JP2007174971A - Working vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a working vehicle designed to be automatically stopped by lifting working units 5 and 28 to nonworking positions and thereby to smoothly make its turning travel with reducing engine rotating speed drop attributable to the drive load of these working units. <P>SOLUTION: The working vehicle has the following mechanism. As a first means, a statically hydraulic stepless variable-speed gear (47) that drives a traveling unit (2) is subjected to variable-speed actuation by the control of a variable-speed lever (S) and another statically hydraulic stepless variable-speed gear (76) that drives the working units (5 and 28) is subjected to automatic variable-speed actuation in association with lifting the working units (5 and 28) to nonworking positions. As a second means, additionally, the statically hydraulic stepless variable-speed gear (76) is subjected to variable-speed actuation by the control of a switch (119) furnished on the variable-speed lever (S). <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a work vehicle such as a combine.

2. Description of the Related Art Conventionally, work vehicles are provided with a hydrostatic continuously variable transmission that drives a traveling device and a hydrostatic continuously variable transmission that drives a working device.
As an example, Patent Document 1 describes a combine that includes a hydrostatic continuously variable transmission that drives a crawler type traveling device and a hydrostatic continuously variable transmission that drives a mowing device. That is, the drive speed of the reaping device, which is a working device, is shift-controlled to a speed corresponding to the vehicle speed.
Japanese Utility Model Publication No. 56-57025

  However, in a working vehicle such as that described in Patent Document 1 described above, for example, even when the working device is raised to a non-working position during turning, the working device does not automatically stop. Further, there is a problem that the rotational speed of the engine decreases due to an increase in the traveling load accompanying the turning, and the turning cannot be performed smoothly.

  Moreover, in a working vehicle as described in Patent Document 1 described above, the working device cannot be arbitrarily driven while the vehicle is stopped. Therefore, for example, in a harvesting operation using a combine, when a side of the field is cut and the corner of the field is reached, the output of the hydrostatic continuously variable transmission that drives the traveling device by operating the shift lever to the neutral position When the vehicle is stopped and the vehicle is stopped, the output of the hydrostatic continuously variable transmission that drives the reaping device is also stopped, and the planted cereals remaining in the front of the vehicle cannot be harvested.

  As described above, according to the conventional technology, the working device cannot be automatically stopped when turning, and the working device cannot be arbitrarily driven in a state where the airframe is stopped, so that the work efficiency is lowered. There was a problem.

In order to solve the above-mentioned problems, the present invention takes the following technical means.
That is, the invention according to claim 1 is configured such that the hydrostatic continuously variable transmission (47) for driving the traveling device (2) is operated to shift by operation of the transmission lever (S) and the working device (5). , 28), the hydrostatic continuously variable transmission (76) is configured to automatically shift in relation to the working device (5, 28) being raised to the non-working position. This is a working vehicle.

  Thus, when the shift lever S is operated to the forward side, the hydrostatic continuously variable transmission 47 that drives the traveling device 2 is shifted to the forward rotation speed increasing side, and the machine body travels forward. Note that, during this forward traveling, the hydrostatic continuously variable transmission 76 that drives the work devices 5 and 28 may be configured to drive the work devices 5 and 28 by performing a shift operation. Thus, when the working devices 5 and 28 are raised to the non-working position, the hydrostatic continuously variable transmission 76 that drives the working devices 5 and 28 is automatically shifted, and the working devices 5 and 28 are stopped.

  According to a second aspect of the present invention, the hydrostatic continuously variable transmission (47) for driving the traveling device (2) is configured to be shifted by an operation of the transmission lever (S). The hydrostatic continuously variable transmission (76) for driving 28) is configured to be shifted by operating a switch (119) provided on the transmission lever (S), and the working device (5, 28) is not operated. The working vehicle is characterized in that it is configured to automatically perform a shift operation in association with the ascent to the working position.

  Thus, when the shift lever S is operated to the forward side, the hydrostatic continuously variable transmission 47 that drives the traveling device 2 is shifted to the forward rotation speed increasing side, and the machine body travels forward. During this forward travel, the hydrostatic continuously variable transmission (76) that drives the working device (5, 28) may be operated to drive the working device (5, 28). . Thus, for example, the shift lever S is moved to the neutral position by reaching the corner of the work place to stop the machine body, and when the switch 119 provided on the shift lever S is operated in this stopped state, the work devices 5 and 28 are driven. The hydrostatic continuously variable transmission 76 that performs the shift operation operates to drive the work devices 5 and 28. When the working devices 5 and 28 are raised to the non-working position, the hydrostatic continuously variable transmission 76 that drives the working devices 5 and 28 automatically shifts and the working devices 5 and 28 stop.

