WO2011114769A1 - 作業車両及びその例としてのコンバイン - Google Patents

作業車両及びその例としてのコンバイン Download PDF

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Publication number
WO2011114769A1
WO2011114769A1 PCT/JP2011/050982 JP2011050982W WO2011114769A1 WO 2011114769 A1 WO2011114769 A1 WO 2011114769A1 JP 2011050982 W JP2011050982 W JP 2011050982W WO 2011114769 A1 WO2011114769 A1 WO 2011114769A1
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WO
WIPO (PCT)
Prior art keywords
hydraulic
shaft
oil
transmission
case
Prior art date
Application number
PCT/JP2011/050982
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
康一 梶原
晃司 清岡
道雄 塚本
Original Assignee
ヤンマー株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2010057433A external-priority patent/JP5437865B2/ja
Priority claimed from JP2010057434A external-priority patent/JP5437866B2/ja
Application filed by ヤンマー株式会社 filed Critical ヤンマー株式会社
Priority to KR1020117014786A priority Critical patent/KR101701945B1/ko
Priority to CN201180000859.7A priority patent/CN102292233B/zh
Publication of WO2011114769A1 publication Critical patent/WO2011114769A1/ja

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/28—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of power take-off
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D69/00—Driving mechanisms or parts thereof for harvesters or mowers
    • A01D69/03—Driving mechanisms or parts thereof for harvesters or mowers fluid
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/10—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of fluid gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K20/00—Arrangement or mounting of change-speed gearing control devices in vehicles
    • B60K20/02—Arrangement or mounting of change-speed gearing control devices in vehicles of initiating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0408—Exchange, draining or filling of transmission lubricant
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/20—Off-Road Vehicles
    • B60Y2200/22—Agricultural vehicles
    • B60Y2200/222—Harvesters
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/20—Off-Road Vehicles
    • B60Y2200/25—Track vehicles

Definitions

  • the present invention relates to a work vehicle such as a farm work machine or a special work machine, particularly to a combine.
  • Patent Document 1 a technology for electrically controlling a hydraulic continuously variable transmission for shifting engine power in a combine as a work vehicle is known (see Patent Document 1).
  • the combine described in Patent Document 1 is a hydraulic continuously variable transmission that changes the power of an engine, a trunnion shaft (operation shaft) for performing a shift adjustment operation of the hydraulic continuously variable transmission, and an electric that rotates the trunnion shaft. Actuator. Then, the shift output of the hydraulic continuously variable transmission is adjusted by rotating the trunnion shaft by driving the electric actuator according to the operation amount of the main shift lever or the like, and the straight forward and the turn of the combine are executed. It is configured. If an error or failure occurs in the operation amount detection sensor that detects the operation amount of the main transmission lever, etc., the hydraulic continuously variable transmission is operated using another switch other than the main transmission lever, etc., and the combine is reliably stopped. It is configured to let you.
  • the hydraulic continuously variable transmission is built in the hydraulic transmission case.
  • Engine power is transmitted to the left and right traveling crawlers via a hydraulic transmission case and a transmission case.
  • the engine is disposed below the driving unit on the right side in the traveling direction of the traveling machine body.
  • a mission case is placed in front of the engine.
  • a hydraulic transmission case with a built-in hydraulic continuously variable transmission is attached to a side surface (upper left side surface) opposite to the driver's seat in the upper part of the transmission case.
  • the mission case also functions as a hydraulic oil tank, and an oil filler opening is provided on the upper surface side of the mission case.
  • an oil inspection window for visually confirming the amount of hydraulic oil in the mission case from the outside is provided.
  • the oil supply port on the upper surface side of the mission case is manually supplied with a funnel or the like.
  • Patent Document 1 does not take into account, for example, a case where an abnormality occurs in a control means (controller) that drives an electric actuator, for example. Since there is no choice but to stop the traveling machine body, for example, there has been a problem that limp home operation (degeneration operation) that allows the combine to escape only from the field cannot be performed.
  • the present invention has a technical problem to provide a work vehicle that solves these problems and an example combine.
  • the invention according to claim 1 is directed to a hydraulic transmission case incorporating a hydraulic continuously variable transmission for shifting engine power, wherein the transmission output of the hydraulic continuously variable transmission is transmitted to the left and right traveling units.
  • a work vehicle attached to one side upper part of the transmission case for transmitting, to the other side upper part of the transmission case, an input pulley for receiving power from the engine, and a speed change output from the hydraulic continuously variable transmission.
  • a PTO pulley to be driven, and an oil supply port for supplying hydraulic oil is provided in front of the PTO pulley on the other side surface of the transmission case.
  • an oil inspection window is provided at a position below the fuel filler opening and lower than the PTO pulley
  • a suction filter is provided behind the oil inspection window and at a position lower than the PTO pulley.
  • the front part of the traveling machine body can be opened and rotated laterally outward about the vertical axis on the left side of the front part of the traveling machine body.
  • a cutting device is provided, and is configured to expose the oil supply port and the oil detection window on the left side surface of the transmission case in a state where the cutting device is opened and rotated laterally outward. That's it.
  • the work vehicle according to the first aspect, wherein the linear operation tool for changing the straight traveling speed of the traveling machine body, the turning operation tool for changing the traveling direction of the traveling machine body, An electric actuator for adjusting a shift output of the step transmission, and a control means for driving the electric actuator in accordance with an operation amount of each of the operating tools.
  • An emergency manual operating tool for manually operating the output separately from the electric actuator is provided.
  • the emergency manual operation tool when the shift output is adjusted by the electric actuator, operates in conjunction with the driving of the electric actuator. It is said that it is comprised.
  • the hydraulic continuously variable transmission an adjustment cylinder that adjusts a shift of the hydraulic pump, and the adjustment cylinder that reciprocates.
  • An electro-hydraulic valve as an electric actuator and a proportional control valve for switching the electro-hydraulic valve are provided.
  • the spool of the electro-hydraulic valve and the proportional control spool of the proportional control valve are operated by a spool.
  • An operation shaft as the emergency manual operation tool that can be manually rotated on the other end side of the spool operation arm is related to interlocking movement via a linkage pin provided on one end side of the arm. And the linkage pin rotates the spool operation arm about the operation shaft as a rotation center in conjunction with the operations of the two spools.
  • the operating shaft is that is configured to rotate.
  • the hydraulic continuously variable transmission, the adjustment cylinder, and a hydraulic shift case incorporating the electromagnetic hydraulic valve are provided, the proportional control valve, A proportional control housing having a spool operation arm and the operation shaft is detachably attached to the outer surface of the hydraulic transmission case so that the spool of the electromagnetic hydraulic valve and the proportional control spool of the proportional control valve are brought close to each other. It is that.
  • the hydraulic transmission case incorporating the hydraulic continuously variable transmission for shifting the engine power transmits the shift output of the hydraulic continuously variable transmission to one side of the transmission case.
  • An input pulley that receives power from the engine and a PTO pulley that is driven by a shift output from the hydraulic continuously variable transmission are disposed on the other side upper portion of the transmission case.
  • an oil supply port for supplying hydraulic oil is provided in front of the PTO pulley. Therefore, when supplying oil to the transmission case, for example, heavy oil There is no need to lift the oil can into the upper part of the transmission case, and the refueling work is simplified and the burden on the operator is low in the refueling work. The effect of requiring Te.
  • the oil supply port is located at a midway height position in the vertical direction of the transmission case that also serves as a hydraulic oil tank, the oil can only be supplied up to just below the oil supply port. Accordingly, it is possible to prevent oil from being excessively supplied into the mission case more than necessary, and to reliably suppress the possibility that the power loss in the mission case increases due to the excessive amount of hydraulic oil.
  • the upper side in the transmission case is not filled with hydraulic oil, the hydraulic oil easily flows in the transmission case, and the surface area of the portion of the transmission case that is not in contact with the hydraulic oil is conventional. It becomes much wider than. Due to the fluidity of the hydraulic fluid and the heat radiation effect of the portion not in contact with the hydraulic fluid, the temperature rise of the hydraulic fluid as a whole can be suppressed.
  • an oil inspection window is provided at a position below the oil supply port and lower than the PTO pulley, so that the oil detection window has the same side surface as the oil supply port. While looking at the oil inspection window, the hydraulic oil can be supplied into the transmission case from the oil supply port (the oil inspection window can be easily confirmed during the oil supply). Therefore, the refueling operation becomes much easier than before. Further, on one side of the transmission case, a suction filter is provided at a position behind the oil detection window and lower than the PTO pulley, so that the oil detection window and the suction filter are arranged inside the transmission case.
  • the oil detection window and the suction filter can be efficiently arranged using the internal space below the oil supply port in the mission case, and the hydraulic oil in the mission case can be arranged from the oil detection window.
  • the presence of the suction filter does not get in the way when checking the quantity.
  • the front part of the traveling machine body is provided with a reaping device that can be opened and rotated laterally outward about the vertical axis on the left side of the front part of the traveling machine body.
  • the reaping device is configured to expose the oil supply port and the oil inspection window on the left side surface of the transmission case in a state where the reaping device is opened and rotated laterally outward. If the is opened and rotated laterally outward, a wide working space is created around the oil supply port and the oil inspection window in the mission case. For this reason, there is an effect that maintenance workability for the mission case such as pre-use inspection and refueling work is remarkably improved.
  • the fourth aspect of the present invention even if an electrical trouble such as an abnormality occurs in the control means, for example, if the emergency manual operation tool is manually operated, the straight operation tool or the turning operation is performed. In a state where the tool does not work, for example, a limp home operation (degenerate operation) that allows the combine to escape only from the field can be executed. Therefore, there is an effect that the options for dealing with an emergency situation increase in the combine, and the handling of the combine is improved.
  • a limp home operation degenerate operation
  • the operation state of the hydraulic continuously variable transmission can be easily visually recognized from the operation of the emergency manual operating tool.
  • a mechanical connection structure is not provided between the linear operation tool and the turning operation tool and the hydraulic continuously variable transmission, and the space between them is electrically controlled, the linear operation tool and the turning operation are provided. There is an effect that it is easy to find an operation trouble related to the tool and the hydraulic continuously variable transmission at an early stage.
  • the said hydraulic continuously variable transmission, the adjustment cylinder which carries out speed adjustment of the said hydraulic pump, the electrohydraulic valve as said electric actuator which reciprocates the said adjustment cylinder, and the said electrohydraulic type A proportional control valve for switching the valve, and the spool of the electrohydraulic valve and the proportional control spool of the proportional control valve are moved together via a linkage pin provided on one end side of the spool operation arm.
  • the other end of the spool operation arm is provided with an operation shaft as the emergency manual operation tool that can be manually rotated, and in conjunction with the operations of both spools.
  • the linkage pin is configured to rotate the operation shaft by rotating the spool operation arm with the operation shaft as a rotation center.
  • the hydraulic continuously variable transmission, the adjustment cylinder, and a hydraulic transmission case incorporating the electromagnetic hydraulic valve are provided, and the proportional control valve, the spool operation arm, and the operation shaft are provided. Since the proportional control housing is detachably attached to the outer surface of the hydraulic transmission case so that the spool of the electromagnetic hydraulic valve and the proportional control spool of the proportional control valve are close to each other, the adjusting cylinder and the The proportional control housing can be attached to and detached from the hydraulic transmission case in a state where an electromagnetic hydraulic valve is assembled to the hydraulic transmission case. That is, since the hydraulic transmission case and the proportional control housing are divided into units, the number of parts during assembly can be reduced, and assembly workability and maintenance workability of the proportional control housing with respect to the hydraulic transmission case can be reduced. Can be improved.
  • the left side in the forward direction of the traveling machine body 1 is simply referred to as the left side
  • the right side in the forward direction is also simply referred to as the right side.
  • the combine includes a traveling machine body 1 supported by a pair of left and right traveling crawlers 2 as traveling portions.
  • a six-row mowing device 3 that takes in while harvesting cereals is cut by a single-acting lifting / lowering hydraulic cylinder 4 as a lifting / lowering actuator. The details are described later).
  • a threshing device 5 having a feed chain 6 and a grain tank 7 for storing the grains taken out from the threshing device 5 are mounted on the traveling machine body 1 side by side.
