JP5457083B2 - Combine - Google Patents

Description

The present invention relates to a feed Konbai down to collect combine, or harvests fodder culms as feed to collect grain harvests culms were planted in the field, more particularly, a pair of left and right traveling crawlers It is related with the combine provided with traveling parts, such as.

  Conventionally, a traveling vehicle such as a combiner includes a traveling machine body equipped with an engine, and a pair of left and right traveling crawlers are mounted on the traveling machine body, and the pair of left and right traveling crawlers are driven and controlled to move in a farm field or the like. ing. In addition, the combine cuts the stock of uncut cereal planted in the field with a cutting blade device, conveys the cereal to a threshing device with a cereal conveying device as a cereal conveying means, and The cereal is threshed and the grains are collected. (For example, refer to Patent Document 1) Conventionally, a track frame that includes a rolling actuator that corrects the tilting posture of the traveling aircraft in the left-right direction and a pitching actuator that corrects the tilting posture of the traveling aircraft in the front-rear direction, and on which the traveling crawler is mounted. The track frame is connected to the traveling machine body via the front link and the rear arm in the form of parallel links, and the rolling actuator is connected to the front arm and the rear arm via the connecting rod via the front and rear tilt arms. In addition, the configuration is such that the tilting posture in the left-right direction of the traveling machine body is changed by the operation of the rolling actuator (see, for example, Patent Document 1 and Patent Document 2).

Japanese Utility Model Publication No. 6-28387 JP 2000-106740 A

  The prior art (Patent Document 1) includes a front-rear connecting rolling frame that connects front and rear left and right tilting arms, and a pitching actuator is provided in the middle of the front-rear connecting rolling frame extending in the front-rear direction. Since the tilting posture of the direction is changed, when the pitching actuator is operated, a twisting force (mainly compression force) other than the expansion / contraction direction acts on the front / rear connecting rolling frame, and the front / rear connecting rolling frame and its There is a structural problem such as easily damaging the connecting portion. Further, in the prior art (Patent Document 2), the rolling crawler and the traveling machine body are prevented from interfering with each other by simultaneously operating the rolling actuator in conjunction with the operation of the pitching actuator that changes the tilting posture of the traveling machine body in the front-rear direction. Therefore, there are structural problems such as a structure in which the track frame is connected to the traveling machine body, and a control controller for the pitching actuator or the rolling actuator cannot be easily configured.

  An object of the present invention is to provide a traveling vehicle that can easily prevent the traveling crawler mounted on the track frame and the traveling body from interfering with each other, while the connection structure between the traveling body and the track frame can be easily configured. It is to provide.

In order to achieve the above object, the combine according to the first aspect of the present invention provides a rolling actuator (38) for correcting the tilting posture of the traveling aircraft body (1) in the left-right direction and an inclination posture of the traveling aircraft body (1) in the front-rear direction. In the combine provided with the pitching actuator (177) to be corrected, when the traveling machine body (1) is supported at the lowest position, the rolling actuator (38) is operated to raise the vehicle height, and the traveling machine body (1 ) Is supported at a predetermined height position, and the pitching actuator (177) is tilted forward or backward, and the maximum backward tilt angle of the traveling body (1) by the pitching actuator (177). The maximum forward tilt angle (F) of the traveling machine body (1) by the pitching actuator (177) is larger than (R). It is one that is set.

According to a second aspect of the present invention, in the combine according to the first aspect, a left / right inclination sensor (374) for detecting a right / left inclination of the traveling machine body (1) and a left ground height of the traveling machine body (1). A left vehicle height sensor (375) and a right vehicle height sensor (376) for detecting the height and right ground height, and a front / rear inclination sensor (381) for detecting a front / rear direction inclination of the traveling machine body (1), The structure is such that the rolling actuator (38) is operated to raise or lower the vehicle height to change the inclination of the traveling body (1) in the left-right direction, the left vehicle height sensor (375) and the right vehicle Based on the detection result of the high sensor (376) and the detection result of the front / rear tilt sensor (381), the pitching actuator (177) is configured to be capable of tilting back and forth.

According to a third aspect of the present invention, in the combine according to the first aspect, the pitching actuator (177) can be tilted forward when the traveling machine body (1) is supported at the highest position. Is.

  According to a fourth aspect of the present invention, in the traveling vehicle according to the first aspect, when the traveling body (1) is supported at the highest position, the rolling actuator (38) is operated to lower the vehicle height. The pitching actuator (177) can be tilted backward while the traveling machine body (1) is supported at a predetermined height position.

According to the first aspect of the present invention, the rolling actuator (38) for correcting the tilting posture in the left-right direction of the traveling machine body (1) and the pitching actuator (177) for correcting the tilting posture in the front-rear direction of the traveling machine body (1). in combined with a, when the traveling machine body (1) is supported on the top lowered position, the rolling actuator (38) by vehicle height increasing operation, the traveling machine body (1) to the predetermined height position The pitching actuator (177) is tilted forward or backward in a supported state, with respect to the maximum rearward tilt angle (R) of the traveling machine body (1) by the pitching actuator (177). wherein the maximum because before those that are larger inclination angle (F) is of the traveling machine body (1) according to pitching actuator (177), Compared to come structure, can easily configure a connection structure of the traveling machine body (1) and the running part (track frame, etc.). In addition, it is possible to easily prevent the traveling unit (such as a traveling crawler attached to a track frame) and the traveling machine body (1) from interfering with each other. For example, the traveling machine body (1) can be tilted forward without being restricted by a lowermost stopper or the like that sets the lower limit of the vehicle height adjustment range of the rolling actuator (38). Further, when the pitching actuator (177) is tilted backward, it is possible to prevent the traveling unit (traveling crawler, etc.) from interfering with the traveling machine body (1), and the traveling machine body (1) is brought into a tilted posture. It can operate smoothly.

  According to the invention which concerns on Claim 2, the left-right inclination sensor (374) which detects the inclination of the left-right direction of the said traveling body (1), and the left ground height and the right ground height of the said traveling body (1) are detected. A left vehicle height sensor (375) and a right vehicle height sensor (376), and a front / rear inclination sensor (381) for detecting a front / rear inclination of the traveling machine body (1), and the rolling actuator (38) The structure is configured to change the horizontal inclination of the traveling machine body (1) by raising or lowering the vehicle height, and the detection results of the left vehicle height sensor (375) and the right vehicle height sensor (376) And the pitching actuator (177) can be tilted forward and backward based on the detection result of the forward / backward tilt sensor (381). When actuating tilted backward, the prevent the travel section to the traveling machine body (1) (driving crawlers, etc.) from interfering, be tilted back and forth smoothly the traveling machine body (1).

  According to the third aspect of the invention, the pitching actuator (177) is configured to be able to tilt forward when the traveling machine body (1) is supported at the highest position. The traveling machine body (1) can be easily changed to a predetermined forward leaning posture while maintaining (1) at the highest position. That is, the traveling machine body (1) can be smoothly operated in the forward tilted posture without lowering the vehicle height.

  According to the invention which concerns on Claim 4, when the said traveling body (1) is supported by the highest position, the said rolling actuator (38) is made to carry out a vehicle height lowering operation, and the said traveling body (1) is predetermined. Since the pitching actuator (177) is configured to be able to tilt backward while being supported at a height position, the pitching actuator (177) travels to the traveling machine body (1) when the pitching actuator (177) is tilted backward. It is possible to prevent the parts (travel crawlers and the like) from interfering with each other, and the travel machine body (1) can be smoothly operated in the backward tilt posture.

