JP4808481B2 - Automobile power unit support structure - Google Patents

Description

  The present invention relates to a power unit support structure including an automobile engine and a transmission.

In an automobile, a power unit including an engine, a transmission, and the like is elastically supported on the vehicle body side via mount rubbers and the like at a plurality of locations. The setting of the support points of the power unit by these mount rubbers and the support structure at each support point are extremely important in order to reduce the transmission of power unit vibration to the vehicle body side, reduce vehicle interior noise, and ensure improved riding comfort. It is important and has been developed in various ways according to the engine type and mounting type.

  For example, a vertically mounted power unit for automobiles is provided with a center mount provided almost immediately below the center of gravity, left and right front mounts provided respectively on the left and right sides of the front of the power unit, and a rear provided on the rear end of the power unit. There is known a power unit support structure that is supported on the vehicle body side via a mount rubber at four positions of the mount (for example, see Patent Document 1).

  According to this power unit support structure, by supporting almost the entire mass of the power unit by the center mount, the left and right front mount and rear mount greatly reduce the weight sharing of the power unit, and each mount rubber in the left and right front mount and rear mount The spring constant of the vehicle can be made sufficiently low, the vibration absorbing function is improved, the transmission of the power unit vibration to the vehicle body side can be reduced, and the vehicle interior noise can be reduced.

  However, by setting the spring constants of the left and right front and rear mount rubbers to a low value, if a large acceleration is applied to the vehicle body when starting, winding, acceleration / deceleration, cornering, etc., the inertial force of the power unit The displacement in which the power unit is tilted in the front-rear direction and the left-right direction is increased, which is a factor that affects riding comfort and steering stability. In particular, since the power unit is supported by the vehicle body at a position lower than its center of gravity, the resistance against the tilting of the power unit is small, and it is difficult to suppress the displacement due to the tilting of the power unit. The turning ability is lowered and the driving stability is greatly affected.

  As a countermeasure, in the power unit support structure in which the power unit is supported on the vehicle body side via the mount rubber, the cushion rubber is interposed between the portion above the center of gravity of the power unit and the strut housing disposed on the side frame on the vehicle body side. It is known that by connecting with a support member, the displacement of the power unit is suppressed while maintaining the spring constant of the mount rubber low (see, for example, Patent Document 2).

Japanese Utility Model Publication No. 7-8035 JP 2004-345387 A

  According to Patent Document 2, it is possible to suppress the displacement due to the inclination of the power unit while keeping the spring constant of the mount rubber that supports the power unit on the vehicle body side low. The vehicle interior noise can be reduced by reducing the vibration transmitted to the vehicle, and the displacement of the power unit at the time of winding and cornering can be suppressed by connecting with the support member interposing the cushion rubber.

  However, since the displacement due to the tilt of the power unit is regulated by the spring constant of the cushion rubber provided on the support member laid between the strut housing and the power unit, the suppression of the displacement due to the tilt of the power unit is suppressed by the cushion rubber. Limited by characteristics.

  That is, the displacement of the power unit is gradually increased in association with the increase of the acceleration G as shown by the solid line a in the correlation diagram between the acceleration G acting on the vehicle body during winding running and cornering shown in FIG. 9 and the displacement X of the power unit. It has a characteristic that it continuously increases and the displacement X gradually decreases in conjunction with a decrease in acceleration G. Since the cushion rubber has this characteristic, when a large acceleration G is applied during a sudden winding run or cornering, the displacement X due to the tilt of the power unit increases, which affects the turning performance and steering stability of the vehicle body during turning operations. give. As a countermeasure against this, if the spring constant of the cushion rubber is increased, the displacement X of the power unit when a large acceleration G is applied as shown by the broken line b can be suppressed, but vibration occurs as the spring constant of the cushion rubber increases. There is a concern that the absorption function is lowered, and the vibration of the power unit is transmitted to the vehicle body via the support member to increase the vehicle interior noise. On the other hand, if the spring constant of the cushion rubber is decreased in order to ensure the vibration absorbing function by the cushion rubber, the displacement X of the power unit is reduced even when a small acceleration G is applied at the time of gentle cornering, etc., as indicated by the alternate long and short dash line c. There is concern that it will become larger and affect the turning performance and steering stability.

