JPS62196457A - Transmission for working machine such as snowplow - Google Patents

Abstract

PURPOSE:To reduce the slippage of both frictional boards when the speed reduction ratio is high by providing a drive and a driven frictional boards with the axes thereof crossing perpendicularly each other wherein one frictional board is provided with a circular projection in the center of the rotary face thereof and frictionally jointed with the other frictional board on the outer circumferential face thereof. CONSTITUTION:A metallic device frictional board 32 is fixed slidably only in the axial direction to the rear end of an input shaft 27 being driven through a V-belt entraining means 22 and a driven frictional board 35 is fixed slidably only in the axial direction to an output shaft 33 crossing perpendicularly with the input shaft 27. A circular rotary face 32a of the drive frictional board 32 is jointed frictionally to the outer circumferential face 36a of the driven frictional board 35 so as to enable the transmission of power from the drive frictional board 32 to the driven frictional board 35. When jointing the outer circumferential face 32d of the drive frictional board 32 and the outer edge section 36b of the rotary face of the driven frictional board 35 frictionally, the output shaft 33 can be rotated with high speed. Here, a circular projection 32b is provided in the center of the rotary face of the drive frictional board 32 so as to enable the frictional joint between the outer circumferential face thereof and the driven frictional board 35.

Description

[Detailed description of the invention] (Industrial application field) The present invention relates to a transmission device for a working machine such as a snow blower.

(Prior Art) A transmission device for a varnish snow blower is disclosed in Japanese Patent Application Laid-Open No. 59-89227 filed by the present applicant.

The CR is equipped with a disk-shaped drive friction plate that is driven by the engine and rotates. Further, a disk-shaped driven friction plate is provided, which has an axis perpendicular to the axis of the drive friction plate and is connected to the running wheel side, which is the driven side, and has a circular shape on the axial end face side of the drive friction plate. The driven friction plate is movable in the radial direction of the driving friction plate along the rotating surface of the drive friction plate. Then, the rotating surface of the driving friction plate and the outer circumferential surface of the driven friction plate are frictionally joined, thereby transmitting power.

When the driven friction plate and the rotating surface on the radially outer end side of the driving friction plate, which has a high rotational speed, come into contact, the driven friction plate rotates at a high speed, and this is transmitted to the running wheels, thereby enabling high-speed running. can get. Furthermore, when the driven friction plate and the rotating surface on the radially inner side of the drive friction plate, which has a slow rotational speed, come into contact, the driven friction plate rotates at a low speed [7], and this is transmitted to the running wheels, thereby allowing low-speed running. can get.

(Problems to be Solved by the Invention) By the way, in a transmission, when attempting to increase the reduction ratio, it is conceivable to frictionally join the driven friction plate as close to the center of the rotating surface of the driving friction plate as possible. However, in this case, since the radius of rotation is small at the center of the rotating surface of the drive friction plate, the relative rotational direction of the joint surfaces at the joint of both friction plates may be partially different. becomes. For this reason, a large amount of sliding occurs between the two friction-welded joint surfaces, which generates torsional force between them, which tends to cause wear on the joint surfaces.・There is a disadvantage that it cannot be increased by a certain amount.

([Objective 1] of the invention) This invention was made in consideration of the circumstances (1) as described in (-), and provides a transmission device that can sufficiently increase the reduction ratio without causing any inconvenience in terms of the life of both friction plates. The purpose is to serve Jw.

(Structure of the Invention) The feature of the present invention for achieving the above [1] is that among the driving friction plate and the driven friction plate, the force friction plate is rotated along the circular rotating surface of the force friction plate. The other friction plate is relatively movable in the radial direction, and! , In a transmission device for a working machine such as a snow blower, in which the outer circumferential surface of one friction plate is friction-bonded to the rotating surface of the other friction plate, the shaft center I- of the friction plate on the one side is A protruding body having a circular cross section is provided at the center of the rotating surface, and the outer circumferential surface of this protruding body and the other friction plate are frictionally joined.

(Example) Embodiments of the present invention will be described below with reference to the drawings.

1 to 14 show a first embodiment.

In FIG. 1, ■ is a snow blower which is an example of a working machine, and the arrow Fr in the figure indicates the front of this snow blower l. This snow removal @1 is carried out between the body frame 2 and this body frame 2.
A running section 3 that is pivoted so as to be movable downwardly so as to function as a running entrance on the road surface -1-, a snow blower main body 4 provided at the front part of the vehicle distribution body frame 2, and a rear part of the same heavy body frame 2. It has an engine 5 supported by. 6 is a drive shaft, and this drive shaft 6 is interlocked and connected to the crankshaft of the engine 5. In addition, a pair of left and right handles 7 are provided at the rear end of the vehicle body frame 2.
7 is provided protruding toward one side of the rear 1. And a snow blower
Snow removal work is performed by the operator grasping the handle 7.7.

1- To explain the traveling section 3, this traveling section 3 has a traveling section frame 8, a drive shaft 9 is supported at the front part of this traveling section frame 8, and a drive shaft 9 is supported at both ends of the drive shaft 9. A wheel 10, 1.0 is attached. On the other hand, a driven shaft 11 is attached to the rear part of the traveling section frame 8, and driven wheels 12 and 12 are attached to both ends of the driven shaft 11, respectively.
is supported. Furthermore, rubber crawlers 13 and 13 are wound around these driving wheels 10 and driven wheels 12, respectively. The drive wheels 10 are driven by the engine 5 via the power transmission device 14, thereby causing the crawler 13 to roll on the road surface, and the traveling section 3 to travel on this road surface.

