JPH05169969A - Radiator supporting device - Google Patents

Abstract

PURPOSE:To reduce vibration of a vehicle body through dynamic damper action by tuning the natural frequency of a sub-vibration system in which an elastic member for supporting a radiator on a vehicle body is restricted only in one direction of the vibration of the radiator and the radiator acts as a mass, in a specified vehicle body vibration frequency range. CONSTITUTION:One end of plate springs 3, 4 are fixed to the upper and lower headers 1b, 1c of a radiator 1 by means of bolts 7, 8 through rubber sheets 5, 6, and the other ends are fixed to brackets 11, 12 on a vehicle body 2 side by means of bolts 9, 10, and the degree of freedom of the vibration is restricted only in the vertical direction. Further, the natural frequency in the vertical direction of a sub-vibration system of which radiator 1 acts as a mass and plate springs 3, 4 act as springs in is tuned in the idle vibration range of the vehicle body 2. Consequently, when the specified vibration of the vehicle body is generated, the vehicle body vibration can be effectively reduced by dynamic damper action using the radiator 1.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a radiator supporting device for supporting a radiator provided for cooling an engine on a vehicle body.

[0002]

2. Description of the Related Art As a conventional radiator supporting device, for example, a device shown in FIG. 11 is generally known.

In FIG. 11, 01 is a radiator,
02 is a vehicle body. The radiator 01 is configured to have a radiator core 01a and headers 01b and 01c, and the headers 01b and 01c are provided with radiator-side brackets 03 and 04. Brackets 05 and 06 on the vehicle body side are fixed to the vehicle body 02 with bolts 07 and 08.

The radiator 01 is supported on the vehicle body 02 by a soft mount in which rubbers 09, 010 are interposed between the brackets 03, 05 and 04, 06.

[0005]

However, in the above-mentioned conventional radiator supporting device, the soft mount is adopted for the purpose of suppressing the vibration input to the radiator to a low level, and the mass of the dynamic damper (dynamic vibration absorber) is adopted. As a result, it had no technical purpose to reduce vehicle vibration such as idle vibration by using a radiator.

In addition, in the case where the natural vibration frequency of the sub-vibration system having the radiator as the mass and the supporting elastic member as the spring coincides with the specific vibration frequency of the vehicle body such as idle vibration, the natural vibration frequency of the radiator is Even if there is a vibration input, the radiator's body support is a soft mount that does not constrain the degree of freedom of vibration, so the radiator shakes in all directions such as up, down, left and right, front and back, and rotation, especially due to the shake in the rotation direction. Since the vibration energy is dispersed, the effect of reducing the vehicle body vibration by the dynamic damper can hardly be expected.

The vibration reduction effect obtained by the dynamic damper is proportional to the mass and stroke of the dynamic damper.

The present invention has been made in view of the above problems, and in a radiator supporting device for supporting a radiator provided for cooling an engine on a vehicle body,
A first object is to effectively reduce vehicle body vibration by a dynamic damper action using a radiator when a specific vehicle body vibration occurs.

Further, in a radiator supporting device for supporting a radiator provided for cooling an engine on a vehicle body, when the vehicle body vibration occurs, the vehicle body vibration can be effectively reduced in a wide vibration frequency range by an active dynamic damper action using the radiator. Is the second subject.

[0010]

In order to solve the above-mentioned first problem, in the radiator supporting device of the present invention, the vibration freedom of the radiator is restricted only in one direction, and the characteristic of the sub-vibration system whose mass is the radiator is inherent. The radiator is supported on the vehicle body by a vibration degree-of-freedom constraining elastic member in which the vibration frequency is tuned to a specific vehicle body vibration frequency range.

