JPH06305442A - Speed change operating device for vehicle with hydraulic continuously variable transmission - Google Patents

Abstract

(57) [Summary] (Modified) [Purpose] In a vehicle with a hydraulic continuously variable transmission that drives the left and right crawler belts and wheels separately, it is possible to easily return the hydraulic continuously variable transmission to a neutral state. (EN) Provided is a gear shift operation device. [Structure] The gear shift operating device 45 is loosely fitted with a sliding guide member 46 integrally fitted to the swing shaft 28, a ring-shaped sliding member 47 fitted slidably in the axial direction. Cup-shaped member 50
A rotating member 53 integrally connected via a screw 52, three outer V-shaped grooves 48 formed on the outer peripheral surface of the ring-shaped sliding member 47 at equal intervals in the circumferential direction, and a corresponding one. A steel ball 55 fitted into three circular holes 51 formed in the cup-shaped member 50 at a position, a sliding operation lever 56 for axially moving the ring-shaped sliding member 47, and a rotating member 53. The sliding operation lever 56 has a pin 57, and the pin 57 of the sliding operation lever 56 is an inner circumferential groove of the ring-shaped sliding member 47. Engaged with 49.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to, for example, a crawler-type carrier having a crawler track, a construction machine with a caterpillar (registered trademark), a cultivator, a snowmobile, etc. The present invention relates to a gear shift operating device capable of easily returning a hydraulic continuously variable transmission to a neutral state in a vehicle with a continuously variable transmission.

[0002]

2. Description of the Related Art In a vehicle such as a cultivator equipped with crawler tracks and a snowmobile, it is necessary to continuously change the rotational traveling speed of the left and right crawler belts when changing the traveling direction. As a device that meets such a demand, there is a control device (see FIG. 16) described in Japanese Patent Publication No. 49-20418.

In the vehicle shown in FIG. 16, one on the left and one on the right.
A pair of hydraulic continuously variable transmissions 01 are provided, a control arm 02 for continuously changing the gear ratio of the hydraulic continuously variable transmissions 01 is provided, and a control lever 03 is provided in front of the hydraulic continuously variable transmissions 01.
A control box 04 provided with is arranged, and the operation arm 06 is integrally fitted to the outer ends of the operation shaft 05 protruding on both sides of the control box 04.
02 and the operation arm 06 are connected via a connecting rod 07, a differential gear box (not shown) is built in the control box 04, and the control lever 03 can be moved forward or backward without tilting to the left or right. When rocked, both the left and right operation arms 06 and the left and right control arms 02 are rocked forward or backward, and the vehicle is allowed to travel straight forward or backward.

When the control lever 03 is tilted to the left, for example, while the control lever 03 is swung to the front limited position and the vehicle is traveling straight ahead, the right operation arm 06r moves forward. The left operation arm 06l swings backward due to the action of the differential gearbox built in the control box 04 while stopping at the limited position, and only the left control arm 02l tries to return to the neutral side. Therefore, the left crawler belt decelerates or stops, and only the right crawler belt is in a rotational traveling state, and the vehicle can turn left.

[0005]

In the gear shift operating device shown in FIG. 16, when the left and right operation arms 06 are swung to the limit position, the differential gearbox operates reliably to smoothly turn the vehicle. However, if the left and right operation arms 06 are not swung to the local position, the operation arm 06 on the side where the control lever 03 is tilted is not fixed and is swung, so that the left and right operation arms 06 are shaken. The dynamic state was not uniquely determined, and there was a problem that steering became unstable. Also control lever 04
When swinging back and forth and left and right,
It was difficult to fix one track and rotate only the other track.

[0006]

SUMMARY OF THE INVENTION The present invention relates to an improvement of a gear shift operating device for a vehicle with a hydraulic continuously variable transmission that overcomes the above problems, and relates to a left and right traveling device, a power source, and A hydraulic continuously variable transmission that transmits power from a power source to the left and right traveling devices, the hydraulic continuously variable transmission including a pump input shaft that is rotationally driven by power from the power source, and the pump input. A pump having a swash plate swingable with respect to the shaft and supplying pressure oil according to the inclination angle of the swash plate by rotation of the input shaft, and a motor driven by hydraulic pressure generated by the pump. The hydraulic continuously variable transmission includes a pair of left and right hydraulic continuously variable transmissions, and the hydraulic continuously variable transmission is in a neutral state by swinging the swash plate from a plane perpendicular to the pump input shaft and the vertical surface. The vehicle's forward and reverse speeds are In the speed change device of the hydraulic stepless transmission with a vehicle capable of shifting to the floor, the pair of hydraulic continuously variable transmission, a first operating member, and a second operating member, said first
A first operation member that is reciprocally operated in one direction by an operation member, and a second operation member that is reciprocally operated in a direction different from the first operation member by the second operation member, respectively. The operation of the second operation member is transmitted to the swash plate shaft via the first operation member while the first operation member is operated and fixed to one side, and the operation position of the second operation member is fixed. A cam mechanism for swinging the swash plate shaft toward the neutral position by operating the other one of the first operating members is interposed between the first operating member and the second operating member. .

