JPH0716017A - Steering operation device such as combine - Google Patents

Abstract

(57) [Abstract] [Purpose] When performing steering operation or turning operation when traveling straight ahead in the combine strike, the differential speed that gives a speed difference to the traveling crawlers on one side can be continuously changed. Improve steering and turning. [Structure] A steering clutch shaft transmission system A for transmitting from an input shaft 1 to a steering clutch shaft 2 and a diff increasing device for increasing the rotation of a diff case 5 of a diff device 4 for differentially manipulating the left and right steering clutches 3. In a transmission device provided with a high speed clutch 6 and a steering clutch transmission system B which is transmitted by a differential reduction brake 7 for reducing the rotation of the differential case 5, a steering control for disengaging the left and right steering clutches 3 A power steering hydraulic circuit 13 having a relief valve 12 operated by a power steering lever 11 for operating the steering control valve 9 on the oil discharge side of the steering hydraulic circuit 10 having the valve 9 and the actuator 8. Actuator of the differential speed increasing clutch 6 which is switched by the mode switching valve 14.
A steering operation device such as a combine, which is provided with an actuator 15 of the differential speed reduction brake 7.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a steering operation device such as a combine and the like. The left and right steering clutches for performing steering operation and turning operation are accelerated or decelerated by increasing or decreasing the diff case of the diff device. Differential running mode and spin running mode
It can be used for things that can be switched to a mode.

[0002]

2. Description of the Related Art Turning is made to change the direction of a machine body in a headland of a field or the like. Recently, during this turning, a running crawler inside the turning is turned. There are some types of vehicles that make a turn by a differential run that gives a speed difference to the outside running crawler, but most of these differential speeds are constant speeds, and turning performance depends on the degree of softness of the soil surface. May be hindered. In addition, even when the steering operation is performed to the left and right when the aircraft is moving straight, this method does not provide sufficient steering action depending on the soil condition, and the steering action is insufficient. If the steering action is performed at a high differential speed, it may be too effective and meander, hindering the mowing operation.

Therefore, in the present invention, in the differential traveling, the differential speed on the steering clutch disengagement side during the steering operation and the differential speed of the traveling crawler on the inside of the turning during the steering operation are continuously variable. It is possible to shift gears to improve steerability and turning performance.

[0004]

The present invention is directed to a steering clutch shaft transmission system A for transmitting power from an input shaft 1 to a steering clutch shaft 2.
And a steering clutch transmission system B that transmits to the pair of left and right steering clutches 3 that move in and out of the steering clutch shaft 2 with different transmission ratios. A differential device 4 for differentially operating the left and right steering clutches 3, a differential speed increasing clutch 6 for speeding up the rotation of a differential case 5 of the differential device 4, and a differential for speeding up the rotation of the differential case 5. In the transmission provided with the deceleration brake 7,
On the oil discharge side of the steering hydraulic circuit 10 having the actuator 8 of the steering clutch 3 and the steering control valve 9, a relief valve operated by a power steering lever 11 for operating the steering control valve 9. A power steering hydraulic circuit 13 having a power steering hydraulic circuit 12 and an actuator 15 of the differential speed increasing clutch 6 and an actuator of the differential speed reduction brake 7 which are switched by a mode switching valve 14 while receiving the hydraulic pressure of the power steering hydraulic circuit 13.
And a steering operation device such as a combine.

[0005]

With the above structure, in the combine operation, the left and right steering wheels are in the steering clutch shaft 2 when the vehicle body is steered straight ahead and is turned in a headland or the like. Put the clutch 3 into the power steering system-1.
The steering control valve 9 is switched by tilting left (right) 1 and the actuator 8 is actuated by this switching to disengage the left (right) steering clutch 3 from the steering clutch shaft 2.
As a result of this switching action, the mode switching valve 14 moves the differential travel mode.
When it is switched to the H side, the power steering hydraulic circuit 1
3, the operation of increasing the tilt angle of the power steering lever 11 causes the relief valve 12 to operate, whereby the differential speed increasing clutch 6
By continuously increasing the speed of the differential case 5, the left (right) steering clutch 3 whose rotation is stopped by the disengagement operation is continuously increased to enter the steering clutch shaft 2. With the right and left steering clutches 3 facing each other, differential steering and differential turning can be performed.

