JP4449957B2 - Combine - Google Patents

Description

  The present invention relates to a combine.

In a combine that has a traveling mission case equipped with a gear interlocking mechanism, this mission case conventionally travels on a steering clutch shaft that is provided with a steering clutch that is turned on and off during steering turning of the vehicle body. Many have been disclosed in which a brake is connected and a turning clutch for mild and spin turning is provided on a turning shaft provided on the lower side of the clutch shaft. (For example, refer to Patent Document 1.)
JP-A-7-274618

  However, since the traveling brake for executing the brake turning and the turning clutch for executing the mild turning and the spin turning are arranged on separate axes, the configuration of the gear interlocking mechanism becomes relatively complicated, In order to continuously execute brake turning, mild turning, and spin turning with different turning methods, troublesome control is required.

  Thus, the configuration of the gear interlocking mechanism in such a traveling mission case and the troublesome control during the turning action are to be improved.

According to the present invention, a traveling device (13) having a pair of left and right traveling crawlers (12) is provided on the lower side of the chassis (11), and a threshing device (17) including a Glen tank (15) is provided on the chassis (11). A reaping device (23) is provided in front of the threshing device (17) so as to be movable up and down, and an operation seat (26) and an operation device (25) are provided on the front side of the Glen tank (15) to mount the vehicle body (2). And a traveling transmission case (4) is provided on the front side of the chassis (11), and a hydraulic continuously variable transmission (29) is attached to the traveling transmission case (4) so as to be interlocked. A variable motor (29b) configured to transmit power from the engine (27) to the input pulley (30) of the variable pump (29a) of the variable continuously variable transmission (29) and driven by the variable pump (29a) Through) A configuration you transmitted to the input shaft of the row for the transmission case (4) (34), the input shaft two the spline (34) slidable in the axial direction series of auxiliary transmission gear (35) is provided, A turning drive gear (57) is provided on the turning shaft (5) of the traveling mission case (4), and a differential case on the outer periphery of the turning drive gear (57) and the differential case (1b) of the differential gear device (1). The gear (1c) is meshed and interlocked, and the axle gear is driven via the output gear (59) of the differential gear device (1). The operating device (25) is provided with the hydraulic continuously variable transmission. A main speed change lever (60) for changing the speed of the variable pump (29a) of the device (29) to perform forward / backward switching and speed change of the vehicle body (2), and a sub speed change gear in the traveling mission case (4) Sub-shift lever (6) A), the body (2) steering operating tool for turning the (9) and the provided, slow turning clutch locks axis turning axis on the basis of the turning operation of該操direction operation member (9) (5) (6) is actuated, and is transmitted to the differential case gear (1c) by driving the turning drive gear (57), and the output gear (59) via the differential gear (1a) in the differential gear device (1). output rotation is changed in, for the one lateral side of the axle formic ya and configuration that can pivot axle formic ya is decelerated in the right and left the other side, based on the spin turning operation of the steering operating member (9) Then, the drive of the turning drive gear (57) is locked by operating the spin turning clutch (8) fixed to the end protruding from the outer wall of the traveling mission case (4) in the turning shaft (5), By the differential case gear (1c) meshing with the turning drive gear (57) Ri locks the rotation of the differential case (1b), by the output rotation one of left and right sides of the output gear to (59) in the opposite direction through the differential gear (1a), the left and right the other side against the one lateral side of the axle formic Ya by reversely rotating the axle formic ya of a configuration that can spin pivoting action of the steering operating member (9) slow turning clutch (6) and spin turning clutch at handle (9b) (8) the wearing the ON / OFF switch for turning the selector switch (9a), by changing the swash plate angle of the variable motor (29 b) and configuration that can shift operation of the hydraulic stepless transmission (29), the single I by one of the sub-transmission lever (62), a shift operation of the auxiliary transmission gear of the driving transmission within the case (4) (35), the variable motor (29 b) of said hydraulic stepless transmission (29) configuration Prefecture that perform a shift operation of changing the swash plate angle A variable motor with a small operation load is operated by a left-right direction operation with a short operation stroke by the sub-shift lever (62), and a sub-shift operation with a heavy operation load is performed by a front-back operation with a long operation stroke by the sub-shift lever (62). The combine structure is characterized in that the swash plate angle changing operation (29b) is performed .

