JPS62196458A - 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 conical projection in the center of the rotary face thereof and jointed frictionally with the other frictional board on the outer circumferential face thereof. CONSTITUTION:A metallic drive 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 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 conical 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] (industry) - field of use) The present invention relates to a transmission device for a working machine such as a snow blower.

(Prior Art) A transmission device for the above-mentioned snow blower is disclosed in Japanese Unexamined Patent Publication No. 59-89227 filed by the same applicant.

In this configuration, a disc-shaped driving friction plate is provided which is rotated by being driven by the engine. In addition, a disk-shaped driven friction plate is provided which is connected to the driving wheel side, which is the driven side, with the axis of the drive friction plate on the right side (the axis perpendicular to the axis). The driven friction plate is movable in the radial direction of the driving friction plate along the circular rotating surface on the side.Then, the rotating surface of the driving friction plate and the η peripheral surface of the driven friction plate They are joined together, thereby transmitting power.

When the driven friction plate and the rotating surfaces on the inner and outer radial ends of the fast-rotating drive friction plate come into contact, the driven friction plate rotates at high speed, and this is transmitted to the running wheels, thereby... This results in a high speed run of 9-■. Also, when the driven friction plate and the rotating surface on the radially inner side of the wide driving friction plate with the rotational speed I come into contact, the driven friction plate rotates at a low speed, and this is transmitted to the running wheel side. This allows for low speed running.

(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 partially differ greatly. Become. 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 these joint surfaces.Therefore, from the viewpoint of longevity, the reduction ratio must be made sufficiently large. The disadvantage is that it cannot be done.

(Objective of the Invention) This invention was made in view of the above-mentioned circumstances, and aims to provide a transmission device that can sufficiently increase the reduction ratio without causing problems in terms of the lifespan of both friction plates. do.

(Structure of the Invention) A feature of the present invention for achieving the object stated in item 1 is that the driving friction plate and the driven friction plate are rotated along the circular rotating surface of the one of the friction plates. In a transmission device for a working machine such as a snow blower, the other friction plate is relatively movable in the radial direction, and the outer peripheral surface of the other friction plate is frictionally joined to the rotating surface of the first friction plate. , a conical protrusion is provided at the center of the rotating surface at the axis 1- of the above friction plate, and the outer circumferential surface of the protrusion is frictionally joined to the outer circumferential surface of the other friction plate. be.

(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 1. This snow blower 1 includes a vehicle body frame 2, a running section 3 that pivots the heavy frame 2 so as to be able to move up and down, and is capable of traveling on a road surface, and a snow blower main body provided at the front of the vehicle body frame 2. 4
and an engine 5 that is fully supported at the rear of the two-body frame 2. 6 is a drive shaft, and this drive shaft 6 is interlocked and connected to the crankshaft of the engine 5. Further, at the rear end of the vehicle body frame 2, a pair of right and left nodles 7.7 are provided to protrude rearward and upward. Snow removal work by the snow blower 1 is performed by the operator grasping the noddle 7.7.

To explain the running section 3, this running section 3 has a running section frame 8, a drive shaft 9 is supported at the front part of this running section frame 8, and drive wheels 10 are supported at both ends of the drive shaft 9, respectively. .10 is removed and 1 is subtracted. On the other hand, a driven shaft 11 is attached to the rear part of the running section frame 8, and driven wheels 12 and 12 are supported at both ends of the driven shaft 11, respectively. Further, rubber crawlers 13, 13 are wound around these driving wheels 1O and driven wheels 12, respectively.

Then, the F starting driving wheel IO is transmitted via the power transmission device 14.
- Driven by the engine 5, the crawler 13 rolls on the road surface, and the traveling section 3 runs 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 the auger 15 and collect snow crushed by the auger 15. Further, a rotary blade 17 is provided for blowing off the snow collected by the snow collecting cover 16, and the auger 15 and the rotary blade 17 are each driven by the engine 5 via a power transmission device 19. A chute 20 is provided above the rotary blade 17 to guide and throw snow from the rotary 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 composed of a V-belt winding means 22, a transmission means 23, and a gear reduction means 24.
The drive shaft 6 and the drive unit 3 are also 119,!
: Intervened by 1■.

