JP3265698B2 - Steering device such as combine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a steering device such as a combine and the like. It can be used for things that can be switched to the differential steering turning state.

[0002]

2. Description of the Related Art During a combine operation, it is necessary to repeat a steering turn many times in order to change the direction of a vehicle body at a headland or the like at a field end.
On extremely soft soil surfaces, the traveling crawler kneads the mud and slips easily due to the repetition of these steering turns. In such a state, the traveling crawler on the inner side of the turning is brought into a braking state at the same time as the disengagement of the steering clutch gear and is towed in order to perform an efficient steering turning with a minimum turning radius. Since the steering turning is performed together with the traveling crawler on the outside of the turning, the turning speed of the braking side is lower than that of the driving side and the speed of the vehicle body is reduced, so that the buoyancy of the traveling crawler due to the towing driving force is reduced, The traveling crawlers rub the soil surface, causing slippage and sinking. Furthermore, in the worst case, it is difficult to drive.

Accordingly, the present invention provides a double-speed differential steering system which utilizes the buoyancy of a traveling crawler effectively by a double-speed driving force by the action of a double-speed clutch and a differential device during a steering turn on an extremely soft soil surface. By making a turn, it is intended to prevent the settlement of the traveling crawler.

[0004]

According to the present invention, a steering clutch shaft transmission system A for transmitting power from an input shaft 1 to a steering clutch shaft 2 is provided.
And a steering clutch gear transmission system B for transmitting to the pair of left and right steering clutch gears 3L and 3R to be turned on and off with respect to the steering clutch shaft 2 at different transmission ratios. The gear transmission system B includes a double-speed clutch 4 for turning on and off the transmission, and the left and right steering clutch gears 3L and 3R.
And a differential brake 7 for braking the rotation of the differential case 6 of the differential device 5. The steering clutch gears 3L and 3R, the double-speed clutch 4, the differential brake 7 and the like are provided. A steering device such as a combine is characterized in that a steering turn is performed by the above operation.

[0005]

According to the above arrangement, the steering clutch shaft transmission system A is used to perform a steering turn for changing the direction of the vehicle body on an extremely soft soil surface during a combine operation. In addition to the steering clutch gear 3L (3R) that is engaged with the transmitted steering clutch shaft 2 and the disengagement action from the steering clutch shaft 2, the differential device 5 is operated by a differential brake.
The steering clutch gear 3R (3) transmitted by the steering clutch gear transmission system B that is braked and decelerated by the operation of the key 7
L), for example, the steering clutch gear 3R (3L)
A pivot turn (hereinafter referred to as a pivot turn) that makes a one-side turn with a minimum radius by a traveling crawler inside the turn
And the pivot turn further deflates.
The differential device 5 in which the braking force of the key 7 is increased performs a deceleration differential steering turn by a spin turn (hereinafter referred to as a spin turn) in which the left and right traveling crawlers are rotated in opposite directions to perform a uniaxial turn. Can be.

[0006] The steering clutch gear 3R (3L) acting on the steering clutch shaft 2 for this decelerated differential steering turn.
By simultaneously performing the disengaging operation from the steering clutch shaft 2 and the engagement operation of the double-speed clutch 4 and the braking release operation of the differential device 5, the steering transmitted by the steering clutch gear transmission system B that performs double-speed differential. With the direction clutch gear 3L (3R), for example, on the turning inner traveling wheel that causes the steering clutch gear 3R (3L) to enter, the turning outer traveling clock that causes the steering clutch gear 3L (3R) to disengage. A double-speed differential steering rotation can be performed by a double-speed turn (hereinafter, referred to as a double-speed turn) for making the motor double-speed differential. At this time, the double-speed differential steering rotation and the deceleration differential steering rotation can be quickly switched by, for example, an operation of a switching tool.

[0007] As described above, when the turning operation for changing the direction of the vehicle body is performed on the extremely soft soil surface during the combine operation, first, when the softness of the soil surface is light, the pivot point is used.
Although the running crawler does not sink much, the running crawler may encounter buoyancy due to a decrease in turning speed if it encounters moderately soft soil during the pivot turn. In this case, the sinking of the traveling crawler can be achieved by increasing the braking force of the differential device 5 to perform the spin turn, thereby reducing the sinking of the traveling crawler.