It is a side view of the combine for 6-saw cutting of 1st Embodiment of this invention. It is the same top view. It is side surface explanatory drawing of a reaping apparatus. It is a plane explanatory view of a reaping device. FIG. 2 is a drive system diagram of the combine of FIG. 1. It is drive system diagrams, such as a mission case. It is drive system diagrams, such as a counter case. FIG. 2 is a hydraulic circuit diagram of the combine of FIG. 1. It is a side view of a traveling machine body and a traveling crawler part. It is the same top view. It is side surface explanatory drawing which moved the traveling body up. FIG. 5 is an explanatory diagram of a front descending side in which a traveling machine body is moved upward and tilted forward. It is front-downside side explanatory drawing which made the traveling body tilt forward. It is a back descending side surface explanatory view which moved the traveling body up and inclined backward. It is back down side surface explanatory drawing which made the traveling body tilt backward. It is a rear view perspective view of a traveling crawler part. It is a diagram which shows the relationship between the ground height of a traveling body and the front-back inclination angle of a traveling body. It is a functional block diagram of a control circuit of the attitude control means. It is a flowchart of attitude control. It is a flowchart of the cereal cutting height control. It is a flowchart of the inclination control of the left-right direction and the front-back direction. It is side surface explanatory drawing which shows a traveling body, a track frame, and a mission case. It is side explanatory drawing which shows a vehicle height adjustment hydraulic cylinder, the hydraulic cylinder for front-back inclination, a rolling link mechanism, and a pitching link mechanism. It is a top view perspective view of FIG.

  DESCRIPTION OF EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings. FIG. 1 is a left side view of the combine, and FIG. 2 is a plan view of the combine. With reference to FIG.1 and FIG.2, the whole structure of a combine is demonstrated. In the following description, the left side in the forward direction of the traveling machine body 1 is simply referred to as the left side, and the right side in the forward direction is also simply referred to as the right side. As shown in FIGS. 1 and 2, a traveling machine body 1 supported by a pair of left and right traveling crawlers 2 as a traveling unit is provided. At the front part of the traveling machine body 1, a 6-row mowing device 3 that takes in while harvesting cereals is mounted by a single-acting lifting hydraulic cylinder 4 so as to be movable up and down around the mowing pivot fulcrum shaft 4 a. The A threshing device 5 having a feed chain 6 and a grain tank 7 for storing grains taken out from the threshing device 5 are mounted side by side on the traveling machine body 1. 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 throw opening 9 of the discharge auger 8 to a truck bed or a container. ing. An operation cabin 10 is provided on the right side of the reaping device 3 and on the front side of the grain tank 7.

  In the driving cabin 10, there are disposed a steering handle 11, a driving seat 12, a main transmission lever 43, a sub transmission switch 44, and a work clutch lever 45 for turning on and off the threshing clutch and the cutting clutch. The operation cabin 10 is provided with a step (not shown) on which an operator gets on, a handle column 46 provided with the steering handle 11, and a lever column 47 provided with the levers 43 and 45, the switch 44 and the like. ing. An engine 14 as a power source is disposed in the traveling machine body 1 below the driver seat 12.

  As shown in FIG. 1, left and right track frames 21 are arranged on the lower surface side of the traveling machine body 1. The track frame 21 includes a drive sprocket 22 that transmits the power of the engine 14 to the traveling crawler 2, a tension roller 23 that maintains the tension of the traveling crawler 2, and a plurality of track rollers that hold the ground side of the traveling crawler 2 in a grounded state. 24 and an intermediate roller 25 that holds the non-grounded side of the traveling crawler 2 are provided. The driving sprocket 22 supports the front side of the traveling crawler 2, the tension roller 23 supports the rear side of the traveling crawler 2, the track roller 24 supports the grounding side of the traveling crawler 2, and the intermediate roller 25 supports the non-traveling crawler 2. Support the ground side.

  As shown in FIGS. 1 and 2, below the cutting frame 221 connected to the cutting rotation fulcrum shaft 4 a of the cutting device 3, a clipper that cuts the stock of uncut grain cereal (grain culm) planted in the field. A type of cutting blade device 222 is provided. In front of the mowing frame 221, a stalk raising apparatus 223 for six stalks that raises an uncut cereal cultivated in the field is disposed. Between the culm pulling device 223 and the front end (feed start side) of the feed chain 6, a culm conveying device 224 that conveys the chopped culm harvested by the cutting blade device 222 is arranged. In addition, in front of the lower part of the grain raising apparatus 223, a weeding body 225 corresponding to six strips for weeding the uncut grain rice planted in the field is provided. While the traveling crawler 2 is driven by the engine 14 and moved in the field, the uncut cereal grains planted in the field are continuously cut by the cutting device 3.

  Next, the structure of the reaping device 3 will be described with reference to FIGS. 3 and 4. As shown in FIGS. 3 and 4, the cutting frame 221 includes a cutting input case 16 that is rotatably supported on the bearing stand 15 on the front end side of the traveling machine body 1, and a vertical transmission that extends forward from the cutting input case 16. A case 18, a horizontal transmission case 19 extending in the left-right direction on the front end side of the vertical transmission case 18, and a weeding frame 20 for six strips connected to the horizontal transmission case 19 are formed. 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 grain raising device 223 includes a six-case raising case 129 having a plurality of raising tines 128 for erecting an uncut grained rice cake that has been weeded by the weed board 225. The grain feeder 224 includes left and right right star wheels 130R and left and right right scooping belts 131R that squeeze the stock side of the right two grain grains introduced from the two right side pulling cases 129, and the left side. Left and right left star foils 130L and left and right left rake belts 131L that scrape the stock side of the left two cereal grains introduced from the two pulling cases 129, and the center introduced from the center two pulling cases 129 It has left and right central star foils 130C and left and right central scoring belts 131C for scooping the stock side of the cereals for two strips.

  The cutting blade device 222 is scraped by the right star wheel 130R and the right and left right scooping belts 131R, the left star wheel 130L and the left and right left scooping belts 131L, the central star wheel 130C, and the left and right central scoring belts 131C. It has clipper-shaped left and right cutting blades 132 for cutting the stock of the cereal grains.

  In addition, the cereal carrying device 224 is configured to convey the right side of the right side of the stock of the right side of the chopped cereal that has been raked by the right side of the star foil 130R and the rake belt 131R. And left stock transport that joins the stock side of the left two cropped grains that have been scraped by the left two star foils 130L and the scraping belt 131L to the transport end of the right stock transport chain 133R In the middle of the transport of the right stock transport chain 133R by transporting the chain 133L, the stock base side of the harvested cereals of the central two strips that have been scraped by the star foil 130C and the scoring belt 131C of the two central strips to the rear It has a central stock transport chain 133C to be merged. By using 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 6 stakes from the right stock former transport chain 133R, and fed from the end of conveyance of the vertical conveyor chain 134. Auxiliary stock source transport chains 135 and 136 as auxiliary transport means for transporting the stock source side of the harvested cereals for six strips are 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 chains 135 and 136.

  The grain culm transporting device 224 is transported by the right stalk transporting tine 137R that transports the tip of the harvested cereals for the two right-hand ridges transported by the right stock transporting chain 133R and the left stock transporting chain 133L. Left tip transport tine 137L that transports the tip side of the left-hand two-line harvested grain culm, and central tip transport tine that transports the tip side of the center two-part harvested grain culm that is transported by the central stock transport chain 133C 137C, and a rear tip transport tine 138 that transports the tip of the harvested cereal rice straw for six strips transported by the vertical transport chain 134. 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.

  Next, the drive structure of the combine will be described with reference to FIG. As shown in FIG. 5, the pulling lateral transmission shaft 143 is connected to the cutting input shaft 17 through 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 rear surface on the upper end 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. 5, 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 configured to be driven synchronously via the 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).

