JP3491777B2 - Fluid power unit mounting device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double orifice type fluid power unit mounting device having two fluid dynamic dampers formed therein.

[0002]

2. Description of the Related Art Conventionally, a double orifice type fluid power unit mounting device is disclosed in, for example, Japanese Patent Laid-Open No.
The one described in Japanese Patent Publication No. 8-72741 is known.

According to the above-mentioned conventional source, a main liquid chamber having a main body rubber on the chamber wall and a sub liquid chamber having a diaphragm on the chamber wall are defined in the main rubber, and the main liquid chamber and the sub liquid chamber are different. A device is described which communicates with two types of orifices having a cross-sectional area and a length.

[0004]

However, it is disclosed that the above-mentioned conventional fluid power unit mounting device can obtain a damping characteristic in which the respective damping characteristics are combined by two kinds of orifices (hereinafter referred to as double orifices). However, when the input vibration amplitude, that is, the deflection becomes large, the fluid resonance due to the double orifice does not occur well, the damping characteristics deteriorate, and the expected damping effect for the input deflection with a large deflection is expected. There is a problem that can not be issued.

That is, in the case of a single orifice, as shown in the dynamic spring constant characteristic of FIG. 5, when the resonance frequency of the fluid dynamic damper is set to f1, the resonance frequency f
The characteristic shows that the dynamic spring constant becomes the lowest at a frequency f2 lower than 1. This is because at the frequency f2, the enclosed fluid moves back and forth between the main liquid chamber and the sub liquid chamber in conformity with the direction of the flow of the enclosed fluid and the direction of the force of the input vibration, and the main body is caused by the volume change of both liquid chambers. This is because the amount of rubber deformation increases.

However, the characteristic that the dynamic spring constant has a peak at the lowest point at the frequency f2 is a prerequisite that fluid resonance occurs well. Therefore, in the case of the double orifice, the amount of deflection is large, and the fluid due to the double orifice is large. If the resonance does not occur well, the dynamic spring constant becomes high, and a sufficient damping effect cannot be expected.

For example, when the resonance frequencies of the two fluid dynamic dampers are tuned so that the lowest point peaks of the dynamic spring constant come at 25 Hz and 50 Hz, as shown in the dynamic spring constant characteristic by the solid line in FIG. Amount is ± 5
When the vehicle is stopped or running within mm, two large bottom points, point A and point B, appear. Point A effectively acts on idle vibration, and point B is effective on muffled noise during torque converter lockup. Act on. However, at the beginning of running when the amount of deflection exceeds 10 mm, 1 from the solid line in FIG.
The dynamic spring constant characteristic indicated by the dashed line also rises as a whole, and the hatched area is the margin of deterioration of the dynamic spring constant. Therefore,
The peak of the lowest point of the dynamic spring constant at 50 Hz rises from point B to point C ', and the muffled noise at the beginning of running cannot be reduced sufficiently.

The present invention has been made in view of the above problems. A first object of the present invention is to reduce the number of parts in a double orifice type fluid power unit mount device having two fluid dynamic dampers formed therein.
Reliable restraint and restraint sound generation without increasing
While preventing it, it is necessary to achieve both the damping of a plurality of input vibrations when the deflection amount is small and the effective damping of a specific input vibration when the deflection amount is large.

[0009]

A second object is to utilize the action of reducing the dynamic spring constant by the fluid dynamic damper to reduce the amount of deflection and reduce the idle vibration when the vehicle is stopped and the muffled sound vibration during running, and increase the amount of deflection. It is to achieve the damping of the muffled sound vibration at the beginning of running.

[0011]

In order to achieve the first object, in the fluid power unit mounting apparatus of the first invention, as shown in the claim correspondence diagram of FIG. 1, the static load of the power unit a is supported on the vehicle body b. Main body rubber c and at least one main liquid chamber d having the main body rubber c on the chamber wall
And the main liquid chamber d, and the first sub-liquid chamber g and the second sub-liquid chamber h which are partitioned from the main liquid chamber d and have the first diaphragm e and the second diaphragm f respectively on the chamber wall, the main liquid chamber d and the The first auxiliary liquid chamber g and the main liquid chamber d are provided with a first orifice i and a second orifice j which respectively communicate with the second auxiliary liquid chamber h, and inside the first orifice i and the second orifice j. A fluid mass is used as the fluid, and each of the liquid chambers d due to the flow of the enclosed fluid,
In a fluid power unit mounting device that includes a first fluid dynamic damper and a second fluid dynamic damper having different resonance frequencies, the elasticity associated with the expansion and contraction of g and h is a plurality of vibrations input to the fluid power unit mounting device. of utilizing the amplitude difference, the first when a large input of vibration amplitude, the second diaphragm e, the diaphragm constraining means k for the constrained state that does not allow one elastic deformation of f is provided, said diaphragm restraining means, said body La
When a restraining contact surface is formed on the diaphragm restraining portion of the bar c
Both are constrained to one of the first and second diaphragms e and f
Gap between the two constraining contact surfaces that form the contact surface and face each other
Set the dimension to the dimension of the amplitude when inputting small amplitude vibration.
It is characterized in that it is configured by .

