JP3100921B2 - Motorcycle shaft drive device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

[0001] The present invention relates to a shaft drive device for a motorcycle.

[0002]

2. Description of the Related Art As a prior art of a shaft drive device for a motorcycle, there is, for example, Japanese Utility Model Publication No. Sho 58-49904. As shown in FIG. 14, a cylindrical case 202 for accommodating a drive shaft 201 in a rear arm structure 200 is provided. Provided. On the other hand, the engine includes a V-belt type automatic transmission 20.
3 and power transmission gears 205, 206, 207, 208, etc., and bevel gears 210, 211 are housed in a rear transmission case 204. Rearward output bevel gears 211 are housed in a rear end. An output shaft 216 protruding toward the rear end is provided. And the output shaft 21
6 and the above-mentioned drive shaft 201 at the rear thereof are connected by a cross joint 215 so as to be freely bent.

Since it is necessary to synchronize the bending operation of the cross joint 215 and the vertical swinging of the rear arm structure 200, the bending center of the cross joint 215 is arranged so as to be on the axis of the pivot shaft 219. It is. The pivot shaft 219 is fixed to each of the left and right pivot portions 217, and the left and right ends of the front end cylindrical portion 200 a of the rear arm structure 200 are rotatably supported by the pivot shaft 219.

[0004]

In a motorcycle, an appropriate distance of a wheelbase is generally determined, and it is not preferable that the distance be long in terms of steerability and the like. Under these conditions, if the V-belt type automatic transmission 203 and the bevel gears 210 and 211 are built in the engine as described above, and the output shaft 216 is formed to project rearward and the cross joint 215 is disposed behind the same, The pivot shaft 219 that matches the bending center of the joint 215 is disposed more rearward than necessary, which limits the length of the rear arm structure 200 to be short.

[0005] When the length of the rear arm structure 200 is shortened, the swing radius of the rear arm structure 200 is shortened. The amount tends to increase.

In order to maintain the length of the rear arm structure 200, it is conceivable to move the position of the output shaft 216 of the engine forward. In this case, as shown in FIG. 15, a shaft center parallel to the pivot shaft is used. Gear 208 and bevel gears 210 and 21 along the circumference of the idle gear 207 having
1, the output shaft 216 must be moved rearward and upward as indicated by the arrow R0. This naturally means that the position of the cross joint 215 is also increased. Therefore, in order to align the center of bending of the cross joint 215 with the pivot axis, the pivot shaft 219 must be increased.

[0007] When the pivot shaft 219 is raised, the contact angle of the rear arm structure 200 is increased, and the amount of forward and backward movement is larger than the amount of up and down movement when sinking.

When the output shaft 216 is moved forward, the position of the driven gear 221 of the V-belt type automatic transmission 203 may be lowered to suppress the position of the output shaft 216 from becoming high. When the position of the wheel 221 is lowered,
Vehicle height decreases.

For this reason, there are various problems to be solved to secure a long rear arm length while making the bending center of the cross joint coincide with the pivot axis.

[0010]

SUMMARY OF THE INVENTION It is an object of the present invention to eliminate the need for a cross joint in a shaft drive device and to keep the length of a rear arm structure long without increasing the pivot axis.

[0011]

According to a first aspect of the present invention, there is provided a drive shaft assembly upstream of a drive shaft assembly constituting a part of a rear arm structure rotatable around a pivot axis. An upstream gear housing 3 incorporating a bevel gear mechanism comprising a pair of bevel gears 87 and 98
9, the upstream gear housing 39 is rotatably fitted to the pivot shaft 11 with its input shaft center being coaxial with the pivot shaft center, and is a cylindrical type of a wrap-around transmission that is interlocked with the engine. The driven shaft 59 is fitted to the pivot shaft 11 with the same axis as the pivot shaft 11, and the inside of the gear housing of the pivot shaft 11 is
The input gear 70 connected to the cylindrical driven shaft 59 is fitted,
Of the bevel gears 87 and 98, the input-side bevel gear 8
7, a gear portion 86 meshing with the input gear 70
Is integrally molded.

According to a second aspect of the present invention, in the motorcycle shaft drive device according to the first aspect, a V-belt type automatic transmission is provided as the winding type transmission.

According to a third aspect of the present invention, in the shaft drive device for a motorcycle according to the first aspect, the wrap-around transmission and the gear housing on the pivot shaft are distributed on both axial sides of the pivot shaft. doing.

According to a fourth aspect of the present invention, in the motorcycle shaft drive device of the first aspect, the left and right ends of the pivot shaft are fixed to the left and right pivot portions by independent fixing mechanisms.

[0015]

1 and 2 show an example in which the present invention is applied to a scooter type motorcycle having a tread plate. First, an overall outline will be described. In FIG. 1 showing the left side surface, the vehicle body frame includes an upper down tube 1 and a lower down tube 2 each in a left and right pair, and a large engine 3 is provided in a space surrounded by the four down tubes 1 and 2. The parts are stored. Since the engine 3 needs to be arranged in a narrow space between the four down tubes 1 and 2, the cylinder center line is arranged in a forwardly inclined posture close to a substantially horizontal state. A pair of left and right mounting brackets 5 are formed at the front, rear, and rear of the lower surface of the engine 3 respectively. Each mounting bracket 5 is provided with an elastic member on an engine mount formed on each cross member 6 of the down tubes 1 and 2. Floating through is supported. The crankcase 8 of the engine 3 is integrally provided with a shaft case 9 extending rearward on the right side thereof.