  According to the first aspect of the present invention, the working devices 5 and 28 can be automatically stopped by raising the working devices 5 and 28 to the non-working position, and work can be performed even if the traveling load increases with turning. Since no load is applied, the engine speed is unlikely to decrease, and the vehicle can smoothly turn.

  According to the second aspect of the invention, even when the airframe is stopped, the work devices 5 and 28 can be arbitrarily driven by the operation of the switch 119 provided on the speed change lever S to improve work efficiency. In addition, the working devices 5 and 28 can be automatically stopped by raising the working devices 5 and 28 to the non-working position, and no work load is applied even if the traveling load increases with turning. For this reason, the engine speed is unlikely to decrease, and the cornering can be smoothly performed.

A working vehicle according to an embodiment of the present invention will be described by exemplifying a self-removing combine as an agricultural working vehicle.
As shown in FIGS. 1 and 2, the combine is provided with a traveling device 2 on the lower side of the machine base 1, and the threshing device 3 and the grain storage device 4 are provided side by side on the upper side of the machine base 1, A reaping device (working device) 5 is disposed on the front side of the threshing device 3, and a control unit 6 is disposed on the front side of the grain storage device 4.

  The traveling device 2 has left and right wheel frames 8, 8 attached to lower ends of frame feet 7, 7 extending outwardly from the left and right lower surfaces of the machine base 1, and the wheel frames 8, 8 are attached. The crawlers 13 and 13, which are endless track belts, are wound around a large number of wheels 9 and 9, the rear end tensioning wheels 10 and 10 and the left and right drive wheels 12 and 12 driven from the traveling mission case 11. Multiply and configure.

  The reaping device 5 pivotally supports the rear end portion of the at-frame 15 on the upper portion of the mowing suspension base 14 installed at the front portion of the machine base 1 so as to be pivotable up and down. A gear case 16 is connected, a weeding frame 17 is extended forward from the gear case 16, a plurality of weeding bodies 18 are attached to the front end portion of the weeding frame 17, and the rear of the weeding body 18 in the weeding frame 17. The lower part of the pulling device 19 is fixed to the side, and the upper part of the pulling device 19 is connected to the upper end of the pulling transmission shaft 20 raised from the upper surface on the left and right sides of the gear case 16. A cutting blade 21 is attached to the side of the cutting blade 21 and a scraping star wheel 22 is rotatably arranged on the upper side of the cutting blade 21. A stock transport chain 23 is erected from the upper side of the stirring star wheel 22 to the rear. Rear part of stock transport chain 23 Followed by constructed by arranging a strain base side supply conveyor device 25 up and down with the tip side supply conveyor device 24 and the threshing depth adjustment functions.

  The threshing device 3 includes an upper handling chamber 26 and a lower sorting chamber 27. That is, a feed chain (working device) 28 is disposed on the outer side of the handling chamber 26, and the processing material sent from the handling cylinder 29 and the second transfer spiral described later is reprocessed in the handling chamber 26. A second treatment cylinder 30 and a dust removal treatment cylinder 31 that rotate coaxially with the second treatment cylinder 30 and perform dust removal treatment on the crushed material sent from the handling cylinder 29 side. A waste transport chain 32 is provided at the upper rear side of the handling cylinder 29 to take over the drained waste from the feed chain 28 and transport it to the outside of the machine. A dust exhaust fan 43 is disposed below the waste transport chain 32. Configure. Further, the sorting chamber 27 is arranged with the auxiliary tang 44, the main tang 33, the first transport spiral 34, the second tang 35, and the second transport spiral 36 from the front side, and the swing sorting shelf 37 is swung above them. It is configured to be movable. Further, the first storage spiral 34 is configured to inject the grain into the grain storage device 4 through the first lifting spiral 38, and the second transport spiral 36 through the second reduction spiral 39. The second product is configured to be returned to the starting end (right end in the drawing) of the second processing cylinder 30.

  The grain storage device 4 has a bottom surface formed in a valley shape, a bottom conveyance spiral 40 is provided at the bottom of the valley, and a cerealing helix 41 is provided at a terminal portion of the bottom conveyance spiral 40 (outside of the grain storage device 4). It connects, and the discharge spiral 42 is connected to the upper end part of this whipping spiral 41, and it is comprised so that rotation up and down is possible.