  As shown in FIG. 5, one end of the vertical transmission shaft 140 in the vertical transmission case 18 is connected to the cutting input shaft 17. The lateral transmission shaft 141 in the lateral transmission case 19 is connected to the other end side of the longitudinal 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 conveying device 224. In other words, the right transmission drive shaft 146 is connected to the vertical transmission shaft 140. Via the vertical transmission shaft 140 and the right transport drive shaft 146, the right stock former transport chain 133R and the right tip transport tine 137R, the right star wheel 130R and the right take-up belt 131R are driven. Further, the auxiliary stock former transport chains 135 and 136 and the rear tip transport tine 138 are driven via the vertical transmission shaft 140 and the rear transport drive shaft 147.

  Further, the left transport 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. Further, 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.

  Next, with reference to FIG.1 and FIG.2, the structure of the threshing apparatus 5 is demonstrated. As shown in FIGS. 1 and 2, 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. In addition, the rotating shaft core line of the handling cylinder 226 extends along the conveying direction of the cereal by the feed chain 6 (in other words, the traveling direction of the traveling machine body 1). The 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.

  As shown in FIG. 1, on the lower side of the rocking sorter 227, there are a first conveyor 231 for taking out the grain (first thing) sorted by the rocking sorter 227 and two branches such as 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.

  As shown in FIG. 1, the rocking sorter 227 is subjected to rocking sorting (specific gravity sorting) by the feed pan 238 and the chaff sheave 239 from the cereal that has 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 portion of the first conveyor 231 that protrudes outward from one side wall (right side wall in the embodiment) of the threshing device 5 near the grain tank 7. . The grain taken out from the first conveyor 231 is carried into the grain tank 7 via the cereal conveyor 233 and collected in the grain tank 7.

  Further, as shown in FIG. 1, 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 thing falling below the chaff sheave 239 is provided. As for the second thing that has fallen from the chaff sheave 239, the dust and swarf in the grain are removed by the sorting air from the sorting fan 241 and dropped onto the second conveyor 232. 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 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 item is returned to the upper surface side of the swing sorter 227 and re-sorted.

  On the other hand, as shown in FIGS. 1 and 2, 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 sewage chain 234 (the slag from which the grain has been threshed) is discharged to the rear of the traveling machine body 1 in a long state, or the rear part of the threshing device 5 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.

  Next, drive structures of the reaping device 3, the threshing device 5, the feed chain 6, the sewage chain 234, the sewage cutter 235, and the like will be described with reference to FIG. As shown in FIG. 5, the output shaft 150 projects from the left side of the engine 14. The traveling input shaft 152 of the mission case 50 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 50 and shifted. Thereafter, 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.

  As shown in FIG. 5, a radiator cooling fan 154 for cooling the engine 14 is provided on the output shaft 150 protruding to the right side of the engine 14. Further, 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. Is discharged into a container or the like.

Moreover, as shown in FIGS. 5 and 7, 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 drive of the threshing selection work input shaft 165 to the handling cylinder 226 and the processing cylinder 230. A threshing drive shaft 160 for transmitting force 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. On threshing drive shaft 160, placing the threshing drum low gear 115 and thresher fast gear 11 6. The rotational force of the threshing sorting work input shaft 165 is transmitted to the threshing drive shaft 160 through the threshing drum low gear 115 or threshing drum fast gear 11 6.

  The threshing drive shaft 160 is connected to a treatment cylinder shaft 163 that supports the treatment cylinder 226 via a treatment cylinder drive belt 117 and a processing cylinder shaft 164 that supports the treatment cylinder 230. 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. In addition, 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 sorter 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.

  As shown in FIGS. 5 and 6, the transmission case 50 has a linearly-traveling (traveling main transmission) hydraulic continuously variable transmission mechanism 53 having a pair of linearly-traveling first hydraulic pump 55 and a linearly-moving first hydraulic motor 56. A turning hydraulic continuously variable transmission mechanism 54 having a pair of turning second hydraulic pump 57 and turning second hydraulic motor 58 is provided. The travel input shaft 152 of the mission case 50 is connected to the first hydraulic pump 55 and the second hydraulic pump 57, respectively, and is driven. A PTO shaft 99 is disposed in the mission case 50. The PTO shaft 99 is driven by the first hydraulic motor 56. One end side of the PTO shaft 99 protrudes from the transmission case 50 to the left outer side.

  As shown in FIG. 5, a counter gear case 89 is provided on the traveling machine body 1 on the left side of the engine 14 and on the front side of the threshing device 5. 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 are arranged.

  As shown in FIG. 7, a one-way clutch 105 that transmits the vehicle speed tuning rotational force of the vehicle speed tuning shaft 100 is provided on the vehicle speed tuning shaft 100 in the counter gear case 89. A cutting transmission shaft 101 is coupled to the vehicle speed tuning shaft 100 via a cutting transmission mechanism 108 and a one-way clutch 105. The cutting transmission mechanism 108 includes a low speed side transmission gear 106 and a high speed side transmission gear 107. The low speed side transmission gear 106 or the high speed side transmission gear 107 is selectively engaged with the cutting transmission shaft 101 by a cutting speed change operation means (not shown) for performing low speed, neutral (zero rotation) and high speed cutting speed changes. The tuning shaft 100 is configured to transmit a cutting shift output to the cutting transmission shaft 101 via the cutting transmission mechanism 108.

  As shown in FIG. 7, the harvesting shaft 101 is connected to the threshing selection work input shaft 165 via the constant rotation mechanism 111. The constant rotation mechanism 111 includes a low speed side constant rotation gear 109 and a high speed side constant rotation gear 110. The cutting drive shaft 102 is connected to the cutting transmission shaft 101 via a torque limiter 114. 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 109. Therefore, the cutting input shaft 17 can be operated at a constant rotational speed from the low-speed constant rotating gear 109 regardless of the moving speed of the traveling machine body 1 to maintain the cutting operation, and the direction change workability on the headland in the field can be improved. It can be improved.

  Further, a rotational output at a constant rotational speed that is 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 107 is transferred from the threshing sorting operation input shaft 165 via the high speed side constant rotational gear 110. Is transmitted to. Therefore, the cutting input shaft 17 can be operated at a constant rotational speed from the high-speed side constant rotating gear 110 that is faster than the maximum speed of the vehicle speed synchronization output, and the efficiency of cutting the fallen cedar can be improved. It is to be noted that the cutting input shaft 17 is operated by a rotational force equal to or less than the torque set by the torque limiter 114, thereby preventing the cutting blade 132 and the like from being damaged.

  The counter gear case 89 is provided with a feed chain tuning mechanism 112 having a planetary gear type transmission structure 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 112 and transmitted to the feed chain drive shaft 103. That is, by operating the feed chain 6 via the feed chain tuning mechanism 112, the feed chain is secured while ensuring the minimum rotational speed (constant rotational speed from the low-speed constant rotational gear 109) necessary for conveying the cereal. The cereal conveyance speed of 6 can be changed in synchronization with the vehicle speed.

  As shown in FIG. 6, 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. In the straight-travel hydraulic continuously variable transmission mechanism 53, hydraulic oil is appropriately fed from the first hydraulic pump 55 toward the first hydraulic motor 56 with the power transmitted to the pump shaft 59. Similarly, in the turning hydraulic continuously variable transmission mechanism 54, hydraulic oil is appropriately fed from the second hydraulic pump 57 toward the second hydraulic motor 58 with the power transmitted to the pump shaft 59.

  A work pump 91 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 work pump 91 is configured to be driven in conjunction with the pump shaft 59. The rectilinear hydraulic continuously variable transmission mechanism 53 changes and adjusts the inclination angle of the rotary swash plate in the first hydraulic pump 55 in accordance with the amount of operation of the main transmission lever 43 and the operation handle 11 disposed in the operation unit 9. By changing the discharge direction and discharge amount of the hydraulic oil to the first hydraulic motor 56, the rotation direction and the rotation speed of the linear motor shaft 60 protruding from the first hydraulic motor 56 are arbitrarily adjusted. ing.