That is, as shown in the claim correspondence diagram of FIG. 1, in a radiator supporting device in which a radiator a is supported with respect to a vehicle body b through an elastic member, the elastic member is provided with a degree of freedom of vibration of the radiator a. In addition to having a function of restricting only in one direction, the natural vibration frequency of the sub-vibration system in which the radiator a is a mass and the elastic member is a spring has a specific vibration frequency that is equivalent to the vibration freedom direction of the radiator a. The elastic member c is a vibration degree of freedom restraint member tuned to the vehicle body vibration frequency range.

In order to solve the above-mentioned second problem, in the radiator supporting apparatus of the present invention, the radiator is supported on the vehicle body by the vibration degree-of-freedom constraining elastic member according to the first aspect, and the radiator from the outside is detected based on the detection of the vehicle body vibration. The control force is used to actively swing the radiator.

That is, as shown in the claim correspondence diagram of FIG. 1, the vibration freedom degree constraining elastic member c according to claim 1, which supports the radiator a with respect to the vehicle body b, and the radiator a in the vibration freedom degree direction. A vibration actuator d for applying a vibration force, a radiator vibration state detection means e for detecting the vibration state of the radiator a, a vehicle body vibration state detection means f for detecting the vibration state of the vehicle body b, and the vehicle body vibration state detection means. When the vehicle body vibration is detected by f, the control force for obtaining the radiator reaction force vibration in the opposite phase to the vehicle body vibration is determined while monitoring the radiator vibration state, and the control command for obtaining this control force is given to the vibration actuator. and an active controller g for outputting to d.

[0014]

The operation of the present invention will be described.

The radiator a is attached to a vibration degree of freedom restraint elastic member c.
Therefore, when the radiator a is supported by the vehicle body b, the natural vibration frequency of the sub-vibration system having the radiator a as the mass and the vibration freedom degree restraining elastic member c as the spring is equivalent to the vibration degree direction of the radiator a. Tuning to a specific body vibration frequency range that you have.

When the vehicle body b of the vehicle equipped with the radiator support device vibrates at a specific frequency that matches the natural vibration frequency of the sub-vibration system, the radiator a resonates, and the vehicle body b, which is the main vibration system, approaches the stationary state. The dynamic damper action is demonstrated.

Moreover, since the vibration freedom degree restraining elastic member c has a function of restraining the vibration freedom degree of the radiator a in only one direction, rotational vibration and the like are coupled in the resonance operation of the radiator a. Instead, it vibrates by a stroke according to the vibration input direction from the vehicle body b, and the tuned specific vehicle body vibration is effectively reduced.

The operation of the invention according to claim 2 will be described.

As described in claim 1, the natural vibration frequency of the sub-vibration system having the radiator a as a mass and the vibration freedom restraint elastic member c as a spring is equivalent to the vibration direction of the radiator a. Even if the vehicle body is tuned to a specific vehicle body vibration frequency range, for example, when both frequencies are deviated due to engine speed fluctuations, variations in the vehicle body bending characteristic value, etc., a sufficient dynamic damper action cannot be exhibited.

On the other hand, according to the second aspect of the present invention, when the vehicle body vibration is detected by the vehicle body vibration state detecting means f,
In the active controller g, the control force for obtaining the radiator reaction force vibration in the opposite phase to the vehicle body vibration is determined while monitoring the radiator vibration state, and the control command for obtaining this control force is output to the vibration actuator d.

As a result, the radiator a can be actively swung by the control force from the vibration actuator d even when the two frequencies are deviated due to fluctuations in the engine speed or variations in the vehicle body bending characteristic value. become,
These fluctuations are not affected. Moreover, the vehicle body vibration reduction is achieved by forcibly oscillating the radiator a like resonance at a wide frequency range where the vehicle body vibration is excited without being limited to a specific vehicle body vibration, as in the dynamic damper action. It

[0022]

【Example】

 (First Embodiment) First, the configuration will be described.

FIG. 2 is a first diagram corresponding to the first aspect of the invention.
The front view which shows the radiator support apparatus of an Example, FIG.
It is a side view which shows the radiator support apparatus of an Example.

