JPS62196461A - Transmission for working machine such as snowplow - Google Patents

Abstract

PURPOSE:To enable the continuous variation of the speed change ratio by providing a drive and driven frictional boards with the axes thereof crossing perpendicularly each other wherein the rotary face of one frictional board is formed approximately in conical into a continuous face from the radial outer end section toward the center of rotation. 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 a 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 into a continuous face from the radial outer edge section toward the center of rotation.

Description

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

(Conventional Branch Techniques) There is a technique disclosed in Japanese Patent Application Laid-Open No. 59-89227, filed by the applicant of ζ-.

This configuration does not include a disk-shaped drive friction plate that is driven and rotated by the engine. Further, a disk-shaped driven friction plate is provided which is connected to the running wheel side, which is the driven side, with the axis perpendicular to the axis of the drive friction plate to the right, and 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 circular rotating surface of the drive friction plate. As a result, 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 with high rotational speed come into contact with each other, the driven friction plate is able to transmit the high speed rotation 1~ to the running wheel side, and this is transmitted to the running wheel side. This results in high speed running. Also, when the driven friction plate and the rotating surface on the radially inner side of the driving friction plate, which has a slow rotational speed, come into contact, the driven friction plate rotates at a low speed, and this is transmitted to the same running wheel side, thereby causing low-speed running. but(
￥I will be charged.

(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 the vibration plates on both sides may differ greatly in some parts. becomes. For this reason, a large amount of sliding occurs between the re-joined 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 perspective of longevity, the reduction ratio must be increased upwards. There is an inconvenience that it is not possible to do so.

Further, the circumferential speed of the rotating surface of the driving friction plate described in -I- 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 portions of the swing plates on both banks will partially differ. And 1. In the conventional configuration, the rotating surface is a surface 1 perpendicular to its axis. Since the rejoining surfaces are friction-welded, a large amount of sliding occurs partially between the re-joining surfaces, which causes a disadvantage in that the joining surfaces are likely to wear out.

(Objective of the Invention) This invention was made in consideration of the above-mentioned circumstances, and it is possible to increase the reduction ratio of the transmission sufficiently, and to extend the life of the vibration plates on both banks. The purpose is to

(Structure of the Invention) A feature of the present invention for achieving the object stated in item 1-1 is that, along the circular rotating surface of one of the driving friction plate and the driven friction plate, the radial direction of this friction plate is In a transmission device for a working machine such as a snow blower, in which the other friction plate is relatively movable, and the rotating surface of one friction plate is friction-bonded with the outer peripheral surface of the other friction plate, The rotating surface of one of the friction plates is formed into a substantially conical shape, and the rotating surface is formed to be a continuous surface from the outer end in the radial direction toward the center of rotation.

(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, ■ 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 l has a body frame 2 and a body frame 2 which is -1-
A running section 3 which is pivotably supported for downward movement and can run on a road surface, a snow removal machine main body 4 provided at the front of the bipedal vehicle body frame 2, and a snow removal machine body 4 supported at the rear of the vehicle body frame 2. It has an engine 5. 6 is a drive shaft; this drive shaft 6
is operatively connected to the crankshaft of the engine 5. Also, at the rear end of the vehicle body frame 2, there is a pair of left and right handles 7°7.
The rear is protruded toward one side. 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 a drive shaft 9 is supported at both ends of the drive shaft 9, respectively. Drive wheels 10.10 are attached. On the other hand, a driven shaft 11 is attached to the rear of the running section frame 8,
Driven wheels 12.12 are supported at both ends of the driven shaft 11, respectively. Furthermore, rubber crawlers 13 and 13 are wound around these driving wheels 10 and driven wheels 12, respectively. Then, the drive wheels 10 are driven by the engine 5 via the power transmission device 14, whereby the crawler 13 rolls on the road surface, and the traveling section 3 runs on this road surface.

On the other hand, the snow removal machine 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. Snow collection cover 16 covers the rear of this auger 15 and collects snow crushed by this auger 15
is provided. Further, a rotary blade 17 is provided to blow away the snow collected by the snow collecting cover 16, and the auger 15 and the rotation 'l'1 root 1'/ are connected to the engine 5i, It can be driven from '. In addition, a chute 20 is provided at the l-noj of the rotary blade 17 to guide the snow to the force surface of the rotary blade 17 or b.