  • the threshing device 5 is disposed on the left side in the forward direction of the traveling machine body 1, and the grain tank 7 is disposed 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 throwing port 9 of the discharge auger 8 to a truck bed or a container. Yes.
  • An operation cabin 10 is provided on the right side of the cutting device 3 and on the front side of the grain tank 7.
  • a steering handle 11 as a turning operation tool, a driving seat 12, a main transmission lever 43 as a straight operation tool, an auxiliary transmission switch 44, a work clutch lever for turning on and off a threshing clutch and a cutting clutch. 45 are arranged.
  • the driving cabin 10 has a step column 357 (see FIGS. 6 to 9) on which the operator gets on, a handle column 46 provided with the steering handle 11, a lever column provided with the levers 43 and 45, the switch 44 and the like. 47 are arranged.
  • An engine 14 as a power source is disposed below the driver seat 12 in the traveling machine body 1.
  • left and right track frames 21 are arranged on the lower surface side of the traveling machine body 1.
  • the track frame 21 includes a drive sprocket 22 that transmits the power of the engine 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 for holding 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 track roller 24 supports the grounding side of the traveling crawler 2
  • the intermediate roller 25 supports the non-traveling crawler 2. Support the ground side.
  • a clipper type cutting blade device 222 that cuts the stock of uncut grain culm planted in the field.
  • a grain stalk elevating device 223 for 6 ridges that erects uncut cereals planted in the field is arranged.
  • a culm conveying device 224 that conveys the chopped culm cut by the cutting blade device 222 is disposed.
  • a weeding body 225 for 6 ridges for weeding the uncut cereals planted in the field is projected. While the traveling crawler 2 is driven by the engine 14 to move in the field, the uncut cereal grains planted in the field are continuously cut by the cutting device 3.
  • the cutting frame 221 includes a cutting input case 16 rotatably supported by a bearing stand 15 on the left side of the front portion of the traveling machine body 1, and extends forward from the cutting input case 16.
  • the vertical transmission case 18, the horizontal transmission case 19 extending in the left-right direction on the front end side of the vertical transmission case 18, and the six weeding frame 20 connected to the horizontal transmission case 19.
  • On the front end side of the weeding frame 20, six weeding bodies 225 are arranged.
  • a cutting input shaft 17 to which power from the engine 14 is transmitted is incorporated in a cutting input case 16 that is horizontally mounted in the horizontal direction of the machine body.
  • the cereal haul raising device 223 has an erecting case 129 for 6 lanes having a plurality of erecting tines 128 for erecting the uncut cereal halves divided by the weed board 225.
  • the cereal masher 224 includes a right star wheel 130R and a right rake belt 131R that squeeze the stock side of the cereals for the two right limbs introduced from the two right erection cases 129, and the two left erection cases.
  • the left star wheel 130L and the left rake belt 131L which rake the stock side of the left side 2 grain cereals introduced from 129, and the center 2 part cereal stocks introduced from the central two raising cases 129 It has a central star wheel 130C and a central scoring belt 131C that scrape the original side.
  • the cutting blade device 222 is composed of six cereal grains that have been scraped by the right star wheel 130R and the right take-up belt 131R, the left star wheel 130L and the left take-up belt 131L, the center star wheel 130C and the center take-up belt 131C. It has clipper-shaped left and right cutting blades 132 for cutting the stock.
  • the grain feeder 224 includes a right stock former transport chain 133R that transports backward the stock side of the two right-handed harvested grain straw that has been raked by the right star wheel 130R and the right rake belt 131R, A left stock former transport chain 133L that joins the stock side of the two left-handed harvested cereal rice cakes that have been scraped by the star wheel 130L and the left scooping belt 131L to the transport end of the right stock transport chain 133R, and the central star A central stock former transport chain 133C that transports the stock base side of the harvested cereal rice cake for the two central strips, which have been scraped by the foil 130C and the central scoop belt 131C, and joins it in the middle of the transport of the right stock transport chain 133R.
  • the left and right and center stock transport chains 133R, 133L, and 133C the stock side of the harvested cereal grains for 6 ridges is joined to the transport end of the right stock transport chain 133R.
  • the cereal feeder 224 is fed from a vertical conveyor chain 134 as a cereal conveyor means that inherits the stock side of the harvested cereals for six strips from the right stocker transport chain 133R, and fed from the transport terminal end of the vertical conveyor chain 134.
  • An auxiliary stock source transport chain 135 serving as an auxiliary transport means for transporting the stock source side of the harvested cereals for 6 strips is provided at the transport start end of the chain 6. From the vertical conveyance chain 134, the stock side of the harvested cereals for 6 ridges is conveyed to the conveyance start end portion of the feed chain 6 through the auxiliary stock source conveyance chain 135.
  • the grain culm transporting device 224 is transported by the right stalk transporting tine 137R that transports the tip of the harvested cereal cocoons for the two right-hand ridges transported by the right stock transporting chain 133R and the left stock transporting chain 133L.
  • the left-hand tip transport tine 137L that transports the tip of the harvested cereals of the two left-hand ridges backward and merges in the middle of the transport of the right-hand tip transport tine 137R, and the center 2 transported by the central stock transport chain 133C It has a central tip transport tine 137C that transports the tip side of the trimmed grain cereals backward and joins it in the middle of the transport of the right tip transport tine 137R.
  • the tip side of the harvested cereal grains for the six strips harvested by the reaping device 3 is conveyed into the handling cylinder 226 installation chamber of the threshing device 5.
  • the reaping device 3 is supported by the bearing stand 15 on the left side of the front of the traveling machine body 1 for the convenience of maintenance of the internal devices 222 to 224, the engine 14, the transmission case 88, and the like.
  • the vertical axis 300 is configured to be openable and turnable laterally outward (openable and closable in the lateral direction).
  • the bearing stand 15 has a substantially trapezoidal shape in a side view and is erected and fixed to the left side of the front portion of the traveling machine body 1 and is horizontally mounted between the upper ends of the pair of left and right side frame bases 301L and 301R and the left and right side frame bases 301L and 301R.
  • a square pipe-like horizontal rail frame 302 is formed in a substantially portal shape when viewed from the front.
  • a cast iron vertical axis 300 is pivotally supported on the left frame 301L so that it cannot be removed and can rotate about the vertical axis.
  • a portion of the vertical axis 300 that protrudes upward from the left frame 301L is a bearing portion 303 that pivotally supports the proximal end side of the cutting input case 16, which is a horizontal axis, so as to be rotatable about the horizontal axis.
  • the bearing portion 303 has a lower main body portion 303a that is formed in the upper half of the vertical axis 300 and is formed in a front oblique upper upward half shape, and a rear oblique lower downward opening half shape that is bolted to the lower main body portion 303a from the front. It is comprised by the upper cover part 303b.
  • the front end side of the crosspiece frame 302 extends further to the center side of the machine body from the right frame base 301R, and is fixed to the upper end part of the columnar frame 290 standing on the front center side of the traveling machine body 1 by welding or the like.
  • a holder body 306 made of cast iron or the like that pivotally supports the distal end side of the cutting input case 16 so as to be rotatable around its horizontal axis center on the mounting seat plate 305 fixed to the upper surface on the distal end side of the horizontal rail frame 302. Is provided.
  • the holder body 306 can be rotated forward and backward via a front diagonally upward opening half-shaped lower holder bearing portion 306a bolted onto the mounting seat plate 305, and a lateral pin shaft 307 to the lower holder bearing portion 306a.
  • the upper holder bearing portion 306b is attached.
  • the upper holder bearing portion 306b is pivoted forward (closed and pivoted) to cover the lower holder bearing portion 306a, and the upper holder bearing portion 306b is fixed to the lower holder bearing portion 306a in a state where the tip end side of the cutting input case 16 is sandwiched.
  • the front end side of the cutting input case 16 is pivotally supported by the holder body 306 in a state in which the cutting input case 16 can be rotated around its horizontal axis.
  • the reaping device 3 is held in a closed posture located in front of the traveling machine body 1 (see the solid line state in FIG. 18).
  • the gripping of the cutting input case 16 on the tip side is released, and the cutting device 3 is centered on the vertical axis 300. It will be in a state in which it can be opened laterally and rotated. If the reaping device 3 is rotated toward the laterally outer side (left outer side) of the traveling machine body 1 in this state, the reaping device 3 assumes an open posture with the front surface of the traveling machine body 1 opened (two points in FIG. 18). (See chain line status). In this case, the reaping device 3 is supported in a cantilevered state on the longitudinal axis 300.
  • the proximal end side of the cutting input shaft 17 incorporated in the cutting input case 16 in a concentric posture protrudes outward (leftward) from the proximal end side of the cutting input case 16;
  • a cutting input pulley 309 is fixed to the protruding end.
  • a cutting drive belt 125 is wound around the cutting input pulley 309 and the cutting drive pulley 124 of the cutting drive shaft 102 in the counter gear case 89.
  • power from the engine 14 via the counter gear case 89 is transmitted from the cutting drive shaft 102 to the cutting input shaft 17 in the cutting input case 16 via the pulleys 124 and 309 and the belt 125 transmission system. Then, power is transmitted from the cutting input shaft 17 to each of the devices 222 to 224 of the cutting device 3.
  • an elevating hydraulic cylinder 4 is disposed as an elevating actuator that moves the reaping device 3 up and down.
  • An end portion on the cylinder side of the lifting hydraulic cylinder 4 is pivotally attached to the front portion of the traveling machine body 1 via a pivot pin shaft (not shown) that is horizontally oriented.
  • the rod-side end of the lifting hydraulic cylinder 4 is detachably connected to the longitudinal middle portion of the vertical transmission case 18 via a mounting bracket 310.
  • the rod-side end of the lifting hydraulic cylinder 4 is pivotally attached to the center side of the mounting bracket 310 so as to be vertically rotatable and detachable by an L-shaped cylinder pin 313.
  • the reaping drive belt 125 wound around the reaping input pulley 309 is removed, and the lifting hydraulic cylinder 4 and the mounting bracket 310 are attached.
  • the cylinder pin 313 to be connected is removed.
  • the threshing device 5 includes a handling cylinder 226 for threshing threshing, a rocking sorter 227 that sorts the cereals falling below the handling cylinder 226, and a tang fan 228.
  • a processing cylinder 229 that reprocesses the threshing waste taken out from the rear part of the cylinder 226 and a dust exhaust fan 230 that discharges dust at the rear part of the swing sorter 227 are provided.
  • 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 stock source side of the corn straw conveyed from the reaping device 3 by the corn straw conveying device 224 is inherited by the feed chain 6 and is nipped and conveyed. Then, the tip side of the cereal cocoon is carried into the handling chamber of the threshing device 5 and threshed by the handling drum 226.
  • first conveyor 231 for taking out the grain (the first thing) sorted by the rocking sorter 227, and a grain with a branch raft.
  • a second conveyor 232 for taking out the articles is provided.
  • the two conveyors 231 and 232 of this embodiment are arranged in the order from the front side in the traveling direction of the traveling machine body 1 to the upper surface side of the traveling machine body 1 above the rear part of the traveling crawler 2 in a side view in order of the first conveyor 231 and the second conveyor 232. It is installed.
  • the grain sorting mechanism 245 is configured by the above-described swing sorter 227, tang fan 228, first conveyor 231, second conveyor 232, dust exhaust fan 230, sorter fan 241, and the like.
  • the rocking sorter 227 is subjected to rocking sorting (specific gravity sorting) by the feed pan 238 and the chaff sheave 239 from the cereals that have leaked from the receiving net 237 stretched below the handling cylinder 226. It is configured as follows. The grains falling from the rocking sorter 227 are removed by the sorting air from the red pepper fan 228, and fall first on the conveyor 231.
  • a cereal conveyor 233 extending in the vertical direction is connected to a terminal end 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 first from the conveyor 231 is carried into the grain tank 7 via the cereal conveyor 233 and collected in the grain tank 7.
  • the rocking sorter 227 is configured to drop a second thing such as a grain with a branch stem from the chaff sheave 239 onto the second conveyor 232 by rocking sorting (specific gravity sorting). .