Further, when the mode switching valve 14 is switched to the spin traveling mode L side, the operation of the relief valve 12 by the tilting angle increasing operation of the power steering lever 11 in the power steering hydraulic circuit 13. Depending on the differential speed reduction blur
By continuously decelerating the diff case 5 by the key 7, the left (right) steering clutch 3 whose rotation is stopped by the disengagement action is continuously reverse-rotated to speed up the steering clutch shaft 2
Opposite right (left) steering clutch 3
The spin rotation can be performed by and.

As described above, in the power steering hydraulic circuit 13, the differential case 5 and the differential speed increasing clutch 6 are operated in the differential travel mode H by the action of the relief valve 12 by the operation of increasing the tilt angle of the power steering lever 11. In the spin traveling mode L, the differential case 5 is decelerated by the differential deceleration brake 7 so that the left and right steering clutches 3 act in a relative manner to increase the speed of the differential in the former case. In the latter case, it is possible to continuously increase and reverse speed, especially in differential driving, to improve the steerability that can prevent meandering regardless of the condition of the soil surface during the steering operation and to improve the soil surface during the turning operation. It is possible to improve the turning performance that enables the turning adapted to the degree of softness.

[0008]

Embodiments of the present invention will be described below with reference to the drawings. A traveling device 1 having a pair of left and right traveling crawlers 18 for traveling on a soil surface below a chassis 17 of the combine.
9 is provided, and a threshing device 21 that threshes the grain culms that are sandwiched by the feed chain 20 and that is fed and that sorts and collects the threshed grains is placed on the chassis 17. In addition, a standing culm culm is weeded on the front side of the threshing device 21, raised and cut, and the cut culm is transferred to the rear side and changed to a sideways posture to the feed chain 20. The reaping device 22 to be delivered is installed on the front end of the chassis 17 so as to be able to move up and down with respect to the soil surface. Further, an operating device 23 for controlling the operation of the combine and an operating seat 24 for this operation are provided on one side of the reaping device 22, and these traveling devices 1
9, a threshing device 21, a harvesting device 22, an operating device 23 and the like constitute a combine body 25.

A traveling mission case 26 is mounted on the front end of the chassis 17, and the transmission case 26 has a gear arrangement as shown in FIGS. 1 and 2. First, the input shaft 1 is provided with a two-way input clutch 27 of an interlocking type in which the one-side clutch that is always turned on by hydraulic pressure is disengaged, and at the same time the other-side clutch is turned on. An input gear 27a on one side and an HST gear 30 that is fixed to an HST input shaft 29 that is connected to a hydraulically driven HST device 28 are meshed and interlocked, and the output side of the HST device 28 is connected via an HST output clutch 31. The counter shaft 32 is connected to one end side thereof, and a high speed side gear 33 and a low speed side gear 34 for auxiliary shifting are axially fixed to the counter shaft 32, and the other side input gear 27b of the dual input clutch 27 is connected to the counter shaft 32. The counter shaft 32 and the low-speed gear 34 are meshed with each other and interlocked with each other.

A transmission gear 36 having a double structure for changing the vehicle speed between high and low stages is provided on one end of the transmission shaft 35 so as to be slidable in the left and right directions by a spline or the like. High speed side gear 33 or low speed side gear 3
4 and 4 are meshed and interlocked with each other, and a transmission gear 37 for transmitting power to the steering clutch shaft 2 is fixed to the speed change shaft 35.

The steering clutch shaft 2 has a center gear 38 which engages with the transmission gear 37 in the central portion thereof and which is provided with meshing claw portions 38a on the left and right sides, and the center gear 38 has a claw. The steering clutches 3 provided with the claw portions that are meshed with and connected to the portion 38a by sliding in the left-right direction are disposed at the left and right positions of the center gear 38, and the left-right steering clutch 3 includes the steering clutches. 3 is provided with a shifter groove 3a into which a shifter 39 for sliding in the left-right direction is inserted,
Left and right pressing springs 40 that constantly press the left and right steering clutches 3 so as to mesh and connect with the center gear 38, respectively.
Is provided and configured.