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

1. The power transmission device 14 has a V-held winding stage 22, a speed change [
It consists of a stage 2:3 and a float reduction stage 24, which are arranged between the drive shaft 6 and the drive shaft 9 of the running section 3.

Note I ■ Pel I - Winding 1st stage 22 is a drive pulley 26 supported by the drive shaft 6, a driven /-928 supported by the human power shaft 27 of the first gear shift 23, and winding around these pulleys 26, 28. JAS becomes a talent with the V bell i 29 that can be hung.

Referring to FIGS. 2 to 6, -1 and the speed change means 23 will be explained.

! The entry shaft 27 is provided so that its axis extends forward and backward li+H', and is supported by the vehicle body 2 through bearing 31'. The rear end of this manpower shaft 27 has a hexagonal cross section, and a metal drive friction plate 32 is supported by the sliding shaft 1 only in the axial direction, and rotates with the manpower shaft 27 and J1.

-Jノ, 1. Behind the drive friction plate 32 is a human powered vehicle 2.
An output shaft 33 whose axis is water-soil and whose axis is perpendicular to the axis 7 is provided. This output shaft 33 is interlocked and connected to the input end of the vehicle speed reduction stage 24 by a bearing 34 on the IΦ body F1/-N,2. This output ll111133 has a hexagonal cross section, and this output shaft 33 has a driven friction plate 3.
6 is slidably supported only in the direction J, and rotates together with this output shaft 33. The outer periphery of the driven friction plate 36 is formed of a friction material 4 made of bullet H manufactured by Inno-1, and a circular rotating surface 32a on the axial end face side of the driving friction plate 32 is friction-bonded to the outer periphery 36a of the outer periphery. By doing so, the driving friction plate 3
Power is transmitted from 2 to the driven friction plate 36. And-
[- The driven friction root 36 is connected to the rotating surface 32a of the driving friction plate 32.
The output shaft 33 is slid on the peak force surface along the peak force surface.
Grind the rotating surface 32a of 4? ′! When joined, the driving friction plate 32 corresponding to the movement f, - position of the driven friction plate 36
The driven friction plate 36 is rotated in accordance with the circumferential speed of the rotating surface 32a.

1- The rotating surface 32a of the drive friction plate 32 is a flat conical surface, and the top surface 32b thereof is an IIZ fjj surface. In this case, this rotating surface 32 a IJ: is formed to be a continuous surface from its radially outer end toward the center of rotation. Further, 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 come into surface contact therewith. Therefore, conventionally, the rotating surface of one friction plate is formed perpendicular to its axis 12, and the outer circumferential surface of the other friction plate is frictionally joined to this. It is possible to reduce the difference in circumferential speed between the two at each part of the joint. In addition, in this case, if the imaginary extended surface of the joint surface of both friction plates is brought as close as possible to the intersection of the axes of both friction plates, the difference in peripheral speed between the two at each part of the l-arrangement joint can be made smaller. be able to.

[The engagement pin 38 is attached to the driven friction plate 36 by the bearing 37.
is supported. On the other hand, on the output shaft 33 L)], a shift bar 39 having a 15-axis horizontal axis orthogonal to the output shaft 33 is supported by the vehicle body frame 2 so as to be rotatable about its axis. A shift fork 40 is protrudingly installed on this shift par 39, and the rotating end of this shift quark 40 is engaged with the engagement pin 38 mentioned in -1-. In addition, at the rear end of the shift bar 39 protruding outward from the shift arm 41 and the shift arm 41, a screw 1 (6 screws) is attached. As the shift I/par 39 rotates, the shift fork 40 that rotates accordingly moves the driven friction plate 36 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 . - Below the human power shaft 27, there is provided a pivot 45 which is orthogonal to the input shaft 27 and has a water/soil axis, and this pivot 45 is supported by the vehicle body frame 2. This axis 4
5, a clutch fork 48 is rotatably supported, and the rotating end of this clutch fork 48 is connected to the engaging pin 44 described in 1-.
is engaged with.