Thus, the transmission mechanism of this combine will be described with reference to FIG.
A transmission belt 49 is wound between an output pulley 46 of an engine 45 provided under the seat of the control unit 6 and an input pulley 48 of a hydrostatic continuously variable transmission 47 attached to the upper part of the traveling mission case 11. The hydrostatic continuously variable transmission 47 includes a hydraulic pump 47p driven by the rotation of the input pulley 48, and a plunger piston type hydraulic motor 47m that receives oil supplied from the hydraulic pump 47p and converts it into rotational power. Are connected by a closed circuit oil passage, and the swash plate angle on the hydraulic pump 47p side is adjusted by the operation of a main transmission lever (transmission lever) S provided in the control section 6. And the drive output rotation speed of the hydraulic motor 47m can be adjusted steplessly in the forward / reverse direction from the stopped state.

  Then, the output shaft of the hydraulic motor 47 m of the hydrostatic continuously variable transmission 47 is connected to the rotation shaft of the input gear 50 of the transmission case K provided on the upper side of the traveling mission case 11. The counter gear 51 is meshed, the output gear 52 is meshed with the counter gear 51, and the auxiliary transmission output gear 53 provided coaxially with the output gear 52 so as to be slidable is provided on the lower intermediate shaft. The sub-transmission mechanism 55 is configured so as to be able to selectively mesh with the sub-transmission input gear 54 of different sizes, and the output gear 56 provided on the intermediate shaft is meshed with the center gear 57 provided on the lower side clutch shaft. Side clutch gears 58, 58 are provided on both the left and right sides of the center gear 57 so as to be freely disengaged from the center gear 57. The side clutch gears 58, 58 are provided outside the left and right side clutch gears 58, 58, respectively. Side brakes 59, 59 for braking the rotation of the clutch gears 58, 58 are provided, and the left and right side clutch gears 58, 58 are meshed with the left and right wheel gears 59, 59 provided at the inner ends of the left and right axles, The left and right drive wheels 12, 12 are attached to the outer ends of the left and right axles.

  Further, a transmission belt 62 having a tension clutch type threshing clutch 61 is wound between the output pulley 46 of the engine 45 and an input pulley 60 provided at one end of the threshing counter shaft, and the intermediate portion of the threshing counter shaft is wound. A transmission belt 65 is wound between an output pulley 63 provided and an input pulley 64 provided at an inner end portion of the drive shaft of the main tang 33, and an output pulley provided at an outer end portion of the drive shaft of the main tang 33 66, the input pulley 67 provided at the outer end of the first transfer spiral 34 axis, the input pulley 68 provided at the outer end of the second transfer spiral 36 axis, and the outer end of the intermediate shaft that is transmitted to the dust exhaust fan 43 axis. A transmission belt 70 is wound around the input pulley 69 provided on the output pulley 69, and between the output pulley 63 provided at the intermediate portion of the threshing countershaft and the input pulley 71 provided on the swing crankshaft of the swing sorting shelf 37. Wound around a transmission belt 72.

  Further, a transmission belt 74 is wound between the output pulley 46 of the engine 45 and an input pulley 73 provided on one end side of the counter shaft, and the bottom conveying spiral of the grain storage device 4 from the other end side of the counter shaft. It is configured to link 40 axes.

  A transmission case 75 is attached to a cutting suspension base 14 that supports the rear end portion of the at-frame 15 of the cutting device 5 so as to be rotatable up and down, and a hydrostatic pressure for feed chain / cutting driving is provided on one side of the transmission case 75. A continuously variable transmission (feed chain / cutting drive HST) 76 is attached. The hydrostatic continuously variable transmission 76 is a hydraulic pump 76p driven by the rotation of an input pulley 79 driven via a transmission belt 78 from an output pulley 77 provided at the outer end of the drive shaft of the main gear 33. And a plunger piston type hydraulic motor 76m that receives oil from the hydraulic pump 76p and converts it into rotational power, and is connected by a closed oil path, and the swash plate on the hydraulic pump 76p side By adjusting the angle by the operation of the feed chain / reaping drive HST control motor 80, the oil feed amount can be changed, and the drive output rotational speed of the hydraulic motor 76m can be adjusted steplessly in the forward / reverse direction from the stopped state. . Then, the output shaft of the hydraulic motor 76m of the hydrostatic continuously variable transmission 76 is connected to the input shaft in the transmission case 75, and the intermediate gear 82 is meshed with the input gear 81 provided on the input shaft. An output gear 83 is meshed with the gear 82, and is provided coaxially with an output pulley 84 provided on an output shaft having the output gear 83 and a vertical rotation axis provided on a rear end portion of the at-frame 15 of the reaping device 5. A transmission belt 86 having a tension clutch function as a cutting clutch is wound around the input pulley 85 of the cutting input shaft. Further, a transmission belt 88 is wound between the output pulley 84 and an input pulley 87 provided on the drive shaft of the auxiliary tang 44.

