JPH0544833A - Running gear of working machine - Google Patents

Abstract

(57) [Summary] [Purpose] The purpose is to enable high-speed running at the maximum output of the engine and effectively utilize the output of the engine. A transmission case 1 having an auxiliary transmission mechanism 3 including a transmission gear group 4 capable of changing the rotation of an input shaft 2 by operating an auxiliary transmission lever 16, and an input side variable output capable of changing output by operating a main transmission lever 15. In the traveling device having the hydraulic continuously variable transmission 8 including the displacement pump 9 and the output side variable displacement motor 10, the variable displacement motor 1 is provided.
The motor swash plate tilt changing arm 14 is attached to the position 0. The motor swash plate tilt changing arm 14 includes the main shift lever 15
Alternatively, any one of the auxiliary transmission levers 16 is connected to the variable displacement pump 9 so that the variable displacement motor 10 has the maximum output when the variable displacement pump 9 has the maximum output.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a traveling device for a working machine such as a combine.

[0002]

2. Description of the Related Art Conventionally, a transmission case having an auxiliary transmission mechanism including a transmission gear group capable of changing the rotation of an input shaft by operating an auxiliary transmission lever, an input side variable displacement pump whose output can be changed by operating the main transmission lever, and A traveling device having a hydraulic continuously variable transmission including an output side constant displacement motor is known.

[0003]

In the above-mentioned known example, since a constant displacement motor on the output side is used, the maximum speed that can be traveled by changing the output of the variable displacement pump cannot be achieved. .. However, since the hydraulic continuously variable transmission is set so that the engine output has a margin even when the output of the variable displacement pump is maximized, the engine output is not set at high speed running at the maximum engine output. There is a problem that it is not used effectively.

[0004]

An object of the present invention is to enable high speed running at the maximum output of the engine and effectively utilize the output of the engine.

[0005]

Therefore, according to the present invention, there is provided a transmission case 1 having a sub-transmission mechanism 3 including a group of speed change gears 4 capable of changing the rotation of the input shaft 2 by operating a sub-transmission lever 16, and a main transmission. In a traveling device having a hydraulic continuously variable transmission 8 including an input side variable displacement pump 9 and an output side variable displacement motor 10 whose output can be changed by operating a lever 15, the variable displacement motor 10 has a motor swash plate tilt. A change arm 14 is attached, and when the variable displacement pump 9 has the maximum output, the variable displacement motor 10 outputs the maximum output when the variable swash plate inclination change arm 14 and the main transmission lever 15 or the auxiliary transmission lever 16 are connected. It is a traveling device of a working machine that is connected in a related manner.

[0006]

Embodiments of the present invention will be described with reference to the drawings.
Is a mission case that drives a traveling device provided below the machine body of a working machine such as a combine. In the mission case 1, there is an input shaft 2 and a gear of an auxiliary transmission mechanism 3 that can change the rotation of the input shaft 2. It has a group 4 and a shifter 5 for switching the gear group 4, a side clutch 6 for turning on and off the rotation from the input shaft 2, an axle 7 for driving the drive wheels of the traveling device, and the like. The mission case 1 is provided with a hydraulic continuously variable transmission 8 that continuously changes the rotation of the engine and transmits the rotation to the input shaft 2. The hydraulic continuously variable transmission 8 includes a variable displacement pump 9 and a variable displacement motor 10, and changes the inclination angles of the pump swash plate 11 and the motor swash plate 12 of the variable displacement pump 9 and the variable displacement motor 10, respectively. Thus, the rotational speed and the rotational torque can be changed. Thirteen
Is a pump swash plate tilt changing arm for changing the tilt angle of the pump swash plate 11 of the variable displacement pump 9, and 14 is a motor swash plate tilt changing arm for changing the tilt angle of the motor swash plate 12 of the variable displacement motor 10. ..