  Accordingly, an object of the present invention made in view of the above points is to improve the vibration noise performance (silence) and the handling stability of the vehicle, and particularly to ensure the improvement of the turning ability and the handling stability at the time of winding and cornering. An object is to provide a power unit support structure for a vehicle.

The power unit support structure for an automobile according to claim 1, which solves the above-described object, is a power unit support for an automobile in which the power unit disposed between the left and right vehicle body side members arranged opposite to each other is supported by the vehicle body via a mount rubber. in construction, proximal to the vehicle body side member of the right side is supported, gradually other end moves to the rear of the vehicle body is supported on a portion of the above the center of gravity of the power unit in accordance with shifts in the vehicle body width direction center side, and the car The base end is supported by the first support member having a linear piston type hydraulic damper extending in the body width direction and the right side vehicle body side member, and gradually shifts to the front of the vehicle body as moving toward the center side in the vehicle width direction. a second support member the other end provided with a direct-acting piston hydraulic damper is supported above the portion from the center of gravity of the power unit, and extending in the vehicle body width direction Te, the left Proximal to the vehicle body side member is supported, and gradually the other end goes to the rear of the vehicle body is supported above the portion from the center of gravity of the power unit, and extending in the vehicle body width direction in accordance with shifts in the width direction of the vehicle body center side A third support member having a linear piston type hydraulic damper and a vehicle body side member on the left side, and a base end is supported by the left side vehicle body member. It is supported from the center of gravity to the upper portion, and a fourth support member having a linear piston hydraulic damper extending in the vehicle body width direction, comprising the to.

The invention according to claim 2, in the power unit support structure of an automobile according to claim 1, said support member, the proximal end of the direct-acting piston hydraulic damper, coupled to the proximal end of the upper Symbol linear piston hydraulic damper And a first cylindrical bush having a rubber interposed between the outer cylinder and the inner cylinder is disposed at the other end of the linear piston type hydraulic damper. , outer cylinder coupled to the other end of the upper Symbol linear piston type hydraulic damper, the cylinder is supported on the power unit, and a second cylindrical bushing having a rubber interposed between the outer cylinder and the inner cylinder are arranged It is characterized by that.

The invention according to claim 3 is the power unit support structure for an automobile according to claim 1 or 2, wherein the support member is detachably supported by the vehicle body side member and the power unit.

According to a fourth aspect of the present invention, in the power unit support structure for an automobile according to any one of the first to third aspects, the linear motion piston type hydraulic damper is capable of switching the size of the orifice drilled in the piston. It is a switching type direct acting piston type hydraulic damper.

According to the first aspect of the present invention, the power unit is supported by the vehicle body via the mount rubber, and the vehicle body side member and the portion above the center of gravity of the power unit extend in the vehicle width direction and extend in the vehicle body longitudinal direction. By connecting the first to fourth support members having a linear piston type hydraulic damper, the linear piston type can be secured in a stable state when a large acceleration is applied during sudden winding traveling or cornering. Displacement due to the tilting of the power unit is suppressed according to the characteristics of the hydraulic damper , and pitching can be suppressed, and good turning performance and steering stability can be obtained. As the displacement of the power unit is controlled by this direct acting piston type hydraulic damper, it becomes possible to reduce the spring constant of the mount rubber that supports the power unit, reducing the transmission of power unit vibration to the vehicle body side and reducing the noise in the vehicle interior. Reduction can be expected.

According to the second aspect of the present invention, the linear piston type hydraulic damper is supported on the vehicle body side member via the first cylindrical bush and supported on the power unit via the second cylindrical bush, so that the fine vibration of the power unit in particular is reduced. Vehicle body transmission is reduced, and vehicle interior noise can be reduced.