Since the present invention is constructed as described above, when the second operating member is operated in one direction while the first operating member is operated and fixed to one side, the second operating member is moved. By the operation, the second operating member is driven to one side, the first operating section is also driven in conjunction with the second operating member, and the swash plate shaft of the hydraulic continuously variable transmission is swung to one side, The hydraulic continuously variable transmission is steplessly changed to a required gear ratio.

Further, when the hydraulic continuously variable transmission is shifted by the operation of the second operating member, if the first operating member is operated in the reverse direction while the second operating member is fixed, the cam mechanism is operated. As a result, the swash plate shaft is swung toward the neutral position via the first operating member, and the hydraulic continuously variable transmission is returned to the neutral or nearly neutral state.

Therefore, in the present invention, when the second operating members of the pair of hydraulic continuously variable transmissions are connected to each other via the link mechanism, the second operating members are operated to either one. With this, the vehicle can be moved forward or backward, and any one of the first continuously variable transmissions attached to the pair of hydraulic continuously variable transmissions with the second operation member being operated.
By operating the operation member, the operated hydraulic continuously variable transmission can be returned to the neutral state or a state close to the neutral state, and the vehicle can be turned to the left or the right.

As described above, according to the present invention, the vehicle can be continuously advanced or retracted by operating the second operating member, and the pair of first operating members can be fixed with the second operating member fixed. By selectively operating only one of the members, the vehicle can be freely turned to the left or right, so that the running of the vehicle can be easily controlled. Moreover, in the present invention, the forward and backward movements and the turning of the vehicle are separately controlled by the two kinds of operation members, so that the control is reliable and the reliability is extremely high.

Further, in a state where the vehicle is moved forward or backward by operating the second operation member, either one of the first operation members is operated.
By operating only the operating member near the limit, the hydraulic continuously variable transmission on the operated side can be reversed to make a super turning turn, and at the same time, smooth start and forward / backward movement are easy and The horizontal sway becomes extremely small, which is extremely effective when transporting a fluid.

[0012]

[Embodiment] An embodiment of the present invention shown in FIGS. 1 to 13 will be described below. The crawler-type carrier 1 has a vehicle body 2, a loading platform 3 and an engine 4 and left and right 1 behind it.
A pair of hydraulic continuously variable transmissions 5 are arranged, and a crawler belt supporting wheel 6 and a crawler belt driving wheel 7 are arranged behind the crawler belt supporting wheel 6 at predetermined intervals on both left and right sides of the vehicle body 2 in the front-rear direction.
The endless crawler belts 8 are bridged over the crawler belt drive wheels 7 and the crawler belts 8 are individually fed by the rotation of the pair of left and right crawler belt drive wheels 7.

A handle 9 is integrally mounted on the rear portion of the vehicle body 2 so as to be directed obliquely upward, and an operation lever 10 is pivotally supported on the upper end of the handle 9 so as to be swingable back and forth and left and right. Further, the drive pulley 12 is fitted integrally with the crank shaft 11 of the engine 4, and the driven pulley 14 is fitted integrally with the input shaft 13 of the hydraulic continuously variable transmission 5 oriented in the direction parallel to the crank shaft 11. , The drive pulley 12 and the driven pulley 14 have an endless V
A clutch arm 16 on which a belt 15 is bridged and pivotally supported so as to be able to approach or separate from the endless V-belt 15.
A tension pulley 17 is pivotally attached to the tip of the handle, and a tension clutch lever is pivotally attached to the handle 9 so as to be swingable back and forth.
The clutch arm 16 is connected to the clutch arm 16 by a clutch cable 19. When the tension clutch lever 18 is operated forward, the clutch arm 16 swings and the tension pulley 17 is pressed against the endless V belt 15. The belt 15 is tensioned, the power of the engine 4 is transmitted to the hydraulic continuously variable transmission 5, and the rearward operation of the tension clutch lever 18 causes the clutch arm 16 to swing in the opposite direction so that the tension pulley 17 is separated from the endless V belt 15. In this state, the power of the engine 4 is not transmitted to the hydraulic continuously variable transmission 5.