On the other hand, the snow remover main body 4 is constructed as follows. That is, an auger 15 that rotates around a horizontal axis to crush snow is supported by the vehicle body frame 2. A snow collection cover 16 is provided to cover the rear of this auger 15 and collect snow crushed by this auger 15. Further, a rotating blade 17 is provided for blowing off the snow collected by the snow collecting cover 16, and the auger 15 and the rotating blade 17 are each driven by the engine 5 via a power transmission device 19. Also, -1
A chute 20 is provided on one side of the rotating blade 17 to guide and throw snow from the rotating blade 17 in a desired direction.

Hereinafter, the power transmission device 14 of the traveling section 3 will be explained.

The power transmission device 14 is comprised of a V-belt winding means 22, a speed change means 23, and a gear reduction means 24, which are interposed between the drive shaft 6 and the drive shaft 9 of the traveling section 3.

The V-belt winding stage 22 is wound around a drive pulley 26 supported by the drive shaft 6, a driven pulley 28 supported by the human power shaft 27 of the first gear shift 23, and both pulleys 26 and 28) (It is composed of a V-belt 29 that is slid.

According to FIGS. 2 to 14, 1. The gear R stage 23 will be explained.

Particularly, in FIGS. 2 to 6, the 1-marked mountain shaft 27 is provided so that its axis extends in the front-rear direction, and is supported by the vehicle body frame 2 by a bearing 31. This input shaft 2
The rear end of 7 has a hexagonal cross section, and a metal drive friction plate 32 is supported here so as to be slidable only in the axial direction, and rotates with the input shaft 27 (J).

- On the other hand, an output shaft 33 of an axial water 41 perpendicular to the axial center of the -I input input shaft 27 is sunk behind the I-start dynamic friction plate 32 . This output shaft 33 is supported by the vehicle body frame 2 by a bearing 34, and is interlocked and connected to the input side of the -1- cable car deceleration means 24. The output shaft 33 has a hexagonal cross section, and a driven friction plate 35 is supported slidably only in the axial direction, and rotates together with the output shaft 33. The outer edge surface 36 of the driven friction plate 35 is formed of an elastic friction material such as rubber.
As a result of the friction welding, power is transmitted from the driving friction plate 32 to the driven friction plate 35. Then, the driven friction plate 35
The output shaft 331- is slid in the radial direction along the rotating surface 32a of the driving friction plate 32, and here, the driven friction plate 3
When the rotating surface 32a of the driving friction plate 32 is frictionally joined to the outer circumferential surface 36a of the drive friction plate 35, the circumferential speed of the rotating surface 32a of the driving friction plate 32 corresponding to the moved position of the driven friction plate 35 corresponds to I.
7, the driven friction plate 35 is rotated.

An engagement pin 38 is supported by a bearing 37 on the driven friction plate 35 . On the other hand, there are 11
A shifter 39 extending perpendicularly to the output shaft 33 and having the shaft center water 11 is supported by the vehicle body frame 2 so as to be rotatable about its shaft center. A shift fork 40 is provided protruding from this shift par 39, and the rotating end of this shift fork 40 is connected to the engagement pin 3.
8 is engaged. In addition, 1-Body frame 2
A shift arm 41 is screwed to the rear end of the shifter 39 that protrudes to the outside. As the shifter 39 rotates due to the rotation of the shift arm 41, the shift fork 40, which rotates accordingly, moves the driven friction plate 35 in the axial direction of the output shaft 33 via the retaining pin 38.

An engagement pin 44 is supported by a bearing 43 on the drive friction plate 32 . On the other hand, a movable pivot 45 is provided below the input shaft 27 and is perpendicular to the input shaft 27 and has a horizontal axis.
Both ends of the movable pivot 45 are fitted into guide grooves 46 formed in the vehicle body frame 2 so as to be slidable in the front and rear directions. A clutch fork 48 is rotatably supported on the movable pivot 45, and a rotating end of the clutch fork 48 is engaged with the engagement pin 44.

In addition, an input shaft 27 is provided on the side of the -1-start dynamic friction plate 32.
A clutch par 49 is provided in the '117-row. This clutch par 49 is supported at its front and rear intermediate portions by a bracket 50 which is screwed into the vehicle body frame 2 by a screw 11, and the clutch par 49 is slidable in its axial direction. Further, a front end of this clutch par 49 is connected to a rotating end of the clutch fork 48. When the clutch par 49 is moved in the axial direction, the clutch fork 48 rotates, and the clutch fork 48 connects the drive friction plate 32 to the input shaft 2 via the retaining pin 44.
7 in the axial direction. In this case, if the driving friction plate 32 is moved rearward, it will be frictionally joined to the driven friction plate 35, and if the driving friction plate 32 is moved forward, it will be separated from the driven friction plate 35. Further, a release spring 51 is provided that biases the clutch par 49 in a direction to separate the driving friction plate 32 from the driven friction plate 35.

Reference numeral 53 denotes a release arm, and one end of this release arm 53 is attached to a bracket 54 fitted to the vehicle body frame 2 with a screw 1.
The release arm 53 is rotatable around this locking portion.