According to the invention of claim 3 , by supporting the support member detachably on the vehicle body side member and the power unit, it can be exchanged with a support member having a direct acting piston type hydraulic damper having different characteristics. The displacement restriction of the inclination of the power unit with respect to the acceleration during cornering can be controlled, and various turning characteristics and steering stability of the vehicle can be adjusted.

According to the invention of claim 4 , since the direct acting piston type hydraulic damper is a characteristic switching type direct acting piston type hydraulic damper capable of switching the size of the orifice, the characteristic of the direct acting piston type hydraulic damper is appropriately switched. As a result, the displacement of the power unit can be suppressed, and the turning ability and steering stability of the vehicle can be variously adjusted.

Hereinafter, the reference examples and the embodiment of the power unit support structure for a vehicle of the present invention will be described with reference to FIG.

( First Reference Example )
A first reference example of the present invention will be described with reference to FIGS. 1 to 6 by taking as an example a case where the power unit is a vertically installed power unit including a horizontally opposed engine. FIG. 1 is a plan view of a front part of a vehicle body showing an outline of a power unit support structure according to this reference example , FIG. 2 is a side view of the main part of FIG. 1, FIG. 3 is a front view of the main part of FIG. It is a disassembled perspective view shown. In each figure, the arrow F indicates the vehicle body front direction, and the arrow W indicates the vehicle body width direction.

  The front part of the vehicle body including the engine room R on which the power unit P in which the horizontally opposed engine E and the transmission TM are unitized is mounted on the left and right side frames 1 and 2 extending in the longitudinal direction of the vehicle body on both sides of the engine room R. The strut housings 3 and 4 are respectively coupled to the side frames 1 and 2 for receiving and supporting the front suspension. The side frames 1 and 2, the strut housings 3 and 4 and the wheel apron and the like form a vehicle body side member having excellent rigidity that continues in the vehicle longitudinal direction along both sides of the engine room R. Although not shown, a cross member that supports the power unit P is installed between the left and right side frames 1 and 2.

  The power unit P supports the almost entire mass of the power unit P via the center mount 5 by arranging the center mount 5 at a position almost directly below the power unit P and attaching the center mount 5 to the cross member.

  Front mounts 6 and 7 are arranged on the left and right portions of the front end of the power unit P, and the left and right front mounts 6 and 7 are attached to left and right vehicle body side members, for example, side frames 1 and 2 via brackets. The rear end portion of the power unit P is supported on the vehicle body member by the rear mount 8.

  In this way, the power unit P is supported on the vehicle body side by the center mount 5, the left and right front mounts 6 and 7, and the rear mount 8. Nearly the entire mass of the power unit P is supported by the center mount 5, and vibrations in the rolling direction are supported. The mass of the power unit P by the front mounts 6, 7 and the rear mount 8 is mainly received by the left and right front mounts 6, and the vibration in the pitching direction is mainly received by the left and right front mounts 6, 7 and the rear mount 8. The sharing is reduced, the spring constants of the mount rubbers of the front mounts 6 and 7 and the rear mount 8 are sufficiently lowered, and the vibration transmission from the power unit P to the vehicle body side is reduced.

A support member extending in the vehicle width direction between a vehicle body side member, in this reference example , a strut housing 3 coupled to the right side frame 1 and a portion Pa of the power unit P above the center of gravity of the power unit P 10 is installed and the support member 10 suppresses displacement due to the tilting of the power unit P.

  The support member 10 installed between the strut housing 3 and the portion Pa of the power unit P is attached to the first bracket 11 coupled to the strut housing 3 and the portion Pa of the power unit P as shown in an exploded perspective view in FIG. The second bracket 15 is coupled to the first bracket 11 and the first bracket 11 and the second bracket 15 are linearly actuated piston-type hydraulic dampers 20 extending in the vehicle width direction.

  The first bracket 11 is substantially U-shaped having a plate-like base portion 12 and a pair of damper attachment portions 13 bent at both ends of the base portion 12. The first bracket 11 has an attachment hole 12 a and a damper attachment portion 13 in the base portion 12. Support holes 13a are respectively drilled, and the base portion 12 is fixed to the mounting portion 3a of the strut housing 3 extending substantially in the vehicle body width direction by mounting bolts 13b.