The hydraulic continuously variable transmission 5 is, as shown in FIGS. 4 to 5, a pair of left and right swash plate type axial piston pumps 20 which are rotationally driven by the power from the engine 4 to generate pressure oil. A pair of left and right swash plate type axial piston motors 21 driven by pressure oil generated by the swash plate type axial piston pump 20, a trochoid pump 22 for filling a hydraulic circuit with oil, a housing 23, and the housing 23. And the pair of swash plate type axial piston pumps 20 are not formed symmetrically but have the same shape, and the input shaft 13 of the swash plate type axial piston pump 20 is The swash plate type axial piston motors 21 are arranged in the same manner, while being arranged toward the center of the vehicle body.

In the swash plate type axial piston pump 20, the cylinder block 25 is integrally spline-fitted to the input shaft 13 which is rotatably supported by the housing 23 and the base plate 24, and the cylinder block 25 is arranged in a direction parallel to the input shaft 13. For example, 7
Individual cylinder chambers 26 are formed in the cylinder block 25 at equal intervals in the circumferential direction, and the return coil spring 27 and the piston 28 are fitted in the cylinder block 25, respectively, and the swash plate is opposed to the cylinder block 25. 29 is the swing axis 30
It is pivotally supported by the housing 23 so as to be swingable around.

Further, a swash plate type axial piston motor 21
Then, the output shaft 31 oriented in the direction parallel to the input shaft 13 is rotatably supported by the housing 23 and the substrate 24, and the output shaft 31
The motor block 32 that is spline-fitted to the
Seven cylinder chambers 33 oriented in a direction parallel to 31 are formed at equal intervals in the circumferential direction, and return coil springs 34 and pistons 35 are fitted in the cylinder chambers 33, respectively, and the motor block 32 is mounted on the motor block 32. The swash plate 36 is inclined and fixed relative to each other.

Furthermore, in the swash plate type axial piston pump 20, two swash plates are divided into two semicircles which are divided by a plane passing through the center line of the input shaft 13 connecting the closest point to the cylinder block 25 and the most different point. An arcuate port (not shown) is formed on the base plate 24, and the swash plate type axial piston motor 21 is also provided.
Also, a similar port (not shown) is formed on the substrate 24,
The ports of the swash plate type axial piston pump 20 and the swash plate type axial piston motor 21 are respectively connected through oil passages not shown, and when the swash plate 29 is significantly inclined as shown in FIG. A large amount of pressure oil is generated in the axial piston pump 20 and supplied to the swash plate type axial piston motor 21, and the swash plate type axial piston motor 21 is rotationally driven at high speed to
When 29 is swung so as to be perpendicular to the input shaft 13, no pressure oil is generated in the swash plate type axial piston pump 20, and the swash plate type axial piston motor 21 is not rotationally driven.

Therefore, a neutral valve 37 for connecting and disconnecting an oil passage (not shown) which short-circuits the two ports of the swash plate type axial piston pump 20 to each other.
Is provided on the base plate 24, and when the neutral valve 37 is pushed in, the swash plate type axial piston pump is
The communication between the two ports of 20 is cut off, and the swash plate type axial piston pump 20 and the swash plate type axial piston motor are cut off.
21 and 21 are hydraulically connected to each other so that pressure oil can be supplied from the swash plate type axial piston pump 20 to the swash plate type axial piston motor 21, and when the neutral valve 37 is pulled out, two swash plate type axial piston pumps 20 are provided. Swash plate type axial piston pump with communicating ports
The pressure oil supply from 20 to the swash plate type axial piston motor 21 is cut off.

