JPH0215064Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to an engine mount that is installed between a vehicle body and a power unit including an engine and transmission of a vehicle to provide vibration isolation, and particularly relates to a front engine/front drive vehicle (FF This invention relates to an engine mount suitable for use in automobiles.

One type of engine mount includes an inner member that is attached to one side of the power unit or the vehicle body, an outer member that is placed outside the inner member at a predetermined distance and attached to the other side of the power unit or the vehicle body, and Some devices include an elastic body disposed between the inner member and the outer member so as to surround the inner member and elastically connect the two members.

In this type of engine mount, it is desirable to set the dynamic spring constant of the elastic body such as a rubber body to be low in order to suppress muffled noise during normal driving. The reaction force of the drive torque during deceleration acts directly on the power unit, and the reaction force reaches the engine mount, so it is necessary to smooth out the large vibration input that occurs when starting, etc. Moreover, it is desirable to have vibration damping characteristics that dampen the vibration quickly. However, no matter how you set the dynamic spring constant of the elastic body, it is difficult to satisfy both the functions of suppressing muffled noise and suppressing large vibrations. There was a resentment that sacrificed functionality.

The present invention has been developed based on the above circumstances, and its purpose is to provide an engine mount for a front-wheel drive vehicle that includes the above-mentioned inner member, outer member, and elastic body. ,
To provide an engine mount capable of effectively damping large vibrations without adversely affecting suppression of muffled noise, etc.

In order to achieve such an object, the present invention forms a plurality of fluid chambers in which a predetermined incompressible fluid is sealed in a portion surrounding the inner member of the elastic body, and An orifice means is provided for making the fluid chambers communicate with each other, and a predetermined damping effect is exerted by the flow resistance generated when the incompressible fluid flows between the plurality of fluid chambers through the orifice means. , the outer member is provided with a stopper portion corresponding to each of the plurality of fluid chambers, and the stopper portion is opposed to a portion of the elastic body in which the plurality of fluid chambers are formed, with a predetermined space in between. That's what I did.

In this way, when a large vibration load is applied to the engine mount, the incompressible fluid in the fluid chamber whose volume is reduced due to the elastic deformation of the elastic body is directed to another fluid chamber through the orifice means. The large vibration input is effectively attenuated by the flow resistance generated during the movement. Therefore, the dynamic spring constant of the elastic body can be set to the optimal value to suppress muffled noise, etc., and as a result, it is possible to provide an engine mount that can significantly improve the vibration and noise characteristics of FF vehicles. It became possible. When an even larger load is applied, the wall of the fluid chamber comes into contact with the stopper part of the outer member facing across a predetermined space, and along with this contact, the fluid chamber In addition to the flow resistance due to fluid movement based on the deformation of the inner member, an effective stopper function can be achieved in preventing excessive displacement between the inner member and the outer member.

Hereinafter, one embodiment of the present invention will be described in detail based on the drawings.

The engine mount that will be explained below is
As shown in FIG. 1, a power unit 6 including an engine 2 and a transmission 4 of a front-wheel drive vehicle elastically supports a horizontal engine installed horizontally with respect to the direction of travel of the vehicle. It is used. Normally, a horizontally mounted engine (power unit) of a FF car has engine mounts located in four locations: a front mount 8, a rear mount 10, and a left mount 12.
The weight of the power unit 6 is supported mainly by both the left and right mounts 12 and 14, which are suspended, and by the front and rear mounts 8. , 10 support the power unit 6 substantially obliquely from below and serve to reduce idling vibrations and rolling vibrations.

Among them, the engine mount described below is particularly suitable for use as the rear mount 10. As is clear from FIG. 2, this rear mount 10 connects the vehicle body 16 and the power unit 6.
The drive torque of the FF vehicle acts on the power unit 6, causing rolling in the A direction during acceleration and rolling in the B direction during deceleration, and this rolling vibration The important role of the rear mount 10 is to reduce this.

Below, the rear mount 10 according to the present invention will be described.
A specific example will first be explained based on FIG.

