JP2994368B1 - Starting device for vehicle engine - Google Patents

Abstract

An object of the present invention is to reduce the distance between a freewheel gear and a starting drive gear arranged side by side with a one-way clutch therebetween in a starting device for a vehicle engine, thereby achieving a compact engine width. . SOLUTION: An inner ring 56 formed on a free wheel gear 36 is extended along an outer periphery of a boss portion 50 of the starting drive gear 35 into an annular concave portion 51 of the starting drive gear 35, and an outer periphery of the starting drive gear 35 is provided. A one-way clutch cam 60 is arranged between the outer ring 52 formed at the end and the inner ring 56 so that the bearing 53 of the boss 50 overlaps the axial position. As a result, the axial distance between the free wheel gear 36 and the starting drive gear 35 is reduced, and the starting motor 33 having the small idle gear 67 and the large idle gear 68 connected to the free wheel gear 36 and the output gear 34.
Are not greatly shifted to one side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a starting apparatus for a vehicle engine provided with a starting gear train for transmitting a starting torque from a starting motor to a crankshaft, and more particularly, to a starting gear train in a starting gear train. The present invention relates to a starting device for a vehicle engine in which a starting drive gear that constantly idles due to rotation of a shaft and a free wheel gear are arranged on the same support shaft via a one-way clutch.

[0002]

2. Description of the Related Art As a conventional example, there is a starting device described in Japanese Utility Model Publication No. 2-18284, in which a holder 110 having a flange 108 is fixed to an end of a crankshaft 101 as shown in FIG. A generator rotor 109 is fixed to one side surface of the collar portion 108, and a starting free wheel gear 111 is arranged at an axial distance from the other side surface. , A one-way clutch is interposed. The free wheel gear 111 is fixed to a boss portion 112 rotatably fitted to the crankshaft 101, and meshes with the idle small gear 117 of the starting gear train.

[0003] The one-way clutch includes an outer ring 105 fixed to the other side surface of a collar portion 108 and a free wheel gear 11.
An inner ring 112a extending in the axial direction from the boss portion 112 to the flange portion 108 side, and a one-way clutch cam 107 disposed between the inner ring 112a and the outer ring 105.
The torque is transmitted only to the motor.

[0004]

In the prior art shown in FIG. 4, a one-way clutch and a free wheel gear 111 for starting are arranged in parallel between a generator rotor 109 and a main bearing housing 103.
And the engine width is increased. Further, a large space for accommodating the cam member is provided between the free wheel gear 111 and the flange portion 108, which also promotes an increase in the crankshaft width.

On the other hand, a free wheel gear and a starting drive gear are arranged side by side via a one-way clutch on a support shaft different from the crankshaft, and the starting drive gear is connected to the starting gear of the crankshaft. The one-way clutch can be eliminated from above the crankshaft, and the width of the crankshaft itself can be reduced.

However, the space between the freewheel gear and the starting drive gear must have a large cam accommodating space on the support shaft in the same manner as the space between the collar portion and the freewheel gear in FIG. It does not change. However, since the axial position of the starting gear on the crankshaft is fixed and cannot move, the axial position of the starting drive gear meshing with the starting gear is also fixed,
As described above, when the axial width of the starting drive gear and the free wheel gear is increased, the axial position of the free wheel gear must be farther away in the axial direction from the position of the starting gear.

In this case, the axial positions of the starting motor having the small idle gear, the large idle gear connected to the free wheel gear, and the output gear are sequentially shifted to one side in the axial direction, and the axial width of the engine is reduced. It becomes difficult to make it compact.

If the sliding portion of the cam member of the one-way clutch is axially separated from the bearing of the starting drive gear that always idles, the bending load applied to the bearing by centrifugal force due to the unbalance between the one-way clutch and the outer ring. Therefore, in order to ensure a smooth idle operation by the bearing, the entire length of the boss portion and the entire length of the bearing must be increased.