Further, as shown in FIG. 6, a driving bevel gear 38 is integrally fitted to the outer end of the output shaft 31 of the swash plate type axial piston motor 21, and is rotatably pivoted to the housing 23 by orienting in the front-back direction. Driven bevel gear on front and rear axis 40
The driven bevel gear 39 that meshes with the 38 is integrally fitted and shown in FIG.
As shown in the figure, a gear 41 is integrally fitted to the front ends of the front and rear shafts 40, and a worm shaft 43 oriented in a direction parallel to the front and rear shafts 40 closer to the vehicle body width center than the front and rear shafts 40 rotates on the vehicle body 2. A pinion gear 42, which is freely pivoted and meshes with the gear 41, is integrally fitted to the rear end of the worm shaft 43, and the worm 44 formed on the worm shaft 43 is integrally fitted to the drive shaft 45 of the crawler belt drive wheel 7. The output of the output shaft 31 of the swash plate type axial piston motor 21 that is meshed with the worn worm wheel 46 is a drive bevel gear 38, a driven bevel gear 39, a front and rear shaft 40, a gear 41,
It is adapted to be transmitted to the crawler belt drive wheel 7 via the pinion gear 42, the worm 44, the worm wheel 46 and the drive shaft 45.

Further, as shown in FIG. 7, a swing shaft for swinging the swash plate 29 of the swash plate type axial piston pump 20.
A shift operation device 47 is attached to the 30.

The gear shift operation device 47 includes a sliding guide member 48 integrally fitted to the swing shaft 30, and the sliding guide member 48.
A ring-shaped sliding member that is fitted to the shaft so that it can slide axially 49
And a cup-shaped member 52 loosely fitted to the ring-shaped sliding member 49
A rotating member 55 integrally connected to the cup-shaped member 52 via a screw 54, and three outer V-shaped grooves formed on the outer peripheral surface of the ring-shaped sliding member 49 at equal intervals in the circumferential direction. A steel ball 57 fitted into 50 and three circular holes 53 formed in the cup-shaped member 52 at a position corresponding thereto, and a sliding operation lever 58 for moving the ring-shaped sliding member 49 in the axial direction. A rotation operation lever 60, one end of which is pivotally attached to the arm 56 of the rotation member 55 so as to rotate the rotation member 55, and a pair of rotation operation levers 60, which are coupled to each other. It consists of a link 61 (see FIG. 3) pivotally attached to the other end of the rotary operation lever 60,
The pin 59 of 58 is engaged with the inner circumferential groove 51 of the ring-shaped sliding member 49, and when the sliding operation lever 58 is swung, the ring-shaped sliding member 49 is slid back and forth, and the link When 61 is swung, the turning member 55 is turned via the turning operation lever 60.

Furthermore, the operating lever 10 is connected to a link 61 via a front-rear operating cable 62 and a front-rear operating mechanism 64. When the operating lever 10 is swung forward or backward, the link 61 is reversed in FIG. It is oscillated clockwise or clockwise, and the oscillating shaft 30 of the swash plate type axial piston pump 20 is interlocked with this and together with the rotation operation lever 60, the swash plate type axial piston pump 20 on the right side is rotated clockwise when viewed from the rear. Alternatively, the swash plate type axial piston motor 21 is swung counterclockwise and the swing shaft 30 of the left swash plate type axial piston pump 20 is swung counterclockwise or clockwise as viewed from the rear, and the swash plate type axial piston motor 21 is moved in the forward direction or It is designed to be rotationally driven in the backward direction.

However, in the front-back operation mechanism 64, as shown in FIGS. 10 to 12, the lower end of the tubular body 65 of the operation lever 10 is fitted in the U-shaped holding piece 66 in the front-back direction. The U-shaped holding piece 66 and the tubular body 65 are pivotally attached to the U-shaped holding piece 66 by left and right tilting pivot support pins 67 penetrating the U-shaped holding piece 66 and the lower end of the U-shaped holding piece 66. The inverted U-shaped base piece 68 is integrally fixed to the inverted U-shaped base piece 68, and the inverted U-shaped base piece 68 is provided between the pair of left and right handle brackets 69 (shown only on the left side in FIG. 11) integrally with the handle 9. In the fitted state, the handlebar 69 is pivotally supported by the operating lever support shaft 70 penetrating the handle bracket 69 and the inverted U-shaped base piece 68 in the handle bracket 69 so as to be tiltable back and forth. The lower end of 68 is connected to the upper end of the front / rear operation cable 62, and the operation lever 10
Can be tilted back and forth and left and right.

Further, a knob 71 is freely fitted in the upper and lower portions of the tubular body 65 so as to be vertically retractable, and an inverted U-shaped guide member 73 integrally connected to the knob 71 via a connecting rod 72 is tilted to the left or right. While being fitted to the pivot pin 67, it is fitted in the tubular body 65 so as to be vertically movable.

