JP2009112265A - Harvester - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a harvester in which a PTO speed change mechanism for driving a farm work portion at a vehicle speed synchronizing speed and a PTO constant rotation mechanism for driving the farm work portion at a fixed rotation speed can be disposed, in a compact manner and at low cost. <P>SOLUTION: This harvester wherein first speed change means 88 for speed-changing the output of an engine, second speed change means 89 for speed-changing the output of the first speed change means 88, and third speed change means 102 for speed-changing the second speed change means 89 are provided in a mission case 26; a PTO shaft 94 is connected to the output side of the second speed change means 89; and the output of the engine 20 is transmitted from the second speed change means 89 to the farm work portion via the PTO shaft 94, is such that the PTO speed change mechanism 110 for driving the farm work portion at a vehicle speed-synchronizing speed and the PTO constant-rotation mechanism 111 for driving the farm work portion at a constant rotation speed are provided in the mission case 26; the PTO speed change mechanism 110 is disposed between the output side of the second speed change means 89 and the PTO shaft 94; and the PTO constant-rotation mechanism 111 is disposed between the input side of the first speed change means 88 and the PTO shaft 94. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a combine harvester provided with a farming unit that harvests grains by harvesting cereals planted in a field, or a feed harvester provided with a farming unit that harvests cereals and pasture for feed and collects them as feed Or a harvester such as a vegetable harvester equipped with a farming unit that takes in vegetables such as cabbage, radish and onion in the field, and more specifically, a transmission case that transmits engine output to the traveling unit or farming unit. It is related with the harvester which prepared and was made to operate | move in synchronization with a traveling part and an agricultural work part.

  Conventionally, in general, a harvesting machine provided with a farming unit maintains the engine output speed in a state where the engine output is maximized, and transmits the engine output from the mission case to the traveling unit and the farming unit, By operating the farm working unit at a speed synchronized with the vehicle speed, the farm working unit operates at a substantially constant speed on crops in the field even when the vehicle speed is changed.

In the conventional combine, as shown in Patent Document 1, a traveling hydraulic pump (first transmission means) for shifting the output of the engine and a traveling hydraulic pressure for further shifting the output of the traveling hydraulic pump are provided in the transmission case. A motor (second transmission means) and an auxiliary transmission mechanism (third transmission means) for further changing the output of the traveling hydraulic motor are arranged. Further, a cutting drive pulley (PTO shaft) is connected to the output side of the traveling hydraulic motor so that the output of the engine is transmitted from the traveling hydraulic motor to the pre-cutting device (agricultural working unit) via the cutting drive pulley. It is composed. (For example, refer to Patent Document 1).
JP 2005-261279 A

  In the prior art, as disclosed in Patent Document 1, a counter case for transmitting power from the engine to the cutting pretreatment device is attached to the front portion of the traveling machine body. In this counter case, to switch to a low speed side constant rotation operation state or a low speed side constant rotation operation state and a low speed side constant rotation operation state for switching to a low speed side vehicle speed synchronization output or a high speed side vehicle speed synchronization output. And a constant cutting mechanism (PTO constant rotation mechanism). The power from the engine is input to the mowing transmission mechanism from the vehicle speed transmission mechanism in the transmission case, while the constant rotational power from the engine is directly input to the mowing constant speed mechanism.

  Therefore, in Patent Document 1, an engine and a transmission case, and an engine and a cutting pre-processing device are compared with a driving structure in which a cutting speed change mechanism and a constant cutting speed mechanism for synchronizing vehicle speed are configured by a belt transmission mechanism having a tension clutch. The belt transmission mechanism disposed between each of the two can be easily configured. However, the counter case provided at the front of the traveling machine body incorporates a cutting speed change mechanism and a constant cutting speed mechanism for vehicle speed synchronization, thereby greatly increasing the size and weight and manufacturing cost of the traveling machine body in the combine. There is a problem of inviting up. In addition, a threshing device is mounted on the traveling machine body, and there is a problem that the large counter case present in front of the threshing device significantly hinders maintenance of the threshing device.

  An object of the present invention is to utilize a transmission case having a first speed change means, a second speed change means, and a third speed change means, to drive a farm work section at a vehicle speed synchronization speed, and to a farm work section at a constant rotational speed. The harvesting machine is configured to be able to arrange the PTO constant rotation mechanism that drives the vehicle in a compact and low-cost manner.

  In order to achieve the object, the harvesting machine of the invention according to claim 1 includes a traveling machine body having a traveling unit that is operated by an engine, an agricultural work unit disposed in the traveling machine body, and the traveling unit or the agricultural working unit. A transmission case for transmitting the output of the engine; a first transmission means for shifting the output of the engine; a second transmission means for shifting the output of the first transmission means; and a second transmission means. A third speed change means for shifting the output, a PTO shaft is connected to the output side of the second speed change means, and the output of the engine is transmitted from the second speed change means to the farm working section via the PTO shaft. In the harvesting machine configured to transmit, a PTO transmission mechanism that drives the farm work unit at a vehicle speed synchronization speed and a farm work unit that is driven at a constant rotational speed inside the mission case. A constant TO rotation mechanism is provided, the PTO transmission mechanism is disposed between the output side of the second transmission means and the PTO shaft, and the PTO is disposed between the input side of the first transmission means and the PTO shaft. A constant rotation mechanism is arranged.

  According to a second aspect of the present invention, in the harvester according to the first aspect, the high speed side output of either the speed change output of the PTO speed change mechanism or the constant speed output of the PTO constant speed rotation mechanism is supplied to the PTO shaft. It is provided with clutch means for transmitting to

  According to a third aspect of the present invention, in the harvester according to the first aspect, the PTO speed change mechanism is configured to change the output of the second speed change means so as to output the speed change, and the second speed change means. It is configured to be switchable to a PTO stop state that cuts off the output.

  According to a fourth aspect of the present invention, in the harvester according to the first aspect, the PTO constant rotation mechanism includes a low-speed constant rotation operation state that maintains a minimum number of rotations necessary for driving the farm work unit, and the farm work. Switchable between a high-speed-side constant rotational operation state that maintains the maximum rotational speed necessary for driving the part and a PTO stop state that cuts off the output of the second transmission means.

  According to the first aspect of the present invention, a traveling machine body including a traveling unit that is operated by an engine, an agricultural work unit disposed on the traveling machine body, and a transmission case that transmits the output of the engine to the traveling unit or the agricultural work unit. First transmission means for changing the output of the engine, second transmission means for changing the output of the first transmission means, and third transmission means for changing the output of the second transmission means. And a PTO shaft is connected to the output side of the second transmission means, and the output of the engine is transmitted from the second transmission means to the farm working unit via the PTO shaft. In the harvesting machine, a PTO transmission mechanism that drives the farm working unit at a vehicle speed synchronization speed and a PTO constant rotation mechanism that drives the farm working unit at a constant rotational speed are provided inside the mission case. Wherein between the PTO shaft and the output side of the second gear unit arranged PTO transmission mechanism, placing the PTO constant rotational mechanism between the input side and the PTO shaft of the first gear means. Therefore, the engine, the transmission case, and the engine and the farm working unit are compared with the conventional drive structure in which the PTO transmission mechanism and the PTO constant rotation mechanism are configured using a belt transmission mechanism having a tension clutch. The belt transmission mechanism disposed between each of the two can be easily configured. The maintenance workability of the belt transmission mechanism can be improved. Further, the PTO transmission mechanism and the PTO constant rotation mechanism can be made compact and low-cost using the transmission case having the first transmission means, the second transmission means, and the third transmission means. Can be placed. By incorporating the PTO speed change mechanism and the PTO constant rotation mechanism in the transmission case, it is possible to omit providing a counter case at the front portion of the traveling machine body as in the prior art, or provisionally providing the counter case. In any case, the counter case can be miniaturized.