  Further, a transmission belt 91 is wound between the output pulley 84 and the input pulley 90 provided at the outer end of the input shaft on the feed chain transmission case 89 side, and the inner end of the input shaft provided with the input pulley 90. The input gear 92 provided on the intermediate shaft and the counter gear 93 provided on the intermediate shaft are meshed with each other, and the counter gear 93 and the output gear 94 provided only slidably on the inner end of the output shaft are separated by operating the shifter 95. The drive sprocket 96 is provided at the outer end of the output shaft, and an intermediate portion of the feed chain 28 is wound around the drive sprocket 96.

Reference numeral 125 denotes a cooling fan.
Next, the above-described combine control system will be described with reference to FIG.
The hydraulic circuit connects a three-position switching valve 98 for switching the oil feeding direction to the discharge side of the hydraulic pump 97, and feeds oil to the hydraulic cylinder 99 for driving the lifting / lowering device 5 on the lower side of the three-position switching valve 98. A three-position switching valve 100 for switching the oil feeding direction is connected to the lower side of the oil feeding path for direction control, and the three-position switching valve 100 The left and right side clutch gears 58, 58 are slid on the lower side, and oil supply paths to the left and right push cylinders 101, 101 that are detached from the center gear 57 are connected. 102 is a hydraulic oil tank, 103 is a high-pressure relief valve, 104 is a variable relief valve in which the relief pressure is changed by operation of a steering lever 105 provided in the control unit 6, and 107 is a flow control valve. Further, the three-position switching valve 100 supplies oil by operating a steering lever 105 provided in the control unit 6 and a signal from a direction control sensor 106 provided on the rear side of the weeding body 18 in the cutting device 5. Interlock so that the direction changes.

  Then, the lower oil passage of the variable relief valve 104 is connected to the closed circuit of the hydrostatic continuously variable transmission 47 for driving the traveling device and the hydrostatic continuously variable transmission (feed for driving the feed chain and reaping drive). Connected to the closed circuit of the chain / cutting drive HST) 76 to replenish hydraulic oil. 108 is a check valve, 109 is a relief valve, and 110 is a throttle valve.

  Further, on the input side of the controller (CPU) 111, an HST trunnion angle detection sensor (swash plate angle detection sensor) 112, a vehicle speed detection sensor 113, a reverse detection sensor 114, a neutral detection sensor 115, and a feed chain speed setting dial are provided. 116, feed chain drive switch 117, feed chain stop switch 118, scraping switch (switch) 119, engine stop switch 120, handling operation detection switch 121, feed chain / cutting reverse switch 122, feed chain / cutting speed increasing switch The feed chain / reaping drive HST control motor 124 is connected to the output side. The scraping switch 119 and the feed chain / cutting speed increasing switch 123 are provided on the side surface of the grip portion of the main transmission lever S.

  With this configuration, when the main shift lever S is operated from the neutral position to the slow forward position and the scraping switch 119 is turned on with the threshing clutch engaged, the controller 111 moves to the feed chain / reaping drive HST control motor 124. The drive output is made, and the swash plate angle of the hydraulic motor 76p of the hydrostatic continuously variable transmission (feed chain / cutting drive HST) 76 for feed chain / cutting drive is changed from the neutral position to the forward rotation speed increasing direction, The output shaft of the hydraulic motor 76m rotates in the forward direction at a constant speed. Further, the rotation to the constant speed may be realized by gradually increasing from the low speed to the high speed. Thereby, it is possible to stably carry out the scraping operation of the planted cereal at the end of the field while driving the reaping device 5 and the feed chain 28 at a constant speed.

