JPS62196460A - Transmission for working machine such as snowplow - Google Patents

Abstract

PURPOSE:To reduce the abrasion by providing a drive and driven frictional boards with the axes thereof crossing perpendicularly each other and forming the rotary face of one frictional board approximately in conical thereby preventing the occurrence of considerable slippage between the joint faces of both frictional boards. CONSTITUTION:A drive frictional board 32 is fixed slidably only in the axial direction to an input shaft 27 being rotated 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. When frictionally jointing the outer circumferential face 36a of the driven frictional board 35 to the circular rotary face 32a of the drive frictional board 32, the power can be transmitted from the drive frictional board 32 to the driven frictional board 35. While when frictionally jointing the outer circumferential face 32d of the drive frictional board 32 to the outer edge section 36b of the rotary face of the driven frictional board 35, the output shaft 33 can be rotated with high speed. Here, the rotary face 32a of the drive frictional board 32 is formed approximately in conical wherein the top face 32 thereof is formed in flat and the outer circumferential face 36a of the driven frictional board 35 is formed to have a triangular cross-section.

Description

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

(Prior Art) -1- A transmission device for a snow blower is disclosed in Japanese Unexamined Patent Publication No. 59-89227 filed by the present applicant.

In this configuration, a disk-shaped drive friction plate is provided that is driven and rotated by the engine. 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. and,
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. Also, when the driven friction plate and the rotating surface on the radially inner side of the driving friction plate with a slow rotational speed come into contact, the driven friction plate rotates at a low speed L, which is the same as I-
The power is transmitted to the running wheels, thereby achieving 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 rejoined surfaces that have been friction-welded, and a torsional force is generated between the two, which tends to cause wear on these joint surfaces. Therefore, from the viewpoint of longevity, the reduction ratio must be sufficiently large. The disadvantage is that it cannot be done.

Further, the circumferential speed of the rotating surface of the driving friction plate gradually increases as it moves outward in the radial direction, whereas the circumferential speed of the outer circumferential surface of the driven friction plate is the same in the axial direction. For this reason, the circumferential speeds between the joint surfaces at the joint portion of both friction plates are partially different. In the conventional configuration described above, since the rotating surface is formed on the plane I- perpendicular to the axis, large sliding occurs partially between the re-joined surfaces that have been friction-welded. There is a disadvantage in terms of life and IL that wear is likely to occur.

(Object of the Invention) This invention was made by paying attention to the situation as described in 1- above, and it is possible to make the reduction ratio of the transmission sufficiently large.
Moreover, the purpose is to improve the life of both friction plates.

(Structure of the Invention) A feature of the present invention for achieving the above object is that one of the driving friction plate and the driven friction plate is rotated along the circular rotating surface of the other friction plate in the radial direction of the other friction plate. In a transmission device for a working machine such as a snow blower, the friction plates of one of the friction plates are relatively movable, and the rotating surface of one friction plate is friction-bonded with the outer circumferential surface of the other friction plate. This is due to the fact that the rotating surface is approximately conical.

(Example) Hereinafter, embodiments of the present invention will be described with reference to the drawings.

1 to 6 show a first embodiment.

In FIG. 1, l is a snow blower which is an example of a working machine, and an arrow Fr in the figure indicates the front of this snow blower l. This snow blower 1 includes a vehicle body frame 2, a running section 3 that pivots the vehicle body plate 2 so as to be movable up and down, and can run on a road surface -■-, and a snow removal device provided at the front of the vehicle body frame 2. It has a machine body 4 and an engine 5 supported at the rear of the vehicle body frame 2. 6 is a drive shaft, and this drive shaft 6 is interlocked and connected to the crankshaft of the engine 5. In addition, at the rear end of the two-body frame 2, there are a pair of left and right handles 7°7.
protrudes toward the rear. Snow removal work using the snow blower 1 is performed by the operator grasping the handle 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 attached. On the other hand, a driven shaft 11 is provided at the rear of the running portion plate 8, and driven wheels 12, 12 are supported at both ends of this driven shaft 11, respectively. Furthermore, rubber crawlers 13 and 13 are wound around these driving wheels 10 and driven wheels 12, respectively.

The L driving wheels 10 are driven by the engine 5 via the power transmission device 14, and thereby the crawler 1
3 rolls on the road surface, and the running 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. Further, 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 includes a V-belt winding means 22 and a speed changer.
It is composed of eight stages 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.

1- V-belt winding "The stage 22 includes a drive pulley 26 supported by the drive shaft 6, a driven pulley 28 supported by the input shaft 27 of the transmission means 23, and a V-belt wound around both pulleys 26 and 28. It is composed of a belt 29.