[0012]

In order to achieve the above-mentioned second object , the fluid power unit mounting device according to the second invention is the fluid power unit mounting device according to claim 1 , wherein the first
The fluid dynamic damper is a damper whose resonance frequency is tuned so as to reduce the dynamic spring constant in the vibration frequency range that causes muffled sound, and the second fluid dynamic damper reduces the dynamic spring constant in the idle vibration range. The resonance frequency is tuned so that the diaphragm restraining means k utilizes the difference in amplitude between the idle time and the beginning of running, and the second diaphragm of the second fluid dynamic damper is used when starting running with a large amplitude. It is a means for restraining f.

[0014]

The operation of the first invention will be described.

When the vibration input to the fluid power unit mounting device is a vibration having a small amplitude, the diaphragm is not restricted by the diaphragm restricting means k. Therefore, the first diaphragm e and the second diaphragm f
In the first sub-liquid chamber g and the second sub-liquid chamber h, each of which has its respective inner wall, the volume change due to the inflow / outflow of the enclosed fluid is allowed, and the first orifice i and the second orifice communicating with the main liquid chamber d By the fluid flow through j, the fluid in the first orifice i and the second orifice j is used as a fluid mass, and the elasticity associated with the expansion / contraction of each liquid chamber d, g, h due to the flow of the enclosed fluid is used as a fluid spring, and the resonance frequency is set. The first fluid dynamic damper and the second fluid dynamic damper differing from each other are configured, whereby a plurality of vibrations having different frequencies can be reduced by utilizing the dynamic spring constant reduction or the fluid dynamic damper action. When the amplitude of the input vibration is small and the amount of flexure of the main body rubber c is small, fluid resonance occurs well and the dynamic spring constant is lowered or the fluid dynamic damper action is effectively achieved in two different frequency ranges.

When the vibration input to the fluid power unit mounting device is a vibration having a large amplitude, one of the first and second diaphragms e and f is elastically deformed by the diaphragm restraining means k utilizing the magnitude of the amplitude. It is in a restrained state that does not allow it.

Therefore, on the diaphragm e side or the diaphragm f side that is constrained, the volume change of the sub-liquid chamber is suppressed, so that the fluid flow through the orifice is also eliminated,
This is a single-orifice mounting device in which only the non-restrained orifice is utilized.

Therefore, when the amplitude of the input vibration is large and the amount of deflection of the main body rubber c is large, the fluid resonance does not occur well in the case of the double orifice, whereas the single orifice makes the orifice on the non-restraining side. In this case, the fluid resonance occurs well, and the reduction of the dynamic spring constant or the fluid dynamic damper action in one frequency range is effectively achieved.

[0019]

When restraining one of the first and second diaphragms e and f, when the amount of deflection of the main body rubber c is large, the restraining contact surface of the diaphragm contact restraining portion that bends integrally with the deflection of the main body rubber c has the first and second restraints . Second diaphragm e,
The diaphragm comes into contact with one of the constraining contact surfaces of f and is in a constrained state in which elastic deformation is not allowed.

In this way, the diaphragm restraining means k forms a restraining contact surface on the diaphragm contact restraining portion of the main body rubber c.
And one of the first and second diaphragms e and f
Between the restraining contact surfaces that form the restraining contact surface and face each other
By means of defining the gap size, addition of parts is not required, and reliable restraint accompanied by elastic body deformation and generation of restraint noise due to elastic body contact are achieved.

The operation of the second invention will be described.

When the vibration input to the fluid power unit mounting device is a vibration having a small amplitude when the vehicle is stopped or running, the diaphragm is not restricted by the diaphragm restricting means k. Therefore, the first fluid dynamic damper whose resonance frequency is tuned so as to reduce the dynamic spring constant in the vibration frequency range that causes muffled noise and the resonance frequency is tuned so as to reduce the dynamic spring constant in the idle vibration range. The second fluid dynamic damper described above acts together, and lockup muffled noise and idle vibration of the running torque converter are effectively damped by reducing the dynamic spring constant.

