JP2009219465A - Combine harvester - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a combine harvester which can simplify a reaping-driving mechanism and can easily lower a cost for making the reaping-driving mechanism. <P>SOLUTION: Provided is the combine harvester which includes a travel machine frame having a travel portion 2 operated with an engine 14, a reaping blade device 222, a grain straw-conveying device 224, and a vehicle speed sensor for detecting the travel speed of the travel machine frame, and in which a constant rotation output from the engine is changed into a vehicle speed-synchronizing speed, and then transmitted to the reaping blade device or the grain straw-conveying device, characterized by disposing a planet gear mechanism 91 for transmitting a constant rotation output from the engine to the grain straw-conveying device and the like, and a reaping speed-changing actuator for decelerating the output of the planet gear mechanism to the grain straw-conveying device and the like, and decelerating the planet gear mechanism with the reaping speed-changing actuator on the detection result of the vehicle speed sensor. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a combine harvester that harvests cereals planted in a field and collects grains, or a combine such as feed combine that harvests cereals for feed and collects it as feed, and more particularly, a cutting blade device The present invention relates to a combine in which a cereal conveyance device or the like for conveying cereals or cereals for feed that are cut by the plant is operated by an engine.

Conventionally, a combiner cuts a stock of uncut grain culm planted in a field with a cutting blade device, conveys the cereal to a threshing device by a cereal conveying means, and threshs the cereal with a threshing device. , Configured to collect grain. As shown in Patent Document 1, a reaping device such as a cutting blade device or a grain feeder is operated by a driving force from an engine via a belt transmission mechanism having a tension clutch.
JP 2004-97038 A

  As shown in Patent Document 1, the prior art has a speed synchronized with the moving speed (vehicle speed) of the traveling machine body when the cutting blade device or the culm conveying means is operated by a part of the driving force from the engine. Therefore, it is necessary to improve the driving performance of the cutting device by providing a mechanical cutting drive mechanism such as a cutting speed change mechanism and a constant cutting rotation mechanism. . There is a problem that the cutting drive mechanism that transmits the rotation of the engine to the cutting device cannot be easily configured. A hydraulic continuously variable transmission having a hydraulic pump and a hydraulic motor is provided in place of the cutting speed change mechanism or the constant cutting rotation mechanism, and the rotation of the engine is transmitted to the cutting device via the hydraulic continuously variable transmission. In this case, the mowing drive mechanism can be configured easily, but there is a problem that the transmission efficiency is lower than that of the mechanical transmission mechanism at the time of high speed operation in which the mowing apparatus is operated at the highest speed. In order to improve the driving performance of the reaping device, it is necessary to use an expensive hydraulic continuously variable transmission whose transmission efficiency does not decrease even during high-speed work. When the cutting drive mechanism is configured by a hydraulic continuously variable transmission, there is a problem that the manufacturing cost cannot be easily reduced.

  An object of the present invention is to provide a combine that can easily reduce the manufacturing cost of a mowing drive mechanism while being able to easily configure a mowing drive structure that transmits engine rotation to the mowing device.

  In order to achieve the above object, a combine of an invention according to claim 1 includes a traveling machine body having a traveling unit that is operated by an engine, a cutting blade device that cuts a stock of cereals planted in a field, and the cutting A cereal conveying device that conveys the cereal that has been cut by the blade device, and a vehicle speed sensor that detects a moving speed of the traveling machine body, and the constant rotational output from the engine is changed to a vehicle speed synchronization speed. A planetary gear mechanism for transmitting a constant rotational output from the engine to the grain feeder, etc., in the combine configured to transmit to the cutting blade device or the grain feeder, etc., and the grain A cutting gear shifting actuator that decelerates the output of the planetary gear mechanism to a saddle transport device or the like, and based on the detection result of the vehicle speed sensor, the planetary gear is driven by the cutting gear shifting actuator. It is obtained by configured to decelerate actuating the mechanism.

  According to a second aspect of the present invention, in the combine according to the first aspect, when the moving speed of the traveling machine body is within a predetermined range, the planetary gear is driven by the cutting gear shift actuator based on the detection result of the vehicle speed sensor. While the mechanism is configured to decelerate, when the traveling speed of the traveling machine body is equal to or higher than a predetermined range, the rotational output of the cutting gear shifting actuator is maintained at a constant high speed, and the traveling speed of the traveling machine body is predetermined. When it is below the range, the rotational output of the cutting gear shift actuator is maintained at a constant low speed or stopped.

  According to a third aspect of the present invention, in the combine according to the first aspect, the combine includes a reverse rotation work switch that allows reverse rotation of the cereal conveying device or the like, and the planetary gear is based on a reverse rotation permission operation of the reverse rotation work switch. The output of the planetary gear mechanism to the grain feeder is reversed at a low speed when the control output for cutting and shifting of the actuator for cutting and shifting to the gear mechanism is a rotation speed near the maximum rotation. .

  According to a fourth aspect of the present invention, in the combine according to the first aspect, a harvesting shift input clutch for transmitting an output of the harvesting shift actuator to the planetary gear mechanism, and a constant rotational output of the engine. A reverse rotation input mechanism capable of maintaining the output rotation of the planetary gear mechanism at substantially zero, and a reverse rotation input clutch for switching a reverse rotation input transmitted from the reverse rotation input mechanism to the planetary gear mechanism. The output rotation of the planetary gear mechanism can be maintained at zero rotation by the reverse rotation input transmitted from the rotation input mechanism to the planetary gear mechanism via the reverse input clutch.

  According to a fifth aspect of the present invention, in the combine according to the first aspect, the output of the planetary gear mechanism is generated with respect to an electric motor for cutting gear shift that forms the actuator for cutting gear shifting and a substantially constant rotational input of the engine. A reverse rotation input mechanism that can be maintained at substantially zero, and a reverse rotation input clutch that turns on and off a reverse rotation input transmitted from the reverse rotation input mechanism to the planetary gear mechanism, from the reverse rotation input mechanism to the reverse rotation input clutch. The output rotation of the planetary gear mechanism can be maintained at substantially zero by the reverse rotation input transmitted to the planetary gear mechanism via the.

  According to the first aspect of the present invention, the traveling machine body including the traveling unit that is operated by the engine, the cutting blade device that cuts the stock of the cereal planted in the field, and the stock is cut by the cutting blade device. A cereal conveying device that conveys the cereal cedar and a vehicle speed sensor that detects a moving speed of the traveling machine body, and after changing a constant rotational output from the engine to a vehicle speed synchronized speed, the cutting blade device Alternatively, in a combine configured to transmit to the cereal transport device or the like, a planetary gear mechanism that transmits a constant rotational output from the engine to the cereal transport device or the like, and the planet for the cereal transport device or the like A cutting gear shifting actuator that decelerates the output of the gear mechanism, and configured to decelerate the planetary gear mechanism by the cutting gear shifting actuator based on the detection result of the vehicle speed sensor. Therefore, the cutting drive structure that transmits the rotation of the engine to the grain feeder etc. is simpler than the conventional structure with a mechanical cutting drive mechanism such as a cutting speed change mechanism and a constant cutting rotation mechanism. The manufacturing cost of the cutting drive mechanism can be easily reduced. In addition, when driving the cereal conveying device or the like at high speed, the rotational output from the engine is transmitted to the cereal conveying device or the like via the planetary gear mechanism. Compared to the conventional structure constituting the mechanism, the mowing drive mechanism can be constructed at low cost and the transmission efficiency can be improved. In particular, the higher the cutting speed, the better the transmission efficiency, so that high-speed workability can be improved. Furthermore, not only the forward movement of the traveling machine body but also the backward movement, the reaping device such as the grain feeder can be easily operated in the same way as the forward movement. Workability can be improved.

  According to a second aspect of the present invention, the planetary gear mechanism is configured to decelerate the planetary gear mechanism by the cutting gear shifting actuator based on the detection result of the vehicle speed sensor when the traveling speed of the traveling machine body is within a predetermined range. On the other hand, when the moving speed of the traveling machine body is equal to or higher than a predetermined range, the rotational output of the cutting gear shifting actuator is maintained at a high speed constant rotational speed, and when the moving speed of the traveling machine body is equal to or lower than the predetermined range, Since the rotation output of the speed change actuator is configured to be maintained at a constant low speed or stopped at a low speed, by the control of the cutting speed change actuator, at a vehicle speed synchronization speed related to the moving speed of the traveling machine body, While being able to easily operate the harvesting device such as the cereal conveying device, it retains functions such as the shifting speed and the constant rotation of the harvesting. It is those that can improve the work of.

  According to a third aspect of the present invention, the chopping speed change actuator for the planetary gear mechanism is provided with a reverse rotation work switch that allows reverse rotation of the grain feeder, etc., and based on the reverse rotation permission operation of the reverse rotation switch. Since the output of the planetary gear mechanism with respect to the rice culm transporting device or the like is reversed at a low speed when the control output for cutting and shifting is at a rotation speed near the maximum rotation, for example, the traveling machine body is fixed. In a state where it is stopped at a place, the cereal conveying device or the like can be operated in a reverse rotation at a low speed, and maintenance operability of the cereal conveying device or the operability of removing cereals clogged in the cereal conveying device or the like Can be improved. In addition, when exchanging a part of the long chain of the cereal conveying device, the chain connecting portion and the like can be easily moved to a place where separation work is easy, so that the disassembling and assembling of the cereal conveying device, etc. It is possible to improve the maintenance workability.