The radiator supporting device of the first embodiment is shown in FIG.
As shown in FIG. 3, the upper and lower portions of the radiator 1 provided for cooling the engine are supported by the vehicle body 2 via plate-like leaf springs 3 and 4 (corresponding to elastic members for vibrating freedom restraint). There is.

The radiator 1 is a radiator core 1a.
And an upper header 1b and a lower header 1c.

As the leaf springs 3 and 4, a radiator 1 is used.
By using a flat plate spring that is long in the longitudinal (width) direction and supporting its long sides, the torsional rigidity (figure in the vertical direction of the radiator 1) against the bending rigidity of the leaf springs 3 and 4 (Fig. Two
The rigidity in the rotating direction of the radiator 1 when viewed from the perspective is sufficiently high,
The vibration degree of freedom of the radiator 1 is restricted only in the vertical direction.

On the radiator 1 side, the leaf springs 3 and 4 are attached to the rubber sheets 5 to the headers 1b and 1c.
It is fixed with bolts 7 and 8 via 6, and is fixed to the vehicle body side brackets 9 and 10 on the vehicle body 2 side with bolts 11 and 12.

Furthermore, the vertical natural vibration frequency of the sub-vibration system having the radiator 1 as a mass and the leaf springs 3 and 4 as springs is tuned to the idle vibration range (20 Hz to 30 Hz) of the vehicle body 2. Here, the idle vibration is the bending vibration of the vehicle body, but this bending vibration of the vehicle body is equivalent to the vertical direction on the radiator 1.

The radiator 1 is used as a mass and the leaf springs 3 and 4 are used.
The natural vibration frequency in the rotational direction of the sub-vibration system using the spring as a spring is 100 Hz or more due to the large difference in rigidity as described above, and the natural vibration frequencies of the two are sufficiently separated.

Next, the operation will be described.

For example, in the case of a four-cylinder vehicle, the explosive force in the cylinder becomes the exciting force at the secondary component frequency of the engine speed, and this frequency (about 20 Hz) in the idling state of the vehicle.
(.About.30 Hz) is usually close to the bending eigenvalue of the vehicle body, so that the bending vibration of the vehicle body is excited and becomes a problem as idle vibration.

On the other hand, in the apparatus of the first embodiment, when the radiator 1 is supported by the leaf springs 3 and 4 with respect to the vehicle body 2, a secondary vibration system in which the radiator 1 is a mass and the leaf springs 3 and 4 are springs is used. The vertical natural vibration frequency is tuned to the idle vibration range (20 Hz to 30 Hz) of the vehicle body 2.

When the bending vibration of the vehicle body is excited in the idling state of the vehicle equipped with the radiator supporting device of the first embodiment, the radiator 1 having a natural vibration frequency that matches the idle vibration region resonates, and the main vibration system. The bending vibration of the vehicle body 2 is suppressed, and a dynamic damper action of approaching stationary is exhibited.

Moreover, the radiator 1 is constituted by the leaf springs 3 and 4.
Since it has a function of restraining the vibration freedom degree of the vehicle only in the vertical direction, the rotational vibration is not coupled in the resonance operation of the radiator 1, and the vertical direction is increased by a large stroke in accordance with the vibration input direction from the vehicle body 1. It vibrates and idle vibration is effectively reduced.

As described above, the radiator supporting device of the first embodiment has the following effects.

(1) The vibration degrees of freedom of the radiator 1 are restricted only in the vertical direction, and the radiators are made by the leaf springs 3 and 4 in which the natural vibration frequency of the sub-vibration system whose mass is the radiator 1 is tuned to the idle vibration frequency range. Since 1 is supported by the vehicle body 2, the idle vibration can be effectively reduced by the dynamic damper action using the radiator 1 when the idle vibration occurs.

