JPH0771506A - Ff type automobile engine supporting device - Google Patents

Abstract

PURPOSE:To offer an automobile engine supporting device for an FF four cycle transverse engine type excellent in vibrationproof characteristic for shake vibration and idling vibration. CONSTITUTION:A No.1 orifice passage 64 and a No.2 orifice passage 66, which is tuned to a high frequency range higher than that of the No.1 orifice passage 64 and having the peripheral part of the partition member 46 extended by the length of more than 2/3 round in the circumferential direction, are provided for the partition member 46 partitioning a pressure room 48 and a parallel room 50. Using a fluid charged type mount device composed by arranging a movable member 72 on the opening of the No.2 orifice passage 66, such fluid charged type mount device is applied to at least the front side mount device of a plural number of mount device supporting an engine to the body.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an FF type automobile equipped with a horizontally installed four-cylinder engine, and to an engine support device for supporting an engine (a unit including a transaxle; the same applies hereinafter) to a body in a vibration-proof manner. is there.

[0002]

2. Description of the Related Art Conventionally, a support system for supporting an automobile engine on a body includes an engine support device including a plurality of mount devices in order to reduce body vibration of the automobile and improve riding comfort. Has been adopted.

By the way, in such an engine supporting device, particularly, the vibration damping performance against shake vibration and idling vibration, which greatly affects the riding comfort, is emphasized. Therefore, conventionally, by adjusting the damping coefficient and the dynamic spring constant by utilizing the resonance action of the fluid enclosed in the mount, the vibration damping effect in the frequency range of shake vibration and the vibration damping effect in the frequency range of idling vibration can be achieved. The design was carried out with the aim of improving the vibration isolation effect together. However, since the vibration damping property and the vibration insulating property are contradictory requirements, it is extremely difficult to obtain a satisfactory vibration damping effect against both shake vibration and idling vibration.

In particular, in an FF type automobile equipped with a laterally placed engine having a crankshaft oriented in the left and right direction of the vehicle, which is often found in general small passenger cars, the moment input of roll vibration due to engine torque fluctuation is input. Since the vertical bending of the body can be easily excited, and in the case of a 4-cylinder engine, the idling vibration was a big problem because the roll vibration frequency during idling rotation was almost the same as the frequency of the longitudinal bending mode of the body. Therefore, there has been a long-felt need for an engine support device capable of exhibiting an effective vibration damping effect against idling vibration while ensuring a high damping effect against shake vibration.

In Japanese Utility Model Publication No. 2-121313,
A fluid-filled mount is applied to either the front side or the rear side, and the vibration force transmitted to the body via the front mounting device and the force transmitted to the body via the rear mounting device are applied. An engine support device is disclosed in which a total vibration force exerted on a vehicle body is reduced by shifting a phase of the vibration force to obtain a vibration damping effect against idling vibration.

However, in the engine support device disclosed in this publication, since the mounting device having the conventional structure having a single orifice passage is adopted, when such an orifice passage is tuned for idling vibration, the shake occurs. There is a problem that the vibration damping effect against vibration is unavoidably deteriorated, and the vibration damping effect against shake vibration and the vibration damping effect against idling vibration cannot be achieved at the same time.

[0007]

The present invention has been made in view of the circumstances as described above, and the problem to be solved is to provide a high damping effect against shake vibration,
It is an object of the present invention to provide an engine support device for an FF type automobile equipped with a horizontally arranged four-cylinder engine, which can exhibit an effective vibration damping effect against idling vibration.