  The second bracket 15 is substantially U-shaped having a plate-like base portion 16 and a pair of opposing damper mounting portions 17 that are bent at both ends of the base portion 16. The mounting hole 16 a and each damper mounting portion are formed in the base portion 16. 17, support holes 17a are respectively drilled, and the base 16 is fixed to the portion Pa of the power unit P by mounting bolts 16b.

  The linear motion piston type hydraulic damper 20 is slidable by dividing the inside of the tube 21 into a pair of first hydraulic chamber 22a and second hydraulic chamber 22b, for example, as schematically shown in FIG. The first hydraulic chamber 22a and the second hydraulic chamber 22b are filled with oil. The piston 23 is fitted with the orifice 23a and the rod 24 extends from the piston 23 and protrudes from the tube 21. When the rod 24 extends and contracts, the oil passes through the orifice 23a and generates drag when moving from the first hydraulic chamber 22a side to the second hydraulic chamber 22b or from the second hydraulic chamber 22b side to the first hydraulic chamber 22a. Is.

  A first cylindrical bush 26 provided with an outer cylinder 27, an inner cylinder 28, and a rubber 29 interposed between the outer cylinder 27 and the inner cylinder 28 at the end of the tube 21 that is the base end of the linear piston type hydraulic damper 20. Are connected to each other, and a second cylinder 24 is provided with an outer cylinder 31, an inner cylinder 32, and a rubber 33 interposed between the outer cylinder 31 and the inner cylinder 32 at the end of the rod 24 which is the other end of the linear piston type hydraulic damper 20. A cylindrical bush 30 is coupled.

  The first cylindrical bush 26 is inserted between the opposing damper mounting portions 13 of the first bracket 11 fixed to the strut housing 3, and is supported by the support bolts 35 passing through both the support holes 13 a and the inner cylinder 28. A support bolt that is supported by the bracket 11 and the second cylindrical bush 30 is inserted between the opposing damper mounting portions 17 of the second bracket 15 fixed to the power unit P and penetrates both the support holes 17a and the inner cylinder 32. 36 is supported by the second bracket 15 and the linear piston type hydraulic damper 20 is interposed between the strut housing 3 and the upper portion of the power unit P with the first cylindrical bush 26 and the second cylindrical bush 30 interposed therebetween. It is installed and extended.

  According to the power unit support structure configured as described above, the center mount 5 supports almost the entire mass of the power unit P, and the mass sharing of the power unit P by the left and right front mounts 6 and 7 and the rear mount 8 is greatly reduced. The spring constants of the respective mounting rubbers of the left and right front mounts 6 and 7 and the rear mount 8 can be made sufficiently low. By reducing the spring constants of the mount rubbers of the front mounts 6 and 7 and the rear mount 8, the vibration absorbing function is improved, and the vibration of the power unit P transmitted from the power unit P to the vehicle body side is reduced to reduce the vehicle interior noise. Can be planned. Also in the support member 10 installed between the strut housing 3 and the power unit P, the vibration of the power unit P is caused by the vibration absorbing function by the direct acting piston type hydraulic damper 20 and the first and second cylindrical bushes 26 and 30. The vibration of the power unit P transmitted to the side is reduced, and the vehicle interior noise is reduced. In particular, the first cylindrical bushes 26 and 30 reduce the transmission of fine vibrations of the power unit P to the vehicle body via the support member 10.

  On the other hand, the displacement of the power unit P that is tilted due to the inertia force during vehicle winding and cornering is directly applied to the support member 10 that extends between the strut housing 3 and the power unit P and extends in the vehicle width direction. It is regulated by the characteristics of the dynamic piston type hydraulic damper 20, the first cylindrical bush 26 and the second cylindrical bush 30.