Further, a clutch par 49 is provided on the L side of the drive friction plate 32 in parallel with the input shaft 27. This clutch par 4
9 is supported by a bracket i.50 screwed to the vehicle body frame 2 at its front and rear midpoints, and this clutch par 49 is slidable in its axial direction. Further, the front end of the clutch par 49 is connected to the rotating end of the clutch fork 48. When the clutch par 49 is moved in the axial direction, the clutch fork 4
8 rotates, and this clutch fork 48 engages the engagement pin 44.
The drive friction plate 32 is moved in the axial direction of the input shaft 27 via the input shaft 27 . In this case, if the driving friction plate 32 is moved rearward, it will be frictionally joined to the driven friction plate 36, and if the driving friction plate 32 is moved forward, it will be separated from the driven friction plate 36. Further, a release spring 51 is provided which biases the clutch par 49 by 1 in the direction of separating the driving friction plate 32 from the driven friction plate 36.

Reference numeral 53 designates a release arm. One end of the release arm 53 is engaged with a bracket 54 screwed to the vehicle body frame 2, and the release arm 53 is rotatable around this engagement portion.

The pivoting end of this release arm 53 engages with the shift bar 39 marked -1-, and this release arm 53
The intermediate portion in the longitudinal direction is externally fitted onto the rear end portion of the clutch par 49 so as to be relatively slidable therein. ”-Bracket 5
A connecting spring 55 is interposed in a compressed and deformed state between the release arm 53 and the middle part marked -1- of the release arm 53. 56 rearward via the release arm 53 (mainly shown by the dotted chain line in FIG. 3). In this case, the joining spring 5
5 overcomes the elastic force of the release spring 51 and pushes the clutch par 49 backward, and the pivot 45 interlocks with this.
As the clutch fork 48 rotates, 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. 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, 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 operating lever 68 and the clutch arm 61 are interlocked and connected by a clutch rod 70.

Further, a positioning arm 72 is provided protruding from the cylindrical body 58, and this positioning arm 72 rotates together with the shift fork 40 around the axis of the shifter 39, but is movable relative to the axial direction of the shifter 39. It is engaged with the shift fork 40. A lock bin 73 is provided protruding from this positioning arm 72. On the other hand, the rotation locus of the lock bin 73 accompanying the positioning arm 72 in I-
A corresponding arcuate member 74 is screwed to the vehicle body frame 2. 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 axial movement of the cylinder 58.

In Figures 5 and 6, F1 to F4 of the locking holes 75 marked -1-6 indicate forward lth speed (low speed) to fourth speed (high speed), and R,, R2 represent reverse lth speed and second speed. , and N is the first year of junior high school.
'/ is shown.

[7] Then, by rotating the L notation fl+/par 68 backward, as shown by the solid line in Figs.
The cruncher-1.61 rotates through the door 0, and the J
The cruncher 1 of - pushes the cylinder 58 forward.

As a result, as described above, the driving friction plate 32 is separated from the driven friction plate 3G, and the power transmission from the engine 5 to the driving wheel IO side is disconnected. In this case, the lock bin 73 is disengaged from the chemical hole 75,
The free rotation of the shift fork 4o related to the rotation of the shift drive-39 is corrected.

! When the steering lever 73 is rotated left and right from the state shown below,
Via Shifdro Ndo69 1. The shift door 1141 rotates, and the shifter 39 rotates along with this I-arm 41. As described above, the driven friction plate 36 is moved to a predetermined corresponding position of the driving friction plate 32 by the rotation of the shift I/par 39. In this case, when the driven friction plate 36 moves along the radial center of the rotating surface 32a of the driving friction plate 32, the center of the rotating surface 32a and the outer circumferential surface 36a of the driven friction plate 36 come into contact. To avoid this, the driving friction plate 32 is moved forward by 1" by operating the operating lever 68 f+.

In FIGS. 2 to 4, in the state indicated by the solid line, the driven friction plate 36 is located at the outer circumferential side of the rotating surface 32a of the driving friction plate 32 where the circumferential speed is high; The lock pin 73 corresponds to F4 of the arc-shaped member 74.1. ing.

