JPS59124433A - Power unit supporting, drive wheel driving and suspending devices for vehicle - Google Patents

Abstract

PURPOSE:To aim at simplifying the structure of a power unit and as well at making the same compact, by providing such an arrangement that drive wheels are carried by a power unit casing which is rigidly formed, and as well by swingably coupling the casing with a vehicle body frame through a suspension spring. CONSTITUTION:The casing 70 of a power unit P is rigidly formed such that a crank case 50 in which the crankshaft and output shaft of an engine E, etc. are disposed, is integrally incorporated with a pair of mission casings 71, 71' which extend rearward from the left and right sides of the crank case 50 to contain therein automatic transmission units M, M'. A pivot shaft 83 laid in parallel with the crankshaft, is supported to supporting brackets 74 through 77 which are integrally formed with the outer surface of the casing 70 and which project therefrom. The power unit P is swingably coupled to a vehicle body frame F by means of the pivot shaft 83. Further, the pivot shaft 83 is journalled, at positions between both outermost supporting brackets 74, 77, to left and right supporting plates 1a, 1a' on the vehicle body frame F through a pair of left and right suspension spring Sb, Sb'.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a power unit, a drive wheel drive, and a suspension system in a vehicle equipped with a pair of left and right drive wheels.

Conventionally, in a vehicle that has a pair of left and right drive wheels, such as a four-wheeled vehicle, the power unit support device, the drive wheel drive device, and the suspension device are each independent, but these devices share components with each other. If it were possible to configure the device in an integrated manner, it would be extremely beneficial for simplifying and downsizing the entire device.

The present invention was made based on this idea, and aims to provide the above-mentioned device that is simple in structure, compact, and robust. A pair of transmission devices and a horizontal power unit are configured to individually transmit power to both driving wheels, and a casing of the power unit is formed into a rigid body to support both driving wheels, and a plurality of support brackets are protruded from the casing. A pivot shaft extending in the arrangement direction of both driving wheels is supported between these support brackets and a plurality of support caps bolted to these support brackets, and the casing is attached to the vehicle body frame via this pivot shaft. These casings and the vehicle body frame are connected to each other so as to be swingable, and a suspension spring device is interposed between the casing and the vehicle body frame, and the mating surfaces of each set of the support bracket and the cap connected by bolts are shifted from each other in phase in the circumferential direction of the pivot shaft. It's there.

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

First, in FIGS. 1 to 3, the illustrated vehicle has a pair of left and right drive wheels W'f, 'f' and a power unit P that drives them at the front part of the vehicle body frame F, and one at the rear part of the vehicle body frame F. A driven wheel Wr is provided, respectively.

The vehicle body frame F includes a pair of left and right vertical members 1, 1' with support plates 1α l (Z/) erected at each front end, and a plurality of horizontal members 2, 3, 4.5 that connect these vertical members in a ladder shape. , a pair of reinforcing members 6, 6' connecting the two intermediate horizontal members 3, 4.
and three inverted U-shaped roll pars γ connected to the front, center and rear parts of the longitudinal members 1 and 1',
8, 9, and the front roll par 1. The frontmost cross member 2 and the left and right support plates 1α, 1a′ are connected via a cross-shaped reinforcing member 10, and the tops of the central roll par 8 and rear roll par 9 are connected via a reinforcing member 11. be done. A steering column supporting a steering steering wheel 13 is attached to the center of the front roll par 1.

Said pair of reinforcing members 6 along the center line between both longitudinal members 1, 1'
, 6', a fuel tank 12 is disposed between them.

The fuel tank 12 is bolted to the cross member 3 and both arm reinforcements 6, 6'.

A floor plate 16 is attached to the lower surface of the vehicle body frame F, and a front seat 14 for the driver and a passenger A are attached to the upper surface of the floor plate 16.
A rear seat 15 is installed for the vehicle, and the backrests 14α, 15α are arranged substantially along the center rollper 8 and the rear rollper 9, respectively. Of course, these rollpers 8 and 9 are the pilot and passenger A.
are preselected to a height that passes over each of the above.

In FIGS. 4 to 6, the power unit P consists of an engine E and a pair of left and right belt-type automatic transmissions M, Ml arranged on both sides of the rear of the engine.
M' is equipped with a reduction gear mechanism R on the output side. These automatic transmissions M and Ml constitute the transmission device of the present invention.