With this configuration, a slow turn and a spin turn are executed to the left (or right) side in conjunction with the hydraulic continuously variable transmission ( 29 ) .
The traveling shift is also performed by a sub-shift operation and a shift operation of the variable motor ( 29b ) of the hydraulic continuously variable transmission ( 29 ) .

According to the present invention, the operation of the slow turning clutch (6) and the spin turning clutch (8) is turned on / off by the operation of the turning switch (9a) mounted on the handle (9b) of the steering operation tool (9). It can be switched off, and in conjunction with the hydraulic continuously variable transmission ( 29 ) , it is possible to execute a slow turn and a spin turn to the left (or right) side through the differential gear device (1) , respectively. Thus, the troublesome control during the turning operation can be improved, and each turning operation can be smoothly shifted by the differential gear device (1) . Also, I by the single auxiliary shift lever (62), a variable mode of the auxiliary speed change operation that by the first gear (35), hydraulic continuously variable transmission interlocking the traveling transmission (29) - motor ( 29b ) can be operated continuously, and the operability of the shifting operation can be improved.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 10 shows the overall structure of the combine. A traveling device 13 having a pair of left and right traveling crawlers 12 traveling on the soil surface is disposed on the lower side of the chassis 11, and the chassis 11 includes a feed chain. 14 threshing the cereal grains that are nipped and transported between the two, the grain tank 15 that selectively collects and recovers the threshed grain, and the waste that discharges the grain stored in the tank 15 to the outside of the machine. A threshing device 17 provided with a cereal auger 16 is placed, and a waste disposal device 18 is mounted on the rear end of the threshing device 17.

  In front of the threshing device 17, a weeding body 19 for weeding an uncut grain culm from the front end side, a pulling part 20 for causing the weed cereal culm, and a cutting blade part 21 for harvesting the induced culm, A reaping device 23 having a supply adjustment transporting section 22 and the like that scrapes the harvested culms and takes over the cereals that are transported by adjusting the handling depth in the course of transportation and transfers them to the feed chain 14. The cutting and lifting cylinder 24 by driving is suspended from the front end of the chassis 11 so as to be movable up and down with respect to the soil surface.

  An operating device 25 for controlling the operation of the combine is provided on one side of the mowing device 23 and an operating seat 26 for this operation. The Glen tank 15 is disposed on the rear side of the operating seat 26, and on the lower side. Includes an engine 27 and a cabin 28 that covers the operation device 25 and the operation seat 26. The traveling vehicle 13, the threshing device 17, the reaping device 23, the operating device 25, the engine 27, the cabin 28, and the like constitute the combine vehicle body 2.

  The traveling device 13 has a traveling mission case 4 mounted on the front side of the chassis 11, and a hydraulic continuously variable transmission 29 can be interlocked with the upper side of the mission case 4 as shown in FIG. And a transmission belt or the like is stretched to the input pulley 30 fixed to the variable pump 29a of the continuously variable transmission 29 so that power can be transmitted from the engine 27, and is driven integrally by the variable pump 29a. The variable gear 29b is configured such that the output gear 31 is fixed on the shaft.

The gear interlocking mechanism of the transmission case 4 fixes an input gear 33 meshingly interlocked from the output gear 31 via the idle gear 32 to an input shaft 34 as a first shaft, For this purpose, a double low and medium speed drive gear ( first gear) 35 slidable by a spline or the like and a shaft fixed high speed drive gear 36 are provided side by side.

  Two low / medium speed driven gears 37 that mesh with and interlock with the low / medium speed drive gear 35 are provided to rotate freely on a sub-transmission shaft 38 as a second shaft. A low and medium speed clutch 39 connected to the driven gear 37 to turn on and off the shaft rotation of the gear 37 and a high speed driven gear 40 meshingly interlocked with the high speed drive gear 36 are integrally joined to the shaft rotation of the gear 40. Each of the high speed clutches 41 for turning on and off is fixed to the shaft, and the auxiliary transmission drive gear 42 is fixed to be adjacent to the high speed clutch 41.

