JPS60192139A - Liquid-containing power unit mount device - Google Patents

Abstract

PURPOSE:To improve vibration transmission characteristic of a mount device by disposing an orifice in series to an elastically deformed intermediate chamber provided on a partition plate and mounting a valve on the partition plate, which is adapted to move for high frequency and is restrained to move for low frequency. CONSTITUTION:A partition plate 5 disposed on a mount device is provided with the first and second orifices 13, 14 having resonance point in low-frequency area, which are respectively disposed in series to the first valve mechanism 9 and the second valve mechanism 12, which are movable for high-frequency slight vibration and restrained to move for low-frequency large-amplitude vibration. Since the resonance frequency of the first valve mechanism is 60-170Hz, that of the second valve mechanism is 250-300Hz and that of the first orifice is 6-15Hz, vibration can be absorbed effectively.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a fluid-filled/dinner work unit mounting device.

(Prior Art) As a conventional fluid manpower unit mounting device, for example, there is a device as shown in FIG.
No. 740). That is, an internal space 5 in which fluid is sealed between a board 51 on the power unit side and a board 52 on the vehicle body side.
A mount Rano-53 having a length of 3 m is fixed, a diaphragm 54 and a partition plate 55 are attached to one side of the substrate 52,
A subchamber 56 is formed between the diaphragm 54 and the partition plate 55, and a fluid chamber 57 is formed between the partition plate 55 and the other substrate 51.
The fluid chamber 56 and the fluid chamber 57 are filled with a fluid, and the partition plate 55 is provided with an orifice 60 so that the fluid chamber 57 and the subsidiary chamber 56 communicate with each other through the orifice 60. be.

Such a mount device can obtain a high damping force by the orifice 60 in a predetermined low frequency range as shown in FIG.

The dynamic spring constant value of the mount device can be lowered in a lower frequency range. In addition, by forming a rubber mechanism whose peripheral edge is restrained from elastic movement to the substrate 52 by the mounting rubber 53, it is possible to reduce the dynamic spring constant value of the mounting device in a predetermined high frequency range. .

However, in such a conventional mounting device, since the Oriice 60 is formed on the plate-shaped partition plate 55, it is difficult to obtain a good dynamic spring constant value in a low frequency range, for example, from 6 to 40. The problem is that the range in which vibration can be achieved is relatively narrow, and good vibration transmissibility characteristics cannot be obtained.

(Object of the Invention) The present invention has been made to solve the problems of the conventional art, and includes forming an elastically deformable intermediate chamber in the partition plate, and connecting a plurality of orifices in series through the intermediate chamber. In addition, by equipping the partition plate with a no-no-ruzo mechanism that is movable against high-frequency minute vibrations and restrained from moving against low-frequency large-amplitude vibrations, the practical frequency range of the engine, such as The purpose of this invention is to provide a good dynamic spring constant value between θ and 400 Hz and to solve the above problems.

(Embodiments) The present invention will be described below with reference to illustrated embodiments.

FIG. 3 shows an embodiment of the present invention. A mount rubber having an internal space 3 between a board 1 on the power unit side and a board 2 on the vehicle body side? The partition plate 5 and the diaphragm 6 are sandwiched together with the diaphragm 6 placed on the outside between the substrate 1 and the bracket 7, and the rivets 8 Fix it with. Reference numeral 21 denotes an embedded ring that prevents the mount rubber 4 from expanding when it contracts.

The partition plate 5 includes an upper plate 19a, a lower plate 19b, and both plates 19.
It has an intermediate chamber 19 defined by a side plate 19c that connects the intermediate chambers 19a and 19b, and at least a part of the side plate 19c is formed of a relatively soft elastic body 19d made of rubber or elastomer to make the intermediate chamber 19 elastic. The structure should be deformable.

Furthermore, the partition plate 5 has a first knob mechanism 9 and a second knob mechanism 12 which are movable against high frequency micro vibrations and restrained from moving against low frequency large amplitude vibrations. The structure 9 includes a first orifice 13 and a second orifice 14 having a resonant frequency, and an annular portion 10 with a U-shaped cross section, which is provided on the upper plate 19m and whose two opposing sides form a pair of stoppers 10b, a stopper 10a, The movable plate 11 is loosely fitted between the stoppers 10b and movable between the stoppers 10a and 10b. The second valve mechanism 12 is provided on the lower plate 19b, and has two opposing sides that are provided with a pair of stoppers 15a and 1.
The annular portion 15 with a U-shaped cross section forming the 5b, and the stock 7#15
It is loosely fitted between 1L*15b, and both stoppers 15a, 155
It consists of a movable plate 16 that can be moved between. Then, the resonance frequency of the first valve mechanism 9 is set to 6, for example, which causes a muffled sound.
It is set to a high frequency around 0 to 170 parts, and the dynamic spring constant value as a mount device is lowered in the range of 60 to 170 parts.