  • a sorting fan 241 for wind-selecting the second object falling below the chaff sheave 239 is provided.
  • 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.
  • the terminal portion of the second conveyor 232 that protrudes outward from one side wall near the grain tank 7 in the threshing device 5 is located on the upper surface side of the rear part of the feed pan 238 (the front part of the chaff sheave 239) via the reduction conveyor 236.
  • the second connection is returned to the upper surface side of the swing sorter 227 and re-sorted.
  • an exhaust chain 234 and an exhaust cutter 235 are disposed 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 slag 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 part of the threshing device 5
  • the paper After being cut to an appropriate length by a waste cutter 235 provided on the rear, the paper is discharged to the lower rear side of the traveling machine body 1.
  • the drive structure of the combine (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.
  • the output shaft 150 projects from the left side of the engine 14.
  • the traveling input shaft 152 of the transmission case 88 is connected to the output shaft 150 of the engine 14 via the traveling drive belt 151, and the rotational driving force of the engine 14 is transmitted from the front output shaft 150 to the transmission case 88 and shifted.
  • the left and right traveling crawlers 2 are transmitted to the left and right traveling crawlers 2 via the left and right axles 153, and the left and right traveling crawlers 2 are driven by the rotational force of the engine 14.
  • a cooling fan 154 for a radiator or the like for cooling the engine 14 is provided on the output shaft 150 protruding to the right side of the engine 14.
  • a discharge auger drive shaft 157 is connected to the output shaft 150 on the right side of the engine 14, and the discharge auger 8 is driven via the discharge auger drive shaft 157 by the rotational drive force of the engine 14, so that the grains in the grain tank 7 are transferred. It is configured to be discharged into a container or the like. Further, as shown in FIG.
  • the threshing selection work input shaft 165 that transmits the rotational driving force of the engine 14 to each part of the threshing device 5, and the rotational driving force of the threshing selection work input shaft 165 is transmitted to the handling cylinder 226 and the processing cylinder 230.
  • a threshing drive shaft 160 is provided.
  • a threshing sorting operation input shaft 165 is connected to the output shaft 150 on the left side of the engine 14 via a tension roller type threshing clutch 161 and a threshing drive belt 162.
  • a barrel low speed gear and a barrel high speed gear are arranged on the threshing drive shaft 160.
  • the rotational force of the threshing selection work input shaft 165 is transmitted to the threshing drive shaft 160 via the barrel low speed gear or the barrel high speed gear.
  • the threshing drive shaft 160 is connected to a treatment cylinder shaft 163 that supports the treatment cylinder 226 and a processing cylinder shaft 164 that supports the treatment cylinder 230 via a treatment cylinder drive belt 117.
  • the handling cylinder 226 and the processing cylinder 230 are configured to rotate at a predetermined rotation speed (low speed rotation speed or high speed rotation speed) by the rotational force of the engine 14 at a substantially constant rotation speed.
  • the rotational force of the engine 14 at a substantially constant rotational speed causes the scouring and sorting operation input shaft 165 to pass through the swing sorting plate 227, the tang fan 228, the first conveyor 231, the second conveyor 232, the sorting fan 241, and the dust exhaust.
  • the fan 230 is configured to rotate at a substantially constant rotational speed.
  • the transmission case 88 includes a linearly-traveling (traveling main transmission) hydraulic continuously variable transmission 53 having a pair of linearly-moving first hydraulic pump 55 and a linearly-moving first hydraulic motor 56.
  • a turning hydraulic continuously variable transmission 54 having a pair of turning second hydraulic pump 57 and turning second hydraulic motor 58 is provided.
  • the traveling input shaft 152 of the mission case 88 is connected to the first hydraulic pump 55 and the second hydraulic pump 57, respectively, and is driven.
  • a PTO shaft 99 is disposed on the mission case 88. The PTO shaft 99 is driven by the first hydraulic motor 56. One end side of the PTO shaft 99 protrudes from the mission case 88 to the left outer side.
  • a counter gear case 89 (see FIGS. 3, 6, 7, and 9) is provided on the left side of the engine 14 and on the front side of the threshing device 5 on the traveling machine body 1.
  • the counter gear case 89 includes a threshing drive shaft 160, a threshing selection operation input shaft 165 connected to the threshing drive shaft 160, a vehicle speed tuning shaft 100 connected to the PTO shaft 99, and a threshing selection operation input shaft 165 or vehicle speed synchronization.
  • a cutting transmission shaft 101 connected to the shaft 100, a cutting drive shaft 102 connected to the cutting input shaft 17, and a feed chain driving shaft 103 that drives the feed chain 6 and the succeeding auxiliary stock former transfer chain 136 are arranged. .
  • a cutting transmission shaft 101 is coupled to the vehicle speed tuning shaft 100 via a cutting transmission mechanism and a one-way clutch.
  • the cutting transmission mechanism has a low speed side transmission gear and a high speed side transmission gear.
  • the low-speed side shifting gear or the high-speed side transmission gear is selectively engaged with the cutting transmission shaft 101 by the cutting shift operating means for performing the low-speed, neutral (zero rotation) and high-speed cutting shifts.
  • the cutting gear shift output is transmitted to the cutting transmission shaft 101 via the mechanism.
  • the mowing transmission shaft 101 is connected to the threshing selection work input shaft 165 via a constant rotation mechanism.
  • the constant rotation mechanism has a low speed side constant rotation gear and a high speed side constant rotation gear.
  • the cutting drive shaft 102 is connected to the cutting transmission shaft 101 via a torque limiter.
  • the cutting input shaft 17 is connected to the cutting drive shaft 102 via the cutting drive pulley 124 and the cutting drive belt 125, and the cutting drive force is transmitted from the cutting drive shaft 102 to the cutting device 3.
  • a rotation output at a constant rotational speed necessary for maintaining the cutting operation is transmitted from the threshing selection operation input shaft 165 to the cutting transmission shaft 101 via the low-speed constant rotation gear. Therefore, regardless of the moving speed of the traveling machine body 1, the cutting input shaft 17 can be operated at a constant rotation speed from the low-speed constant rotation gear to maintain the cutting operation, and the direction change workability at the headland in the field is improved. it can.
  • a rotational output of a constant rotational speed faster than the maximum speed of the vehicle speed synchronous output from the vehicle speed tuning shaft 100 and the high speed side transmission gear is transferred from the threshing selection work input shaft 165 to the cutting transmission shaft 101 via the high speed side constant rotational gear.
  • the cutting input shaft 17 can be driven at a constant rotational speed from the high-speed constant rotational gear that is faster than the maximum speed of the vehicle speed synchronized output, so that the workability of harvesting the fallen cereal can be improved.
  • the cutting blade 132 and the like are prevented from being damaged by driving the cutting input shaft 17 with a rotational force equal to or less than the torque set by the torque limiter.
  • the counter gear case 89 is provided with a planetary gear-type shift structure feed chain tuning mechanism that connects the feed chain drive shaft 103 to the threshing sorting operation input shaft 165.
  • the rotational output of the threshing selection work input shaft 165 is shifted in proportion to the rotational speed of the cutting transmission shaft 101 by the feed chain tuning mechanism and transmitted to the feed chain drive shaft 103. That is, by operating the feed chain 6 and the inheritance auxiliary stock former transport chain 136 via the feed chain tuning mechanism, the minimum rotational speed (constant rotational speed from the low-speed constant rotational gear) required for transporting the cereals is reduced. While ensuring, the grain straw conveyance speed of the feed chain 6 and the inheritance auxiliary stock former conveyance chain 136 can be changed in synchronization with the vehicle speed.
  • the pulling lateral transmission shaft 143 is connected to the cutting input shaft 17 via the longitudinal transmission shaft 140, the lateral transmission shaft 141, and the left conveyance drive shaft 142.
  • the pulling lateral transmission shaft 143 is connected to the pulling tine drive shaft 144 of each pulling case 29 for six lines.
  • a pulling case 129 is erected on the rear side of the weed body 225 and above the weeding frame 20, and the pulling tine drive shaft 144 protrudes from the upper back side of the pulling case 129.
  • the pulling tine chain 128a provided with a plurality of pulling tines 128 is driven via the pulling tine drive shaft 144 and the pulling lateral transmission shaft 143. As shown in FIG.
  • the left and right cutting blades 132 are connected to the lateral transmission shaft 141 via the left and right crankshafts 145.
  • the left and right cutting blades 132 are driven in conjunction with each other via a lateral transmission shaft 141.
  • 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 132, and the left and right cutting blades 132 are reciprocated in opposite directions, and the left and right generated by the reciprocating movement.
  • the cutting blade 132 is configured to be able to cancel the vibration (inertial force).
  • one end side of the longitudinal transmission shaft 140 in the longitudinal transmission case 18 is connected to the cutting input shaft 17.
  • the horizontal transmission shaft 141 in the horizontal transmission case 19 is connected to the other end side of the vertical transmission shaft 140.
  • the rotational force of the cutting input shaft 17 is transmitted from the vertical transmission shaft 140 and the horizontal transmission shaft 141 to each drive unit of the cereal conveyance device 224. That is, the right transmission drive shaft 146 is connected to the vertical transmission shaft 140. Via the vertical transmission shaft 140 and the right conveyance drive shaft 146, the right stock former conveyance chain 133R, the right star wheel 130R, the right take-up belt 131R, and the vertical conveyance chain 134 are driven.
  • a rear conveyance drive shaft 147 is connected to the longitudinal transmission shaft 140 behind the right conveyance drive shaft 146.
  • the auxiliary stock former conveyance chain 135 and the right tip conveyance tine 137 ⁇ / b> R are driven via the vertical transmission shaft 140 and the rear conveyance drive shaft 147.
  • the left conveyance drive shaft 142 is connected to the left end side of the horizontal transmission shaft 141.
  • the left stock former transport chain 133L and the left tip transport tine 137L, the left star wheel 130L, and the left take-up belt 131L are driven via the left transport drive shaft 142.
  • a central transport drive shaft 148 is connected to the lateral transmission shaft 141, and the central stock transport chain 133C and the central tip transport tine 137C, the central star wheel 130C, and the central scraping belt 131C are connected via the central transport drive shaft 148. Is configured to be driven.
  • the transmission case 88 includes a pair of linearly traveling first hydraulic pumps 55 and a linearly traveling first hydraulic motor 56. And a turning hydraulic continuously variable transmission 54 having a turning second hydraulic pump 57 and a turning second hydraulic motor 58.
  • the traveling input shaft 152 of the transmission case 88 is connected to the first hydraulic pump 55 and the second hydraulic pump 57, respectively, and is driven.
  • a travel input pulley 155 is provided on the travel input shaft 152, and the travel drive belt 151 is wound around the travel input pulley 155.
  • a PTO shaft 99 is arranged in the mission case 88.
  • the PTO shaft 99 is driven by a first hydraulic motor 56 via a straight traveling motor shaft 60 and a main transmission output counter shaft 70. One end side of the PTO shaft 99 protrudes from the transmission case 88 to the left outer side.
  • a PTO pulley 119 is provided on the PTO shaft 99, and a PTO belt 120 is wound around the PTO pulley 119.
  • the driving force output from the output shaft 150 of the engine 14 is pumped by the pump shaft 59 of the first hydraulic pump 55 and the pump of the second hydraulic pump 57 via the travel drive belt 151 and the travel input shaft 152. Each is transmitted to the shaft 59.
  • hydraulic oil is appropriately sent from the first hydraulic pump 55 toward the first hydraulic motor 56 with the power transmitted to the pump shaft 59.
  • hydraulic oil is appropriately sent from the second hydraulic pump 57 toward the second hydraulic motor 58 with the power transmitted to the pump shaft 59.
  • a charge pump 251 for supplying hydraulic oil to the hydraulic pumps 55 and 57 and the hydraulic motors 56 and 58 is attached to the pump shaft 59.
  • the straight-traveling hydraulic continuously variable transmission 53 changes and adjusts the inclination angle of the swash plate 55a in the first hydraulic pump 55 according to the operation amount of the main transmission lever 43 and the steering handle 11 arranged in the driving cabin 10,
  • the rotation direction and the rotation speed of the linear motor shaft 60 protruding from the first hydraulic motor 56 are arbitrarily adjusted. Yes.