  A sub-transmission driven gear 43 that meshes with the sub-transmission driving gear 42 is fixed to a counter shaft 44 serving as a third shaft, and the counter transmission gear 45 is sandwiched between the counter-shaft driven gear 43 and the counter shaft 44. And the brake drive gear 46 and the mild drive gear 47 are respectively configured to be axially fixed.

  The counter transmission gear 45 of the counter shaft 44 and the steering center gear (second gear) 49 fixed at the center position of the steering clutch shaft 48 as the fourth shaft are engaged with each other, and both sides of the steering center gear 49 are engaged. Are provided with clutch pawls 49a, and two left and right steering clutches 3 each comprising a large-diameter gear 3a and a small-diameter gear 3b are slidably pivoted on both sides of the center gear 49. .

  Each of the left and right steering clutches 3 is provided with clutch pawls that engage and connect with the clutch pawls 49a of the steering center gear 49 on the inner surface of the large diameter gear 3a. A shifter groove 3c for loosely fitting the left and right shifters 51 for sliding the steering clutch 3 by the push cylinder 50 is provided between the outer small-diameter gear 3b.

  The axle gear 52 meshed with the small-diameter gear 3b of the steering clutch 3 is fixed to one end portion of the left and right axles 53 as the fifth shaft, and the other end portion of the left and right axles 53 protruding to the outside. In addition, the left and right traveling sprockets 54 that drive the traveling crawler 12 are axially fixed.

  A brake driven gear 55 and a mild driven gear 56 that mesh with and interlock with the brake drive gear 46 and the mild drive gear 47 of the counter shaft 44 are provided, and are integrally joined with the brake driven gear 55 to input shaft rotation of the gear 55. The brake turning clutch 7 to be turned off and the mild turning clutch 6 which is integrally joined with the mild driven gear 56 to turn on and off the shaft rotation of the gear 56 are fixed to the turning clutch shaft 5 as the fourth A axis. To make it up.

  The shaft end of the turning clutch shaft 5 is protruded from the outer wall 4a of the transmission case 4, and the spin turning clutch 8 is fixed to the protruding portion, and the turning clutch shaft 5 is turned to an appropriate position. The drive gear 57 is fixed on the shaft.

A orbiting drive gear 57, and four Defukesugi Ya 1 c fixed to the differential case 1b outer periphery of the differential gear unit 1 for combined interior a differential formic Ya 1 a with are engaged interlocked, the differential case 1b from the differential gear 1a The left and right differential output gears (output gears) 59 are fixed to the turning control shaft 58 as the 4B axis, which protrudes to the left and right sides, and the differential output gear 59 and the steering clutch 3 The large-diameter gear 3a is configured to mesh with each other.

  As shown in FIG. 2, on one side of the operation panel 25 a of the operation device 25, a main transmission lever 60 that performs forward / reverse switching and main shift of the vehicle body 2 by the hydraulic continuously variable transmission 29 and the low and medium speeds. A sub-transmission lever 62 that shifts the drive gear 35 to low / medium speed by operating a shifter 61 by a link mechanism 62a, and a power steering lever 9 that serves as a steering operation tool 9 that performs left-right steering and turning of the vehicle body 2. Arrange and configure.

  As shown in FIG. 3, the handle 9b of the power steering lever 9 is fitted with a turning switch 9a for switching on and off the actions of the mild turning clutch 6 and the spin turning clutch 8 respectively, and the lower end of the lever 9 Power steering reliefs that are actuated by left and right power steering switches 64 that are turned on when the lever 9 is swung left and right by the metal portion 63a of the rocking plate 63 joined to the rocking plate 63 and an action plate 65 that is pressed downward by the rocking plate 63. Each of the valves 66 is disposed and configured.