  According to the second aspect of the present invention, the clutch means for transmitting either the speed change output of the PTO transmission mechanism or the constant rotation output of the PTO constant rotation mechanism to the PTO shaft is provided. Therefore, it is possible to prevent both the shift output for vehicle speed synchronization of the PTO transmission mechanism and the constant rotation output of the PTO constant rotation mechanism from being simultaneously transmitted to the farm working unit. Further, it is possible to prevent the PTO shaft from reversing due to the reverse travel of the traveling machine body.

  According to a third aspect of the present invention, the PTO speed change mechanism is divided into a PTO operating state in which the output of the second speed change means is changed to output a speed change, and a PTO stop state in which the output of the second speed change means is cut off. Since it is configured to be switchable, a conventional belt tension clutch for driving or stopping the farm working unit is not necessary. Further, it is not necessary to provide a clutch for driving or stopping the farm working unit on the counter case or the like. A clutch for driving or stopping the farm working unit can be configured at low cost and in a compact manner.

  According to the invention which concerns on Claim 4, the said PTO constant rotation mechanism is the low speed side constant rotation operation state holding the minimum rotation speed required for the drive of the said farm work part, and the maximum rotation speed required for the drive of the said farm work part. Can be switched between a high speed side constant rotation operation state that holds the output and a PTO stop state that cuts off the output of the second transmission means, so that the low speed side constant rotation output from the PTO constant rotation mechanism, or The farm working unit can be operated by a high-speed constant rotation output or a shift output for synchronizing the vehicle speed of the PTO transmission mechanism. The machine vibration or damage of the farm working unit can be reduced, and the work performance of the farm working unit can be properly maintained.

  DESCRIPTION OF EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings. 1 is a left side view of a combine, FIG. 2 is a plan view of the combine, FIG. 3 is a drive system diagram of the combine, FIG. 4 is a drive system diagram of the transmission case, FIG. 5 is a hydraulic circuit diagram, and FIG. 7 is a functional block diagram of the control circuit, FIG. 7 is a flowchart of the cutting speed control, and FIG. 8 is a diagram showing the relationship between the vehicle speed and the cutting speed. The overall structure of the combine will be described with reference to FIGS. 1 and 2. In the following description, the left side in the traveling direction of the traveling machine body 1 is simply referred to as the left side, and the right side in the traveling direction is also simply referred to as the right side.

  The combine according to the present embodiment includes a traveling machine body 1 supported by a pair of left and right traveling crawlers 2 as traveling portions. At the front part of the traveling machine body 1, a four-line mowing pre-treatment device 3 as a farming part that takes in while harvesting cereals is raised and lowered around a cutting pivot point 4a by a single-acting lifting hydraulic cylinder 4. It is mounted adjustable. A threshing device 5 having a feed chain 6 and a grain tank 7 for storing grains taken out from the threshing device 5 are mounted on the traveling machine body 1 side by side. In this embodiment, the threshing device 5 is disposed on the left side in the traveling direction of the traveling machine body 1, and the grain tank 7 is disposed on the right side in the traveling direction of the traveling machine body 1. A swivelable discharge auger 8 is provided at the rear part of the traveling machine body 1, and the grains inside the grain tank 7 are discharged from the throat throw 9 of the discharge auger 8 to a truck bed or a container. ing. An operation unit 10 is provided on the right side of the pre-cutting processing device 3 and on the front side of the grain tank 7.

  A steering handle 11 and a driver seat 12 are arranged in the driver 10. The steering handle 11 is provided on a handle column 13 disposed in front of the driver seat 12. In addition, a main speed change lever 14, a sub speed change lever 15, a threshing clutch lever 16, and a mowing clutch lever 17 are arranged in the operating unit 10. The levers 14, 15, 16, 17 and the like are provided on a lever column 18 disposed on the left side of the driver seat 12. An engine 20 as a power source is disposed in the traveling machine body 1 below the driver seat 12.

  As shown in FIG. 1, left and right track frames 21 are arranged on the lower surface side of the traveling machine body 1. The track frame 21 includes a drive sprocket 22 that transmits the power of the engine 20 to the traveling crawler 2, a tension roller 23 that maintains the tension of the traveling crawler 2, and a plurality of track rollers that hold the ground side of the traveling crawler 2 in a grounded state. 24 and an intermediate roller 25 that holds the non-grounded side of the traveling crawler 2 are provided. The drive sprocket 22 is disposed on a mission case 26 provided on the front end side of the track frame 21 via an axle 27 (see FIG. 3). The driving sprocket 22 supports the front side of the traveling crawler 2, the tension roller 23 supports the rear side of the traveling crawler 2, the track roller 24 supports the grounding side of the traveling crawler 2, and the intermediate roller 25 supports the non-traveling crawler 2. The ground side will be supported.

  Next, the structure of the pre-cutting processing device 3 will be described with reference to FIGS. 1 and 2. As shown in FIGS. 1 and 2, below the cutting frame 29 connected to the cutting rotation fulcrum shaft 4a, a clipper type cutting blade that cuts the stock of uncut grain culm (crop) planted in the field. A device 30 is provided. In front of the cutting frame 29, a grain culling pulling device 31 for four ridges that raises an uncut grain culm planted in a field is arranged. Between the grain raising apparatus 31 and the front end (feed start side) of the feed chain 6, a grain feeder 32 for conveying the harvested grain produced by the cutting blade device 30 is arranged. In addition, in front of the lower part of the cereal habit raising device 31, a four-row weed body 33 for weeding uncut cereals planted in a farm is protruded. While the traveling crawler 2 is driven by the engine 20 and moved in the field, the uncut grain culms planted in the field are continuously cut by the pre-cutting processing device 3.

  Next, the harvesting drive structure for the combine will be described with reference to FIG. As shown in FIG. 3, the grain raising device 31 has a four-case raising case 35 having a plurality of raising tines 34 that erect uncut wheat grains that have been weeded by the weed body 33. The grain feeder 32 includes left and right right star wheels 36R and left and right right take-up belts 37R that squeeze the stock side of the two right-side grains introduced from the right-side two-stage pulling case 35, and the left side. It has left and right left star wheels 36L and left and right left rake belts 37L that rake up the stock side of the left cereal grain cereals introduced from the two pulling cases 35. The cutting blade device 30 is a clipper type that cuts the stock of four rows of cereals scraped by the right star foil 36R and the left and right right take-up belts 37R, the left star wheel 36L and the left and right left take-up belts 37L. Left and right cutting blades 38.

  Further, the cereal haul conveying device 32 is configured to transfer the right stocker of the right two reaped harvested rice straws by the right side two pieces of the star foil 36R and the rake belt 37R to the rear, the right stock former carrying chain 39R. And the left stock transport that joins the stock side of the two left-handed harvested cereals that have been scraped by the star foil 36L and the scraping belt 37L on the left-hand side to the transport end portion of the right stock transport chain 33R. Chain 39L. The stock base sides of the four reaped grain straws transported by the left and right stock transport chains 39R and 39L are joined to the transport end portion of the right stock transport chain 39R.

  The corn straw transporting device 32 includes a vertical transport chain 40 that inherits the stock side of the harvested cereals for four ridges from the right stock transport chain 39R, and a transport start end of the feed chain 6 from the transport terminal end of the vertical transport chain 40. And an auxiliary stock former transport chain 41 for transporting the stock side of the harvested cereal meals for four lines. From the vertical conveyance chain 40, the stock side of the four sown cereal grains is conveyed to the conveyance start end of the feed chain 6 through the auxiliary stock element conveyance chain 41.