  According to the fourth aspect of the present invention, a cutting shift input clutch that transmits the output of the cutting shift actuator to the planetary gear mechanism, and an output rotation of the planetary gear mechanism with respect to a constant rotation output of the engine. A reverse rotation input mechanism capable of maintaining the reverse rotation input mechanism, and a reverse rotation input clutch for turning on and off the reverse rotation input transmitted from the reverse rotation input mechanism to the planetary gear mechanism, the reverse rotation input mechanism from the reverse rotation input mechanism Since the output of the planetary gear mechanism can be maintained at zero rotation by the reverse rotation input transmitted to the planetary gear mechanism via the clutch, the cutting operation of the input gear for cutting shift and the reverse input By the clutch engagement operation, the cutting gear shifting actuator can be stopped, and the output of the planetary gear mechanism can be maintained at zero rotation. For example, when the cereal conveyor device or the like is stopped and maintained for a long time in the movement between fields, etc., it is not necessary to operate the cutting gear shifting actuator at a high speed for a long time. The mowing shift actuator can be simply configured.

  According to the fifth aspect of the present invention, the electric motor for cutting gear shift that forms the actuator for cutting gear shift, and the reverse rotation capable of maintaining the output of the planetary gear mechanism at substantially zero with respect to the substantially constant rotation input of the engine. An input mechanism, and a reverse rotation input clutch that turns on and off a reverse rotation input transmitted from the reverse rotation input mechanism to the planetary gear mechanism. The reverse rotation input mechanism passes through the reverse rotation input clutch to the planetary gear mechanism. Since the output rotation of the planetary gear mechanism can be maintained at substantially zero by the transmitted reverse rotation input, the output of the planetary gear mechanism can be maintained at zero rotation by the engagement operation of the reverse input clutch. . In addition, when the cereal conveyance device or the like is stopped and maintained for a long time during movement between fields, the electric power for the mowing shift electric motor can be reduced to 2 because the mowing gear shifting electric motor can be used as a generator. It can be stored in a secondary battery or the like.

  DESCRIPTION OF EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings. FIG. 1 is a left side view of the combine, FIG. 2 is a plan view of the combine, FIG. 3 is a side view of the cutting blade device and the culm conveying device, and FIG. 5 is a drive system diagram of the combine, FIG. 6 is a drive system diagram of a harvesting device including a cutting blade device and a grain feeder, FIG. 7 is a block diagram of the drive system shown in FIG. 6, and FIG. It is a functional block diagram of a control circuit. 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 forward direction of the traveling machine body 1 is simply referred to as the left side, and the right side in the forward 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 6-row mowing device 3 that takes in while harvesting cereals is mounted by a single-acting lifting hydraulic cylinder 4 so as to be movable up and down around the mowing pivot fulcrum shaft 4 a. ing. 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 the present embodiment, the threshing device 5 is arranged on the left side in the forward direction of the traveling machine body 1, and the grain tank 7 is arranged on the right side in the forward 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 cabin 10 is provided on the right side of the reaping device 3 and on the front side of the grain tank 7.

  In the driving cabin 10, there are disposed a steering handle 11, a driving seat 12, a main transmission lever 42, a sub transmission lever 43, and a work clutch lever 44 for turning on and off the threshing clutch and the cutting clutch. Although not shown, the driving cabin 10 is provided with a step on which an operator gets on, a handle column provided with the steering handle 11, and a lever column provided with the levers 42, 43, 44 and the like. An engine 14 as a power source is disposed in the traveling machine body 1 below the driver seat 12.

  As shown in FIGS. 1 to 4, 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 14 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 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 intermediate roller 25 supports the ungrounded side of the traveling crawler 2, and the track roller 24 supports the traveling crawler 2. Landing.

  The cutting frame 221 is connected to the cutting rotation fulcrum shaft 4 a of the cutting device 3. A clipper-type cutting blade device 222 is provided below the cutting frame 221. A cutting blade device 222 cuts the stock of uncut grain cereals (grain culms) planted in the field. Six grain ridge pulling devices 223 are arranged in front of the cutting frame 221. The uncut grain culm planted in the field is caused by the culm pulling device 223. Between the culm pulling device 223 and the front end (feed start end side) of the feed chain 6, the culm conveying device 224 is arranged. The harvested culm cut by the cutting blade device 222 is conveyed by the culm conveying device 224. In addition, the weed body 225 for 6 strips is protrudingly provided in the front lower part of the grain raising apparatus 223. An uncut grain cereal planted in the field is weeded by the weeding body 225. The traveling crawler 2 is driven by the engine 14 so that the uncut cereal grains planted in the field are continuously cut by the reaping device 3 while moving in the field.

  Next, the structure of the reaping device 3 will be described with reference to FIGS. 3 and 4. As shown in FIGS. 3 and 4, the cutting frame 221 includes a cutting input case 16 that is rotatably supported by the bearing stand 15 on the front end side of the traveling machine body 1, and a vertical extension that extends forward from the cutting input case 16. A transmission case 18, a horizontal transmission case 19 extending in the left-right direction on the front end side of the vertical transmission case 18, and a weeding frame 20 for six strips connected to the horizontal transmission case 19 are formed. A weed body 225 is supported on the front end side of the weed frame 20. A cutting input case 16 is horizontally mounted in the left-right direction of the traveling machine body 1. A cutting input shaft 17 that transmits a driving force to each part of the cutting device 3 is incorporated in the cutting input case 16. The power from the engine 14 is configured to be transmitted to the cutting input shaft 17.

  The grain raising apparatus 223 has a pulling case 29 for 6 ridges for raising the uncut grained rice that has been weeded by the weed board 225. The pulling case 29 incorporates a plurality of pulling tines 28. The grain feeder 224 includes left and right right star wheels 30R and left and right right scooping belts 31R that squeeze the stock side of the two right-side grains introduced from the pulling case 29 for the two right-hand sides, and the left side Left and right left star wheels 30L and left and right left scooping belts 31L that scrape the stock side of the left two cereal grains introduced from the two pulling cases 29, and the center introduced from the two pulling cases 29 in the center It has left and right central star wheels 30C and left and right central rake belts 31C that rake up the stock side of the cereals for two strips.

  The cutting blade device 222 is scraped by the right star wheel 30R and the left and right right take-up belts 31R, the left star wheel 30L and the left and right left take-up belts 31L, the center star wheel 30C, and the left and right center take-up belts 31C. It has clipper-shaped left and right cutting blades 32 for cutting the stock of uncut cereal grains.

  In addition, the cereal carrying device 224 is configured to convey the stock side of the right side 2 portion of the harvested cereal that has been scraped by the right side 2 pieces of the star foil 30R and the scraping belt 31R to the rear side. And the left stock transport that joins the stock side of the left two strips of harvested cereals that have been scraped by the left side star foil 30L and the scraping belt 31L to the transport end of the right stock transport chain 33R During the transportation of the right stock transport chain 33R by transporting the stock 33 side of the chain 33L, the central two portions of the star foil 30C and the central two strips of the harvested cereal rice bran, and the right stock transport chain 33R A central stock transport chain 33C to be merged. The right and left stock transfer chains 33R, 33L, and 33C are configured to join the stock end sides of the six cropped cereal grains to the transport end of the right stock transport chain 33R.

  The cereal transport device 224 includes a vertical transport chain 34 that inherits the stock base side of the harvested cereals for six strips from the right stock transport chain 33R, and a transport start end of the feed chain 6 from the transport end of the vertical transport chain 34. And auxiliary stock transport chains 35 and 36 for transporting the stock side of the harvested cereals for 6 lines. From the vertical conveyance chain 34, it is configured so as to convey the stock side of the six cropped cereal grains to the conveyance start end of the feed chain 6 via the auxiliary stock source conveyance chains 35 and 36.

  The grain culm transporting device 224 is transported by the right stalk transporting tine 37R that transports the head of the harvested stalks for the two right-hand strips transported by the right cultivating transport chain 33R, and the left cultivating transport 33L. Left tip transport tine 37L that transports the tip of the left side of the cut grain halves, and central tip transport tine that transports the tip of the cut center of the central two parts that are transported by the central stock transport chain 33C 37C and a rear tip transporting tine 38 for transporting the tip of the harvested cereals for six strips transported by the vertical transport chain 34. It is configured so that the tip side of the harvested cereal cocoons for the six strips harvested by the reaping device 3 is conveyed into the handle barrel 226 of the threshing device 5.

  Next, the drive structure will be described with reference to FIG. As shown in FIG. 5, a pulling lateral transmission shaft 48 is connected to the cutting input shaft 17 via a longitudinal transmission shaft 40, a lateral transmission shaft 41, and a left conveying drive shaft 69 which will be described later. The pulling lateral transmission shaft 48 is connected to the pulling tine drive shaft 45 of each pulling case 29 for six lines. The pulling case 29 is erected on the rear side of the weed body 225 and above the weed frame 20. A pulling tine drive shaft 45 protrudes from the back surface on the upper end side of the pulling case 29. A pulling tine chain 28a provided with a plurality of pulling tines 28 is driven via a pulling tine drive shaft 45 and a pulling lateral transmission shaft 48.

  As shown in FIG. 5, the left and right cutting blades 32 are connected to the lateral transmission shaft 41 via the left and right crankshafts 52a and 52b. The left and right cutting blades 32 are configured to be driven synchronously via the lateral transmission shaft 41. The cutting blade device 222 is divided at the central portion of the cutting width for six lines to form the left and right cutting blades 32, and the left and right cutting blades 32 are reciprocated in opposite directions, and left and right generated by the reciprocating movement. This is configured to cancel the vibration (inertial force) of the cutting blade 32.