The rear mount 10 shown in FIG. 3 includes a cylindrical inner metal fitting 20, a cylindrical outer metal fitting 22 disposed outside the inner metal fitting 20 at a predetermined distance,
It is provided so as to surround the inner metal fitting 20 while forming a substantially C-shaped or U-shaped space between it and the outer metal fitting 22. It includes a rubber body 24 as an elastic body connected to the body.

A bracket 26 is fixed to the outer metal fitting 22, and the outer metal fitting 22 is connected to the outer metal fitting 22 via this bracket 26.
is attached to the vehicle body 16. On the other hand, the outer metal fitting 2
The inner metal fitting 20, which is disposed inside the metal fitting 2 and parallel to the opening direction thereof, has a shaft hole 28 along its longitudinal direction, and a shaft (not shown) inserted into the shaft hole 28 faces the power unit 6 side. By being attached to the fixed bracket 32, the inner metal fitting 20 is attached to the power unit 6 side.

The inner metal fitting 20 has a cylindrical shape, and the outer metal fitting 22 disposed on the outside thereof has a hexagonal cylinder shape in which a trapezoid is combined with a rectangle. and,
Two of the hexagonal sides of the outer fitting 22 are stopper parts 30 and 32 that face each other in parallel, and rubber layers 34 and 36 are provided on the inner surfaces of the stopper parts 30 and 32, respectively. It is fixed to form a planar stopper surface. Also, one side of the outer metal fitting 22 perpendicular to the stopper parts 30 and 32 is connected to another stopper part 3 that connects them.
8, and as a result, the stopper portions 30, 3
2 and 38 are formed to form three sides of a rectangle. Furthermore, the stopper portion 38 of the outer metal fitting 22
One side portion 40 parallel to the stopper portion 3
0 and 32 are connected by the two side parts, and the outer metal fitting 22 has a hexagonal cylinder shape as a whole.

On the other hand, as is clear from FIGS. 4 and 5, the inner metal fitting 20 has both ends connected to the outer metal fitting 20.
Although it protrudes slightly from the openings on both sides,
It is surrounded by the rubber body 24 in a range that approximately corresponds to the width dimension of the outer metal fitting 22. As is clear from FIG. 3, the rubber body 24 surrounds the inner metal fitting 20 in a substantially cylindrical shape around its axis, and a part of the surrounding portion is attached to the outer metal fitting 20.
The second stopper portion 38 extends perpendicularly to the opposite side thereof, and is fixed to the one side portion 40 to connect the inner metal fitting 20 and the outer metal fitting 22. As a result, a predetermined space is secured between the remaining surrounding portion of the rubber body 24 and the outer metal fitting 22.

Note that the portion of the rubber body 24 on the stopper portion 38 side is a planar contact surface 42, and the stopper portion 38
8 and are arranged to face in parallel with each other at a certain distance from each other. Further, in this embodiment, an outer contact portion 44 covered with a rubber layer of a predetermined thickness is provided on the outer surface of the stopper portion 38 of the outer metal fitting 22,
The abutment portion 44 is opposed to a plate-shaped external stopper portion 46 protruding from the bracket 32 on the power unit 6 side at a predetermined distance.

Two fluid chambers 48 are provided at symmetrical positions with respect to the center line of the inner fitting 20 in a substantially cylindrical portion of the rubber body 24 surrounding the inner fitting 20 that is not connected to the outer fitting 22. It is provided. These fluid chambers 48 are arranged in A and B where the power unit 6 receives reaction forces of acceleration/deceleration torque.
The rubber bodies 24 are arranged facing each other in the direction.
The rubber body 24 is formed to have a cross section extending in a substantially arc shape in the circumferential direction, and as shown in FIG. It has a depth that extends toward.