The rotation end of this release arm 53 is connected to the shift l
-/” engaged with the knee 39 and this release arm 5
A midway portion in the longitudinal direction of the clutch par 49 is fitted onto the rear end of the clutch par 49 so as to be relatively slidable therein. A connecting spring 55 is interposed in a compressed and deformed state between the bracket 50 marked ``-'' and the midway portion F of the release arm 53, and this connecting spring 55 is provided at the rear end of the clutch par 49. Push the locking pin 56 rearward via the release arm 53 (
Mainly shown by the dotted chain line in the center of Figure 3). In this case, the joining spring 55
overcomes the elastic force of the release spring 51 and pushes the clutch par 49 backward, and as the clutch fork 48 rotates around the pivot shaft 45 in conjunction with this, the drive friction plate 32
is joined to the driven friction plate 35.

A cylinder 58 is slidably fitted onto the shifter 39 behind the release arm 53, and a return spring 59 is provided to bias the cylinder 58 rearward. Also,
A clutch arm 61 is rotatably supported on the rear surface of the vehicle body frame 2 via a bracket 60, and the rotary end of the clutch arm 61 can push the cylindrical body 58. When the rotation of the clutch arm 61 pushes the cylindrical body 58 forward against the biasing force of the return spring 59, the cylindrical body 58 resists the biasing force of the joining spring 55 and pushes the release arm. 53 forward. Then, the old handle of the connecting spring 55 with respect to the locking pin 56 is released, and the clutch par 49 is pushed forward by the force of the release spring 51, thereby releasing the connection of the driving friction plate 32 with the driven friction plate 35. be done.

In the one-varnish configuration, a cylindrical protrusion 32b is formed at the center of the rotating surface 32a on the axis of the drive friction plate 32, and its top surface 32c is a flat surface. In this case, since the protruding body 32b is a cylindrical body, the structure is simple and the molding thereof is easy. Further, the outer edge surface 36 of the driven friction plate 35 is connected to the outer peripheral surface 36a of the driven friction plate 35.
It has a rotating surface outer edge portion 36b which is a circular rotating surface formed on the axial end surface side of the rotating surface.

As shown by solid lines in FIGS. 2 to 4, the rotating surface 32a of the driving friction plate 32 and the outer circumferential surface 36a of the driven friction plate 35
When these are frictionally joined, power is transmitted from the driving friction plate 32 to the driven friction plate 35, and the snow remover 1 moves forward at a medium speed. Also,
Similarly to the above, when the rotating surface 32a of the driving friction plate 32 and the outer circumferential surface 36a of the driven friction plate 35 are frictionally joined as shown by the two-dot chain line in FIGS. 3 and 4, the case shown by the solid line above The driven friction plate 35 is rotated in the opposite direction, thereby causing the snow blower 1 to move backward.

Further, as shown by solid lines in FIGS. 5 and 6, the outer peripheral surface 32d of the driving friction plate 32 and the outer edge 3 of the rotating surface of the driven friction plate 35
6b, the snow remover 1 moves forward at high speed.

Further, as shown by the two-dot chain line in FIG. 6, when the outer circumferential surface of the protrusion 32b and the outer edge portion 36b of the rotating surface of the driven friction plate 35 are frictionally joined, the snow blower 1 moves forward at a low speed. Further, as shown by the dashed line in FIG. 6, for example, when switching from either the forward gear shift state or the reverse gear shift state to the other,
Outer peripheral surface 36a of driven friction plate 35 and top surface 3 of protrusion 32b
The drive friction plate 32 is moved largely forward so as not to interfere with the drive friction plate 2c. Then, the driven friction plate 35
2b is positioned opposite the top surface 32c of the drive friction plate 32, which is considered to be a neutral state, and the driving friction plate 32 to the driven friction plate 3
Power transmission to 5 is cut off.

Note that the means for operating the speed change means 23 to obtain the desired speed change state among the items 1-- will be described later.

In the above case, in order to prevent slippage between the driving friction plate 32 and the driven friction plate 35 when obtaining high-speed forward movement and when obtaining low-speed forward movement, the two are elastically friction-bonded. A biasing means 62 is provided.

Referring to FIG. 6, the urging means 62 is provided with a post 62a that supports the driven friction plate 35 and is slidably fitted onto the output shaft 33. A sliding body 62b supporting the pin 38 is fitted onto the outside of the post 62a with a spline so as to be slidable in the axial direction. Further, a sliding body 62b (7) and an 11th ring 62c are attached to the end of the post 62a in the direction of 1-j away from the driven friction plate 35 (a=1+1). A compressed spring 62d is inserted between the first driven friction root 35 and the sliding body 62b. be done. This spring 62d has a driving friction of 4
1932 No. Driven friction plate 35.1- is friction J! ! When bonding, it functions to ensure that the bond is bone-like.

In addition, in the case of 1-, the sliding body 62b and Fuichime ring 62
Between the other springs I and the outer edge of the rotating surface 3
The outer edge of the other rotating surface is attached to the driven friction plate 35 on the back side of 6b. It may also be possible to obtain low-speed reverse movement by friction welding.