  That is, the support member 10 including the direct acting piston type hydraulic damper 20, the first cylindrical bush 26, and the second cylindrical bush 30 is shown by a solid line a in the correlation diagram between the acceleration G and the displacement X of the power unit P in FIG. In a range where the acceleration G is relatively small, the rubber increases mainly according to the spring constants of the first cylindrical bush 26 and the second cylindrical bush 30 but is interposed between the outer cylinder 27 and the inner cylinder 28 of the first cylindrical bush 26. 29 and the rubber 33 interposed between the outer cylinder 31 and the inner cylinder 32 of the second cylindrical bush 30 are relatively thin and are restrained from being deformed as the acceleration G increases, and the acceleration according to the characteristics of the direct acting piston type hydraulic damper 20 Regardless of the increase in G, it remains almost constant.

  Accordingly, when a small acceleration G is applied during gentle cornering, the vibration of the power unit P is transmitted to the vehicle body side by the vibration absorbing function in which the displacement X of the power unit P increases according to the characteristics of the first cylindrical bush 26 and the second cylindrical bush 30. This effectively reduces the noise in the vehicle interior and ensures quietness in the vehicle interior.

  On the other hand, when a large acceleration G acts during a sudden winding run or cornering, the displacement X due to the inclination of the power unit P caused by the inertial force extends between the strut housing 3 and the power unit P in the vehicle width direction. It is constrained by the characteristics of the direct acting piston type hydraulic damper 20 and the first cylindrical bush 26 and the second cylindrical bush 30 of the support member 10 that is stretched over, so that good turning performance and steering stability of the vehicle body can be obtained.

FIG. 6 compares the relative relationship between the acceleration G and the displacement X of the power unit P by the support member 10 including the direct acting piston type hydraulic damper 20, the first cylindrical bush 26, and the second cylindrical bush 30 in this reference example . Therefore, the relative relationship between the acceleration G and the displacement X of the power unit P in a state in which the support member 10 installed between the strut housing 3 and the power unit P is omitted is indicated by a broken line b. A relative relationship between the acceleration G and the displacement X of the power unit P in the above-described conventional structure in which a cylindrical bush is interposed in a support member installed between the portion Pa is indicated by an alternate long and short dash line c.

Therefore, according to the power unit support structure in this reference example, the spring constant of each mount rubber that supports the power unit P can be made sufficiently low, and transmission of power unit vibration to the vehicle body side is reduced to reduce vehicle interior noise. In addition, the direct acting piston type hydraulic damper 20 and the first cylindrical bush 26 and the second cylinder of the support member 10 extending between the strut housing 3 and the power unit P and extending in the vehicle width direction. When a large acceleration G is applied during shock absorption traveling or cornering where the displacement X of the power unit P increases in a range where the acceleration G is relatively small, the first cylindrical bush 26, the second cylindrical bush 30 and the linear motion piston are operated. The displacement X of the power unit P is suppressed according to the characteristics of the hydraulic damper 20 and is good. Fogging and steering stability can be obtained.

  Further, the support member 10 installed between the strut housing 3 and the power unit P is used as a direct acting piston type hydraulic damper 20 having different characteristics, for example, a direct acting piston type having an effective diameter of an orifice 23a formed in the piston 23. By replacing the support member 10 with the hydraulic damper 20, the regulation of the displacement X of the inclination of the power unit P when the acceleration G applied during winding and cornering acts can be controlled, and the turning performance and steering stability of the vehicle can be controlled. Can be adjusted in various ways.

  Further, the size of the orifice 24a formed in the piston 24 is cut by operating the operation unit attached to the linear motion piston type hydraulic damper 20 or the operation unit disposed in the passenger compartment. By using a direct-acting piston type hydraulic damper of the characteristic switching type, the displacement X of the power unit P can be appropriately adjusted to adjust the turning performance and steering stability of the vehicle.

Further, a support member 10 can be additionally disposed between the strut housing 3 and the power unit P of an existing vehicle.