[0008]

In order to solve such a problem, a feature of the present invention resides in that, as described above, a horizontally mounted four-cylinder engine is supported on a body through a plurality of mounting devices. In an automobile engine support device, (a) a first support fitting attached to either one of the engine and the body, and (b) a second support attachment attached to the other side of the engine and the body. Support metal fittings, (c) a rubber elastic body connecting the first support metal fittings and the second support metal fittings, and (d) a partition member supported by the second support metal fittings,
(E) A pressure-receiving chamber formed on one side of the partition member, a part of the wall portion of which is made of the rubber elastic body, and which causes internal pressure fluctuation when vibration is input, and (f) the partition member. An equilibrium chamber formed on the other side, in which a part of the wall portion is made of a flexible film and is allowed to change in volume, and And (h) a first orifice passage which is provided so as to penetrate the partition member and communicates the pressure receiving chamber and the equilibrium chamber with each other, and (i) a predetermined amount of displacement or deformation by the partition member. A movable member supported and disposed between the pressure receiving chamber and the equilibrium chamber; and (j) the outer peripheral portion of the partition member in the circumferential direction on the pressure receiving chamber side or the equilibrium chamber side of the movable member. 2 /
A second orifice passage tuned to a frequency range higher than that of the first orifice passage, which is provided with a length of three rounds or more and in which a fluid flow is generated inside due to the displacement or deformation of the movable membrane. A fluid-filled mount device configured to include and is used, and the fluid-filled mount device is applied to at least the front side of the plurality of mount devices.

[0009]

EXAMPLES Examples of the present invention will now be described in detail with reference to the drawings in order to clarify the present invention more specifically.

First, FIG. 1 shows a schematic structure of an engine support device having a structure according to the present invention. In the figure, reference numeral 10 is a main body of an automobile having a monocoque structure, and the main body 10 forms an engine room 12 in the front portion of the vehicle body.
A four-cylinder engine 14 is housed in the engine room 12, and the crankshaft is arranged in a horizontal position extending in the vehicle left-right direction. The engine 14 is connected to and supported by the main body 10 by an engine support device including a plurality of mounts.

Here, in the present embodiment, such an engine support device includes a left mount 16 and a right mount 18 arranged on both left and right sides of the engine 14, and a front mount 20 and a rear mount 22 arranged on both front and rear sides. It is composed of four mounting devices consisting of and. As the front mount 20, a fluid-filled mount 24 as shown in FIG. 2 is adopted, while the other mounts 16, 18, 22 are used.
Has a solid solid type rubber mount.

The fluid-filled mount 24 has a structure in which a first support fitting 26 and a second support fitting 28 are elastically connected by a rubber elastic body 30 interposed therebetween. One of the first support fitting 26 and the second support fitting 28 is attached to the engine 14 and the other is attached to the main body 10,
It is arranged to be interposed between the engine 14 and the main body 10.

More specifically, the first support fitting 26 has an inverted truncated cone shape. Also, on the large diameter end surface,
A mounting bolt 32 is provided so as to project outward, and is mounted on the engine 14 or the main body 10 by the mounting bolt 32.

On the other hand, the second support fitting 28 has a large diameter portion 34.
And has a stepped cylindrical shape including a small diameter portion 36.
An annular plate-shaped mounting plate 39 that spreads outward in the radial direction is fixed to the stepped portion 38, and the mounting plate 39 allows the mounting plate 39 to be mounted on the main body 10 or the engine 14. ing.

The second support fitting 28 is connected to the first support fitting 26 in a state where the opening on the large diameter portion 34 side opens toward the end on the small diameter side of the first support fitting 26. The rubber elastic bodies 30 are disposed so as to face each other at a predetermined distance on substantially the same axis, and between the facing surfaces of the first support fitting 26 and the second support fitting 28.

The rubber elastic body 30 has a substantially truncated cone shape, and has a recess 40 that is open at the end surface on the large diameter side. The first support fitting 26 is vulcanized and adhered to the small-diameter side end surface of the rubber elastic body 30 while being embedded from the small-diameter side end portion, while the second supporting metal member 26 is secondly attached to the outer peripheral surface of the large-diameter side end portion. The support metal fitting 28 is vulcanized and adhered to the inner peripheral surface of the large diameter portion 34. As a result, the first support fitting 26 and the second support fitting 28 are elastically coupled to each other by the rubber elastic body 30, and the rubber elastic body 30 also allows the second support fitting 28 to be connected. The opening on the side of the large diameter portion 34 is covered in a fluid-tight manner.