Note ■Bell I - Suspension - "The stage 22 includes a drive pulley 26 supported by the drive shaft 6, a driven pulley 28 supported by the input sum 127 of the speed change/1st stage 23, and this f:)ij;i It is composed of ■・＼rut 29 which is wrapped around the pulley 26 and 28.

From FIG. 2 to FIG. 14, the gear shift LFu23 will be explained.

(The Beka support 27 is set so that it extends in the longitudinal direction of the axis, = (1←), and is supported by the above-mentioned Todo rest clay A 2 from the 4 + 111 support 31 No. 2. After this human power 41 + 27 The cross section of the end ζ is hexagonal, and a metal drive friction plate 32 is slidably supported only in the axial direction and rotates together with the input shaft 27.

One Puno, 1. Behind the starting dynamic friction plate 32, there is a
-qL output shaft 33 is provided at the axis 7 perpendicular to the axis 27. This output shaft 33 has a Φ body due to the bearing 34 ]/
- is supported by the frame 2 and is interlocked and connected to the input end of the 14-tooth heavy reduction gear F stage 24. This output shaft 33 has a hexagonal cross section, and the driven friction plate 35 of this output shaft 33 rotates together with this output shaft 33 as it slides only in the direction of the driver. This driven friction plate 35 has a circumferential portion 1i manufactured by Goto.
The circular rotating surface 32a on the end surface facing the axis Jj of the driving friction plate 32 is frictionally joined to the outer circumferential surface 36 of the row circumferential part 1 of the bullet H, thereby forming a driving friction plate. :32 force mill] Motion) J is transmitted to the driven friction plate 35. Then, [
Record &, l! lI friction holder 35 is driven by friction 4 along rotating surface 32a of 32.
3-1-, and here, when the outer circumferential surface 36i of this driven friction plate 35 and the rotating surface 32a of the driving friction plate 320 are frictionally joined, the dynamic friction plate 35 is moved to the position 1- at this t. The driven friction plate 35 is rotated in accordance with the circumferential speed of the rotating surface 32a of the corresponding driving friction plate 320.

1. The engagement pin 38 is connected to the driven friction plate 35 by the IJ bearing 37.
is supported. -・Force, -1-1 The output shaft 33 has a shifter 39 which is perpendicular to the output shaft 33 and has an axis center tree "l".
is supported by the 4j-body clay A2 so as to be rotatable around its axis. A shift fork 40 is provided protrudingly from the shifter 39, and a rotating end of the shift fork 40 is engaged with the engagement pin 38 shown in -1-. In addition, the heavy body frame i, 2 protrudes outward from the heavy body frame 1. A shift arm 41 is screwed into the rear end of the shift bar 39.The shift arm 41 is rotated so that the shift bar 39
With this rotation, the shift fork 40, which rotates with kneading, moves the driven friction plate 35 in the J direction of the output shaft 33 via the engagement pin 38.

The driving friction plate 321 is connected to the engagement pin 44 by the bearing 43.
is supported. - force, the F force of the input shaft 27 is provided with a movable pivot 45 whose axis is horizontal and intersects IT+ with this input shaft 27, and both ends of this movable pivot 45 are connected to guide grooves formed in the heavy body frame 1.2. 46 and is inserted into the front-rear direction sliding mechanism 1. A clutch fork 48 is rotatably supported on the movable pivot 45, and the rotary end of the clutch fork 48 is engaged with the engagement pin 44 shown in -1-.

Further, a clutch par 49 is provided above the L-starting dynamic friction plate 32 and parallel to the input shaft 27. This clutch par 4
9 is attached to a support 7 at its front and rear midpoints to a bladder nt 50 which is screwed into the small body rules 11 and 2, and this flange bar 49 is slidable in the +hJj direction of E.