The direction correction sensitivity (direction correction amount) when performing the automatic direction control action when the vehicle body 2 goes straight is changed from small to large by switching between the mild turning clutch 6, the brake turning clutch 7, and the spin turning clutch 8. The sensitivity setting dial 10 is arranged on one side of the operation panel 25a of the operation device 25 and configured. (See Figure 2)
In addition, the direction sensor 67 for automatic direction control is each arrange | positioned and comprised in the weed ridge 19a which supports the weeding body 19 of the left end side of the said cutting device 23, and a right end side.

  As shown in FIG. 4, the pressurized oil pressurized by the hydraulic pump 69 from the oil tank 68 is diverted by the diverter valve 70, and one of the diverted sides is passed through the sub-shift switching electromagnetic valve 71 for switching between four ports and two positions. A low / medium speed clutch 39 and a high speed clutch 41 are connected to be switchable.

  The other diverting side is pressurized by operating the electromagnetic proportional valve 73 and the power steering lever 9 through the left and right push cylinders 50 through the four-port / three-position switching electromagnetic valve 72 to the working discharge side oil passage p. The power steering relief valve 66 that performs control is connected to the relief valve 66 so that oil can be returned.

  Further, the operation discharge side oil passage p is connected to a mild turning clutch 6, a brake turning clutch 7, and a spin turning clutch 8 through a 6-port / 3-position switching turning solenoid valve 74 so as to be switchable. At the same time, the direction switching solenoid valve 72 and the power steering relief valve 66 and the direction switching solenoid valve 72 and the direction sensor 67 are electrically connected to each other.

  The power from the engine 27 is linked to the variable pump 29a of the hydraulic continuously variable transmission 29 via the input pulley 30, and the variable motor 29b is driven by the variable pump 29a whose speed is adjusted by operating the main transmission lever 60. Transmission is performed from the output gear 31 of the variable motor 29b to the input gear 33 fixed to the input shaft 34 via the idle gear 32.

  Two low and medium speed drive gears 35 that rotate and slide on the input shaft 34 are operated by operating the shifter 61 by the sub-shift lever 62 and are swung on the sub-shift shaft 38. By the separate meshing interlocking with the driven gear 37, the connected low / medium speed clutch 39 is turned on according to the OFF state of the sub shift switching electromagnetic valve 71 to shift to low speed and medium speed, respectively.

  The high-speed drive gear 36 fixed to the input shaft 34 and the high-speed driven gear 40 integrally joined to the auxiliary transmission shaft 38 and the high-speed driven gear 40 are interlocked with each other to engage the clutch 41 with the auxiliary transmission switching electromagnetic valve. When the switch 71 is in the ON state, it is shifted to a high speed by entering, and a shift as a sub-shift is performed by these low speed, medium speed, and high speed.

  The power that has been subjected to the sub-shift is transferred from the sub-transmission drive gear 42 that is fixed to the sub-transmission shaft 38 to the sub-transmission driven gear 43 that is fixed to the counter shaft 44, and from the sub-transmission driven gear 43 to the steering clutch. It is transmitted to the steering center gear 49 that is fixed at the center position of the shaft 48.

  Due to the transmission to the steering center gear 49, the clutch pawl 49a of the steering center gear 49 and the clutch pawl of the large-diameter gear 3a of the left and right dual steering clutch 3 rotating freely on the steering clutch shaft 48 are moved in the direction. When the switching solenoid valve 72 is opened, the left and right push cylinders 50 and the shifter 51 are engaged and connected to each other so that the vehicle travels straight.

  Transmission is performed from the small-diameter gear 3 b of the left and right steering clutch 3 to the axle gear 52 that is fixed to the axle 53, and the left and right traveling crawlers 12 are driven by the left and right traveling sprockets 54 that are transmitted through the axle gear 52.

  Next, the brake drive gear 46 fixed to the counter shaft 44 is transmitted to the brake driven gear 55 integrally joined to the brake turning clutch 7 fixed to the turning clutch shaft (turning shaft) 5.