( Second reference example )
The second reference example of the present invention will be described with reference to FIG. FIG. 7 is a plan view of the front portion of the vehicle body showing an outline of the power unit support structure according to this reference example corresponding to FIG. 1 of the first reference example . In FIG. 7, parts corresponding to those in FIGS. 1 to 5 are denoted by the same reference numerals, and detailed description thereof is omitted.

In the present reference example , the support member 10 is installed between the right strut box 3 and the portion Pa of the power unit P in the same manner as in the first reference example, and is further supported at the same position in the longitudinal direction of the vehicle body. 10 is constructed on the left strut box 4 and the portion Pa of the power unit P, and other configurations are the same as those of the first reference example .

According to this reference example , the support members 10 extending in the vehicle width direction are arranged symmetrically with respect to the center in the vehicle width direction, and between the strut box 3 and the power unit P and between the strut box 4 and the power unit P. by erection disposed between, in addition to the first exemplary embodiment, in a state of excellent stability to the left and right balance, when a large acceleration G of the isochronous winding travel and cornering is applied, each arranged on the left and right The displacement X of the power unit P can be suppressed in accordance with the characteristics of the direct acting piston type hydraulic damper 20, the first cylindrical bush 26, and the second cylindrical bush 30 of the support member 10, and it is more stable and more stable than the first reference example. Performance and steering stability.

Also in this reference example , the left and right linear piston type hydraulic dampers 20 are arranged with the size of the orifice 24a formed in the piston 24 in the operation unit attached to the linear piston type hydraulic damper 20 or in the passenger compartment. It was with cutting switched characteristic switchable type linear piston type hydraulic damper through operation via the operation section, the displacement X of the power unit P with suitable Mubecho integer to various adjusted turning property and steering stability of the vehicle Can be configured.

( Embodiment )
Embodiments of the present invention will be described with reference to FIG. FIG. 8 is a plan view of the front portion of the vehicle body showing an outline of the power unit support structure according to the present embodiment corresponding to FIG. 1 of the first reference example . In FIG. 8, parts corresponding to those in FIGS. 1 to 5 are denoted by the same reference numerals, and detailed description thereof is omitted.

This embodiment, between the upper portion of the side frame 1 and the power unit P, the process proceeds to the proximal end on the right side of the side frame 1 moves to and is supported vehicle width direction center side thus gradually to the rear of the vehicle body and the other end There a first support member 10a that is supported above the part Pa from the center of gravity of the power unit P, is supported the proximal end on the right side of the side frame 1 or strut housing 3, thus progressively vehicle front to migrate in the width direction of the vehicle body center side a second support member 10b that the other end moves is supported on portion Pa of the power unit P, the proximal end on the left side of the side frame 2 is supported, transition to migrate in the width direction of the vehicle body center side thus gradually to the rear of the vehicle body The other end is supported by the third support member 10c supported by the portion Pa of the power unit P, and the base end is supported by the left side frame 2 or the strut housing 4. Characterized in that a fourth support member 10d which is supported in the direction central side, and the other configuration is the same as the first embodiment. The first to fourth support members 10a to 10d are configured similarly to the support member 10 of the first reference example .

  According to this embodiment, between the side frame 1 and the power unit P and between the side frame 2 and the power unit P, the first to fourth support members 10a to 10d are arranged in an X shape symmetrically about the center in the vehicle body width direction. By erection, in addition to the first embodiment, when a large acceleration G acts during winding driving or cornering in a stable state with excellent left-right balance, displacement of the power unit P can be suppressed, More stable and good turnability and handling stability can be obtained.

  In addition, the support members 10a to 10d arranged to be inclined with respect to the traveling direction can restrict the displacement of the power unit in the front-rear direction at the time of starting or acceleration / deceleration, that is, pitching.