On the other hand, the small diameter portion 3 of the second support fitting 28
A diaphragm 42 made of a thin rubber film as a flexible film is disposed in the opening of 6, and an annular metal fitting 44 vulcanized and bonded to the outer peripheral edge portion is provided with a small diameter portion of the second support metal fitting 28. It is attached by being caulked and fixed to the opening of 36. The opening of the second support fitting 28 on the side of the small diameter portion 36 is fluid-tightly covered by the diaphragm 42, so that a predetermined incompressible fluid is enclosed in the second support fitting 28. A fluid chamber is formed. As the enclosed fluid, for example, water, alkylene glycol, polyalkylene glycol, silicone oil, or the like is adopted, and the diaphragm 42 for the second support fitting 28 is used.
The assembly is performed in a fluid to fill the fluid chamber.

Further, in the fluid chamber, a partition member 46 having a substantially thick disk shape as a whole is provided with a second support fitting 28.
It is accommodated and arranged so as to spread in the direction orthogonal to the axis of the above, and is fixedly attached to the second support fitting 28. The partition member 46 divides the fluid chamber into two parts in a fluid-tight manner. Therefore, on one side of the partition member 46 (the first support metal fitting 26 side), a part of the wall portion is made of a rubber elastic body. The pressure receiving chamber 48 is formed by 30 and in which an internal pressure fluctuation is generated at the time of vibration input, while a part of the wall portion is formed by the diaphragm 42 on the other side of the partition member 46 to change the volume. An equilibrium chamber 50 is formed that allows

Further, the partition member 46 for partitioning the pressure receiving chamber 48 and the equilibrium chamber 50 has the first and second orifice members 56, 56 inside the inverted cup-shaped outer metal fitting 54 having the outer flange portion 52 at the opening peripheral edge portion. 58 is incorporated. Then, the outer flange portion 52 of the outer metal fitting 54
Is an annular metal member 44 vulcanized and bonded to the diaphragm 42.
At the same time, it is fixedly attached to the second support fitting 28 by being caulked and fixed to the opening of the small diameter portion 36 of the second support fitting 28.

In the outer peripheral portion of the partition member 46, the outer metal fitting 54 and the first orifice member 56 extend in the circumferential direction between the radial overlapping surfaces, and the communication holes 6 are formed at both ends in the circumferential direction.
A first orifice passage 64 that communicates with the pressure receiving chamber 48 and the equilibrium chamber 50 through 0 and 62 and allows the fluid flow between the two chambers 48 and 50 is formed. Then, the first orifice passage 64, based on the resonance of the fluid flowing through the internal, such a large damping coefficient upon input of vibration near 10 H _Z, which corresponds to shake vibration is obtained, the length and cross-sectional area Is tuned.

Furthermore, the first orifice passage 6
The second orifice passage 6 extending radially inward of 4 extends a distance of ⅔ or more in the circumferential direction between the radial overlapping surfaces of the first orifice member 56 and the second orifice member 58.
6 is formed. The second orifice passage 66 has one end in the circumferential direction through the communication hole 68,
The other end 7 in the circumferential direction communicates with the pressure receiving chamber 48.
0 is opened between the axial overlapping surfaces of the first orifice member 56 and the second orifice member 58.

The second orifice passage 66 is movable between the axially overlapping surfaces of the first orifice member 56 and the second orifice member 58 in which one end portion 70 in the circumferential direction is opened. Disc-shaped rubber film 7 as a member
2 are provided. The rubber film 72 holds the thickened outer peripheral edge portion between the first orifice member 56 and the second orifice member 58 under pressure, and allows a predetermined amount of deformation in the central portion. It is like this. Then, one end 70 of the second orifice passage 66 in the circumferential direction is opened on one surface side of the rubber film 72, while the other surface side of the rubber film 72 passes through the communication hole 74. It communicates with the equilibrium chamber 50.

As a result, one surface of the rubber film 72 is
The internal pressure of the pressure receiving chamber 48 is exerted through the second orifice passage 66, while the internal pressure of the equilibrium chamber 50 is exerted through the communication hole 74 on the other surface side of the rubber film 72. Then, when the vibration is input, the rubber film 72 is generated based on the internal pressure difference generated between the pressure receiving chamber 48 and the equilibrium chamber 50.
Is deformed, so that a fluid flow is generated in the second orifice passage 66.