  The rotational power of the linear motor shaft 60 is transmitted from the linear transmission gear mechanism 62 to the auxiliary transmission gear mechanism 51. The auxiliary transmission gear mechanism 51 includes an auxiliary transmission low speed gear 62 and an auxiliary transmission high speed gear 63 that are switched by an auxiliary transmission shifter 64. By operating the auxiliary transmission switch 44 disposed in the lever column 47, the output rotational speed of the linear motor shaft 60 is switched to two speed stages, low speed or high speed. Note that a neutral position (a position where the output of the sub-shift is zero) is provided between the low speed and the high speed of the sub-shift. A parking brake shaft 65 provided on the output side of the auxiliary transmission gear mechanism 51 is provided with a wet multi-plate disc type parking brake 66.

  Rotational power from the auxiliary transmission gear mechanism 51 is transmitted to the differential mechanism 52 from an auxiliary transmission output gear 67 fixed to the parking brake shaft 65. The differential mechanism 52 includes a pair of planetary gear mechanisms 68 arranged in a symmetrical manner and a relay shaft 69 located between the planetary gear mechanism 68 and the parking brake shaft 65. The auxiliary transmission output gear 67 of the parking brake shaft 65 meshes with an intermediate gear 70 a attached to the relay shaft 69.

  Each of the left and right planetary gear mechanisms 68 can rotate one sun gear 71, a plurality of planetary gears 72 meshing with the sun gear 71, a ring gear 73 meshing with the planetary gear 72, and the plurality of planetary gears 72 on the same circumference. And a carrier 74 to be arranged. The carriers 74 of the left and right planetary gear mechanisms 68 are arranged on the same axis so as to oppose 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. Further, the left and right ring gears 73 are connected to the relay shaft 69 by engaging the outer teeth of the outer peripheral surface with the left and right intermediate gears 70b. Each ring gear 73 is rotatably supported by left and right axles 153 projecting left and right outward from the outer surface of the carrier 74. Left and right drive sprockets 22 are attached to the left and right axles 153. Accordingly, the rotational power transmitted from the auxiliary transmission gear mechanism 51 to the left and right planetary gear mechanisms 68 is transmitted from the axle 153 of each carrier 74 to the left and right drive sprockets 22 at the same rotational speed in the same direction, and left and right traveling crawlers. 2 is driven.

  The turning hydraulic continuously variable transmission mechanism 54 changes and adjusts the inclination angle of the rotary swash plate in the second hydraulic pump 57 in accordance with the amount of rotation of the main transmission lever 43 and the steering handle 11 disposed in the control unit 9. Then, by changing the discharge direction and discharge amount of the hydraulic oil to the second hydraulic motor 58, the rotation direction and the rotation speed of the turning motor shaft 61 protruding from the second hydraulic motor 58 are arbitrarily adjusted. It is configured.

  Further, a steering brake 79 provided on a turning motor shaft 61 (steering brake shaft), a steering clutch shaft 80 having a steering clutch 81, and a left input gear connected to the left center gear 76 in the transmission case 50. A mechanism 82 and a right input gear mechanism 83 that meshes with the right center gear 76 via a reverse gear 84 are provided. The rotational power of the turning motor shaft 61 is transmitted to the steering clutch shaft 80 via the steering clutch 81. The rotational power transmitted to the steering clutch shaft 80 is transmitted to the left and right input gear mechanisms 82 and 83 corresponding thereto.

  When the auxiliary transmission gear mechanism 51 is neutral, power transmission from the first hydraulic motor 56 to the left and right planetary gear mechanisms 68 is blocked. When a sub-shift output other than neutral is output from the sub-transmission gear 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. On the other hand, when the steering brake 79 is engaged and the steering clutch 81 is disengaged, power transmission from the second hydraulic motor 58 to the left and right planetary gear mechanisms 68 is blocked. When the steering brake 79 is turned off and the steering clutch 81 is turned on, the rotational power of the second hydraulic motor 58 is transmitted to the left center gear 76 via the left input gear mechanism 82 and the reverse gear 84. On the other hand, it is transmitted to the right center gear 76 via the right input gear mechanism 83. As a result, at the time of forward rotation (reverse rotation) of the second hydraulic motor 58, the left center gear 76 rotates in the reverse direction (forward rotation) and the right center gear 76 rotates in the forward direction (reverse rotation) at the same rotation speed in the opposite directions.

  As can be seen from the above configuration, the shift output from each of the motor shafts 60 and 61 is transmitted to the drive sprockets 22 (drive sprockets) of the left and right traveling crawlers 2 via the auxiliary transmission gear mechanism 51 and the differential mechanism 52, respectively. Is done. As a result, the vehicle speed (traveling speed) and traveling direction of the traveling machine body 1 are determined.

  That is, when the first hydraulic motor 56 is driven while the second hydraulic motor 58 is stopped and the left and right sun gears 71 (center gear 76) are stationary and fixed, the rotational output from the linear motor shaft 60 is applied to the left and right ring gears 73. 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.

  Conversely, when the second hydraulic motor 58 is driven in a state where the first hydraulic motor 56 is stopped and the left and right ring gears 73 are stationary, the left sun gear 71 is rotated by the rotational power from the turning motor shaft 61. The right sun gear 71 rotates reversely or forwardly. As a result, 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 turns on the spot (spin turn).

  When the left and right sun gears 71 are driven by the second hydraulic motor 58 while the left and right ring gears 73 are driven by the first hydraulic motor 56, a difference occurs in the speed of the left and right traveling crawlers 2, and the traveling machine body 1 moves forward or backward. However, it turns left or right (U-turn) with a turning radius larger than the radius turning radius. The turning radius at this time is determined according to the speed difference between the left and right traveling crawlers 2.

  Next, the hydraulic circuit structure of the combine will be described with reference to FIG. As shown in FIG. 8, the hydraulic circuit 250 includes the first hydraulic pump 55, the first hydraulic motor 56, the second hydraulic pump 57, the second hydraulic motor 58, and the charge pump 251 described above. 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.

  Further, as shown in FIG. 8, the above-mentioned lifting hydraulic cylinder 4, the auger lifting hydraulic cylinder 254 that lifts and lowers the side of the discharge auger 8, and the left and right end portions of the traveling body 1 are lifted and lowered. Left and right vehicle height adjustment hydraulic cylinders 38 that tilt the left and right, the above-described work pump 91, and left and right front and rear tilt hydraulic cylinders 177 that raise and lower the front and rear parts of the traveling machine body 1 to tilt the traveling machine body 1 back and forth. Prepare. A diversion valve 255 and a relief valve 256 are connected to the discharge side of the work pump 91. A first high pressure oil passage 257 and a second high pressure oil passage 258 are connected to the diversion valve 255. A low-pressure tank oil passage 259 is connected to the relief valve 256.

  The first high-pressure oil passage 257 includes a cutting lift solenoid valve 260 that operates the lifting hydraulic cylinder 4, a left tilt solenoid valve 261 that operates the left vehicle height adjustment hydraulic cylinder 38, and a right vehicle height adjustment hydraulic cylinder 38. An actuating right tilting electromagnetic valve 262 and a grain discharging electromagnetic valve 263 that operates the auger lifting hydraulic cylinder 254 are connected. Further, the cutting lifting solenoid valve 260 is set as one group, and the left tilting solenoid valve 261, the right tilting solenoid valve 262, and the grain discharge solenoid valve 263 are set as two groups and connected to the priority operation solenoid valve 264 for each group. In the state where the operation of the vehicle height adjusting hydraulic cylinder 38 or the auger raising / lowering hydraulic cylinder 254 is prohibited, the raising / lowering hydraulic cylinder 4 is configured to be raised through the priority operation electromagnetic valve 264 for cutting up. On the other hand, the vehicle height adjusting hydraulic cylinder 38 or the auger lifting hydraulic cylinder 254 is operated via the priority operation solenoid valve 264 in a state where the operation of the lifting hydraulic cylinder 4 is prohibited.