Then, the high frequency range higher than that, for example 250 to 300
In this case, the first valve mechanism 9 exceeds the resonance point and does not work well, resulting in a deterioration region where the dynamic spring constant value as a mount device increases, transmitting high-frequency micro-vibrations due to engine combustion to the vehicle body. > - 1, 3 cod, - 1 reef building, set the number of small flood fields to a high frequency around 250 to 300 Hz, and set the dynamic spring constant value as a mount device in the range of 250 to 300 Hz. Lower the first knob mechanism 9
For example, 60 to 40 in the fusion of the second valve mechanism 12 and the second valve mechanism 12.
To satisfactorily set a dynamic spring constant value for a mount device in a high frequency range of 0 H2.

The first orifice 13 is provided on the upper plate 19a, and in order to suppress engine shake, a resonance frequency is given to, for example, 6 to 15H2, and a high damping force is obtained. Then,
In the low frequency range slightly higher than that, that is, the engine idle vibration range, for example 20 to 30) (at Z, the dynamic spring constant value as a mount device is high 9, and the engine idle vibration is transmitted to the car body. The resonant frequency of the second nitride orifice 14 is set to a higher low frequency, for example 40 H2, and the dynamic spring constant value of the mount device in the engine idle vibration range is reduced.

Note that the resonant frequency at which the damping capacity of the orifices 13 and 14 reaches its maximum value depends on the equivalent mass of the fluid in the orifices 13 and 14 and the diameter of the orifices 13 and 14, and the larger the mass, the higher the resonant frequency. The smaller the diameter, the lower this resonant frequency. Also, the diameter is large #
It has been found through various experiments conducted by the present inventor that the attenuation capacity increases.

Furthermore, the resonance frequency of the stoppers 10a, 12 becomes higher as the cross-sectional area becomes larger.
It has been found that the shorter the distance between 10b, 15a, and 15b, the higher the resonant frequency.

Next, the operation will be explained with reference to FIGS. 4 to 6.

Low frequency range that causes engine shake, e.g. 6 to 15
When a large-amplitude vibration of Hz is input to the substrate l, the mount rubber 4 expands and contracts significantly, causing a change in the volume of the fluid chamber 170. As a result, the movable plate 16 of the second valve mechanism 12 is locked to the stopper 15at or 15b and movement is restricted, and the fluid mass in the second niorifice 14 resonates at the resonance frequency f, generating a large damping force. to suppress this vibration (see Figure 4).

Low frequency range caused by engine idle vibration, for example 20
When a large amplitude vibration of ~30H2 is input from the board 1,
Each movable plate 11.16 of the first valve mechanism 9 and the second knob mechanism 12 is a stopper 10! L, 15ai or 10b
, 15b to restrict movement, and the first orifice 1
Since it is a slightly lower frequency than the resonance frequency f2 of 3,
The dynamic spring constant value of the mount device is reduced, and the transmission of this vibration to the vehicle body is suppressed (see Fig. 5).

In this way, it is possible to give the first orifice 13 and the second orifice 14 individual resonant frequencies f, , f, by means of the side plate 19 of the intermediate chamber 19 into which both orifices 13, 14 open.
This is because a part of the intermediate chamber 19c is made of a relatively soft elastic body 19d, so that the intermediate chamber 19 has a structure that can be elastically deformed, and this property also has some influence.

High frequency range that produces a loud sound, e.g. 60 to 170 H2
When a small-amplitude vibration of The fluid cannot flow through one orifice 13 and is confined in the fluid chamber 17 and intermediate chamber 19. In this case, the mount rubber 4 expands and contracts, and the second nodal mechanism $12 having the resonance frequency f3 mainly acts. That is, the movable plate 11 is the stopper 10a,
10b to maintain the dynamic spring constant value of the mount device substantially constant, thereby reducing the transmission of small amplitude vibrations to the vehicle body in the high frequency range of 60 to 170 Hz (see FIG. 6).