[0009]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, an invention according to claim 1 of the present application is to start a vehicle engine that starts a crankshaft from a starting motor via a starting gear train having a one-way clutch. In the device, the starting drive gear that always idles due to the rotation of the crankshaft and the free wheel gear are arranged side by side on the same support shaft, and the outer peripheral end of the starting drive gear projects toward the free wheel gear. The outer ring for the one-way clutch is integrally formed, the boss portion extending toward the freewheel side is integrally formed at the inner peripheral end of the starting drive gear, and the freewheel gear is formed on the web of the starting drive gear. An annular recess is formed that opens toward the outer ring and connects to the annular space between the outer ring and the boss, and the boss is rotatably supported on a support shaft via a bearing, and is formed on the inner periphery of the free wheel gear. Is An inner ring for a one-way clutch is formed integrally with the outer peripheral surface of the boss portion of the starting drive gear, which extends toward the moving drive gear and is opposed to the outer peripheral surface of the boss portion with a radial gap therebetween, and the bearing and the shaft are interposed between the inner ring and the outer ring. A one-way clutch is formed by arranging cam members for the one-way clutch such that the positions in the directions overlap.

[0010] The starting torque of the starting motor is transmitted from the free wheel gears of the starting gear train to the starting drive gear on the crankshaft side via the one-way clutch to start the crankshaft. After the start, during the operation of the engine, only the start drive gear idles with the crankshaft, and the free wheel gear is stopped. During the idle rotation, the cam member of the one-way clutch and the outer ring rotate at a high speed, and centrifugal force is generated due to imbalance.However, since the cam member and the outer ring overlap with the axial position of the bearing, the cam member and the outer ring are not rotated. On the other hand, no excessive bending load is applied, the starting drive gear idles smoothly, and the cam member also slides smoothly.

According to a second aspect of the present invention, in the vehicle engine starter according to the first aspect, an oil passage is formed in the support shaft to reach a bearing on the inner peripheral surface of the boss portion, and the axial direction of the boss portion is formed. The gap between the end face and the axial end face of the free wheel gear, the gap between the inner peripheral face of the boss portion and the outer peripheral face of the inner ring, and the gap between the axial end face of the inner ring and the bottom face of the annular concave portion allow the bearing to move from the bearing to the cam member sliding portion. It constitutes a lubricating oil path leading to.

Thus, while the starting drive gear idles, the sliding parts of the bearing and the cam member are efficiently lubricated by the centrifugal force.

[0013]

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a schematic cross-sectional view of a four-cylinder engine for a motorcycle to which the present invention is applied (a schematic cross-sectional view corresponding to a II-II section in FIG. 3). Since it extends in the left-right direction, the direction of the crankshaft center line O1 will be described below as the left-right direction. The cylinder block 4 includes first to fourth cylinders 3-1, 3-2, 3-cylinders.
3, 3-4, and is coupled to the upper end of the crankcase 2, and a piston 11 is fitted into each of the cylinders 3-1, 3-2, 3-3, 3-4. Crankcase 2
The main bearing housing 5 is positioned between the left and right ends and each cylinder.
Each journal 7 of the crankshaft 1 is rotatably supported on each main bearing housing 5 via a bearing metal.

The crankshaft 1 includes first to fourth cylinders 3
-1, 3-2, 3-3, 3-4, the crank pin 6, the journal 7, and a crank web (crank arm) 8-1, which integrally connects the crank pin 6 and the journal 7 to each other. 8-2, 8-3, 8-4, 8-5, 8
-6, 8-7 and 8-8. Each crank pin 6 is pivotally connected to each piston 11 via a connecting rod 10.

A rotor 15 for a generator is fixed to one end, for example, the left end of the crankshaft 1, and a cam chain drive gear 16 is integrally formed at the other end. Of the crank webs 8, the rightmost crank web 8-8 is
A primary gear 20 for driving a wheel is directly toothed on the outer peripheral surface thereof, and the primary gear 20 is formed on a shift input gear 21 of a transmission gear mechanism. Are engaged.