  By this transmission, for example, when the brake turning action to the left is performed, the direction switching solenoid valve 72 is switched to the left position by turning on the left power steering switch 64 by tilting the power steering lever 9 to the left. At the same time that the push cylinder 50 is hydraulically operated and the left steering clutch 3 is disengaged, the brake turning clutch 7 is moved by the oil supply from the operating discharge side oil passage p of the cylinder 50 by the OFF state of the turning switching solenoid valve 74. Enter.

  When the brake turning clutch 7 is engaged, the turning drive gear 57 fixed to the turning clutch shaft 5 is driven, and the differential case gear 1c fixed to the outer periphery of the differential case 1b of the differential gear device 1 from the turning drive gear 57. The differential case 1b is rotated by transmission of the differential case gear 1c, and the differential gear 1a is operated by rotation of the differential case 1b.

  Due to the action of the differential gear 1a, the left turning control gear 58 is fixed to the right turning control shaft 58 that is driven to rotate in the normal state by the large diameter gear 3a of the right steering clutch 3. The differential output gear 59 fixed to the control shaft 58 is output and rotated in response to the rotational change of the differential case 1 b and is transmitted to the large-diameter gear 3 a of the left steering clutch 3.

  The rotation of the axle gear 52 from the large diameter gear 3a of the left steering clutch 3 to the small diameter gear 3b is stopped with respect to the axle gear 52 from the large diameter gear 3a of the right steering clutch 3 of the normal rotation to the small diameter gear 3b. By doing so, the brake turning action to the left side can be performed.

For example, when the left and right turning control shafts 58 are set to X and Y and the differential case 1b is set to Z, the speed change operation of the differential gear device 1 is configured such that 2Z = X + Y. (The numerical value of this speed change configuration is free)
Next, the mild drive gear 47 fixed to the counter shaft 44 is transmitted to the mild driven gear 56 integrally joined to the mild rotary clutch 6 fixed to the rotary clutch shaft 5.

  For example, when performing a mild turning action to the left side by this transmission, the direction switching solenoid valve 72 is switched to the left position by turning on the left power steering switch 64 by tilting the power steering lever 9 to the left side. At the same time that the push steering cylinder 50 is hydraulically operated and the left steering clutch 3 is disengaged, and the mild turning side of the turning switch 9a of the handle portion 9b is turned on, the turning switching electromagnetic valve 74 is switched to the right position, and the cylinder The mild turning clutch 6 is engaged by feeding oil from the 50 operation discharge side oil passage p.

  When the mild turning clutch 6 is engaged, the turning drive gear 57 that is fixed to the turning clutch shaft 5 is driven. After that, through the same operation stroke as in the brake turning action as described above, By reducing the rotation of the axle gear 52 from the large-diameter gear 3a of the left steering clutch 3 to the axle gear 52 via the small-diameter gear 3b relative to the axle gear 52 via the small-diameter gear 3b from the large-diameter gear 3a of the steering clutch 3, A mild turning action can be performed.

  Next, for example, when performing the spin turning action to the left side, the direction switching solenoid valve 72 is switched to the left position by turning on the left power steering switch 64 by tilting the power steering lever 9 to the left side. When the push cylinder 50 is hydraulically operated and the left steering clutch 3 is disengaged, the turning switch 9a of the handle portion 9b is turned on to turn on the spin turning side, whereby the turning switching electromagnetic valve 74 is switched to the left position. The spin turning clutch 8 is engaged by oil feeding from the operation discharge side oil passage p.

  When the spin turning clutch 8 is engaged, the drive of the turning drive gear 57 fixed to the turning clutch shaft 5 is locked, and the differential case gear 1c of the differential gear device 1 meshing with the turning drive gear 57 is used as a differential case. 1b is locked, and by the action of the differential gear 1a, a differential output gear 59 that is fixed to the right turning control shaft 58 that is rotationally driven in a normal state by the large-diameter gear 3a of the right steering clutch 3; A differential output gear 59 fixed to the left turning control shaft 58 is rotated in the opposite direction and transmitted to the large-diameter gear 3a of the left steering clutch 3.