  As shown in FIG. 5, one end side of the vertical transmission shaft 40 in the vertical transmission case 18 is connected to the cutting input shaft 17. One end side of the lateral transmission shaft 41 in the lateral transmission case 19 is connected to the other end side of the longitudinal transmission shaft 40. Via the longitudinal transmission shaft 40 and the lateral transmission shaft 41, the rotational force of the cutting input shaft 17 is transmitted to each drive unit of the cereal conveyor device 224.

  That is, the right transport drive shaft 62 is connected to the vertical transmission shaft 40. Via the vertical transmission shaft 40 and the right transport drive shaft 62, the right stock former transport chain 33R and the right tip transport tine 37R, the right star wheel 30R and the right take-up belt 31R are driven. Further, the vertical transmission shaft 63 is connected to the vertical transmission shaft 40 via the right conveyance drive shaft 62. The vertical conveyance chain 34 is driven via the right conveyance drive shaft 62 and the vertical conveyance transmission shaft 63. Further, the rear conveyance drive shaft 54 is connected to the vertical transmission shaft 40. The auxiliary stock former transport chains 35 and 36 and the rear tip transport tine 38 are driven via the vertical transmission shaft 40 and the rear transport drive shaft 54.

  Further, a left transport drive shaft 69 is connected to the left end side of the lateral transmission shaft 41. The left stock former transfer chain 33L and the left tip transfer tine 37L, the left star wheel 30L, and the left take-up belt 31L are driven via the left transfer drive shaft 69. Further, the central transmission drive shaft 75 is connected to the lateral transmission shaft 41. The central stock transport chain 33C and the central tip transport tine 37C, the central star wheel 30C and the central scooping belt 31C are driven via the central transport drive shaft 75.

  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 226 for threshing threshing, a rocking sorter 227 that sorts the shed matter falling below the handling cylinder 226, and a tang fan 228. A dust removal processing drum 229 that reprocesses the threshing waste taken out from the rear portion of the handling drum 226 and a dust discharge fan 230 that discharges dust at the rear portion of the swing sorter 227 are provided. In addition, the rotating shaft core line of the handling cylinder 226 extends along the conveying direction of the cereal by the feed chain 6 (in other words, the traveling direction of the traveling machine body 1). The stocker side of the harvested cereals conveyed by the cereal conveying device 224 of the reaping device 3 is inherited by the feed chain 6 and is nipped and conveyed. And the tip side of the harvested cereal culm is carried into the handling chamber of the threshing device 5 and threshed by the handling cylinder 226.

  On the lower side of the swing sorter 227, a first conveyor 231 that takes out the grain (first thing) sorted by the swing sorter 227, and a second that takes out a second thing such as a grain with a branch raft. A conveyor 232 is provided. Each of the conveyors 231 and 232 is provided on the upper surface side of the traveling machine body 1 above the rear part of the traveling crawler 2 in a side view in order of the first conveyor 231 and the second conveyor 232 from the front side of the traveling machine body 1.

  The swing sorter 227 is configured such that the cereals that have leaked from the receiving net 237 stretched below the handling cylinder 226 are peristally sorted (specific gravity sorting) by the feed pan 238 and the chaff sheave 239. The grain that has fallen from the rocking sorter 227 is removed by the sorting air from the red pepper fan 228 and the dust in the grain falls first on the conveyor 231. The threshing conveyor 233 extending in the vertical direction is connected to the terminal portion of the first conveyor 231 that protrudes outward from one side wall (in the embodiment, the right side wall) near the grain tank 7 in the threshing device 5. The grain taken out from the first conveyor 231 is carried into the grain tank 7 via the cereal conveyor 233 and collected in the grain tank 7. In addition, along the inclination of the rear surface of the grain tank 7, the raising conveyor 233 is erected on the rear side of the grain tank 7 in a backward inclined posture in which the upper end side of the raising conveyor 233 is inclined backward.

  Further, the swing sorter 227 is configured to drop a second thing such as a grain with a branch infarction from the chaff sheave 239 onto the second conveyor 232 by peristaltic sorting (specific gravity sorting). A sorting fan 241 for wind-selecting the second thing falling below the chaff sheave 239 is provided. As for the second thing that has fallen from the chaff sheave 239, the dust and swarf in the grain are removed by the sorting air from the sorting fan 241 and dropped onto the second conveyor 232. A reduction conveyor 236 that intersects the whipping conveyor 233 and extends in the front-rear direction is provided. A terminal portion of the second conveyor 232 protruding outward from one side wall near the grain tank 7 in the threshing device 5 is connected to the upper surface side of the feed pan 238 via the reduction conveyor 236. That is, the second item is returned to the upper surface side of the feed pan 238 and re-sorted.

  On the other hand, a waste chain 234 is arranged on the rear end side (feed end side) of the feed chain 6. The slag passed from the rear end side of the feed chain 6 to the sewage chain 234 (the slag 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 235 provided on the rear, the vehicle is discharged to the lower rear of the traveling machine body 1.

  Next, the drive structure of the reaping device 3, the threshing device 5, the feed chain 6, the waste chain 234, the waste cutter 235, etc. will be described with reference to FIGS. As shown in FIGS. 5 and 6, an output shaft 70 of the engine 14 projects from the front side and the rear side of the engine 14. A travel input shaft 84 of the transmission case 71 is connected to an output shaft 70 on the front side of the engine 14 via a universal joint 83. The rotational driving force of the engine 14 is transmitted from the front output shaft 70 to the transmission case 71 and shifted, and then transmitted to the left and right traveling crawlers 2 via the left and right axles 72. That is, the left and right traveling crawlers 2 are configured to be driven by the rotational force of the engine 14.

  As shown in FIGS. 5 and 6, a discharge auger drive shaft 76 is connected to the output shaft 70 on the rear side of the engine 14, and the discharge auger 8 is driven via the discharge auger drive shaft 76 by the rotational drive force from the engine 21. The grain in the grain tank 7 is discharged to a container or the like. Further, a threshing drive shaft 77 that transmits the rotational driving force from the engine 14 to the handling cylinder 226 and the processing cylinder 230 is provided. A threshing drive shaft 77 is connected to the output shaft 70 on the rear side of the engine 14 via a threshing drive belt 79 provided with a threshing clutch 78 of a tension roller type. The threshing drive shaft 77 is connected to a handling cylinder shaft 80 that supports the processing cylinder 226 and a processing cylinder shaft 81 that supports the processing cylinder 230. The handling cylinder 226 and the processing cylinder 230 are configured to rotate at a substantially constant rotational speed by the rotational output of the engine 14 at a substantially constant rotational speed.

  As shown in FIGS. 5 and 6, a sorting input shaft 82 is connected to the threshing drive shaft 77. Due to the rotational output of the engine 14 at a substantially constant rotational speed, the swinging sorter 227, the Kara fan 228, the first conveyor 231, the second conveyor 232, the sorting fan 241, and the dust exhaust fan 230 are substantially omitted via the sorting input shaft 82. It is configured to rotate at a constant rotational speed. Further, in the transmission case 71, a hydraulic continuously variable transmission mechanism 96 for traveling main transmission having a pair of traveling hydraulic pumps and traveling hydraulic motors, and a swinging hydraulic pressure having a pair of swing hydraulic pumps and swing hydraulic motors. A continuously variable transmission mechanism 97 is provided. The rotation of the traveling input shaft 84 of the transmission case 71 is shifted and transmitted to the axle 72 by the hydraulic continuously variable transmission mechanism 96 for main traveling speed and the hydraulic continuously variable transmission mechanism 97 for turning. That is, the left and right traveling crawlers 2 are driven in the same direction by the hydraulic continuously variable transmission mechanism 96 for the main traveling speed to move straight. On the other hand, the left and right traveling crawlers 2 are driven in opposite directions by the hydraulic continuously variable transmission mechanism 97 for turning so as to turn.

  As shown in FIGS. 6 and 7, a counter gear case 90 is provided on the left side of the engine 14 on the traveling machine body 1 on the front side of the threshing device 5. In the counter gear case 90, the above-described threshing drive shaft 77, the selection input shaft 82 connected to the threshing drive shaft 77 via the forward rotation bevel gear 86, and the rotational output of the engine 14 at a substantially constant rotational speed are transmitted to the reaping device 3. A planetary gear mechanism 91 for continuously variable cutting drive, a speed-control rotating shaft 92 for adjusting (decelerating adjustment) a cutting rotation output transmitted from the planetary gear mechanism 91 to the cutting device 3, and a reverse bevel gear on the threshing drive shaft 77. The reverse rotation shaft 100 connected via the 87 and the cutting transmission shaft 101 for transmitting the rotational output of the engine 14 to the cutting device 3 via the planetary gear mechanism 91 are arranged.

  The planetary gear mechanism 91 includes a sun gear 93, a planetary gear 94, a ring gear 95, and a carrier gear 98. A planetary gear 94 is supported on the carrier gear 98 so as to be freely rotatable. The constant rotation gear 107 of the sorting input shaft 82 is engaged with the outer gear of the ring gear 95. The planetary gear 94 is engaged with the inner gear of the ring gear 95 and the sun gear 93. The cutting rotation gear 108 of the cutting transmission shaft 101 is engaged with the carrier gear 98. The speed adjusting rotary shaft 92 is connected to the sun gear 93 via an electromagnetic mowing shift input clutch 109. The electromagnetic mowing shift input clutch 109 is configured to perform an on / off operation by exciting or releasing an electromagnetic solenoid coil. The rotation from the governing rotary shaft 92 is transmitted to the sun gear 93 via the electromagnetic mowing shift input clutch 109. That is, when the governing rotation shaft 92 is rotated at a high speed (a constant rotational speed) by a mowing shift hydraulic motor 118, which will be described later, the rotational speed of the carrier gear 98 becomes zero with respect to the constant rotational speed of the ring gear 95. The carrier gear 98 stops. As a result, even if the ring gear 95 rotates at a constant rotational speed, the rotational speed of the cutting input shaft 17 becomes zero by rotating the sun gear 93 at the constant rotational speed in the reverse output direction, and the cutting apparatus 3 is stopped and maintained. It is constituted so that.