  Further, a cutting lowering electromagnetic valve 265 for operating the lifting hydraulic cylinder 4 is connected to the tank oil passage 259 on the side where the cutting device 3 is lowered. Separately from the lifting and lowering movement of the cutting device 3 for switching the cutting lifting electromagnetic valve 260, the priority operating electromagnetic valve 264 is switched to raise the cutting device 3, while the cutting lowering electromagnetic valve 265 is switched to lower the cutting device 3. doing.

  The second high pressure oil passage 258 is connected to a front / rear tilting electromagnetic valve 266 that operates the left / right front / rear tilting hydraulic cylinders 177. Regardless of the operation state of the lifting hydraulic cylinder 4 or the vehicle height adjusting hydraulic cylinder 38 or the auger lifting hydraulic cylinder 254, the flow dividing action of the flow dividing valve 255 always causes the high-pressure oil necessary for the operation of the left and right hydraulic cylinders 177 to move forward and backward. It is secured. That is, when the left and right forward / backward tilt hydraulic cylinder 177 is actuated, the traveling machine body 1 is tilted forward and the ground height of the front part of the traveling machine body 1 is increased. It is constructed so that it can be lifted quickly and the cutting device 3 can be prevented from colliding with an obstacle such as a rice field.

  Next, a structure for adjusting the inclination angle in the left-right direction of the traveling machine body 1 will be described with reference to FIGS. 9 to 16. 9 to 16, a pair of left and right rolling fulcrum frames 26 provided on the lower surface side of the traveling machine body 1, a pair of left and right front bearing bodies 27, and a pair of left and right rear bearing bodies 28 are provided. A pair of left and right front bearing bodies 27 are arranged on the front end side of the rolling fulcrum frame 26 fixed to the lower surface side of the traveling machine body 1. A pair of left and right rear bearing bodies 28 are arranged on the rear end side of the pair of left and right rolling fulcrum frames 26. A pair of left and right front rolling fulcrum shafts 29 are passed through the left and right front bearing bodies 27, and a pair of left and right rear rolling fulcrum shafts 30 are passed through the left and right rear bearing bodies 28, respectively. A drive sprocket 22 (mission case 88) is arranged on the lower surface side of the traveling machine body 1 via the traveling chassis 1a. The rear side of the mission case 88 is fastened to the front portion of the traveling machine body 1.

  The base end sides of the pair of left and right upper front rolling arms 31 extended in the vertical direction are integrally fixed to one end side of the pair of left and right front rolling fulcrum shafts 29 extended in the left and right direction. To the other end side of the pair of left and right front rolling fulcrum shafts 29, the base end sides of the pair of left and right lower front rolling arms 33 extending in the front-rear direction are fixed integrally. That is, the pair of left and right upper front rolling arms 31 and the pair of left and right lower front rolling arms 33 rotate integrally around the pair of left and right front rolling fulcrum shafts 29, respectively. In addition, the front portion of the track frame 21 is connected to the distal end side of the lower front rolling arm 33 via a connecting shaft body 40.

  Moreover, the base end side of a pair of left and right upper rear rolling arms 32 is rotatably fitted to one end side of the rear rolling fulcrum shaft 30 extended in the left-right direction. As shown in FIGS. 7 and 15, a pair of left and right front and rear connecting rolling frames 36 with turnbuckles that can be expanded and contracted are provided. The long rod-like front / rear connecting rolling frame 36 extends in the front / rear direction parallel to the traveling machine body 1 at a position lower than the upper surface of the traveling machine body 1. The front end side of the front / rear connecting rolling frame 36 is connected to the front end side of the pair of left and right upper front rolling arms 31 via the shaft body 35. The rear end side of the front / rear connecting rolling frame 36 is connected to the upper end side of the upper rear rolling arm 32 via a shaft body 37.

  As shown in FIGS. 9 to 16, a pair of left and right vehicle height adjusting hydraulic cylinders 38 for changing the inclination angle in the left and right direction of the traveling machine body 1 are provided. The traveling machine body 1 is provided with a pair of left and right cylinder support brackets 39. A pair of left and right vehicle height adjusting hydraulic cylinders 38 are connected to a pair of left and right cylinder support brackets 39 via a base shaft body 48, respectively. Piston rods 41 of a pair of left and right vehicle height adjusting hydraulic cylinders 38 are connected to the upper ends of the pair of left and right upper rear rolling arms 32 via front end side shaft bodies 42, respectively.

  To the other end side of the pair of left and right rear rolling fulcrum shafts 30, the base end sides of the pair of left and right lower rear rolling arms 34 are integrally fixed. That is, the pair of left and right rear rolling fulcrum shafts 30 and the pair of left and right lower rear rolling fulcrum arms 34 are configured to rotate integrally around the axis of the pair of left and right rear rolling fulcrum shafts 30, respectively. Further, one end side of the driven link body 175 is connected to the distal end side of the lower rear rolling arm 34 via the connecting shaft body 174. The rear portion of the track frame 21 is connected to the other end side of the driven link body 175 via a connecting shaft body 179.

  As shown in FIGS. 9 to 16, a front and rear tilt hydraulic cylinder 177 for changing the front and rear tilt angle of the traveling machine body 1 is provided. The base end sides of the pair of left and right pitching arms 176 are fixed to one end side of the pair of left and right rear rolling fulcrum shafts 30. The pair of left and right pitching arms 176 and the pair of left and right lower rear rolling arms 34 are configured to rotate integrally around the axis of the pair of left and right rear rolling fulcrum shafts 30, respectively. Further, a pair of left and right front and rear tilt hydraulic cylinders 177 are connected to the pair of left and right upper rear rolling arms 32 via a connecting shaft body 180, respectively. The front end side of the pitching arm 176 is connected to the piston rod 178 of the hydraulic cylinder 177 for forward / backward tilting via a connecting shaft body 181.

  As shown in FIGS. 9 and 10, the pair of left and right vehicle height adjusting hydraulic cylinders 38 and the front / rear inclination hydraulic cylinders 177 are arranged in a line in the front-rear direction in a side view or a plan view. The pair of left and right rolling link mechanisms R1 that change the tilt angle in the left-right direction of the traveling machine body 1 by the operation of the pair of left and right vehicle height adjusting hydraulic cylinders 38 includes an upper front rolling arm (left and right tilt arm) 31, an upper rear rolling arm ( It includes a left / right tilt arm 32, a lower front rolling arm (front arm) 33, a lower rear rolling arm (rear arm) 34, a front / rear connecting rolling frame 36, and a driven link body (pitching link) 175. When the vehicle height adjusting hydraulic cylinder 38 is operated, the upper front rolling arm 31 and the lower front rolling arm 33 are integrally rotated around the front rolling fulcrum shaft 29, and at the same time, the upper rear rolling arm 32 and the lower The side rear rolling arm 34, the pitching arm 176, and the forward / backward tilt hydraulic cylinder 177 rotate integrally around the rear rolling fulcrum shaft 30.

  That is, as shown in FIGS. 9 and 11, when the vehicle height adjusting hydraulic cylinder 38 is operated, the traveling machine body 1 and the track frame 21 are maintained while maintaining the inclination angle of the traveling machine body 1 with respect to the track frame 21. Change the relative spacing. When the amount of subsidence of the left and right traveling crawlers 2 changes and the traveling machine body 1 tilts to the left and right, or when the operator wants to tilt the traveling machine body 1 to the left and right, the vehicle travels by automatic control or manual control of the vehicle height adjusting hydraulic cylinder 38. The horizontal inclination angle of the aircraft 1 can be changed, and the ground inclination angle of the traveling aircraft 1 in the horizontal direction can be maintained at a set angle (substantially horizontal posture).