In the operating section of the working machine, the main transmission lever 15 for rotating the pump swash plate inclination changing arm 13 of the variable displacement pump 9 of the hydraulic continuously variable transmission 8 and the sub transmission mechanism 3 are provided. An auxiliary shift lever 16 for operating a shifter 5 for switching the gear group 4 is provided. Further, any one of the main shift lever 15 and the sub shift lever 16 and the motor swash plate tilt changing arm 14 is configured so that the pump swash plate tilt changing arm 13 rotates and the variable displacement pump 9 transmits high speed rotation. When either the main speed change lever 15 or the sub speed change lever 16 is operated on the high speed side with the pump swash plate 11 tilted to the maximum, the motor swash plate tilt change arm 14 is rotated in conjunction with this operation. The variable displacement motor 10 is associated with the input shaft 2 so as to incline the motor swash plate 12 so as to transmit high speed rotation. That is, since the conventional hydraulic continuously variable transmission 8 is composed of the variable displacement pump and the constant displacement motor, the maximum speed that can be traveled by changing the inclination angle of the swash plate of the variable displacement pump. Since the hydraulic continuously variable transmission 8 for transmitting the rotation of the engine normally transmits the rotation to the input shaft 2 with a margin, if the motor can be of a variable displacement type and the inclination angle of the swash plate can be changed, the input shaft 2 is changed. The number of rotations transmitted can be further increased.

According to the present invention, the hydraulic continuously variable transmission 8 is constructed by including the variable displacement pump 9 and the variable displacement motor 10, and the variable displacement pump 9 allows the main transmission lever 15 or When any one of the auxiliary transmission levers 16 is tilted, the inclination angle of the motor swash plate 12 of the variable displacement motor 10 is changed to enable output at the maximum horsepower point at all times, and the wheel output required torque and the hydraulic continuously variable transmission 8 are provided. The maximum output torque is matched with the maximum output torque, and the rotation of the engine is effectively transmitted to the axle 7 to enable high speed traveling. Hereinafter, a connection structure of the main shift lever 15 or the sub shift lever 16, the pump swash plate tilt changing arm 13 and the motor swash plate tilt changing arm 14 will be described.

In the first embodiment shown in FIGS. 1 to 3, the base portion of the arm 17 is fixed to the base portion of the main shift lever 15, and one end of the rod 18 is pivotally attached to the tip of the arm 17. Rod 18
One end of the control arm 19 is pivotally attached to the other end of the.
The central portion of the control arm 19 is axially attached to the machine body by a shaft 20, and an engaging groove 21 is formed at the other end of the control arm 19. The engaging groove 21 is used for the control arm 19.
Is formed to be long in the longitudinal direction, and the tip 22 of the pump swash plate tilt changing arm 13 is engaged. An arc-shaped escape groove 23, which is long in the rotation direction of the control arm 19, is formed in communication with the engagement groove 21. When the main shift lever 15 is tilted to the high speed side, the control arm 19 causes the engagement groove 21 side of the control arm 19 to rotate downward, which causes the pump swash plate tilt changing arm 13 to rotate downward to move the pump tilt of the variable displacement pump 9. Although the plate 11 is tilted, when the pump swash plate 11 reaches the maximum tilted state, the pump swash plate tilt changing arm 13
The tip 22 of the pump is exposed in the escape groove 23, and the pump swash plate tilt changing arm 13 does not rotate even if the control arm 19 rotates.

Further, the motor swash plate inclination changing arm 14
Of the control arm 19 is located below the other end of the control arm 19, and when the control arm 19 is in a position where the pump swash plate tilt changing arm 13 faces the escape groove 23, the other end lower surface of the control arm 19 is located on the motor swash plate. The tip 24 of the tilt changing arm 14 is rotated to rotate the variable displacement motor 10.
The motor swash plate 12 is tilted to increase the rotation transmitted to the input shaft 2 so that the traveling device travels at the maximum speed. 25 is a spring. Reference numeral 26 denotes a neutral holding arm that holds the rotation of the control arm 19 when the main shift lever 15 is in the neutral position.
6 has a lower portion pivotally attached to the fuselage side, an engaging groove 27 is formed in an intermediate portion of a neutral holding arm 26, and an engaging protrusion 28 formed at one end of the control arm 19 is engaged with the engaging groove 27. The upper end of the neutral holding arm 26 is locked at the other end of a spring 29 having one end locked to the machine body side, and the elastic force of the spring 29 restricts the rotation of the control arm 19. The relationship between the main shift lever 15 and the arm 17 is as follows.
The arm 17 rotates when 5 is tilted forward, but the arm 17 does not rotate when the main transmission lever 15 is tilted backward. In the figure, 30 is a passive pulley that receives rotation from the engine, and 31 is a connecting mechanism between the sub-transmission lever 16 and the shifter 5 of the sub-transmission mechanism 3.