Further, a pair of left and right long holes 74 oriented vertically are formed on both sides of the tubular body 65 below the left and right tilting pivot support pins 67, and the node pins penetrating the long holes 74 respectively. The 75 is integrally connected to a ring 76 that abuts against the lower end of the inverted U-shaped guide member 73 in the tubular body 65 by the spring force of a coil spring 77 loosely fitted in the tubular body 65. 75
Are arranged on both the left and right sides of the tubular body 65 and are engaged with the corrugated locking portions 79 of the lever guide plate 78 provided integrally with the handle 9. When the operation lever 10 is tilted left and right, While the pin 75 remains tilted to the wavy locking portion 79, the elongated hole 74 on the opposite side to the tilted side moves upward with respect to the nodal pin 75, so that the tubular body 65 moves to the left and right tilting pivot support pin 67. It is designed to be tilted around.

Moreover, the operating lever 10 is a left and right operating cable.
The left and right operation mechanism 80 is connected to the sliding operation lever 58 via the 63 and the left and right operation mechanism 80, and is configured as described below.

That is, a pair of right and left turning drive levers 81 and a left and right driven levers 82 for turning are located in front of and behind the U-shaped holding piece 66 and are fitted on the handle 9 on the extension lines of the left and right tilting pivot support pins 67. A pivoting support lever 81l and a pivoting driven lever 82 on the left side are pivotally supported by a mounted pivoting pin 83 so as to be tiltable.
The lower part of l and the lower part of the turning drive lever 81r and the right part of the swivel driven lever 82r are integrally connected to each other by connecting rods 84l and 84r. When the operating lever 10 is tilted to the left, for example, The lower part of the body 65 contacts the connecting rod 84l, and
In FIG. 0 and FIG. 11, only the turning drive lever 81l and the turning driven lever 82l are tilted counterclockwise.

As also shown in FIGS. 11 and 13,
The top of the bolt 85 is pivotally attached to the upper portion of the turning drive lever 81 via a shaft 86, the lower end of the bolt 85 is screwed into an upper nut 87, and the upper portion of the adjusting bolt 89 is attached to the lower nut 88 and the upper nut 87. Threaded, bolt 85 and adjusting bolt 89
The joint length of the upper nut 87 can be adjusted by adjusting the screwing depth of the upper nut 87, and is fixed by the lower nut 88.

Further, the upper end of the inner cable 99 of the left / right operation cable 63 is integrally bound to the lower end of the adjusting bolt 89, and the protrusion 90 of the adjusting bolt 89 is slidable up and down in the guide groove 92 of the holding sleeve 91. Is fitted to the holding sleeve 91
A coil spring 93 and a ring 94 are loosely fitted on the outer periphery of
The outer case 95 of the left / right operation cable 63 penetrates the receiving piece 96 that is integral with the handle 9, and the outer case 95 of the left / right operation cable 63 is inserted by the nuts 97 and 98 that are vertically screwed to the outer case 95 with the receiving piece 96 interposed therebetween. The upper end of the handle 9
Installed in 96.

By configuring the left / right operation mechanism 80 in this way, when the operation lever 10 is rocked to the right, only the inner cable 99 of the right / left operation cable 63r is attached to the slide operation lever 58. 1, the sliding operation lever 58r attached to the swash plate type axial piston pump 20 in the hydraulic continuously variable transmission 5 on the right side is swung clockwise in FIG. 1 to form a ring shape. The sliding member 49 is pulled out forward, and the operation lever 10
When is swung to the left, only the sliding operation lever 58l attached to the swash plate type axial piston pump 20 in the left hydraulic continuously variable transmission 5 is swung counterclockwise in FIG. The moving member 49 is adapted to be pulled out rearward.

Therefore, the rotational movement amount of the rotating member 55 and the circular hole 53 when the operating lever 10 is operated in the front-rear direction to its local position is R, and the cup-shaped member 52 and the rotating member 55 are fixed. , The operating lever 10 is operated from the vertical state to the left or right to its limit position, and the axial movement amount of the ring-shaped sliding member 49 pushed toward the swash plate type axial piston pump 20 is set to L, and the outer side V is set to V. If the included angle of the groove 50 is 2α, R, L, and α are set so that the relationship of R + ΔR = (L−ΔL) tan α (1) holds. However, ΔR is the length of a foot (L which is a perpendicular line from the center of the steel ball 57 in a state where the steel ball 57 is located at the end of the outer V-shaped groove 50 to the axis of symmetry MM of the outer V-shaped groove 50). −ΔL) tan α and R
The difference ΔL between the turning point O of the groove center line V-O-V of the outer V-shaped groove 50 and the center point B of the steel ball 57 in the state where the steel ball 57 is located at the bottom of the outer V-shaped groove 50. distance,