  A pair of left and right pitching link mechanisms P1 that change the inclination angle in the front-rear direction of the traveling machine body 1 by the operation of the pair of left and right hydraulic cylinders 177 for the front and rear are composed of a lower rear rolling arm (rear arm) 34, a driven link body (pitching). Link) 175 and a pitching arm (front and rear tilt arm) 176. When the forward / backward tilting hydraulic cylinder 177 is operated, the lower rear rolling arm 34 and the pitching arm 176 rotate integrally around the rear rolling fulcrum shaft 30, and the front rolling fulcrum shaft is driven via the driven link body 175. The track frame 21 is rotated around 29.

  That is, as shown in FIGS. 12 to 15, when the forward / backward tilt hydraulic cylinder 177 is actuated, the longitudinal direction of the traveling machine body 1 with respect to the track frame 21 is maintained while maintaining the ground inclination angle in the left / right direction of the traveling machine body 1. Change the tilt angle. When the traveling road surface on which the left and right traveling crawlers 2 are moved is an upward or downward sloping slope, or when the traveling machine body 1 tilts back and forth due to a change in the amount of settlement at the front (or rear) of the left and right traveling crawlers 2 Alternatively, when the operator wants to tilt the traveling machine body 1 back and forth, the front and rear tilt angle of the traveling machine body 1 is changed by automatic control or manual control of the front and rear tilt hydraulic cylinder 177, and the ground tilt angle of the traveling machine body 1 in the front and rear direction is reduced. Can be maintained at a set angle (substantially horizontal posture).

  The intermediate roller 25 that holds the non-grounded side of the traveling crawler 2 is rotatably supported by a roller shaft 64 that protrudes laterally from the traveling machine body 1. That is, on the non-grounded side of the traveling crawler 2 between the drive sprocket 22 and the intermediate roller 25, the inclination angle of the traveling body 1 in the left-right direction or the front-rear direction is changed by the vehicle height adjusting hydraulic cylinder 38 or the front-rear tilting hydraulic cylinder 177. However, the distance from the lower surface of the traveling machine body 1 is always maintained substantially constant.

  With the above configuration, as shown in FIG. 11, either one or both of the pair of left and right vehicle height adjusting hydraulic cylinders 38 are operated, and either one or both piston rods 41 of the pair of left and right vehicle height adjusting hydraulic cylinders 38 are operated. , One or both of the pair of left and right track frames 21 move downward, push down either one or both of the pair of left and right traveling crawlers 2, and the left or right side or both of the traveling body 1 It is configured to increase the vehicle height.

  Further, as shown in FIG. 9, one or both of the pair of left and right vehicle height adjusting hydraulic cylinders 38 are operated to retract the piston rod 41 of either one or both of the pair of left and right vehicle height adjusting hydraulic cylinders 38. In this case, either one or both of the pair of left and right track frames 21 move upward, pushes up one or both of the pair of left and right traveling crawlers 2 and raises the vehicle height on the left or right side or both of the traveling body 1. Is configured to be low. That is, by operating the pair of left and right vehicle height adjusting hydraulic cylinders 38 to change the heights of the contact surfaces of the left and right traveling crawlers 2 with respect to the traveling machine body 1, the inclination angle of the traveling machine body 1 in the horizontal direction can be increased. The traveling machine body 1 is adjusted so as to be supported substantially horizontally (left and right inclination angle 0 degree).

  As shown in FIG. 12 (FIG. 13), when the piston rod 41 is advanced (or the piston rod 41 is retracted) when the vehicle height is high, the front / rear tilt hydraulic cylinder 177 is operated to make a pair of left and right front / back tilts. When the piston rods 178 of the hydraulic cylinders 177 are retracted, the pair of left and right pitching arms 176 are actuated, respectively, and the pair of left and right driven link bodies 175 are respectively pushed downward, and the pair of left and right track frames 21 Both rear end sides move down at the same time.

  As a result, the parallel posture of the lower rear rolling arm 34 with respect to the lower front rolling arm 33 is changed, the grounding side of the rear part of the pair of left and right traveling crawlers 2 is pushed down, and the vehicle on the rear end side of the traveling machine body 1 is pushed. The height is increased, and the traveling machine body 1 is configured to tilt forward and downward. That is, the rear end side of the traveling machine body 1 is moved up around the front rolling fulcrum shaft 29 so that the rear end side of the traveling machine body 1 is tilted to a forward inclined posture (front downward inclined posture) that is higher than the front end side. It is composed. As a result, when moving on a traveling road surface that is inclined forwardly upward, the longitudinal inclination of the traveling machine body 1 can be maintained substantially horizontal.

  14 and 15, by retracting the piston rods 178 of the pair of left and right hydraulic cylinders 177, the rear end sides of the pair of left and right track frames 21 are reversed. Needless to say, the vehicle body moves upward at the same time, the vehicle height on the rear end side of the traveling machine body 1 becomes lower, and the traveling machine body 1 tilts backward and downward.

  FIG. 17 shows the height of the traveling machine body 1 with respect to the height of the combiner body (height of the traveling machine body 1) on the vertical axis and the inclination angle of the combined machine body in the front-rear direction (front and rear inclination angle of the traveling machine body 1). FIG. 6 is a diagram showing a relationship (attitude control operation range) between the height (tilt control in the left-right direction) and the front-back tilt angle (tilt control in the front-rear direction) of the traveling machine body 1; The vehicle height adjusting hydraulic cylinder 38 and the front / rear tilt hydraulic cylinder 177 are actuated based on the detection result of the front / rear tilt sensor 381, etc. within the range indicated by the thick solid line in FIG. 17 (deformed hexagonal frame). The tilt control operation in the left-right direction of the adjusting hydraulic cylinder 38 is maintained in a predetermined range, and the tilt control in the front-rear direction of the front-rear tilt hydraulic cylinder 177 is executed.

  For example, in the left / right tilt control operation of the vehicle height adjusting hydraulic cylinder 38, the vehicle height C is about 60% (about one third) of the maximum vehicle height D and about 10% of the maximum vehicle height D. Between the percentage (about 1/10) of the vehicle height A, the forward / backward inclination of the hydraulic cylinder 177 for the forward / backward tilt is increased from 0 ° to the maximum forward tilt angle F (for example, about 5 °). Tilt control is performed, and the traveling machine body 1 is configured to be supported in a forward leaning posture (a forward descending leaning posture). When the vehicle height D is the maximum, the forward tilt control (forward tilt) of the forward / backward tilt hydraulic cylinder 177 is within a range of about 60 percent (about one third) of the forward tilt angle F1 with respect to the maximum forward tilt angle F. Operation) is executed. Further, when the vehicle height A is equal to or less than the vehicle height A or equal to or greater than the vehicle height C, the forward tilt control of the forward / backward tilt hydraulic cylinder 177 is executed within the range of the maximum forward tilt angle F or less. A forward tilt operation restriction area E1 (shaded display range) of vehicle height A or less and a forward tilt operation restriction area E3 (shaded display range) of vehicle height C or more are formed. When the vehicle height C is less than the vehicle height A or greater than the vehicle height A, the forward and backward tilting hydraulic cylinder 177 is moved in the forward direction within a range of the front and rear tilt angle of the traveling machine body 1 from 0 degrees to the maximum forward tilt angle F (for example, about 5 degrees). The tilt control is executed.