To explain in more detail, the first orifice 1 is
3 provides a high damping effect, so it is possible to set the static spring constant value lower than the static spring constant value of the mount rubber 4. In combination with the action of the second nitrogen orifice 14, it is possible to obtain a high damping effect in the low frequency range where engine idle vibration occurs. The dynamic spring constant value can be lowered, and in combination with the combined action of both valve mechanisms 9 and 12, the dynamic spring constant value as a mounting device can be used in high frequency ranges that cause muffled sounds, for example, 60 to 170. can be maintained approximately constant.

In the deterioration range where the dynamic spring constant value of the mounting device increases in a high frequency range that is slightly higher than the high frequency range that produces the small υ sound, for example, 250 to 300H2, the resonant frequency f,
The main action of the second knob mechanism 12 can reduce the deterioration of the dynamic spring constant value in the shaded area in FIG.

In addition, in FIGS. 4 to 6, solid lines indicate the characteristics of the mounting device of the present invention. Further, the characteristics of a mounting device made of a single mount rubber are shown by a dashed line in FIG. 6 for comparison.

FIGS. 7 and 8 show a first orifice 113 and a second orifice 114, each having a resonant frequency in a low frequency range, and a first orifice 113 and a first orifice 114, which are movable with respect to high-frequency minute vibrations and whose movement is restrained with respect to low-frequency large-amplitude vibrations. Pulp mechanism 10
9 and a second valve mechanism 112 are shown.

The first valve mechanism 109 has an opening 105a in the partition plate ios.
A thin film-like flexible member tio mainly made of rubber or elastomer and embedded with a fibrous member is adhered to the partition plate 105, and the flexible member 110 covers the opening 105a. is set near the high frequency range that produces the υ sound. The first orifice 113 is the partition plate 1
A t1 surface fluid passage 113m having a relatively large volume is formed around the opening 105a of 05, one end of the passage 113a is communicated with the outside through a constriction part 113b, and the other end is connected to the intermediate chamber 119 through a constriction part 113c. The resonant frequency is set slightly higher than the low frequency range caused by engine idle vibration. The intermediate chamber 119 is constructed by adhering a rectangular tube-shaped relatively hard elastic body 120 between the partition plate ios and the intermediate plate 115. Each 121 is a column embedded in the elastic member 120, and serves to maintain the distance between the partition plate 105 and the intermediate plate 115 and to increase the rigidity of the elastic member 120 (9th column).
(see figure).

The second valve mechanism 112 has an opening 115a in the intermediate plate 115.
A thin film-like flexible member 122 mainly made of rubber or elastomer and embedded with a fibrous member is adhered to the intermediate plate 115, and the flexible member 122 covers the opening 115a. is set to a high frequency range where the dynamic spring constant value is deteriorated in a high frequency range, for example, around 250 to 300. The first niorifice 114 has a relatively large volume fluid passage 114a around the opening 115a of the intermediate plate 115.
One end of the passage 114a is communicated with the outside through a constriction part 114b, and the resonant frequency is set to a low frequency range that causes engine shake.

By incorporating this partition plate 105 into the mounting device in place of the partition plate 5 of the embodiment described above, the constriction part 113b of the first orifice 113 opens into the subchamber 18, and the constriction part 114b of the second orifice 114 opens. The first orifice 113 opens into the fluid chamber 17 to obtain the same effect as in the embodiment described above.
And the second niorifice 114 is located in both parts 113b.

113c, 114b, and the diaphragm portion 113b between 114c,
The thick surface fluid passages 113a, 11 have a larger surface cross-sectional area than the cross-sectional areas of 113e, 114b, and 114c, and have a relatively large volume.
4a, the aperture portions 113 b , 1
．． 13'c,, 114b.

Even if the diameter of 114c is relatively large, the frequency at which the attenuation capacity reaches its maximum value can be adjusted to a predetermined low frequency, and the diameter can be set large, so that the attenuation capacity can be increased.

Moreover, since it is outside the elastic material 120 that defines the intermediate chamber 119, the elastic material 120 is made relatively hard so that each oriice 1
13, 114 can be given separate resonant frequencies.

Note that both knob mechanisms 109 and 112 are connected to the flexible member 11.
By increasing the rigidity of 0.122, the resonance frequency can be set to a much higher frequency side.