The engine E has its crankshaft 20 in the left and right direction of the vehicle.
That is, both driving wheels Wf and Wfl are arranged in the direction in which they are arranged, and the crankshaft 20 has an output shaft 21 on one side, and a primary inertia force balancing shaft 22 and a pump drive shaft 23 on the other side. and a starting motor 24 are respectively arranged parallel to the crankshaft 2o. A generator 2 is attached to one end of the crankshaft 20.
5, and a centrifugal automatic start clutch 26 is attached to the other end, and a forward/reverse switching device 21 is provided between the clutch 26 and the output shaft 21.

This device 21 includes a drive gear 28 fixed to the output member of the clutch 26, a relay gear 29 rotatably supported by the output shaft 21 and always in mesh with the drive gear 28, and a crankshaft 20.
A small-diameter idle gear 31 rotatably supported on an idle shaft 30 parallel to the drive gear 28 and always meshing with the drive gear 28, a large-diameter idle gear 32 integrally connected to the small-diameter idle gear 31, and a relay gear 29 and a large-diameter It is comprised of a switching gear 33 that is slidably spline-fitted to the output shaft 21 adjacent to the idle gear 32. The switching gear 33 is
It can move along the output shaft 21 between a forward position on the right and a reverse position on the left in FIG. The switching gear 33 and the relay gear 29 are provided with a dog clutch consisting of a dog 34 and a dog hole 35 that can be engaged with each other, and in the backward position, the dog clutch 34, 35 is released and the switching gear 33 is rotated. It is designed to mesh with a diameter idle gear 32.

Therefore, when the switching gear 33 is placed in the forward position, the rotational torque of the crankshaft 20 is transferred to the starting clutch 26, the driving gear 28,
The signal is transmitted to the output shaft 21 through the relay gear 29 and the switching gear 33 in order, and can be rotated in the normal direction. Furthermore, if the switching gear 33 is shifted to the reverse position, the rotational torque is transferred to the starting clutch 26, the drive gear 28, the small diameter idle gear 31,
The signal is transmitted to the output shaft 21 through the large-diameter idle gear 32 and the switching gear 33 in order, and can be reversed.

An annular engagement groove 36 is provided on the outer periphery of the boss portion of the switching gear 33, and a shift fork 38 that is slidably supported on a guide shaft 3T parallel to the crankshaft 20 is provided in this groove 36.
The projection 38α of the boss portion of the shift fork 38 is further engaged with the cam groove 39α of the shift drum 39, which is disposed parallel to the guide shaft 3T. The shift drum 39 has a shift lever 40 fixed to one end thereof.
When the cam groove 39 is rotated in one direction or the other direction by
The switching gear 33 can be shifted to the forward position or the backward position by displacing the shift fork 38 to the right or left by the guiding action of α.

The -order inertia force balancing shaft 22 is connected to drive gears 41 having the same diameter.
and is synchronously rotated from the crankshaft 20 via the driven gear 42. This balance shaft 220 weight 22 (Z is provided at a position where it enters between a pair of opposing crank webs 20 (Z, 20α) when approaching the crankshaft 20, but the engine E due to this weight 22α Since the primary inertial force balancing effect is well known, its explanation will be omitted.

The pump drive shaft 23 is driven by the crankshaft 20 via a chain transmission 43. A lubricating oil pump 44 is connected to one end of the pump drive shaft 23, and a cooling water pump is connected to the other end, and the water pump 45 can be easily attached and detached as follows.

That is, the rotary shaft 4T having the impeller 46 of the water pump 45 is connected to the pump drive shaft 23 via a removable joint 48, and the pump housing 49 that supports the rotary shaft 4T and houses the impeller 46 is It is fixed to the crankcase 50 of the engine E with bolts 51. Therefore, by removing the bolts 51, the water pump 45 can be easily taken out from the engine E, which is convenient for maintenance.

Incidentally, when the engine E is an air-cooled type, the water pump 45 is removed in this way, and an appropriate blind cover is provided on the opening of the crankcase 50 behind the pump housing 49.