At the rear lower part of the lower down tube 2,
The pair of pivot portions 10 are welded and both pivot portions 1
Zero horizontal pivot shafts 11 are arranged, and the left and right ends of the pivot shafts 11 are fixed to the respective pivot portions 10 by independent fixing mechanisms.

The pivot shaft 11 has a rear arm structure 1
4 is rotatably supported at the front end and a driven gear 19 of a V-belt type automatic transmission 18 is rotatably provided. The rear end of the rear arm structure 14 supports a rear wheel 15 and is suspended by an upper frame via a rear cushion 16 so as to be able to pivot vertically (swing).

In FIG. 2 which is a plan view, the rotating shaft 2 parallel to the crankshaft 20 is arranged so that the left and right width of the engine 3 is within a narrow space surrounded by four down tubes 1 and 2.
1 is rotatably supported on the rear shaft case 9, and the rotating shaft 21 includes a centrifugal start clutch 23, a drive gear thrust generating mechanism (centrifugal governor) 24, and a V-belt automatic transmission 18. The driving wheel 25 is mounted. The rotating shaft 21 and the crankshaft 20 are paired with a pair of sprocket gears 26 and 27.
And a primary deceleration transmission mechanism 29 comprising a chain 28 and an interlocking connection.

The V-belt type automatic transmission 18 includes a drive wheel 25, a driven wheel 19 disposed on a rear cylindrical driven shaft 59, and a V-wheel wound between the two wheels 25 and 19. A belt 33 and the drive sheave thrust generating mechanism 24 for applying an axial thrust to the movable sheave of the drive sheave 25, and both the sheds 25, 19 and the V-belt 33 are mounted on the pivot shaft 11. It is located to the left of.

The rear arm structure 14 has an arm 35 made of a normal square pipe on the left side, and the shaft drive device 36 also functions as an arm on the right side. That is, the V-belt type automatic transmission 18 and the shaft drive device 36 are disposed separately on the left and right. The rear end of the arm 35 and the shaft drive device 36 are connected by a rear wheel support shaft 41, and the cross member 3
7 are connected. Shaft drive device 36
Is a transmission cylinder case 3 for accommodating the drive shaft assembly.
8 and an upstream gear housing 39 and a downstream gear housing 40 connected to the front and rear ends of the transmission cylinder case 38, and the upstream gear housing 39 is reinforced and connected to the cross member 37 by a reinforcing stay 49. At the same time, it is supported by the pivot shaft 11 so as to be rotatable around the axis.
The left arm 35 integrally has a boss 43 separately from the upstream gear housing 39, and the boss 43 is supported by the pivot shaft 11 so as to be rotatable around the axis.

A rear wheel hub 42 is rotatably supported on the rear wheel support shaft 41, and a brake cover 44 is fixed. The rear wheel hub 42 is connected to the rear wheel hub 42 via a rib.
And the brake cover 44 is fixed to the left arm 35 via a stay 58 and the like.

The structure of each part of the power transmission mechanism will be described. In the shaft case 9 of the crankcase 8, the centrifugal start clutch 23 is configured such that when the rotation speed becomes equal to or higher than a certain value, the shoe expands radially outward due to centrifugal force and presses against the inner peripheral surface of the drum. Is to be connected.

In the drive adjusting thrust generating mechanism 24, the cam weight expands radially outward with an increase in the rotational speed on the input side, and the drive adjuster 25 is driven through an axially movable movable sleeve. The movable sheave is configured to be pressed toward the fixed sheave.

The V-belt type automatic transmission 18 will be described. In FIG. 3, which is an enlarged cross-sectional view taken along the line III-III of FIG. 1, the driven gearbox 19 includes a fixed sheave 60 on the right and a movable sheave 61 on the left, and is disposed to the left on the pivot axis. Numeral 60 is fixed to the cylindrical driven shaft 59 in the axial and rotational directions, and the movable sheave 61 is fixed to a movable sleeve 62 fitted to the cylindrical driven shaft 59 by rivets or the like. The movable sleeve 62 is formed with a plurality of spiral cam guide grooves 63 that are twisted forward in the rotational direction as they move toward the fixed sheave side. The cam guide grooves 63 are roller pins fitted and supported on the cylindrical driven shaft 59. When the rotational torque from the V-belt 33 increases and the movable sheave 61 is twisted forward in the rotational direction, the movable sheave is cammed by the roller pin 64 and the cam guide groove 63. 61 is pushed to the fixed sheave side. A cover 65 with a brim is fitted around the outer periphery of the movable sleeve 62, and a spring 66 is contracted between a right end brim portion of the cover 65 and a left spring receiving seat 68, and is movable by the spring 66. The sleeve 62 and the movable sheave 61 are urged toward the fixed sheave by a constant spring force.