(2) Since the leaf springs 3 and 4 are used as the elastic members for restraining the degree of freedom of vibration, a long stroke can be easily secured, and a greater vibration reducing effect can be effectively obtained in a limited space. be able to.

That is, in the conventional rubber mount, it is necessary to make the rubber volume very large in order to lengthen the stroke within the range in which the rigidity value is determined, and there is a space limitation like a vehicle. On the other hand, it is not realistic.

In order to increase the torsional rigidity of the leaf spring, it is conceivable to use comb-shaped leaf springs 3'and 4'as shown in FIGS. 4 and 5, and as shown in FIG. It is also possible to use wavy leaf springs 3 "and 4".

(Second Embodiment) First, the structure will be described.

FIG. 7 shows a second embodiment of the invention according to claim 2.
The front view which shows the radiator part of the radiator support device of an Example, FIG. 8 is the side view which shows the radiator part of the radiator support device of a 2nd Example, FIG. 9 is the whole system view which shows the radiator support device of a 2nd Example, FIG. 10 is a block diagram of the control system of the radiator support device of the second embodiment.

The radiator supporting device of the second embodiment is shown in FIG.
As shown in FIG. 3, the leaf springs 3 and 4 (corresponding to elastic members for restraining vibration freedom) similar to those of the first embodiment for supporting the radiator 1 with respect to the vehicle body 2 and the vibration freedom are given to the radiator 1. A vibration actuator 20 for applying a vibration force in the vertical direction, a strain gauge 21 for detecting a radiator displacement X2 in the vertical direction of the radiator 1 (corresponding to a radiator vibration state detecting means), and a vehicle body in the vertical direction of the vehicle body 2. Acceleration d ²
A vehicle body acceleration sensor 22 (corresponding to a vehicle body vibration state detecting means) for detecting X1 and a radiator vibration state based on a radiator displacement X2 from a strain gauge 21 when a vehicle body bending vibration is detected by the vehicle body acceleration sensor 22 in an idling state. The control force U for obtaining the radiator reaction force vibration in the opposite phase to the vehicle body bending vibration is determined while monitoring the
And an active controller 23 which outputs a control command to obtain the vibration actuator 20 to the vibration actuator 20.

As shown in FIGS. 7 and 8, the vibration actuator 20 is composed of a cylindrical electromagnetic coil 20a provided on the vehicle body 2 side and a magnet assembly 20b provided on the radiator 1 side. The electromagnetic coil 20a is attached to the vehicle body 2 through the pedestal 20c and the bolt 20d.
It is fixed by. The magnet assembly 20
In b, since the magnetic circuit is configured by the cylindrical permanent magnet 20f, the permanent magnet 20f has a magnet core 20g.
Further, a magnet head 20g is adhered and is constituted by these permanent magnets 20f, a magnet core 20g and a magnet head 20h, and this magnet assembly 20b is fixed to the lower header 1c of the radiator 1 by bolts 24.

The strain gauge 21 is attached to the leaf spring 3, detects the radiator displacement X2, and inputs a detection signal to the active controller 23 via the amplifier 25.

The vehicle body acceleration sensor 22 is attached to the vehicle body 2, detects the vertical acceleration d ² X1 of the vehicle body 2, and inputs a detection signal to the active controller 23 via the amplifier 26 to detect it.

The active controller 23 includes integrators 23a and 23b, a differentiator 23c, and a control force calculator 23d.
Has vertical acceleration d ² X1 and radiator displacement.
The control force U is determined by feeding back each state quantity of X2,
The control current for generating the control force U is applied to the electromagnetic coil 20a.
Is being supplied to.

Next, the operation will be described.

Radiator 1 as described in the first embodiment
The vibration frequency of an idle vibration having a natural vibration frequency of a sub-vibration system having a mass of 1 and a leaf springs 3 and 4 as springs and an equivalent vibration direction (vehicle body bending direction) to the vertical direction, which is the vibration freedom direction of the radiator 1. Even if the frequency is tuned to a frequency range (20 Hz to 30 Hz), for example, when both frequencies are deviated due to variations in engine speed or variations in the body bending characteristic value, a sufficient dynamic damper action is not exhibited.