  • the rotational power of the linear motor shaft 60 is transmitted from the linear transmission gear 50 to the auxiliary transmission mechanism 51.
  • the sub transmission mechanism 51 includes a sub transmission low speed gear 62 and a sub transmission high speed gear 63 that are switched by a sub transmission shifter 64.
  • the output rotational speed of the straight traveling motor shaft 60 is switched to two speed stages, low speed or high speed.
  • a neutral position (a position where the output of the sub-shift is zero) is between the low speed and the high speed of the sub-shift.
  • the auxiliary transmission switch 44 includes a low speed switching button, a neutral switching button, and a high speed switching button. By pressing the low speed switch button, neutral switch button or high speed switch button, the sub-shift output is selectively switched to the low speed output, neutral or high speed output.
  • a parking brake shaft 65 provided on the output side of the subtransmission mechanism 51 (subtransmission output shaft) is provided with a wet multi-plate disc type parking brake 66.
  • Rotational power from the auxiliary transmission mechanism 51 is transmitted to the left and right differential mechanisms 52 from an auxiliary transmission output gear 67 fixed to the parking brake shaft 65.
  • the left and right differential mechanisms 52 are each provided with a planetary gear mechanism 68.
  • a rectilinear pulse generation rotating wheel 92 is provided on the parking brake shaft 65, and a rectilinear pickup rotation sensor 93 (straight vehicle speed sensor) is arranged to face the rectilinear pulse generating rotating wheel 92 so that the rectilinear pickup rotation is performed.
  • the sensor 93 is configured to detect the rotational speed of the straight-ahead output (straight-ahead vehicle speed, auxiliary transmission output gear 67 output).
  • each of the left and right planetary gear mechanisms 68 includes one sun gear 71, a plurality of planet gears 72 that mesh with the sun gear 71, a ring gear 73 that meshes with the planet gear 72, and a plurality of planet gears 72. And a carrier 74 rotatably disposed on the circumference.
  • the carriers 74 of the left and right planetary gear mechanisms 68 are arranged on the same axis so as to face each other with an appropriate interval.
  • a center gear 76 is fixed to a sun gear shaft 75 provided with left and right sun gears 71.
  • the left and right ring gears 73 are arranged concentrically with the sun gear shaft 75 in a state where the inner teeth of the inner peripheral surface thereof are engaged with the plurality of planetary gears 72.
  • Each of the left and right ring gears 73 is connected to the relay shaft 85 by engaging the outer teeth of the outer peripheral surface thereof with the left and right turning output gear 86.
  • Each ring gear 73 is rotatably supported by left and right forced differential output shafts 77 projecting left and right outward from the outer surface of the carrier 74.
  • Left and right axles 153 are connected to the left and right forced differential output shafts 77 via final gears 78a and 78b.
  • Left and right drive sprockets 22 are attached to the left and right axles 153.
  • the rotational power transmitted from the auxiliary transmission mechanism 51 to the left and right planetary gear mechanisms 68 is transmitted from the left and right axles 153 to the drive sprockets 22 at the same rotational speed in the same direction, and the left and right traveling crawlers 2 are transmitted in the same direction. And the traveling machine body 1 is moved straight (forward, backward).
  • the turning hydraulic continuously variable transmission 54 changes and adjusts the inclination angle of the swash plate 57a in the second hydraulic pump 57 in accordance with the operation amount of the main transmission lever 43 and the steering handle 11 arranged in the driving cabin 10,
  • the rotation direction and the rotation speed of the turning motor shaft 61 protruding from the second hydraulic motor 58 are arbitrarily adjusted.
  • a turning pulse generating rotary wheel 94 is provided on a steering counter shaft 80 which will be described later, and a turning pickup rotation sensor 95 is arranged to face the turning pulse generating rotary wheel 94 so that the turning pickup rotation sensor 95 is turned.
  • the rotation speed (turning vehicle speed) of the steering output of the second hydraulic motor 58 is detected by the (turning vehicle speed sensor).
  • a steering brake 79 (swing brake) provided on the turning motor shaft 61 (steering input shaft) and a steering counter connected to the turning motor shaft 61 via a reduction gear 81 are provided.
  • the rotational power of the turning motor shaft 61 is transmitted to the steering counter shaft 80.
  • the rotational power transmitted to the steering counter shaft 80 is transmitted to the left ring gear 73 as reverse rotational power via the left intermediate gear 87 and the reverse gear 84 of the left input gear mechanism 82, and the right input gear mechanism 83. It is transmitted to the right ring gear 73 as forward rotation power through the right intermediate gear 87.
  • auxiliary transmission mechanism 51 When the auxiliary transmission mechanism 51 is neutral, power transmission from the first hydraulic motor 56 to the left and right planetary gear mechanisms 68 is blocked.
  • a sub-shift output other than neutral is output from the sub-transmission mechanism 51, power is transmitted from the first hydraulic motor 56 to the left and right planetary gear mechanisms 68 via the sub-transmission low speed gear 62 or the sub transmission high speed gear 63.
  • the output of the second hydraulic pump 57 is in the neutral state and the steering brake 79 is in the on state, power transmission from the second hydraulic motor 58 to the left and right planetary gear mechanisms 68 is blocked.
  • the rotational output from the linear motor shaft 60 is output to the left and right sun gears 71 at the same left and right rotational speed.
  • the left and right traveling crawlers 2 are driven at the same rotational speed in the same direction via the planetary gear 72 and the carrier 74, and the traveling machine body 1 travels straight.
  • the left ring gear 73 is rotated by the rotational power from the turning motor shaft 61.
  • the ring gear 73 rotates forward (reverse) and the right ring gear 73 rotates reverse (forward).
  • one of the drive sprockets 22 of the left and right traveling crawlers 2 is rotated forward, the other is rotated backward, and the traveling machine body 1 is turned on the spot (reliable turning spin turn).
  • the traveling machine body 1 moves forward or backward. While turning to the left or right (U-turn) with a turning radius larger than the belief turning radius. The turning radius at this time is determined according to the speed difference between the left and right traveling crawlers 2.
  • the combined hydraulic circuit 250 includes a first hydraulic pump 55 and a first hydraulic motor 56 for straight travel, a second hydraulic pump 57 and a second hydraulic motor 58 for turning, a charge pump 251, and the like. Is provided.
  • the first hydraulic pump 55 and the first hydraulic motor 56 are connected by a closed loop straight oil passage 252.
  • the second hydraulic pump 57 and the second hydraulic motor 58 are connected by a closed loop revolving oil passage 253.
  • the first hydraulic pump 55 and the second hydraulic pump 57 are driven by the engine 14, and the first hydraulic motor 56 or the second hydraulic pressure is controlled by the swash plate angle control of the first hydraulic pump 55 or the swash plate angle control of the second hydraulic pump 57.
  • the motor 58 is configured to perform forward rotation or reverse rotation.
  • an electrohydraulic steering valve 270 that is electrically switched in response to manual operation of the steering handle 11 and a steering cylinder 271 that is connected to the charge pump 251 via the electrohydraulic steering valve 270 are provided.
  • the electrohydraulic steering valve 270 is switched corresponding to the steering angle of the steering handle 11 detected by the steering angle sensor 402
  • the steering cylinder 271 is activated to change the swash plate 57a angle of the second hydraulic pump 57.
  • the rotation speed of the second hydraulic motor 58 is changed steplessly, or the left and right steering operation is performed to reverse the direction, the direction of travel is changed to the left and right, and the direction is changed on the field headland. Correct the course.
  • a steering hydraulic servo mechanism 275 is provided, and the hydraulic servo mechanism 275 performs a feedback operation in which the electromagnetic hydraulic steering valve 270 is neutrally returned by the angle adjustment operation of the swash plate 57a.
  • the angle of the swash plate 57a is changed in proportion to the operation amount, and the rotational speed of the turning motor shaft 61 of the second hydraulic motor 58 is changed.
  • an electrohydraulic shift valve 272 that is electrically switched in response to manual operation of the main shift lever 43, and a shift cylinder that is connected to the charge pump 251 via an electrohydraulic shift valve 272. 273 is provided.
  • the shift cylinder 273 is operated to change the angle of the swash plate 55a of the first hydraulic pump 55. Then, a traveling speed change operation is performed in which the rotational speed of the straight traveling motor shaft 60 of the first hydraulic motor 56 is steplessly changed or reversed.
  • a hydraulic servo mechanism 277 for travel shifting is provided, and the hydraulic servo mechanism 277 is caused to perform a feedback operation in which the electrohydraulic shift valve 272 is neutrally returned by the angle adjusting operation of the swash plate 55a.
  • the angle of the swash plate 55a is changed in proportion to the amount, the rotational speed of the linear motor shaft 60 of the first hydraulic motor 56 is changed, and the linear motor shaft 60 is rotated forward and backward by operating the main transmission lever 43. It is composed.
  • a hydraulic cutting gear cylinder 280 for switching the operating speed of the cutting device 3 and a hydraulic cutting speed cylinder 281 for operating the cutting device 3 at a constant rotational speed are provided.
  • the hydraulic cutting gear shift cylinder 280 and the hydraulic cutting constant speed cylinder 281 are arranged on the top cover (oil path base) of the counter gear case 89.
  • a cutting speed change valve 282 for operating the cutting speed change cylinder 280 and a cutting speed control valve 283 for operating the constant cutting speed cylinder 281 are hydraulically connected to the charge pump 251 in parallel.
  • FIG. 1 As shown in FIGS. 1, 2, and 6 to 8, the engine 14 is mounted on the right side of the upper surface of the traveling machine body 1, and a transmission case 88 is installed in front of the left and right width center of the traveling machine body 1.
  • a counter gear case 89 is arranged on the upper left side.
  • An output pulley 149 is pivotally supported on the left end portion of the output shaft 150 extended in the left-right direction in the engine 14, and a traveling drive belt 151 is hung between the traveling input pulley 155 and the output pulley 149 on the upper left side of the mission case 88. It is turning. With this configuration, the output of the engine 14 is transmitted to each of the hydraulic continuously variable transmissions 53 and 54 of the mission case 88.
  • a columnar frame 290 that supports the discharge auger 8 in a storage (non-working) position is erected on the upper surface of the traveling machine body 1, and a PTO countershaft 121 is mounted on the front surface of the base end portion of the columnar frame 290 via a bearing body 291. Is rotatably supported.
  • the PTO belt 120 is wound around the PTO counter pulley 122a on the PTO counter shaft 121 and the PTO pulley 119 below the traveling input pulley 155 in the upper left portion of the mission case 88.
  • a vehicle speed tuning belt 123 is wound around the PTO counter pulley 122 b on the PTO counter shaft 121 and the vehicle speed tuning pulley 104 fixed to the vehicle speed tuning shaft 100 of the counter gear case 89. With this configuration, the vehicle speed tuning driving force of the transmission case 88 is transmitted from the PTO shaft 99 to the vehicle speed tuning shaft 100.
  • a threshing drive belt 162 is wound around an output pulley 149 on the output shaft 150 of the engine 14 and a threshing drive pulley 118 fixed to the threshing selection work input shaft 165 of the counter gear case 89.
  • the threshing clutch electric motor 175 as a threshing input actuator which switches the threshing clutch 161 is provided.
  • a clutch unit chassis 176 is disposed behind the engine 14 on the traveling machine body 1, and a threshing clutch insertion / closing mechanism 177 is assembled to the clutch unit chassis 176, and an electric motor 175 for threshing clutch is provided on the clutch unit chassis 176.
  • a threshing clutch electric motor 175 is connected to a tension arm (not shown) that supports the threshing clutch 161 via a threshing clutch on / off mechanism 177.
  • a threshing clutch electric motor 175 is arranged on the opposite side of the counter gear case 89 with a threshing drive pulley 118 on a threshing selection work input shaft 165 supported by the counter gear case 89 interposed therebetween.