[0008] However, when a soil surface of a severe softness is encountered at the time of the spin turn, the traction of the traveling crawler is still insufficient with the spin turn, so that the sinker sinks. Switching by automatic or manual operation from decelerated differential steering turning to perform a pivot turn or spin turn to double speed differential steering turning to perform a double speed turn, that is, the engagement action of the double speed clutch 4 and the differential device By releasing the braking state of No. 5, the buoyancy is increased by the double-speed driving of the traveling crawler on the outer side of the turn, and the effect of reducing the traction driving force by the double speed is used to break down the soil surface due to the lug of the traveling crawler. As a result, the settlement due to slip can be minimized, so that the turning radius is slightly increased, but smooth steering turning at high speed can be performed.

[0009]

DESCRIPTION OF THE PREFERRED EMBODIMENTS In the drawings, the present invention will be described for a combine for harvesting cereals. A traveling device 10 having a pair of left and right traveling crawlers 9 that travels on the soil surface is disposed below the undercarriage 8 of the combine.
A threshing device 12 for threshing the grain culm supplied and fed to the feed chain 11 and selectively collecting the threshed grain is mounted. In addition, weeding, raising, and cutting of the raised culm on the front side of the threshing device 12, and changing the posture of the cut culm to the feed chain 11 while transporting the cut culm to the rear side. The harvesting device 13 to be delivered is mounted on the front end of the chassis 8 so as to be able to move up and down with respect to the soil surface. An operation device 14 for controlling the operation of the combine is provided on one side of the threshing device 12, and an operation seat 15 for this operation.
And a vehicle body 16 of the combine is constituted by these devices 10, 12, 13 and 14.

A traveling case 17 is mounted on the front end side of the chassis 8 and an output shaft 19 of a hydraulically driven continuously variable transmission 18 is interlocked to the input shaft 1 of the mission case 17. On the input shaft 1 of the transmission case 17, a gear for shifting the vehicle speed in two stages is integrally formed, and a transmission gear 20 for sliding transmission is slidably supported by a spline or the like, and the transmission gear 20 slides. As a result, the high-speed gear 21 and the low-speed gear 21b as counter gears that mesh with each other are stopped on the counter shaft 22, and power is transmitted to the steering clutch shaft 2 at one end of the counter shaft 22. The transmission gear 23 is configured to be axially stopped.

The steering clutch shaft 2 is provided with an interlocking gear 24 for engaging and interlocking with the transmission gear 23 at one end thereof, and left and right steering clutch gears 3L and 3R at the center in the left and right direction. A center clutch 25 having left and right side connection receiving portions 25a for meshing connection is axially fixed, and the left and right steering clutch gears 3L and 3R are connected to the center clutch 25 by sliding in the left and right directions. 25a is provided with a connecting portion which meshes with each other, and a gear portion which is slidably meshed with the left and right reduction gears 26 for transmitting the traveling crawler 9 is provided on the outer peripheral portion thereof, and is opposite to the connecting portion. The left and right sliding springs 27 for sliding the left and right steering clutch gears 3L and 3R in the left and right directions are respectively elastically stretched to form a steering clutch shaft transmission system A.

The large-diameter gear portion is connected to the steering clutch gears 3L, 3L.
The right and left reduction gears 26 of a two-stage configuration, which mesh with and interlock with R, respectively, are idled on left and right reduction shafts 28, and the small-diameter gear portion of the reduction gear 26 drives the steering crawler 9. The left and right drive wheel gears 29 are fixed to one end of the left and right drive wheel shafts 30, respectively, and the other end is connected to the transmission case 17 at the other end.
The left and right driving wheels 31 of the traveling crawler 9 are respectively mounted on the other end portions of the traveling crawler 9 projecting outward.

A double-speed gear 32 driven by the engaging action of the double-speed clutch 4 that is stopped on the counter shaft 22 is idled on the other end of the counter shaft 22. The idle gear 34 that is rotatably supported is meshed with the idle gear 34. The idle gear 34 meshes with a gear provided on the outer periphery of the disk 6a provided on the differential case 6 of the differential device 5, and
A differential shaft 36 protruding in the left-right direction from a differential gear 35 provided in the differential case 6 is provided, and left and right differential drive gears 37 are fixed to the differential shaft 36, respectively. The left and right differential drive gears 37 and the left and right steering clutch gears 3L and 3R are engaged with each other, and when the differential case 6 is braked at an appropriate position on the disk 6a, the differential gear is decelerated and differentially driven. A differential brake 7 that is released during a differential operation is provided, and a deceleration differential mode L and a double speed differential mode H constitute a steering clutch gear transmission system B.