Moreover, as is clear from Fig. 3, the rubber body 2
Each portion in which the four fluid chambers 48 are formed faces the stopper portions 30 and 32 of the outer metal fitting 22 at a predetermined distance from each other. That is, the stopper parts 30 and 32 are opposed to each other in parallel in directions A and B in which the power unit 6 receives the reaction force of acceleration/deceleration torque, and the fluid of the rubber body 24 is opposed to the stopper parts 30 and 32. The chamber 48 forming portions are further opposed to each other.

Furthermore, a pair of protrusions 50 are provided on the wall surface of the fluid chamber 48 on the inner metal fitting 20 side so as to protrude in opposite directions. One protrusion 50
is formed so as to protrude toward the stopper portion 30 of the outer metal fitting 22 at the center of the fluid chamber 48 in the curve direction, and the other protrusion 50 is formed so as to protrude toward the stopper portion 32. As shown in FIG. 4, which protrusion 50
The rubber body 24 also has a length that substantially corresponds to the depth dimension of each fluid chamber 48 along the axial direction.

Each fluid chamber 48 has a dead end shape at one end of the rubber body 24, but is opened laterally at the other end of the rubber body 24. A first plate 52 functioning as a first member is vulcanized and bonded to the end of the rubber body 24 on the side where each fluid chamber 48 is opened. This first plate 52 is an annular plate member, and a window portion 54 of a size corresponding to the opening is formed in a portion facing the opening of each fluid chamber 48 passing through the plate in the thickness direction, and has a center hole. is fitted to the end of the inner metal fitting 20.

A second plate 56, which is also an annular plate member, is brought into close contact with the outer surface of the first plate 52 in a liquid-tight manner. This second plate 56 is
The inner metal fitting 20 is fitted into one end of the inner metal fitting 20 and caulked in the radially expanding direction, and the outer peripheral portion of the first plate 52 is caulked to the second plate 56 side. The second plate 56 closes the openings of the respective fluid chambers 48 to form a liquid-tight space. Each fluid chamber 48 so formed
For example, water, polyalkylene glycol,
Incompressible fluids such as silicone oil and low-molecular polymers are each sealed.

An orifice 58 is provided between the first plate 52 and the second plate 56, which is an annular flow path that allows the fluid chambers 48 to communicate with each other. This orifice 58 is provided at each window 5 of the first plate 52 on the inner surface of the second plate 56.
An annular groove formed along the circumference passing through the first plate 52 is closed with the outer surface of the first plate 52, and communicates with each fluid chamber 48 at the window 54, so that one of the fluids can be The incompressible fluid is allowed to flow from the chamber 48 through the orifice 58 to the other fluid chamber 48 . In this embodiment, the first plate 52 and the second plate 56 constitute orifice forming members, and together with the orifice 48 formed on their mating surfaces, constitute orifice means.

By the way, engine mount 10 like this
is manufactured, for example, according to the following steps.

First, the first plate 5 is attached to one end of the inner metal fitting 20.
2 fitted and fixed together and the outer metal fitting 22 are set in a predetermined mold, and a rubber material is injected between them and vulcanization molded, thereby forming the inner metal fitting 2.
0 and the first plate 52 are vulcanized and bonded, and the rubber body 24 is simultaneously vulcanized and molded. Simultaneously with the vulcanization molding of the rubber body 24, the two fluid chambers 48 are opened at one end surface of the rubber body 24, and these openings are connected to the window portion 5 of the first plate 52.
It is made to be continuous to 4. Moreover, the rubber layers 34, 36, and 44 of the outer metal fitting 22 can also be formed at the same time during the vulcanization molding. after that,
In a liquid tank containing an incompressible fluid as described above, a second plate 56 is disposed on the outer surface of the first plate 52 to cover the window 54, and the end of the inner fitting 20 and the first By caulking the outer peripheral portions of the plates 52, the first plate 5
Integrates with 2nd class. By this integrated operation, a predetermined incompressible fluid can be easily and effectively sealed in the fluid chamber 48, and the orifice 58 can be easily and effectively sealed.
is formed, and the engine mount 10 as shown in FIGS. 3 to 5 is completed.