In the second embodiment shown in FIG. 4, the base of the arm 17 is fixed to the base of the main shift lever 15, the arm 17 and the pump swash plate tilt changing arm 13 are directly connected by a rod 18, and the auxiliary shift is performed. The lever 16 and the motor swash plate inclination changing arm 14 are configured to interlock with each other. That is, the base portion of the sub-shift lever 16 is fixed to the base portion of the control arm 32 that rotates in conjunction with the rotation of the sub-transmission lever 16. An engagement groove 33 is formed in the control arm 32, and an engagement pin 35 provided at one end of the intermediate arm 34 is engaged with the engagement groove 33. An escape groove 36 is provided in the engaging groove 33.
To communicate with each other. One end of a rod 37 is pivotally attached to the other end of the intermediate arm 34, and the other end of the rod 37 is pivotally attached to an operating arm 38 that operates the shifter 5 of the sub transmission mechanism 3. In the vicinity of the control arm 32, a central portion of a second intermediate arm 39 is axially attached to the machine body by a shaft 40, and a rod 41 is provided between one end of the second intermediate arm 39 and the motor swash plate inclination changing arm 14. The other end of the second intermediate arm 39 is located below the tip of the control arm 32.

When the auxiliary shift lever 16 is tilted between the low speed position and the high speed position, the control arm 32 is moved.
When the engaging groove 33 of the intermediate arm 34 rotates the engaging pin 35 side of the intermediate arm 34 downward and further tilts it from the high speed position to the traveling position, the engaging pin 35 simply moves in the escape groove 36 of the control arm 32. The shifter 5 of the sub transmission mechanism 3 does not operate. When the auxiliary transmission lever 16 is tilted from the high speed position to the traveling position, the lower surface of the control arm 32 contacts the other end of the second intermediate arm 39, and the rotation of the second intermediate arm 39 causes the motor swash plate tilt changing arm to rotate. The motor swash plate 12 of the variable displacement motor 10 is tilted by 14 so as to travel at the highest speed. Reference numeral 42 is an output pulley for outputting to the harvesting section of the combine.

In the third embodiment shown in FIGS. 5 and 6, the base of the speed change arm 43 is fixed to the base of the auxiliary speed change lever 16,
The tip of the speed change arm 43 and the shifter 5 of the sub speed change mechanism 3
An arbitrary gear shifting coupling mechanism 31 is provided between the arm 44 and the operating arm 38, and the intermediate portion of another L-shaped arm 45 is pivotally attached to the shaft 44 to which the base portion of the sub-transmission lever 16 is pivotally attached, and the upper end 46. Is provided with a U-shaped engaging member 47, and an arbitrary connecting mechanism 49 is provided between the lower end 48 and the motor swash plate tilt changing arm 14 of the variable displacement motor 10. The engaging member 47 is located below the high speed position of the speed change groove 50 of the plate of the auxiliary speed change lever 16, and the upper side in FIG. 6 is opened. That is, the speed change groove 50 is bent at a high speed position to form a key shape, and a low speed side groove 51 between a low speed position and a high speed position, and a running side groove 52 communicating with the low speed side groove 51 at a high speed position. The engaging member 47 does not engage with the engaging member 47 even if the auxiliary shift lever 16 is tilted in the low speed side groove 51, and moves to the engaging member 47 when the auxiliary shift lever 16 is moved from the high speed position into the running side groove 52. When the auxiliary shift lever 16 is engaged and the auxiliary shift lever 16 is tilted from the high speed position to the traveling position in this state, the engaging member 47 rotates the L-shaped arm 45 in accordance with the tilt of the auxiliary shift lever 16, and the variable displacement motor 10 is engaged. The motor swash plate tilt changing arm 14 is rotated.