Further, the front end of this clutch fork 48 is connected to the rotating end of the clutch fork 48. And 1
When the clutch park 49 is moved in the axial direction, the clutch park 48 rotates, and the clutch park 48 is moved through the engagement pin 44 to the driving friction plate 3.
2 in the axial direction of the input shaft 27. In the case of ζ-, 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. Also,
- [- A release spring 51 is provided that moves the clutch par 49 in a direction that separates the starting dynamic friction plate 32 from the driven friction plate 35.

53 is a release arm, and one end of this release arm 53 is attached to a bracket 5 screwed to the heavy body frame 2.
4 and 112, and the release arm 53 is rotatable around a part of this engagement 11.

The pivoting end of the release arm 53 engages with the shift parr 39, and a longitudinally intermediate portion of the release arm 53 is externally fitted to the rear end of the clutch parr 49 so as to be relatively slidable therein. And ”-Bracket]・50
A connecting spring 55 is interposed in a compressed and deformed state between
) - Push the pin 56 rearward via the release arm 53 (mainly shown by the dotted chain line in FIG. 3). In this case, the connecting spring 55 overcomes the elastic force of the release spring 51 and pushes the clutch par 49 backward, and the pivot shaft 4
As the clutch fork 48 rotates five times, the driving friction plate 32 is joined to the driven friction plate 35.

A cylindrical body 58 is slidably fitted onto the shifter 39 behind the release arm 53, and a return spring 59 is provided to move the cylindrical body 58 backward. Further, 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 is capable of pushing the cylinder 58. If the rotation of the clutch arm 61 pushes the cylindrical body 58 forward against the urging force of the return spring 59,
Accordingly, the cylinder 58 rotates the release arm 53 forward against the urging force of the joining spring 55. Then, the biasing force of the joining spring 55 against the locking pin 56 is released, and the clutch par 49 is pushed forward by the biasing force of the release spring 51.1 This releases the joining of the driving friction plate 32 to the driven friction plate 35. Ru.

In the above configuration, a conical 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. Further, the outer peripheral surface 36 of the driven friction plate 35 includes a large diameter friction surface 36a, a small diameter friction surface 36b, and an inclined friction surface 36c that is frictionally joined to the outer peripheral surface of the protrusion 32b between these two 36a and 38b.
These are arranged in parallel in the axial direction of the driven friction plate 35. And, as shown in Figures 2 to 5,
When the large diameter friction surface 36a corresponds to the rotating surface 32a of the drive friction plate 32, or when the tilting friction surface 36C corresponds to the protrusion 32b
When the movable pivot 45 corresponds to the outer peripheral surface of the guide groove 46, the movable pivot 45 is placed in contact with the front end of the guide groove 46. On the other hand, when the drive friction plate 32 corresponds to the small-diameter friction surface 36b as shown in FIGS. 6 to 8, the movable pivot 45 comes into contact with the rear end of the guide groove 46 and is positioned there.

To explain the structure for moving the movable pivot 45 along the guide groove 46, an interlocking shaft 63 is interposed between the drive shaft 9 of the traveling section 3 and the movable pivot 45 in parallel thereto. 9, interlocking shaft 63, and movable pivot 4
5 and the interlocking shaft 63 are connected by interlocking links 64 and 65, respectively. When the interlocking shaft 63 is pushed downward, the re-interlocking links 64 and 65 are bent, thereby drawing the movable pivot 45 toward the front end of the guide groove 46. Moreover, if the interlocking shaft 63 is pulled until the axis of the above-mentioned interlocking shaft 63 is approximately located on the line connecting the axes of the drive shaft 9 and the movable pivot 45, or until it slightly exceeds this line,
The re-interlocking links 64, 65 become substantially straight, thereby pushing the movable pivot 45 toward the rear end of the guide groove 46.