Since the illustrated embodiment is configured as described above, when the engine 4 is started with the tension pulley 17 pressed against the endless V-belt 15, the crankshaft 11 of the engine 4 drives the drive pulley 12, Left and right 1 in the hydraulic continuously variable transmission 5 via the endless V-belt 15 and the driven pulley 14.
Power is transmitted to the input shaft 13 of the pair of swash plate type axial piston pumps 20.

When the operating lever 10 is vertically oriented and set to the neutral state, the swash plate 29 of the swash plate type axial piston pump 20 is oriented in the direction perpendicular to the input shaft 13, Even if the input shaft 13 is driven to rotate, there is no pressure oil supply from the swash plate type axial piston pump 20, and the swash plate type axial piston motor 21 does not operate, either.
The crawler-type carrier 1 is held in a stopped state, and the ring-shaped sliding member 49 is held in the pushed-in direction A.

When the operation lever 10 is swung forward, for example, at a local position, the operation lever 10 is moved through the front-rear operation cable 62.
The forward swing of 10 is transmitted to the link 61, and the cup-shaped member 52 and the turning member 55 of the left and right gear shift operating devices 47 are moved forward (the right turning operation lever 60 is turned to the left or left). The lever 60 is turned to the right), and the turning angle of the arm 56 of the turning member 55 becomes 15 °. The swash plate type axial piston pump
Since the swing shaft 30 of 20 is swung forward, the pressure oil generated by the swash plate type axial piston pump 20 is supplied to the swash plate type axial piston motor 21, and the swash plate type axial piston motor 21 is driven to the forward side. Left and right crawler drive wheels 7
Is rotated in the forward direction, the crawler belt 8 is forwarded in the forward direction,
The crawler type carrier 1 moves forward.

When the operating lever 10 is further swung rearward, the gear shift operating device 47 is operated in the reverse direction as described above, and the crawler type carrier 1 is retracted.

Further, when the operation lever 10 is tilted to the left, for example, in the state where the crawler type carrier 1 is moved forward, the sliding operation lever 58l of the left speed change operation device 47l is moved in the B direction via the left operation cable 63l. And the ring-shaped sliding member 49 is pulled out in the pulling direction B.

Thus, when the operating lever 10 is tilted to the left to the limit, the outer V-shaped groove is formed based on the axial movement amount L of the ring-shaped sliding member 49, as shown in the equation (1). The rotational movement amount (L−ΔL) tan α of the ring-shaped sliding member 49 and the sliding guide member 48 by 50 exceeds the rotational movement amount R of the rotating member 55, and the rotation angle of the arm 56 of the rotating member 55 is 20 °, figure
As shown in FIG. 15, the symmetry axis of the outer V-shaped groove 50 is N-
The symmetry axis MM of the outer V-shaped groove 50 in the center state shown by N
Since it is rotated by an additional amount ΔR in comparison with the above, only the swing shaft 30 of the left swash plate type axial piston pump 20 moves from the forward side to the neutral position to the backward side (L-ΔL) tan α
-R = ΔR (5 ° at the rotation angle of the arm 56), the output shaft of the left swash plate type axial piston motor 21
31 rotates in the backward direction at a slight speed, and the crawler belt drive wheel 7 on the left side is also driven to rotate slightly in the backward direction, so that the crawler type carrier 1 can turn to the left in the super-confidential state.

Moreover, when the crawler-type carrier 1 is turning to the left and the operating lever 10 tilted to the left is returned to the vertical position, the left speed change operating device 47 of the left operating cable 63l is moved.
The sliding operation lever 58l of 1 is swung back in the direction A, the ring-shaped sliding member 49 is pushed in the pushing direction A, and the output shaft 31 of the left swash plate type axial piston motor 21 rotates forward at full speed. However, the left and right crawler belt drive wheels 7 and the crawler belt 8 are rotated and run at the same forward speed, and thus can return to the straight traveling state.