Also, when the vibration input to the fluid power unit mounting device has a large amplitude and starts to run,
The diaphragm restraining means k restrains the second diaphragm f of the second fluid dynamic damper.

Therefore, a single-orifice mounting device in which only the first fluid dynamic damper is utilized is provided, fluid resonance occurs well in the first fluid dynamic damper, and the muffled noise at the beginning of running is effectively damped by the reduction of the dynamic spring constant.

[0026]

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

First, the structure will be described.

FIG. 2 is a sectional view showing the fluid power unit mounting apparatus of the embodiment of the present invention, and FIG. 3 is a vertical sectional view taken along the line I--I of FIG.

2 and 3, 1 is an inner cylinder, 2 is an outer cylinder, 3 is a main rubber, 4 is a main liquid chamber, 5 is a first sub liquid chamber, and 6
Is a second auxiliary liquid chamber, 7 is a first diaphragm, 8 is a second diaphragm, 9 is a first orifice, 10 is a second orifice,
Reference numeral 11 is a diaphragm contact restraint portion, and 12 is a liquid chamber separate plate.

One of the inner cylinder 1 and the outer cylinder 2 is attached to a power unit (not shown) via a bracket, and the other is attached to a vehicle body (not shown) via a bracket.

The body rubber 3 is composed of the inner cylinder 1 and the outer cylinder 2.
And to support the static load of the power unit on the vehicle body.

The main liquid chamber 4 is formed above the inner cylinder 1, and the main body rubber 3 and the liquid chamber separate plate 12 are formed.
Is a liquid chamber defined by and as chamber walls.

The first sub liquid chamber 5 is a liquid chamber which is formed above the main liquid chamber 4 via a liquid chamber separate plate 12 and has a first diaphragm 7 on the chamber wall.

The second auxiliary liquid chamber 6 is a liquid chamber which is formed below the inner cylinder 1 and has a second diaphragm 8 on its chamber wall.

The first orifice 9 is a communication passage that connects the main liquid chamber 4 and the first auxiliary liquid chamber 5, and the first orifice 9 extends along the left inner surface of the outer cylinder 2 in FIG. It is formed by a passage.

The second orifice 10 is provided in the main liquid chamber 4
The second orifice 10 is formed by a passage extending along the right inner surface of the outer cylinder 2 in FIG.

The diaphragm contact restraint portion 11 is formed by the lower portion of the inner cylinder of the main body rubber 3, and utilizes the difference in amplitude between the idle time and the start of running, and the second diaphragm 8 at the start of running with a large amplitude. Are bound by surface contact. It should be noted that restraining contact surfaces 11a and 8a are formed at the facing portions of the diaphragm contact restraining portion 11 and the second diaphragm 8, respectively.

The first fluid dynamic damper composed of the main liquid chamber 4, the first auxiliary liquid chamber 5 and the first orifice 9 is
The resonance frequency is tuned by setting the orifice cross-sectional area, the orifice length, etc. so that the dynamic spring constant reduction peak appears at about 50 Hz, which is the vibration frequency range that causes muffled noise.

The second fluid dynamic damper constituted by the main liquid chamber 4, the second auxiliary liquid chamber 6 and the second orifice 10 has a dynamic spring constant reduction peak at about 25 Hz which is an idle vibration region. The resonance frequency is tuned by setting the orifice cross-sectional area and the orifice length.

Next, the operation will be described.

[When Small Amplitude Vibration is Input] When the amplitude of the vibration input to the fluid power unit mount device is a small vibration of about ± 5 mm, such as when the vehicle is idling or running, the diaphragm contact restraint portion 11 and the second portion. Diaphragm 8
Even if the and are slightly contacted with each other, the elastic deformation that allows the second diaphragm 8 to change the volume of the second auxiliary liquid chamber 6 is ensured, and the second diaphragm 8 is not constrained.

Therefore, in the first sub-liquid chamber 5 and the second sub-liquid chamber 6 each having the first diaphragm 7 and the second diaphragm 8 on the chamber wall, the volume change due to the inflow / outflow of the enclosed fluid is allowed, By the fluid flow through the first orifice 9 and the second orifice 10 communicating with the liquid chamber 4, the fluids in the first orifice 9 and the second orifice 10 are used as fluid masses, and the liquid chambers 4 and 5 are caused by the flow of the enclosed fluid. , 6 is used as a fluid spring, and the first fluid dynamic damper and the second fluid dynamic damper having different resonance frequencies work together to form a double orifice state.

When the amplitude of the input vibration is small and the amount of deflection of the main body rubber 3 is small, fluid resonance occurs well, and as shown by the solid line characteristics in FIG. 4, the peaks of the dynamic spring constant decrease around 25 Hz and around 50 Hz. There are two characteristics that appear in the vicinity.