  The grain culm transporting device 32 is transported by the right stalk transporting tine 42R that transports the head of the harvested stalks for the two right-hand ridges that are transported by the right cultivating transport chain 39R, and the left cultivating transport 39L. It has a left tip transporting tine 42L that transports the tip side of the harvested cereal rice cake for the two left-hand sides. In the handling room of the threshing device 5, the tip side of the harvested cereal rice bran for 4 strips will be conveyed.

  As shown in FIG. 3, a cutting input shaft 45 disposed on the cutting rotation fulcrum shaft 4 a described above is provided. The pulling horizontal transmission shaft 49 is connected to the cutting input shaft 45 through the vertical transmission shaft 46, the horizontal transmission shaft 47, and the pulling transmission mechanism 49. The pulling lateral transmission shaft 48 is connected to the pulling tine drive shaft 50 of each pulling case 35 for four lines. A pulling case 35 is erected on the rear side of the weed body 33 and above the cutting frame 29, and the pulling tine drive shaft 50 protrudes from the rear surface on the upper end side of the pulling case 35. The pulling tine chain 34 a provided with a plurality of pulling tines 34 is driven via the pulling tine drive shaft 50 and the pulling lateral transmission shaft 49.

  As shown in FIG. 3, the left and right cutting blades 38 are connected to the lateral transmission shaft 47 via the left and right crankshafts 52a and 52b. The left and right cutting blades 38 are configured to be driven synchronously via the lateral transmission shaft 47. The cutting blade device 30 is divided at the central portion of the cutting width for four lines to form left and right cutting blades 38, and the left and right cutting blades 38 are reciprocated in opposite directions, and left and right generated by the reciprocating movement. The vibration (inertial force) of the cutting blade 38 can be offset.

  As shown in FIG. 3, the rotational force of the cutting input shaft 45 is transmitted to each drive unit of the grain feeder 32 via a longitudinal transmission shaft 46 and a lateral transmission shaft 47. In other words, the rear conveyance drive shaft 54 is connected to the cutting input shaft 45, and the auxiliary stock former conveyance chain 41 and the right tip conveyance tine 42R are driven via the rear conveyance drive shaft 54. The right transfer drive shaft 55 is connected to the vertical transmission shaft 46, and the right stock former transfer chain 39R and the right tip transfer tine 42R, the right star wheel 36R, and the right take-up belt 37R are driven via the right transfer drive shaft 55. It is configured to do.

  Further, the vertical conveyance transmission shaft 56 is connected to the right conveyance drive shaft 55, and the vertical conveyance chain 40 is driven via the vertical conveyance transmission shaft 56. A left conveying drive shaft 57 provided with a pulling transmission mechanism 48 is connected to the left end side of the lateral transmission shaft 41. The left stock former transfer chain 39L and the left tip transfer tine 42L, the left star wheel 36L and the left take-up belt 37L are driven via the left transfer drive shaft 57.

  Next, with reference to FIG.1 and FIG.2, the structure of the threshing apparatus 5 is demonstrated. As shown in FIG. 1 and FIG. 2, the threshing device 5 includes a handling cylinder 60 for threshing threshing, a rocking sorter 61 that sorts shed matter falling below the handling cylinder 60, and a tang fan 62. A processing cylinder 63 that reprocesses the threshing waste taken out from the rear part of the handling cylinder 60 and a dust exhaust fan 71 that discharges dust at the rear part of the swing sorter 61 are provided. In addition, the rotating shaft core line of the handling cylinder 60 is extended along the conveyance direction (in other words, the advancing direction of the traveling body 1) of the cereal by the feed chain 6. The stockholder side of the cereals conveyed by the cereal conveyance device is inherited by the feed chain 6 and is nipped and conveyed. Then, the tip side of this cereal is carried into the handling chamber of the threshing device 5 and threshed by the handling drum 60.

  Below the swing sorter 61, the first conveyor 64 for picking up the grain (the first thing) sorted by the swing sorter 61 and the second for taking out the second thing such as a grain with a branch raft. A conveyor 65 is provided. The two conveyors 64 and 65 of this embodiment are arranged in the order of the first conveyor 64 and the second conveyor 65 from the front side in the traveling direction of the traveling machine body 1 to the upper surface side of the traveling machine body 1 above the rear part of the traveling crawler 2 in a side view. It is installed.

  The oscillating sorter 61 is configured such that threshing that has leaked from a receiving net (not shown) stretched below the handling cylinder 60 is peristally sorted (specific gravity selected) by a feed pan and a chaff sheave (not shown). ing. Grains that fall from the swing sorter 61 are removed by the sorting air from the tang fan 62 and fall to the conveyor 64 first. A cereal conveyor 66 extending in the vertical direction is connected to a terminal portion of the first conveyor 64 that protrudes outward from one side wall (right side wall in the embodiment) of the threshing device 5 that is close to the grain tank 7. . The grain taken out first from the conveyor 64 is carried into the grain tank 7 via the cereal conveyor 66 and collected in the grain tank 7.

  Further, the swing sorter 61 is configured to drop a second thing such as a grain with a branch stem on the second conveyor 65 by peristaltic sorting (specific gravity sorting) from the chaff sheave. The second item dropped from the chaff sheave falls on the second conveyor 65. Of the second conveyor 65, a terminal portion protruding outward from one side wall near the grain tank 7 in the threshing device 5 intersects with the whipping conveyor 66 and extends in the front-rear direction, and a reprocessing portion at the tip. 68 is connected to the upper surface side of the front portion (feed pan) of the rocking sorter 61, and the second item is returned to the upper surface side of the feed pan and re-sorted.

  On the other hand, a waste chain 69 is disposed on the rear end side (feed end side) of the feed chain 6. The waste passed through the feed chain 6 from the rear end side of the feed chain 6 (the grain from which the grain has been threshed) is discharged to the rear of the traveling machine body 1 in a long state, or the rear side of the threshing device 5 After being cut to a suitable length by the waste cutter 70 provided at the front, the paper is discharged to the lower rear of the traveling machine body 1.

  Next, the drive structure of the mission case 26 and the drive structures of the threshing device 5, the feed chain 6, the waste chain 69, the waste cutter 70, etc. will be described with reference to FIG. As shown in FIG. 3, the output shaft 75 of the engine 20 is connected to the input shaft 78 of the transmission case 26 via a travel transmission belt 76 and a belt tension clutch 77. The rotational driving force of the engine 20 is transmitted from the output shaft 75 to the transmission case 26 and shifted, and then transmitted to the left and right traveling crawlers 2 via the left and right axles 27, so that the left and right traveling crawlers 2 rotate the engine 20. It is configured to be driven by force. In addition, a discharge auger drive shaft 79 is connected to the output shaft 75, and the discharge auger 8 is driven via the discharge auger drive shaft 79 by the rotational driving force from the engine 21, and the grains in the grain tank 7 are transferred to a container or the like. It is configured to be discharged.