Also, 1. Among the gear shift states described above, except for the intermediate 1γ state, the iq motion pivot 45 is arranged at a position where it is in contact with the rear end of the guide groove 46 at 41. But 12.1. Go to the notes
When the state is set, the drive friction plate 32 is moved as shown in E7 above.
Relationship 1: Is it necessary to separate the driven friction plate 35 from the driven friction plate 35 by a large distance?
-114 The 11th moving pivot 45 is moved to the front end side of the groove 46.

In particular, in FIGS. 7 and 8, the above 1-Ir! lI axis 45 along the guide groove 46 -1τ forward force (arrow Fr in the figure)
To explain the configuration for moving, the traveling section 3
An interlocking shaft 63 is interposed between the drive shaft 9 and the IJF moving pivot 45 in parallel with them. are connected by interlocking links (34, 65).The movable pivot 4
5, normally, as shown by the solid line in FIGS. 2 and 4 and the 17-dot chain line in FIGS. , the axes of the drive shaft 9, the movable pivot +4.5, and the interlocking shaft 63 are approximately on the same plane -
! 6 and position 17.

And l-kii'ir! IJI axis 45 Guy IC
To move to the front end of 46, turn the interlocking shaft 63
ni pull l.

and bend both interlocking links 64 and 65. As a result, the movable pivot 45 is drawn toward the front end of the guide groove 46 (as shown by solid lines in Figures 1 and 8).

Then, due to the forward movement of the +i7 pivot 45 of ζ'-, the clutch fork 48 is rotated forward approximately around the connecting portion between the clutch fork 48 and the clutch par 49, and the engaging pin 44 is accordingly rotated forward. By moving forward, the driving friction plate 32 is largely separated from the driven friction plate 35. Part 12
In this state, even if the driven friction plate 35 is moved in the axial direction, the driven friction plate 35 is prevented from coming into contact with the protrusion 32b.

Next, a description will be given of means for operating the 1-f gear shift 23.

9 to 11, the inner handles 7, 7
111 k-, , an operation panel 67 is installed. A movable bracket 71 is pivotally supported on the operation panel 67 by a first pivot 70 so as to be rotatable left and right. Further, an operation 1/bar 73 is pivotally supported on the six-swing bracket 71 by a second pivot 72 so as to be rotatable back and forth. In this case, the above movable bracket)
71 is rotated left and right in conjunction with the operation 1/bar 73.

Part 1. Then, the arm 75 protruding from the movable bracket 71 and the shift arm 41 are connected to the shift arm 41.
6, the arm 77 protruding from the operation lever 73 and the Grancia Toro 1 are interlocked and connected by the clutch par 178.

l, the middle part of lever 73 is l-recording 'l @6
7 through 1. This control panel is 67! In Y, a guide groove 79 is formed to guide the 12th operation 1//<-73. This guide groove 79 is composed of a shift groove 80 extending in the Φ-width direction, and a plurality of joining grooves 81 extending forward from each of the shift I and shift 80 positions. In FIG. 11, two of the 1-way joint grooves 81, F1 to F4, are in the first forward speed (
(low speed) to 4th speed (high speed), R,, R2 indicates reverse 1st and 2nd speeds, and N indicates medium to γ.

As shown by solid lines in FIGS. 9 to 11, when the operation 1/bar 73 is positioned in the shift groove 80, the arm 77 and the clutch rod 78 are inserted into the 1. The crankshaft 1 is rotated, and the cylindrical body 58 is pushed forward by the crunchy jaw 1. As a result, the driving friction plate 32 is separated from the driven friction plate 35 as described above (see FIG. 2).
(solid line in FIG. 3, dashed line in FIG. 7), power transmission from the engine 5 to the drive wheels 10 is cut off. in this case,
In the illustrated example, the operating lever 73 is positioned in the shift groove 80 corresponding to the joining groove 81 of F3.

-1- When the operating lever 73 is rotated left and right in the shift groove 80, the arm 75 and the shift! - The shift arm 41 is rotated via the rod 76, and the shift arm 41
The shifter 39 is rotated. By the rotation of this shifter 39, the driven friction plate 3 is rotated as described above.
5 is moved to a predetermined corresponding position on the drive friction plate 32.

”-, the operating lever 73 in the shift groove 80 is connected to the joint groove 8 of F2 + F3 + R1 and R2.
1, the outer peripheral surface 36a of the driven friction plate 35 is moved to a predetermined corresponding position on the rotating surface 32a of the driving friction plate 32, as shown in FIGS. 2 to 4. Furthermore, when the operating lever 73 is made to correspond to the F4 joint groove 8■ in the shift groove 80 marked -, as shown in FIGS. 5 and 6, the outer peripheral surface 32d of the driving friction plate 32 and the driven friction plate 35 The outer edge portion 36b of the rotating surface corresponds thereto. Further, by performing the same operation as above and aligning 8-73 with the joining groove 81 of F, the outer circumferential surface of the protrusion 32b corresponds to the outer edge portion 36b of the rotating surface of the driven friction plate 35, as shown in FIG.

Further, the shift groove 80 corresponding to the N joining groove 81 is bent so as to bypass the front side, and the operation lever 7
3 passes through the bent portion 80a, the movable pivot 45 is moved forward along the guide groove 46 in conjunction with the operating lever 73.

A configuration in which the movable pivot 45 is linked to the operating lever 73 will be explained.