The drive sheave 25 shown in FIG. 2 has substantially the same structure as that of the driven sheave 19, but the movable sheave is interlocked with the drive sheave thrust generating mechanism 24, and the movable sheave is increased by the rotation speed. The sheave is moved to the fixed sheave side to reduce the space between the sheaves and increase the effective winding diameter of the drive pulley 25.

Returning to FIG. 3, the right end 32 of the cylindrical driven shaft 59
An input cylindrical shaft 67 for a shaft drive device is screw-connected to the shaft. A combined body of the cylindrical driven shaft 59 and the input cylindrical shaft 67 has a pair of inner peripheral surfaces on the left end portion of the cylindrical driven shaft 59. Bearing 5
3 and is rotatably supported by the pivot shaft 11 via the shaft 3, and the outer peripheral surface of the intermediate portion of the input cylinder shaft 67 is provided with a needle bearing 57 on the inner peripheral surface of the left end insertion hole 69 of the upstream gear housing 39. It is rotatably supported via. The inner peripheral surface of the input cylinder shaft 67 and the outer peripheral surface of the pivot shaft 11 oppose each other with a small annular gap 50 filled with grease therebetween, and the gap between the inner peripheral surface of the cylindrical driven shaft 59 and the pivot shaft 11 is And a relatively large annular space 100 for accommodating grease, and the annular space 100 also communicates with the cam guide groove 63 via the outer peripheral surface of the fitting support portion (small diameter portion) of the roller pin 64. ing. The input cylinder shaft 67 extends into the upstream gear housing 39 and is provided with the helical tooth input gear 7.
0 is integrally provided.

A structure for supporting the rear arm structure 14 on the pivot shaft 11 will be described. The front end boss portion 43 of the left arm 35 is arranged between the cylindrical driven shaft 59 and the left pivot portion 10, and is connected to the pivot shaft 1 via a rear arm bearing 55.
An oil seal 71 is fitted between the inner peripheral surface of the right end of the boss 43 and the outer peripheral surface of the left end of the cylindrical driven shaft 59. A housing lid 72 is fitted to the right open end of the upstream gear housing 39 by a bolt or the like and fastened by bolts or the like. The housing cover 72 has a pivot shaft insertion hole 73 formed therein, and the insertion hole 7.
A cylindrical partition wall 74 extending coaxially with the pivot shaft 11 and extending leftward from the pivot shaft 11 with a constant annular space S2 therebetween.
Are formed integrally, and the inner peripheral surface of the insertion hole 73 is rotatably supported on the outer peripheral surface of the pivot shaft 11 via a metal bearing 75. An oil seal 76 is fitted to the right end of the housing lid 72 between the pivot shaft 11 and a rotary oil seal 77 between the left end of the cylindrical partition wall 74 and the outer peripheral surface of the right end of the input cylinder shaft 67. Is fitted. In the left end insertion hole 69 of the upstream gear housing 39,
An oil seal 78 is fitted between the left side position of the needle bearing 57 and the outer peripheral surface of the input cylinder shaft 67. The right end face of the housing lid 72 has an appropriate gap d2 between the right side pivot part 10 and the housing lid 72, so that it can be easily inserted between the pivot part 10 when the pivot shaft 11 and the rear arm structure 14 are disassembled and attached.

The upstream bevel gear mechanism in the upstream gear housing 39 will be described. The upstream gear housing 39 and the rear half of the housing lid 72 are provided with bevel gear shaft support holes 8.
0, 81 are formed respectively, and the support holes 80 on the left side are formed.
Is closed by the left wall of the housing, but the right supporting hole 81 is in a penetrating state, and is closed by fitting a removable resin or rubber cap 82. Bearings 83 are fitted into the support holes 80 and 81, respectively.
The left and right bearings 83 rotatably support an intermediate gear shaft 84 parallel to the pivot shaft 11, and the intermediate gear shaft 84 integrally includes a helical gear tooth type gear portion 86 that meshes with the input gear 70. Are fixed. Between the right end surface of the inner race of the left bearing 83 and the left end surface of the intermediate bevel gear 87, a suitable number of shims 89 for adjusting the tooth gap are interposed as necessary. An internal thread is formed on the inner peripheral surface of the right support hole 81, and a ring nut 88 is screwed into the internal thread to press the intermediate gear shaft 84 to the left via the right bearing 83. Then, it is fixed at a predetermined position.

A drive shaft insertion hole 93 that opens rearward is formed at the rear end of the upstream housing 39, and a flanged bearing holder 92 is fitted into the insertion hole 93.
An upstream drive shaft 96 is rotatably supported on the inner peripheral surface of the bearing holder 92 via a pair of front and rear bearings 95.
The rear end face of the upstream gear housing 39 and the transmission cylinder case 3
The flange portion of the bearing holder 92 is interposed between the mounting flange 97 and the mounting flange 97 welded to the front end of the front gear housing 8, and a plurality of stud bolts 99 and nuts 99 a are used for the upstream gear housing 3.
9, the bearing holder 92 and the mounting flange 97 are integrally fastened. An output bevel gear 98 that meshes with the intermediate bevel gear 87 is fixed to the front end of the upstream drive shaft 96, and the rear portion of the upstream drive shaft 96 projects into the transmission cylinder case 38 coaxially therewith. In order to adjust the tooth gap of the output side bevel gear 98, as shown in FIG. 13, between the inner step surface 98a on the front face of the flange of the bearing holder 92 and the rear end peripheral edge of the insertion hole 93 of the upstream gear housing 39. This is performed by sandwiching an appropriate number of shims 90.