-4; In the case described above, S in the back and forth movement of the movable pivot 45 is determined as follows. That is, in FIG. 7, the movable pivot 45
When the clutch fork 48 moves from one end of the guide groove 46 to the other end, the clutch fork 48 rotates about the connection point between the clutch fork 48 and the clutch par 49.
In this case, if the connecting point is a stationary temporary rotation center O, and the clutch fork 48 is rotated around this rotation center 0, then as the clutch fork 48 rotates, The moving distance S in -1- is determined so that the amount of movement of the moving drive friction plate 32 substantially matches the radius difference between the large-diameter friction surface 36a and the small-diameter friction surface 38b.

Therefore, the A.1 force exerted by the joining spring 55 when the driving friction plate 32 joins the large diameter friction surface 36a is the same as the force exerted by the joining spring 55 when the driving friction plate 32 joins the small diameter friction surface 36b. The forces will almost match. That is, one of the large-diameter friction surfaces 36a and the small-diameter friction n'+1361-+ is connected to the drive friction plate 32 by the other friction surface, ! - When switching to connection with the drive friction plate 32,
The bonding force of the 6 joints before and after the VJ change is approximately 2 times.

Next, -I gearshift "as a means of operating gear 23-"
stomach? 1.Explain.

In Figure 9 l:+il1, the inner handle 7.
Between 7 and 7, the board 67 was erected. , ゛'s control panel 671j is pivoted by the first pivot 70, number 11 φIJ Brakent 71), and the clockwise rotating automatic I.
i) The movable plate, 1.71 i: is pivoted by the second pivot @I+ 72 so that the operation full/he-73 can be rotated after 1) 1j. In this case, l', '1r moving block 7'',,''
・n) 711;i LM 1'l and y''-73+ko is rotated to the right.

Is there a protruding brush 711 on the left? - The puff I/R 41 is interlocked with the shift lever 6, and is also protruded from the operating lever 73.
Muro 1 is linked and extended by taracchiro 178.

The middle part of the above operation lever 73 is described in step 11 ('l board 67).
A blade groove 79 for guiding the bar 73 during the operation described above is formed in the IS 67 by 2 degrees Celsius. This kite groove 79 is composed of a shift groove 80 extending in the Φ width direction, and a plurality of joining grooves 81 extending L forward from the position of the shift groove 80. Figure 11: Kooi-C
, l The back side of 81, Fl~F4 is forward 1st speed (low speed)
indicates 4th gear (high speed) 2, R1* R2 is reverse l
Speed and 2nd speed are increased by 1, and ri:da, N is medium)'/ is decreased.

Figure 9 +-) Figure 11 (indicated by the solid line)
When the steering wheel 73 is placed in the groove 80, the clutch 7-A61 rotates through the 7-, 77, and 77 → 78 rods. this clan 4
The cylindrical body 58 is pushed forward by the arm 61. As a result, the driving friction plate 32 is separated from the driven friction plate 35 as described above (as shown by the solid line in FIGS. 2 and 3, and the dashed-dotted line in FIG. 7). Power transmission is disconnected. In this case, in the illustrated example, the bar 73 corresponds to the joining groove 81 of R3, T shift 1 Tom 8
It is positioned at 0.

When the operating lever 73 is rotated left and right in the groove 80, the shift arm 41 is rotated via the A-J75 and the shift iron door 6, and this Jino I-A-1,
At 41, the shifter 39 stops rotating. As described above, the driven friction plate 35 is moved to a predetermined corresponding position of the drive friction plate 32 by the rotation of the shift bar 39.

In the above case, when the operating lever 73 is rotated in the shift groove 80 between the joint groove 81 of R3 and the joint groove 81 of R2, the large diameter friction surface 36a of the driven friction plate 35 moves to the rotation surface 32a of the drive friction plate 32. It is adapted to be moved to a predetermined corresponding position. That is, for example, -1, the joining groove 8 of F3
When the operating lever 73 is rotated from the position in the shift groove 80 corresponding to 1 toward the R2 side joining groove 81 (first
1), the large frame friction surface 36a corresponds to the outer side of the rotating surface 32a of the drive friction plate 32 toward the outer side of the shuttle force where the circumferential speed is high, as shown by the solid line in FIGS. 3 and 4. It is moved at the position indicated by the two-dot chain line in the figure. Also, during this movement, the driven friction plate 35
2b, the driving friction plate 32 is separated from the center of the driven friction plate 35 by a larger distance (the dashed double-dot line in the figure, indicated by 32' in Figure 5), that is, in Figure 11. As shown, the shift groove 80 is bent in the middle, and when the operating lever 73 passes through the bent part 80a of this shift groove 80, it is guided by this bent part 80a and the operating lever 73 rotates. The angle becomes larger, and as a result, the driving friction plate 32 is further separated from the center of the driven friction plate 35 as shown in letter L.

