a and 20b are the main elastic body portion 18a and the second partition wall portion 1
8c is a second through-hole formed between the two and 8c, and is divided into two in the left-right direction by the connecting portion 18e.

Further, 21 and 21 are the second partition 18
It is a flap portion formed at both left and right positions with the central wall portion 18d of c interposed therebetween, and a plate 15 oriented substantially vertically is embedded inside. The left and right flap portions 21 and 21 and the central wall portion 18d are formed to have a substantially W-shaped cross section.

The inner cylindrical body 6 is eccentric to the outer cylindrical body 7 by a predetermined amount in an eccentric position with respect to the outer cylindrical body 7 in the unloaded state before being mounted on the radiator 1 by the main elastic body portion 18a or the like. It is in a supported state (state shown in FIG. 10),
In this state, the main elastic body portion 18a and each of the flap portions 21 are
The vacant space-side convex portions 21a are separated from each other. Then, in the mounted state in which the weight of the radiator 1 acts, the radiator 1 is supported at the concentric position with the outer cylinder body 7 (the state shown in FIG. 11) as in the first embodiment. In the state, the main elastic body portion 18a is bent and the central wall portion 18d is pushed down, so that the flap portions 21, 2 are
Both the liquid chamber side convex portions 21b, 21b of the No. 1 widen outward in the left-right direction, and the both space side convex portions 21a, 21a are stopper portions 19
The main elastic portion 18a is brought into contact with the main elastic body portion 18a in a state of being close to the side.

Also in the second embodiment, the basic effect of damping the vehicle body by the spring action and the damping action based on the flow resistance of the liquid L can be obtained as in the first embodiment. .

Further, in the second embodiment, when a vibration of a high frequency and a small amplitude is vertically input to the mount means 3 from the vehicle body side through the support cylinder portion 5, the input vibration is the outer cylinder. It is transmitted to the main elastic body portion 18a of the elastic body 18 via the body 7, and the main elastic body portion 18a is deflected in the vertical direction between each space-side convex portion 21a and the first partition wall portion 18b. Due to the spring action of the main elastic body portion 18a, it is possible to surely absorb the vibration of the above-mentioned high-frequency minute amplitude and perform vibration isolation.

Further, when the vibration at the time of idle rotation of the engine, which has a larger amplitude and a lower frequency than the above-mentioned vibration, is input, the main elastic body portion 18a is bent, and as a result, the inner cylindrical body 6 relatively moves in the vertical direction. When this relative movement is, for example, in the direction of being pushed downward, the second partition wall portion 1 is connected via the connecting portion 18e.
The central wall portion 18d of 8c is pushed down to reduce the size of the second liquid chamber 12. Therefore, the liquid L is forcibly flowed from the second liquid chamber 12 side to the first liquid chamber 11 side through both orifices 13 and 13, and due to the flow resistance of the liquid L when passing through each orifice 13, the input Vibration is dampened. Therefore, the damping of the input vibration is achieved by the spring action of the second partition wall portion 18c connected via the main elastic body portion 18a and the connecting portion 18e and the flow resistance of the liquid L in each orifice 13. It can be done based on both.

Further, in this case, when the central wall portion 18d is pushed down, both flap portions 21 and 21 swing about the axis parallel to the cylinder axis X, and the respective liquid chamber side convex portions 21b move to the second liquid. Since the swinging movement in the left-right direction is repeated in the chamber 12, the forced flow of the liquid L in the second liquid chamber 12 is caused to promote the damping of the input vibration as in the first embodiment. Can be planned.

Further, when a large impact force larger than the vibration at the time of idle rotation is inputted, the relative movement of the inner cylinder body 6 pushes the central wall portion 18d further strongly, and the central wall portion 18d is further pushed. Greater downsizing and greater swinging of the flaps 16, 16 results. In addition, contact between the main elastic body portion 18a and each void-side convex portion 21a, and
The contact between the liquid chamber side convex portion 21b and the inner peripheral surface 7a of the outer cylindrical body 7 occurs, and further downward displacement of the inner cylindrical body 6 is restricted. Therefore, similarly to the first embodiment, it is possible to reliably prevent the displacement of the inner cylinder body 6 by a predetermined amount or more when a large impact force is input, and also to prevent local concentration of excessive stress. be able to.