A structure in which the pivot shaft 11 shown in FIG. 3 is fixed to the pivot portion 10 by an independent fixing mechanism with little compression or tensile force applied in the entire axial direction will be described. A male screw portion 105 is formed at the left end of the pivot shaft 11, and a hexagon hole 104 for engaging a hexagon wrench is formed at the right end surface. On the left pivot 10
A stepped hole 45 for supporting a pivot shaft having a stepped portion 46 is formed. A tapered hole 47 and a cylindrical nut fitting hole 48 having the same axis as the stepped hole 45 and a gentle inclination are formed in the right pivot portion 10.
Are formed, and the through pivot shaft 11 is disposed so as to extend over the left and right pivot portions 10, and is inserted into the stepped hole 45, the tapered hole 47, and the cylinder nut fitting hole 48, respectively, and is provided by an independent fixing mechanism. Fixed.

The fixing mechanism on the left side will be described. A cylindrical spacer 54,
56, and the nut 52 screwed to the left end screw portion 105 of the pivot shaft 11 is tightened and pressed against the step portion 46, so that the left pivot portion 10 and the bearing locking step portion 51 of the pivot shaft 11 are At (interval d1), the bearings 53 and 55 and the spacers 54 and 56 are pressed in the axial direction without any gap therebetween. Thereby, the left end of the pivot shaft 11 is fixed to the left pivot 10 independently of the right pivot 10.

The right fixing mechanism includes a split cylindrical collet 102 having an outer peripheral tapered surface corresponding to the tapered hole 47 and the cylindrical nut fitting hole 48, a tapered surface of the tapered hole 47, and an axially extending collet 102. And a cylindrical nut 103 for moving to the position.

FIG. 5 is an exploded perspective view of the right fixing mechanism. The collet 102 is formed with a split groove 106 parallel to the axial direction so that the diameter of the collet 102 can be reduced. The diameter of the screw cylinder 1 is increased at the right end via an annular small diameter portion 109.
07 are integrally formed. The inner peripheral surface of the tapered hole 47 is formed so as to increase in diameter as it goes to the left corresponding to the outer tapered surface of the collet 102, and the right end of the tapered hole 47 expands through a step 108, and the cylindrical nut The cylindrical nut fitting hole 48 is formed in a straight shape so that the cylindrical nut 103 can be inserted therein. A notch 110 for tool engagement is formed at the right end in the axial direction of the cylinder nut 103.

The collet 102 is inserted and fitted into the tapered hole 47 from the left side, while the cylindrical nut 103 is inserted from the right side and loosely screwed into the external threaded cylindrical portion 107 of the collet 102. Then, after inserting the pivot shaft 11 from the right side of the cylinder nut 103, the cylinder nut 103 is tightened.
Pull collet 102 to the right. As a result, the diameter of the collet 102 is reduced by the wedge action between the inner peripheral tapered surface of the tapered hole 47 and the outer peripheral tapered surface of the collet 102, and the outer peripheral surface of the pivot shaft 11 is strongly gripped. At this time, no external force is applied to the pivot shaft 11 in the axial direction.

FIG. 4 is an enlarged cross-sectional view taken along the line IV-IV of FIG.
The structure of the inside and rear wheel hubs 42 and the like will be described. The downstream gear housing 40 has shaft insertion holes 111, 112, and 145 at the front end and the left and right ends, respectively.
Bearing holders 113 and 114 are fitted into the housings 1 and 112, respectively. The front bearing holder 113 is mounted on a mounting flange 115 welded to the rear end of the conductive cylinder case 38 together with the front end of the downstream gear housing 40. The left end bearing holder 114 is fixed to the downstream gear housing 40 by bolts 116.

On the front bearing holder 113, a downstream drive shaft 118 integrally provided with an input bevel gear 117 is rotatably supported via a pair of front and rear bearings 120. The downstream drive shaft 118 is a transmission cylinder. It protrudes into the case 38 and is connected to the upstream drive shaft 96 via a telescopic spline joint mechanism. Left bearing holder 1
An output side bevel gear 122 is rotatably supported on an inner peripheral surface of the base 14 via a bearing 121. An inner peripheral surface of the output side bevel gear 122 is spline-coupled to a rear wheel output cylinder shaft 125 so as to be integrally rotatable. doing. Rear wheel output cylinder shaft 12
5 is rotatably supported on the inner peripheral surface of a boss 126 formed in the downstream gear housing 40 via a bearing 127. An oil seal 1 is provided on the right side of the bearing 127.
28 are fitted. On the rear wheel hub 42, a flanged boss 130 and a coupling disk 131 having inner peripheral spline teeth are fastened to the same axis by bolts 132. The inner peripheral surface of the left end of the rear wheel hub 42 is the bearing 13
4 is rotatably supported by the support shaft 41, and the inner peripheral surface of the flanged boss 130 has a collar 13 fitted to the support shaft 41.
5, rotatably supported via a needle bearing 136,
The inner spline teeth of the disk 131 are the rear wheel output cylinder shaft 1.
25 is spline-coupled to the outer peripheral spline teeth at the left end, so that the output cylinder shaft 125 and the rear wheel hub 42 rotate integrally. 137 and 138 are oil seals disposed between the bearing holder 114, the disk 131 and the rear wheel output cylinder shaft 125.