The transmission means 23 will be explained with reference to FIGS. 2 to 6.

The input shaft 27 is provided so that its axis extends in the longitudinal direction, and is supported by the vehicle body frame 2 by a bearing 31. The rear end of the input shaft 27 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 together with the input shaft 27.

- On the other hand, the I- input input shaft 2 is located behind the drive friction plate 32.
An output shaft 33 whose axis is perpendicular to the axis of No. 7 is provided. This output shaft 33 is supported by the vehicle body frame 2 by a bearing 34 and is operatively connected to the input side of the L2 gear reduction means 24. The output shaft 33 has a hexagonal cross section, and a driven friction plate 36 is supported slidably only in the axial direction, and rotates together with the output shaft 33. The outer peripheral part of the driven friction plate 36 is formed of an elastic friction material such as rubber, and the circular rotating surface 32a on the axial end face side of the driving friction plate 32 is frictionally joined to the outer peripheral surface 36a of this outer peripheral part, thereby driving the driven friction plate 36. Power is transmitted from the friction plate 32 to the driven friction plate 36. Then, the driven friction plate 36 is connected to the rotating surface 3 of the driving friction plate 32.
2a in the radial direction on the output shaft 33, and here, when the rotating surface 32a of the driving friction plate 32 is frictionally joined to the outer peripheral surface 36a of the driven friction plate 36, the rotational surface 32a of the driven friction plate 36 is The driven friction plate 36 is rotated in accordance with the circumferential speed of the rotating surface 32a of the driving friction plate 32 corresponding to the moved position.

1- The rotating surface 32a of the driving friction plate 32 is a flat conical surface, and the top surface 321) thereof is a flat surface. Also,
The outer circumferential surface 36a of the driven friction plate 36 has a triangular cross section so as to match the inclination angle of the rotating surface 32a and make surface contact therewith. Therefore, compared to the conventional case where the rotating surface of one friction plate was formed flush with the axis perpendicular to the rotating surface and the outer circumferential surface of the other friction plate was frictionally joined to this, the joining of both friction plates was It is possible to reduce the difference in circumferential speed between the two parts. In addition, in this case, if the virtual extension of the joint surfaces of both friction plates is brought as close as possible to the intersection of the axes of both friction plates, the difference in circumferential speed between the two at each part of the joint can be made smaller. .

An engagement pin 38 is supported by a bearing 37 on the driven friction plate 36 . On the other hand, on the 1; side of the - and h output shafts 33, a shifter 39 which is orthogonal to the output shaft 33 and whose axis is horizontal is supported by the vehicle body frame 2 so as to be rotatable about its axis. A shift fork 40 is protruded from this shifter 39,
The rotating end of this shift fork 40 is
is engaged with S. Further, a shift arm 41 is screwed to the rear end portion of the shifter 39 that protrudes from the vehicle body frame 2 to the outside. Then, 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 36 in the axial direction of the output shaft 33 via the retaining pin 38. let

An engagement pin 44 is supported by a bearing 43 on the drive friction plate 32 . On the other hand, a pivot 45 is provided below the input shaft 27 and is perpendicular to the input shaft 27 and has a horizontal axis, and this pivot 45 is supported by the vehicle body frame 2. This axis 45
A clutch fork 48 is rotatably supported by the clutch fork 48, and a rotating end of the clutch fork 48 is engaged with the engagement pin 44.

Further, a clutch par 49 is provided on one side of the driving friction plate 32 in the 11th row with the input shaft 27. This clutch par 49 is supported by a bracket 50 which is screwed to the heavy frame 2 at its front and rear middle parts.
9 is slidable in its axial direction. Further, the front end of this clutch par 49 is located at the front end of the clutch fork 48.
is connected to the rotating end of the When the clutch par 49 is moved in the axial direction, the clutch fork 48 rotates, and the clutch fork 48 moves the drive friction plate 32 in the axial direction of the input shaft 27 via the engagement pin 44. move it. In this case, if the driving friction plate 32 is moved backward, it will be friction-bonded to the driven friction plate 36, and if the driving friction plate 32 is also moved forward, this will be friction-bonded to the driven friction plate 36.
Separated from 6. Further, a release spring 51 is provided which urges the clutch par 49 in a direction to separate the drive friction plate 32 from the driven friction plate 36.

53 is a release arm, and one end of this release arm 53 is connected to a placket 5 screwed into the vehicle body frame 2 by a screw 11.
4, and the release arm 53 is rotatable around this engagement 1.