As shown in FIGS. 5A and 5B, a signal protrusion 52 of the ignition balsa is provided on the outer peripheral surface of the rotor 25α of the generator 25.
is protruding, and the pickup coil 5 of the ignition pulsar
3, its base plate 53α is attached to the crankcase 5 so as to face the turning path of the signal protrusion 52 with a certain gap therebetween.
It is fixed to a fixed support base 54 in 0 with bolts 55. In order to facilitate the position adjustment and attachment/detachment of this pickup coil 53, a working window 56 is provided in the end wall of the crankcase 50 facing the pickup coil 53, and this window 56 is normally closed by a cap 5T. Output shaft 21 of automatic transmission M, J/'l engine E
0 both ends and left and right drive wheels 11J.

ff/ are arranged so as to be connected to each other. Therefore, the driving wheels Wf and Wf' on both sides are connected to automatic transmissions M and Wf', respectively.
It is connected in parallel to the output shaft 21 via M'.

Since the belt type automatic transmissions M and Mf have the same structure, only the structure of the one on the left H will be explained.

A variable diameter drive pulley 58 is attached to the end of the output shaft 21, and a variable diameter driven pulley 59 is attached to the driven shaft 61, which is the input shaft of the reduction gear mechanism R.
An endless belt 60 is stretched between 9 and 9. Drive pulley 58
The driven pulley 59 is equipped with a centrifugal mechanism 62 that operates to increase its effective diameter as its rotational speed increases, while the driven pulley 59 is equipped with a spring 63 that constantly operates to increase its effective diameter. Due to the interaction of the mechanism 62 and the spring 63, the gear ratio between the output shaft 21 and the driven shaft 61 is automatically decreased as the rotational speed of the output shaft 210 increases.

A wheel drive shaft 65 is provided at the outer end of the output shaft 64 of the reduction gear mechanism R.
is spline-coupled, and further to this wheel drive shaft 65,
An axle 6T fixed to a hub 65 of a drive wheel Wf is connected via a constant velocity joint 68. Therefore, the power that has been shifted and transmitted to the driven shaft 61 is appropriately torque amplified by the reduction gear mechanism R, and then transmitted to the axle 61 via the wheel drive shaft 65 and the constant velocity joint 68 to drive the drive wheel Wf. do.

Since the left and right driving wheels If, Wf/ are connected in parallel to the output shaft 21 via such automatic transmissions M, Ml, both driving wheels Wf are connected to each other due to turning of the vehicle or the like.

When a rotational speed difference occurs in ff/, a difference occurs in the gear ratios of both automatic transmissions M and IW, and as a result, the output shaft 2
The output torque of 1 is distributed to both driving wheels If, IFf/ according to their rotational speeds. That is, the automatic transmissions M and W can not only each perform a normal speed change function, but also work together to perform a differential function.

C17- The casing 70 of the unit P is
A crankcase 50 accommodates and supports a crankshaft 20, an output shaft 21, etc., and an automatic transmission M extending rearward from both left and right ends of the crankcase 50.

A pair of mission cases 11゜11 that accommodate and support M'
The transmission cases 71 and 71' are arranged substantially horizontally so as to be sandwiched between the left and right sides of the front end of the vehicle body frame F. In this way, the space between the two transmission cases γ1°11' can be effectively used as a vehicle body space, making the vehicle more compact and contributing to lowering the center of gravity of the power unit P.

Crank case 50 and each transmission case 11゜γ1/
There is a partition wall 12 between them that partitions them in an oil-tight manner, and inside each transmission case 71, 71' there are each automatic transmission M,
Ml's both boos! A partition wall γ3 that oil-tightly partitions between the transmission mechanism including the transmission mechanisms M and Ml including 58 and 59 and the reduction gear mechanism R is provided as a lubrication method.
The transmission mechanism uses a dry type, and the reduction gear mechanism R uses a wet type.

The casing TO is divided into several blocks and cast as follows. That is, the central part of the crankcase 50, the intermediate part between the central part and each transmission case 11° 11', and the central part of each mission case 71° 71' are divided along a plane perpendicular to the axis of the crankshaft 20. The blocks thus divided are called first to sixth blocks 10, to 106 from the left in FIG. These blocks γ0
．． ~70e are bolted together between adjacent comrades.