In this state y2; or Ll) operation; / Move bar 68 forward -11
When the crankshaft 1, 61 is rotated by the number 12, the clutch rod 7o is rotated 12 and the cylindrical body 58 is released from being pushed, as shown by the dashed line in the figure. By the dirt,
Said 1. As shown above, the driving friction plate 32 is frictionally joined to the driven friction plate 36, and power is not transmitted from the engine 5 to the driving wheel 10 side, and the running portion 3 moves forward at high speed.

Also, at this time, the L1 pick pin 73 is inserted into the F of the tithing hole 75.
4, thereby preventing free movement of the driven friction plate 36 of the output shaft 331-.

Then, by operating the operating lever 68 similar to the above, the rotating surface 32a of the driving friction plate 32 is frictionally joined from the inner side in the radial Jj direction (when the driven friction plate 36 is frictionally joined, the circumferential speed of the rotating surface 32a is gradually lowered). As a result, the driven friction plate 36 is rotated at a low speed, and the traveling section 3 is rotated at a low speed T'#7'dj to match the rotation of the driven friction plate 36.

! In this 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 part 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. Further, by moving the driven friction plate 36 to a position corresponding to the top surface 32b of the driving friction plate 32 and rotating the operating lever 68 forward, the cockbin 73 is fitted into the N of the locking hole 75. ,
As shown by the dashed line in FIGS. 5 and 6, this N is formed into a shallow groove so that the lock pin 7
The protruding end of 3 comes into contact with the bottom of N. This prevents the top surface 32b from coming into contact with the outer peripheral portion 36a,
Prevents power transmission from friction plate 32 to driven friction plate 36.
1, and the transmission means 23 is in the intermediate state.

Fig. 7 shows a second embodiment. The bales 1 are shaped to have a large concave arc.
The outer peripheral surface 36a of the driven friction plate 36 is formed so that its cross section is approximately semicircular.

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 in the radial direction of the other friction plate along the rotating surface of the other friction plate, -1- In a transmission device for a working machine such as a snow blower, in which the outer peripheral surface of the other friction plate is friction-bonded to the rotating surface of one friction plate, the rotating surface of one friction plate is formed into a substantially conical shape. Therefore, firstly,
Even if the outer circumferential surface of one friction plate is friction-bonded to the center of the rotational 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 large sliding between the rejoining surfaces and the generation of torsional force, thereby preventing problems in terms of life. 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 where the rotating surface of one friction plate was formed into a surface 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,
The amount of sliding between the joint surfaces is reduced, and as a result, wear of the joint surfaces is suppressed, which is beneficial for the life of the friction plate.

Moreover, in the structural acid described in "-", one of the friction plates is formed so as to form a continuous surface from the radially outer end of its rotating surface toward the center of rotation. When the outer circumferential surface of the other friction plate is sequentially friction-welded at a predetermined interval from the end toward the center of rotation, the change in the gear ratio due to each joint becomes continuous. Therefore, since the movement operation amount of the other friction plate and the change in the gear ratio almost match, the desired gear ratio can be easily obtained and the gear ratio can be changed easily.
-beneficial.

[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 a rV of Fig. 3. - A sectional view taken along the line IV, FIG. 5 is a partial view taken along the v-v line of FIG. 2, FIG. 6 is a plan sectional view of FIG. 5, and FIG. It is a partial plan equivalent view. 1. Snow blower (working machine), 32.. Drive friction plate (one friction plate), 32a-φ rotating surface, 36.. Driven friction plate (other friction plate), 36a.. Outer peripheral surface. ? 54' Near-1-
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;1:, :, □t lj4', ;x2. = ('1,,
): 124 ILμs-fourth stab 2382\
+ Government＼ 'y, 1゜Q, --, hw ----""-'"3G"Q5'
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, 72-Snow ゛・F4 Figure 5. 73-F:1. 73 73 74 F. 1 figure - 'ζ・l [

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 In a transmission device for a work machine such as a snow blower in which the outer circumferential surface of the other friction plate is friction-bonded, the rotating surface of one of the friction plates is formed into a substantially conical shape, and this rotating surface is formed at its radially outer end. 1. A transmission device for a working machine such as a snow blower, characterized in that it is formed so as to form a continuous surface from the top toward the center of rotation.