As an internal expansion type brake mechanism for a rear wheel, a brake drum 14 is provided on an inner peripheral surface of a rear wheel hub 42.
The brake cover 44 is provided with an expandable arm 141, and the shoe 142 attached to the radially outer peripheral surface of the arm 141 is attached to the drum 140.
And can be pressed against (can be expanded from the inside).

The rear wheel support shaft 41 is inserted from the shaft insertion hole 133 of the left arm 35 to reach the right end insertion hole 145 of the downstream gear housing 40, and the outer peripheral surface thereof includes a spacer 146 and a brake cover in order from the left. 44, a rear wheel hub bearing 134, an intermediate spacer 147, the needle bearing collar 135, an intermediate spacer 148, and a flanged spacer 149 are arranged. By tightening a nut 150 screwed to the right end of the support shaft 41, Between the right end wall of the downstream gear housing 40 and the left arm 35, the flanges of the spacers 146, 147, 148, the collar 135, the cover 44, and the collar 149 with the collar are pinched without any gap in the axial direction.

When the rear wheel is disassembled, after the support shaft 41 is pulled out to the left, the rear wheel hub 42 is moved to the left by an interval corresponding to the width d3 of the left spacer 146, so that the disk 131 and the output cylinder shaft are removed. The spline connection with the rear wheel hub 125 can be released, and the rear wheel hub 42 can be removed from between the left arm 5 and the downstream housing 40.

The spline joint mechanism of the shaft drive device 36 will be described. The front and rear drive shafts 96, 118
Spline joint cylinder 160 having inner peripheral spline
Each of the drive shafts 96,
A drive shaft assembly is formed by a spline joint tube 160 connecting the shaft 118 and both shafts 96, 118. The joint tube 160 is press-fitted and fixed to the downstream drive shaft 118, and the upstream drive shaft 96 moves in the axial direction. It is kept in a possible state. Upstream drive shaft 9
6 is fitted with a sleeve 161 and the upstream drive shaft 96
Are locked by the tapered portion 162. A rubber boot 164 is fixed to the downstream drive shaft 118.
An outward flange 165 is integrally formed with the joint cylinder 160, and a spring 166 is contracted between the flange 165 and the rear end surface of the sleeve 161 to separate the front and rear drive shafts 96 and 118 back and forth. Biased in the direction. Also, the sleeve 161 and the joint cylinder 1
An O-ring 169 is fitted between the sleeves 16 and the sleeve 16.
Grease is sealed in the rubber boot 1 and the rubber boot 164 to lubricate the spline portion of the joint cylinder 160. The rear end of the rubber boot 164 is connected to the downstream drive shaft 11.
8 with a rubber boot 164
Is fixed to the outer periphery of the joint cylinder 160 by another clip.

The lubricating structure of the inside of the upstream gear housing 39 and the driven gear 19 will be described with reference to FIGS. As described above, the upstream gear housing 3 shown in FIG.
Inside 9, an inner chamber S2, which is an inner annular space facing the outer peripheral surface of the pivot shaft, and gears 87 and 98 of the upstream bevel gear mechanism are housed by a cylindrical partition wall 74 to supply lubricating oil. The lubricating oil in the outer chamber (gear chamber) S1 is prevented from leaking when the pivot shaft 11 is disassembled and assembled, and mud or the like adhered to the pivot shaft 11 is separated from the chamber (gear chamber) S1. From entering the outer chamber (gear chamber) S1.

Input cylinder shaft 67 for bevel gear and pivot shaft 1
Grease is filled in the gap 50 between the cylindrical driven shaft 59 and the inner peripheral surface of the cylindrical driven shaft 59 facing the annular space 100 as described above. Tubular driven shaft 59
Some of the grease on the inner peripheral surface of the
The lubrication is performed through the fitting support portion of the roller pin 64 to the roller pin head. The grease passing through the bearing 53 moves radially outward due to centrifugal force, but is prevented by the oil seal 71.

An oil level hole 171 communicating with the outside is formed in the left wall of the upstream gear housing 39, and the position of the oil level hole 171 in the front-rear direction substantially corresponds to the rear end edge of the intermediate bevel gear 98. The height of the intermediate gear shaft O is set at the time of use, that is, in a state of being inclined rearward and downward.
It is set so that the oil level L2 is lower than 2 and the lower end portion of the intermediate bevel gear 98 can be maintained at an oil level L2 slightly immersed in lubricating oil. In FIG. 8, reference numeral 184 denotes a drain hole, which is normally closed by a plug.