  Moreover, the threshing drive shaft 80 which transmits the rotational drive force from the engine 20 to the handling cylinder 60 and the process cylinder 63 is provided. A threshing drive shaft 80 is connected to an output shaft 75 of the engine 20 via a threshing drive belt 81 and a threshing belt tension clutch 82. The threshing drive shaft 80 is connected to a handling cylinder shaft 83 that supports the handling cylinder 60 and a processing cylinder shaft 84 that supports the processing cylinder 63. The handling cylinder 60 and the processing cylinder 63 are configured to rotate at a substantially constant rotational speed by the rotational force of the engine 20 at a substantially constant rotational speed. A sorting input belt 85 is connected to the threshing drive shaft 80. The feed chain 6, the swing sorter 61, the Kara fan 62, the first conveyor 64, the second conveyor 65, the dust exhaust fan 71, the exhaust fan, via the sorting input belt 85 by the rotational force of the engine 20 at a substantially constant rotational speed. The cocoon cutter 70 is configured to rotate at a substantially constant rotational speed.

  Next, the drive structure of the mission case 26 and the like will be described with reference to FIGS. As shown in FIGS. 3 and 4, the mission case 26 includes a linear hydraulic stepless transmission mechanism 90 having a pair of linear hydraulic pumps 88 and a linear hydraulic motor 89, and a pair of swing hydraulic pumps. 91 and a turning hydraulic continuously variable transmission mechanism 93 having a turning hydraulic motor 92. A straight traveling hydraulic pump 88 and a turning hydraulic pump 91 are connected to an input shaft 78 of the mission case 26 to drive the pumps 88 and 91, respectively. Further, a cutting drive PTO shaft 94 is disposed horizontally and horizontally inside the mission case 26. The reaping drive PTO shaft 94 is driven by a straight advance hydraulic motor 89. One end side of the cutting drive PTO shaft 94 projects from the transmission case 26 to the left outer side. A cutting drive PTO shaft 94 is connected to the cutting input shaft 45 via a cutting drive belt 95.

  As shown in FIG. 4, in the transmission case 26, parallel to the input shaft 78, a straight traveling hydraulic pump shaft 96, a straight traveling hydraulic motor shaft 97, a cutting drive PTO shaft 94, a counter shaft 98, and a straight travel A variable speed output shaft 99 is arranged. A linear hydraulic pump shaft 96 is connected to the input shaft 78 via the input gear 100. The straight hydraulic pump 88 is driven by the straight hydraulic pump shaft 96, the straight hydraulic motor shaft 97 is driven by the straight hydraulic motor 89, and the rotation output of the straight hydraulic pump shaft 96 is stepless by the straight hydraulic pump 88. The speed is shifted in two stages (high speed and low speed) by the straight traveling hydraulic motor shaft 97 and transmitted to the straight traveling hydraulic motor shaft 97.

  As shown in FIG. 4, a countershaft 98 is connected to a straight hydraulic motor shaft 97 via a counter gear 101. A sub-transmission gear mechanism 102 is provided that connects the straight-shift transmission output shaft 99 to the counter shaft 98. The auxiliary transmission gear mechanism 102 includes an auxiliary transmission low speed gear 103, an auxiliary transmission high speed gear 104, and an auxiliary transmission shifter 105. By operating the auxiliary transmission lever 15, the auxiliary transmission shifter is moved to a neutral position (a position where the output is zero), a low-speed output position that is engaged with the auxiliary transmission low-speed gear 103, or a high-speed output position that is engaged with the auxiliary transmission high-speed gear 104. The sub-transmission gear mechanism 102 is configured to be switched to a shift mode of neutral or low-speed output or high-speed output with zero output. In other words, the linear shift output shaft 99 stops when the sub-shift shifter 105 is in the neutral position, and the linear shift output shaft 99 operates at a low speed (working speed) when the sub-shift shifter 105 is in the low-speed output position. When the auxiliary shift shifter 105 is at the high-speed output position, the straight-shift transmission output shaft 99 is configured to operate at a high speed (road travel speed).

  In addition, the rotational output of the straight traveling speed change output shaft 99 is transmitted to the left and right traveling crawlers 2 via the straight traveling speed change output gear 106, and the left and right traveling crawlers 2 are driven by the rotational output of the straight traveling speed change output shaft 99. The traveling machine body 1 is configured to move in the forward direction or the reverse direction. A linear brake output shaft 99 includes a parking brake 107 that brakes the left and right traveling crawlers 2, and a vehicle speed sensor 108 that detects the driving speed of the left and right traveling crawlers 2 (the moving speed of the traveling machine body 1 and the vehicle speed). Is arranged.

  That is, as shown in FIG. 4, a linear hydraulic pump 88 as a first transmission means for shifting the output of the engine, a linear hydraulic motor 89 as a second transmission means for shifting the output of the linear hydraulic pump 88, An auxiliary transmission gear mechanism 102 as third transmission means for changing the output of the linear hydraulic motor 89 is disposed in the mission case 26. Further, in the transmission case 26, the PTO transmission mechanism 110 that connects the reaping drive PTO shaft 94 to the linear hydraulic motor shaft 97 on the output side of the linear hydraulic motor 89, and the linear actuator on the input side of the linear hydraulic pump 88. A PTO constant rotation mechanism 111 that connects the cutting drive PTO shaft 94 to the hydraulic pump shaft 96 is provided.

  In other words, the output of the engine 20 is transmitted from the output side of the straight traveling hydraulic motor 89 to the pre-cutting processing device 3 (agricultural work unit) via the PTO transmission mechanism 110 and the cutting drive PTO shaft 94, and the PTO transmission mechanism 110. The cutting input shaft 45 is rotationally driven by the output of the vehicle speed synchronization speed. Further, the output of the engine 20 is transmitted to the pre-cutting processing device 3 from the input side of the straight hydraulic pump 88 via the PTO constant rotation mechanism 111 and the cutting drive PTO shaft 94, so The cutting input shaft 45 is driven to rotate by the output of the rotational speed.

  As shown in FIG. 4, the PTO transmission mechanism 110 includes a PTO low speed gear 112, a PTO high speed gear 113, and a PTO transmission shifter 114. By the switching control of the PTO speed change hydraulic cylinder 115, the PTO speed change shifter is set to the neutral position (position where the output is zero), the low speed output position locked to the PTO low speed gear 112, or the high speed output position locked to the PTO high speed gear 113. 114 is configured to move. In other words, the PTO speed change mechanism 110 can be switched between a PTO operation state in which the output of the straight-ahead hydraulic motor 89 is shifted and shifted and a PTO stop state (PTO clutch disengagement) in which the output of the straight-ahead hydraulic motor 89 is disconnected. It is configured.

  That is, the PTO speed change mechanism 110 is configured to be switched to a shift mode of neutral, low speed, or high speed output by switching control of the PTO speed change hydraulic cylinder 115. In other words, when output from the straight-travel hydraulic motor 89, the cutting drive PTO shaft 94 stops when the PTO shift shifter 114 is in the neutral position, and the cutting drive PTO shaft 94 when the PTO shift shifter 114 is in the low speed output position. Is operated at a low speed, and the cutting drive PTO shaft 94 is configured to operate at a high speed when the PTO shift shifter 114 is at the high-speed output position.

  Further, the PTO shift shifter 114 is pivotally supported by a reaping drive PTO shaft 94 via a one-way rotation clutch 116 for PTO shift. That is, of the rotations in the straight traveling hydraulic motor shaft 97, the rotation in the direction in which the traveling machine body 1 moves forward is transmitted to the cutting drive PTO shaft 94 via the one-way rotation clutch 116, but in the straight traveling hydraulic motor shaft 97. Of the rotations, the rotation in the direction in which the traveling machine body 1 moves backward is not transmitted to the reaping drive PTO shaft 94. In addition, the rotation is not transmitted via the PTO transmission mechanism 110 in the direction from the reaping drive PTO shaft 94 to the linear hydraulic motor shaft 97.