In addition to the wheel driving primary gear 20, the right crank web 8-6 for the third cylinder is also formed in a circular shape with the crank axis O1 as the center, and the starting gear 23 is directly toothed on the outer peripheral surface. It has been cut. The starting gear 23 meshes with a starting drive gear 35 of a starting system gear train 29, and a balancer gear 26 of the balancer shaft 25
Are also engaged. That is, the gear 23 is provided as a balancer driving and starting gear.

The configuration of the starting device will be described. FIG. 3 is a longitudinal side view (a sectional view taken along the line III-III in FIG. 2) of the starting device.
The state of the piston 11 for the third cylinder is shown at the top dead center position. In FIG. 3, a first support shaft 31 for starting is disposed above and behind the crankshaft 1, and a second support shaft 32 for starting is disposed above and behind the first support shaft 31.
A starting motor 33 and an output gear (pinion gear) 34 are disposed in front of the second support shaft 32, and the output gear 34 meshes with a front end portion of the large idle gear 68. The crankcase 2 is vertically divided into an upper case member 2a and a lower case member 2b with the crankshaft center line O1 as a boundary, and both of the support shafts 31, 32 and the starting motor 33 are both upper case members 2a. It is fixed to. First
Behind the second support shafts 31, 32, a breather chamber 17 for the crank is formed integrally with the upper case member 2a.

In FIG. 2 showing an enlarged cross-sectional view taken along the line II-II of FIG. 3, the first support shaft 31 is supported by a pair of support holes 38 and 39 formed in the upper case member 2a in a double-supported manner. And the retaining plate 41 and the bolts 42 and 43
As a result, an oil passage 44 is formed in the shaft center portion, and the oil passage 44 communicates with a lubricating oil supply oil passage 46 formed in the wall of the crankcase 2.

On the first support shaft 31, the starting drive gear 35 is disposed at the same position in the axial direction as the starting gear 23, and a free wheel gear 36 is located on the left of the starting drive gear 35.
Are disposed, and a sprag type (cam type) one-way clutch 48 is disposed between the two gears 35 and 36. The starting drive gear 35 is integrally formed with a boss 50 extending leftward (to the free wheel gear side) at an inner peripheral end, and integrally formed with a one-way clutch outer ring 52 projecting leftward at an outer peripheral end. An annular recess 51 is formed in the intermediate wall (web) and is connected to the annular space between the outer ring 52 and the boss 50. The boss portion 50 is connected to the first
Is rotatably supported by the support shaft 31.

The free wheel gear 36 has a wide inner peripheral boss 55 rotatably fitted directly on the outer peripheral surface of the first support shaft 31, and a right side portion (starting drive) of the inner peripheral boss 55. On the gear side portion), a starting drive gear 3 extending rightward is provided.
The one-way clutch inner ring 56 is formed integrally with the outer peripheral surface of the boss portion 50 of the No. 5 with a radial gap d1 therebetween. Numerous sprags (cams) 60 for a one-way clutch are arranged between the inner wheel 56 and the outer wheel 52, and the free wheel gear 36 is connected to the starting drive gear 35 as is well known.
The torque is transmitted only to the motor. Sprag 6
0, that is, the clutch sliding portion width W1 is completely contained within the width W2 of the needle bearing 53, and
About half of the tooth width of the starting drive gear 35 is inserted.

On the left side of the free wheel gear 36 and the right side of the starting drive gear 35, a collar 5 for a spacer is provided.
7, 58 are fitted to position both gears 36, 35 in the axial direction. A plurality of radial oil grooves 59 are formed on the left end surface of the boss 50 of the starting drive gear 35 so that the inner race 5
6 faces the bottom surface of the annular concave portion 51 with a gap d2 therebetween, and a radial oil passage 61 from the oil passage 44 to the needle bearing 53 is formed in the first support shaft 31. And the gap d1 between the oil groove 59 and the inner peripheral surface of the inner ring.
The gap d2 at the tip of the inner ring constitutes a lubricating oil path from the needle bearing 53 to the sliding portion of the sprag 60.