11 and 12, an interlocking arm 85 is connected to a bracket 83 supported by the operation panel 67 via a pivot 84.
can be pivoted to freely rotate back and forth. This interlocking arm 85'
The rotating end on the one end side is formed so as to engage only with the operating lever 73 that moves on the bent portion 80a in an attempt to engage with the N joining groove 81. This engagement causes the interlocking arm 85 to rotate together with the operating lever 73.

- Forces, Figures 3, 7, 8, 10 and 12
As shown in the figure, the lower rotating end of the interlocking arm 85 and the interlocking link 64 are connected by an interlocking wire 86. The interlocking wire 86 is composed of an inner wire 86a and an outer wire 86b that slide relative to each other, one end of the inner wire 86a is connected to the lower rotating end of the interlocking arm 85 via a spring 87, and the other end is connected to the interlocking link 64. Furthermore, one end of the outer wire 86b is fixed to the handlebar 7 side, and the other end is fixed to a bracket 88 on the vehicle body frame 2 side. 89 is a spring, this spring 89
is provided to urge the interlocking link 64 downward.

Then, when the operating lever 73 is rotated so as to engage with the N joining groove 81 (arrow A in FIGS. 11 and 12),
Along with this, the interlocking arm 85 is rotated, and the interlocking wire 8
6, the interlocking shaft 63 is pulled up. Then, as described above, the movable pivot 45 moves forward, that is, the driven friction plate 35
be moved away from the side. As a result, the driving friction plate 32 is further separated from the center of the driven friction plate 35 so that the driven friction plate 35 does not interfere with the protrusion 32b.

Next, the operation for transmitting power from the driving friction plate 32 to the driven friction plate 35 will be explained.

First, as shown by arrow B in FIGS. 9 and 11, the Schiff I
- When the -1- operation lever 73 is rotated forward from the groove 80 side and engaged with the joining groove 81 of F3, the clutch arm 61 is rotated via the arm 77 and the clutch rod 78, and the cylindrical body 58 is rotated. The push motion is released. As a result, in FIG. 2 to FIG.
As shown in 5 by the solid line, the rotating surface 32a of the drive friction plate 32
is frictionally joined to the outer circumferential surface 36a of the driven friction plate 35, and the snow remover l moves forward at a medium speed. Moreover, when the operating lever 73 is engaged with the joining groove 81 of F2 in the same manner as in the case of -1-, the snow remover 1 moves forward at a medium speed at a lower speed than when it is engaged with the joint groove of F8.

In addition, the operation E/bar 73 is also set to R1. < engages R2. 1: In Figs. 2 to 4, both the driving friction plate 32 and the driven friction plate 35 are connected to the 21-dot chain line r +',
'The rotating surface 32a of the driving friction plate 32 is the outer circumferential surface 36a of the driven friction plate 35.
-ru.

Next, operate the bar in the shift groove 80 of "-11".
73 to the joint 11%81 of R4 (arrow C in FIG. 11), the driven friction plate 35 is placed 1!-1 to the external force in the row direction of the driving friction plate 32. I'm sure.

This R4 joint groove 81 is a nail! When the diagonals 1 and 5 (i) are engaged with the joint groove 81 and the bar 13 (turn l - arrow D in FIG. 11), the rotating surface 32 of the drive friction plate 32
Since the driven friction plate 35 does not have the joint I2 in the position a, the driving friction plate 32 moves rearward by the force of the joint spring Fi 5-r 41 . Part 1-7, operation l, bar 73
Turn it all the way to the 81 end of the joining groove of R4! When I+(L), the outer circumferential surface 3 of the starting dynamic friction plate 32 is guided and guided by this inclined joining groove 81, as shown by the solid line in FIGS. 5 and 6.
2d and subordinate ItI++? 'The rotating surface of the shaking plate 35 1st edge rm
36) 1 is frictionally joined, and snow blower 1 is at high speed if4!
-Jru.

Also, when the operating lever 73ter FI□') is aligned with the joint groove 81, the driven friction plate on the outer circumferential surface of the protrusion 32 of the drive friction plate 32 will appear as indicated by the dashed line in Fig. The outer edge portion 36 t:1 of the rotating surface of 35 is frictionally joined, and the snow blower l moves forward at low speed. ], In the case of 1., the rotating surface 32a of the driving friction plate 32 is made to not come into contact with the outer circumferential surface 36a of the driven friction plate 35. , c:, both for one bite 32a, 36a
A gap il is formed in 1st 7. Also, in the configuration 1-1, when the speed change operation fi is performed by operating the doper 73, the driving friction is A single positioning stage is provided to maintain the plate 32 in its predetermined gear shifting attitude. A positioning arm 92 is protruded from the oil body 58. Both the positioning arm 92 and the lifting fork 40 rotate around the axis of the shift bar 39. Engage with No. 40 so that it can move relatively
In 92, Ij Shinkun 93 suddenly died. -・force, l
2. The positioning arm 92 and the rotating opening 2. Kubin 9
3 that rotation 1Il11. Arc-shaped member 94 that conforms to the trace
is seriously ill) -ノ・2nd, ゛nel:) +f is evaluated.

This arc-shaped member 94ij includes a plurality of lock pins 1 and 93 that removably engage the lock pins 93 by moving the recording cylinder 58 in the axial direction.
l-7L 95 is formed 1.