The breather structure in the upstream gear housing 39 will be described. In FIG. 6, the upstream gear housing 3
9, a breather chamber (gas-liquid separation chamber) 173 that extends rearward and has a rear end opened is formed on the top wall of the upstream gear housing 39. On the other hand, as shown in FIG. An eyebrow-shaped eaves rib 174 is integrally formed so as to cover an outer chamber (gear chamber) S1 that houses a gear mechanism such as the input gear 70 and the intermediate bevel gear 98 from above. In the space S3, the breather chamber 173 is provided.
Has a breather inlet hole 175 communicating with the front end of the breather. That is, the eaves rib 174 is provided in the outer chamber (gear chamber).
The outer chamber (gear chamber) S1 for storing gears and the like and the breather inlet hole 175 so that the lubricating oil stirred by the gear rotation in S1 does not splash directly on the breather inlet hole 175.
Are shielded from the upper space S3 which is open.

In FIG. 9, the rear end of the breather chamber 173 is an opening whose diameter is increased through two steps.
A breather member 180 including, for example, a filter sheet 177, a protection sheet 178, and a pressing ring 179 is fitted into the opening. Filter sheet 17
Reference numeral 7 denotes a special functional film made of a material that allows gas to pass therethrough but does not allow liquid such as lubricating oil to pass therethrough, and is made of, for example, a nonwoven fabric or a porous material having a predetermined clearance. The protection sheet 178 is made of a coarse mesh material,
Excludes dust and the like, but has the property of passing both liquids and gases. The holding ring 179 is made of brass or resin. The filter sheet 177 and the protection sheet 178 are overlapped on the rear step, and the holding ring 179 is provided.
Is fixed by press-fitting.

At the lower end of the breather chamber 173 and immediately before the breather member 180, a return hole 182 extending obliquely rearward and downward is formed. It reaches the upper end of the inner peripheral surface of the shaft insertion hole 93. The bearing holder 92 is fitted into the insertion hole 93 as described above.
An annular groove 185 is formed at a position corresponding to the return hole 182 on the outer peripheral surface of the bearing holder 92, and a lower end of the outer peripheral surface of the bearing holder 92 communicates with the annular groove 185 to form the bearing holder 92.
A longitudinal groove 186 extending axially forward to the front end of the annular groove 185, the longitudinal groove 186 and the insertion hole 93 is formed.
A lubricating oil return passage is formed with the inner peripheral surface of the lubricating oil. That is, the lower end of the outer chamber (gear chamber) S1 in the upstream gear housing 39 extends from the rear lower end of the breather chamber 173, through the return hole 182, through the outer periphery of the bearing holder 92 to the lower end, and then extends forward. A lubricating oil return passage for guiding lubricating oil to the portion is formed.

As the breather member 180, a well-known rubber umbrella check valve (not shown) can be used.

[0048]

When the power transmission paths are summarized, the rotational force of the crankshaft 20 in FIG.
And transmitted to the rotating shaft 21 through the centrifugal start clutch 2
3, transmitted to the cylindrical driven shaft 59 on the pivot shaft 11 via the drive gear thrust generating mechanism 24, the drive gear 25 of the V-belt type automatic transmission, the V-belt 33, and the driven gear 19.

In FIG. 3, on the pivot shaft 11, the power is transmitted from the cylindrical driven shaft 59 to the input gear 70 in the upstream gear housing 39 via the input cylinder shaft 67, and then on the rear intermediate gear shaft 84. Is transmitted to the upstream drive shaft 96 via the intermediate bevel gear 87 and the output side bevel gear 98.

In FIG. 4, the rotational force transmitted from the upstream drive shaft 96 to the downstream drive shaft 118 via the spline joint mechanism is transmitted to the rear wheel hub via the bevel gears 117 and 122 and the rear wheel output cylinder shaft 125. 42 to rotate the rear wheel.

When the rear arm structure 14 swings about the pivot axis, the drive shafts 96 and 118 swing about the pivot axis together with the upstream gear housing 39 and the intermediate bevel gear 87.

The operation of attaching and detaching the rear arm structure 14 and the pivot shaft 11 shown in FIG. 3 will be described. When removing the rear arm structure 14, a tool is engaged with the notch 110 of the cylinder nut 103 shown in FIG. 5 and rotated to loosen the screw engagement with the collet 102. After loosening the screw, by pushing the cylinder nut 103 to the left, the collet 102 is pushed to the left to move the collet 1.
02 can be returned to the expanded state. Next, pivot axis 1
A hexagon wrench is engaged with the hexagon hole 104 at the right end of FIG. 1, a box wrench is engaged with the nut 52 at the left end of the pivot shaft in FIG. 3, and the nut 52 is rotated to remove the nut 52. Then, the pivot shaft 11 is pulled out to the right of the right pivot portion 10.

The cylinder nut 103 is connected to the right pivot portion 1
0 so that the collet 102 is axially immovably locked by a locking ring or the like, and by rotating the cylinder nut 103, the collet 102 is moved to the left in the axial direction without applying an axial force. It is also possible.

After the pivot shaft 11 is pulled out, the rear arm structure 14 can be taken out from between the pivot portions 10.