Therefore, at idle, the engine speed is 2
The vibration at the frequency of about 25 Hz due to the next component is input, but this vibration is effectively damped by the reduction peak point A of the dynamic spring constant near about 25 Hz, and the idle vibration is suppressed.

When the torque converter is locked up while the vehicle is running, vibration at a frequency of about 50 Hz, which causes a lockup muffled noise, is input. This vibration reduces the dynamic spring constant in the vicinity of about 50 Hz. The peak point B effectively damps the lock-up muffled noise during traveling.

[When Large-Amplitude Vibration is Input] When the engine torque suddenly increases and the power unit starts to sway, when the amplitude of the vibration input to the fluid power unit mounting device is a large vibration of about ± 10 mm, the diaphragm is The constraint contact surfaces 11a and 8a of the contact constraint portion 11 and the second diaphragm 8 are always in close contact with each other, and the second diaphragm 8 is in a constraint state that does not allow elastic deformation.

Therefore, on the side of the constrained second diaphragm 8, the volume change of the second sub-liquid chamber 6 is suppressed, so that the fluid flow through the second orifice 10 is also stopped, and the first orifice on the non-constrained side. A single orifice mount device in which only 9 is utilized. Therefore, when the amplitude of the input vibration is large and the amount of deflection of the main body rubber 3 is large,
In the case of the double orifice, the fluid resonance does not occur well, whereas by using the single orifice, the fluid resonance occurs well in the first orifice 9 on the unconstrained side,
As shown by the alternate long and short dash line characteristic in FIG. 4, there is only one large reduction peak of the dynamic spring constant at around 50 Hz.

Therefore, at the beginning of running, vibration at a frequency of about 50 Hz, which causes a muffled noise at the beginning of running, is input, but this vibration is effectively damped by the reduced peak point C of the dynamic spring constant near about 50 Hz. Then, the muffled noise starts to run.

Next, the effect will be described.

(1) In a double orifice type fluid power unit mounting device having two fluid dynamic dampers formed therein, the amplitude difference between a plurality of vibrations input to the fluid power unit mounting device is utilized to input a large amplitude vibration. Diaphragm contact restraint portion 11 for keeping the second diaphragm 8 in a restrained state in which elastic deformation is not allowed
The double orifice characteristic of multiple input vibrations when the amount of deflection is small and the effective damping by the single orifice characteristic of specific input vibration when the amount of deflection is large can be achieved. it can.

(2) Since the diaphragm restraining means is the diaphragm contact restraining portion 11 of the main body rubber 3, it is possible to secure restraint by tight contact with elastic deformation and elastic body contact without increasing the number of parts. It is possible to prevent the restraint sound from being generated.

(3) The resonance frequency of the first fluid dynamic damper is tuned so that the reduction peak of the dynamic spring constant appears at about 50 Hz which is the vibration frequency range that causes muffled noise, and the resonance of the second fluid dynamic damper is tuned. The frequency was tuned so that the peak of the reduction of the dynamic spring constant appeared in the idle vibration range of about 25 Hz, and the diaphragm contact restraint part 11 was started by using the difference in amplitude between when idling and when starting running Since the second diaphragm 8 of the second fluid dynamic damper is constrained at the time of, the action of reducing the dynamic spring constant by the fluid dynamic damper is utilized, and the amount of deflection is small. It is possible to achieve damping and damping of muffled sound vibration at the beginning of running when the amount of deflection is large.

Although the embodiments have been described above with reference to the drawings, the specific structure 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.

For example, in the embodiment, the fluid power unit mounting device having the cylindrical bush structure is shown, but the present invention can be applied to a mounting device having a structure other than the embodiment, such as a power unit mounting device having a structure in which an elastic body is adhered between plates. .

In the embodiment, an example in which the vibration causing the idle vibration, the lock-up muffled sound and the running start muffled noise is attenuated by the action of reducing the dynamic spring constant is shown. Due to the action of reducing the dynamic spring constant,
Alternatively, the damping may be performed by a fluid dynamic damper action (a vibration damping action against vibration in the resonance frequency range), or by a combined use of a dynamic spring constant reducing action and a fluid dynamic damper action.