13121 and FIG. 14, -1, 1?1 to F4 of the arrangement IL hole 95 are from forward 1st speed (low speed) to 4th speed (
・No, 1-1, R,, R2 is reverse 1st and 2nd speed)
The speed is 1ζ11,'' and N indicates the medium f. Part 1. For example, the above operation ・8・-73 is inserted into the joining groove 8.
When it is engaged with R3 of 1, the 1st screw pin 93 engages with the stiff joint groove 81 with 1 (F31 of hole 95 engages)]
1 hole 95).

Then, by operating as described above, position r The free rotation of the Shibdoor 40 accompanying the movement is visible in the AV mode.

In the case of 1-, the 11th hole 950F4i,'' is the inclined surface 95
a is formed, and operation 1/・< -73 is the joining groove 8
When R4 of No. 1 is moved in the direction of inclination, the locking pin 93 is guided along the -1,4 inclined surface 95 a l; in the direction of the inclination force (14th [Δ hollow mark E).

Further, the joining groove 81(7)F is formed as follows. That is, when the operating lever '73 is engaged with Fl of the joining groove 81 from the side of the jig 80, the lock pin 93 is also fitted into the engaging hole 95 at F+lj. This person (l,
The hole F of the hole 95 is formed in a shallow gate structure as 71\ in FIG. 14, and as already explained in FIG. The surface outer edge portion 3Bb is frictionally joined 1. After that, the protruding end of the long pin 93 comes into contact with the bottom surface of F1 marked -1-7 at the point where the rotating surface 32a of the driving friction plate 32 is joined to the outer circumferential surface 36a of the driven friction plate 35. , the rotating surface 32 of the drive friction plate 32
Prevents a from approaching the outer circumferential surface 36a.
A gap is formed between these J32a and J36a to prevent their interference.

Also, when the second varnishing part 73 is engaged with the N of the joining groove 81 from the bent part 80a side of the shift groove 80,
Similarly to the above, this N is formed into a shallow groove, and the protruding end of the lock pin 93 comes into contact with the bottom surface of the N before the top surface 32c of the protruding body 32b comes into contact with the outer peripheral surface 36a of the driven friction plate 35. . As a result, the top surface 32c marked -h becomes the outer circumferential surface 36a.
In other words, transmission of power from the driving friction plate 32 to the driven friction plate 35 is prevented, and the transmission means 23 is maintained in a neutral state.

Each of the following figures shows other embodiments, and for this, the different configurations from the embodiments described in 1-1 will be explained, and the common configurations will be indicated with corresponding reference numerals in the drawings and their explanation will be omitted. .

15 to 28 show a second embodiment.

16 to 21, a conical protrusion 32b is formed at the center of the rotating surface 32a of the driving friction plate 320 at the axis -1-. Further, the outer edge surface 36 of the driven friction plate 35 has a large diameter friction surface 36a' and a small diameter friction surface 36b'.
, and an inclined friction surface 36c frictionally joined to the outer circumferential surface of the projection 32b between the two 36a' and 36b', and these are arranged in parallel in the axial direction of the driven friction plate 35.

As shown in FIGS. 16 to 19, when the large-diameter friction surface 36a' corresponds to the rotating surface 32a of the drive friction plate 32, or when the inclined friction surface 36c corresponds to the outer peripheral surface of the protrusion 32b, In this case, the movable pivot 45 is positioned in contact with the front end of the guide groove 46.

On the other hand, when the rotating surface 32a of the drive friction plate 32 corresponds to the small diameter friction surface 36b' as shown by the solid line in FIGS. 20 to 22, the movable pivot 45 comes into contact with the rear end of the guide groove 46 and be positioned.

To explain the structure for moving the movable pivot shaft 45 along the guide groove 46, when the interlocking shaft 63 is pushed downward, the re-interlocking links 64, 65 are bent, thereby moving the movable pivot shaft 45 along the guide groove 46. is attracted to the front end of the In addition, if the interlocking shaft 63 is pulled until the axis of the interlocking shaft 63 is approximately located on the line connecting the drive shaft 9 and the axis of the movable pivot 45, or slightly beyond this line, The interlocking links 64, 65 are substantially straight, thereby pushing the movable pivot 45 toward the rear end of the guide groove 46.

In the case of -1-, the longitudinal movement amount S of the movable pivot 45 is determined as follows. That is, in FIG. 21, the movable pivot 4
5 moves from one end of the guide groove 46 to the other end, the clutch fork 48 rotates around the connection point between the clutch fork 48 and the clutch par 49; Assuming that the clutch fork 48 is rotated around the rotation center 0, assuming that it is a stationary temporary rotation center O, the amount of movement of the drive friction plate 32 that moves with the rotation of the clutch fork 48 is The above-mentioned movement amount S is determined so that the distance S substantially matches the radius difference between the large-diameter friction surface 36a and the small-diameter friction surface 36b.

Therefore, the +1 force by the joining spring 55 when the driving friction plate 32 joins to the large-diameter friction surface 36a', and the +1 force from the joining spring 55 when the driving friction plate 32 joins to the small-diameter friction surface 36b'. 1 faction is almost the same. That is, when switching the connection between one of the large-diameter friction surface 36a' and the small-diameter friction surface 36b' and the drive friction plate 32 to the connection between the other friction surface and the drive friction plate 32, the The bonding force of each bonding portion is made to be approximately the same.