  On the other hand, the PTO constant rotation mechanism 111 includes a low speed side constant rotation gear 117, a high speed side constant rotation gear 118, and a constant rotation shifter 119. By switching control of the PTO constant rotation hydraulic cylinder 120, the neutral position (position where the output is zero), the low speed side constant rotation position locked to the low speed side constant rotation gear 117, or the high speed locked to the high speed side constant rotation gear 118. The constant rotation shifter 119 is configured to move to the side constant rotation position. In other words, the PTO constant rotation mechanism 111 holds the low-speed constant rotation operation state that maintains the minimum rotation speed necessary for driving the pre-cutting processing device 3 and the maximum rotation speed necessary for driving the pre-cutting processing device 3. The high speed side constant rotation operation state and the PTO stop (PTO clutch disengagement) state in which the output of the straight traveling hydraulic motor shaft 97 is cut off can be switched.

  That is, by the switching control of the PTO constant rotation hydraulic cylinder 120, the output is neutral, zero output, constant rotation output at low speed side (low speed cut mode), or constant rotation output mode at high speed side (high speed cut mode). Further, the PTO constant rotation mechanism 111 is configured to be switched. In other words, when the straight traveling hydraulic pump shaft 96 is driven, the reaping drive PTO shaft 94 stops when the constant rotation shifter 119 is in the neutral position, and when the constant rotation shifter 119 is at the low speed side constant rotation output position. The drive PTO shaft 94 operates at a low speed side constant rotation speed (pour speed), and the mowing drive PTO shaft 94 operates at a high speed side constant rotation speed (high speed cut speed) when the constant rotation shifter 119 is at a high speed side constant rotation output position. It is configured to do.

  Therefore, the rotation output at a constant rotational speed necessary for maintaining the cutting operation is transmitted to the cutting drive PTO shaft 94 via the low-speed constant rotation gear 117. Regardless of the traveling speed of the traveling machine body 1, the cutting input shaft 45 can be operated at a constant rotational speed from the low-speed constant rotating gear 117 to maintain the cutting operation, and the direction changing workability at the headland in the field can be improved. . Further, a rotational output at a constant rotational speed that is faster than the maximum speed of the vehicle speed synchronization output from the PTO transmission mechanism 110 is transmitted to the cutting drive PTO shaft 94 via the high-speed constant rotational gear 118. Therefore, the cutting input shaft 45 can be operated at a constant rotational speed from the high-speed side constant rotating gear 118 that is faster than the maximum speed of the vehicle speed synchronization output, and the efficiency of cutting the fallen cedar can be improved.

  The constant rotation shifter 119 is pivotally supported by the cutting drive PTO shaft 94 via a one-way rotation clutch 121 for constant rotation. The rotation of the rectilinear hydraulic pump shaft 96 is transmitted to the cutting drive PTO shaft 94 via the one-way rotation clutch 121. That is, rotation is transmitted to the direction from the straight hydraulic pump shaft 96 to the cutting drive PTO shaft 94 via the PTO constant rotation mechanism 111, but the direction from the cutting drive PTO shaft 94 to the straight hydraulic pump shaft 96 is transmitted. In the configuration, the rotation is not transmitted via the PTO constant rotation mechanism 111.

  As a result, the rotational output of the PTO transmission mechanism 110 transmitted through the PTO transmission shifter 114 and the PTO transmission one-way rotation clutch 116, or the transmission through the constant rotation shifter 119 and the one-way rotation clutch 121 for constant rotation. The cutting input shaft 45 is driven via the cutting drive PTO shaft 94 by the rotation output on the high speed side among the rotation outputs of the PTO constant rotation mechanism 111 to be operated, and the pre-cutting processing device 3 operates. That is, either the low-speed constant rotational output of the PTO constant rotational mechanism 111, the rotational output of the vehicle speed synchronization speed of the PTO speed change mechanism 110, or the high-speed constant rotational output of the PTO constant rotational mechanism 111 is used for the cutting drive PTO shaft 94. The cutting input shaft 45 is driven via Therefore, the rotation output of the vehicle speed synchronization speed of the PTO transmission mechanism 110 and the constant rotation output of the PTO constant rotation mechanism 111 are not transmitted to the reaping drive PTO shaft 94 at the same time. Further, the rotational output of the backward movement of the traveling machine body 1 is not transmitted to the cutting drive PTO shaft 94.

  Next, referring to FIG. 5, the structures of the straight-traveling hydraulic continuously variable transmission mechanism 90 and the turning hydraulic continuously variable transmission mechanism 93 will be described. As shown in FIG. 5, the charge pump 125 is connected to the pump shaft of the turning hydraulic pump 91. The rectilinear hydraulic pump 88 and the rectilinear hydraulic motor 89 are hydraulically connected by a closed hydraulic circuit, and the charge hydraulic pressure of the charge pump 125 is supplied to the closed hydraulic circuit. Similarly, the swing hydraulic pump 91 and the swing hydraulic motor 92 are hydraulically connected by a closed hydraulic circuit, and the charge hydraulic pressure of the charge pump 125 is supplied to the closed hydraulic circuit. The rotational driving force of the engine 20 transmitted to the input shaft 78 of the mission case 26 is transmitted to the left and right axles 27 after being shifted by the straight traveling hydraulic continuously variable transmission mechanism 90 or the turning hydraulic continuously variable transmission mechanism 93. The left and right traveling crawlers 2 are configured to be driven via the left and right axles 27, respectively.

  As shown in FIG. 5, a main transmission cylinder 126 that adjusts the output by changing the inclination angle of the swash plate 88a of the straight hydraulic pump 88, and a main transmission valve 127 that is connected to the main transmission lever 14 and the steering handle 11 for switching. And a deceleration valve 128 that decelerates the output of the straight hydraulic pump 88 by a certain amount, and the charge pump 125 is hydraulically connected to the main transmission cylinder 126 via the main transmission valve 127 or the reduction valve 128. As a result, the main transmission valve 127 is switched by the main transmission lever 14 and the main transmission cylinder 126 is operated to change the angle of the swash plate 88a of the linear hydraulic pump 88, thereby rotating the motor shaft 97 of the linear hydraulic motor 89. The number is continuously changed in the forward direction or the backward direction.

  Further, a sub-transmission cylinder 129 that adjusts the output by changing the angle of the swash plate 89a of the straight traveling hydraulic motor 89, and an electromagnetic sub-transmission valve 130 having a hydraulic sub-transmission high-speed solenoid 130a and a hydraulic sub-transmission low-speed solenoid 130b are provided. Yes. An auxiliary transmission cylinder 129 is hydraulically connected to the charge pump 125 through an electromagnetic auxiliary transmission valve 130. When the sub-transmission valve 130 is in the neutral switching position, the sub-transmission cylinder 129 is short-circuited to the transmission case 26 that is an oil tank, and the swash plate 89a of the linear hydraulic motor 89 is hydraulically connected to the hydraulic pump 88 (closed circuit hydraulic pressure). ) To maintain the maximum tilt position.

  On the other hand, when the sub-transmission valve 130 is switched to a switching position other than the neutral position, the hydraulic pressure of the charge pump 125 is applied to the sub-transmission cylinder 129 via the sub-transmission valve 130, and the hydraulic pressure (closed circuit) of the straight traveling hydraulic pump 88 is applied. Regardless of the hydraulic pressure), the angle of the swash plate 89a of the straight traveling hydraulic motor 89 is forcibly changed by the auxiliary transmission cylinder 129, and the rotational speed of the straight traveling hydraulic motor shaft 97 is changed to the high speed side or the low speed side. . That is, an operation for changing the angle of the swash plate 89a of the straight-travel hydraulic motor 89, in other words, a sub-shift operation for switching the sub-shift valve 130, switches the output rotational speed of the straight-travel hydraulic motor 89 to the high speed side or the low speed side. It is configured.