  That is, at the maximum vehicle height D, the forward tilting operation of the traveling machine body 1 is restricted to be equal to or less than the forward tilt angle F1 of about 60 percent (about one third) with respect to the maximum forward tilt angle F. In a state where the vehicle height C is higher than the vehicle height C, the forward tilting operation of the traveling machine body 1 is restricted below the maximum forward tilt angle F, and the front end side of the reaping device 3 can be prevented from being supported low. As a result, even when the reaping device 3 is lifted to the non-working position (high position) by the lifting hydraulic cylinder 4, the traveling machine body 1 can be appropriately tilted forward. For example, even when the traveling machine body 1 moves in a posture that is greatly inclined forward and downward in operations such as entering and leaving a farm field and loading and unloading to a truck bed, it is possible to prevent the front end side of the reaping device 3 from colliding with a field surface or a road surface. .

  On the other hand, as shown in FIG. 17, in the tilt control operation in the left-right direction of the vehicle height adjusting hydraulic cylinder 38, the vehicle height is the maximum vehicle height D and about 25 percent (about ¼) of the maximum vehicle height D. Control of the forward / backward tilt hydraulic cylinder 177 in the backward direction (backward tilting operation) from the vehicle body height B to the maximum tilt angle R (for example, about 3 °). Is performed, and the traveling machine body 1 is configured to be supported in a rearward tilt posture (backward tilt posture). Further, when the vehicle height is equal to or less than the vehicle height B, the backward tilt control of the forward / backward tilt hydraulic cylinder 177 is executed within the range of the maximum rearward tilt angle R or less. A rearward tilt operation restriction area E2 (shaded display range) below the vehicle height B is formed. That is, while maintaining the vehicle height B (approximately 25% of the maximum vehicle height D) or more, the traveling machine body 1 can be tilted backward to the maximum rearward tilt angle R, so that the cutting device 3 is moved to the non-working position by the lifting hydraulic cylinder 4 ( Even if it is raised to the high position), the traveling machine body 1 can be smoothly tilted backward to further raise the reaping device 3, and the reaping device 3 can be quickly avoided with respect to obstacles.

Further, when the vehicle height is higher than the vehicle height C, or when the vehicle height is lower than the vehicle height A or the vehicle height B, the vehicle height adjusting hydraulic cylinder 38 is operated before the front / rear tilt hydraulic cylinder 177 is operated. The vehicle height adjustment (tilt in the left-right direction) control operation of the vehicle height adjusting hydraulic cylinder 38 is prioritized to maintain the vehicle height of the traveling machine body 1 at a predetermined vehicle height or higher, and then the front-rear direction hydraulic cylinder 177 is moved in the front-rear direction. The tilt control can be executed. As a result, it is possible to prevent the front portion of the reaping device 3 from entering the soil such as a farm field or a straw. In addition, when the vehicle height (vehicle height A or vehicle height B or less) is about 25 percent (about one-fourth) or less of the maximum vehicle height D, compared to the vehicle height at which the forward tilting operation of the traveling machine body 1 is restricted. Therefore, the vehicle height at which the backward tilting operation of the traveling machine body 1 is restricted increases (vehicle height A <vehicle height B). The maximum backward inclination angle R (for example, about 3 degrees) and the forward inclination angle F1 of about 60 percent (about one third) with respect to the maximum forward inclination angle F are formed to be substantially equal. That is, the maximum rearward tilt angle R is formed to have a tilt angle magnitude of about 60 percent with respect to the maximum forward tilt angle F.

  As shown in FIG. 17, by increasing the maximum forward tilt angle F with respect to the maximum rearward tilt angle R, the traveling crawler 2 sinks greatly in the super wet field, and the height of the traveling machine body 1 is increased to perform the cutting operation. The traveling machine body 1 is tilted forward without lowering the vehicle height of the traveling machine body 1 and increasing the running resistance, or without lowering the cutting device 3 and causing the cutting blade device 222 or the like to enter the soil. By doing so, the stock of uncut cereal can be cut by the cutting blade device 222 at a predetermined height.

  As shown in FIGS. 1 and 9 to 16, a traveling machine body 1 having a traveling crawler 2 as a left and right traveling unit, and a vehicle height adjusting hydraulic cylinder 38 as a rolling actuator that corrects the inclined posture of the traveling machine body 1 in the left-right direction. And a vehicle height adjustment hydraulic cylinder 38 and a front / rear tilt hydraulic cylinder 177 in a plan view in a traveling vehicle provided with a front / rear tilt hydraulic cylinder 177 as a pitching actuator for correcting the front / rear tilt posture of the traveling machine body. Therefore, the installation length (connection support length) of the front / rear tilt hydraulic cylinder 177 can be shortened compared to the prior art, and the twisting force other than the expansion / contraction direction acting on the front / rear tilt hydraulic cylinder 177 can be reduced. Durability can be improved. Moreover, the lower surface side space of the traveling machine body 1 between the left and right traveling crawlers 2 can be widely formed, mud can be reduced from being accumulated on the lower surface side of the traveling machine body 1, and wet field workability can be improved. Further, it is possible to prevent the upper surface side structure of the traveling machine body 1 or the support position of the front and rear tilt hydraulic cylinder 177 from being restricted to each other, and the traveling machine body 1 and the like can be configured easily.

  As shown in FIGS. 9 to 16, the vehicle height adjusting hydraulic cylinder 38 and the front / rear tilt hydraulic cylinder 177 are arranged in a line in a side view. (Supporting length) can be shortened as compared to the conventional case, and the twisting force other than the expansion / contraction direction acting on the forward / backward tilting hydraulic cylinder 177 can be reduced, and the durability can be improved. Moreover, the lower surface side space of the traveling machine body 1 between the left and right traveling crawlers 2 can be widely formed, mud can be reduced from being accumulated on the lower surface side of the traveling machine body 1, and wet field workability can be improved. Further, it is possible to prevent the upper surface side structure of the traveling machine body 1 or the support position of the front and rear tilt hydraulic cylinder 177 from being restricted to each other, and the traveling machine body 1 and the like can be configured easily.

  As shown in FIGS. 9 to 16, the upper front rolling arm 31 and the upper rear rolling arm 32 as left and right tilt arms connected to the vehicle height adjusting hydraulic cylinder 38, and the front and rear tilt arms connected to the front and rear tilt hydraulic cylinder 177. Since the pitching arms 176 are arranged on the same fulcrum shafts 29 and 30, the traveling machine body 1 having the same specifications can be used regardless of the presence or absence of a forward / backward tilt mechanism such as the forward / backward tilt hydraulic cylinder 177. The traveling machine body 1 and the like can be configured at low cost.

  As shown in FIGS. 9 to 16, a structure is provided in which a lower front rolling arm 33 as a parallel link-like front arm operated by a vehicle height adjusting hydraulic cylinder 38 and a lower rear rolling arm 34 as a rear arm are provided. Since the pitching arm 176 is connected to either the lower front rolling arm 33 or the lower rear rolling arm 34, the vehicle body 1 is maintained while maintaining the vehicle height of the vehicle body 1 in the left-right inclined posture. Can be tilted back and forth. The control performance of the vehicle height adjusting hydraulic cylinder 38 that corrects the tilting posture of the traveling machine body 1 in the left-right direction can be maintained, and the control performance of the front-rear tilting hydraulic cylinder 177 that corrects the tilting attitude of the traveling machine body 1 in the front-rear direction can be improved. .

  As shown in FIGS. 1 and 9 to 16, a traveling machine body 1 having a traveling crawler 2 as a left and right traveling unit, and a vehicle height adjusting hydraulic cylinder 38 as a rolling actuator that corrects the inclined posture of the traveling machine body 1 in the left-right direction. And a hydraulic cylinder 177 for tilting forward and backward as a pitching actuator for correcting the tilting posture of the traveling machine body 1 in the front-rear direction so that the traveling machine body 1 can be moved up and down on the left and right track frames 21 via the left and right link mechanisms R1 and P1. In the traveling vehicle which is mounted and configured to be able to correct the tilting posture of the traveling aircraft body 1 in the left-right direction and the tilting posture of the traveling aircraft body 1 in the front-rear direction, the link mechanisms R1 and P1 are the lower side as parallel link-shaped front arms. A structure having a front rolling arm 33 and a lower rear rolling arm 34 as a rear arm, Connecting the one of the lower front rolling arm 33 or the lower rear roll arm 34 through the driven link member 175 as pitching link.