Then, rotate the operation lever 73 (1-4) forward from the shift groove 80 side to F2. When engaged with the joint groove 81 of Fa or R1+R2 (arrow B in Fig. 9 and Fig. 11)
, the clutch arm 61 is rotated via the arm 77 and the clutch rod 78, and the pushing of the cylinder 58 is released. As a result, as described above, the rotating surface 3 of the drive friction plate 32
2a is frictionally joined to the large-diameter friction surface 36a (Figs. 2 and 3).
(Illustrated with chain dotted lines in the figure).

Further, when the operation 8-73 is rotated forward and engaged with the joint groove 81 of Fl by operating -1 from the shift groove 80 side, the pushing movement of the cylinder 58 is released in the same manner as above, and thereby, The outer peripheral surface of the protruding body 32b is frictionally joined to the inclined friction surface 36c.

Further, in this case, a predetermined gap is formed between the rotating surface 32a of the driving friction plate 32 and the large-diameter friction surface 36a of the driven friction plate 35 so that the rotating surface 32a does not come into contact with the large-diameter friction surface 36a of the driven friction plate 35.

(The dashed-dotted line section shown in Figure 5 with the number 35 and the number 3
2). Through these connections, power is transmitted from the engine 5 to the driving wheels 10 in a predetermined speed change state selected by the operating lever 73.

Further, when the operating lever 73 is rotated in the shift groove 80 to a position corresponding to the joining groove 81 of F4 (arrow C in FIG. 11), the small diameter friction surface 36b of the driven friction plate 35 changes to the rotating surface 32a (shown by a solid line in FIG. 6). Then, when the operating lever 73 is engaged with the joining groove 81 of F4 from here (arrow D in FIG. 11), the joining spring 55 4=I
The force causes the clutch fork 48 to rotate backward around the movable pivot 45, and as a result, the rotating surface 32a of the drive friction plate 32
is moved to join the small diameter friction surface 36b of the driven friction plate 35.

In the above case, the -1- movable pivot 45 is moved to the rear end side of the guide groove 46, that is, to the driven friction plate 35 side in conjunction with the operation lever 73.

To explain the configuration in which the movable pivot 45 is linked to the operation lever 73, in FIGS. It is pivoted so that it can rotate forward and backward. The upper end side rotation end of this interlocking arm 85 is formed to engage with the operating lever 73 that rotates to engage with the joining groove 81 of F4. This engagement causes the interlocking arm 85 to rotate together with the operating lever 73.

On the other hand, as shown in FIGS. 7, 8, 10, and 12, the lower rotating end of the interlocking arm 85 and the interlocking link 64 are connected by an interlocking wire 86. This interlocking wire 86 is a relatively sliding inner wire 86.
a and an outer wire 86b, and the inner wire 8
One end of the interlocking arm 6a 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. Further, 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.
Fixed. 89 is a spring, and this spring 89 is provided so as to move the interlocking link 64 downward.

Then, when the operating lever 73 is rotated so as to engage with the joining groove 81 of F4 (arrow D in FIGS. 11 and 12)
Accordingly, the interlocking arm 85 is rotated, and the interlocking shaft 63 is pulled up via the interlocking wire 86. Then,
As described above, the movable pivot 45 is moved toward the driven friction plate 35 side.

Further, in the above configuration, a positioning means is provided for holding the drive friction plate 32 in a predetermined speed change attitude when a speed change operation is performed by operating the operation lever 73. This will be explained.