A differential speed increasing clutch 6 is provided on the other end side of the speed change shaft 35, and a speed increasing gear 6a driven by the engaging action of the differential speed increasing clutch 6 is provided. An intermediate gear 42 fixed to the shaft 41 is meshed and interlocked with each other, and the intermediate gear 42 and the differential case gear 5a mounted on the differential case 5 of the differential device 4 are interlocked with each other. From the differential gear 4a installed in the differential case 5,
The left and right diff drive gears 44 are axially fixed to the diff shafts 43 provided so as to project and extend in the left and right directions, respectively, and the left and right diff drive gears 44 are provided on the outer walls of the shifter grooves 3a of the left and right steering clutch 3 And a large clutch gear 3b are meshed and interlocked with each other, and a small clutch gear 3c provided on the inner wall of the shifter groove 3a and a traveling gear 46 fixed to the traveling shaft 45 are respectively meshed and interlocked. A differential reduction brake 7 is provided at one end of the brake shaft 41 to act between the brake shaft 41 and the transmission case 26.

The input shaft 1 to the steering clutch shaft 2
The steering clutch shaft transmission system A is constituted by the transmission path that is transmitted to the differential clutch, and the differential gear speed increasing clutch 6 acts on the differential clutch.
The steering clutch transmission system B is formed by a transmission path including a differential traveling mode H for increasing the speed of the gear 5 and a spin traveling mode L for decelerating the differential case 5 by the action of the differential deceleration brake 7. Make up.

As shown in FIG. 3, the hydraulic circuit for operating the power transmission path installed in the mission case 26 passes through a steering control valve 9 for turning the steering clutch 3 on and off from a hydraulic pump 47, Steering hydraulic circuit 1 connected to left and right actuators 8 for operating the left and right shifters 39, respectively.
0, and a mode switching valve 14 for switching between the differential traveling mode H and the spin traveling mode L is connected to the oil discharge side of the actuator 8, and this mode switching valve 14 is When it is switched to the differential running mode H side, it is connected to the actuator 15 of the differential speed increasing clutch 6 and also to the proportional pressure reducing valve 50 operated by the CPU 49 via the check valve 48. The proportional pressure reducing valve 50 is further connected to a relief valve 12 which is operated by tilting the power steering lever 11 to the left and right, and a circuit in which the relief valve 12 is returned to the tank 51 and the mode switching valve 14 are connected. Is a spin running mode
When it is switched to the drive L side, the check valve 52 is opened by the pilot pressure to connect it to the actuator 16 of the differential reduction brake 7, and thereafter, by the same operation as the differential traveling mode H side. A power steering hydraulic circuit 13 including a circuit that is returned to the tank 51 is configured. An unload valve 53 is connected between the steering control valve 9 and the tank 51, and between the relief valve 12 and the tank 51.

As a separate circuit, a floating bearing is supported on the input shaft 1 as shown in FIG. 4 via an input switching valve 54 for switching the input from the hydraulic pump 47 to the input by the HST device 28 and the direct mechanical connection input. In the dual input clutch 27, the left input gear 27a, which is always pressed and connected by the pressing spring 27c, is disconnected, and at the same time, the actuator 55 is connected to the right input gear 27b, and the HST output is always connected. An input switching hydraulic circuit 57 is configured by connecting in parallel with an actuator 56 that operates to disengage the clutch 31.

An HST lever 58 for switching the forward and backward movements of the body 25 and shifting the vehicle speed by the HST device 28.
And the power steering lever 11 for controlling the flow rate of the power steering hydraulic circuit 13 by the operation of the relief valve 12 depending on the size of the tilting operation angle to the left and right sides, respectively, to the appropriate positions of the operating device 23 so that they can be manually operated. It is arranged and provided. The HS
As shown in FIG. 3, the grip portion of the T lever 58 is provided with the above-mentioned mower.
The mode changeover switch 59 connected to the solenoid of the mode changeover valve 14, the input changeover switch 60 connected to the solenoid of the input changeover valve 54, and the both unload valves 53 for instantaneously increasing the vehicle speed when traveling straight ahead. A speed increasing switch 61 connected to a solenoid is appropriately arranged and provided, and the power steering lever 11 has the steering control valve 9 at the initial tilting operation angle.
Power steering switch 6 connected to a solenoid that activates
2 is provided at an appropriate position on the periphery and is configured.

CPU 49 connected to the proportional pressure reducing valve 50
Is connected to various sensor groups 63 for detecting the horizontal state, the inclined state, the subsidence state, the balance state of the machine body 25, the presence or absence of grain stalks, etc. It is configured to control the action. Next, the operation of the above configuration will be described.