  Further, a turning cylinder 131 for adjusting the output by changing the angle of the swash plate 91a of the turning hydraulic pump 91 is provided, and a turning valve 132 that is switched by the steering handle 11 or the main shift lever 14 or an electromagnetic automatic steering valve 133 is provided. The charge pump 125 is hydraulically connected to the swivel cylinder 131. By switching the turning valve 132 by the steering handle 11, the turning cylinder 131 is operated, and the angle of the swash plate 91a of the turning hydraulic pump 91 is changed steplessly. As a result, the output rotation speed of the turning hydraulic motor 91 changes steplessly by the operation of the steering handle 11, or the output rotation of the turning hydraulic motor 91 is reversed. In other words, the angle of the swash plate 91a changes in proportion to the amount of left and right rotational operation (steering angle) of the steering handle 11, and the output rotational speed of the turning hydraulic motor 91 changes or reverses, so that the traveling machine body 1 The path (left and right turning angle) is changed leftward or rightward.

  When the steering handle 11 is operated to a steering angle position other than straight travel while the main speed change lever 14 is operated to a speed change position other than neutral, the operation direction (forward, reverse) and operation of the main speed change lever 14 are operated. In proportion to the amount (acceleration / deceleration), the angle (output hydraulic pressure) of the swash plate 88a of the straight hydraulic pump 88 increases / decreases or reverses, and the hydraulic motor 89 is increased / decreased, rotated forward / reversely. The forward speed or the reverse speed (the straight movement speed and the traveling direction) is changed. Further, the output hydraulic pressure of the turning hydraulic pump 91 changes (increases / decreases) in proportion to the operation amount of the main transmission lever 14, and the turning radius is automatically set by the high-speed traveling shift of the main transmission lever 14. The turning radius is automatically increased by the low-speed traveling shift of the main transmission lever 14. Therefore, if the main shift lever 14 is operated to a shift position other than neutral while the steering handle 11 is held at a constant steering angle position other than straight travel, the shift operation position (straight travel speed) of the main shift lever 14 ) Regardless of), the turning radius of the left and right traveling crawler 2 is maintained substantially constant so that the traveling speed (working vehicle speed) of the traveling machine body 1 can be changed, or the machine body is moved along an uncut grain row, etc. The course of Aircraft 1 can be corrected.

  On the other hand, in accordance with the operation amount (steering angle) of the steering handle 11, the output of the straight hydraulic pump 88 is changed by the control of the main speed change valve 27, and the output of the swing hydraulic pump 91 is controlled by the control of the swing valve 132. It is configured to change. That is, when the steering angle of the steering handle 11 is increased and the turning radius of the traveling machine body 1 is reduced, the moving speed (vehicle speed) of the traveling machine body 1 is reduced in proportion to the turning radius (steering angle). Thus, the speed difference between the left and right traveling crawlers 2 can be increased and the traveling machine body 1 can be turned left and right. In a harvesting operation in which cereals are continuously harvested and threshed, the driving speed of the left and right traveling crawlers 2 can be changed to change the course such as alignment and to change the direction such as spin turn on the field headland. When the main transmission lever 14 is neutral, the swing valve 132 is maintained neutral regardless of the operation of the steering handle 11, the hydraulic output of the swing hydraulic pump 91 is maintained at substantially zero, and the swing hydraulic motor 92 is turned on. It is configured to keep stopped.

  As shown in FIG. 5, there are provided an electromagnetic cutting speed change valve 134 having a cutting speed high speed solenoid 134a and a cutting speed low speed solenoid 134b, and an electromagnetic constant rotation valve 135 having a high speed side constant speed solenoid 135a and a low speed side constant speed solenoid 135b. Yes. A PTO speed change hydraulic cylinder 115 is hydraulically connected to the charge pump 125 described above via an electromagnetic mowing speed change valve 134. The PTO shift hydraulic cylinder 115 is operated by switching the electromagnetic mowing shift valve 134. In addition, a PTO constant rotation hydraulic cylinder 120 is hydraulically connected to the charge pump 125 described above via an electromagnetic constant rotation valve 135. The PTO constant rotation hydraulic cylinder 120 is operated by switching the electromagnetic constant rotation valve 135.

  The PTO speed change hydraulic cylinder 115 and the PTO constant rotation hydraulic cylinder 120 are formed by a three-position cylinder. When the three-position four-port valves 134 and 135 are switched, the pistons of the cylinders 115 and 120 are held in the advanced position or the retracted position by the hydraulic pressure from the charge pump 125. Further, when the valves 134 and 135 are maintained neutral, the pistons of the cylinders 115 and 120 are held at an intermediate position between the advanced position and the retracted position.

  Next, the cutting speed control of this embodiment will be described. FIG. 6 is a functional block diagram of the cutting speed control means, which includes a cutting operation controller 140 such as a microcomputer having a ROM storing a control program and a RAM storing various data. As shown in FIG. 6, on the input side of a mowing operation controller 140 configured by a microcomputer, a work switch 141 that detects the driving of the threshing device 5 and the like and the cereal of the cereal wakening device 31 (uncut reashed稈) or a culm sensor 142 for detecting the culm (harvested cereal) of the culm transporting device 32, a reaping rotation sensor 143 for detecting the rotational speed of the reaping input shaft 45, the vehicle speed sensor 108 described above, and the hydraulic auxiliary A hydraulic sub-shift switch 144 that switches one of the shift high-speed solenoid 130a and the hydraulic sub-shift low-speed solenoid 130b or switches both of them off to switch the electromagnetic sub-shift valve 130, and a cutting shift high-speed solenoid 134a or a cutting shift low-speed solenoid. Cutting which switches electromagnetic cutting gear shift valve 134 by turning on either one of both 134b or turning off both of them A shift switch 145, a constant rotation switch 146 for switching either the high-speed constant-speed solenoid 135a or the low-speed-side constant-speed solenoid 135b to turn on or both of them to switch the electromagnetic constant-rotation valve 135, and a high-speed constant speed A high speed side constant speed setter 147 that sets the vehicle speed value at which the solenoid 135a operates is connected to a low speed side constant speed setter 148 that sets the vehicle speed value at which the low speed side constant speed solenoid 135b operates.

  As shown in FIG. 6, on the output side of the mowing operation controller 140, the hydraulic sub-speed high speed solenoid 130a and the hydraulic sub-speed low speed solenoid 130b, the mowing speed change high speed solenoid 134a and the mowing speed change low speed solenoid 134b, and the high speed side constant speed are provided. The solenoid 135a and the low speed side constant speed solenoid 135b are connected. That is, the solenoids 130a, 130b, 134a, 134b, 135a, 135b are excited by manual operation of the switches 144, 145, 146 described above, while the detected value of the vehicle speed sensor 108 and the settings of the setting devices 147, 148 are set. The solenoids 135a and 135b are automatically excited based on the values.

  Next, FIG. 7 is a flowchart of the conveyance speed control. With reference to FIG. 7, the cutting operation of the cereals planted in the field will be described. When the work switch 141 is on (S1yes) and the culm sensor 142 is on (S2yes), it is determined that the culm is being harvested and the detected value of the vehicle speed sensor 108 is The detection value of the cutting re-rotation sensor 143 is read (S3), and the setting value of the high speed side constant speed setting device 147 and the setting value of the low speed side constant speed setting device 148 are read (S4). The cutting speed is calculated from the detection value of the vehicle speed sensor 108, the detection value of the cutting rerotation sensor 143, the setting value of the high speed side constant speed setting device 147, and the setting value of the low speed side constant speed setting device 148 (S5). ).