  The rotation of the axle gear 52 through the small diameter gear 3b from the large diameter gear 3a of the left steering clutch 3 is reversed with respect to the axle gear 52 through the small diameter gear 3b from the large diameter gear 3a of the right steering clutch 3 of normal rotation. By rotating, a spin turning action to the left side can be performed.

  In the combine work, the work by the normal brake turning is the most, and the work in the mild turning and the spin turning is less frequent. Therefore, by setting the turning switching solenoid valve 74 to the brake turning action at the center position (OFF). The durability of the electromagnetic coil can be improved and the power consumption can be reduced.

  Further, when performing the direction automatic control action when going straight, the direction is corrected by the detection signal of the direction sensor 67 in the direction automatic control mode. When the direction is corrected, the direction of the sensitivity setting dial 10 is adapted to each work condition. By changing the sensitivity (direction correction amount) between small, medium and large with the mild turning clutch 6, brake turning clutch 7, and spin turning clutch 8, the operability of direction correction in the automatic direction control action can be changed. Can be improved.

Even when manual direction correction is performed by tilting the power steering lever 9 to the left and right, the same action as that during automatic direction correction can be performed.
In addition, the direction correction sensitivity when performing the direction automatic control action when going straight is largely supported by switching of each of the turning clutches 6, 7, 8, and fine adjustment of the direction correction amount for each turning action can be made by the push cylinder. By adjusting the pressure of the electromagnetic proportional valve 73 disposed in the 50 operation discharge side oil passage p, it is possible to perform automatic direction correction with high accuracy.

Further, the sub-shift operation by the low / medium-speed drive gear 35 and the shift operation by the variable motor 29 b of the hydraulic continuously variable transmission 29 are configured to be performed by a single sub-shift lever 62.
As shown in FIG. 5, the speed change operation by the auxiliary speed change lever 62 is long in the front-rear direction in which the operation of the lever 62 arranged on one side of the operation panel 25 a of the operation device 25 is easy to generate the operation force by the support shaft 83. As the stroke as, the sub-shift with a heavy operation load is switched by the link mechanism 62a, and a light operation for changing the swash plate angle of the variable motor 29b is performed as a short stroke bs in the left-right direction via the bent metal 84. A combination shift is performed by 62c.

By such a combination of shifts, the low and medium speed shifts of the sub shift and the speed increase shift of the variable motor 29b can be operated continuously, so that the operability can be improved.
Further, as shown in FIG. 6, in the basic hydraulic circuit shown in FIG. 4, a brake switching electromagnetic valve 75 is connected to an oil passage r that returns oil from the direction switching electromagnetic valve 72 to the oil tank 68. The switching electromagnetic valve 75 is electrically connected to a brake switch 76 provided at an appropriate position.

  With such a configuration, when the brake switch solenoid valve 75 is switched and the oil passage r is locked by turning on the brake switch 76, the left and right push cylinders 50 are simultaneously hydraulically operated to disengage the left and right steering clutch 3 and turn. By switching the switching electromagnetic valve 74 to the left position and turning on the spin turning clutch 8 by oil feeding from the operation discharge side oil passage p of the cylinder 50, the spin turning clutch 8 is also used as a parking brake. Can do.

  In this state, the cutting output pulley 77 that is fixed to the outward projecting end portion of the input shaft 34 can be driven. Therefore, when the cutting device 23 is operated while the vehicle body 2 is stopped, the work is performed. It is necessary for the above, and workability can be improved.

  Further, as shown in FIG. 7, in the basic traveling mission case 4 shown in FIG. 1, the parking brake pedal 78 is rotatably supported by a support shaft 78a, and the operation arm 78b side and the left and right operations are controlled. The direction clutch 3 is connected so as to be able to act simultaneously (disconnect), and the same action arm 78b side and the spin turning clutch 8 are connected so as to be able to act (lock).

  With such a configuration, when the parking brake pedal 78 is depressed, the left and right steering clutches 3 are simultaneously disconnected, and the spin turning clutch 8 is mechanically locked, whereby the clutch 8 is used as a parking brake. Since it can be utilized, there is a cost reduction effect.