Further, in this case, the second orifice passage 66 is arranged so that the outer peripheral portion of the partition member 46 is circumferentially divided into two.
/ 3 laps or more because it is formed so as to extend in length, upon input of vibration around 20 to 30 H _Z, which corresponds to idling vibration, the flow of the fluid flowing to the second orifice passage 66 Based on this, a large phase deflection effect is produced. That is, specifically,
Since the second orifice passage 66 is formed with the outer peripheral portion of the partition member 46 having a length of ⅔ or more in the circumferential direction, a vibration transmission phase angle of 100 deg or more can be obtained.
It can be easily obtained.

Therefore, in the engine supporting apparatus of this embodiment, which is constructed by applying the fluid-filled mount 24 having the above-mentioned structure to the front mount 20, the front mount 20 is in the frequency range corresponding to the idling vibration.
Since the vibration transmission phase angle of can be tuned in a sufficiently wide range, the front mount 20
The vibration transmission force transmitted to the main body 10 through
To easily and advantageously set the vibration transmission phase angle of the front mount 20 so that the resultant force of the vibration transmission force transmitted to the main body 10 through the left and right mounts 16 and 18 and the rear mount 22 is exerted. Can be done.

As a result, during idling, the main body 1 is passed through the mounts 16, 18, 20, 22.
Mutual canceling effects of vibrations reaching 0 can be effectively exhibited, and idling vibrations in the main body 10 can be extremely effectively reduced.

Further, in the above-described engine support device, since the fluid mount type mount 24 is applied to the front mount 20 which is positioned at a portion of the main body 10 where the vibration mode amplitude is large, the other mount 16 is used. The effect of canceling the vibration transmission force transmitted to the main body through the front mount 20, the vibration transmission force transmitted through the front mount 20, and the effect of reducing idling vibration can be more effectively exhibited.

The vibration transmission phase angle of the front mount 20 generally depends on the characteristics of the other mounts 16, 18, 22 and the characteristics of the main body 10, but is generally 3 degrees.
It has been confirmed that an effective reduction effect of idling vibration can be obtained by setting it to 0 to 180 deg, especially 60 to 130 deg.

Further, in the above-described engine support device, the fluid-filled mount 2 is used even when the shake vibration is input.
An excellent vibration damping effect can be exerted by the damping effect exerted based on the resonance action of the fluid made to flow through the first orifice passage 64 formed in 4.

Since the shake vibration has a sufficiently large amplitude as compared with the idling vibration, when the shake vibration is input, the shake vibration substantially flows between the pressure receiving chamber 48 and the equilibrium chamber 50 through the second orifice passage 66. By limiting the amount of fluid to be caused by the rubber film 72, it is possible to secure a sufficient amount of fluid to be caused to flow through the first orifice passage 64 when the shake vibration is input.

Further, in the present embodiment, both the first orifice passage 64 and the second orifice passage 66 are formed so as to extend in the circumferential direction on the outer peripheral portion of the partition member 46. The lengths of the orifice passages 64 and 66 can be sufficiently secured, and the desired vibration damping effect can be advantageously obtained.

Although one embodiment of the present invention has been described above in detail, this is a literal example and the present invention should not be construed as being limited to such a specific example.

For example, in the above-described embodiment, the fluid-filled mount 24 is applied only to the front mount 20, but the other mounts 16, 18 and 22 are also provided with at least one orifice passage. Mounts may be applied.

Further, in the above embodiment, the four mounts 1
One specific example of applying the present invention to an engine supporting device provided with 6, 18, 20, 22 is shown. However, in addition to the engine supporting device having a structure in which the engine is supported at three points by three mounts. However, the present invention can be similarly applied. In that case, at least,
For the mount that is located on the most front side,
The fluid-filled mount having the structure as described above is applied.

Furthermore, in the above-described embodiment, the second orifice passage 66 is formed on the pressure receiving chamber 48 side of the rubber membrane 72. However, the second orifice passage 66 is formed in the rubber membrane 72.
It may be formed closer to the equilibrium chamber 50 side.