The present invention is not limited to the first and second embodiments described above, but includes various other modifications. That is, in the above-described first and second embodiments, the convex shaft body 4 is shown as the first support portion and the support tubular portion 5 is shown as the second support portion, but the present invention is not limited to this, and for example, the support tubular portion is provided as the first support portion. May be formed to form a convex shaft body as the second support portion, and the outer cylinder body of the mounting means may be connected to the radiator side and the inner cylinder body may be connected to the vehicle body side.

In the first embodiment, the tip end portion 14a of the stopper portion 14 and the central wall portion 8d of the second partition wall portion 8c are in contact with each other in the mounted state. For example, both may be in a state of being close to each other with a slight gap. Also in this case, the same effect can be obtained.

[0042]

As described above, according to the liquid ring radiator support device of the first aspect of the present invention, when vibration such as during idle rotation of the engine is input from the vehicle body side to the radiator side, the vibration is transmitted. Vibration can be suppressed by the vibration absorption by the spring action of the elastic body of the mounting means and the vibration absorption by the damping action based on the flow resistance of the liquid through the throttle passage between the plurality of liquid chambers. In this case, the resonance frequency range can be expanded as compared with the case where only the spring action of the elastic body is used in the conventional device, and the vibration can be effectively suppressed over the entire frequency range of the vibration during the idle rotation. Moreover, even if the mounting position of the mounting means with respect to the radiator deviates due to the expansion of the resonance frequency region and the position of the resonance peak deviates somewhat, the degree of deterioration of the vibration damping function can be made smaller than in the case of the conventional device.

Further, due to the damping action based on the flow resistance of the liquid, it is possible to reduce the vibration acceleration of the vibration system whose mass is the radiator when a large impact force is input, and the vibration force acting on the radiator is reduced. It can be reduced.
As a result, the durability of the radiator itself and the connection with the radiator hose can be improved.

Furthermore, the damping function of the mounting means can be easily increased by adjusting the degree of flow resistance of the liquid, and the adjustment can be made to a range that is difficult to adjust only by changing the material of the rubber in the conventional device. be able to. Therefore, the degree of freedom of increasing the damping function, that is, the degree of freedom in designing the radiator support device can be increased, and the radiator support having the optimum vibration damping function according to the conditions of the vehicle body side on which the radiator is mounted is provided. A device can be formed. Further, this makes it possible to easily prevent deterioration of durability due to a change in the material of the rubber in the conventional device.

According to the second aspect of the invention, in addition to the effect of the first aspect of the invention, the weight of the radiator is reduced by interposing the mounting means between the first support portion and the second support portion. Since the inner cylinder of the mounting means is positioned concentrically with the outer cylinder by supporting the mounting means on the vehicle body side, a predetermined elastic support characteristic can be surely exhibited in the mounted state. Then, when the radiator as the mass is vibrated in the vibration input direction, the inner cylindrical body relatively moves in the vertical direction, and the tip portion of the stopper portion presses the partition wall portion having the flap portion toward the liquid chamber side. As a result, the liquid flows from this liquid chamber side to the other liquid chamber side through the throttle passage, so that the input vibration can be absorbed by the spring action of the elastic body supporting the inner cylindrical body, and the liquid It can also be damped by the flow resistance when passing through the throttle passage. Therefore, the effect of the invention described in claim 1 can be easily and surely achieved.

Moreover, in this case, as a result of the stopper portion pressing the partition wall portion between both flap portions, both flap portions are swung around an axis parallel to the cylinder axis of the inner cylinder to the liquid chamber side. The projecting portion is forcibly moved in the liquid chamber, and the liquid is forcibly flown in the liquid chamber, so that the forced flow of the liquid can further accelerate the damping action of the input vibration.

Further, in this case, even with respect to a relatively large vibration such as a large impact force, the both flap portions pushed down by the stopper portion come into contact with the inner peripheral surface of the outer cylindrical body, so that the impact force is dispersed. In this state, further displacement regulation can be reliably performed.