Next, a description will be given of means for operating the speed change means 23.

In FIGS. 23 to 25, the joint groove 81 of R3 and the R
When the operating lever 73 is rotated in the shift groove 80 between the two joining grooves 81, the large diameter friction surface 36a' of the driven friction plate 35 is moved to a predetermined corresponding position on the rotating surface 32a of the drive friction plate 32. has been done. That is, for example, from the position in the shift groove 80 corresponding to the joining groove 81 of F3, the operation fl[//<-73 is directed toward the joining groove 81 on the R7 side.
,)-c rotation, when the rotation is made (indicated by the hollow mark A in Fig. 25), the large-diameter friction surface 36a'l is rotated as shown by the solid line in Figs. 17 and 18. On the surface 32a, τ' corresponds to the outer side in the radial direction where the circumferential speed is higher (:/) and is moved from the position indicated by the dot-dashed line in the figure.

Also, during this movement, the driven friction plate 35
1), the driving friction plate 32 is separated from the center of the driven friction plate 35 by a greater distance ('19th
(The one-dot chain line in the figure is indicated by the reference numeral 32' in the figure). That is, the 25th
As shown in the figure, the shifter i b* 80 is bent in the middle, and when the operating bar 73 passes through the bending part 80a of the shifter 80, the bending part 80a
The rotation angle of the operating lever 73 is increased as a result of this, and as a result, the drive friction plate 32 is further separated from the center of the driven friction plate 35 as described above.

Then, from the shift groove 80 side, 1-operation I/Par 73
By making CI the anterior rotation, F2 + F3 is also 1. < is RI
+R2 is engaged with the joining groove 81 (Fig. 23, 2
4), the rotating surface 32a of the drive friction plate 32 is frictionally joined to the large-diameter friction surface 36a' (small dot-dashed line diagram in FIGS. 16 and 17).

Also, shift]・Groove 80 side or operation 1.・Bar 73
When the shaft is rotated forward and engaged with the joining groove 81 of τF1,
The outer peripheral surface of the protruding body 321 is frictionally joined to the inclined friction surface 36c. Further, in this case, the co-rotating surface 32a of the drive friction plate 32
1. to prevent the large-diameter friction surfaces 36a'+,' of the driven friction plate 35 from coming into contact with each other. A predetermined gap is formed between 32a and 36a', 7 (Figure 19, middle row number 3).
1 (dotted chain line part shown by 5, and tl, dashed line part not shown by 32). Then, by these connections, the operating lever 7
3 is selected and the predetermined gear shift state is selected! P: Power is transmitted from the engine 5 to the drive wheels 10 side-2.

Maj-, shift 1 different 80 smell-C operation and half 3 F
25 (arrow C in FIG. 25), the small diameter friction surface 36b of the driven friction plate 35
' corresponds to the outer edge of the rotating surface 32a which is connected to the drive friction plate 32 (the small solid line in FIG. 20).

From here, when the operation lever 9-73 is engaged with the joint groove 81 of Ij4 (arrow D in FIG. 25), when the operation lever '73 is engaged toward the other joint groove 81, Similarly, the clutch fork 48 is rotated backward around the llfl pivot 45 by the biasing force of the joining spring 55, and as a result, the rotating surface 32a of the driving friction plate 32 becomes the small diameter friction surface 36b' of the driven friction plate 35. is moved to join.

(In the case of , the above-mentioned opening r is
The dynamic pivot 45 is moved to the rear end side of the guide groove 46, that is, to the driven friction plate 35 side.

-1- To explain the configuration in which the movable pivot 45 is interlocked with the operation lever 73, in FIG. 24 and FIG.
The control lever 73 is formed to engage with the operating lever 73 which rotates in an attempt to engage the control lever 73. With this engagement, the interlocking arm 85 is operated and rotated 1 with <-73.

Then, when the handle 111/par 73 is rotated so as to engage with the joint groove 81 of F4 (arrow D in FIGS. 25 and 26), the interlocking arm A 85 is rotated accordingly. It is rotated, and the interlocking shaft 63 is pulled up by -1 via the interlocking wire 86. Then, the movable pivot 45 is moved toward the driven friction plate 35 side.

FIG. 29 shows a third embodiment. In this example, the force edge surface 36 of the driven friction plate 35 is connected to the first circumferential surface 36a and the inclined friction surface 3.
6c, and the small diameter friction surface 36b' in the second embodiment 1j is not provided.

Therefore, in this configuration, the movable pivot 45 in -1-2 of the first embodiment does not need to be IIf movable. , the interlocking links 64, 65, the interlocking arm 1185, the interlocking wire 86, etc. are unnecessary.

FIG. 30 shows a smaller version of the fourth embodiment. In the driving friction plate 32, a cylindrical body 32d coaxially protrudes from the top surface of a truncated conical protrusion 32b, and an outer edge 36 of the rotating surface of the driven friction plate 35.
1] and 1. The protruding body 32b and the outer circumferential surface of the cylindrical body 32d can be frictionally joined.

When the protruding body 32b is formed in a circular shape as shown in 1-, compared to when the protruding body 32b is formed in a cylindrical shape, both friction plates 32. The difference in rotation direction can be made smaller. Therefore, the wear of the 1-arrangement joint is more effectively suppressed, and this is due to the fact that the friction plate 3
2.35 is beneficial for the lifespan.