  As shown in FIGS. 6 and 7, the reverse rotation shaft 100 is connected to the sun gear 93 via the electromagnetic reverse input clutch 110. The electromagnetic reverse input clutch 110 is configured to be turned on or off by exciting or releasing the electromagnetic solenoid coil. That is, when the sun gear 93 is rotated via the reverse rotation shaft 100 by turning on and operating the electromagnetic reverse input clutch 110, the rotation speed of the carrier gear 98 becomes zero with respect to the constant rotation speed of the ring gear 95. The carrier gear 98 is configured to stop. As a result, even when the ring gear 95 rotates at a constant rotational speed, the rotational speed of the cutting input shaft 17 is maintained at zero by the operation of engaging the electromagnetic reverse input clutch 110, and the cutting apparatus 3 can be stopped. Even if the sun gear 93 rotates through the reverse rotation shaft 100, the rotation from the sun gear 93 is not transmitted to the governing rotation shaft 92 due to the disengagement operation (idling) of the electromagnetic mowing shift input clutch 109.

  Note that a one-way clutch may be provided instead of the electromagnetic mowing shift input clutch 109. When the speed control rotating shaft 92 is connected to the sun gear 93 through the one-way clutch, even if the sun gear 93 rotates through the electromagnetic reverse input clutch 110, the one-way clutch is idled and the speed control rotating shaft is rotated. 92 does not rotate. In addition, the sun gear 93 is rotated via the one-way clutch by the forced rotation of the governing rotation shaft 92.

  Further, a cutting drive shaft 102 that is connected to the cutting input shaft 17, a torque limiter 104 that connects the cutting drive shaft 102 to the cutting transmission shaft 101, and a feed chain driving shaft 103 that drives the feed chain 6 are arranged. The reaping drive shaft 102 is configured to rotate below the torque set by the torque limiter 104. A feed chain drive shaft 103 is connected to the sorting input shaft 82 via a feed chain transmission mechanism 111.

  As shown in FIGS. 6 and 7, a cutting and shifting mechanism 116 for rotating the speed-controlling rotating shaft 92 to decelerate the planetary gear mechanism 91 is provided. The mowing transmission mechanism 116 is an output variable type mowing transmission hydraulic pump 117 as a mowing shifting actuator that is driven to rotate at a constant speed by a constant rotational output of the engine 14, and the mowing transmission hydraulic pump 117 via a closed loop hydraulic circuit. And a cutting shift hydraulic motor 118 as a cutting shift actuator to be connected. Further, there is provided a cutting shift hydraulic cylinder 119 for changing the angle of the swash plate 117a of the cutting shift hydraulic pump 117. The rotational speed of the swash plate 117a of the chopping speed change hydraulic pump 117 is changed by operating the chopping speed change hydraulic cylinder 119, whereby the output rotational speed of the chopping speed change hydraulic motor 118 is changed.

  That is, when the angle of the swash plate 117a of the cutting gear shift hydraulic pump 117 is adjusted by the cutting gear shifting hydraulic cylinder 119 and the cutting gear shifting hydraulic motor 118 is operated, the sun gear 93 is rotated by the output rotation of the cutting gear shifting hydraulic motor 118. The planetary gear 94 rotates through the gap. When the planetary gear 94 is rotated by the mowing shift hydraulic motor 118, the rotation speed of the carrier gear 98 rotated by the ring gear 95 is changed in inverse proportion to the rotation speed of the sun gear 93. Therefore, by adjusting the angle of the swash plate 117a of the cutting gear shift hydraulic pump 117 and operating the cutting gear shifting hydraulic motor 118 to rotate the sun gear 93, the carrier gear 98 rotates relative to the constant rotation of the ring gear 95. Decelerated. As a result, the cutting and shifting hydraulic motor 118 is controlled to increase or decrease in proportion to the traveling speed (vehicle speed) of the traveling machine body 1 and the rotation speed of the carrier gear 98 is changed, so that the cutting is performed via the cutting input shaft 17. The device 3 can be driven at a speed synchronized with the vehicle speed.

  Further, when the sun gear 93 is rotated at a high speed by increasing the rotational speed of the cutting gear hydraulic motor 118 by adjusting the angle to increase the inclination angle of the swash plate 117a of the cutting gear hydraulic pump 117, the ring gear 95 is kept constant. With respect to the rotation of the rotation speed, the rotation speed of the carrier gear 98 becomes zero and the carrier gear 98 stops. As a result, even if the ring gear 95 rotates at a constant rotational speed, the rotational speed of the cutting input shaft 17 becomes zero and the cutting apparatus 3 is stopped and maintained.

  Further, by adjusting the maximum angle of the swash plate 117a of the cutting gear shift hydraulic pump 117, the output of the cutting gear shifting hydraulic motor 118 is maximized, and the sun gear 93 is rotated at the highest speed, whereby the ring gear 95 is rotated at a constant rotational speed. On the other hand, the carrier gear 98 is configured to rotate at a low speed in the direction opposite to the rotation direction of the carrier gear 98 by the ring gear 95. As a result, the cutting input shaft 17 is reversely rotated at a low speed, and the cutting blade device 222 or the culm transporting device 224 of the reaping device 3 can be operated in the direction opposite to that during the mowing operation. It is possible to easily perform the exchange operation of the transfer chain or the removal operation of the harvested cereal culm clogged during the conveyance.

  Next, the cutting speed control of this embodiment will be described. FIG. 8 is a functional block diagram of the cutting speed control means of the cutting device 3, and includes a work controller 282 such as a microcomputer having a ROM storing a control program and a RAM storing various data. As shown in FIG. 8, on the input side of the work controller 282 constituted by a microcomputer, a threshing switch 273 that detects an operation (such as driving of the threshing device 5) of the work clutch lever 44 and a work clutch. A cutting switch 274 that detects the operation of the lever 44 with the cutting clutch 78, a vehicle speed sensor 285 that detects the moving speed of the traveling machine 1, an engine-side rotation sensor 286 that detects the rotational speed of the ring gear 95, and a hydraulic motor for cutting and shifting. The rotational speed sensor 287 for detecting the rotational speed of the cutting gear 118, the rotational speed sensor 288 for detecting the rotational speed of the cutting input shaft 17, and the output rotational speed of the hydraulic motor 118 for the cutting speed (the operating speed of the cutting device 3). The cutting speed setting dial 262 for stepless adjustment and the minimum output speed of the hydraulic motor 118 for cutting speed change. A low-speed rotation setting device 266 as a minimum rotation number setting device for setting the number (minimum operating speed of the cutting device 3) and a maximum output rotation number (maximum operating speed of the cutting device 3) of the hydraulic motor 118 for cutting gear shifting are set. A high-speed rotation setting device 267 as a maximum rotation number setting device is connected to a reverse rotation work switch 270 that allows an operator to allow reverse rotation of the cereal conveyance device 224 and the like.

  As shown in FIG. 8, on the output side of the work controller 282, an electromagnetic reverse input clutch 110, an electromagnetic mowing shift input clutch 109, and a speed regulating valve 301 for operating the mowing gear shifting hydraulic cylinder 119 are connected. is doing. As a result, based on the detection result of the vehicle speed sensor 285, the angle of the swash plate 117a of the cutting gear shift hydraulic pump 117 is changed by the cutting gear shift hydraulic cylinder 119, and the cutting gear shifting hydraulic motor 118 is automatically controlled to increase or decrease. Therefore, the reaping device 3 can be operated at a vehicle speed synchronization speed synchronized with the moving speed (vehicle speed) of the traveling machine body 1. Further, based on the setting value of the conveyance speed setting dial 262 as a speed change dial, the angle of the swash plate 117a of the cutting shift hydraulic pump 117 is changed by the cutting shift hydraulic cylinder 119 so that the cutting shift hydraulic motor 118 is automatically operated. Therefore, the reaping device 3 can be operated at a speed according to the state of the reaping operation of the uncut cereals planted in the field.

  When the threshing clutch 78 is turned on by operating the work clutch lever 44, the electromagnetic reverse input clutch 110 is turned on by turning on the threshing switch 273, and the sun gear 93 is rotated via the reverse bevel gear 87. As a result, even if the ring gear 95 is rotated by the engagement of the threshing clutch 78, the planetary gear 94 is rotated in the reverse direction by the sun gear 93. Therefore, the rotation of the carrier gear 98 is held at zero, and the cutting transmission shaft 101 is stopped and maintained. .

  Therefore, even if the threshing clutch 78 is turned on and the threshing device 5 is operated, the reaping device 3 is stopped and maintained by the reaping stop maintenance control in step 2. That is, the operation performed by stopping the reaping device 3 while the threshing device 5 is operated, for example, the handling operation in which the operator supplies the reaped cereal to the feed chain 6, or the transportation of the grains in the grain tank 7 Can be loaded into other trucks. Even if the sun gear 93 is rotated by the reverse rotation bevel gear 87, the governing rotation shaft 92 is stopped and maintained by the disengagement operation (idling) of the electromagnetic mowing shift input clutch 109.