Traveling device 19, threshing device 21, harvesting device 2
2. During the harvesting work performed by the operation of the operation device 23 or the like, the steering operation when the machine body 25 goes straight and the turning operation on the headland are frequently performed. This is performed by operating the HST lever 58 and its switches by an operator and tilting the power steering lever 11.

The transmission path driven by these operations is
First, the steering clutch shaft transmission system A causes the HST lever to move.
By switching the input selector valve 54 by the input selector switch 60 of 58, the dual input clutch 27 is driven while being connected to the input gear 27a side by the pressing spring 40, and the HS
Power is transmitted to the HST input shaft 29 via the T gear 30,
The HST input shaft 29 drives the HST device 28, and hydraulic drive is used to transmit from the output side of the HST device 28 to the counter shaft 32 via the HST output clutch 31 and the input changeover switch 60 of the HST lever 58.
By switching the input switching valve 54 by the above, the actuators 55 and 56 are operated to drive the dual input clutch 27 in a state of being connected to the input gear 27b side, and
With the ST output clutch 31 in the disengaged state, the input gear 2
Two-system input drive is performed depending on the case of mechanical direct drive in which power is transmitted from 7b to the counter shaft 32 via the low-speed gear 34.

In the two-system input drive, the hydraulic drive side is normally used, and the mechanical direct drive side is used only when necessary. By this input drive, the high speed side gear 33 of the counter shaft 32 or the low speed side drive gear is driven. The side gear 34 and the speed change gear 36 of the speed change shaft 35 are slidably engaged with each other to change the speed between high and low,
This changed power is transmitted from the transmission gear 37 to the steering clutch shaft 2
To the center gear 38, and when the steering clutch 3 is in the center gear 38, power is transmitted to the steering clutch 3.

While the steering clutch shaft transmission system A is transmitting, the steering clutch transmission system B transmits the power. This transmission is performed by the mode changeover switch 59 of the HST lever 58. When the mode switching valve 14 is switched to the differential travel mode H side, the differential speed increasing clutch 6 of the transmission shaft 35 is engaged by the operation of the actuator 15, and the differential speed increasing clutch 6 is engaged. The power is transmitted to the differential case gear 5a of the differential device 4 from the intermediate gear 42, and the differential case 5 is driven. Also, the mode switching valve 1
4 is switched to the spin running mode L side, the differential deceleration brake 7 of the brake shaft 41 causes the actuator 1 to move.
A braking state is established by the operation of 6, and the differential gear 5 is braked from the intermediate gear 42 through the differential gear 5a.

In such a state, if the power steering lever 11 is slightly tilted to the left (right) side, the power steering switch 62 is turned on, and the steering control valve 9 is switched to the left (right) side. The left (right) actuator 8 is operated to disengage the left (right) steering clutch 3.
Due to this disengagement action, in the case of the differential travel mode H, the right (left) steering clutch 3 on the opposite side drives the differential gear 4a via the right (left) differential drive gear 44. At this time, when the left (right) steering clutch 3 is stopped by a constant load, the differential case 5 freely rotates and the left (right) steering clutch 3 remains stopped. .

However, when the differential gear 5 is driven by the differential speed increasing clutch 6, the left (right) differential shaft 43 is driven, and the left (right) differential drive gear 44 is used to drive the left (right) differential gear 43. The steering clutch 3) is driven. This drive is differentially accelerated by the action of the relief valve 12 as the tilt angle of the power steering lever 11 increases. By this differential running in which the speed is continuously increased from 0, the differential steering control and the differential turning control when going straight can be smoothly performed without being influenced by the condition of the soil surface.

In the case of the spin traveling mode L, the same is true up to the point where the differential case 5 freely rotates and the left (right) steering clutch 3 is stopped, but thereafter. The rotation of the differential case 5 is braked by the differential deceleration brake 7, so that the left (right) differential shaft 43 is reversely driven, and the left (right) differential drive gear 44 is used to move the left differential shaft 43 to the left. The (right) steering clutch 3 is reversely driven. This drive is released as the tilting angle of the power steering lever 11 increases.
The reverse valve speed is increased by the action of the valve 12. By this spin running in which the reverse speed is continuously increased from 0, spin turning control can be smoothly performed even under adverse conditions on the soil surface.