In FIGS. 2, 3, 13, and 14, a positioning arm 92 is provided protruding from the cylindrical body 58. As shown in FIGS. This positioning arm 92 rotates together with the shift fork 40 around the axis of the shifter 39.
is engaged with the shift fork 40 so as to be relatively movable in the axial direction. This positioning arm 92
A lock pin 93 is provided in a protruding manner. On the other hand, an arcuate member 94 corresponding to the rotation locus of the lock pin 93 that rotates together with the positioning arm 92 is screwed to the vehicle body frame 2. A plurality of locking holes 95 are formed in this arcuate member 94 to allow locking pins 93 to be removably engaged with the axial movement of the cylinder 58 .

In Figs. 13 and 14, ■ - Of the 11 recorder holes 95, Fl to F4 are forward speeds from 1st speed (low speed) to 4th speed (high speed).
tj<L, R1+R2 is the reverse 1st speed and 2nd speed, and N is the middle speed.11. I'm here. For example, when the operating l/bar 73 is engaged with the F3 of the joint groove 81, the lock pin 93 is engaged with the F3 of the 11 hole 95, so that the joint groove 81 and the A4+I hole 95 are connected to each other. Response 4
It is formed so that

Part 1. - (As mentioned above, when the control f1 river 2...68 is placed in the shift groove 80), the lock pin '93 is released from the engagement hole 95, and the shift bar 39 51 degrees of free rotation of the shift fork 40 due to the rotation of the shift fork 40 is eliminated.

In the case of 1., F of the joining groove 81 is formed as follows. That is, when the operating lever 73 is engaged with the joining groove 81I7)FI from the shift groove 80 side, the -C lock pin 93 is also fitted into the engaging groove 81I7)FI accordingly. Fl of this gate 11 and hole 95 is shallow gate structure 1 as shown in FIG.
As already explained in FIG. 5,
The outer peripheral surface of the protruding body 32b is the inclined friction surface 3 of the driven friction plate 35.
6c, the rotating surface 32 of the drive friction plate 32
Before a is joined to the large-diameter friction surface 36a of the driven friction plate 35, the protruding end of the lock pin 93 comes into contact with the bottom surface of "F",
With this contact, the rotating surface 32a of the drive friction plate 32 is
- is prevented from coming into contact with the large-diameter friction surface 36a.

In addition, when the operation lever 73 is engaged with the N of the joint groove 81 from the 80 side after shifting, the N is formed into a shallow gate structure and protrudes as in the case described in I. Before the m-plane 37c of the body 321) comes into contact with the large-diameter friction @ 36 a + of the driven friction plate 35, the protrusion E of the lock pin 93 (7) comes into contact with the bottom surface of the N. By this 5! , ζ- where the recording surface 32c comes into contact with the large-diameter friction surface 36a is prevented, power transmission from the driving friction plate 32 to the driven friction plate 35 is prevented, and the gear R stage 23 is set to middle)'l kept in condition.

Each of the following figures shows other embodiments on a smaller scale, and only one configuration different from the embodiment 1-1 will be explained.

FIG. 15 shows a second embodiment. The outer circumferential surface 36 of the driven friction plate 35 in this example includes a large frame friction surface 36a and an inclined friction surface 3.
6c, and no small diameter friction surface 361) is provided. Therefore, in this configuration, the movable pivot 45 in the first embodiment shown in +:i:,1- does not need to be movable; therefore, the guide groove 46 for moving this movable pivot 45, The interlocking shaft 63, interlocking links 64, 65, interlocking arm 85, interlocking wire 86, etc. are unnecessary.

FIG. 16 shows a third embodiment. In the drive friction plate 32, a cylindrical body 32d is coaxially attached to the top surface of the protruding body 32b at -14.
I was attacked by J4. On the other hand, the outer peripheral surface 3 of the driven friction plate 35
6 (A side friction surface 36d that is perpendicular to the axis is formed on the axial end surface side of the driven friction plate 35 so as to be continuous with the inclined friction surface 36c, and this side friction surface 36d
and -F, the row circumferential surface of the cylindrical body 32d can be frictionally joined (in the figure, reference numerals 32 and 35, 1 < dashed line).