  • the threshing drive pulley 118 can be supported close to the right side of the counter gear case 89. Without being restricted by the threshing clutch electric motor 175 or the threshing clutch insertion / cutting mechanism 177, the rigidity of the bearing structure accompanying the extension of the threshing selection work input shaft 165 is not required, and a large gear ratio (reduction ratio) is obtained. A settable large-diameter threshing drive pulley 118 can be easily installed.
  • FIG. 9 The mission case 88 installed in front of the center of the left and right width in the traveling machine body 1 has a split structure that is vertically long and can be divided into left and right.
  • the split case 88 has a substantially hollow box shape by fastening with a plurality of bolts.
  • a hydraulic transmission case 350 containing the straight and turning hydraulic continuously variable transmissions 53 and 54 is attached to the upper side of the left and right side surfaces of the transmission case 88 (upper right side in the embodiment).
  • the straight hydraulic continuously variable transmission 53 (the first hydraulic pump 55 and the first hydraulic motor 56) is positioned on the front side in the hydraulic transmission case 350, and the turning hydraulic continuously variable at the rear side in the hydraulic transmission case 350.
  • the transmission 54 (second hydraulic pump 57 and second hydraulic motor 58) is located.
  • a gear train such as the auxiliary transmission mechanism 51 and the differential mechanism 52 as described with reference to FIG.
  • the lower part of the mission case 88 protrudes outward in the left and right direction and protrudes downward in a bifurcated shape, and is roughly formed in a gate shape when viewed from the front.
  • An axle case 351 that protrudes outward from the left and right is bolted to a gear case 349 that protrudes downward from the lower portions of the left and right sides of the transmission case 88.
  • Axles 153 are rotatably supported in the left and right axle cases 351, and drive sprockets 22 are attached to the protruding end portions of the axles 153.
  • the bottoms of both gear cases 349 are located below the bottom of the transmission case 88, and the bottom of the transmission case 88 is higher than the left and right axle cases 351 protruding from the gear cases 349.
  • the mating surface at the bottom of the mission case 88 is connected by fastening a bolt 389 inside the mission case 88.
  • the direction of the mold split can be made common to the entire half split (the mold split direction can be one direction).
  • the cost can be simplified and the manufacturing cost can be reduced.
  • the outer shape of the bottom of the mission case 88 is a continuous shape regardless of the split structure, the fastening rigidity of the mission case 88 (half halves) can be improved, and hydraulic oil leaks from the mission case 88. It is possible to exert a high effect on the suppression.
  • a spline portion 390 is formed in a portion of the protruding end portion of each axle 153 near the axle case 351.
  • the spline portion 390 is fitted (spline fitted) so that the rotation center portion of the drive sprocket 22 is slidable and cannot be relatively rotated.
  • the drive sprocket 22 is removed from the protruding end of the axle 153 by screwing a nut 394 after fitting a retaining collar 392 having a packing 393 on the inner peripheral side to the bolt portion 391 further outside the spline portion 390. It is impossible.
  • the presence of the packing 393 in the retaining collar 392 prevents muddy water or the like from entering between the spline portion 390 of the axle 153 and the rotation center portion of the drive sprocket 22.
  • the opening portion on the tip end side of the axle case 351 is closed by a sleeve packing 395 and an annular seal body 396 that are fitted to the root portion of the spline portion 390 on the axle case 351 side.
  • the sleeve packing 395 is provided with outward lip portions 395a projecting on both sides in the axle 153 direction. For this reason, the thickness dimension of the sleeve packing 395 in the axle 153 direction is larger than that of the annular seal body 396.
  • the outward lip portion 395 a is in close contact with the rotation center portion side of the drive sprocket 22 and the retaining ring 398 on the bearing body 397 side that supports the axle 153. Due to the close structure of these outward lip portions 395a, intrusion of muddy water into the axle case 351 and grease leakage from the bearing body 397 and the like are suppressed, and the sealing performance of the axle case 351 is improved.
  • the first hydraulic pump 55 and the first hydraulic pump 55 are connected to the transmission case 88 from the side surface (upper left side in the embodiment) opposite to the hydraulic transmission case 350.
  • a travel input shaft 152 that is coupled to the hydraulic pump 57 so as to be capable of transmitting power protrudes outward in the lateral direction.
  • a travel drive belt 151 wound around an output pulley 149 of the engine 14 is wound around a travel input pulley 155 fixed to the projecting end of the travel input shaft 152.
  • a PTO pulley 119 is provided on the projecting end side of the PTO shaft 99 projecting laterally outward from the upper left side surface of the mission case 88.
  • the PTO pulley 119 is located below the travel input pulley 155, and the PTO belt 120 is wound around the PTO pulley 119 and the PTO counter pulley 112a located behind the PTO pulley 119. Between the PTO pulley 119 and the PTO counter pulley 122a, a tension pulley 352 for contacting the PTO belt 120 from below and holding the PTO belt 120 in a tensioned state is provided.
  • the tension pulley 352 is supported by the bearing body 291 of the columnar frame 290 so as to be vertically rotatable, and is configured to always tension the PTO belt 120 by a spring bias.
  • a rectilinear pickup rotation sensor 93 (straight vehicle speed sensor) as a rectilinear output detecting means associated with the rectilinear pulse generating rotating wheel 92 in the mission case 88.
  • a turning pickup rotation sensor 95 (turning vehicle speed sensor) as a turning output detecting means associated with the turning pulse generating rotating wheel body 94 is provided with a part thereof exposed outward. As shown in FIG. 10, both pickup rotation sensors 93 and 95 are arranged side by side.
  • both pickup rotation sensors 93 and 95 are located between the PTO shaft 99 and the lower left projecting portion of the transmission case 88, with the straight pickup pickup rotation sensor 93 on the front side and the pickup pickup rotation sensor 95 on the rear side. is doing.
  • a substantially lid-like guard plate 353 with the right side surface and the lower surface side opened is attached to the positions of both pickup rotation sensors 93 and 95 in the left side surface portion of the mission case 88 by bolt fastening. Therefore, the outer peripheral sides of both pickup rotation sensors 93 and 95 are covered with the guard plate 353. If comprised in this way, both the pick-up rotation sensors 93 and 95 can be easily protected from the mud etc. which the traveling crawler 2 rolled up by the single guard board 353. Moreover, it can also contribute to the suppression of the number of parts and the reduction of the assembly work man-hours. Furthermore, the harnesses (not shown) of the pickup rotation sensors 93 and 95 can be protected in a wide range.
  • the upper surface portion of the guard plate 353 of the embodiment has a shape that is inclined in a front-rear and a rear-high state. For this reason, the mud or the like placed on the guard plate 353 easily slides down the inclined upper surface portion, and accumulation of the mud or the like on the guard plate 353 can be effectively prevented.
  • the right side surface side of the guard plate 353 is blocked by the left side surface portion of the mission case 88, and the lower surface side of the guard plate 353 is blocked by the upper surface side of the lower left projecting portion of the mission case 88.
  • the left and right width dimensions of the guard plate 353 are set to such a size that the guard plate 353 fits between the left side surface portion of the mission case 88 and the PTO pulley 119 when viewed from the front.
  • the portion of the guard plate 353 that overlaps the tension pulley 352 in the side view is directed toward the left and right side surfaces (left side surface portion in the embodiment) of the mission case 88 on the PTO shaft 99 side. It has a shape inclined inward (a shape bent inward).
  • the power transmission system (PTO) from the mission case 88 can be made compact in the left-right width direction while avoiding interference between the guard plate 353 and the tension pulley 352. It is also effective in avoiding interference with the lifting hydraulic cylinder 4 which is located in the vicinity of the tension pulley.
  • the straight traveling hydraulic continuously variable transmission 53 (the first hydraulic pump 55 and the first hydraulic motor 56) is provided on the front side in the hydraulic transmission case 350 that is bolted to the upper right side of the transmission case 88. Yes.
  • a turning hydraulic continuously variable transmission 54 (second hydraulic pump 57 and second hydraulic motor 58) is provided on the rear side in the hydraulic transmission case 350.
  • an electromagnetic hydraulic transmission valve 272 as an electric actuator for operating the transmission cylinder 273 for the swash plate 55 a of the first hydraulic pump 55 is provided in the hydraulic circuit 250 ( The unit is assembled so as to communicate with each other (see FIG. 5).
  • the swash plate 55a of the first hydraulic pump 55 is manually operated to manually change the discharge direction and the discharge amount of the hydraulic oil to the first hydraulic motor 56 for the straight advance emergency.
  • a straight operation shaft 355 as a manual operation tool is projected forward. If the rectilinear operation shaft 355 is rotated around its axis, the inclination angle of the swash plate 55a of the first hydraulic pump 55 is changed independently from the electrical control of the electrohydraulic shift valve 272, and the first The discharge direction and discharge amount of the hydraulic oil to the hydraulic motor 56 are changed.
  • the straight operation shaft 355 and the electrohydraulic shift valve 272 are arranged side by side on the front side of the hydraulic shift case 350.
  • an electromagnetic hydraulic steering valve 270 for operating the steering cylinder 271 for the swash plate 57a of the second hydraulic pump 57 is a hydraulic circuit 250 in the hydraulic transmission case 350 (see FIG. 5). It is assembled and unitized so as to communicate with. Further, on the rear side of the hydraulic transmission case 350, an emergency for turning which manually changes the discharge direction and discharge amount of the hydraulic oil to the second hydraulic motor 58 by manually operating the swash plate 57a of the second hydraulic pump 57. A turning operation shaft 356 as a manual operation tool protrudes rearward.
  • the turning operation shaft 356 is turned around its axis, the inclination angle of the swash plate 57a of the second hydraulic pump 57 is changed independently from the electrical control of the electromagnetic hydraulic steering valve 270, and the second The discharge direction and discharge amount of the hydraulic oil to the hydraulic motor 58 are changed.
  • the turning operation shaft 356 and the electrohydraulic steering valve 270 are arranged side by side on the rear surface side of the hydraulic transmission case 350.
  • the step 357 of the traveling aircraft 1 is located on one side of the mission case 88 (on the left side in the embodiment).
  • the hydraulic transmission case 350 is located between the step 357 and the mission case 88.
  • a battery 358 is mounted inside the frame.
  • the battery housing space 359 in step 357 is open to the left and right outwards, and the straight operation shaft 355 on the front side of the hydraulic transmission case 350 as viewed from the left side of step 357 faces the battery housing space 359 in step 357.
  • the rectilinear operation shaft 355 is driven by the electrohydraulic shift. It is configured to operate in conjunction with the switching operation of the valve 272.
  • the shift cylinder 273 is actuated to change the angle of the swash plate 55 a of the first hydraulic pump 55 by the switching operation of the electrohydraulic shift valve 272 based on the command of the shift steering controller 400.
  • the rectilinear operation shaft 355 automatically rotates about its axis (in conjunction with the swash plate 55a). That is, the operations of the electromagnetic hydraulic shift valve 272 and the straight operation shaft 355 are linked via the swash plate 55 a of the first hydraulic pump 55.
  • the turning operation shaft 356 is driven by the electrohydraulic type.
  • the steering valve 270 is configured to operate in conjunction with the switching operation.
  • the steering cylinder 271 is operated by the switching operation of the electrohydraulic steering valve 270 based on the command of the shift steering controller 400, and the swash plate 57a angle of the second hydraulic pump 57 is changed.
  • the turning operation shaft 355 automatically rotates about its axis (in conjunction with the swash plate 57a). That is, the operations of the electrohydraulic steering valve 270 and the turning operation shaft 356 are linked via the swash plate 57 a of the second hydraulic pump 57.
  • the operation shafts 355 and 356 are not normally operated.
  • the operation shafts 355 and 356 are for emergency avoidance that is operated when a malfunction occurs in the electric system involved in the shift steering control, for example, an abnormality occurs in the shift steering controller 4000. is there.
  • Even when such an electrical trouble occurs if the operation shafts 355 and 356 are manually rotated, the combine can be escaped only from the field, for example, without the main transmission lever 43 and the steering handle 11 being effective.
  • Such limp home operation degenerate operation
  • Such limp home operation degenerate operation
  • the straight operation shaft 355 on the front side of the hydraulic transmission case 350 as viewed from the left side of step 357 faces the battery housing space 359 of step 357 so that at least the straight operation shaft 355 can be manually operated from the outside of the traveling machine body 1.