  In the above-described configuration, when the main shift lever S is operated from the neutral position to the slow forward position and the scraping switch 119 is turned on while the threshing clutch is engaged, the controller 111 controls the feed chain / reaping drive HST. A drive output is made to the motor 124 for a set time, and the swash plate angle of the hydraulic motor 76p of the hydrostatic continuously variable transmission (feed chain / cutting drive HST) 76 for feed chain / cutting driving is increased from the neutral position to the forward rotation speed. The angle may be changed in the direction, and the output shaft of the hydraulic motor 76m may rotate in the forward direction at a constant speed, and this state may be maintained for a set time. That is, conventionally, when reaching the field corner during the cutting operation, the main shift lever is operated with the parking brake applied to drive the cutting unit to cut and interrupt the planted cereal in this field corner. In this case, the main transmission lever has to be operated to the neutral position, which is troublesome. Further, when the feed chain and the cutting device are driven for a long time, there is a problem that the uncut grain culm that is not the target of cutting is scraped. However, according to the above-described configuration, even if cutting is interrupted at the corner of the field, it can be scraped by a switch operation, so that spilling of cereal can be prevented. Moreover, since this scraping is performed for a set time, it is possible to eliminate the problem of scraping an uncut grain culm that is not to be cut.

  In the above-described configuration, the neutral detection sensor 115 indicates that the driving of the reaping device 5 and the feed chain 28 by the ON operation of the scraping switch 119 is stopped, and that the hydrostatic continuously variable transmission 47 for traveling is in a stopped state. It may be configured to be effective only when it is detected. As a result, the scraping operation can be performed only when the aircraft is stopped, so that a problem caused by an erroneous operation can be solved.

  Further, in the above-described configuration, when the main transmission lever S is in the neutral range, even if the feed chain / cutting speed increasing switch 122 is turned ON, the speed increasing drive of the cutting device 5 and the feed chain 28 is not performed, and the scraping is performed. The drive of the cutting device 5 and the feed chain 28 may be started when the turning switch 119 is turned on. In this case, the driving start of the reaping device 5 and the feed chain 28 by the ON operation of the raking switch 119 is performed only when the main transmission lever S is in the neutral range. As a result, even if both the scraping switch 119 and the feed chain / cutting speed increasing switch 122 are operated, the operation is restricted by the operation position of the main transmission lever S. Trouble can be reduced.

  In the above-described configuration, when the feed chain / cutting reverse switch 122 is turned on, a drive output is made from the controller 111 to the feed chain / cutting drive HST control motor 124 for a set time. The swash plate angle of the hydraulic motor 76p of the hydraulic continuously variable transmission (feed chain / cutting drive HST) 76 is changed from the neutral position to the reverse acceleration direction, and the output shaft of the hydraulic motor 76m rotates at a constant speed in the reverse direction. It may be configured so that this state is maintained for a set time. Thereby, when clogging of the cereals occurs in the reaping device 5 or the feed chain 28, the reaping device 5 or the feed chain 28 can be reversed to easily remove the clogged cereals. Further, since this reverse rotation state automatically ends with the set time, the operation can be facilitated.

  Further, as shown in FIG. 4, even when the one-way clutch 126 is provided in the drive input unit of the tip side supply / conveyance device 24 and the drive input unit of the pulling device 19, the tip of the cutting device 5 is driven in reverse as described above. The side supply transport device 24 and the pulling device 19 may be configured not to be driven in reverse. Thereby, the breakage of the lugs of the tip side supply / conveyance device 24 and the pulling device 19 can be prevented.

  Further, as shown in FIG. 5, when the transmission of the pulling device 19 is configured so that a plurality of the pulling devices 19 are interlocked from the pulling transmission shaft 20 via the upper lateral transmission shaft 127, the pulling transmission shaft 20. The one-way clutch 126 may be provided in the middle of transmission from the upper lateral transmission shaft 127 to the upper lateral transmission shaft 127. If comprised in this way, since the reverse rotation of the several raising apparatus 19 in the multi-row mowing apparatus can be prevented with the single one-way clutch 126, it can comprise at low cost.

  In addition, as shown in FIG. 6, the maximum vehicle speed when the auxiliary transmission mechanism 55 is in the “standard” position is Vm, the maximum vehicle speed when the auxiliary transmission mechanism 55 is in the “low speed” position is VL, and the number of basic cutting strips is When N is set, the vehicle speed may be set so that the formula Vm × N = VL × (N + 1) holds. In other words, the self-removing combiner can cut the number of basic cutting lines (the number of cutting lines set) N or N + 1, and by setting the vehicle speed as described above, any number of cutting lines can be obtained. However, the threshing ability can be made the same, and the threshing ability can be maximized.