  Further, during the cutting operation for cutting the grain culm planted in the field, the hydraulic sub-shifting high-speed solenoid 130a is excited by the operation of the hydraulic sub-shifting switch 144, and the electromagnetic sub-shifting valve 130 is switched to the high-speed side, so When the 89 is operated at a high speed (S6yes), the cutting speed low speed solenoid 134b is excited and the electromagnetic cutting speed change valve 134 is switched to the low speed side (S7yes), the PTO low speed gear 112 of the PTO speed change mechanism 110 is cut. The low speed control of the cutting gear shift is executed, which is engaged with the driving PTO shaft 94 and operates the cutting driving PTO shaft 94 via the PTO low speed gear 112 (S8). During the low speed control in step 8, it is determined whether or not the detected value of the cutting rotation sensor 143 (the rotational speed of the cutting input shaft 45) is within the range of the vehicle speed synchronization speed.

  When it is determined that the detected value of the cutting rotation sensor 143 (the number of rotations of the cutting input shaft 45) is higher than the high speed side constant rotational speed set by the high speed side constant speed setting device 147 (S9yes), The high speed side constant speed solenoid 135a is excited to switch the electromagnetic constant rotation valve 135 to the high speed side, the high speed side constant rotation gear 118 of the PTO constant rotation mechanism 111 is engaged with the cutting drive PTO shaft 94, and the high speed side constant rotation gear is engaged. The high speed side constant rotation control of the cutting speed of operating the cutting drive PTO shaft 94 via 118 is executed (S10).

  On the other hand, when it is determined that the detection value of the cutting rotation sensor 143 (the number of rotations of the cutting input shaft 45) has decreased below the low speed side constant rotational speed set by the low speed side constant speed setting device 148 (S11yes), The low speed side constant speed solenoid 135b is excited to switch the electromagnetic constant rotation valve 135 to the low speed side, the low speed side constant rotation gear 117 of the PTO constant rotation mechanism 111 is engaged with the cutting drive PTO shaft 94, and the low speed side constant rotation gear is engaged. The low speed side constant rotation control of the cutting speed of operating the cutting drive PTO shaft 94 via 117 is executed (S12).

  As a result, when the output of the straight traveling hydraulic motor 89 is switched to the high speed side and the PTO transmission mechanism 110 is switched to the low speed side, the vehicle speed synchronization speed synchronized with the traveling speed of the traveling machine body 1 or the high speed side constant speed is set. By either the high speed side constant rotational speed set by the speed setter 147 or the low speed side constant rotational speed set by the low speed side constant speed setter 148 (the cutting speed indicated by the thick solid line A in FIG. 8), The cutting input shaft 45 rotates to operate the cutting blade device 30, the culm pulling device 31, and the culm transporting device 32, respectively, so that the culm planted in the field can be harvested.

  Therefore, compared with the moving speed of the traveling machine body 1, the transport speed of the culm pulling device 31 and the culm transporting device 32 does not become too fast, and the culm pulling device 31 and the culm transporting device 32 are overloaded. It can be prevented from operating, and it is possible to reduce the disorder or damage of the grain conveying posture. Moreover, compared with the moving speed of the traveling machine body 1, the conveying speed of the culm pulling device 31 and / or the culm conveying apparatus 32 does not become too slow, and the conveying posture of the culm is being jammed or being transported. It can be prevented from being disturbed.

  Further, during the cutting operation for cutting the grain culm planted in the field, the hydraulic sub-shifting low-speed solenoid 130a is excited by the operation of the hydraulic sub-shifting switch 144, and the electromagnetic sub-shifting valve 130 is switched to the low-speed side, so When the 89 is operated at low speed (S13yes), the cutting speed low speed solenoid 134b is excited and the electromagnetic cutting speed change valve 134 is switched to the low speed side (S14yes), the PTO low speed gear 112 of the PTO speed change mechanism 110 is cut. It is engaged with the drive PTO shaft 94 and operates the cutting drive PTO shaft 94 via the PTO low speed gear 112. That is, the low speed control of the cutting gear shift in step 8 described above is executed, and then the high speed side constant rotation control in step 10 or the low speed side constant rotation control in step 12 is executed.

  As a result, when the output of the straight traveling hydraulic motor 89 is switched to the low speed side and the PTO transmission mechanism 110 is switched to the low speed side, the vehicle speed synchronization speed synchronized with the moving speed of the traveling machine body 1 or the low speed side constant speed is set. The cutting input shaft 45 is rotated by any one of the low-speed constant rotation speeds set by the speed setting device 148 (the cutting speed indicated by the thick two-dot chain line B in FIG. 8), and the cutting blade device 30 and the grain culm The pulling device 31 and the culm conveying device 32 can be operated to cut the culm planted in the field.

  On the other hand, in step 13, when the linear hydraulic motor 89 is operated at low speed (S13yes), the cutting speed high speed solenoid 134a is excited and the electromagnetic cutting speed change valve 134 is switched to the high speed side (S14yes). The high speed control of the cutting speed is performed in which the PTO high speed gear 113 of the speed change mechanism 110 is engaged with the cutting drive PTO shaft 94 and the cutting drive PTO shaft 94 is operated via the PTO high speed gear 113 (S16). That is, the high speed control of the cutting shift in step 16 is executed, and then the high speed side constant rotation control in step 10 or the low speed side constant rotation control in step 12 is executed.

  As a result, when the output of the straight traveling hydraulic motor 89 is switched to the low speed side and the PTO transmission mechanism 110 is switched to the high speed side, the vehicle speed synchronization speed synchronized with the moving speed of the traveling machine body 1 or the high speed side constant speed is set. By either the high speed side constant rotational speed set by the speed setter 147 or the low speed side constant rotational speed set by the low speed side constant speed setter 148 (the cutting speed indicated by the thin solid line C in FIG. 8), The cutting input shaft 45 rotates to operate the cutting blade device 30, the culm pulling device 31, and the culm transporting device 32, respectively, so that the culm planted in the field can be harvested.

  In FIG. 8, the cutting speed indicated by the thick solid line A, the cutting speed indicated by the thick two-dot chain line B, and the cutting speed indicated by the thin solid line C are all in the state where the auxiliary transmission gear mechanism 102 is switched to the high speed side. In other words, this is the cutting speed when the gear sub-shift is in a high-speed output state and the cutting operation that the culm planted in the field does not fall down is executed. When the grain planted in the field is lying down, the sub-transmission gear mechanism 102 is switched to the low speed side, the gear sub-transmission is kept in the low-speed output state, and the hydraulic motor 89 for straight running is operated at low speed. The lying grain harvesting operation is executed at a speed (a cutting speed indicated by a thin broken line D in FIG. 8) in which the sub-shift is in a low-speed output state and the PTO transmission mechanism 110 is in a high-speed output state.

  That is, when the cereal planted in the field is lying down, the vehicle speed synchronization speed synchronized with the moving speed of the traveling machine 1 or the high speed side constant rotation speed set by the high speed side constant speed setting device 147 or the low speed side The cutting input shaft 45 is rotated at any one of the low-speed constant rotational speeds set by the constant speed setting device 148 (the cutting speed indicated by the thin broken line D in FIG. 8), and the cutting blade device 30 and the culling pulling are caused. The apparatus 31 and the culm conveying device 32 are respectively operated, and the fallen culm can be harvested. Therefore, since the moving speed (vehicle speed) of the traveling machine body 1 is decreased, the speeds of the cutting blade device 30, the culm pulling device 31, and the culm conveying device 32 are respectively increased. As a result, the harvesting speed of the fallen corn straw becomes relatively fast, and the grain culling raising performance of the corn straw pulling apparatus 31 can be maintained to prevent uncut residue or clogging.