  • a rectilinear lever indicator 361 that facilitates manual rotation operation of the rectilinear operation shaft 355 is detachably mounted on the projecting end side of the rectilinear operation shaft 355.
  • a turning lever indicator 362 that facilitates manual turning operation of the turning operation shaft 356 is detachably attached to the protruding end side of the turning operation shaft 356.
  • the rectilinear lever indicator 361 and the rectilinear operation shaft 355 can constitute a rectilinear emergency manual operation tool (motion display body), and the swivel lever indicator 362 and the swivel operation shaft 356 together with a swivel emergency manual operation tool (motion display body). Can be configured.
  • the shift output amount of the linear hydraulic continuously variable transmission 53 or the turning hydraulic continuously variable transmission 54 is adjusted by the switching operation of the electromagnetic hydraulic shift valve 272 and the electromagnetic hydraulic steering valve 270.
  • the lever indicators 361 and 362 are mounted, the angle of the swash plates 55a and 57a of the hydraulic pumps 55 and 57 and the respective hydraulic continuously variable transmissions 53 are determined from the operation of the lever indicators 361 and 362. , 54 can be easily visually confirmed.
  • the main transmission lever 43 and the steering handle 11 are controlled. It becomes easy to find an operation trouble related to the handle 11 and the both hydraulic continuously variable transmissions 53 and 54 at an early stage.
  • the electrical control (shift control operation) is prohibited, so that the electrohydraulic shift valve 272 and the electrohydraulic control valve 270 are controlled.
  • the shift output adjustment of the hydraulic continuously variable transmissions 53 and 54 based on the switching operation is prohibited. If any one of the operation shafts 355 and 356 is manually rotated during execution of the shift steering control, the shift steering control described above is forcibly terminated, and the main shift lever 43 and the steering handle 11 are terminated.
  • the switching operation of the electrohydraulic shift valve 272 and the electrohydraulic steering valve 270 according to the operation amount is disabled. Then, unless the combine is turned off and then turned on again, the shift steering control is not restored.
  • an oil supply port 365 for supplying hydraulic oil is provided in front of the PTO pulley 119 in the left side surface of the mission case 88 that also functions as a hydraulic oil tank.
  • the oil filler 365 is closed by a detachable oil cap 366.
  • An oil inspection window 367 for visually confirming the amount of hydraulic oil in the mission case 88 from the outside is provided on the left side surface of the mission case 88 at a position below the oil supply port 365 and lower than the PTO pulley 119. .
  • the oil inspection window 367 of the embodiment is located higher than the left gear case 349 and the guard plate 353.
  • the oil supply port 365 and the oil inspection window on the left side surface of the transmission case are opened with the cutting device 3 opened and rotated laterally outward about the vertical axis 300. 367 is exposed.
  • the oil supply cap 366 is opened and closed, and hydraulic oil is supplied from the oil supply port 365 into the mission case 88 while looking at the oil detection window 367 on the same side as the oil supply port 365.
  • the oil supply port 365 is located at a midway height in the vertical direction of the transmission case 88 that also serves as a hydraulic oil tank, the oil level is directly below the oil supply port 365, that is, the maximum oil level indicated by a one-dot chain line in FIG. You can only refuel up to Hm.
  • a suction filter 368 for filtering hydraulic oil is incorporated in the right side surface of the mission case 88 at a position behind the oil detection window 367 and lower than the PTO pulley 119.
  • the suction filter 368 of the embodiment is located behind and in the vicinity of the right gear case 349 and is configured to filter the hydraulic oil on the bottom side of the mission case 88. Accordingly, the oil inspection window 367 and the suction filter 368 are located at positions facing each other in the front-rear and left-right directions across the differential mechanism 52 below the mission case 88.
  • the suction filter 368 is connected to a charge pump 251 attached to the outer surface of the hydraulic transmission case via a suction hose 369 extending vertically.
  • the charge pump 251 is configured to be rotationally driven by the pump shaft 59 of the second hydraulic pump 57.
  • the hydraulic oil on the bottom side of the mission case 88 is sucked into the charge pump 251 through the suction filter 368 and the suction hose 369 when the charge pump 251 is driven, and supplied to the oil passages 252, 253, 257, etc. of the hydraulic circuit 250. Is done.
  • the hydraulic servomechanism 277 for travel shifting (for the first hydraulic pump 55) and the hydraulic servomechanism 275 for steering (for the second hydraulic pump 57) are provided symmetrically with respect to the front and rear of the hydraulic transmission case 350. Both have basically the same configuration.
  • a hydraulic servomechanism 277 for traveling speed change is built in the front side of the hydraulic speed change case 350.
  • the traveling speed change hydraulic servo mechanism 277 includes a speed change cylinder 273 as an adjustment cylinder, and an electrohydraulic speed change valve 272 disposed inside the speed change cylinder 273 and having a speed change spool 440.
  • the transmission cylinder chamber 441 of the transmission cylinder 273 is formed inside the front portion of the hydraulic transmission case 350.
  • the speed change piston 442 of the speed change cylinder 273 is accommodated in the speed change cylinder chamber 441 so as to be vertically slidable.
  • a pin shaft 443 protruding from the swash plate 55 a of the first hydraulic pump 55 is fitted to the side surface of the transmission piston 442.
  • a speed change spool 440 of an electrohydraulic speed change valve 272 is slidably inserted into a through hole that penetrates the shaft center portion of the speed change piston 442.
  • An oil passage is formed in the speed change piston 442 to communicate the upper and lower portions of the speed change cylinder chamber 441.
  • the oil passage is configured to be connected or blocked by vertical sliding of the speed change spool 440 based on the switching operation of the electrohydraulic speed change valve 272 and supply hydraulic oil to the upper and lower oil chambers of the speed change piston 442.
  • a proportional control housing 444 with a built-in proportional control valve 445 for switching the electrohydraulic shift valve 272 is installed near the shift cylinder chamber 441 on the front side of the hydraulic shift case 350. It is attached as possible.
  • the proportional control spool 446 of the proportional control valve 445 in the proportional control housing 444 is configured to slide up and down like the speed change piston 442.
  • the transmission spool 440 and the proportional control spool 446 are related to each other so as to move together (sliding up and down) via a linkage pin 448 provided on one end side of the spool operation arm 447.
  • the proportional control housing 444 is provided with a proportional control solenoid 449 for sliding the proportional control spool 446 up and down.
  • the proportional control solenoid 449 is configured to be excited when the main transmission lever 43 is operated, and to slide the proportional control spool 446 up and down in proportion to the operation amount.
  • a midway portion of the linkage pin 448 is fixed to one end side of the spool operation arm 447.
  • a rectilinear operation shaft 355 that can be manually rotated is projected.
  • the straight operation shaft 355 of the embodiment protrudes forward from the front surface of the proportional control housing 444.
  • the proportional control solenoid 449 slides the proportional control spool 446 up and down in response to the operation amount of the main shift lever 43, so that the shift spool 440 similarly slides up and down via the linkage pin 448, and the shift cylinder 273 shifts.
  • the piston 442 is operated, and the swash plate 55a angle of the first hydraulic pump 55 is changed.
  • the linkage pin 448 moves up and down in conjunction with the operation (sliding up and down) of both spools 440 and 446, so that the spool operation arm 447 moves around the rectilinear operation shaft 355 (with the rectilinear operation shaft 355 as a rotation fulcrum). Turns up and down.
  • the rectilinear operation shaft 355 rotates about its axis in accordance with the operation of the transmission spool 440.
  • the spool operation arm 447 rotates up and down around the rectilinear operation shaft 355 to move the linkage pin 448 up and down.
  • the speed change spool 440 slides up and down to operate the speed change piston 442 of the speed change cylinder 273, and the angle of the swash plate 55a of the first hydraulic pump 55 is independent of the electric control of the electrohydraulic speed change valve 272.
  • the discharge direction and discharge amount of hydraulic oil to the first hydraulic motor 56 are changed.
  • a hydraulic servo mechanism 275 for steering is incorporated in the rear side of the hydraulic transmission case 350.
  • the steering hydraulic servomechanism 275 includes a steering cylinder 271 as an adjustment cylinder, and an electrohydraulic steering valve 270 disposed inside the steering cylinder 271 and having a steering spool 450.
  • the steering cylinder chamber 451 of the steering cylinder 271 is formed inside the rear portion of the hydraulic transmission case 350.
  • the steering piston 452 of the steering cylinder 271 is accommodated in the steering cylinder chamber 451 so as to be slidable up and down.
  • a pin shaft 453 protruding from the swash plate 57 a of the second hydraulic pump 57 is fitted to the side surface of the steering piston 452.
  • a steering spool 450 of the electrohydraulic steering valve 270 is slidably inserted into a through hole that penetrates the axial center portion of the steering piston 452.
  • the steering piston 452 is formed with an oil passage that communicates the upper and lower portions of the steering cylinder chamber 451.
  • the oil passage is configured to be connected or blocked by vertical sliding of the steering spool 450 based on the switching operation of the electrohydraulic steering valve 270 and supply hydraulic oil to the upper and lower oil chambers of the steering piston 452. ing.
  • the steering piston 452 slides up and down in the steering cylinder chamber 451, and the angle of the swash plate 57a of the second hydraulic pump 57 is changed.
  • a proportional control housing 454 incorporating a proportional control valve 455 for switching the electromagnetic hydraulic steering valve 270 in the vicinity of the steering cylinder chamber 451 is incorporated. Is detachably attached.
  • the proportional control spool 456 of the proportional control valve 455 in the proportional control housing 454 is configured to slide up and down similarly to the steering piston 452.
  • the steering spool 450 and the proportional control spool 456 are related so as to move together (up and down slide) via a linkage pin 458 provided on one end side of the spool operation arm 457 (linked together). .
  • the proportional control housing 454 is provided with a proportional control solenoid 459 for sliding the proportional control spool 456 up and down (see FIG. 10).
  • the proportional control solenoid 459 is configured to be excited when the steering handle 11 is operated, and to slide the proportional control spool 456 up and down in proportion to the operation amount.
  • a midway portion of the linkage pin 458 is fixed to one end side of the spool operation arm 457.
  • a turning operation shaft 356 that can be manually rotated is projected.
  • the turning operation shaft 356 of the embodiment protrudes rearward from the rear surface of the proportional control housing 454.
  • the proportional control solenoid 459 slides the proportional control spool 456 up and down correspondingly to the operation amount of the steering handle 11, so that the steering spool 450 similarly slides up and down via the linkage pin 458, and the steering cylinder 271.
  • the steering piston 452 is actuated to change the swash plate 57a angle of the second hydraulic pump 57.
  • the linkage pin 458 moves up and down in conjunction with the operation (sliding up and down) of both spools 450 and 456, the spool operation arm 457 moves around the turning operation shaft 356 (with the turning operation shaft 356 as a turning fulcrum). Turns up and down.
  • the turning operation shaft 356 rotates around its axis in accordance with the operation of the steering spool 450.
  • the spool operation arm 457 is turned up and down around the turning operation shaft 356 to move the linkage pin 458 up and down. Therefore, the steering spool 450 slides up and down to operate the steering piston 452 of the steering cylinder 271, and the angle of the swash plate 57 a of the second hydraulic pump 57 is electrically controlled by the electromagnetic hydraulic steering valve 270. It is changed independently and the discharge direction and the discharge amount of the hydraulic oil to the second hydraulic motor 58 are changed.
  • a shift steering controller 400 as a control means mounted on the traveling machine body 1 includes detection information of a main shift sensor 401 that detects an operation amount of the main shift lever 43 and a steering angle sensor 402 that detects a steering angle of the steering handle 11. Based on this, the shift operation control for adjusting the vehicle speed and the traveling direction of the traveling machine body 1 is performed by switching the electrohydraulic shift valve 272 and the electrohydraulic steering valve 270. That is, in the embodiment, there is no mechanical connection structure between the main transmission lever 43 and the steering handle 11 and the both hydraulic continuously variable transmissions 53 and 54, and a steer-by-wire system that electrically controls between them.
  • the shift steering control is executed.