Support brackets 14 to 77 are integrally provided on the outer surfaces of the second to fifth blocks 10□ to γ03, respectively, and support brackets 14 to 77 are integrally provided, and support caps are connected to these support brackets 74 to T7 through through bolts γ8, respectively. A single pivot shaft 83 arranged parallel to the crankshaft 20 is sandwiched between the support brackets 19 to 82 in order to connect the work unit P to the vehicle body frame F. ~γ
1 and the support caps 19 to 82 are each formed into a semicircular shape that is easy to process and can be brought into close contact with the circumferential surface of the pivot shaft 83, and each through bolt is used to position and securely fix the pivot shaft 3 to the casing 10. γ8 is passed through the pivot 83. Thus, the second to fifth blocks 102~
γ06 is also connected to each other by the pivot 83, increasing the bonding strength.

Furthermore, each set of support bracket and cap γ4゜19
: γ5, 80; 76.81; 77.82 mating surfaces are:
They are formed to be out of phase with each other in the circumferential direction of the pivot shaft 830. In this way, the relatively weak portions of the support brackets 14 to γγ and the plurality of through bolts 18 are not biased in one direction, and the pivot shaft 83 can be firmly supported in all directions.

The pivot 83 connects a pair of left and right suspension spring devices Sf inside the support bracket 14°1γ in the bilateral position.

The left and right support plates 1a of the vehicle body frame F via Sf'.

1α'. In the illustrated example, the suspension spring device Sf.

5f/ is constructed in the Knight-Nord type and they have the same structure, so only the one on the left Sf will be explained. As shown in FIG. The crank 90 has a flat spring chamber 91 and has a basic hexagonal cross-sectional shape.
Spring operating body 92 accommodated in spring chamber 91 and spring chamber 91
It consists of six cylindrical rubber springs 93 filled between a housing 90 and a spring operating body 92 at six corners, and the spring operating body 92 is fixed to the pivot shaft 83 by multi-face fitting or spline fitting. A mounting flange 94 is integrally formed on the outer peripheral surface of the housing 90 and projects over half the circumference thereof.

On the other hand, the support plates 1α, 1α of the vehicle body frame F! A semicircular support recess 95 that opens toward the front is formed in the recess 95, and the housing 90 is fitted into the recess 95, and the mounting flange 94 is fixed to the support plates 1α and 1α' with a plurality of bolts 96. Ru.

Thus, the power unit P serves as the left and right driving wheels If.

, if it swings around the axis 83 with the vertical movement of ffl,
The spring actuating body 92 rotates with respect to the housing 90 to apply compressive deformation to all the rubber springs 93 at the same time, and the repulsive force of the rubber springs 93 caused by the deformation causes the drive wheels If, I
f' is elastically suspended. By the way, since the casing γ0 of the power unit P constitutes a rigid body as described above and connects both driving wheels Wf and WfI, it has a stabilizer function that suppresses the vertical vibration of one driving wheel by the other driving wheel. You will be prepared.

In order to damp the vertical movement of both driving wheels Wf and IFfl,
A hydraulic damper 9T is interposed between each of the support plates 1α, 1α' of the vehicle body frame F and the transmission case 71, 71'. - The pivot shaft 83 is arranged to pass through the center of gravity of the power unit P. In this way, the driving wheel TF'f.

The moment of inertia of the swing system around the pivot 83 consisting of ff/ and the power unit P can be significantly reduced,
As a result, the road surface followability of the driving wheels WftWf' is improved, and the Neidhardt type spring device Sf.

The load burden of 5f/ is reduced.

Furthermore, in order to reduce the moment of inertia, in the illustrated example, the balancing shaft 22, the starter motor 24, and the water pump 45, which are relatively heavy, are connected to the drive wheel If.

It is placed at the front of engine E to balance the weight of Wfl. Note that arranging the water pump 45 at the front of the engine E is convenient because its maintenance can be performed without being obstructed by the vehicle body frame F.

A support cylinder 100 surrounding the wheel drive shaft 65 is integrally formed on the outer surface of each mission case γ1, 11', and an outer cylinder 101 rotatably supported by this support cylinder 100 includes:
A pair of king pins 10 whose knuckles 102, which rotatably support the hubs 66 of the corresponding drive wheels Wf, If', are coaxially arranged with the center of swing of the constant velocity joint 68 in between.
3, and the knuckle 102 is connected to the steering handle 13 via a steering mechanism (not shown).

Therefore, by rotating the steering handle 13 to rotate the knuckle 102 around the king pin 103, the driving wheels If and Wfr can be turned.

Further, the knuckle 102 has a corresponding drive wheel If.