The vehicle body 1 is controlled by the continuously variable transmission 18.
6, a continuously variable lever 38 for switching between the forward and reverse directions and shifting the vehicle speed, and the contact is turned to the right by tilting left and right.
And a power telescopic lever 39 for causing the vehicle body 16 to steer and turn to the left and right.
4, a mode changeover switch 40 for switching between a deceleration differential mode L and a double speed differential mode H at a grip portion of the continuously variable lever 38, and a power telescopic switch. -3
9 is provided with a power steering relief valve 41 whose closing action becomes stronger as the operation angle of the lever to the left and right increases.

As shown in FIG. 4, various sensors provided at an appropriate position of the vehicle body 16 are provided at an input side of a control device 42 for performing arithmetic control mainly by a CPU provided at an arbitrary position of the vehicle body 16 as shown in FIG. 16, a horizontal sensor 43 for detecting a horizontal state, a tilt sensor 44 for detecting a tilt state, a sinking sensor 45 for detecting a sinking state with respect to a soil surface, and a balance sensor 4 for detecting a front-back and left-right balance state.
6, a grain stalk sensor 47 for detecting the presence or absence of a transported grain stalk
And a vehicle speed sensor 48 for detecting the state of the vehicle speed are connected. To the output side, the contact is turned on by the tilting operation of the power telescopic lever 39 to the left or right, or the right and left steering expansion and contraction is performed by turning on and off the left and right steering clutch gears 3L and 3R by the action of the copying straight movement sensor 49. A steering electromagnetic valve 51 for operating the cylinder 50, the mode changeover switch 40, and the ON / OFF operation of the switch 40 brakes the double-speed telescopic cylinder 52 for turning on and off the double-speed clutch 4 and the differential brake 7. A mode switching solenoid valve 54 for switching with the brake telescopic cylinder 53
And a proportional pressure reducing valve 55 for adjusting the braking force of the differential brake 7 and the like.

As shown in FIG. 4, the hydraulic drive circuit is connected from a hydraulic pump 56 to an inlet port of the steering solenoid valve 51, and from the outlet port, the left and right steering telescopic cylinders 50 are connected.
To the entrance of The outlets of the left and right steering telescopic cylinders 50 are connected to each other, and the connection circuit is connected to the inlet port of the mode switching solenoid valve 54, and the double speed telescopic cylinder is connected from the outlet port. 52 and the brake telescopic cylinder 53 respectively. A connection circuit between the mode switching electromagnetic valve 54 and the brake telescopic cylinder 53 is connected to the proportional pressure reducing valve 55, and the proportional pressure reducing valve 55 is further connected to the power steering relief valve 41, and the power steering relief is connected to the power steering relief valve 41. It is constituted by refluxing from the valve 41 to the tank 57.

Next, the operation of the above configuration will be described. Traveling device 10, threshing device 12, reaper 1
3. Harvesting operation is performed by the operation of the operation device 14 and the like.
It is necessary to repeat the traveling turning for changing the direction of the vehicle body 16 many times, but on extremely soft soil surface, by repeating these steering turnings, the mud is kneaded and the traveling crawler 9 slips. Easily occur. Therefore, at the time of the steering turn, the mode is switched to a deceleration differential mode L for decelerating and differentially driving the traveling roller 9 on the inside of the turn, or a double speed differential mode for differentially driving the traveling roller 9 on the outside of the turn. By switching to -H, the steering turn corresponding to the state of the soil surface at that time can be performed.

As shown in FIG. 2, a series of these power transmission paths are transmitted from an output shaft 19 of a continuously variable transmission 18 which switches between forward and reverse and continuously changes the vehicle speed by operating a continuously variable transmission lever 38. Power is transmitted to the input shaft 1 of the transmission case 17, and power is transmitted from the input shaft 1 to the steering clutch shaft 2 by the steering clutch shaft transmission system A. The steering clutch shaft transmission system A first slides the transmission gear 20 of the input shaft 1 in the left-right direction, and the high-speed gear 21 of the counter shaft 22.
a and the low-speed gear 21b are engaged with each other to perform a shift, and the shifted power is transmitted from the transmission gear 23 to the interlocking gear 2b.
4, the traveling clutch shaft 2 and the center clutch 2
Transmit to 5.