  • the shift steering controller 400 includes a CPU that executes various arithmetic processes and controls, an EEPROM that stores control programs and data, a flash memory, a RAM that temporarily stores control programs and data, and It has an input / output interface.
  • a main shift sensor 401 that detects at least the amount of operation of the main shift lever 43, a steering angle sensor 402 that detects the steering angle of the steering handle 11, a low-speed output of the sub-shift output, neutral or A sub-shift switch 44 for selectively switching to high-speed output, a threshing switch 403 for detecting the on / off state of the threshing clutch 161, a reaping switch 404 for detecting the operating state of the reaping shift operating means (reaching shifting clutch), and the engine 14 Engine rotation speed sensor 405 for detecting the rotation speed (camshaft position of the output shaft 150), the rotation speed of the straight-ahead output of the first hydraulic motor 56 (straight-ahead vehicle speed, auxiliary transmission output gear 67 output), that is, a straight-forward hydraulic continuously variable transmission Straight traveling pickup rotation sensor 93 (straight traveling vehicle speed sensor) for detecting the shift output amount of the machine 53, second hydraulic pressure Rotational speed of the steering output over data 58 (turning speed
  • At least the electromagnetic hydraulic shift valve 272 as an electric actuator for operating the shift cylinder 273 for the swash plate 55 a of the first hydraulic pump 55 and the swash plate 57 a of the second hydraulic pump 57.
  • An electro-hydraulic steering valve 270 as an electric actuator for operating the steering cylinder 271, a cutting shift valve 282 for operating the cutting shift cylinder 280, a cutting constant speed valve 283 for operating the cutting constant speed cylinder 281, and a threshing clutch 161 are provided.
  • An electric motor 175 for threshing clutch to be turned on and off is connected.
  • the electrohydraulic shift valve 272 is electrically switched to operate the shift cylinder 273 to change the angle of the swash plate 55a of the first hydraulic pump 55.
  • a traveling speed change operation (forward / reverse switching operation) is performed in which the rotational speed of the linear motor shaft 60 of the hydraulic motor 56 is steplessly changed or reversed.
  • the steering cylinder 271 is operated to change the swash plate 57a angle of the second hydraulic pump 57.
  • the left and right steering operation for changing the rotation speed of the turning motor shaft 61 of the second hydraulic motor 58 steplessly or reversely is performed, the direction of travel is changed to the left and right, and the direction is changed at the field headland. Correct the course. Furthermore, the steering brake 79 maintains the turning motor shaft 61 in the stopped state (non-rotatable state) by the neutral operation (straight forward maintaining operation) of the steering handle 11 and the neutral operation of the subtransmission mechanism 51, and the second hydraulic motor 58. Is stopped and the turning output is stopped.
  • the shift steering controller 400 reads the detected values of the main shift sensor 401, the steering angle sensor 402, and the sub shift switch 44 (S1), and sets the sub shift switch 44 to the neutral position. If operated (S2: YES), the turning output stop control is performed to brake the steering brake 79 and stop the second hydraulic motor 58 (S3). If the sub-shift switch 44 is operated other than neutral (S2: NO), it is then determined whether or not the main shift lever 43 is in the neutral position (S4). If the main transmission lever 43 is in the neutral position (S4: YES), the turning output stop control (S3) described above is executed.
  • the steering angle of the steering handle 11 is determined (S5), and if the steering handle 11 is in the neutral position (straight forward maintaining position) ( (S5: YES), the electrohydraulic shift valve 272 is electrically switched in accordance with the operation amount of the main shift lever 43, and the shift travel control is performed for causing the traveling machine body 1 to travel straight forward or backward (S6). . If the steering handle 11 is operated to a position other than neutral (S5: NO), the electrohydraulic steering valve 270 is electrically switched in accordance with the amount of operation of the main transmission lever 43 and the steering handle 11 to travel. Left and right steering control is executed to change the traveling direction of the body 1 to the left and right (S7).
  • the shift steering controller 400 forcibly ends the above-described shift steering control (S9).
  • the switching operation of the electrohydraulic shift valve 272 and the electrohydraulic steering valve 270 according to the operation amount of the shift lever 43 and the steering handle 11 is disabled. Then, unless the combine is turned off and then turned on again, the shift steering control is not restored. For this reason, when the operation shafts 355 and 356 are manually rotated, the shift output adjustment of the hydraulic continuously variable transmissions 53 and 54 by the electrohydraulic shift valve 272 and the electrohydraulic steering valve 270 coexists.
  • the planetary gear mechanism 68 constituting the differential mechanism 52 is arranged on the bottom side in the mission case 88, and the auxiliary transmission mechanism 51 and the relay shaft 85 are arranged in front and rear above the planetary gear mechanism 68.
  • a rotating shaft of the reverse gear 84 is disposed between the planetary gear mechanism 68 and the relay shaft 85 in the vertical direction and on the rear side.
  • a main shift output counter shaft 70 is disposed between the planetary gear mechanism 68 and the relay shaft 85 in the front-rear direction and on the upper side, and a steering counter shaft 80 is disposed on the rear side of the main shift output counter shaft 70. Has been placed.
  • a linear motor shaft 60 is disposed above the main shift output counter shaft 70, and a turning motor shaft 61 is disposed above the steering counter shaft 80.
  • a steering brake 79 and a reduction gear 81 as wet brakes are provided on the turning motor shaft 61.
  • a pump shaft 59 of the first hydraulic pump 55 is disposed above the linear motor shaft 60, and a pump shaft 59 of the second hydraulic pump 57 is disposed above the turning motor shaft 61.
  • a travel input shaft 152 is arranged between the front and rear directions of both pump shafts and on the upper side.
  • an oil strainer 430 communicating with the suction filter 368 is disposed on the rear side of the planetary gear mechanism 68 in the bottom of the mission case 88.
  • the periphery of the oil strainer 430 is surrounded by partition ribs 431 formed at the bottom in the mission case 88.
  • An introduction hole 432 for introducing hydraulic oil is formed on the upper surface side of the partition rib 431. For this reason, the oil strainer 430 is blocked from the planetary gear mechanism 68 by the partition rib 431, so that the hydraulic oil around the oil strainer 430 can be prevented from being agitated by the rotation of the planetary gear mechanism 68.
  • the oil supply port 365 for supplying hydraulic oil is located in front of the linear motor shaft 60 and the PTO shaft 99 on the left side surface of the mission case 88.
  • five shafts that is, the straight pump shaft 59, the swing pump shaft 59, the straight motor shaft 60, the swing motor shaft 61, and the travel input shaft 152, are connected to the oil supply port 365. It will be located on the upper side. That is, these five shafts 59, 59, 60, 61, 152 do not rotate while immersed in the hydraulic oil, and the stirring resistance is reduced accordingly.
  • a return oil port 410 for returning the working oil from outside the mission case 88 is opened on the upper surface side of the mission case 88 (left upper surface front side in the embodiment).
  • a pair of reinforcing ribs 411 and 412 project inwardly on the upper side in the mission case 88 as a guide body for guiding the hydraulic oil returned from outside the mission case 88 toward the steering brake 79 from the return oil port 410. It is installed.
  • a rectilinear boss portion 413 that supports the bearing portion of the pump shaft 59 for rectilinear advance (first hydraulic pump 55) is provided inwardly on the upper left inner surface of the mission case 88.
  • a feed-side reinforcing rib 411 is integrally connected to the rectilinear boss 413.
  • the feed-side reinforcing rib 411 is inclined obliquely downward and rearward from the return oil port 410 toward the steering brake 79 so that the steering brake 79 side is lowered.
  • a turning boss portion 414 that supports the bearing portion of the pump shaft 59 for turning (second hydraulic pump 57) is also provided inwardly on the upper left inner surface of the mission case 88.
  • the receiving-side reinforcing rib 412 is integrally connected to the turning boss 414.
  • the receiving side reinforcing rib 412 is inclined forward and downward so that the steering brake 79 side is lowered.
  • Both the reinforcing ribs 411 and 412 have a tapered funnel shape in the right side cross-sectional view of FIG. 13, and the steering brake 79 is located at the narrowed tip.
  • the hydraulic oil that flows down from the return oil port 410 is sent to the steering brake 79 mainly by the guide of the feed side reinforcing rib 411 and falls on the steering brake 79.
  • the steering brake 79 is forcibly lubricated and lubricated. Therefore, regardless of the amount of hydraulic oil in the mission case 88, the shortage of the amount of oil supplied to the steering brake 79 that is not immersed in the hydraulic oil can be suppressed. Further, since the amount of hydraulic oil in the mission case 88 is not limited, the steering brake 79 can be provided in the mission case 88 at a position where it is not immersed in the hydraulic oil. That is, the degree of freedom in designing the steering brake 79 is improved.
  • both the reinforcing ribs 411 and 412 have a tapered funnel shape in the right side cross-sectional view of FIG. 13, the narrowed portion can function as an oil reservoir, and hydraulic oil is applied to the steering brake 79. There is also an advantage that it can be supplied stably. Furthermore, since the hydraulic oil from the return oil port 410 is guided to the steering brake 79 by the two reinforcing ribs 411 and 412 that ensure the rigidity of the mission case 88, the rigidity of the mission case 88 is ensured and the steering brake 79 is lubricated. Both functional improvement can be realized at low cost.
  • a communication groove 415 for distributing the hydraulic oil guided by the feed-side reinforcement rib 411 to the bearing portion of the straight-travel pump shaft 59 is provided in a part of the boss 413 for rectilinear movement near the feed-side reinforcement rib 411. Is formed.
  • a return conduit 416 for sending hydraulic oil from the outside toward the mission case 88 is connected to the return oil port 410 of the mission case 88.
  • a branch pipe 417 branches and extends from the return pipe 416 near the base portion near the mission case 88.
  • the branch pipe 417 is connected to the steering brake 79 on the left side of the mission case 88.
  • the return conduit 416 of the embodiment is connected to the return oil port 410 of the mission case 88 via the branch connector 418.
  • One end of the branch pipe 417 is connected to the branch connector 418, and the other end of the branch pipe 417 is connected to the steering brake 79 on the left side of the mission case 88.
  • the branch pipe 417 is located outside the mission case 88 and extends along the left outer side surface of the mission case 88.
  • the branch conduit 417 is externally attached to the mission case 88.
  • a part of the hydraulic oil returned from outside the mission case 88 is sent directly to the steering brake 79.
  • the remaining hydraulic oil is sent into the mission case 88 and guided onto the steering brake 79 by both reinforcing ribs 411 and 412. That is, the steering brake 79 is lubricated and lubricated by the hydraulic oil that has passed through the branch pipe 417 and the hydraulic oil guided by the two reinforcing ribs 411 and 412.
  • a PTO boss portion 420 is integrally provided on the upper left side of the mission case 88.
  • a PTO shaft 99 is rotatably supported by the PTO boss portion 420 via a pair of bearing bodies 421 and 422.
  • a PTO gear 423 that receives rotational power from a main shift output counter shaft 70 located below is fixed to an end portion of the PTO shaft 99 in the mission case 88.
  • a rectilinear transmission gear 50 that rotates integrally with the rectilinear motor shaft 60 is rotatably supported via a bearing body 425 on a rectilinear transmission boss 424 that is integrally provided on the upper right side of the mission case 88. .
  • the PTO gear 423 is supported on the PTO shaft 99 in a cantilever state, and similarly, the linear transmission gear 50 is supported on the linear motor shaft 60 in a cantilever state. Power transmission from the linear motor shaft 60 to the PTO shaft 99 is relayed by the main shift output counter shaft 70. Therefore, it is possible to place the PTO gear 423 and the straight transmission gear 50 so as to overlap each other in a side view (viewed in the axial direction) (see FIG. 23). As a result, the degree of freedom in arrangement of the PTO gear 423 and thus the PTO shaft 99 with respect to the mission case 88 is improved.
  • a hydraulic oil groove 426 for guiding the hydraulic oil in the mission case 88 between the two bearing bodies 421 and 422 for the PTO shaft 99 is formed on the upper side of the PTO boss portion 420.
  • a damming portion 427 that surrounds the longitudinal middle portion of the PTO shaft 99 is formed to protrude toward the PTO shaft 99 between the bearing bodies 421 and 422.