  Next, with reference to FIG. 9 thru | or FIG. 13, the harvesting operation | work which operates the harvesting apparatus 3 is demonstrated. FIG. 9 is a flowchart of mowing clutch control. When the cutting switch 274 is not on (S1no), when the driving flag is on (S2yes), the driving flag is reset (S3), and the stop control of the cutting gear shift hydraulic pump 117 is executed (S4). The stop flag is set (S5). On the other hand, when the cutting switch 274 is turned on by the operation of engaging the cutting clutch of the work clutch lever 44 (S1yes), when the stop flag is turned on (S6yes), the stop flag is reset (S7), and the cutting shift hydraulic pressure The drive start control of the pump 117 is executed (S8), and the drive flag is set (S9). In step 6, when the stop flag is not on (S6no) and when the reverse rotation work switch 270 is not on (S10no), the shift control of the reaping device 3 is executed (S11). In Step 10, when the reverse rotation work switch 270 is on (S10yes), the reverse rotation work control of the reaping device 3 is executed (S12).

  FIG. 10 is a flowchart of the shift control of the reaping device 3 in step 11 of the flowchart shown in FIG. The detection value of the vehicle speed sensor 285, the detection value of the cutting rotation sensor 288, and the setting value of the cutting speed setting dial 262 are read (S13). The target cutting speed (vehicle speed synchronization speed) of the cutting device 3 is calculated from the detection value of the vehicle speed sensor 285, the detection value of the cutting rotation sensor 288, and the setting value of the cutting speed setting dial 262 (S14). It is determined whether or not the cutting speed (actual cutting speed) of the cutting apparatus 3 detected by the cutting rotation sensor 288 is equal to the target cutting speed calculated in step 14 (S15). When the harvesting speed of the harvesting device 3 is not equal to the target harvesting speed (S15no), it is determined whether the target harvesting speed is higher than the harvesting speed of the harvesting device 3 (S16).

  When the cutting speed of the cutting device 3 is smaller than the target cutting speed in the determination of step 16 (S16yes), the cutting shift hydraulic cylinder 119 that decelerates the cutting shift hydraulic pump 117 is controlled (S17). The hydraulic motor 118 is decelerated to reduce the rotation speed of the sun gear 93 and increase the cutting speed of the cutting device 3. As a result, the reaping device 3 is operated at the vehicle speed synchronization speed synchronized with the moving speed (vehicle speed) of the traveling machine body 1 to perform the reaping work. Further, when the cutting speed of the cutting device 3 is increased by the speed increasing control in step 17, the maximum operating speed setting value of the cutting device 3 of the high-speed rotation setting device 267 is read (S18). When the cutting speed of the cutting device 3 matches the maximum operating speed setting value of the high-speed rotation setting device 267 and it is determined that the cutting device 3 is operating at high speed (S19yes), the high-speed constant rotation control of the cutting device 3 is performed. Is executed (S20). Even if the moving speed (vehicle speed) of the traveling machine body 1 is further increased, the cutting speed of the cutting device 3 is maintained at the set value of the high-speed rotation setting device 267 by the high-speed constant rotation control (S20) of the cutting device 3. That is, since the reaping device 3 is configured to operate at a speed equal to or lower than the rotational speed set by the high speed rotation setting device 267, the reaping is performed even when the traveling speed (vehicle speed) of the traveling machine body 1 is extremely high. The mowing operation speed of the device 3 does not become too fast, the mowing device 3 can be prevented from operating in an overloaded state, and the disorder of the hauling posture of the culm or damage to the mowing device 3 can be reduced.

  On the other hand, when the cutting speed of the cutting device 3 is not smaller than the target cutting speed in the determination of step 16 (S16no), the cutting gear shift hydraulic cylinder 119 is controlled to increase the speed of the cutting gear shift hydraulic pump 117 (S21). The cutting gear shifting hydraulic motor 118 is increased in speed to increase the rotational speed of the sun gear 93 and reduce the cutting speed of the cutting device 3. As a result, the reaping device 3 is operated at the vehicle speed synchronization speed synchronized with the moving speed (vehicle speed) of the traveling machine body 1 to perform the reaping work. Further, when the cutting speed of the cutting device 3 is reduced by the deceleration control in step 21, the minimum operating speed setting value of the cutting device 3 of the low speed rotation setting device 266 is read (S22). When the cutting device 3 operates at a low speed, the cutting speed of the cutting device 3 matches the minimum operating speed setting value of the low speed rotation setting device 266, and it is determined that the cutting device 3 is operating at a low speed (S23yes). The low speed constant rotation control (S24) of the reaping device 3 is executed. Therefore, even if the moving speed (vehicle speed) of the traveling machine body 1 is further reduced, the cutting speed of the cutting device 3 is maintained at the set value of the low-speed rotation setting device 266 by the low-speed constant rotation control (S24) of the cutting device 3. . That is, since the reaping device 3 can be operated at a speed higher than the rotational speed set by the minimum rotational speed setting device 266, the reaping speed of the reaping device 3 even when the traveling speed (vehicle speed) of the traveling machine body 1 is extremely slow. Therefore, it is possible to prevent clogging of the culm during transportation and maintain the transport performance of the culm transporting device 223 of the reaping device 3.

  Based on the detection result of the vehicle speed sensor 285, the moving speed of the traveling body 1 is increased by executing the speed increasing control (step 17) of the mowing apparatus 3 or executing the speed reduction control (step 21) of the mowing apparatus 3. The cutting speed of the cutting device 3 is changed in synchronization with the (vehicle speed), and the cutting operation of the uncut grain culm planted in the field is performed. As shown in FIG. 15, the relationship between the moving speed (vehicle speed) of the traveling machine body 1 and the cutting speed of the cutting device 3 is a pattern P1, P2 represented by a linear line, or a pattern P3 represented by a quadratic curve, It can be arbitrarily set to P4 or the like. The patterns P1, P2, P3, and P4 can be switched or selected by switching the cutting speed setting dial 262 or selecting a pattern selection switch (not shown). As shown in FIG. 15, the cutting speed of the cutting device 3 changes in proportion to the moving speed (vehicle speed) of the traveling machine body 1. As shown in FIG. 16, the cutting shift output from the cutting shift hydraulic motor 118 changes in inverse proportion to the moving speed (vehicle speed) of the traveling machine body 1.

  FIG. 11 is a flowchart of the mowing drive start control of the mowing device 3 in step 8 of the flowchart shown in FIG. When the electromagnetic reversal input clutch 110 is engaged by turning on the threshing switch 273, the value of the engine side rotation sensor 286 and the value of the cutting shift side rotation sensor 287 are read (S25). It is determined whether or not the cutting shift rotational speed from the cutting shift hydraulic motor 118 detected by the cutting shift-side rotation sensor 287 is equal to the engine speed detected by the engine-side rotation sensor 286 (S26). When the cutting gear shift rotation speed from the cutting gear shifting hydraulic motor 118 is not equal to the engine rotation speed (S26no), the cutting gear shifting hydraulic pump 117 is controlled to increase in speed (S27). On the other hand, when the cutting gear speed from the cutting gear shift hydraulic motor 118 is equal to the engine speed (S26yes), the cutting gear clutch 109 is engaged and controlled (S28) as shown in the timing chart of FIG. The input clutch 110 is controlled to be disengaged (S29). As a result, as described above, the cutting speed of the cutting device 3 is changed in synchronization with the moving speed (vehicle speed) of the traveling machine body 1, and the cutting device 3 is adjusted by the vehicle speed synchronization speed synchronized with the moving speed (vehicle speed) of the traveling machine body 1. Can be operated. In addition, during the harvesting operation for harvesting the cereals planted in the field, the operator can manually change the rotation speed of the harvesting shift electric motor 291 by manually operating the conveyance speed setting dial 262. For example, even in the case of a cutting operation under special conditions such as a cutting operation of cereals lying on the field, the cutting device 3 can be operated at a speed adapted to it.

  FIG. 12 is a flowchart of the cutting stop control of the cutting device 3 in step 4 of the flowchart shown in FIG. The engine-side rotation sensor 286 value and the trimming shift-side rotation sensor 287 value are read (S30). It is determined whether or not the cutting shift rotational speed from the cutting shift hydraulic motor 118 detected by the cutting shift side rotation sensor 287 is equal to the engine speed detected by the engine side rotation sensor 286 (S31). When the cutting gear shift rotation speed from the cutting gear shifting hydraulic motor 118 and the engine rotation speed are not equal (S31no), the cutting gear shifting hydraulic pump 117 is controlled to increase in speed (S32). On the other hand, when the cutting gear speed from the cutting gear shift hydraulic motor 118 is equal to the engine speed (S31yes), the reverse input clutch 110 is turned on (S33), and then the cutting gear clutch 109 is turned off (S33). S34). Then, the cutting gear shift hydraulic pump 117 is subjected to deceleration control (S35), and the cutting gear shift hydraulic pump 117 is stopped (S36), whereby the stop control of the cutting device 3 is completed.

  FIG. 13 is a flowchart of the reaping drive reverse rotation control of the reaping device 3 in step 12 of the flowchart shown in FIG. When the reverse rotation switch 270 is turned on by the operator (S37 yes), the engine side rotation sensor 286 value and the cutting speed change side rotation sensor 287 value are read (S38). It is determined whether or not the cutting shift rotational speed from the cutting shift hydraulic motor 118 detected by the cutting shift side rotation sensor 287 is equal to the engine speed detected by the engine side rotation sensor 286 (S39). When the cutting gear shift rotation speed from the cutting gear shifting hydraulic motor 118 is not equal to the engine rotation speed (S39no), the cutting gear shifting hydraulic pump 117 is controlled to increase in speed (S40). On the other hand, when the cutting gear speed from the cutting gear shift hydraulic motor 118 is equal to the engine speed (Yes in S39), the cutting gear clutch 109 is turned on (S41), and then the reverse input clutch 110 is turned off. (S42). Next, the detection value of the cutting rotation sensor 288 and the setting value of the cutting speed setting dial 262 are read (S43). It is determined whether or not the cutting rotation speed of the cutting device 3 detected by the cutting rotation sensor 288 is equal to the target reverse rotation speed set by the cutting speed setting dial 262 (S44). When the cutting speed of the reaping device 3 and the target reverse rotation speed are not equal (S44no), until the reaping rotational speed of the reaping device 3 matches the target reverse rotation speed (S44yes), the chopping shift hydraulic pump 117 is operated. The speed is increased or decreased (S45). As a result, at the target reverse rotation speed set by the cutting speed setting dial 262, the reaping device 3 rotates reversely for a preset time.