On the other hand, in the second embodiment, when the vehicle body vibration is detected by the vehicle body acceleration sensor 22, the active controller 23 monitors the radiator vibration state and the radiator reaction force vibration in the opposite phase to the vehicle body vibration. The control force U for obtaining the control force U is determined by the following arithmetic expression, and the control current for obtaining the control force U is output to the electromagnetic coil 20a.

U = K1 · dX1 + K2 · dX2 + K3 · X1 + K4 · X2 However, K1, K2, and K3 are fixed gains. As a result, there is a case where deviations occur in both frequencies due to fluctuations in engine speed or variations in the body bending characteristic value. Even if the radiator 1 can be actively swung by the control force U from the vibration actuator 20, the passive dynamic damper effect as in the first embodiment device can be obtained without being affected by these fluctuations. In comparison, it is possible to obtain vibration reduction that greatly exceeds this effect.

Moreover, the radiator 1 is forcibly oscillated at resonance as in the dynamic damper action in a wide frequency range in which the vehicle body vibration is excited without being limited to a specific vehicle vibration such as only the idle vibration. By doing so, vibration reduction of the vehicle body is achieved.

At this time, in order to accurately perform the reaction force control, the clearance between the electromagnetic coil 14 and the permanent magnet 11 must be constant and as small as possible. When the electromagnetic coil 14 and the permanent magnet 11 are attached to the conventional radiator support device, the permanent magnet 11 freely vibrates with respect to the electromagnetic coil 14 in a direction other than the vertical direction, so that the clearance cannot be kept constant. It was impossible to control the reaction force because the electromagnetic coil 14 and the permanent magnet 11 vibratingly interfered with each other.

However, in the radiator supporting device of this embodiment, since the vibrational freedom of the radiator is restricted only in the vertical direction, the clearance between the electromagnetic coil 14 and the permanent magnet 11 can be kept small and the reaction force can be controlled. It is done with high precision.

As a result, even if the idle speed of the engine fluctuates or the eigenvalue of the vehicle body varies, the vibration can be actively suppressed, and the frequency range with a reduction effect can be widened. It is possible to obtain vibration reduction that greatly exceeds the passive dynamic vibration absorption effect described above.

As described above, the radiator supporting device of the second embodiment has the following effects.

(1) The radiator 1 is supported on the vehicle body 2 by the leaf springs 3 and 4 which restrain the vibrational freedom of the radiator 1 only in the vertical direction, and the radiator is controlled by the external control force U based on the detection of the vehicle body vibration. Since the device 1 is actively shaken, the vehicle body vibration can be effectively reduced in a wide vibration frequency range by the active dynamic damper action using the radiator 1 when the vehicle body vibration occurs.

That is, even if the idle speed of the engine fluctuates or there is a variation in the bending characteristic value of the vehicle body, the vibration of the vehicle body can be reduced without being affected by the variation. Not only that, the vibration reduction effect can be obtained.

(2) Since the radiator 1 has its vibrational freedom restricted only in the vertical direction, the clearance between the electromagnetic coil 20a and the permanent magnet 20f is kept small and constant, and the reaction force between the radiator 1 and the vehicle body 2 is controlled. Can be performed accurately.

That is, in order to accurately control the reaction force, the clearance between the electromagnetic coil 20a and the permanent magnet 20f must be constant and as small as possible. When the electromagnetic coil 20a and the permanent magnet 20f are attached to the conventional radiator supporting device, the permanent magnet 20f becomes the electromagnetic coil 20.
Since it vibrates freely except in the vertical direction with respect to a,
Not only can the clearance be kept constant, but the electromagnetic coil 20a and the permanent magnet 20f vibrately interfere with each other,
It is impossible to control the reaction force.