Such a rear mount 10 is suitably used for a horizontally mounted engine of a front-wheel drive vehicle. That is, as described above, the inner metal fitting 20 is attached to the power unit 6 side, and the outer metal fitting 22 is attached to the vehicle body 16 side, and the stopper parts 30, 32 of the outer metal fitting 22 allow the power unit 6 to absorb the reaction force of acceleration/deceleration torque. The rubber body 24 is used in such a state that the stopper parts 30 and 32 are opposed to each other in parallel with each other in directions A and B, and the parts in which the fluid chambers 48 of the rubber body 24 are formed are opposed to each other with a predetermined space in between. It is.

In such an engine mount 10, the FF
If rolling vibration occurs in directions A and B when the car starts or brakes, one of the fluid chambers 4
As the volume of the fluid chamber 8 decreases, incompressible fluid is forced to flow from the fluid chamber 48 to the other fluid chamber 48 through the orifice 58, and the flow resistance generated at this time causes problems such as when starting or braking. Therefore, rolling vibrations in the vehicle can be damped quickly and effectively. Further, an orifice 58 through which an incompressible fluid flows is provided on the first plate 52.
It is formed on the mating surface of the rubber body 24 and the second plate 56, and its flow cross-sectional area is always kept constant regardless of the elastic deformation of the rubber body 24, so that stable damping characteristics can be obtained.

By suppressing large rolling vibrations due to such fluid flow resistance, the dynamic spring constant of the rubber body 24 itself can be set to the optimum value for the actual vehicle, which is most desirable for suppressing muffled noise etc. While suppressing muffled noise, it has also achieved significant attenuation of rolling vibrations, making it possible to effectively improve the vibration and noise characteristics of front-wheel drive vehicles.

Moreover, in this embodiment, the portion of the rubber body 24 where the fluid chamber 48 is formed is opposed to the stopper portion 30 or 32 of the outer metal fitting 22, and protrudes from the wall surface of the fluid chamber 48 on the inner metal fitting 20 side. Since the portion 50 is formed, for example, the above AB
When a large load is applied in the direction, the outer wall portion of the rubber body 24 forming the fluid chamber 48 is brought into contact with the rubber layer 34 of the stopper portion 30, and the protrusion 50
is brought into contact with the outer wall portion of the fluid chamber 48,
A so-called two-step stopper action is obtained, and furthermore, flow resistance is added when the incompressible fluid is caused to flow to the other fluid chamber 48 due to the volume reduction of the fluid chamber 48, and the overflow between the inner metal fitting 20 and the outer metal fitting 22 is reduced. A complex stopper function is performed in preventing large displacements. Also, when a large load acts in the direction A, the rubber layer 36 of the stopper portion 32 is exposed to the other fluid chamber 48 side.
The same applies to the case where it is brought into contact with.

As a result, as shown in the graph of Figure 6,
Conventional engine mounts without fluid chambers
As is clear from the load-deflection curve shown by the dashed line,
In contrast to the case where the dynamic spring constant suddenly rises after the stopper action is performed, in the engine mount of this embodiment, due to the fluid flow resistance and the two-stage stopper action as described above, the rubber body 24
This prevents the spring constant from increasing rapidly when the elastic deformation exceeds a certain level, and provides a gentle stopper function, so even when a large load is applied, excessive deformation of the rubber body 24 is prevented with very little shock feeling. It can be prevented.

Furthermore, if an excessive vibration input is applied between the inner metal fitting 20 and the outer metal fitting 22 in directions C and D, which are substantially perpendicular to the directions A and B, due to vibrations from the road surface, for example, the rubber body 24 comes into contact with the stopper part 38 of the outer metal fitting 22, or the outer contact part 44 formed on the outside of the outer metal fitting 22 comes into contact with an external stopper part 46 provided on the power unit 6 side. This also prevents such excessive displacement in the C and D directions.