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, written in Bracken I.50
A connecting spring 55 is interposed in a compressed and deformed state between the intermediate portion of the release arm 53 and the intermediate portion of the release arm 53. Pushed backward via arm 53 (
-1, shown in dot-dashed line in Figure 3). In this case, the connection spring 55 overcomes the elastic PI force of the release spring 51 and pushes the clutch par 49 backward, and the pivot 4
As the clutch fork 48 rotates five times, the driving friction plate 32 is joined to the driven friction plate 36.

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,
Clalatches 1 and 61 are rotatably supported on the rear surface of the vehicle body frame 2 via brackets 60, and the rotary end of this 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 biasing force of the return spring 59, the cylindrical body 58 will accordingly resist the 4=j force of the joining spring 55. Rotate the release arm 53 forward. 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 urging force of the release spring 51, thereby releasing the joining of the driving friction plate 32 to the driven friction plate 36. Ru.

Next, a means for changing the speed of the speed change means 23 will be explained.

An operation panel 67 is installed between the handles 7.7, and an operation lever 68 is pivotably supported on the operation panel 67 so as to be rotatable back and forth and left and right.

The operating lever 68 and the shift arm 41 are interlocked and connected by a shift rod 69, and the -L operating lever 68 and the clutch arm 61 are interlocked and connected by a clutch Ron door 0.

Further, a positioning arm 72 is projected from the cylinder 58, and this positioning arm 72 rotates together with the shift fork 40 around the axis of the shifter 39, but can move relatively in the axial direction of the shifter 39. The shift fork 40 is engaged with the shift fork 40. A lock pin 73 is provided protruding from this positioning arm 72. On the other hand, an arcuate member 74 corresponding to the rotation locus of the lock pin 73 accompanying the positioning arm 72 is fitted onto the vehicle body frame 2 by the screw 1. A plurality of locking holes 75 are formed in this arcuate member 74 to allow the locking pin 73 to be removably engaged with the locking pin 73 by moving the cylinder 58 in the axial direction.

In FIG. 5 and FIG. 6, F1 of the arrangement locking holes 75
~F4 indicates forward speed 1 (low speed) to 4 speed (high speed),
R1+R2 indicates reverse 1st speed and 2nd speed, and N indicates neutral.

When the L operating lever 68 is rotated rearward, the clutch rod 70 is rotated as shown by the solid line in FIGS.
The clutch arm 61 is rotated via the clutch arm 61, and the clutch arm 61 pushes the cylinder 58 forward. As a result, the drive friction plate 32 is separated from the driven friction plate 36 as described above, and power transmission from the engine 5 to the drive wheels 10 is cut off. In this case, the lock pin 73 is disengaged from the engagement hole 75 of the locking member 11 and the shifter 3
The shift fork 4o is allowed to freely rotate along with the rotation of the shift fork 9.

From the above state, rotate the operating lever 73 left and right.
The shift arm 41 rotates via the shift rod 69,
Along with this shift arm 41, the shifter 39 shown in - rotates. By this rotation of the shift I/par 39, the driven friction plate 36 is moved to a predetermined corresponding position of the drive friction plate 32, as described above. In this case, the radial center of the rotating surface 32a of the driving friction plate 32 is connected to the driven friction plate 36.
When the operating lever 6 moves, the operating lever 6 is moved so that the center part of the rotating surface 32a and the outer circumferential surface 36a of the driven friction plate 36 do not come into contact with each other.
The drive friction plate 32 is sufficiently moved forward by the operation in step 8.

In FIGS. 2 to 4, in the state shown by the solid line, the driven friction plate 36 is located on the outer circumferential side of the rotating surface 32a of the driving friction plate 32, where the circumferential speed is high. Therefore, the lock pin 73 is shaped like an arc. This corresponds to F4 of the locking hole 75 in the member 74. When the operating lever 68 is rotated forward from this state, the clutch arm 61 is rotated via the clutch rod 70 as shown by the two-dot chain line in the same figure, and the cylindrical body 58 is rotated.
is released. As a result, as described above, the drive friction plate 32 is frictionally joined to the driven friction plate 36, power is transmitted from the engine 5 to the drive wheels 10, and the traveling section 3 moves forward at high speed.

Also, at this time, the lock pin 73 is connected to the F of the engagement 11 and the hole 75.
4, thereby preventing free movement of the driven friction plate 36 on the output shaft 33.

Then, by operating the operating lever 68 in the same manner as described above, the driven friction plate 3
6 is friction-joined, the circumferential speed of this rotating surface 32a gradually decreases, so the driven friction plate 36 is rotated at a low speed, and the running section 3 is therefore rotated at a low speed to match the rotation of the driven friction plate 36. move forward.