At the time of such disassembly, the outer chamber (gear chamber) S1 remains in the cylindrical partition 74 even when the pivot shaft 11 is pulled out.
As a result, the lubricating oil in the outer chamber (gear chamber) S1 does not leak to the outside, and dust and oil mud, etc., adhering to the tip of the pivot shaft 11 are removed from the inner chamber S2. There is no intrusion into the chamber (gear chamber) S1.

Further, since a clearance d2 sufficient for removal is secured between the right end of the gear housing cover 72 at the upstream side of the rear arm structure 14 and the right pivot portion 10, the removal operation of the rear arm structure 14 can be performed. Easy to do.

When assembling, the collet 10 at the right end
2 is inserted into the tapered hole 47 and the cylinder nut 103 is loosely screwed to maintain the diameter-expanded state, the front end of the rear arm structure 14 is disposed between the left and right pivot portions 10, and the right pivot The pivot shaft 11 is inserted through the collet 102 from the right side of the portion 10 and the housing lid 7 is inserted.
2. Pass through the input cylinder shaft 67 and the cylindrical driven shaft 59, and let the small diameter portion of the pivot shaft 11 on the left side of the left step portion 51 further pass through the bearing 53 and the boss 43 of the left arm 35, and The left and right ends of the pivot shaft 11 are fixed to the left and right pivot parts 10 by separate right and left fixing mechanisms.

Regarding the fixation on the left side, first, the pivot shaft 11
And a box wrench is engaged with the nut 52, a hexagon wrench is engaged with the right end hexagonal hole 104 of the pivot shaft 11, and the nut 52 is rotated and tightened. Thereby, between the step part 51 of the pivot shaft 11 and the left pivot part 10, the bearings 53, 55 and the spacers 54, 56 are tightened in the axial direction without any gap. That is, the left end of the pivot shaft 11 is
3, 55 and the spacers 54, 56, etc., are fixed to the left pivot portion 10 irrespective of the right pivot portion 10, and the pivot shaft 11, the pivot portion 10 and the frame 2 are fixed to the pivot axis direction. No load is applied and the frame does not flex.

For fixing the right side, the rotating tool is engaged with the notch 110 on the right end of the cylinder nut 103 and rotated, thereby pulling the collet 102 rightward and reducing the diameter of the collet 102 by wedge action between the tapered surfaces. Then, the right end of the pivot shaft 11 is gripped and fixed. At this time, an axial load is applied due to the rightward movement of the collet 102,
The load in the axial direction is almost equal to the load for gripping the pivot shaft 11 in the radial direction. Thus, even in the right fixing work, the load in the pivot axis direction is hardly applied to the pivot shaft 11, the pivot portion 10, and the frame 2, and the frame 2 does not bend.

[0060]

[Other embodiments]

(1) FIG. 10 shows a pivot shaft 1 attached to the right end of the pivot shaft 11 instead of the collet-type fixing mechanism on the right side of FIG.
Forming a male thread portion 190 having a diameter larger than that of the main body portion 1;
A pair of nuts 191 and 19 screwed into the external thread portion 190
2, the right pivot 10 is held from both left and right ends, and the right end of the pivot shaft 11 is fixed. Before inserting the pivot shaft 11 into the right pivot portion 10, the left nut 191 is arranged on the left side of the right pivot portion 10, and after the pivot shaft 11 is inserted from the right into the right pivot portion 10, The body of the pivot shaft 11 is inserted into the nut 191 of the left side, and the left side nut 1
91 is screwed.

(2) FIG. 11 shows an example in which a nut 194 and a locking ring 195 are used instead of the pair of nuts shown in FIG. At the right end of the pivot shaft 11, a pivot shaft 1
1 is formed with a male screw portion 193 having a diameter larger than that of the main body portion, and an annular groove 196 for ring fitting is formed on the left side thereof, and the right pivot portion 10 is sandwiched between the nut 194 and the locking ring 195 from the left and right. By doing so, the right end of the pivot shaft 11 is fixed.

FIG. 12 is a reference example in the case where the engine rotation direction is supposed to be counterclockwise rotation. A pair of helical gear tooth gears for reversal are omitted, and the upstream gear mechanism is constituted only by a pair of bevel gears 87 and 98. Make up. Therefore, the bevel gear 87 is fixed to the input cylinder shaft 67 so as to be coaxial with the pivot shaft 11.

[0063]

As described above, according to the present invention, (1) an upstream gear housing 39 having a built-in upstream bevel gear mechanism is provided upstream of a drive shaft assembly constituting a part of a rear arm structure. The gear housing 39 is rotatably fitted to the pivot shaft 11 such that its input shaft coincides with the pivot shaft, and the output shaft of the wrapping type transmission that is interlocked with the engine is connected to the pivot shaft 11. And the bevel gear in the gear housing 39 is interlockingly connected on the pivot shaft to the output shaft of the above-mentioned transmission, so that the output shaft is compared with a conventional structure having a rearward projecting output shaft. In addition to eliminating the cross joint, the structure can be simplified and the cost can be reduced.
The arm can be moved forward without increasing the height, so that the length of the rear arm structure 14 can be increased while maintaining the normal height of the pivot axis.