In the fourth embodiment shown in FIGS. 7 to 9, the pump engagement member 53 is located below the low speed side groove 51 at the high speed position from the low speed position of the speed change groove 50 of the auxiliary transmission lever 16.
A motor engaging member 54 is provided below the traveling side groove 52 at a traveling position from the high speed position of the speed changing groove 50, and the pump engaging member 53 and the motor engaging member 54 are any speed change coupling mechanisms 31. The connecting mechanism 64 connects the pump swash plate tilt changing arm 13 and the motor swash plate tilt changing arm 14 of the hydraulic continuously variable transmission 8. That is, the intermediate portion of another L-shaped arm 55 is pivotally attached to the shaft 44 to which the base portion of the sub-transmission lever 16 is pivotally attached, the pump engaging member 53 is provided at the upper end 56, and the lower end 57 and the variable capacity are provided. An arbitrary connecting mechanism 58 is provided between the pump 9 and the pump swash plate inclination changing arm 13, an intermediate portion of another L-shaped arm 59 is attached to the shaft 44, and an upper end 60 is engaged with a motor. A member 54 is provided, and an arbitrary connecting mechanism 49 is provided between the lower end 61 and the motor swash plate tilt changing arm 14 of the variable displacement motor 10. The auxiliary shift lever 16 engages with the pump engagement member 53 in the low speed side groove 51 between the low speed position and the high speed position of the speed change groove 50 to rotate the pump swash plate inclination changing arm 13 of the variable displacement pump 9. When the auxiliary transmission gear 16 is moved to a high speed position and the pump swash plate 11 of the variable displacement pump 9 is tilted to the maximum, and the auxiliary transmission lever 16 enters the travel side groove 52 on the travel position side from the high speed position, the variable speed is changed. With the pump swash plate 11 of the displacement pump 9 left as it is, the motor swash plate tilt changing arm 14 of the hydraulic continuously variable transmission 8 is engaged with the motor engagement member 54.
Is rotated to incline the motor swash plate 12 of the hydraulic continuously variable transmission 8 to further increase the number of revolutions and drive at the highest speed.

In the fifth embodiment of FIG. 10, the base portion of the main transmission lever 15 is pivotally attached to the upper end 65 of the L-shaped arm 64 by a shaft 65, and the main transmission lever 15 is attached to one end 65 of the L-shaped arm 64. A spring 67 that rotates integrally with the L-shaped arm 64 is provided, and the upper end of the rod 69 is pivotally attached to the tip of the other end 68 of the L-shaped arm 64. The tip of the pump swash plate inclination changing arm 13 is pivotally attached to the lower end of the rod 69. At a position on the rotation locus line of the main transmission lever 15, the intermediate arm 70
The central portion of the intermediate arm 70 is pivotally attached to the machine body side by a shaft 71 so that one end 72 of the pump is tilted, and the one end 72 causes the main shift lever 15 to rotate the pump swash plate tilt changing arm 13 to the maximum. Then, the other end 73 of the intermediate arm 70 and the motor swash plate inclination changing arm 14 are connected by a rod 74. The L-shaped arm 6
When the main transmission lever 15 is tilted to the high speed side, the pump swash plate inclination changing arm 13 is rotated to incline the pump swash plate 11 of the variable displacement pump 9, but when the pump swash plate 11 is in the maximum inclination state. , The L-shaped arm 64 does not rotate, the main shift lever 15 rotates against the elastic force of the spring 67 and abuts against one end 72 of the intermediate arm 70 to rotate, and the one end 72 of the variable displacement motor 10 rotates. The motor swash plate tilt changing arm 14 is rotated to tilt the motor swash plate 12 of the variable displacement motor 10 to increase the rotation transmitted to the input shaft 2 so that the traveling device travels at the maximum speed.

11 and 12 show a sixth embodiment. The variable displacement pump 9 is provided in the forward oil passage 75 of the hydraulic continuously variable transmission 8. The variable oil pump 75 is provided in the forward oil passage 75. The oil passage 77 from another oil feed pump 76 is connected, and the oil feed pump 76 is connected.
A switching valve 78 is provided between the oil passage 77 and the oil passage 77. That is, when the oil feed pump 76 is in an unloaded state, the switching valve 7
When 8 is switched and oil is fed from the oil feed pump 76 to the forward oil passage 75 via the oil passage 77, the amount of oil flowing into the motor 10 'increases, and the rotation speed transmitted by the motor 10' to the input shaft 2 is increased. Is raised, and high speed running becomes possible. 79 is a reverse passage oil passage, 80 is a check valve, 81 is the main shift lever 1
5 is a position detection switch, 82 is a changeover switch for the changeover valve 78 provided on the main shift lever 15, and 83 is a solenoid for the changeover valve 78.