[0056]

According to the first invention of claim 1,
In a double orifice type fluid power unit mounting device having two fluid dynamic dampers formed therein, the first and second diaphragms are used when a large amplitude vibration is input by utilizing the amplitude difference of a plurality of vibrations input to the fluid power unit mounting device. A diaphragm restraining means for restraining elastic deformation on one side of the die is provided .
The yaf-ram restraint means is the diaphragm restraint of the main body rubber.
A restraining contact surface is formed on the first and second diaphragms.
A constraint contact surface is formed on one of the
Set the gap between the contact surfaces to the level of the amplitude when inputting small amplitude vibration.
The number of parts is increased because it is configured by setting the dimensions.
Without restraint, the restraint and the restraint noise are prevented.
It is possible to achieve both the damping of a plurality of input vibrations when the flexure amount is small and the effective damping of the specific input vibration when the flexure amount is large while achieving the stoppage .

[0057]

In the second invention according to claim 2 , the contract
In the fluid power unit mounting device according to claim 1, the first fluid dynamic damper is a damper whose resonance frequency is tuned so as to reduce a dynamic spring constant in a vibration frequency range that causes muffled sound, and a second fluid dynamic damper. Is a damper whose resonance frequency is tuned so as to reduce the dynamic spring constant in the idle vibration range, and the diaphragm restraint means uses the difference between the amplitudes at idle and when starting running, and Since the second diaphragm of the two-fluid dynamic damper is restrained, the action of reducing the dynamic spring constant by the fluid dynamic damper is used to reduce the amount of deflection and to reduce idle vibration during stoppage and muffled vibration during running, and flexure. A large amount of muffled sound at the beginning of running and vibration damping can be achieved. The effect is obtained that.

[Brief description of drawings]

FIG. 1 is a diagram corresponding to claims showing a fluid power unit mounting apparatus of the present invention.

FIG. 2 is a cross-sectional view showing a fluid power unit mounting device of an embodiment.

FIG. 3 is a vertical cross-sectional view taken along the line I-I of FIG. 2 showing the apparatus of the embodiment.

FIG. 4 is a frequency characteristic diagram of a dynamic spring constant in the apparatus of the embodiment.

FIG. 5 is a dynamic spring constant frequency characteristic diagram in a single orifice fluid power unit mounting device.

FIG. 6 is a frequency characteristic diagram of a dynamic spring constant in a conventional double orifice fluid power unit mounting device.

[Explanation of symbols]

a Power unit b car body c Body rubber d Main liquid chamber e First diaphragm f Second diaphragm g First auxiliary liquid chamber h Second auxiliary liquid chamber i First Orifice j Second orifice k Diaphragm restraint means

Continuation of front page (56) Reference JP-A-4-321834 (JP, A) JP-A-6-129472 (JP, A) JP-A-7-233847 (JP, A) JP-A-7-317832 (JP , A) JP-A-58-72741 (JP, A) Actual development 4-77041 (JP, U) Actual development 4-127442 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB) Name) F16F 13/08

Claims (2)

(57) [Claims] 1. A main body rubber for supporting a static load of a power unit on a vehicle body, at least one main liquid chamber having the main body rubber on a chamber wall, and the main liquid chamber are partitioned into a first diaphragm and a second diaphragm. A second auxiliary liquid chamber and a second liquid chamber, each of which has a chamber wall
Sub liquid chamber, the main liquid chamber, the first sub liquid chamber, the main liquid chamber, and the second
A first orifice and a second orifice which respectively communicate with the sub-liquid chamber, wherein the fluid in the first orifice and the second orifice is used as a fluid mass, and the elasticity caused by the expansion and contraction of each liquid chamber due to the flow of the enclosed fluid is fluidized. A fluid power unit mounting device comprising a first fluid dynamic damper and a second fluid dynamic damper having different resonance frequencies, which are springs, and uses a difference in amplitude of a plurality of vibrations input to the fluid power unit mounting device to generate a large amplitude. A diaphragm restraint means is provided for restraining one of the first and second diaphragms from elastically deforming at the time of vibration input , and the diaphragm restraint means is a diaphragm of the main body rubber.
The restraint contact surface is formed on the ram restraint portion, and
A constraining contact surface is formed on one of the second diaphragms,
Input the small-amplitude vibration input to the gap between the two facing contact surfaces.
A fluid power unit mounting device, characterized in that it is configured by setting the dimensions to the amplitude of time . 2. The fluid power unit mounting device according to claim 1, wherein the first fluid dynamic damper causes a muffled sound.
To reduce the dynamic spring constant in the vibration frequency range
It is a damper in which the resonance frequency is tuned,
The fluid dynamic damper has a dynamic spring constant in the idle vibration range.
Its resonant frequency is tuned to reduce the number
The damper, and the diaphragm restraint means is an idle
By using the difference in amplitude between the time of running and the start of running, running with large amplitude
The second diamond of the second fluid dynamic damper when starting
A fluid power unit mounting device, which is a means for restraining a flam .