In the above embodiment, the movable member is
Although the rubber film 72 is adopted in which the outer peripheral edge portion is clamped and the center portion is allowed to be deformed, a movable plate structure having a movable plate structure which is displaceable by a predetermined distance without the outer peripheral edge portion being clamped is used. It is also possible to adopt.

Furthermore, the second orifice passage 66 is axially displaced from the portion of the partition member 46 where the first orifice passage 64 and the second orifice passage 66 are formed, so that the second orifice passage 66 is located at the outermost peripheral portion of the partition member 46. It is also possible to form it.

Further, it is possible to secure a longer flow path length by forming the first orifice passage 64 in a spiral shape.

Although not listed one by one, the present invention is
The present invention can be carried out in a mode in which various changes, modifications, improvements, etc. are added based on the knowledge of those skilled in the art, and such a mode does not depart from the gist of the present invention.
It goes without saying that both are included within the scope of the present invention.

[0040]

As is apparent from the above description, in the FF type automobile engine supporting device having the structure according to the present invention, the second extending in the circumferential direction of the partition member is not less than 2/3 round. Since the fluid-filled mount device with the orifice passage is applied to the front mount device, it is possible to tune the vibration transmission phase angle at the time of input of idling vibration in the front mount device over a wide range. This makes it possible to extremely easily and effectively obtain the effect of reducing idling vibration by canceling the resultant force of the vibration transmission force exerted on the body through another mounting device.

Further, in the fluid-filled mount device used as the front mount device in the FF type automobile engine support device according to the present invention, the amount of fluid flow through the second orifice passage is limited by the movable member. In addition, since the first orifice passage tuned to a frequency range lower than that of the second orifice passage is provided, the resonance action of the fluid caused to flow through the first orifice passage of the fluid-filled mount device is provided. Based on the above, it is possible to obtain an excellent anti-vibration effect against shake vibration.

[Brief description of drawings]

FIG. 1 is an explanatory diagram showing a schematic configuration of an engine support device as an embodiment of the present invention.

FIG. 2 is a vertical sectional view showing a fluid-filled mount applied to the front mount of the engine support device shown in FIG.

[Explanation of symbols]

 10 Main Body 14 Engine 16 Left Mount 18 Right Mount 20 Front Mount 22 Rear Mount 24 Fluid Mounted Mount 26 First Support Metal Fitting 28 Second Support Metal Fitting 30 Rubber Elastic Body 42 Diaphragm 46 Partition Member 48 Pressure Receiving Chamber 50 Balance Room 64 First orifice passage 66 Second orifice passage 72 Rubber film

Claims (1)

[Claims] 1. An FF type automobile engine support device for supporting a horizontally installed four-cylinder engine on a body through a plurality of mounting devices, wherein: (a) one of the engine and the body is provided. A first support fitting to be attached; (b) a second support fitting attached to the other side of the engine and the body; and (c) connecting the first support fitting and the second support fitting. A rubber elastic body, (d) a partition member supported by the second support fitting, and (e) a part of a wall formed on one side of the partition member is made of the rubber elastic body. And (f) a part of the wall formed on the other side of the partition member is made of a flexible film to allow a volume change. Equilibration chamber, and (g) those A non-compressible fluid enclosed in the pressure chamber and the equilibrium chamber, and (h) a first orifice passage that penetrates through the partition member and communicates the pressure receiving chamber and the equilibrium chamber with each other. ) A movable member supported by the partition member so as to be displaced or deformable by a predetermined amount and disposed between the pressure receiving chamber and the equilibrium chamber,
(J) On the pressure receiving chamber side or the equilibrium chamber side of the movable member, the outer peripheral portion of the partition member is provided with a length of ⅔ or more in the circumferential direction, and is accompanied by displacement or deformation of the movable film. Using a fluid-filled mount device configured to include a second orifice passage tuned to a frequency range higher than that of the first orifice passage in which fluid flow is generated inside An FF type engine support device for an automobile, wherein the mounting device is applied to at least a front side mounting device of the plurality of mounting devices.