When the tilting angle of the operating lever 10 to the left is set to half the local tilting angle described above, the rotational movement amount of the ring-shaped sliding member 49 and the sliding guide member 48 is 1.
/ 2 (L-ΔL) tan α, the output shaft 31 of the swash plate type axial piston motor 21 on the left side rotates at about half the speed in the forward direction, and the crawler type carrier 1 makes a large left turn. You can turn in a radius.

Thus, by swinging one operating lever 10 back and forth, the crawler type carrier 1 can be moved forward or backward, and if the operating lever 10 is tilted left and right, the crawler type carrier 1 can be moved. You can turn left or right,
The crawler type carrier 1 can be easily operated.

Further, since the shift operating device 47 is separated into the forward operating system and the left-right turning operating system, the structure can be simplified and the cost can be reduced, and the maintainability and maintainability can be greatly improved. .

[Brief description of drawings]

FIG. 1 is a side view of a vehicle equipped with a shift operating device according to the present invention.

2 is a rear view of the vehicle shown in FIG. 1. FIG.

FIG. 3 is an exploded perspective view of a main part of FIG.

4 is a partially longitudinal rear view of the right half of the vehicle body cut along the line IV-IV in FIG. 1. FIG.

5 is a view taken along the line VV of FIG.

6 is a view taken along line VI-VI in FIG.

FIG. 7 is an exploded perspective view showing an embodiment of the gear shift operating device of the present invention.

FIG. 8 is a vertical cross-sectional side view of essential parts of the embodiment in a state where the operation lever is held neutral and the ring-shaped sliding member 49 is pushed in.

FIG. 9 is a ring-shaped sliding member in which the operation lever is tilted left and right.
FIG. 49 is a vertical sectional side view of a main part of the embodiment, in which 49 is pulled out.

10 is an overall perspective view of a front / rear operation mechanism 64 and a left / right operation mechanism 80. FIG.

11 is a view taken along the line XI-XI of FIG.

12 is an exploded top perspective view of FIG.

13 is a bottom exploded perspective view of FIG.

FIG. 14 is an explanatory diagram illustrating the operating principle in a state where the pressure oil supply from one of the swash plate type axial piston pumps 20 in the above embodiment is zero.

FIG. 15 is an explanatory diagram showing the operation principle of the super-spot turning state of the embodiment.

FIG. 16 is a perspective view of a conventional transmission.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Crawler type transport vehicle, 2 ... Car body, 3 ... Loading platform, 4 ... Engine, 5 ... Hydraulic continuously variable transmission, 6 ... Crawler track support wheel, 7 ... Crawler drive wheel, 8 ... Crawler track, 9 ... Steering wheel, 10 ... Operation Lever, 11
... crankshaft, 12 ... drive pulley, 13 ... input shaft, 14 ... driven pulley, 15 ... endless V-belt, 16 ... clutch arm, 17 ...
Tension pulley, 18 ... Tension clutch lever, 19
... Clutch cable, 20 ... Swash plate type axial piston pump, 21 ... Swash plate type axial piston motor, 22 ... Trochoid pump, 23 ... Housing, 24 ... Board, 25 ... Cylinder block, 26 ... Cylinder chamber, 27 ... Return coil spring, 28 ... Piston, 29 ... Swash plate, 30 ... Oscillation shaft, 31 ... Output shaft, 32 ... Motor block, 33 ... Cylinder chamber, 34 ... Return coil spring, 35 ... Piston, 36 ... Swash plate, 37 ... Neutral valve , 38 ... Drive bevel gear, 39 ... Driven bevel gear, 40 ... Front / rear axis, 41 ... Gear, 42 ... Pinion gear, 43 ... Worm axis, 44 ... Worm, 45 ... Drive axis, 46 ... Worm wheel, 47 ... Gear change operating device, 48 … Sliding guide members, 49…
Ring-shaped sliding member, 50 ... Outer V-shaped groove, 51 ... Inner circumferential groove,
52 ... Cup-shaped member, 53 ... Circular hole, 54 ... Screw, 55 ... Rotating member, 56 ... Arm, 57 ... Steel ball, 58 ... Sliding operation lever, 59 ...
Pin, 60 ... Rotating operation lever, 61 ... Link, 62 ... Front / rear operation cable, 63 ... Left / right operation cable, 64 ... Front / rear operation mechanism,
65 ... Tubular body, 66 ... U-shaped holding piece, 67 ... Left / right tilting pivot support pin, 68 ... Reverse U-shaped base piece, 69 ... Handle bracket, 70 ...
Operating lever support shaft, 71 ... Knob, 72 ... Connecting rod, 73 ... Inverted U-shaped guide member, 74 ... Long hole, 75 ... Nodal pin, 76 ... Ring,
77 ... Coil spring, 78 ... Lever guide plate, 79 ... Wavy locking portion, 80 ... Left and right operating mechanism, 81 ... Rotating drive lever, 82
... Turning driven lever, 83 ... Pivot pin, 84 ... Connecting rod, 85 ...
Bolt, 86 ... Shaft, 87 ... Upper nut, 88 ... Lower nut, 89
… Adjustment bolt, 90… Projection piece, 91… Holding sleeve, 92… Guide groove, 93… Coil spring, 94… Ring, 95… Outer case, 96… Receiving piece, 97,98… Nut, 99… Inner cable.