The second support shaft 32 is connected to the upper case member 2a.
The support holes 62, 63 are formed in a two-sided manner and fixed by an L-shaped retaining plate 64 and bolts 66. A small idle gear 67 meshing with the free wheel gear 36 and a large idle gear 68 with a torque limiter are rotatably fitted on the second support shaft 32. The large idle gear 68 is a taper fit for the torque limiter. The inner member 68a is spline-fitted to the boss portion of the idle small gear 67, and the outer member 68b is connected to the output gear of the starting motor 33 as described above. 34 is engaged. The taper fitting portion 69 exerts a torque limiter function of slipping at a predetermined rotational torque or more by generating a frictional force by the disc spring 71.

The starting motor 33 is fitted in a mounting hole 72 of the upper case member 2a, and is fastened to the upper case member 2a by a bolt (not shown).

[0024]

When the engine is started, when the starting motor 33 shown in FIG. 2 is operated, the starting torque is transmitted from the output gear 34 to the large idle gear 68, the torque limiter (fitting portion 69), the small idle gear 67, and the free wheel gear 36. Is transmitted to the starting gear 23 on the outer periphery of the crank web via the one-way clutch 48 and the starting drive gear 35 to rotate the crankshaft 1. If the load on the crankshaft side is too large for some reason, the torque limiter of the large idle gear 68 operates and the starting force is cut off.

After the start is completed, the starting gear train 29
Only the starting drive gear 35 idles with the crankshaft 1 at all times, and the remaining gears 36, 67, 68 are stopped. That is, since only the starting drive gear 35 closest to the crankshaft in the starting system gear train 29 is always idle, the needle bearing 53 is interposed only in the starting drive gear 35 and the other gear 36 , 67, 68 are sufficient for direct fitting. While the start drive gear 35 is idle, the sprag 60
The outer ring 52 and the needle bearing 53 are rotating at the same position in the axial direction, so that the sprag 60 and the outer ring 52 are rotated.
The bending load applied to the bearing due to the centrifugal force due to the unbalance can be further reduced, and a smooth idle operation and sliding operation can be ensured.

The lubricating action of the starting drive gear 35 and the one-way clutch 48, which always idle, will be described. The lubricating oil pumped from the lubricating oil pump (not shown) to the lubricating oil supply passage 46 in FIG. Oil passages 44 and 61 in 31
Is supplied to the needle bearing 53 through the gap d1 between the oil groove 59 at the tip of the boss portion and the outer peripheral surface of the boss portion and the inner peripheral surface of the inner ring.
And the gap d2 at the tip of the inner ring, and is supplied to the sprag 60 portion.

[0027]

[Other Embodiments] (1) The starting gear is not limited to the case where it is also used as a balancer driving gear, but can be applied to an engine without a balancer, and can also be used as a primary gear for driving wheels. It is also possible.

(2) The present invention is not limited to a four-cylinder engine but can be applied to various multi-cylinder engines.

(3) As a cam member of the one-way clutch, a member utilizing various sprags such as a parallelogram, a dwarf type or a triangular shape can be applied.

[0030]

As described above, according to the present invention, (1) a starting drive gear that always idles and a free wheel gear are arranged side by side on a support shaft separate from the crankshaft, and An outer ring and a boss extending toward the free wheel gear are integrally formed at an outer end and an inner end of the drive gear, and an annular recess opening toward the free wheel gear is formed between the outer ring and the boss. The boss is rotatably supported on a support shaft via a bearing, and the freewheel gear is formed with an inner ring extending into the annular recess along the outer periphery of the boss, and between the inner ring and the outer ring, Since the one-way clutch is formed by arranging the one-way clutch cam member so that the bearing and the axial position overlap with each other, for example, by inserting the annular concave portion into the tooth width of the starting drive gear, the free wheel gear And starting drive The axial distance from the gear can be reduced, so that the axial position of the starting motor having the idle small gear and the idle large gear connected to the free wheel gear and the output gear is also largely offset to one side. However, the compactness of the axial width of the engine can be maintained.