The present invention is not limited to the form of the above you facilities, various modifications are possible without departing from the scope of the invention. For example, in the above-described embodiment, the power unit is disposed at the center mount 5 disposed almost immediately below the power unit P, the front mounts 6 and 7 disposed at the left and right portions of the front end of the power unit P, and the rear disposed at the rear end portion of the power unit P. Although the power unit P is supported on the vehicle body member by the mount 8, the power unit P is supported on the vehicle body member by the front mount disposed at the left and right portions of the front end of the power unit P and the rear mount disposed at the rear end portion of the power unit. In the power unit support structure that supports the power unit, the support member may be installed between the vehicle body side member and the power unit. In the above embodiment, an example of the power unit P including a horizontally opposed engine has been described. However, a power unit including a V-type engine or another type of engine can be similarly configured.

It is a top view of the vehicle body front part which shows the outline | summary of the power unit support structure of a 1st reference example . It is a principal part side view of FIG. It is a principal part front view of FIG. It is a disassembled perspective view which shows the principal part. It is a figure which shows a direct acting type piston type hydraulic damper typically. It is a correlation diagram of the displacement of an acceleration and a power unit. It is a top view of the vehicle body front part which shows the outline | summary of the power unit support structure of the 2nd reference example . It is a plan view of a vehicle body front illustrating an outline of implementation in the form of a power unit support structure of the present invention. It is a correlation diagram of the displacement of an acceleration and a power unit.

Explanation of symbols

P Power unit 1, 2 Side frame (vehicle body side member)
3, 4 Strut housing (vehicle body side member)
3a Mounting surface 5 Center mount 6, 7 Front mount 8 Rear mount 10 Support members 10a to 10d First to fourth support members 11 First bracket 15 Second bracket 20 Direct acting piston type hydraulic damper 23 Piston 23a Orifice 26 First cylinder Bush 27 Outer cylinder 28 Inner cylinder 29 Rubber 30 Second cylindrical bush 31 Outer cylinder 32 Inner cylinder 33 Rubber

Claims (4)

In a power unit support structure of an automobile in which a power unit disposed between left and right vehicle body side members disposed opposite to each other is supported by the vehicle body via a mount rubber,
Supported the base end to the vehicle body side member of the right, gradually other end moves to the rear of the vehicle body is supported above the portion from the center of gravity of the power unit, and vehicle body width direction in accordance with shifts in the vehicle body width direction center side A first support member comprising a linear piston type hydraulic damper extending to
Proximal to the vehicle body side member of the right side is supported, the other end and gradually moves to the front of the vehicle body in accordance with shifts in the width direction of the vehicle body center side is supported above the portion from the center of gravity of the power unit, and the vehicle body width direction A second support member comprising a linear piston-type hydraulic damper extending;
Proximal to the vehicle body side member of the left is supported, the other end and gradually moves to the rear of the vehicle body in accordance with shifts in the width direction of the vehicle body center side is supported above the portion from the center of gravity of the power unit, and the vehicle body width direction A third support member comprising a linear piston-type hydraulic damper extending;
Proximal to the vehicle body side member of the left is supported, the other end and gradually moves to the front of the vehicle body in accordance with shifts in the width direction of the vehicle body center side is supported above the portion from the center of gravity of the power unit, and the vehicle body width direction A fourth support member comprising a linear piston-type hydraulic damper extending;
A structure for supporting a power unit of an automobile. The support member is
The proximal end of the direct-acting piston hydraulic damper, the outer tube coupled to the proximal end of the upper Symbol linear piston type hydraulic damper, the cylinder is supported on the vehicle body side member, and between the outer cylinder and the inner cylinder A first cylindrical bush with an interposed rubber is disposed;
The other end of the linear piston type hydraulic damper rubber interposed between the upper Symbol outer cylinder coupled to the other end of the linear piston type hydraulic damper, the cylinder is supported on the power unit, and the outer cylinder and the inner cylinder The power unit support structure for an automobile according to claim 1, wherein a second cylindrical bush including The support member is
The power unit support structure for an automobile according to claim 1 or 2, wherein the structure is detachably supported by the vehicle body side member and the power unit.   4. The direct acting piston type hydraulic damper according to claim 1, wherein the direct acting piston type hydraulic damper is a characteristic switching type direct acting piston type hydraulic damper capable of switching a size of an orifice bored in the piston. The automobile power unit support structure described.

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