  Next, with reference to FIGS. 17, 18, and 19, the cutting transmission mechanism 116 and the cutting clutch control of the second embodiment will be described. As shown in FIGS. 17 and 18, the cutting gear shift mechanism 116 for rotating the speed adjusting rotation shaft 92 to decelerate the planetary gear mechanism 91 is used as the cutting gear shifting hydraulic pump 117 and the cutting gear shifting mechanism of the first embodiment. Instead of the hydraulic motor 118 for cutting and the hydraulic cylinder 119 for cutting speed change, an electric motor 291 for cutting speed change is provided. The output shaft of the mowing shift electric motor 291 is connected to the speed-regulating rotating shaft 92. The electromagnetic mowing shift input clutch 109 of the first embodiment is omitted, and the speed-control rotating shaft 92 is directly connected to the sun gear 93 integrally. When the speed adjusting shaft 92 is rotated at a high speed (constant rotation speed) by the electric motor 291 for cutting and shifting, the rotation speed of the carrier gear 98 becomes zero with respect to the rotation of the ring gear 95 at a constant rotation speed. Stop. That is, even if the ring gear 95 rotates at a constant rotational speed, the rotational speed of the cutting input shaft 17 becomes zero by rotating the sun gear 93 at a constant rotational speed in the reverse output direction, and the cutting apparatus 3 is stopped and maintained. It is constituted so that.

  Next, the mowing clutch control of the second embodiment will be described. FIG. 19 is a functional block diagram of the harvesting clutch control means of the harvesting device 3 and includes a work controller 282 configured by a microcomputer as in the first embodiment. As shown in FIG. 19, on the input side of the work controller 282, a threshing switch 273 that detects an operation of entering the threshing clutch 78 of the work clutch lever 44 (driving of the threshing device 5, etc.), and a cutting clutch of the work clutch lever 44. The cutting switch 274 that detects the operation of entering 78, the vehicle speed sensor 285 that detects the moving speed of the traveling machine 1, the engine-side rotation sensor 286 that detects the rotation speed of the ring gear 95, and the rotation speed of the electric motor 291 for cutting speed change. The rotation speed sensor 287 for detecting the cutting speed change, the cutting rotation sensor 288 for detecting the rotation speed of the cutting input shaft 17, and the output rotation speed (the operating speed of the cutting apparatus 3) of the electric motor 291 for cutting speed are adjusted steplessly. The cutting speed setting dial 262 and the minimum output rotation speed of the cutting shift electric motor 291 (the minimum operating speed of the cutting apparatus 3). ) And a high-speed rotation as a maximum rotation speed setting device for setting the maximum output rotation speed (maximum operating speed of the cutting device 3) of the electric motor 291 for cutting gear shifting. The setting device 267 is connected to a reverse rotation work switch 270 that allows the operator to allow the reverse rotation of the cereal conveyance device 224 or the like.

  As shown in FIG. 19, on the output side of the work controller 282, an electromagnetic reverse input clutch 110 and a speed-regulating driver 302 that operates a mowing shift electric motor 291 are connected. As a result, the mowing shift electric motor 291 can be automatically controlled to be accelerated or decelerated based on the detection result of the vehicle speed sensor 285, so that the mowing device 3 can be operated at a vehicle speed synchronized with the moving speed (vehicle speed) of the traveling machine body 1. Can operate. In addition, since the speed-changing electric motor 291 can be automatically controlled to increase or decrease based on the set value of the conveyance speed setting dial 262 as a speed change dial, the cutting operation status of uncut grain culms planted in the field The mowing device 3 can be operated at a speed according to.

  When the threshing clutch 78 is turned on by operating the work clutch lever 44, the electromagnetic reverse input clutch 110 is turned on by turning on the threshing switch 273, and the sun gear 93 is rotated via the reverse bevel gear 87. As a result, even if the ring gear 95 is rotated by the engagement of the threshing clutch 78, the planetary gear 94 is rotated in the reverse direction by the sun gear 93. Therefore, the rotation of the carrier gear 98 is held at zero, and the cutting transmission shaft 101 is stopped and maintained. .

  Therefore, even if the threshing clutch 78 is turned on and the threshing device 5 is operated, the reaping device 3 is stopped and maintained by the reaping stop maintenance control in step 2. That is, the operation performed by stopping the reaping device 3 while the threshing device 5 is operated, for example, the handling operation in which the operator supplies the reaped cereal to the feed chain 6, or the transportation of the grains in the grain tank 7 Can be loaded into other trucks. When the sun gear 93 is rotated by the reversing bevel gear 87, the cutting gear shift electric motor 291 is reversely rotated via the speed-regulating rotating shaft 92, so that the cutting gear shifting electric motor 291 is used as a generator to A battery (not shown) as a power source for starting or other electrical equipment can be charged. It is possible to prevent overdischarge of the battery.

  Next, with reference to FIG. 20 thru | or FIG. 24, the cutting work which operates the cutting device 3 is demonstrated. FIG. 20 is a flowchart of the cutting clutch control. When the cutting switch 274 is not on (S51no), when the driving flag is on (S52yes), the driving flag is reset (S53), and the cutting stop control (cutting gear shifting electric motor 291 off control) is executed. (S54), a stop flag is set (S55). On the other hand, when the cutting switch 274 is turned on by the operation of engaging the cutting clutch of the work clutch lever 44 (S51yes), when the stop flag is turned on (S56yes), the stop flag is reset (S57), and the cutting drive start control is performed. (Moving shift electric motor 291 ON control) is executed (S58), and the drive flag is set (S59). In step 56, when the stop flag is not on (S56no), and when the reverse rotation work switch is not on (S60no), the shift control of the reaping device 3 is executed (S61). In step 60, when the reverse rotation work switch is ON (S60yes), the reverse rotation work control of the reaping device 3 is executed (S62).

  FIG. 21 is a flowchart of the shift control of the reaping device 3 in step 61 of the flowchart shown in FIG. The detection value of the vehicle speed sensor 285, the detection value of the cutting rotation sensor 288, and the setting value of the cutting speed setting dial 262 are read (S63). The target cutting speed (vehicle speed synchronization speed) of the cutting device 3 is calculated from the detection value of the vehicle speed sensor 285, the detection value of the cutting rotation sensor 288, and the setting value of the cutting speed setting dial 262 (S64). It is determined whether or not the cutting speed (actual cutting speed) of the cutting apparatus 3 detected by the cutting rotation sensor 288 is equal to the target cutting speed calculated in step 54 (S65). When the cutting speed of the cutting device 3 is not equal to the target cutting speed (S65no), it is determined whether the target cutting speed is higher than the cutting speed of the cutting device 3 (S66).

  If it is determined in step 66 that the cutting speed of the cutting device 3 is smaller than the target cutting speed (S66yes), the cutting shift electric motor 291 is decelerated to reduce the rotational speed of the sun gear 93, and the cutting speed of the cutting device 3 is reduced. Speed up. As a result, the reaping device 3 is operated at the vehicle speed synchronization speed synchronized with the moving speed (vehicle speed) of the traveling machine body 1 to perform the reaping work. Further, when the cutting speed of the cutting device 3 is increased by the speed increase control in step 67, the maximum operating speed setting value of the cutting device 3 of the high-speed rotation setting device 267 is read (S68). When the cutting speed of the cutting device 3 matches the maximum operating speed setting value of the high-speed rotation setting device 267 and it is determined that the cutting device 3 is operating at high speed (S69yes), the high-speed constant rotation control of the cutting device 3 is performed. Is executed (S70). Even when the traveling speed (vehicle speed) of the traveling machine body 1 is further increased, the cutting speed of the cutting device 3 is maintained at the set value of the high-speed rotation setting device 267 by the high-speed constant rotation control (S70) of the cutting device 3. That is, since the reaping device 3 is configured to operate at a speed equal to or lower than the rotational speed set by the high speed rotation setting device 267, the reaping is performed even when the traveling speed (vehicle speed) of the traveling machine body 1 is extremely high. The mowing operation speed of the device 3 does not become too fast, the mowing device 3 can be prevented from operating in an overloaded state, and the disorder of the hauling posture of the culm or damage to the mowing device 3 can be reduced.

  On the other hand, when the cutting speed of the cutting device 3 is not smaller than the target cutting speed in the determination of step 66 (S66no), the cutting shift electric motor 291 is increased to increase the rotation speed of the sun gear 93, and the cutting device is increased. Decrease the cutting speed of 3. As a result, the reaping device 3 is operated at the vehicle speed synchronization speed synchronized with the moving speed (vehicle speed) of the traveling machine body 1 to perform the reaping work. Further, when the cutting speed of the cutting device 3 is reduced by the reduction control of the cutting speed in step 71, the minimum operating speed setting value of the cutting device 3 of the low speed rotation setting device 266 is read (S72). When the mowing device 3 operates at a low speed, the mowing speed of the mowing device 3 matches the minimum operating speed setting value of the low speed rotation setting device 266, and it is determined that the mowing device 3 is operating at a low speed (S73yes). Then, the low speed constant rotation control (S74) of the reaping device 3 is executed. Therefore, even if the moving speed (vehicle speed) of the traveling machine body 1 is further reduced, the cutting speed of the cutting device 3 is maintained at the set value of the low-speed rotation setting device 266 by the low-speed constant rotation control (S74) of the cutting device 3. . That is, since the reaping device 3 can be operated at a speed higher than the rotational speed set by the minimum rotational speed setting device 266, the reaping speed of the reaping device 3 even when the traveling speed (vehicle speed) of the traveling machine body 1 is extremely slow. Therefore, it is possible to prevent clogging of the culm during transportation and maintain the transport performance of the culm transporting device 223 of the reaping device 3.