  Further, as shown in FIG. 7, the driving rotation of the counter gear 51 driven from the hydrostatic continuously variable transmission 47 for traveling is transferred to the input pulley 85 of the reaping device 5 via the belt-type continuously variable transmission 128. The swash plate angle of the hydraulic motor 47m of the hydrostatic continuously variable transmission 47 for traveling is configured to be changeable, the reaping device 5 is configured to be swingable to the left and right, and the reaping device. 5 is configured so that it can be rotated in the left-right direction, and when the cutting device 5 swings toward the cutting side, the cutting-side weeding body 18 rotates toward the cutting side and travels. The swash plate of the hydraulic motor 47m of the hydrostatic continuously variable transmission 47 may be interlocked by a wire 129 so that the angle of the swash plate is changed to the deceleration side. That is, when the cutting body 18 on the cutting side is opened to the cutting side and the cutting operation is performed, it is a case where the stalks for three rows are introduced into the cutting device set to two cuttings, and the cutting is performed. There is a problem that the threshing amount increases and the amount of swarf generated in the handling room increases and the threshing loss increases. However, such a problem can be solved by configuring as described above. it can.

  As another embodiment, as shown in FIG. 8, the swash plate angle of the hydraulic motor 47m of the hydrostatic continuously variable transmission 47 for traveling in the above configuration can be changed by the HST motor swash plate switching actuator 142. In addition, the transmission mechanism in the traveling mission case 11 may be replaced with a differential gear mechanism 130, a linear clutch 131, and a swing clutch 132. That is, the side clutch gear 58 on the inner side of the turning is disengaged from the center gear 57 and the turning clutch 132 is connected, so that the driving speed of the wheel gear 59 on the inner side of the turning is reduced and the wheel gear 59 is turned in the reverse direction. It is possible to spin-turn.

  Then, as shown in FIG. 9, a cutting height detection sensor 133 is connected to the input side of the controller 111 described above. Further, an HST trunnion angle detection sensor 135, a vehicle speed detection sensor 113, and an input side of a controller (CPU) 134 that controls the swash plate angle of the hydraulic motor 47 m of the traveling hydrostatic continuously variable transmission 47 are provided. Reverse detection sensor 114, neutral detection sensor 115, maximum vehicle speed setting change means 136, crop type maximum vehicle speed setting means 137, crop condition maximum vehicle speed setting means 138, body weight detection means 139, proficiency level condition maximum vehicle speed setting means 140, and working conditions While connecting with the maximum vehicle speed setting means 141, the HST motor swash plate switching actuator 142 is connected to the output side.

  With this configuration, when the cutting height detection sensor 133 detects that the cutting device 5 has risen above the set height, an output is made from the controller 111 to the feed chain / cutting drive HST control motor 124, and the feed chain The swash plate angle of the hydraulic motor 76p of the hydrostatic continuously variable transmission (feed chain / cutting drive HST) 76 for cutting drive returns to the neutral angle. As a result, the output of the hydraulic motor 76p is stopped, and the driving of the feed chain 28, the driving of the cutting device 5 and the driving of the auxiliary tang 44 are stopped. That is, when the cutting operation speed is increased, in order to improve the sorting performance in the threshing device 3, the auxiliary tang 44 is increased, and the drive of the feed chain 28 and the driving of the cutting device 5 by the rising of the cutting device 5. When ceases, the amount of cereal straw supplied to the threshing device 3 decreases. In this case, it is possible to weaken the sorting wind by stopping the auxiliary tang 44, to prevent the scattering of the grains due to the too strong sorting wind, and to reduce the threshing loss. In the above-described configuration, when the cutting device 5 is raised to a set height or higher, the drive of the feed chain 28, the driving of the cutting device 5, and the driving of the auxiliary tang 44 are stopped, and the driving of the second tang 35 is also stopped. To do. In other words, in order to improve the sorting performance in the threshing device 3 when the cutting work speed is increased, the auxiliary tang 44 and the second tang 35 are provided. When the driving of the reaping device 5 stops, the amount of cereal straw supplied to the threshing device 3 decreases. In this case, the selection wind is weakened by stopping the driving of the auxiliary tang 44 and the driving of the second tang 35, the scattering of the grains due to the selection wind being too strong can be prevented, and the threshing loss can be reduced. .