FIG. 31 shows a fifth embodiment. In this example, the rotating surface 32a of the drive friction plate 32 has a flat truncated cone shape. Further, the outer circumferential surface 36a of the driven friction plate 35 is formed into an inclined surface so as to be in surface contact with the rotating surface 32a of the driving friction plate 32.

FIG. 32 shows a sixth embodiment. In this example, a small diameter cylindrical protrusion 3 which is coaxial with the cylindrical protrusion 32b and whose protruding end has a diameter smaller than that of the -I protrusion 32b is used.
2b'.

Then, as shown by the two-dot chain line in the figure, if the drive friction plate 32 is moved forward greatly and the small diameter protrusion 32b' and the outer edge 36b of the rotating surface of the driven friction plate 35 are frictionally joined, the small diameter protrusion Since the circumferential speed of the body 32b' is lower than the circumferential speed of the protruding body 32b, the snow remover l moves forward at an even lower speed than the above-mentioned low speed forward movement. That is, the small diameter protrusion 32b' indicated by -
An even larger reduction ratio can be obtained by forming .

Although the above is based on the illustrated example, a protrusion with a circular cross section is formed on the rotational surface of the driven friction plate 35 on the axial end surface side, and the driving friction plate 32 is frictionally joined to the outer peripheral surface of this protrusion. Good too.

(Effects of the Invention) According to the present invention, the other friction plate is relatively movable in the radial direction of one of the friction plates along the rotating surface of the one friction plate, and In a transmission device for a working machine such as a snow blower, in which the outer circumferential surface of one friction plate is frictionally joined to the other friction plate, a protrusion having a circular cross section is provided at the center of the rotating surface on the axis of one friction plate. In order to frictionally bond the other friction plate to the outer circumferential surface of this protruding body, the rotation radius of the other friction plate is larger than that of the outer circumferential surface of the protruding body at the center of the rotating surface of one friction plate. can be friction welded. Therefore, since the relative rotational directions of the joint surfaces at the joint portion of both friction plates are almost the same over the entire contact surface, large sliding motion between the two joints and generation of torsional force is prevented. 11- The occurrence of inconveniences in life can be prevented. As a result, it is possible to frictionally join the center portion of one friction plate, where the circumferential speed is low, with the other friction plate, and the reduction ratio can be made sufficiently large.

[Brief explanation of drawings]

The drawings show an embodiment of the present invention, and FIGS. 1 to 14 show the first embodiment, FIG. 1 is a schematic side view of the entire snow blower, and FIG. 3 is a plan sectional view of FIG. 2, FIG. 4 is a sectional view taken along the line 4-4 of FIG. 3, FIG. 5 is an explanatory view of the action corresponding to FIG. 7 is a partial enlarged view of FIG. 2, FIG. 8 is a view taken along the line 8-8 in FIG. 7, and FIG. Figure 10 is a lo-10 line arrow view of Figure 9,
Figure 1 is a view taken from line 11 to 11 in Figure 10, Figure 12 is a view taken from line 12 to 12 in Figure 10, and Figure 13 is taken from line 13 in Figure 2.
-13 line arrow view, Fig. 14 is a plan sectional view of Fig. 13, i
15 to 28 show the second embodiment, FIG. 15 is a schematic side view of the entire snow blower, FIG. 16 is a partially enlarged detailed view of FIG. 15, and FIG. 17 is a plan sectional view of FIG. 16. Figure 18 is the first
7 is a sectional view taken along the line 18-18, FIG. 19 is a partial action explanatory diagram of FIG. 17, FIG. 20 is an action explanatory diagram corresponding to FIG. 18, and FIG. Explanatory diagram, 2nd
Figure 2 is a view from arrow 22-2211i1 in Figure 21, Figure 23 is a partially enlarged detailed view of Figure $15, and Figure 24 is 2 in Figure 23.
4-24 line arrow view, FIG. 25 is a 25-25 line arrow view view in FIG. 24, FIG. 26 is a 26-28 line arrow view view in FIG. 24,
Fig. 27 is a view taken along the line 27-27 in Fig. 16, Fig. 28 is a plan sectional view of Fig. 27, and Figs. 29 to 32 correspond to Fig. 6 for the third to sixth embodiments. This is a diagram. 1e・Snow blower (work equipment), 32・φ drive friction plate, 32a
@@Rotating surface, 32b--protruding body, 35...driven friction plate,
36b: Outer edge of rotating surface, 360-shape, inclined friction surface.

Claims (1)

[Claims] 1. A disc-shaped driving friction plate that rotates in conjunction with the driving side is provided, and a disc-shaped driven friction plate that has an axis substantially perpendicular to the axis of the driving friction plate and is connected to the driven side. A plate is provided, and the other friction plate is relatively movable in the radial direction of the friction plate along the circular rotating surface of one of the friction plates. In a transmission device for a working machine such as a snow blower in which the outer circumferential surface of the plate is friction-bonded, a protrusion with a circular cross section is provided at the center of the rotating surface on the axis of one of the friction plates, and the protrusion has a circular cross section. A transmission device for a working machine such as a snow blower, characterized in that an outer circumferential surface and the other friction plate are frictionally joined.