  Based on the detection result of the vehicle speed sensor 285, the moving speed of the traveling body 1 is increased by executing the speed increase control (step 67) of the mowing apparatus 3 or the speed reduction control (step 71) of the mowing apparatus 3. The cutting speed of the cutting device 3 is changed in synchronization with the (vehicle speed), and the cutting operation of the uncut grain culm planted in the field is performed. As shown in FIG. 15, the relationship between the moving speed (vehicle speed) of the traveling machine body 1 and the cutting speed of the cutting device 3 is a pattern P1, P2 represented by a linear line, or a pattern P3 represented by a quadratic curve, It can be arbitrarily set to P4 or the like. The patterns P1, P2, P3, and P4 can be switched or selected by switching the cutting speed setting dial 262 or selecting a pattern selection switch (not shown). As shown in FIG. 15, the cutting speed of the cutting device 3 changes in proportion to the moving speed (vehicle speed) of the traveling machine body 1. As shown in FIG. 16, the cutting shift output from the cutting shift electric motor 291 changes in inverse proportion to the moving speed (vehicle speed) of the traveling machine body 1.

  FIG. 22 is a flowchart of the mowing drive start control of the mowing device 3 in step 58 of the flowchart shown in FIG. When the electromagnetic reversal input clutch 110 is engaged by turning on the threshing switch 273, the value of the engine side rotation sensor 286 and the value of the cutting shift side rotation sensor 287 are read (S75). Further, the operation mode of the electric motor 291 for cutting and shifting is changed to the drive mode (S76). Next, the reverse input clutch 110 is controlled to be disconnected (S77). As a result, as shown in the timing chart of FIG. 25, the suspension of the reaping device 3 by the reverse input clutch 110 is released, and the operating speed of the reaping device 3 can be changed (reaching shift) by the electric motor 291. Become. Therefore, as shown in FIG. 21, based on the detection result of the vehicle speed sensor 285, the cutting speed control of the cutting device 3 can be started in synchronization with the moving speed (vehicle speed) of the traveling machine body 1, and the moving speed (vehicle speed) of the traveling machine body 1 can be started. The cutting speed of the cutting device 3 can be maintained at the vehicle speed synchronization speed synchronized with the above. In addition, during the harvesting operation for harvesting the cereals planted in the field, the operator can manually change the rotation speed of the harvesting shift electric motor 291 by manually operating the conveyance speed setting dial 262. For example, even in the case of a cutting operation under special conditions such as a cutting operation of cereals lying on the field, the cutting device 3 can be operated at a speed adapted to it.

  FIG. 23 is a flowchart of the cutting stop control of the cutting apparatus 3 in step 54 of the flowchart shown in FIG. The engine side rotation sensor 286 value and the trimming shift side rotation sensor 287 value are read (S80). It is determined whether or not the cutting speed of rotation from the electric motor 291 for cutting speed detected by the cutting speed side rotation sensor 287 is equal to the engine speed detected by the engine side rotation sensor 286 (S81). When the cutting gear shift rotation speed from the cutting gear shift electric motor 291 and the engine rotation speed are not equal (S81no), the cutting gear shift electric motor 291 is controlled to increase in speed (S82). On the other hand, when the rotational speed of the cutting gear from the electric motor 291 for cutting and shifting is equal to the engine speed (S81yes), the reverse input clutch 110 is turned on and controlled (S83), and then the operating mode of the electric motor 291 for cutting and shifting is operated. Is changed to the charging mode (S84). As a result, the mowing shift electric motor 291 can be used as a generator. The cutting shift electric motor 291 is driven by the output of the engine 14 as a generator, and the electric power from the cutting shift electric motor 291 can be charged and stored in a secondary battery such as a starting battery for the engine 14. The battery can be prevented from being overdischarged to improve durability. For example, the secondary battery such as the battery can be used for various purposes as a power source for an electric motor used for opening and closing the threshing cover, moving the discharge auger 8, or other electric devices.

  FIG. 24 is a flowchart of the mowing drive reverse rotation control of the mowing device 3 in step 62 of the flowchart shown in FIG. When the reverse rotation switch 270 is turned on by the operator (S87yes), the engine side rotation sensor 286 value and the cutting speed change side rotation sensor 287 value are read (S88). It is determined whether or not the cutting speed of rotation from the electric motor 291 for cutting speed detected by the cutting speed side rotation sensor 287 is equal to the engine speed detected by the engine side speed sensor 286 (S89). When the cutting gear shift rotation speed from the cutting gear shift electric motor 291 and the engine rotation speed are not equal (S89no), the cutting gear shift electric motor 291 is controlled to increase in speed (S90). On the other hand, when the cutting gear shift rotational speed from the cutting gear shift electric motor 291 is equal to the engine rotational speed (Yes in S89), the reverse input clutch 110 is controlled to be disconnected (S91). Next, the detection value of the cutting rotation sensor 288 and the setting value of the cutting speed setting dial 262 are read (S92). It is determined whether or not the cutting rotation speed of the cutting device 3 detected by the cutting rotation sensor 288 is equal to the target reverse rotation speed set by the cutting speed setting dial 262 (S93). When the cutting rotation speed of the reaping device 3 and the target reverse rotation speed are not equal (S93no), until the reaping rotational speed of the reaping device 3 coincides with the target reverse rotation speed (S93yes), the electric motor 291 for cutting gear shifting is used. The speed is increased or decreased (S94). As a result, at the target reverse rotation speed set by the cutting speed setting dial 262, the reaping device 3 rotates reversely for a preset time.

  That is, by turning on the reverse rotation work switch 270, the reaping device 3 can be reversely rotated at a low speed for a predetermined period of time that is initially set. In the maintenance operation of the reaping device 3 or the operation of removing the clogged culm, the reaping device 3 is set to the maximum number of rotations of the electric motor 291 for reaping shift by manual operation of the conveyance speed setting dial 262. Can be reversely rotated at a low speed to change the chain of the culm transport device 223, or to remove the culm clogged with the culm transport device 223 or the like. Since the reversing operation time of the reaping device 3 when the reversing operation switch 270 is turned on is limited, the reaping device 3 is prevented from performing a reversing operation for a long time regardless of the on operation time of the reversing operation switch 270. It is possible to prevent a malfunction from occurring in the reaping device 3 or the like due to the reverse rotation for a long time.

  In addition, in the power transmission path between the cutting transmission shaft 101 and the cutting input shaft 17, a cutting clutch capable of turning on and off the cutting power can be provided. The rotation from the ring gear 95 and the rotation from the electric motor 291 for cutting speed change keep the cutting clutch open until the planetary gear 94 is idle. When the planetary gear 94 is idle, the cutting clutch is engaged and the cutting clutch is engaged. You may control the rotation speed of the cutting input shaft 17 by rotation control of the electric motor 291 for transmission.

  In the above embodiment, as shown in FIG. 6 or FIG. 17, the ring gear 95 is connected to the engine 14, the sun gear 93 is connected to the governing rotary shaft 92, and the carrier gear 98 is connected to the cutting input shaft 17. It is not limited to the structure. Needless to say, the engine 14, the governing rotary shaft 92, the cutting input shaft 17, and the sun gear 93, the ring gear 95, and the carrier gear 98 can be combined in a plurality of combinations. For example, the sun gear 93 may be connected to the engine 14, the ring gear 95 may be connected to the governing rotary shaft 92, and the carrier gear 98 may be connected to the cutting input shaft 17. Alternatively, the sun gear 93 may be connected to the engine 14, the carrier gear 98 may be connected to the governing rotary shaft 92, and the ring gear 95 may be connected to the cutting input shaft 17.

  As is clear from the above description and FIGS. 1, 6, and 8, the traveling machine body 1 including the traveling unit 2 that is operated by the engine 14, and the cutting blade device that cuts the stock of the cereal planted in the field. 222, a culm conveying device 224 that conveys the cereal cocoon whose stock has been cut by the cutting blade device 222, and a vehicle speed sensor 285 that detects the moving speed of the traveling machine body, and outputs a constant rotational output from the engine 14. In a combine configured to transmit to the cutting blade device 222 or the culm transport device 224 after changing to the vehicle speed synchronization speed, the planet that transmits a constant rotational output from the engine 14 to the culm transport device 224 or the like. A gear mechanism 91, and a cutting shift hydraulic motor 118 as a cutting shift actuator that decelerates the output of the planetary gear mechanism 91 to the grain feeder 224 and the like. Based on the output result, the planetary gear mechanism 91 is configured to decelerate by the mowing shift hydraulic motor 118. Therefore, the conventional mowing drive mechanism such as the mowing speed change mechanism and the mowing constant rotation mechanism is provided. Compared to the structure, the cutting drive structure that transmits the rotation of the engine 14 to the grain feeder 224 and the like can be easily configured, and the manufacturing cost of the cutting drive mechanism can be easily reduced. Further, when the cereal conveyor device 224 or the like is driven at a high speed, the rotational output from the engine 14 is transmitted to the cereal conveyor device 224 or the like via the planetary gear mechanism 91, so that the chopping drive is driven by the hydraulic continuously variable transmission. Compared to the conventional structure constituting the mechanism, the mowing drive mechanism can be constructed at low cost and the transmission efficiency can be improved. In particular, the higher the cutting speed, the better the transmission efficiency, so that high-speed workability can be improved. Furthermore, since not only the forward movement of the traveling machine body 1 but also the backward movement, the reaping device 3 such as the grain feeder 224 can be easily operated in the same way as the forward movement. Conversion workability can be improved.