[0017]

[Operation] Next, the operation will be described. The present invention is configured as described above, and when the engine is rotated, this rotation is transmitted to the hydraulic continuously variable transmission 8, and the hydraulic continuously variable transmission 8 is operated by continuously operating the main transmission lever 15 to input the continuously variable transmission. Rotation from the engine is transmitted while changing the rotation speed to the shaft 2, and the shifter 5 of the auxiliary transmission mechanism 3 is operated by operating the auxiliary transmission lever 16 to change the rotation of the input shaft 2 to the axle 7. It transmits and makes the traveling device of the working machine travel. When the main shift lever 15 is tilted to the high speed side, the tilt angle of the pump swash plate 11 of the variable displacement pump 9 of the hydraulic continuously variable transmission 8 is changed to increase the rotation speed transmitted to the input shaft 2. However, in the present invention, since the motor of the hydraulic continuously variable transmission 8 is formed in the variable displacement motor 10, if the motor swash plate 12 of the variable displacement motor 10 is further tilted in the above-described state, the maximum horsepower point will always be reached. Output is possible, and the wheel output required torque and the maximum output torque of the hydraulic continuously variable transmission 8 are matched,
The rotation of the engine can be effectively transmitted to the axle 7 for high speed traveling.

In the first embodiment of FIG. 1, the main transmission lever 15
When the arm is tilted to the forward side, the arm 17 rotates to pull the rod 18, and the rod 18 moves the control arm 19 to the shaft 20.
The control groove 19 of the control arm 19
The reference numeral 1 indicates that the pump swash plate tilt changing arm 13 of the variable displacement pump 9 of the hydraulic continuously variable transmission 8 is rotated downward, and when the pump swash plate tilt changing arm 13 is rotated downward, the variable displacement pump 9 is rotated.
The pump swash plate 11 is tilted. When the pump swash plate 11 reaches the maximum tilt state, the pump swash plate tilt changing arm 13
The tip 22 of the pump faces the relief groove 23, and even if the control arm 19 is rotated, the pump swash plate tilt changing arm 13
However, the lower surface of the control arm 19 has the tip 2 of the motor swash plate tilt changing arm 14 of the variable displacement pump 9.
4, the control arm 19 turns the tip 24 of the motor swash plate tilt changing arm 14 when the pump swash plate tilt changing arm 13 reaches the escape groove 23. Then, the motor swash plate 12 of the variable displacement motor 10 is tilted, the number of rotations transmitted to the input shaft 2 is further increased, and the traveling device is caused to travel at the maximum speed. Therefore, since the outputs of the variable displacement pump 9 and the variable displacement motor 10 can be continuously adjusted by operating the main shift lever 15, operability is improved.

In the second embodiment of FIG. 4, the main transmission lever 15
Is tilted to the forward side, the arm 17 pivots to pull the rod 18, and the rod 18 pivots the pump swash plate tilt changing arm 13 of the variable displacement pump 9 downward to move the pump swash plate 11 of the variable displacement pump 9. Incline to increase the traveling speed. Next, when the auxiliary shift lever 16 is tilted from the low speed position to the high speed position, the engaging groove 33 of the control arm 32 causes the engaging pin 35 side of the intermediate arm 34 to rotate downward, and further tilts from the high speed position to the traveling position. Then, the engagement pin 35 only moves in the escape groove 36 of the control arm 32, and the shifter 5 of the sub transmission mechanism 3 does not operate, but the lower surface of the control arm 32 contacts the other end of the second intermediate arm 39. The second intermediate arm 39 is rotated in contact with the second intermediate arm 39, and the second intermediate arm 39 rotates the motor swash plate inclination changing arm 14 to incline the motor swash plate 12 of the variable capacity motor 10 so that the traveling device travels at the highest speed. .. Further, since the output of the variable displacement motor 10 does not change when the auxiliary shift lever 16 is tilted from the low speed position to the high speed position, when the reverse rotation mechanism is provided in the mission case 1, the auxiliary speed change lever 16 is turned or swung. (Swiping turn) can be performed with a margin, and the relationship between the working speed of the mowing unit and the traveling speed does not change, and good work can be expected.