Further, in this example, a post 97 is provided which supports the driven friction plate 35 and is slidably fitted onto the output shaft 33, and this boss 97 supports the bearing 37 and the engagement pin 38. A sliding body 98 is fitted onto the outside of the post 97 with a spline so as to be slidable in the axial direction. Further, a retaining ring 99 of the sliding body 98 is attached to the end of the boss 97 in the opposite force direction to the driven friction plate 35.
1 is taken and 1 is kicked. And -1- driven friction plate 3
A pressure-wired spring 100 is interposed between 5 and the sliding body 98.

As described in 1-, this spring 100 functions so that when the side friction surface 36d of the driven friction plate 35 is frictionally joined to the outer peripheral surface of the cylindrical body 32d, this joint is targeted at the bone+, and both of these This suppresses the occurrence of slippage between 36d and 32d.

FIG. 17 shows the fourth embodiment.1. ing. In this example ↑, the rotating surface 32a of the driving friction plate 320 has a truncated conical shape with an offset 41. Further, the large-diameter friction surface 36a on the outer peripheral surface 36 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 drive friction plate 32.

Although the second example is based on the example of the same vehicle, a conical protrusion is formed on the rotating surface of the driven friction plate 350 on the axial end surface side, and the outer circumferential surface of the driving friction plate 32 is rubbed against the outer circumferential surface of this protrusion. They may also be joined.

(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 other friction plate, and In a transmission device for a working machine such as a snow blower, in which the outer circumferential surface of the other friction plate is friction-bonded to the rotating surface of the other plate, -1- the axis of one friction plate is located at the center of the rotating surface. A conical protrusion is provided, and in order to frictionally bond the outer circumferential surface of the other friction plate to the outer circumferential surface of the protrusion, the friction of the other friction plate is It is possible to frictionally join parts of the plate with a large rotation radius. Therefore, since the relative rotational directions of the joint surfaces at the joints of the vibration plates on both sides are almost the same over the entire joint surface, it is possible to prevent a large sliding movement between the two joint surfaces and the generation of torsional force. Therefore, the occurrence of the inconvenience of [life]- can be prevented by +1=. 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.

Moreover, since the protruding body described in - is conical, the difference in the rotation direction of both sides of the joint surface of the vibration plate on both sides can be made smaller than if the protruding body were simply made cylindrical. Generation of torsional force can be suppressed. Therefore, the wear of the joint surfaces described in - is more effectively suppressed, which is beneficial for the life of the friction plate.

[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. Fig. 3 is a plan sectional view of Fig. 2, Fig. 4 is a sectional view taken along the line IV-■ in Fig. 3, Fig. 5 is a partial action explanatory diagram of Fig. 3, and Fig. 6 corresponds to Fig. 4. Figure 7 is a partial enlarged diagram of Figure 2.
The figures are a view taken along the ■-W line in Fig. 7, Fig. 9 is a partially enlarged detailed view of Fig. 1, Fig. 10 is a view taken along the X-X line in Fig. 9, and Fig. 11
The figure is a view taken along the Xl-Xl line in Fig. 10, and Fig. 12 is a view taken along the Xl-Xl line in Fig.
Figure 13 is a view taken along the line ■-■ in Figure 0, Figure 14 is a cross-sectional plan view of Figure 13, and Figures 15 to 17 are views taken from Figure 2. FIG. 6 is a diagram corresponding to FIG. 5 in the fourth embodiment; 1. Snow blower (work machine), 32. Drive friction plate, 32a
...Rotating surface, 32b...Protruding body, 35...Following friction plate, 36c.Fist tilting friction surface (outer peripheral 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 conical protrusion is provided at the center of the rotating surface on the axis of one of the friction plates. A transmission device for a working machine such as a snow blower, characterized in that an outer circumferential surface and an outer circumferential surface of the other friction plate are frictionally joined.