  Further, in the traveling mission case 4 shown in FIG. 7, the mission oil used in the case 4 is used for the operation of the hydraulic continuously variable transmission 29 and the operation of the respective turning clutches 6, 7, 8. And an oil filter 79 is provided at an appropriate position in the circuit of the continuously variable transmission 29.

  With such a configuration, since the transmission oil can be used as each hydraulic pressure source, the configuration can be simplified, and the suction filter 79a and the line filter 79b are disposed at appropriate positions in the circuit of the continuously variable transmission 29. Clean oil filtered by the filters 79a and 79b can be fed into the continuously variable transmission 29, which can clean the entire mission oil and reduce various hydraulic troubles.

  Conventionally, the continuously variable transmission 29 is equipped with a dedicated oil tank, and the circuit of the continuously variable transmission 29 and the circuit of the hydraulic clutch are provided with separate oil filters, resulting in high costs. It was.

  Further, as shown in FIG. 8, the gear interlocking mechanism of the traveling mission case 80 is basically the same as the construction according to the traveling mission case 4 shown in FIG. There is no change in the mild turning clutch 6 and the brake turning clutch 7 that are fixed to the shaft 5, but the spin turning that is fixed to the shaft end portion of the turning clutch shaft 5 that protrudes from the outer wall 80a of the transmission case 80. Instead of the clutch 8, only the part where the parking brake 81 is fixed is changed.

  As shown in FIG. 9, the hydraulic circuit for operating the mission case 80 is basically the same as the configuration according to the hydraulic circuit shown in FIG. It is possible to switch to the mild turning clutch 6 and the brake turning clutch 7 through a 4-port / 2-position switching turning solenoid valve 82 instead of the turning switching solenoid valve 74 fed from the side oil passage p. Only the part to be connected is changed.

  With such a configuration, when the turning switching electromagnetic valve 82 is in the OFF state, the brake turning is performed by supplying oil to the brake turning clutch 7. In general, combine work involves the most work by brake turning, and the frequency of work in mild turning is low. Therefore, by deenergizing the brake turning side, the durability of the electromagnetic coil and power consumption can be reduced. Can do.

  Further, in the transmission case 80, a parking brake 81 pivotally supported by the support shaft 78a is fixed to the parking brake 81 that is fixed to the shaft end portion of the turning clutch shaft 5 protruding from the outer wall 80a of the case 80. The left and right steering clutches 3 are connected via an action arm 78b of the brake pedal 78 so as to be able to act simultaneously (disconnect), and the action arm 78b and the parking brake 81 are connected so as to be able to act (lock).

  With such a configuration, when the parking brake pedal 78 is depressed, the left and right steering clutches 3 are simultaneously disconnected and the parking brake 81 can be locked, so that the rotation of the differential gear device 1 is fixed. It can be used as a parking brake with a simple mechanism of braking.

  In the mission case 80, only the mild turning action and the brake turning action can be executed, and the spin turning action cannot be executed. However, since the spin turning action is executed less frequently, it is practically inconvenient. There is nothing.

The front expanded line figure which shows the arrangement | sequence state of the gear interlocking mechanism of the mission case for driving | running | working. The top view which shows the arrangement | positioning state of each levers etc. which were provided on the operation panel of the operating device. The front view which shows the structure of the steering operation tool (power steering lever) which acts by tilting operation. The block diagram which shows the hydraulic circuit which performs switching of a subshift and each clutch for turning. FIG. 5 is an operation diagram illustrating switching of a sub-shift by a sub-shift lever and a shift state of a hydraulic motor. The block diagram which shows the switching relationship of a parking brake in the hydraulic circuit shown in FIG. The action figure which shows the state of a mechanical parking brake and lubricating oil in a mission case. FIG. 3 is a front development diagram showing the omission of spin rotation in the mission case shown in FIG. 1. The block diagram which shows the change relationship of a turning switching solenoid valve in the hydraulic circuit shown in FIG. The side view which shows the whole structure in a combine.