In the third embodiment shown in FIGS. 5 and 6, when the main transmission lever 15 is tilted, the pump swash plate tilt changing arm 13 of the variable displacement pump 9 is rotated to rotate the variable displacement pump 9, though not shown. The pump swash plate 11 of 9 is inclined to increase the traveling speed. Next, when the sub shift lever 16 is tilted in the low speed side groove 51 of the shift groove 50 between the low speed position and the high speed position, the shifter of the sub speed change mechanism 3 is switched via the connecting mechanism 31. At this time, the sub-shift lever 16 moves the L-shaped arm 4
5 is not engaged with the engaging member 47 of FIG. 5, but is moved from the high speed position into the traveling side groove 52, the auxiliary shift lever 16 is engaged with the engaging member 47, and in this state, the auxiliary shift lever 16 is moved to the high speed position. When the auxiliary shift gear 16 is tilted to the traveling position, the engaging member 47 rotates the L-shaped arm 45 in accordance with the tilting operation of the auxiliary transmission lever 16,
The L-shaped arm 45 rotates the motor swash plate inclination changing arm 14 of the variable displacement motor 10 of the hydraulic continuously variable transmission 8 via the connecting mechanism 49, and the motor swash plate inclination changing arm 14 is the motor of the variable displacement motor 10. The inclination angle of the swash plate 12 is changed so that the traveling device travels at the highest speed.

In the fourth embodiment shown in FIGS. 7 to 9, the auxiliary shift lever 16 is engaged with the pump engaging member 53 in the low speed side groove 51 between the low speed position and the high speed position of the speed change groove 50. When the sub gear shift lever 16 is tilted, the sub gear shift lever 16 pivots to move the pump engagement member 53 to pivot the L-shaped arm 55, and the variable displacement pump 9 via the coupling mechanism 49. When the pump swash plate tilt changing arm 13 is rotated and the sub shift lever 16 is positioned at the high speed position, the pump swash plate 11 of the variable displacement pump 9 is tilted to the maximum, and the sub shift lever 16 is located on the traveling position side from the high speed position. Running side groove 52
When entering, the pump swash plate 11 of the variable displacement pump 9 is left as it is, and the motor swash plate tilt changing arm 14 of the hydraulic continuously variable transmission 8 is rotated by engaging with the motor engaging member 54. The motor swash plate 12 of the continuous variable transmission 8 is tilted to further increase the rotation speed and drive at the highest speed.

In the fifth embodiment of FIG. 10, the main transmission lever 1
5 is tilted to the high speed side, the main speed change lever 15 moves the L-shaped arm 6
4, the other end 68 of the L-shaped arm 64 pushes the rod 69, and the rod 69 rotates the pump swash plate tilt changing arm 13 to rotate the pump swash plate 11 of the variable displacement pump 9. Incline. When the pump swash plate 11 is in the maximum tilted state, the L-shaped arm 64 does not rotate and the main transmission lever 1
When 5 is further rotated against the elastic force of the spring 67, the main shift lever 15 contacts and rotates one end 72 of the intermediate arm 70, and the one end 72 has the motor swash plate tilt changing arm 14 of the variable displacement motor 10. Is rotated to incline the motor swash plate 12 of the variable displacement motor 10 to increase the rotation transmitted to the input shaft 2 so that the traveling device travels at the maximum speed.

In the sixth embodiment shown in FIGS. 11 and 12, when the oil feed pump 76 is in a no-load state, the switching valve 78 is switched to move the oil feed pump 76 through the oil passage 77 to the forward oil passage 7.
When oil is sent to 5, the amount of oil flowing into the motor 10 'from the variable displacement pump 9 increases, the rotational speed of the motor 10' transmitted to the input shaft 2 is increased, and high-speed traveling becomes possible. In this case, the increased oil is discharged from the check valve 80, so that the hydraulic continuously variable transmission 8 maintains a constant hydraulic pressure.

[0024]

According to the present invention, the rotation of the input shaft 2 is controlled by the auxiliary transmission lever 16.
And a main transmission lever 1 having a sub transmission mechanism 3 including a group of transmission gears 4 that can be shifted by
Input side variable displacement pump 9 whose output can be changed by the operation of 5
In the traveling apparatus having the hydraulic continuously variable transmission 8 including the output side variable displacement motor 10 and the output side variable displacement motor 10, the variable displacement motor 10 is provided with the motor swash plate inclination changing arm 14 and the motor swash plate inclination changing arm 14 A traveling device for a working machine in which either the main shift lever 15 or the sub shift lever 16 is connected to the variable displacement pump 9 so that the variable displacement motor 10 has the maximum output when the variable displacement pump 9 has the maximum output. Therefore, the output of the variable displacement pump 9 of the hydraulic continuously variable transmission 8 is increased by operating the main shift lever 15 on the high speed side, and in this state, either the main shift lever 15 or the sub shift lever 16 is operated. Then, the output of the variable displacement motor 10 is further increased, and the rotation of the engine is effectively transmitted to the traveling device, so that high speed traveling can be performed.