  As is clear from the above description and FIGS. 1, 3, and 4, the traveling machine body 1 including the traveling crawler 2 serving as the traveling section that is operated by the engine 20, and before cutting as the farm work section disposed in the traveling machine body 1. The processing device 3 and a transmission case 26 that transmits the output of the engine 20 to the traveling unit 2 or the pre-cutting processing device 3 are provided, and the transmission case hydraulic pressure as a first speed change means that shifts the output of the engine. A pump 88, a linear hydraulic motor 89 as a second transmission means for shifting the output of the first transmission means 88, and an auxiliary transmission gear mechanism 102 as a third transmission means for shifting the output of the hydraulic motor 89 for straight movement. Arrangement is made, and a cutting drive PTO shaft 94 as a PTO shaft is connected to the output side of the straight traveling hydraulic motor 89, and cutting is performed from the straight traveling hydraulic motor 89 via the cutting drive PTO shaft 94. In the harvester configured to transmit the output of the engine 20 to the processing device 3, a PTO transmission mechanism 110 that drives the pre-harvesting processing device 3 at a vehicle speed synchronization speed and a constant rotational speed inside the mission case 26. A PTO constant rotation mechanism 111 for driving the cutting pretreatment device 3 is provided, and the PTO speed change mechanism 110 is disposed between the output side of the linear advance hydraulic motor 89 and the cutting drive PTO shaft 94, and the linear advance hydraulic pump 88 Since the PTO constant rotation mechanism 111 is disposed between the input side and the reaping drive PTO shaft 94, the PTO transmission mechanism 110 and the PTO constant rotation mechanism 111 are connected using a belt transmission mechanism having a tension clutch. Compared to the conventional drive structure that constitutes, the engine 20 and the transmission case 26 and between the engine 20 and the pre-cutting processing device 3 are respectively provided. Disposed belt transmission mechanism can easily configure. The maintenance workability of the belt transmission mechanism can be improved. Further, by utilizing the transmission case 26 having the straight hydraulic pump 88, the straight hydraulic motor 89, and the auxiliary transmission gear mechanism 102, the PTO transmission mechanism 110 and the PTO constant rotation mechanism 111 can be made compact and low cost. Can be placed. By installing the PTO transmission mechanism 110 and the PTO constant rotation mechanism 111 in the mission case 26, it is possible to omit providing a counter case at the front of the traveling machine body 1 as in the prior art, or temporarily Even if it is provided, the counter case can be reduced in size.

  As apparent from the above description and FIGS. 3 and 4, either the shift output of the PTO transmission mechanism 110 or the constant rotation output of the PTO constant rotation mechanism 111 is transmitted to the cutting drive PTO shaft 94. Since the one-way rotation clutch 116 for PTO speed change and the one-way rotation clutch 121 for constant rotation are provided as the clutch means, the gear change output for synchronizing the vehicle speed of the PTO speed change mechanism 110 or the PTO constant speed rotation mechanism 111 is provided. Can be prevented from being simultaneously transmitted to the pre-cutting processing device 3. Further, it is possible to prevent the cutting drive PTO shaft 94 from reversing due to the backward movement of the traveling machine body 1.

  As apparent from the above description and FIGS. 4 and 5, the PTO speed change mechanism 110 cuts off the output of the PTO operating state in which the output of the straight-ahead hydraulic motor 89 is shifted and shifted, and the output of the straight-ahead hydraulic motor 89. Since it is configured to be able to switch to the PTO stop state, the conventional belt tension clutch for driving or stopping control of the pre-cutting processing device 3 becomes unnecessary. Further, it is not necessary to provide a clutch for driving or stopping the cutting pretreatment device 3 in the counter case or the like. A clutch for driving or stopping the cutting pretreatment device 3 can be configured at low cost and in a compact manner.

  As is clear from the above description and FIGS. 4 and 6, the PTO constant rotation mechanism 111 includes a low-speed constant rotation operation state that maintains the minimum number of rotations necessary for driving the cutting pretreatment device 3, and a precutting processing device. 3 is configured to be switchable between a high-speed constant rotation operation state that maintains the maximum rotation speed necessary for driving 3 and a PTO stop state that cuts off the output of the straight traveling hydraulic motor 89. The cutting pre-processing device 3 can be operated by the low-speed constant rotation output from the high-speed side, the high-speed constant rotation output, or the shift output for synchronizing the vehicle speed of the PTO transmission mechanism 110. The machine vibration or damage of the pre-cutting processing device 3 can be reduced, and the cutting work performance of the pre-cutting processing device 3 can be properly maintained.

It is a side view of the combine for 4 thread cutting of 1st Embodiment of this invention. It is the same top view. It is a drive system diagram of a combine. It is a drive system diagram of a mission case. It is a hydraulic circuit diagram. It is a functional block diagram of the control circuit of a cutting speed control means. It is a flowchart of cutting speed control. It is a diagram which shows the relationship between a vehicle speed and a cutting speed.

Explanation of symbols

1 traveling machine body 2 traveling crawler (traveling section)
3 Cutting pre-treatment device (agricultural work department)
20 Engine 26 Transmission case 88 Hydraulic pump for straight running (first transmission means)
89 Straightforward hydraulic motor (second transmission means)
94 Mowing drive PTO shaft 102 Sub-transmission gear mechanism (third transmission means)
110 PTO transmission mechanism 111 PTO constant rotation mechanism 116 One-way rotation clutch (clutch means) for PTO transmission
121 Unidirectional rotating clutch (clutch means) for constant rotation

Claims (4)

A traveling machine body including a traveling unit that is operated by an engine, a farm working unit disposed in the traveling machine body, and a transmission case that transmits the output of the engine to the traveling unit or the farm working unit, A first transmission means for changing the output of the engine, a second transmission means for changing the output of the first transmission means, and a third transmission means for changing the output of the second transmission means are arranged, and the second transmission means In a harvesting machine configured to connect a PTO shaft to the output side of the second transmission means and transmit the output of the engine to the farm working unit via the PTO shaft from the second transmission means,
Inside the mission case, a PTO transmission mechanism that drives the farm working unit at a vehicle speed synchronization speed, and a PTO constant rotation mechanism that drives the farm working unit at a constant rotational speed,
The PTO transmission mechanism is arranged between the output side of the second transmission means and the PTO shaft, and the PTO constant rotation mechanism is arranged between the input side of the first transmission means and the PTO shaft. The harvesting machine that features.   The clutch means for transmitting either the speed change output of the PTO speed change mechanism or the constant speed output of the PTO constant speed rotation mechanism to the PTO shaft is provided. Harvester.   The PTO speed change mechanism is configured to be switchable between a PTO operation state in which the output of the second speed change means is changed to change the output and a PTO stop state in which the output of the second speed change means is cut off. The harvester according to claim 1.   The PTO constant rotation mechanism includes a low speed side constant rotation operation state that maintains a minimum rotation number necessary for driving the farm work unit, and a high speed side constant rotation operation state that maintains a maximum rotation number necessary for driving the farm work unit. 2. The harvester according to claim 1, wherein the harvester is configured to be switchable to a PTO stop state in which the output of the second transmission means is cut off.

Images