  Further, as shown in FIG. 10, a turning hydraulic circuit is provided in addition to the above-described traveling hydraulic circuit. That is, the flow control valve 144, the throttle valve 145, the proportional pressure reducing valve 146, and the oil chamber 147 of the swing clutch 132 are connected in series to the discharge side of the hydraulic pump 143. Reference numeral 148 denotes a high pressure relief valve. Then, on the input side of the controller (CPU) 149, there are an HST motor swash plate angle detection sensor 150, an HST pump swash plate angle detection sensor 151, a vehicle speed sensor 152, a reverse detection sensor 153, a neutral detection sensor 154, and a power steering lever. (Steering lever) Angle detection sensor 155, turning speed detection sensor 156, threshing clutch ON detection sensor 157, reaping clutch ON detection sensor 158, grain culm sensor 159, engine rotation sensor 160, hydraulic clutch (turning clutch) pressure detection sensor 161 The turning state detection sensor 162 and the maximum vehicle speed changing means 163 are connected, and the HST motor swash plate switching actuator 164 is connected to the output side thereof. With this configuration, when the steering lever 105 is operated to the left or right, the power steering lever angle detection sensor 155 detects the operating angle of the steering lever 105, and an output from the controller 149 to the HST motor swash plate switching actuator 164 is made. The swash plate angle of the hydraulic motor 47m of the hydrostatic continuously variable transmission 47 is operated to the deceleration side. As a result, the vehicle speed can be automatically reduced (the maximum three-stage regulation shown in FIG. 11) and the torque can be increased during turning without decelerating the auxiliary transmission mechanism 55, thereby improving operability and turning performance. Can be made.

  Further, as shown in FIG. 12, in the turning state corresponding to the operation angle of the steering lever 105, the left and right brake turn regions are arranged outside the left and right mild turn regions, and the left and right brake turn regions are arranged. The left and right spin-turn regions are arranged outside. Further, as shown in FIG. 13, the greater the tilting of the steering lever 105, the stepwise the swash plate angle of the hydraulic motor 47m of the hydrostatic continuously variable transmission 47 for traveling is reduced. It may be linked. As a result, deceleration during turning and improvement of driving torque can be achieved, and the pressure in the closed circuit of the hydrostatic continuously variable transmission 47 for traveling can be reduced to reduce the operation of the relief valve 109. it can. Further, since the pressure on the high pressure side in the closed circuit of the hydrostatic continuously variable transmission 47 for traveling can be reduced, the engine power consumption during turning can be reduced, and the engine rotation drop can be reduced. Threshing performance can be properly maintained.

  Further, when the vehicle starts turning at a vehicle speed equal to or higher than the set speed, the swash plate angle of the hydraulic motor 47m of the hydrostatic continuously variable transmission 47 for traveling is automatically operated to the deceleration side. The speed draws the line shown in FIG. Thereby, when an operation of turning at a set speed or higher is performed, the vehicle speed is automatically decelerated to the set speed, so that safety can be improved.

  As shown in FIG. 15, when the turning state detection sensor 162 detects whether the current turning state is a mild turn (slow turn), a brake turn, or a spin turn, the controller 149 To the HST motor swash plate switching actuator 164, the swash plate angle of the hydraulic motor 47m of the hydrostatic continuously variable transmission 47 for traveling is regulated so as to be restricted to the maximum vehicle speed set according to each turning state. The change limit angle to the acceleration side is regulated. Thereby, since the upper limit of the vehicle speed is regulated according to each turning state, it is possible to turn safely at an appropriate vehicle speed.

  In addition, as shown in FIG. 16, when the threshing clutch is engaged and operated, the threshing clutch ON detection sensor 157 detects this, and an output is made from the controller 149 to the HST motor swash plate switching actuator 164, so that the static You may comprise so that the change limit angle to the acceleration side of the swash plate angle of the hydraulic motor 47m of the hydraulic continuously variable transmission 47 may be controlled. Thereby, the maximum vehicle speed at the time of a threshing operation can be regulated, and an erroneous operation such as performing a cutting operation in a road traveling speed region can be prevented. Note that the swash plate angle of the hydraulic motor 47m of the hydrostatic continuously variable transmission 47 for traveling is detected when the cutting clutch is engaged and operated or when the culm sensor 159 detects a planted culm to be harvested. You may comprise so that the change limit angle to the acceleration side may be controlled. In addition, the maximum vehicle speed is not restricted during reverse travel. That is, no cutting operation is performed during reverse travel, so that there is no need to restrict the maximum vehicle speed. By not restricting the maximum vehicle speed in this way, the vehicle can be moved backward at high speed and work efficiency can be improved. Further, when the engine speed is detected by the engine speed sensor 160 and it is detected that the engine speed has decreased below the set speed during turning, an output is made from the controller 149 to the HST motor swash plate switching actuator 164, A configuration may be adopted in which the swash plate angle of the hydraulic motor 47m of the hydrostatic continuously variable transmission 47 for traveling is operated to reduce the engine speed so that the engine speed does not fall below the set speed. That is, during the cutting operation, the consumption horsepower applied to the engine is large due to the cutting load, the threshing load, and the traveling load, and during turning, a phenomenon occurs in which the turning load is further applied and the engine speed decreases. By doing this, it is possible to prevent the threshing loss from occurring when the engine speed is equal to or lower than the set speed.