  As apparent from the above description and FIGS. 8 and 10, when the traveling speed of the traveling machine body 1 is within the predetermined range, the planetary gear mechanism 91 is moved by the cutting shift hydraulic motor 118 based on the detection result of the vehicle speed sensor 91. While configured to decelerate, when the traveling speed of the traveling machine body 1 is greater than or equal to a predetermined range, the rotational output of the cutting shift hydraulic motor 118 is maintained at a constant high speed, and the traveling speed of the traveling machine body 1 is predetermined. Since the rotational output of the mowing shift hydraulic motor 118 is maintained at a constant low speed or stopped at a lower speed than the range, movement of the traveling machine body 1 is controlled by the mowing shift hydraulic motor 118. While the reaping device 3 such as the grain feeder 224 can be easily operated at the vehicle speed synchronization speed related to the speed, it retains functions such as reaping speed change and reaping constant rotation. , It is possible to improve the workability reaping.

  As apparent from the above description and FIGS. 8 and 13, the reverse operation switch 270 that allows the reverse rotation of the grain transporter 224 and the like is provided, and the planetary gear mechanism 91 is based on the reverse rotation permission operation of the reverse operation switch 270. The output of the planetary gear mechanism 91 to the grain feeder 224 and the like is reversed at a low speed when the control output for cutting shift of the hydraulic motor 118 for cutting shift is about the maximum rotation speed. For example, while the traveling machine body 1 is stopped at a fixed place, the cereal conveyor device 224 and the like can be reversely rotated at a low speed, and maintenance workability of the cereal conveyor device 224 or the cereal conveyor device 224 is clogged. The workability of removing cereals can be improved. In addition, when exchanging a part of the long chain of the grain feeder 224, the chain connecting portion and the like can be easily moved to a place where the separation work is easy to perform. The maintenance workability can be improved.

  As is clear from the above description and FIGS. 5 and 6, the electromagnetic cutting gear shift input clutch 109 as a cutting gear shifting input clutch 109 that transmits the output of the cutting gear shifting hydraulic motor 118 to the planetary gear mechanism 91, The reverse rotation bevel gear 87 as a reverse rotation input mechanism capable of maintaining the output rotation of the planetary gear mechanism 91 at substantially zero with respect to the constant rotation output of the engine 14 and the reverse rotation input transmitted from the reverse rotation bevel gear 87 to the planetary gear mechanism 91 are turned on and off. The reverse rotation input transmitted from the reverse rotation bevel gear 87 to the planetary gear mechanism 91 via the electromagnetic reverse rotation input clutch 110 can maintain the output of the planetary gear mechanism 91 at zero rotation. Therefore, the electromagnetic mowing shift input clutch 109 is turned off and the electromagnetic reverse input clutch 110 is engaged. By the movement, to stop the shifting hydraulic motor 118 reaper, and can maintain the output of the planetary gear mechanism 91 to zero rotation. In the structure of FIG. 6, the mowing shift hydraulic motor 118 can be stopped simply by engaging and operating the electromagnetic reverse input clutch 110 in conjunction with the operation of engaging the threshing clutch 78. The planetary gear mechanism 91 on the downstream side of transmission can be stopped by turning off the threshing clutch 78. For example, when the grain feeder 224 or the like is stopped and maintained for a long time during the movement between fields, it is not necessary to operate the mowing shift hydraulic motor 118 at a high speed for a long time. Thus, the cutting and shifting hydraulic motor 118 can be simply configured.

  As is clear from the above description and FIGS. 17 and 19, the output of the planetary gear mechanism 91 is substantially zero with respect to the electric motor 291 for the mowing shift that forms the actuator for the mowing gear and the substantially constant rotational input of the engine 14. A reverse rotation bevel gear 87 as a reverse rotation input mechanism that can be maintained at the same time, and an electromagnetic reverse rotation input clutch 110 that turns on and off the reverse rotation input transmitted from the reverse rotation bevel gear 87 to the planetary gear mechanism 91. The reverse rotation input transmitted to the planetary gear mechanism 91 via the input clutch 110 is configured so that the output rotation of the planetary gear mechanism 91 can be maintained at substantially zero. Thus, the output of the planetary gear mechanism 91 can be maintained at zero rotation. Further, when the grain feeder 224 or the like is stopped and maintained for a long time during the movement between the fields, the harvesting shift electric motor 291 can be used as a generator. It can be stored in a secondary battery or the like.

It is a side view of the combine for 6-saw cutting of 1st Embodiment of this invention. It is the same top view. It is side surface explanatory drawing of a cutting blade apparatus and a grain haul conveying apparatus. It is a plane explanatory view of a cutting blade device and a cereal conveyance device. It is a drive system diagram of a combine. FIG. 3 is a drive system diagram in which a hydraulic continuously variable transmission (hydraulic pump and hydraulic motor) is provided as a cutting gear shift actuator. It is a block diagram of the drive system shown in FIG. It is a functional block diagram of a drive control circuit of a reaping device including a cutting blade device and a culm conveying device. It is a flowchart of mowing clutch control. It is a flowchart of the cutting shift control. It is a flowchart of cutting drive start control. It is a flowchart of cutting stop control. It is a flowchart of cutting drive reverse rotation control. It is a timing chart of cutting drive control and cutting clutch switching. It is an output diagram which shows the relationship between a vehicle speed and a cutting speed. It is an output diagram which shows the relationship between a vehicle speed and a cutting speed change output. It is a drive system figure showing a 2nd embodiment of the present invention which provided a mowing shift electric motor as a mowing shift actuator. It is a block diagram of the drive system shown in FIG. It is a functional block diagram of the drive control circuit of the reaping device showing the second embodiment of the present invention. It is a flowchart of mowing clutch control. It is a flowchart of the cutting shift control. It is a flowchart of cutting drive start control. It is a flowchart of cutting stop control. It is a flowchart of cutting drive reverse rotation control. It is a timing chart of cutting drive control and cutting clutch switching.

Explanation of symbols

1 traveling machine body 2 traveling crawler (traveling section)
14 engine 87 reverse bevel gear (reverse rotation input mechanism)
91 Planetary gear mechanism 109 Input clutch for electromagnetic cutting gear shift 110 Input clutch for reverse rotation 118 Hydraulic motor for cutting gear shifting (trigger gear shifting actuator)
222 Cutting blade device 224 Grain feeder 270 Reverse rotation switch 285 Vehicle speed sensor 291 Electric motor for cutting gear shift (Actuator for cutting gear shifting)

Claims (5)

A traveling machine body provided with a traveling unit that is operated by an engine, a cutting blade device that cuts the stock of a cereal planted in a field, and a cereal that transports the cereal that has been cut by the cutting blade device. A conveyor device and a vehicle speed sensor for detecting the moving speed of the traveling machine body are transmitted, and after the constant rotational output from the engine is changed to a vehicle speed synchronization speed, it is transmitted to the cutting blade device or the grain feeder. In the combine configured as follows,
A planetary gear mechanism that transmits a constant rotational output from the engine to the grain feeder and the like, and a cutting gear shift actuator that decelerates the output of the planetary gear mechanism to the grain feeder and the like, the vehicle speed sensor The combine configured to decelerate the planetary gear mechanism by the cutting shift actuator based on a detection result.   When the traveling speed of the traveling machine body is within a predetermined range, the planetary gear mechanism is configured to decelerate by the cutting gear shifting actuator based on the detection result of the vehicle speed sensor. The rotation output of the cutting gear shift actuator is maintained at a constant low speed or stopped when it is above a predetermined range, and when the moving speed of the traveling machine body is below the predetermined range except for the stop, The combine according to claim 1, wherein the rotation output is maintained at a constant high speed.   A reverse rotation work switch that allows reverse rotation of the cereal conveying device or the like, and based on the reverse rotation permission operation of the reverse rotation work switch, the cutting shift control output of the cutting gear shift actuator for the planetary gear mechanism is near the maximum rotation 2. The combine according to claim 1, wherein an output of the planetary gear mechanism with respect to the cereal conveying device or the like is reversed at a low speed when the rotation speed is.   A cutting shift input clutch for transmitting the output of the cutting gear shift actuator to the planetary gear mechanism, and a reverse rotation input capable of maintaining the output rotation of the planetary gear mechanism at substantially zero with respect to a constant rotation output of the engine. And a reverse input clutch that turns on and off the reverse rotation input transmitted from the reverse rotation input mechanism to the planetary gear mechanism, and transmits the reverse rotation input mechanism to the planetary gear mechanism via the reverse rotation input clutch. The combine according to claim 1, wherein the output rotation of the planetary gear mechanism can be maintained at zero rotation by reverse rotation input. An electric motor for cutting gear that forms the actuator for cutting gear, a reverse rotation input mechanism capable of maintaining the output of the planetary gear mechanism at substantially zero with respect to a substantially constant rotation input of the engine, and the reverse rotation input mechanism A reverse input clutch for turning on and off a reverse rotation input transmitted to the planetary gear mechanism, and the planetary gear by a reverse rotation input transmitted from the reverse rotation input mechanism to the planetary gear mechanism via the reverse input clutch. The combine according to claim 1, wherein the output rotation of the mechanism can be maintained at substantially zero.

Images