The back plate 1 104 of the brake device B (drum type in the illustrated example) of Wf' is fixed, and this back plate 1
In order to suppress the 040 rotation, a restraining arm 105 protruding from the outer surface of the outer cylinder 101 is connected to the vehicle body frame F via a torque rod 106. Therefore, during braking, the braking torque acting on the back plate 104 is
It is supported by the vehicle body frame F via the outer cylinder 101 and the torque rod 106. In addition, the axis 83 of the power unit P
Relative rotational displacement between the outer tube 101 and the support tube 100 connected to the knuckle 102 is allowed so that the proper alignment of the drive wheels Wf, Wfl is maintained during rotation.

A rear fork 111 is pivotally attached to the rear end of the vehicle body frame F via a pivot shaft 110 so as to be able to swing vertically, and the driven wheel Wr is pivotally supported at the rear end of the rear fork 111 . In order to suspend the rear fork 111, a spring device Sr having the same structure as the Neidhardt type spring device Sf is installed between the pivot shaft 110 and the rear fork 111.
is interposed.

Further, a hydraulic damper 112 is interposed between the rear fork 111 and the vehicle body frame F to damp the vertical movement of the driven wheel Wr.

As described above, according to the present invention, a power unit is constituted by an engine and a pair of transmission devices that individually transmit the power of the engine to a pair of left and right drive wheels, and the casing of the power unit is formed into a rigid body. supporting said both driving wheels, and allowing vertical movement of said driving wheels;
The casing is swingably connected to the vehicle body frame via a pivot fixed thereto, and a suspension spring device is interposed between the casing and the vehicle body frame, so that the casing of the power unit serves as a swing arm for suspending the drive wheel. It is able to perform its functions and oscillate as the drive wheels move up and down.
Therefore, there is no need to provide a special swing arm,
Furthermore, since the casing can also perform a stabilizer function and suppress the vibration of each drive wheel, there is no need to provide a special stabilizer, and as a result, the structure of the entire device can be simplified and made more compact.

Further, in order to support the pivot shaft, mating surfaces of a plurality of support brackets protruding from the casing and a plurality of support caps bolted to these support brackets are shifted from each other in the circumferential direction of the pivot shaft. Therefore, even if each tie bolt has a weak part, that part will not be biased in one direction, and will firmly support the pivot in all directions, contributing to strengthening the swinging connection structure between the power unit and the vehicle frame. can.

The suspension spring device is not limited to the Neidhard type as in the above embodiment, but may be a coil spring type interposed between the vehicle body frame and the transmission case, such as a hydraulic damper. You can also do that.

[Brief explanation of drawings]

1 to 7 show an embodiment of the present invention,
Fig. 1 is a perspective view of the separated body frame and power unit of the vehicle, Figs. 2 and 3 are a plan view and side view of the vehicle, Fig. 4 is a side view of the power unit, and Fig. 5 is the power unit. 5A is an enlarged vertical sectional view of the engine part of the power unit, FIG. 5B is a sectional view taken along the line VB-VB of FIG. 5A, and FIG. 6 is a side view of the power transmission system of the engine. Figure 7 is an enlarged cross-sectional view taken along the line ■-W in Figure 5. E...engine, F...body frame, M, M/...
...Automatic transmission constituting the transmission device, P...Power unit, Sf, Sf'...Suspension spring device, IP'f,
If'... Drive wheel γ0... Casing, 14-T1... Support bracket, γ8... Bolt, 19-82... Support cap, 83... Axis patent applicant Honda Motor Co., Ltd.

Claims (1)

[Claims] In a vehicle equipped with a pair of left and right driving wheels, a power unit is constituted by an engine and a pair of transmission devices that individually transmit the power of the engine to the two driving wheels, and the casing of the power unit is formed into a rigid body. A plurality of support brackets are protruded from the casing, and a plurality of support caps bolted to the support brackets are provided between the support brackets and a plurality of support caps bolted to the support brackets. The casings support a pivot shaft extending in the arrangement direction, are swingably connected to the vehicle body frame through the pivot shaft, and a suspension spring device is interposed between the casings and the vehicle body frame, and each set is connected by bolts. A power unit support, drive wheel drive, and suspension device for a vehicle, wherein mating surfaces of the support bracket and the cap are offset from each other in the circumferential direction of the pivot shaft.