(2) An inner ring formed on the free wheel gear is provided on the boss portion of the starting drive gear so as to extend into the annular concave portion along the outer peripheral side, and a sliding portion of the cam member is provided as a bearing of the starting drive gear. , So that the bending load and the like that are applied by the centrifugal force due to the unbalance of the idler can be made smaller than the bearing of the starting drive gear that always idles. Even if it is not long, a smooth idle operation of the starting drive gear can be ensured.

(3) Since the one-way clutch is not disposed on the crankshaft, the width of the crankshaft itself can be reduced.

(4) An oil passage is formed in the support shaft to reach the bearing on the inner peripheral surface of the boss portion. A gap between the axial end surface of the boss portion and the axial end surface of the free wheel gear, the inner peripheral surface of the boss portion, The gap between the outer peripheral surface of the inner ring and the gap between the axial end surface of the inner ring and the bottom surface of the annular recess forms a lubricating oil path from the bearing to the sliding portion of the cam member. The lubrication oil can be quickly supplied and lubricated from the bearing to the sliding portion of the one-way clutch by the idle rotation. That is, the bearing and the one-way clutch sliding portion can be efficiently lubricated with a simple lubrication structure.

[Brief description of the drawings]

FIG. 1 is a schematic cross-sectional view of a four-cylinder engine for a motorcycle to which the present invention is applied (II-II cross-sectional schematic view of FIG. 3).

FIG. 2 is an enlarged development view taken along the line II-II of FIG.

FIG. 3 is a sectional view taken along the line III-III in FIG. 2;

FIG. 4 is a longitudinal sectional view of a conventional example.

[Explanation of symbols]

 Reference Signs List 1 crankshaft 2 crankcase 20 primary gear for driving wheels 23 starting gear 29 starting gear train 31 first support shaft 33 starting motor 34 output gear 35 starting driving gear 36 free wheel gear 44, 61 oil passage 48 one-way clutch Reference Signs List 50 Boss portion of starting drive gear 51 Annular concave portion 52 Outer ring 53 Needle bearing 55 Boss portion of free wheel gear 56 Inner ring 60 Sprag (cam member) 67 Small idle gear 68 Large idle gear

Claims (2)

(57) [Claims] 1. A starting device for a vehicle engine for starting a crankshaft from a starting motor via a starting system gear train having a one-way clutch, comprising: a starting drive gear constantly idled by rotation of a crankshaft; Gears are arranged side by side on the same support shaft, and the outer peripheral end of the starting drive gear is integrally formed with an outer ring for a one-way clutch projecting toward the freewheel gear, and the inner peripheral end of the starting drive gear The boss portion extending toward the freewheel side is integrally formed.The web of the starting drive gear has an annular shape that opens toward the freewheel gear and is connected to the annular space between the outer ring and the boss portion. A concave portion is formed, the boss portion is rotatably supported on a support shaft via a bearing, and an inner peripheral portion of the free wheel gear extends toward the driving gear for starting and has an outer periphery of the boss portion of the driving gear for starting. Diameter on face A one-way clutch inner member is integrally formed with a one-way clutch inner ring opposed to the one-way clutch with a gap therebetween, and a one-way clutch cam member is arranged between the inner ring and the outer ring such that the bearing and the axial position overlap each other. A starting device for a vehicle engine. 2. A starting device for a vehicle engine according to claim 1, wherein an oil passage leading to the bearing is formed in the support shaft, and a gap between the axial end surface of the boss portion and the axial end surface of the free wheel gear is provided. The gap between the inner peripheral surface of the boss portion and the outer peripheral surface of the inner ring and the gap between the axial end surface of the inner ring and the bottom surface of the annular concave portion constitute a lubricating oil path from the bearing to the sliding portion of the cam member. Starting device for vehicle engine.