  • the inlet side of the hydraulic oil groove 426 is formed above the bearing body 422 near the inside of the mission case 88.
  • a guide rib 428 for guiding the hydraulic oil to the hydraulic oil groove 426 side is provided on the rotation downstream side of the PTO gear 423.
  • the outer bearing body 421 close to the PTO pulley 119 can be lubricated by lubricating the working oil, which is effective for ensuring the lubricity of the PTO shaft 99 where a large load is applied.
  • the presence of the damming portion 427 makes it easy to collect hydraulic oil around the bearing body 421 near the PTO pulley 119, and the lubricity of the PTO shaft 99 can be further improved.
  • the presence of the guide rib 428 makes it easy to feed the splashed oil of the PTO gear 423 to the hydraulic oil groove 426 side.
  • each axle 153 As shown in FIG. 25, the base end spline portion 434 formed on the base end side of each axle 153 is fitted so that the rotation center portion of the final gear 78b is slidable and relatively non-rotatable (spline fitting). ) A portion further inside the base end spline portion 434 of each axle 153 is rotatably supported by an inner boss tube portion 435 formed in the gear case 349 via a bearing body 436. A portion of each base spline portion 434 near the axle case 351 is rotatably supported by an outer boss cylinder portion 437 formed on the axle case 351 via a one-side seal bearing body 438. For this reason, the lower side of the mission case 88 can be easily sealed without using an expensive oil seal. In addition, since an oil seal is unnecessary, the number of parts can be reduced and the workability of assembling the axle 153 can be improved.
  • the hydraulic transmission case 350 including the hydraulic continuously variable transmissions 53, 54 for shifting the power of the engine 14 is provided in the hydraulic continuously variable transmission 53.
  • 54 is a work vehicle attached to one side upper part of the transmission case 88 that transmits the shift output to the left and right traveling units 2, and receives power from the engine 14 on the other side upper part of the transmission case 88.
  • An input pulley 155 and a PTO pulley 119 that is driven by a shift output from the hydraulic continuously variable transmissions 53 and 54 are disposed, and is operated in front of the PTO pulley 119 on the other side of the transmission case 88.
  • the oil supply port 365 for oil supply is provided, when supplying oil to the mission case 88, for example, an oil can containing hydraulic oil which is a heavy object There is no need to lift the transmission case above the transmission case 88, the refueling operation is simplified, and the burden on the operator in the refueling operation is reduced.
  • the oil supply port 365 is located at a midway height position in the vertical direction of the transmission case 88 that also serves as a hydraulic oil tank, it is possible to supply oil only to a position directly below the oil supply port 365 (the hydraulic oil is supplied until the oil supply port 365 is exceeded. Cannot be supplied). Accordingly, it is not necessary to supply oil in the mission case 88 more than necessary, and the power loss in the mission case 88 (rotational resistance of the gears 51 and 52) increases due to the excessive amount of hydraulic oil. The fear can be reliably suppressed.
  • the upper side in the mission case 88 is not filled with hydraulic oil, the hydraulic oil easily flows in the mission case 88, and the portion of the mission case 88 that is not in contact with the hydraulic oil. The surface area is much wider than before. Due to the fluidity of the hydraulic fluid and the heat radiation effect of the portion not in contact with the hydraulic fluid, the temperature rise of the hydraulic fluid as a whole can be suppressed.
  • an oil inspection window 367 is provided on the other side of the transmission case 88 below the oil supply port 365 and at a position lower than the PTO pulley 119.
  • a suction filter 368 is provided on one side of the mission case 88 at a position behind the oil detection window 365 and lower than the PTO pulley 119.
  • the oil detection window 367, the suction filter 368 are located at locations opposite to each other in the front-rear and left-right directions with the gears 52 below the mission case 88 interposed therebetween. That is, the oil detection window 367 and the suction filter 368 can be efficiently arranged by effectively using the internal space below the oil supply port 365 in the mission case 88, and the mission detection window 367 can transmit the mission. When the amount of hydraulic oil in the case 88 is checked, the presence of the suction filter 368 does not get in the way.
  • the front part of the traveling machine body 1 is laterally outward with the longitudinal axis 300 on the left side of the front part of the traveling machine body 1 as the center.
  • a harvesting device 3 that can be opened and rotated, and the oil supply port 365 and the oil inspection window 367 on the left side surface of the mission case 88 in a state where the harvesting device 3 is opened and rotated laterally outward. Therefore, if the reaping device 3 is opened laterally outward and rotated, a wide working space is provided around the oil supply port 365 and the oil inspection window 367 in the mission case 88. It will be possible. For this reason, maintenance workability for the mission case 88 such as inspection before use and refueling work is remarkably improved.
  • the hydraulic continuously variable transmissions 53 and 54 are provided with emergency manual operating tools 355 and 356 for manually operating the shift output separately from the electric actuators 272 and 270.
  • the emergency manual operating tools 355 and 356 is configured to operate in conjunction with the driving of the electric actuators 272, 270, so that the hydraulic continuously variable transmission 53 is operated from the operation of the emergency manual operating tools 355, 356 (361, 362). , 54 can be easily visually confirmed.
  • the hydraulic continuously variable transmissions 53 and 54, the adjustment cylinders 273 and 271 that adjust the speed of the hydraulic pumps 55 and 57, and the adjustment cylinders 273 and 271 are provided.
  • the electrohydraulic valves 272 and 270 as the electric actuators to be reciprocated and the proportional control valves 445 and 455 for switching the electrohydraulic valves 272 and 270 are provided, and the electrohydraulic valves 272 and 270 are provided.
  • the spools 440 and 450 of the proportional control valves and the proportional control spools 446 and 456 of the proportional control valves 445 and 455 are linked to each other via linkage pins 448 and 458 provided on one end side of the spool operation arms 447 and 457.
  • the other end of the spool operating arms 447 and 457 can be manually rotated.
  • the operation shafts 355 and 356 as emergency manual operation tools are provided, and the linkage pins 448 and 458 are connected to the operation shafts 355 and 356 in conjunction with the operations of the spools 440 and 446 (450 and 456).
  • the hydraulic pump Since the operation shafts 355 and 356 are rotated by rotating the spool operation arms 447 and 457 around the rotation center, the hydraulic pump is connected via the proportional control valves 445 and 455.
  • a remote operation structure for controlling the shift of the hydraulic pumps 55 and 57 and a manual operation structure for controlling the shift of the hydraulic pumps 55 and 57 via the operation shafts 355 and 356 can be compatible.
  • the operating state of the spools 440 and 446 (450 and 456) can be confirmed from the rotating state of the operation shafts 355 and 356. Even if an electric system trouble occurs, if the operation shafts 355 and 356 are manually operated, the main transmission lever 43 and the steering handle 11 are not effective, for example, even from the farm field. A limp home operation (degenerate operation) that escapes (combines) can be executed. Accordingly, there are more options for dealing with emergency situations in the work vehicle, which contributes to improving the handleability of the work vehicle.
  • the hydraulic continuously variable transmissions 53 and 54, the adjusting cylinders 273 and 271, and the hydraulic hydraulic valves 272 and 270 are provided.
  • the proportional control housings 444 and 454 having the proportional control valves 445 and 455, the spool operating arms 447 and 457, and the operating shafts 355 and 356 are proportional to the spools 440 and 450 of the electromagnetic hydraulic valves 272 and 270, respectively.
  • the control cylinders 273 and 271 and the electromagnetic hydraulic valve 272 are detachably attached to the outer surface of the hydraulic transmission case 350 so that the proportional control spools 446 and 456 of the control valves 445 and 455 are close to each other.
  • a hydraulic continuously variable transmission 54 that shifts the power of the engine 14, and a transmission case 88 that transmits the shift output of the hydraulic continuously variable transmission 54 to the left and right traveling units 2.
  • the work case has a wet brake 79 for braking the shift output of the hydraulic continuously variable transmission 54 in the mission case 88, and the wet brake 79 is provided in the mission case 88.
  • a return oil port 410 is opened on the upper surface side of the transmission case 88 and is positioned above the hydraulic oil surface, and the hydraulic oil returned from outside the transmission case 88 is transferred from the return oil port 410 to the wet brake.
  • the wet brake 79 Since guide bodies 411 and 412 for guiding toward the vehicle 79 are provided in the mission case 88, they flow down from the return oil port 410. Aggressive media is sent over the wet brake 79 in the guide of the guide body 411, 412, befall to the wet brake 79. As a result, the wet brake 79 is forcedly lubricated and lubricated. Therefore, regardless of the amount of hydraulic oil in the transmission case 88, it is possible to suppress an insufficient amount of oil to be applied to the wet brake 79 that is not immersed in the hydraulic oil. Further, since the amount of hydraulic oil in the mission case 88 is not limited, the wet brake 79 can be provided in the mission case 88 at a position not immersed in the hydraulic oil. In other words, the wet brake 79 has an advantage that the degree of design freedom in layout is improved.
  • the guide body is constituted by the reinforcing ribs 411 and 412 protruding into the mission case 88. Therefore, the reinforcing rib 411 for ensuring the rigidity of the mission case 88. , 412 guides the hydraulic oil from the return oil port 410 to the wet brake 79. Therefore, both the securing of the rigidity of the transmission case 88 and the improvement of the lubrication function for the wet brake 79 can be realized at low cost.
  • a return pipe 416 is connected to the return oil port 410 of the mission case 88, and a branch pipe 417 branched from the return pipe 416 is connected to the return pipe 416. Since it is connected to the location of the wet brake 79 in the mission case 88 and the branch pipe 417 is located outside the mission case 88, the hydraulic oil passing through the branch pipe 417 and the guide body The wet brake 79 is lubricated and lubricated by the hydraulic oil guided at 411 and 412. Therefore, even if the shape of the mission case 88 is not particularly changed, in combination with the presence of the guide bodies 411 and 412, it is possible to easily solve the shortage of the amount of oil supplied to the wet brake 79.
  • the present invention is not limited to the above-described embodiment, and can be embodied in various forms.
  • the present invention is not limited to the above-described combine, but can be widely applied to various work vehicles such as farm work machines such as tractors and rice transplanters and special work vehicles such as crane cars.
  • work vehicles such as farm work machines such as tractors and rice transplanters and special work vehicles such as crane cars.
  • the structure of each part is not limited to embodiment of illustration, A various change is possible in the range which does not deviate from the meaning of this invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Environmental Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Harvester Elements (AREA)
PCT/JP2011/050982 2010-03-15 2011-01-20 作業車両及びその例としてのコンバイン WO2011114769A1 (ja)

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CN201180000859.7A CN102292233B (zh) 2010-03-15 2011-01-20 作业车辆及作为该作业车辆的例子的联合收割机

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JP2010057433A JP5437865B2 (ja) 2010-03-15 2010-03-15 作業車両及びその例としてのコンバイン
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JP2010057434A JP5437866B2 (ja) 2010-03-15 2010-03-15 作業車両

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US20170097074A1 (en) * 2015-10-02 2017-04-06 Deer & Company Corn head row unit gearbox lubrication
US10130038B2 (en) 2015-10-02 2018-11-20 Deere & Company Corn head row unit gearbox drive shaft seal

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CN103291893B (zh) * 2012-02-23 2018-06-15 株式会社久保田 作业车辆的变速器及联合收割机的变速器
CN103363076A (zh) * 2012-03-31 2013-10-23 高邮市平安开沟机制造有限公司 开沟机齿轮箱
KR102376683B1 (ko) * 2016-06-29 2022-03-21 가부시끼 가이샤 구보다 동력 전동 장치
KR101896832B1 (ko) 2017-03-29 2018-09-11 주식회사기원전자 가상 터미널을 갖는 농기계
JP6910970B2 (ja) * 2018-01-10 2021-07-28 株式会社クボタ 作業車両用の制御装置

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US10130038B2 (en) 2015-10-02 2018-11-20 Deere & Company Corn head row unit gearbox drive shaft seal

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CN102292233B (zh) 2016-02-17
KR20130040681A (ko) 2013-04-24
CN102292233A (zh) 2011-12-21
KR101701945B1 (ko) 2017-02-02

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