Although the embodiments have been described above with reference to the drawings, the specific configuration is not limited to the embodiments, and modifications and additions within the scope of the present invention are included in the present invention. Be done.

In the embodiment, as the vibration freedom restriction elastic member, an example of a leaf spring that restricts the vibration freedom in the vertical direction is shown, but the vibration freedom is restricted in the vehicle front-rear direction, the vehicle left-right direction, and the vehicle rotation direction. Other elastic members for restraining the degree of vibration may be used.

Further, in the embodiment, the example of the idle vibration is shown as the vehicle vibration, but the invention can be applied to other vehicle vibration such as muffled sound vibration.

[0063]

As described above, according to the present invention as set forth in claim 1, in the radiator support device for supporting the radiator provided for cooling the engine on the vehicle body, the vibration freedom degree of the radiator is one direction. When the vibration of a specific vehicle body occurs, the radiator is supported on the vehicle body by a vibration freedom constraint elastic member that tunes the natural vibration frequency of the sub-vibration system whose mass is the radiator to a specific vehicle body vibration frequency range. The effect that the vehicle body vibration can be effectively reduced is obtained by the dynamic damper action using the radiator.

Further, in the present invention according to claim 2,
The radiator is supported on the vehicle body by the vibration degree-of-freedom constraining elastic member according to claim 1, and the radiator is actively shaken by a control force from the outside based on the detection of the vehicle body vibration. Therefore, the radiator is generated when the vehicle body vibration occurs. The effect that the vehicle body vibration can be effectively reduced in a wide vibration frequency range is obtained by the active dynamic damper action using the.

[Brief description of drawings]

FIG. 1 is a diagram corresponding to claims showing a radiator supporting device of the present invention.

FIG. 2 is a front view showing the radiator support device of the first embodiment.

FIG. 3 is a side view showing the radiator support device of the first embodiment.

FIG. 4 is a perspective view showing another example (comb shape) of the leaf springs of the first embodiment device.

5 is a view taken in the direction of arrow A in FIG.

FIG. 6 is a side view showing another example (corrugated) of the leaf spring of the first embodiment device.

FIG. 7 is a front view showing a radiator portion of a radiator supporting device of a second embodiment.

FIG. 8 is a side view showing a radiator portion of a radiator supporting device of a second embodiment.

FIG. 9 is an overall system diagram of a radiator support device of a second embodiment.

FIG. 10 is a block diagram of a control system of a radiator support device of a second embodiment.

FIG. 11 is a side view showing a conventional radiator support device.

[Explanation of symbols]

 a radiator b vehicle body c vibration freedom constraint elastic member d vibration actuator e radiator vibration state detection means f vehicle body vibration state detection means g active controller

Claims (2)

[Claims] 1. A radiator supporting device in which a radiator is supported on a vehicle body via an elastic member, wherein the elastic member has a function of restricting a vibration freedom degree of the radiator in only one direction, and a radiator is provided. The natural vibration frequency of the sub-vibration system with the mass as the spring and the elastic member as the spring,
A radiator support device, characterized in that it is a vibration freedom degree restraining elastic member tuned to a specific vehicle body vibration frequency range having a vibration direction equivalent to the vibration freedom direction of the radiator. 2. The vibration-restriction-restraining elastic member according to claim 1, which supports the radiator with respect to the vehicle body, a vibration actuator that applies a vibration force to the radiator in the vibration freedom direction, and a vibration state of the radiator. Radiator vibration state detection means for detecting the vehicle vibration state, vehicle body vibration state detection means for detecting the vehicle body vibration state, and when the vehicle body vibration state is detected by the vehicle body vibration state detection means, the vehicle body vibration is monitored while monitoring the radiator vibration state. Determine the control force that can obtain the anti-phase radiator reaction vibration,
A radiator support device, comprising: an active controller that outputs a control command for obtaining this control force to the vibration actuator.