In the above case, the driven friction plate 36 must be moved beyond the top surface 32b of the driving friction plate 32 (as shown by dotted chain lines in FIGS. 3 and 4).
, the outer peripheral surface 36a of this driven friction plate 36 is connected to the driving friction plate 32.
When frictionally joined to the rotating surface 32a, the driven friction plate 36 reverses and the traveling section 3 moves backward. Also, -1-
When the driven friction plate 36 is moved to a position corresponding to the top surface 32b of the drive friction plate 32 and the operating lever 68 is rotated forward, and the lock pin 73 is fitted into the locking hole N of the locking hole 75, the fifth
As shown by the dashed line in FIGS. 6 and 6, this N is formed in a shallow concave groove, and the lock pin 73 protrudes before the top surface 32b of the driving friction plate 32 comes into contact with the outer peripheral surface 36a of the driven friction plate 36. The end touches the bottom of N. This prevents the top surface 32b from contacting the outer circumferential surface 36a, and prevents power transmission from the driving friction plate 32 to the driven friction plate 36.
2, and the transmission means 23 enters the neutral state.

The following figures show other embodiments, and the different configurations from the embodiments described in -h will be explained.

FIG. 7 shows a second embodiment, in which the rotating surface 3 of the drive friction plate 32
2a is formed so that its cross section is circularly concave.

Further, the outer circumferential surface 36a of the driven friction plate 36 is formed so that its cross section is approximately semicircular.

FIG. 8 shows a third embodiment, in which the rotating surface 3 of the drive friction plate 32
2a is formed by a rotating surface 32a' on the radially outer side and a rotating surface 32a'' on the inner side, and the former rotating surface 32a' is closer to the axis of the drive friction plate 32 than the latter rotating surface 32a''. It is formed so that the angle of inclination to the heart is large. Also,
The outer peripheral surface 36a of the driven friction plate 36 is in surface contact with the outer rotating surface 32a' and the inner rotating surface 36a'.
It is formed to have a polygonal cross section so as to have a surface 36a'' in surface contact with 2a''.

Although the above embodiments are based on the illustrated examples, the rotating surface of the driven friction plate may be formed into a substantially conical shape, and the outer circumferential surface of the driving friction plate may be friction-bonded to this rotating surface.

(Effects of the Invention) According to the present invention, one of the driving friction plate and the driven friction plate is made relatively movable along the rotating surface of the other friction plate in the radial direction of this 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 friction plate, the rotating surface of one friction plate is formed into a substantially conical shape. Even if the outer circumferential surface of one friction plate is frictionally joined to the center of the rotating surface of the other friction plate, the relative rotational direction of the joint surfaces at the joint of both friction plates is almost the same over the entire joint surface. Therefore, it is possible to prevent a large sliding movement between the rejoining surfaces and the generation of torsional force, thereby preventing the occurrence of the disadvantage of shortening the lifespan to -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.

Second, compared to the conventional method in which the rotating surface of one friction plate was formed on the surface 1- perpendicular to its axis, and the outer circumferential surface of the other friction plate was friction-bonded to this surface, At any joint between the two friction plates in the radial direction of the rotating surface, the difference in circumferential speed between the joint surfaces can be reduced. Therefore,
-I- The sliding speed between the joint surfaces is reduced, and as a result, the wear of the joint surfaces is suppressed, which is beneficial for the life of the friction plate.

[Brief explanation of drawings]

The figures show embodiments of the invention, and Figures 1 to 6 show the first embodiment.
In the examples, Fig. 1 is an overall schematic side view of the snow blower, Fig. 2 is a partially enlarged detailed view of Fig. 1, Fig. 3 is a plan sectional view of Fig. 2, and Fig. 4 is an IT diagram of Fig. 3. - A sectional view taken along the line TV, FIG. 5 is a partial view taken along the line V-V in FIG. 2, FIG. 6 is a plan sectional view of FIG. 5, and FIG. Partial plan equivalent view,
FIG. 8 is a partial plan view corresponding to FIG. 3 of the third embodiment. ■... Snow blower (work machine), 32... Drive friction plate (one friction plate), 32a... Rotating surface, 36... Driven friction plate (other friction plate), 36a... 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 one of the friction plates along the rotating surface on the axial end face side of one of the friction plates, and the other friction plate is relatively movable in the radial direction of the friction plate, and 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, wherein the rotating surface of one of the friction plates is formed into a substantially conical shape. gearbox.