The left and right steering clutch gears 3L, 3L are connected to respective connection receiving portions 25a on the left and right sides of the center clutch 25.
R is turned on and off by sliding connection in the left-right direction by the action of the steering telescopic cylinder 50. By this connection, power is transmitted from the left and right steering clutch gears 3L and 3R to the left and right drive wheel gears 29, respectively, and from the drive wheel gears 29 via the left and right drive wheel shafts 30 by the left and right drive wheels 31. Drive 9 is driven.

When the work is being performed by these power transmissions, in the deceleration differential mode L, the power steering 39
Is tilted to the left, the contact is turned on, and the steering electromagnetic valve 51 is switched to the left. The left steering telescopic cylinder 50 is extended via the steering electromagnetic valve 51, and the left steering clutch is extended. The gear 3L is turned off. Along with this cutting action, the pressure oil extruded from the left steering telescopic cylinder 50 is dissipated by the motor.
When the mode changeover switch 40 is turned off, the brake is switched via the mode changeover solenoid valve 54 which is switched to the deceleration differential mode L side.
The expansion cylinder 53 is extended, and the disk 6a of the differential case 6 is braked by the differential brake 7.

With the differential case 6 being braked, the steering clutch gear transmission system B is actuated. First, from the right steering clutch gear 3R on the entering operation side to the right differential drive gear 37.
And the differential gear 35 is mutually driven by the right differential drive gear 37 in the braking state of the differential case 6 to transmit power to the left differential drive gear 37. By transmitting the power, the left steering clutch gear 3L is reduced and transmitted to the right steering clutch gear 3R by the left differential drive gear 37. The magnitude of the deceleration differential is determined by the strength of the differential brake 7 that brakes the differential case 6 by the tilt operation angle of the power telescopic lever 39.

When the tilt angle of the power steering lever 39 is medium, the power steering relief valve 41 is closed but the proportional pressure reducing valve 55 is open. By the braking of the gear 6, the left differential drive gear 37 is rotated at a reduced speed. Therefore, the left traveling crawler 9 is pulled with respect to the traction driving of the right traveling crawler 9.
This is a pivot turn that makes a left turn while decelerating the differential of the ra 9. The right turn is performed according to the left turn.

However, in this state, the power telescoping 39
When the inclination operation angle of the motor is further increased, the power steering relief valve 41 and the proportional pressure reducing valve 55 are both closed, so that the differential case 6 by the brake telescopic cylinder 53 is used.
The braking force of the left differential driving gear 37 becomes locked at the maximum, and the left differential drive gear 37 shifts from the reduced rotation region to the reverse rotation region. Accordingly, a spin turn is performed in which a left turn is made on the spot while the left traveling crawler 9 is towed in the opposite direction to the towing drive of the right traveling crawler 9. The right turn is performed according to the left turn.

When the tilt angle of the power steering lever 39 is small, the power steering relief valve 41 remains open, and almost no braking force acts on the differential case 6. Thus, no driving force is generated in the left differential drive gear 37. Therefore, it can be used at the time of straight-ahead steering by normal manual operation, at the time of steering control by the copying straight-ahead sensor 49, and the like. In the double speed differential mode H, the mode changeover switch 40 is
Switching from the FF state to the ON state, the power telescopic -3
When the switch 9 is tilted to the left, the contact is turned on to switch the steering electromagnetic valve 51. At the time of the switch, the steering clutch gear 3L on the left is normally operated to the disengagement side. When the mode changeover switch 40 is in the ON state, the right-hand steering telescopic cylinder is switched via the steering solenoid valve 51 to the right-hand switching cylinder. 50 is extended to disengage the right steering clutch gear 3R.