1 differential gear unit
1a differential gear
1b differential case
1c Differential case gear 2 Car body 4 Driving mission case
5 pivot axis
6 Slow turn clutch
8 spin turning clutch 9 power steering lever (steering operation tool)
9a turning switch
9b handle 11 chassis 12 traveling crawler 13 traveling device 15 grain tank 17 threshing device 23 reaping device 25 operating device 26 operating seat 27 engine 29 hydraulic continuously variable transmission 29a variable pump 29b variable motor 30 input pulley 34 input shaft 35 Low and medium speed drive gear (sub transmission gear)
57 Turning drive gear
59 differential output gear (output gear)
60 Main transmission lever 62 Sub transmission lever

Claims (1)

A traveling device (13) having a pair of left and right traveling crawlers (12) is provided on the lower side of the chassis (11), and a threshing device (17) including a Glen tank (15) is provided on the chassis (11), and the threshing device is provided. A mowing device (23) is provided in front of (17) so as to be movable up and down, and an operation seat (26) and an operation device (25) are provided on the front side of the Glen tank (15) to constitute a vehicle body (2). A traveling mission case (4) is provided on the front side of the chassis (11), and a hydraulic continuously variable transmission (29) is attached to the traveling mission case (4) so as to be interlocked. The power from the engine (27) can be transmitted to the input pulley (30) of the variable pump (29a) of the device (29), and via a variable motor (29b) driven by the variable pump (29a). Missi for traveling Nkesu (4) of the configuration you transmitted to the input shaft (34), the input shaft two the spline (34) slidable in the axial direction series of auxiliary transmission gear (35) is provided, traveling Mission A turning drive gear (57) is provided on the turning shaft (5) of the case (4), and a differential case gear (1c) on the outer periphery of the turning drive gear (57) and the differential case (1b) of the differential gear device (1). ) And the axle gear is driven via the output gear (59) of the differential gear device (1), and the hydraulic continuously variable transmission (29) is connected to the operating device (25). ) Of the variable speed pump (29a) to adjust the speed of the vehicle body (2) for forward / reverse switching and shifting, and the auxiliary transmission gear (35) in the traveling transmission case (4). A sub-shift lever (62) for shifting the speed of the vehicle, 2) steering operating tool swirling and (9) is provided actuated,該操direction operating member (9) turning axis on the basis of the turning operation of the (5) slow turning clutch (6) which hermetically axis Then, the rotation of the output gear (59) is changed via the differential gear (1a) in the differential gear device (1) by being transmitted to the differential case gear (1c) by driving the turning drive gear (57). by, for the one lateral side of the axle formic ya then decelerates axle formic ya of the right and left the other side and configurations that can be swiveled, wherein the steering operation member (9) turning axis based on the spin turning operation of ( In 5), the drive of the turning drive gear (57) is locked by operating the spin turning clutch (8) that is fixed to the end protruding from the outer wall of the traveling mission case (4). The differential case gear (1c) meshing with (57) Locks the rotation of (1b), by the output rotation of one of left and right sides of the output gear (59) in the opposite direction through the differential gear (1a), against the one lateral side of the axle formic Ya of the left and right other-side axles by reversely rotating the formic ya and configuration that can spin turning, oN action of the handle portion (9b) slow turning clutch (6) and spin turning clutch (8) of said steering operating member (9) / the OFF switch for turning the selector switch (9a) is mounted, by changing the swash plate angle of the variable motor (29 b) and configuration that can shift operation of the hydraulic stepless transmission (29), of said single I by the auxiliary shift lever (62), a shift operation of the auxiliary transmission gear of the driving transmission within the case (4) (35), the swash plate of the variable motor (29 b) of said hydraulic stepless transmission (29) a configuration that perform a shift operation by the angle changes, the sub-variable The sub-shift operation with a heavy operation load is performed by operating the lever (62) in the front-rear direction with a long operation stroke, and the variable motor (29b) with a light operation load is operated by the left-right operation with a short operation stroke by the sub-shift lever (62). A combine that is configured to change the swash plate angle .

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