Further, the gist of the present invention is to provide the mounting device with good characteristics in a low frequency range, and therefore, at least one valve mechanism 9, 109, 12, 112 may be provided.

(Structure of the Invention) As explained above, according to the present invention, the structure is such that a mount rubber having an internal space is fixed between a base plate on the side of the vehicle unit and a base plate on the vehicle body side. A diaphragm and a partition plate are fixed to one substrate side, a subchamber is formed between the diaphragm and the partition plate, a fluid chamber is formed between the partition plate and the other substrate, and the subchamber is formed between the partition plate and the other substrate. In addition to sealing fluid in the chamber and the fluid chamber, the partition plate has an intermediate chamber in which at least a part of the side surface in contact with the fluid chamber or the sub-chamber is partitioned by an elastic body and in which the fluid is sealed, and The intermediate chamber and the sub-chamber and the intermediate chamber and the fluid chamber are communicated with each other, each of which is equipped with a plurality of oriais having a resonance frequency in the low frequency range, and is movable in response to high frequency micro vibrations, and is capable of responding to low frequency large amplitude vibrations. On the other hand, the fluid manpower unit mounting device is equipped with a knob mechanism that restricts movement.

(Effects of the Invention) Therefore, the Orice provides a high damping force against low frequency, large amplitude vibrations that cause engine shake, and also serves as a mounting device for low frequency, large amplitude vibrations caused by slightly higher engine idle vibrations. The dynamic spring constant value of is reduced to reduce the transmission of this vibration to the vehicle body, and
By lowering the dynamic spring constant value of the mount device against high-frequency minute vibrations that cause muffled noise due to the action of the valve mechanism, the transmission of this vibration to the vehicle body can be reduced, making it possible to reduce the transmission of this vibration to the vehicle body. The effect is that a mounting device having good characteristics can be provided.

[Brief explanation of the drawing]

Figure 1 is a cross-sectional view of a conventional hydraulic power unit mount device, Figure 2 (a) is a diagram showing the frequency-damping force characteristic, and Figure 2 (b) is the same diagram showing the frequency-dynamic spring constant characteristic. 3 is a sectional view showing an embodiment of the present invention, FIG. 4 is a diagram showing the frequency-damping force characteristics, and FIGS. 5 and 6 are the same frequency-dynamic spring constant characteristics. FIG. 7 is a sectional view showing another structural example of the partition plate, FIG. 8 is a sectional view taken along the line ■--■ in FIG. l, 2: Board, 3: Internal space, 4: Mount rubber, 5
, 105: Partition plate, 6: Diamond 7 ram, 9.109: First/no-lube mechanism (), 12.112: Second no-no-lube mechanism (valve mechanism), 13, 113-: No. 1 orifice (orifice), 14.114: 1st orifice (orifice), 17: fluid chamber, 18: sub-chamber, 1
9,119: intermediate chamber, 19d, 120: elastic body. Representative Patent Attorney 1) Toshiyuki (and 1 other person) Figure 1 Figure 2 (a) (b) Figure 3 Figure 4 Day mantissa (Hz) Figure 5 f+ fz h number [H2] 6th Figure 7 Figure 8 Figure 9

Claims (1)

[Claims] 1. Fix a mount plate having an internal space between a board on the power unit side and a board on the vehicle body side, fix a diaphragm and a partition plate to either of the boards, and then connect the diaphragm and the partition plate. A sub-chamber is formed between the partition plate and the other substrate, and a fluid is sealed between the cough sub-chamber and the fluid chamber. Or, a part of the side surface in contact with the secondary chamber ζ is also partially partitioned by an elastic body, and has an intermediate chamber sealed with fluid, so that the intermediate chamber and the secondary chamber and the intermediate chamber and the fluid chamber communicate with each other. , is characterized by having a plurality of orifices each having a resonant frequency in a low frequency range, and further comprising a knob mechanism that is movable in response to high frequency micro vibrations and restrained in motion in response to low frequency large amplitude vibrations. A fluid-filled power unit mouth 2, in which the resonance frequency of the orifice that communicates the intermediate chamber and the sub-chamber is set to a low frequency range that causes engine shake, and the resonance frequency of the orifice that communicates the intermediate chamber and the fluid chamber is set to a low frequency range that causes engine shake. 2. The fluid-filled power unit Makant device according to claim 1, wherein the frequency is set in a low frequency range slightly higher than engine idle vibration.