[Brief description of drawings]

FIG. 1 is a diagram of a first embodiment.

FIG. 2 is a state diagram of the same operation.

FIG. 3 is a state diagram of the same operation.

FIG. 4 is a second embodiment diagram.

FIG. 5 is a diagram of a third embodiment.

FIG. 6 is a plan view of the same.

FIG. 7 is a fourth embodiment diagram.

FIG. 8 is a state diagram of the same operation.

FIG. 9 is a side view of the same.

FIG. 10 is a diagram of a fifth embodiment.

FIG. 11 is a circuit diagram of a sixth embodiment.

FIG. 12 is a schematic explanatory view of the same.

[Explanation of symbols]

1 ... mission case, 2 ... input shaft, 3 ... auxiliary transmission mechanism,
4 ... Gear group, 5 ... Shifter, 6 ... Side clutch, 7 ... Axle, 8 ... Hydraulic continuously variable transmission, 9 ... Variable displacement pump, 1
0 ... Variable displacement motor, 10 '... Motor, 11 ... Pump swash plate, 12 ... Motor swash plate, 13 ... Pump swash plate tilt changing arm, 14 ... Motor swash plate tilt changing arm, 15 ... Main shift lever, 16 ... Sub Gear shift lever, 17 ... Arm, 18 ... Rod, 19 ... Control arm, 20 ... Shaft, 21 ... Engaging groove, 22 ... Tip, 23 ... Escape groove, 24 ... Tip, 25 ... Spring, 26 ... Neutral holding arm, 27 ... engagement groove, 28 ... engagement protrusion, 29 ... spring, 30 ... passive pulley, 31 ... coupling mechanism, 32 ... control arm, 33 ... engagement groove, 34 ...
Intermediate arm, 35 ... Engaging pin, 36 ... Escape groove, 37 ... Rod, 38 ... Actuating arm, 39 ... Second intermediate arm, 40
... Shaft, 41 ... Rod, 42 ... Output pulley, 43 ... Gear changing arm, 44 ... Shaft, 45 ... L-shaped arm, 46 ... Upper end, 4
7 ... Engaging member, 48 ... Lower end, 49 ... Connection mechanism, 50 ... Gear changing groove, 51 ... Low speed side groove, 52 ... Traveling side groove, 53 ... Pump engaging member, 54 ... Motor engaging member, 55 ... L Mold arm, 56 ... upper end, 57 ... lower end, 58 ... coupling mechanism, 59
... L-shaped arm, 60 ... Upper end, 61 ... Lower end, 64 ... L-shaped arm, 65 ... One end, 66 ... Shaft, 67 ... Spring, 68 ... Other end, 69 ... Rod, 70 ... Intermediate arm, 71 ... Shaft, 72
... one end, 73 ... other end, 74 ... rod, 75 ... forward oil passage, 76 ... oil pump, 77 ... oil passage, 78 ... switching valve, 79 ... reverse oil passage, 80 ... check valve, 81 ...
Position detection switch, 82 ... Changeover switch, 83 ... Solenoid.

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[Procedure amendment]

[Submission date] September 27, 1991

[Procedure Amendment 1]

[Document name to be corrected] Drawing

[Correction target item name] All drawings

[Correction method] Change

[Correction content]

[Fig. 2]

[Figure 6]

[Figure 7]

[Figure 1]

[Figure 8]

FIG. 11

[Figure 3]

[Figure 4]

[Figure 5]

[Figure 9]

[Figure 10]

[Fig. 12]

Claims (1)

[Claims] 1. A transmission case 1 having an auxiliary transmission mechanism 3 composed of a transmission gear group 4 capable of changing the rotation of an input shaft 2 by operating an auxiliary transmission lever 16, and an input whose output can be changed by operating a main transmission lever 15. In a traveling device having a hydraulic continuously variable transmission 8 including a side variable displacement pump 9 and an output side variable displacement motor 10, a motor swash plate inclination changing arm 14 is attached to the variable displacement motor 10 and the motor swash plate is attached. Inclination changing arm 14 and the main shift lever 15
Alternatively, when the variable displacement pump 9 has the maximum output, one of the auxiliary transmission levers 16 is connected to the variable displacement motor 10
Is a traveling device for work equipment that is connected so that the maximum output can be obtained.