The relationship between the rotational speeds of the left and right differential shafts 43 and the differential case 5 by the differential speed increasing clutch 6 and the differential speed reducing brake 7 is as shown in FIG. And Y, the differential case 5 is Z, and each rotation speed is N, the rotation of Z in the differential running mode H region is 1/2.
Each X axis when the speed is increased from N to N and when the rotation of Z in the spin traveling mode region is decelerated from 1 / 2N to 0,
The rotation speed of the Y axis is as shown in the table. Of course, the relationship of this rotation speed is not limited to this table and can be freely combined.

Further, in the case of a case where the speed of the steering clutch 3 on the differential side is increased more than the speed of the steering clutch 3 on the non-differential side at the time of turning by the differential traveling mode H. By detecting the point where the speed on the differential side becomes faster and switching the steering clutch 3 from the differential side to the non-operating side, the tilting operation direction and the turning direction of the power steering lever 11 are changed. However, it is possible to perform a safe turning control by preventing the reverse direction from occurring depending on the differential speed range on the differential side.

Further, when the vehicle is traveling straight by the differential running mode H,
The speed increasing switch 61 of the HST lever 58 simultaneously operates the left and right steering clutches 3 to the left and right, and as shown in FIG. 3, by switching the unload valve 53, the steering hydraulic circuit 10 and the power steering circuit are switched. The speed of the differential speed increasing clutch 6 is increased by the action of the hydraulic circuit 13, so that the HS speed is increased.
It is possible to instantly speed up without operating the T lever 58.

Further, as shown in FIG. 3, the grip portion of the HST lever 58 is provided with the mode changeover switch 59, the input changeover switch 60, and the speed increasing switch 61 so that the HST lever 58 can be operated. When traveling by
Instantaneous switching between differential travel mode H and spin travel mode L, switching between HST input and mechanical input, and instantaneous speed increase are possible, greatly improving maneuverability and operability. To do.

Further, as shown in FIG. 4, the structure of the dual input clutch 27 for switching between the input by the HST device 28 provided on the input shaft 1 and the mechanical direct connection input is such that when one is engaged, the other is always engaged. Due to the cutting sequence mechanism,
Even if there is a problem in the hydraulic system, the mechanical lock is never performed, the two clutches are coaxially provided and the structure is simple, and the input side of the HST device 28 that is frequently used is connected to the pressing spring 27c. Since it is always turned on by pressing, it saves energy and prevents troubles.

[Brief description of drawings]

FIG. 1 is a schematic front view showing a gear arrangement of a mission case.

FIG. 2 is a schematic side view showing a gear arrangement of a mission case.

FIG. 3 is a block diagram showing a hydraulic circuit and an electric circuit.

FIG. 4 is a schematic side sectional view showing the structure of a dual input clutch.

5A and 5B are a table and a schematic view showing a working rotation relationship of the differential device.

FIG. 6 is a side view showing the entire combine.

[Explanation of symbols]

 1 input shaft 2 steering clutch shaft 3 steering clutch 4 differential device 5 differential case 6 differential speed increasing clutch 7 differential speed reduction brake 8 actuator 9 steering control valve 10 steering hydraulic circuit 11 power steering lever 12 release F Valve 13 Power steering hydraulic circuit 14 Mode switching valve 15 Actuator 16 Actuator

Claims (1)

[Claims] 1. A steering clutch shaft transmission system A which transmits from an input shaft 1 to a steering clutch shaft 2, and a steering clutch which transmits to a pair of left and right steering clutches 3 which are turned on and off with respect to the steering clutch shaft 2. The transmission system B is interlocked with each other with different transmission ratios, and the steering clutch transmission system B has a differential device 4 for differentially operating the left and right steering clutches 3 and a differential case 5 of the differential device 4. In a transmission equipped with a differential speed increasing clutch 6 for speeding up the rotation of the differential gear and a differential speed reducing brake 7 for speeding up the rotation of the differential case 5, the actuator 8 and the steering of the steering clutch 3 are provided. A power steering hydraulic circuit 13 having a relief valve 12 operated by a power steering lever 11 for operating the steering control valve 9 on the oil discharge side of the steering hydraulic circuit 10 having the control valve 9, and this power steering hydraulic circuit. While receiving 13 hydraulic pressure, A steering operation device such as a combine provided with an actuator 15 of the differential speed increasing clutch 6 and an actuator 16 of the differential speed reduction brake 7 which are switched by a switching valve 14.