Claims (4)

[Claims] 1. A left and right traveling device, a power source, and a hydraulic continuously variable transmission that transmits power from the power source to the left and right traveling devices, wherein the hydraulic continuously variable transmission is the power source. Has a pump input shaft that is rotatably driven by the power from and a swash plate that can swing with respect to the pump input shaft, and supplies pressure oil according to the inclination angle of the swash plate by the rotation of the input shaft. It is composed of a pair of left and right hydraulic continuously variable transmissions each having a pump and a motor driven by the hydraulic pressure generated by the pump. In each of the hydraulic continuously variable transmissions, the swash plate is perpendicular to the pump input shaft. In the gear shift operation device for a vehicle with a hydraulic continuously variable transmission, which is capable of ensuring a neutral state by swinging from a vertical plane and the vertical plane and continuously shifting the forward and reverse speeds of the vehicle, The hydraulic continuously variable transmission is the first
An operation member, a second operation member, a first operation member which is reciprocally operated in one direction by the first operation member, and a reciprocal operation in a direction different from the first operation member by the second operation member. And a second operation member for transmitting the operation of the second operation member to the swash plate shaft via the first operation member in a state where the first operation member is operated to one side and fixed. A cam mechanism that swings the swash plate shaft toward the neutral position by operating the other of the first operating members while fixing the operating position of the second operating member includes the first operating member and the second operating member. A gear shift operation device for a vehicle with a hydraulic continuously variable transmission, characterized in that 2. A left and right traveling device, a power source, and a hydraulic continuously variable transmission that transmits power from the power source to the left and right traveling devices, wherein the hydraulic continuously variable transmission is the power source. Has a pump input shaft that is rotatably driven by the power from and a swash plate that can swing with respect to the pump input shaft, and supplies pressure oil according to the inclination angle of the swash plate by the rotation of the input shaft. It is composed of a pair of left and right hydraulic continuously variable transmissions each having a pump and a motor driven by the hydraulic pressure generated by the pump. In each of the hydraulic continuously variable transmissions, the swash plate is perpendicular to the pump input shaft. In the gear shift operation device for a vehicle with a hydraulic continuously variable transmission, which is capable of ensuring a neutral state by swinging from a vertical plane and the vertical plane and continuously shifting the forward and reverse speeds of the vehicle, The hydraulic continuously variable transmission slides on the swash plate shaft in the axial direction. A sliding member that is spline-fitted at present, a rotating member that is rotatably fitted to the sliding member and is fixed in the axial direction, and a sliding operation member that slides the sliding member, A rotary operation member for rotating the rotary member is provided, and the operation of the rotary operation member is transmitted to the swash plate shaft via the slide member while the slide operation member is operated to one side. And a cam mechanism for rotating the swash plate shaft toward the neutral position by operating the other of the sliding operation members while fixing the rotating position of the rotating operation member. A gear shift operation device for a vehicle with a hydraulic continuously variable transmission, characterized in that 3. A V-groove having an axis of symmetry as an axis of symmetry is formed on an outer periphery of the sliding member, and a concave portion located at a portion corresponding to the V-groove is formed on an inner peripheral surface of the rotating member. A sphere is interposed between the V groove of the sliding member and the recess of the rotating member,
The gear shift operating device for a vehicle with a hydraulic continuously variable transmission according to claim 2, characterized in that the cam mechanism is constituted by a recess and a ball. 4. A shape and dimensions in which the amount of circumferential movement of the ball when the sliding member is slid from one side to the other is larger than the amount of circumferential movement of the turning member recessed by the turning operation member. The gear shift operation device for a vehicle with a hydraulic continuously variable transmission according to claim 3, wherein the V groove is formed in the.