Along with this cutting action, the pressure oil extruded from the right steering telescopic cylinder 50 is switched to the double speed differential mode H by turning on the mode changeover switch 40. Double-speed telescopic cylinder 5 via switching solenoid valve 54
2, the double-speed clutch 4 is engaged to actuate the double-speed gear 32 together with the counter shaft 22, and the driving of the double-speed gear 32 causes the differential case 6 to mesh with the idle gear 34 and interlock. Let it. At this time, since the pressure oil of the differential brake 7 is cut off to the brake telescopic cylinder 53, the braking force on the differential case 6 is released, and the left steering clutch gear 3L on the input operation side is released. Is transmitted to the left differential drive gear 37, and the left differential drive gear 37 causes the differential gears 35 to be mutually driven in the rotational drive state of the differential case 6 to the right differential drive gear 37. Transmit power.

By the transmission of the power, the right steering clutch gear 3R is transmitted by the right differential drive gear 37 with a double speed differential with respect to the left steering clutch gear 3L. Therefore, with respect to the traction drive of the left traveling crawler 9 in which the left steering clutch gear 3L is on the working side,
The right steering clutch gear 3R is a double speed turn that performs a left turn at a speed higher than that in the straight traveling state while making the right traveling crawler 9 on the side of the disengagement differential at a double speed. The steering rotation speed at the time of the double speed turn can be controlled by the tilt operation angle of the power steering lever 39. The right turn is performed according to the left turn.

Also, during the combine operation, field conditions and vehicle body conditions (sinking, inclination, balance, etc.) change every moment, so that the deceleration differential mode L and the double speed differential mode H are changed in accordance with these changes. However, in the case of manual operation, it may be difficult to make a determination or may be forgotten, which may hinder the work. Therefore, the sinking sensor 45
And the sinking state of the vehicle body 16 due to the slippage of the traveling crawler 9 is detected by the balance sensor 46.
The mode may be automatically switched to an optimal mode for the condition at that time.

When the vehicle speed is high, it is dangerous to perform a double-speed turn.
The traction means for disabling the switching to the double speed clutch 4 may be provided by the procedure shown in FIG. Further, in order to prevent the loss such as the uncut portion caused by pushing the uncut culm due to the double speed clutch 4 being engaged and the vehicle body 16 turning suddenly due to an erroneous operation during the cutting operation and pushing down the uncut culm, the procedure shown in FIG. Alternatively, a check means for disabling switching to the double speed clutch 4 may be provided.

The mode changeover switch 40 opens and closes the proportional pressure reducing valve 55 in a state where the mode changeover electromagnetic valve 54 is switched to oil supply to the brake telescopic cylinder 53 side. In the state where the mode switching electromagnetic valve 54 is further switched to the double speed telescopic cylinder 52 side,
The operation may be switched between three stages, that is, the operation of closing the proportional pressure reducing valve 55.

The mode switching solenoid valve 54 may be replaced with a proportional pressure reducing valve, and the double speed clutch 4 may be gradually engaged. Further, the proportional pressure reducing valve 55 is automatically closed so that the detection of the sinking state of the vehicle body 16 by the sinking sensor 45 switches from the pivot turn to the spin turn when the predetermined level is reached. You may.

[Brief description of the drawings]

FIG. 1 is a side view showing the entire combine.

FIG. 2 is a schematic front view showing a gear arrangement of a transmission case.

FIG. 3 is a schematic side view showing a gear arrangement of a transmission case.

FIG. 4 is a block diagram showing an electric circuit and a hydraulic circuit.

FIG. 5 is a flowchart showing a procedure of a check means.

FIG. 6 is a flowchart showing a procedure of a check means.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Input shaft 2 Steering clutch shaft 3L Steering clutch gear 3R Steering clutch gear 4 Double speed clutch 5 Differential device 6 Differential case 7 Differential brake

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int.Cl. ⁷ , DB name) B62D 11/08

Claims (1)

(57) [Claims] 1. A steering clutch shaft transmission system A for transmitting power from an input shaft 1 to a steering clutch shaft 2, and a pair of left and right steering clutch gears 3 which are turned on and off with respect to the steering clutch shaft 2.
L, 3R and the steering clutch gear transmission system B are linked to each other with a different transmission ratio.
Includes a double-speed clutch 4 for turning on and off the transmission, a differential device 5 for differentially driving the left and right steering clutch gears 3L, 3R,
A differential brake 7 for braking the rotation of a differential case 6 of the differential device 5 is provided, and these steering clutch gears 3L, 3L are provided.
A steering device such as a combine, wherein the steering is turned by operating the R, the double speed clutch 4, the differential brake 7, and the like.