  Also, as shown in FIG. 17, when the hydraulic clutch (swing clutch) pressure detection sensor 161 provided in the oil chamber 147 of the swing clutch 132 detects that the operating pressure has risen above the set pressure, the controller 149 causes the HST motor to An output may be made to the swash plate switching actuator 164 so that the swash plate angle of the hydraulic motor 47m of the hydrostatic continuously variable transmission 47 for traveling is continuously (linearly) changed to the deceleration side. . That is, conventionally, since the maximum output torque of the hydraulic motor of the hydrostatic continuously variable transmission for traveling is constant at the time of turning, the relief valve may operate at the brake turn or the spin turn, and the turning may be impossible. Further, when turning at a high speed, a large horsepower is required for the turning, so that the engine speed is reduced, the grain loss is increased, and the threshing performance is lowered. On the other hand, by configuring as described above, it is possible to reduce the pressure on the high pressure side of the hydrostatic continuously variable transmission for traveling during turning, and to reduce the operation of the relief valve, The consumed horsepower can also be reduced, and the decrease in engine rotation can be reduced. Note that the change of the swash plate angle of the hydraulic motor 47m of the traveling hydrostatic continuously variable transmission 47 to the deceleration side is linear after the hydraulic clutch pressure exceeds a predetermined pressure, as shown in FIG. You may comprise so that it may be changed. Thereby, when it is going to perform high-speed turning more than a setting speed, since it decelerates to a setting speed, safety can be improved.

The side view for explanation of a combine. Explanatory diagram of combine transmission. The control system explanatory drawing of a combine. Explanatory drawing of the transmission mechanism of a reaping device. Explanatory drawing of the transmission mechanism of a reaping device. Action explanatory drawing. The top view for description of a combine. Transmission explanatory drawing of the combine in another Example. Explanatory drawing of the control system of the combine in another Example. Explanatory drawing of the control system of the combine in another Example. The graph which shows the relationship between the main transmission lever operating angle and vehicle speed. Explanatory drawing of the operation area | region of a steering lever. The graph which shows the relationship between a steering lever operating angle and the hydraulic oil discharge amount of a hydraulic motor. The graph which shows the relationship between a steering lever operating angle and turning speed. The graph which shows the relationship between each turning mode and the hydraulic oil discharge amount of a hydraulic motor. The graph which shows the relationship between the operation angle of a main transmission lever, and a vehicle speed. The graph which shows the relationship between a hydraulic clutch pressure and a motor discharge amount. The graph which shows the relationship between a hydraulic clutch pressure and a motor discharge amount.

Explanation of symbols

2 Traveling device S Main shift lever (shift lever)
5 Harvesting device (working device)
28 Feed chain (work equipment)
47 Hydrostatic continuously variable transmission 76 Hydrostatic continuously variable transmission 119 Stake-in switch

Claims (2)

  The hydrostatic continuously variable transmission (47) for driving the traveling device (2) is configured to be shifted by the operation of the transmission lever (S), and the hydrostatic continuously variable drive for driving the working devices (5, 28). A working vehicle characterized in that the step transmission (76) is configured to automatically perform a shifting operation in association with the ascent of the working device (5, 28) to the non-working position.   The hydrostatic continuously variable transmission (47) that drives the traveling device (2) is configured to shift by operating the shift lever (S), and the hydrostatic continuously variable drive that drives the working devices (5, 28). The transmission (76) is configured to be shifted by operating a switch (119) provided on the transmission lever (S) and automatically associated with the work device (5, 28) being raised to the non-working position. A working vehicle characterized in that it is configured to operate in a variable speed manner.

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