[Brief description of drawings]

FIG. 1 is a partially cutaway front view showing an embodiment of the present invention.

FIG. 2 is an exploded perspective view of a supporting portion on one side of a radiator.

FIG. 3 is a transverse cross-sectional view of the mounting means of the first embodiment in an unloaded state.

FIG. 4 is a cross-sectional view of the mounting means of FIG. 3 in a mounted state.

5 is a cross-sectional view taken along the line AA of FIG.

6 is a cross-sectional view taken along the line BB of FIG.

7 is a cross-sectional view taken along the line CC of FIG.

FIG. 8 is a diagram showing a vibration system model in which a radiator-side sub-vibration system is added to a vehicle-body-side main vibration system.

FIG. 9 is a diagram showing a resonance curve when the damping coefficient ratio is changed in the relationship between the η value obtained by dividing the vibration frequency by the natural frequency of the radiator and the response magnification.

FIG. 10 is a transverse sectional view of the mounting means of the second embodiment in an unloaded state.

11 is a cross-sectional view of the mounting means of FIG. 10 in a mounted state.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Support substrate of radiator 2 (vehicle body) 3, 3a Mounting means 4 Convex shaft body (1st support part) 5 Support cylinder part (2nd support part) 6 Inner cylinder body 7 Outer cylinder body 8, 18 Elastic body 8a, 18a Main elastic body part 8b, 18b First partition wall part 8c, 18c Second partition part 9 First through space 10, 20a, 20b Second through space 11 First liquid chamber 12 Second liquid chamber 14, 19 Stopper part 16 , 21 Flap parts 16a, 21a Cavity side convex parts 16b, 21b Liquid chamber side convex part L Liquid B Vehicle body X Cylinder axis

Claims (2)

[Claims] 1. A liquid-sealed radiator support device in which both sides of a radiator are supported by a vehicle body through mounting means, wherein the radiator includes a first support portion protruding outward from both side end positions. The vehicle body includes a second support portion facing the first support portion, and the mounting means includes an inner cylindrical body connected to one of the first support portion and the second support portion, and An outer tubular body externally inserted into the tubular body and coupled to the other of the first support portion and the second support portion, an elastic body coupling the outer tubular body and the inner tubular body, and inside the elastic body. A plurality of liquid chambers that are defined, a liquid that is enclosed in the liquid chambers, and a throttle passage that connects the plurality of liquid chambers to each other are provided, and the plurality of liquid chambers include the elastic body from the vehicle body side. From the one liquid chamber to the other liquid chamber due to the input vibration acting on the throttle passage A liquid-sealed radiator supporting device, wherein the liquid-sealed radiator supporting device is arranged so as to cause a liquid to flow therethrough. 2. The first and second mounting means penetrates in parallel to the cylinder axis by elastic bodies sandwiching the inner cylinder and located on both sides in a vibration input direction which is a direction orthogonal to the cylinder axis of the inner cylinder. Between the through space, the stopper portion projecting from the inner cylindrical body toward the second through space toward the one side in the vibration input direction, and between the both ends of the elastic body in the vibration input direction and the outer cylindrical body. A first elastic chamber formed in the first and second liquid chambers, and the elastic body is divided into the first and second through spaces to elastically support the inner cylindrical body; A first partition wall partitioning the first through space and the first liquid chamber;
A second partition wall portion that partitions the through space and the second liquid chamber is provided, while the second partition wall portion is provided with the second partition wall from a position on both sides in a direction orthogonal to the cylinder axis and orthogonal to the vibration input direction. 2 A pair of flaps are formed so as to project to the through space side and the second liquid chamber side respectively, and the inner cylinder body is a predetermined amount with respect to the outer cylinder body in the unloaded state before being mounted on the radiator. While supported by the main elastic body portion in an eccentric position, the radiator is supported in a concentric position with respect to the outer cylinder body in the mounted state where the weight of the radiator acts, and in the mounted state, the tip of the stopper portion is relatively The second partition wall facing is arranged so as to be capable of transmitting vibration.
The liquid ring radiator supporting device described.