(2) As in the second aspect of the present invention, a V-belt type automatic transmission 18 is used as a wrapping type automatic transmission, and a drive gear 25 provided on the output shaft of the engine 3 and a pivot shaft are provided. When the driven gear 19 provided on the vehicle 11 is connected by the V-belt 33, the shock torque of the drive system generated during acceleration or deceleration traveling can be absorbed by the V-belt type automatic transmission. Thereby, for example, a cam damper provided in a conventional shaft drive device can be eliminated.

(3) According to the third aspect of the present invention, when the wrapping type transmission on the pivot shaft and the gear housing 39 are disposed on both sides of the pivot shaft 11 in the axial direction,
Pivot shaft 11 from the transmission and the gear housing 39
And the bending moment due to the bending load applied to the frame is small, and a rigid reinforcing member for the frame is not required.

(4) If the left and right ends of the pivot shaft 11 are fixed to the left and right pivot portions 10 by independent fixing mechanisms as in the invention according to claim 4, the left and right pivot portions at the time of mounting are fixed. In order to maintain the space therebetween, it is not necessary to arrange a spacer or the like without a gap over the entire length between the left and right pivot portions, so that useless members such as the spacer can be omitted and the mounting operation can be simplified. In addition, since the left and right sides are fixed independently, almost no axial compression or tensile force is applied to the entire pivot shaft. Therefore, even if the manufacturing dimensional error of the frame is large, the pivot shaft 11 can be mounted without bending the frame. Can be.

(5) Since the rear arm structure 14 is rotatably supported by the through pivot shaft 11 connecting the left and right frames 2, the support rigidity of the rotation fulcrum of the rear arm structure 14 is also maintained. Can be.

[Brief description of the drawings]

FIG. 1 is a left side view of a main part of a scooter type motorcycle to which the present invention is applied.

FIG. 2 is a plan view of FIG.

FIG. 3 is an enlarged partial sectional view taken along the line III-III of FIG. 1;

FIG. 4 is an enlarged partial view taken along the line IV-IV of FIG. 1;

FIG. 5 is an exploded cross-sectional perspective view of an arrow V portion in FIG. 2;

FIG. 6 is a right side view of the upstream gear housing alone.

7 is a view taken in the direction of the arrow VII in FIG. 6;

FIG. 8 is an enlarged partial view taken along the line VIII-VIII of FIG. 6;

FIG. 9 is a sectional view taken along line IX-IX of FIG. 7;

FIG. 10 is a partial plan view showing a modification of the pivot shaft fixing mechanism.

FIG. 11 is a partial plan view showing another modification of the pivot shaft fixing mechanism.

FIG. 12 is a transmission mechanism diagram showing a structure in which a bevel gear is arranged on a pivot axis.

FIG. 13 is an enlarged view of a portion indicated by an arrow XIII in FIG. 3;

FIG. 14 is a horizontal sectional view of a conventional example.

FIG. 15 is a schematic view taken along the arrow XV in FIG. 14;

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 Pivot part 11 Pivot shaft 14 Rear arm structure 15 Rear wheel 18 V-belt type automatic transmission 38 Transmission cylinder case 39 Upstream gear housing 59 Cylindrical driven shaft 67 Input cylinder shaft 70 Input gear 87, 98 Bevel gear 51, 52, 54 , 56 steps, nuts, spacers, spacers (example of left-side fixing mechanism) 47, 102, 103 Tapered holes, collets, cylinder nuts (example of right-side fixing mechanism) 96, 118, 160 Drive shaft, spline joint cylinder (drive shaft) Assembly)

Continuation of front page (58) Field surveyed (Int. Cl. ⁷ , DB name) B62M 17/00 B62K 25/28 B62M 9/08

Claims (4)

(57) [Claims] An upstream portion incorporating a bevel gear mechanism comprising a pair of bevel gears 87 and 98 at an upstream portion of a drive shaft assembly constituting a part of a rear arm structure rotatable around a pivot axis. A gear housing 39 is provided. The upstream gear housing 39 is rotatably fitted to the pivot shaft 11 with its input shaft center being coaxial with the pivot shaft center. A cylindrical driven shaft 59 is fitted to the pivot shaft 11 coaxially therewith, and an input gear 70 connected to the cylindrical driven shaft 59 is fitted to the inside of the gear housing of the pivot shaft 11, and the bevel gear A shaft drive device for a motorcycle, wherein a gear portion 86 meshing with the input gear 70 is integrally formed on the outer peripheral surface of the bevel gear 87 on the input side of the input gears 87 and 98. 2. The shaft drive device for a motorcycle according to claim 1, further comprising a V-belt type automatic transmission as the winding type transmission. 3. The shaft drive device for a motorcycle according to claim 1, wherein the wrap-around transmission on the pivot shaft and the gear housing are distributed on both axial sides of the pivot shaft. Motorcycle shaft drive device. 4. The motorcycle according to claim 1, wherein the left and right ends of the through pivot shaft are fixed to the left and right pivot portions by independent fixing mechanisms. Shaft drive device.