In addition, in the embodiment described above, the outer metal fitting 22
was in the form of a hexagonal cylinder, but the stopper part 3
0 and 32 are extended as they are to form the side portion 4.
There is no problem even if the whole is formed into a quadrilateral, especially a rectangle, by being connected to 0.
Further, the outer metal fitting 22 may be cylindrical and arranged concentrically with the inner metal fitting 20.

Further, instead of providing two fluid chambers 48, the number can be increased. For example, it is also possible to form a pair of fluid chambers facing each other in the C and D directions. Further, the cross-sectional shape of the fluid chamber can be modified as appropriate in accordance with the vibration characteristics of the actual vehicle to which it is applied, in addition to the shape provided with the convex portion 50 as described above.

In addition, the orifice means for making these fluid chambers communicate with each other is not limited to forming the first and second plates 52 and 56 on the sides of the rubber body, and the orifice means is not limited to forming the first and second plates 52 and 56 on the sides of the rubber body. The bodies may be tightly fitted and an orifice may be formed on the fitting surfaces of the two, or may be formed inside the rubber body.

In addition, although specific explanations are omitted, it goes without saying that the present invention can be implemented with various modifications and improvements based on the knowledge of those skilled in the art.

[Brief explanation of the drawing]

FIG. 1 is a schematic plan view showing an example of a specific configuration of an engine mount according to the present invention, and FIG. 2 is a schematic side view. Third
The figure is a front view showing an engine mount that is an embodiment of the present invention, and is also a view showing a form in which the engine mount is attached between a vehicle body and a power unit. Moreover, FIG. 4 and FIG. 5 are respectively - and - sectional views in FIG. 3. Furthermore, FIG. 6 is a graph showing the stopper characteristics of the engine mount of this embodiment in comparison with a conventional one. 2: Engine, 4: Transmission, 6:
Power unit, 10: Rear mount, 16: Vehicle body, 20: Inner metal fitting (inner member), 22: Outer metal fitting (outer member), 24: Rubber body (elastic body), 48:
Fluid chamber, 52: first plate (first member), 5
4: Window part, 56: Second plate (second member), 5
8: Orifice.

Claims (1)

[Claims for Utility Model Registration] (1) A device that provides anti-vibration support for a power unit including the engine and transmission of a front-wheel drive vehicle, and includes a cylindrical inner member attached to either the power unit or the vehicle body; , a substantially C-shaped or U-shaped space is provided between a cylindrical outer member that is disposed at a predetermined distance outside the inner member and is attached to the other side of the power unit or the vehicle body, and the outer member. and an elastic body that is provided to surround the inner member and elastically connect the inner member to the outer member in a cantilevered state, the inner side of the elastic body In the area surrounding the parts,
A plurality of fluid chambers are formed in which a predetermined incompressible fluid is sealed, and orifice means is provided to allow the plurality of fluid chambers to communicate with each other, and the incompressible fluid flows between the plurality of fluid chambers through the orifice means. A predetermined damping effect is exerted by the flow resistance generated when the fluid flows, and a stopper portion is provided in the outer member corresponding to each of the plurality of fluid chambers, and the stopper portion is arranged in the elastic body. An engine mount for a front-wheel-drive vehicle, characterized in that a portion in which a plurality of fluid chambers are formed are opposed to each other at a predetermined interval. (2) Utility model registration claim 1, wherein the elastic body has protrusions that extend in correspondence with the stopper portions in the plurality of fluid chambers, respectively.
Engine mount as described in section. (3) The plurality of fluid chambers include two fluid chambers formed in the elastic body so as to face each other in the direction in which the power unit receives the reaction force of acceleration/deceleration torque.
The engine mount described in item 2 or item 2. (4) The plurality of fluid chambers have an opening at at least one end of both ends in the axial direction of the inner member of the elastic body, and the orifice means:
a first member having a window portion in a portion corresponding to the opening of the fluid chamber and fixed to an end of the elastic body; and a first member liquid-tightly attached to an outer surface of the first member so as to cover the window portion. and a second member forming a fluid passage connecting the window portion to a mating surface with the first member. Engine mount.