  Accordingly, while the traveling body 1 can be tilted left and right by the operation of the parallel link-shaped lower front rolling arm 33 and lower rear rolling arm 34 (control of the vehicle height adjusting hydraulic cylinder 38), the lower front portion The front or rear side of the track frame 21 is moved up and down via either the rolling arm 33 or the lower rear rolling arm 34 and the driven link body 175 (control of the front / rear tilt hydraulic cylinder 177) to move the traveling machine body 1 back and forth. Can tilt. The traveling machine body 1 can be tilted back and forth in a state where the vehicle height of the traveling machine body 1 in the left-right tilted posture is maintained (control of the vehicle height adjusting hydraulic cylinder 38 is stopped). The connecting structure of the traveling machine body 1 and the track frame 21 can be easily configured, or the control of the hydraulic cylinder 177 for front and rear tilt can be easily executed. A pitching structure for changing the tilting posture of the traveling machine body 1 in the front-rear direction can be assembled at low cost, or a pitching control function for changing the tilting posture of the traveling machine body 1 in the front-rear direction can be improved.

  9 to 16, both the lower front rolling arm 33 and the lower rear rolling arm 34 are connected to the vehicle height adjusting hydraulic cylinder 38, and the lower rear rolling arm 34 connected to the driven link body 175 or A forward / backward tilting hydraulic cylinder 177 is connected to one of the lower front rolling arms 33. Therefore, the front / rear tilt hydraulic cylinder 177 can be assembled compactly close to the vehicle height adjusting hydraulic cylinder 38. Further, it is possible to improve the pitching function for changing the tilting posture in the front-rear direction of the traveling machine body 1 while preventing the rolling function for changing the tilting posture in the left-right direction of the traveling machine body 1 from being complicated.

  As shown in FIGS. 9 to 16, a transmission case 88 is arranged in the front part of the traveling machine body 1, and a hydraulic cylinder 177 for front / rear tilting is connected to the lower rear rolling arm 34, and the follower link of the track frame 21. The lower rear rolling arm 34 is connected via a body 175. Therefore, by installing the front part of the track frame 21 close to the support part of the mission case 88 and changing the inclined posture of the traveling machine body 1 in the front-rear direction, the lower surface side of the traveling machine body 1 and the traveling crawler 2 It is possible to prevent the upper surface side from interfering. The front / rear tilt hydraulic cylinder 177 can be assembled in a compact manner in a line at substantially the same height from the middle to the rear of the track frame 21 in the vicinity of the vehicle height adjusting hydraulic cylinder 38. For example, it is possible to easily ensure the inclination change range in the front-rear direction of the traveling machine body 1 or simplify the connection structure between the traveling machine body 1 and the track frame 21.

  As shown in FIGS. 9 to 16, an upper rear rolling arm 32 connected to the vehicle height adjusting hydraulic cylinder 38 and a pitching arm 176 connected to the front / rear tilting hydraulic cylinder 177 are arranged on the same fulcrum shaft, while A front / rear tilt hydraulic cylinder 177 is provided on the upper rear rolling arm 32 connected to the adjustment hydraulic cylinder 38, and the vehicle height adjustment hydraulic cylinder 38 and the front / rear tilt hydraulic cylinder 177 are arranged in a line in the front-rear direction. Therefore, the traveling machine body 1 having the same specification can be easily shared between the specification in which the front / rear inclination hydraulic cylinder 177 is provided and the specification in which the front / rear inclination hydraulic cylinder 177 is not provided. In addition, a space between the left and right traveling crawlers 2 is formed wide on the lower surface side of the traveling machine body 1 so that the traveling crawler 2 is easily sunk, and workability such as wet fields is easily swollen or mud such as the rice field is greatly raised. It can improve the running performance of easy field headlands.

  As shown in FIGS. 9 to 15 and FIGS. 22 to 24, the front lowest stopper 185 is fixed to the traveling chassis 1a. One end side of the front lowering stopper 185 is extended to the upper surface side of the lower front rolling arm 33. When the front vehicle height of the traveling machine body 1 is the lowest (the state shown in FIG. 9 or FIG. 22), that is, when the front side of the traveling machine body 1 and the track frame 21 are closest to each other, the upper side of the lower front rolling arm 33 is The lower surface of the lowest stop stopper 185 comes into contact with the front side of the traveling machine body 1 and is supported at the lowest position. By contacting the lower front rolling arm 33 and the front lowering stopper 185, the front upper surface of the traveling crawler 2 is prevented from interfering with the front lower surface of the traveling machine body 1.

  In addition, a rear lowermost stopper 186 is fixed to the lower surface of the rear bearing body 28. A receiving body 187 is fixed to the track frame 21. When the rear vehicle height of the traveling machine body 1 is the lowest (the state shown in FIG. 9 or FIG. 22), that is, when the rear side of the traveling machine body 1 and the track frame 21 are closest to each other, The lower surface of the lowest-stop stopper 186 comes into contact, and the rear side of the traveling machine body 1 is supported at the lowest position. The contact between the receiving body 187 and the rear-most lowering stopper 186 prevents the rear upper surface of the traveling crawler 2 from interfering with the rear lower surface of the traveling machine body 1.

  Next, with reference to FIG. 18, the left / right direction tilt control, the front / rear direction tilt control, and the lifting / lowering control of the reaping device 3 will be described. FIG. 18 is a functional block diagram of the left and right direction tilt control means, the front and rear direction tilt control means of the combine (running vehicle body 1), and the lifting control means of the reaping device 3, and a work controller 371 formed by a microcomputer or the like. Is provided. The work controller 371 includes a ROM that stores a control program and a RAM that stores various data.

  As shown in FIG. 18, the work controller 371 includes various sensors and switches of the input system, that is, a crop sensor 372 that detects the harvested culm cut by the harvesting device 3, and a task that detects the operation of the harvesting device 3. A switch 373, a pendulum left / right tilt sensor 374 that detects the tilt angle of the traveling machine body 1 in the left / right direction, and a potentiometer-type left vehicle that detects the relative distance (vehicle height) between the traveling machine body 1 and the left track frame 21. Initially set the height sensor 375, a potentiometer-type right vehicle height sensor 376 that detects the relative distance (vehicle height) between the traveling machine body 1 and the right truck frame 21, and the reference value of the lateral inclination angle of the traveling machine body 1 A manual dial switching potentiometer type right / left tilt setting device 377 is connected.

  Also, the work controller 371 is connected with various electromagnetic hydraulic valves of the output system, that is, a left tilting solenoid valve 261 and a right tilting solenoid valve 262. With this configuration, the left tilt solenoid valve 261 or the right tilt solenoid valve 262 is switched based on the detected value of the left / right tilt sensor 374, the detected value of the left vehicle height sensor 375, and the detected value of the right vehicle height sensor 376, and the left vehicle The high adjustment hydraulic cylinder 38 or the right vehicle height adjustment hydraulic cylinder 38 is operated to correct the inclination of the traveling machine body 1 in the left-right direction so that the traveling machine body 1 is automatically controlled so as to be substantially horizontal.

  Further, as shown in FIG. 18, the work controller 371 includes a pendulum type front / rear inclination sensor 381 that detects an inclination angle of the traveling body 1 in the front / rear direction, a rear portion of the traveling body 1, and a rear end side of the track frame 21. A potentiometer-type main unit inclination sensor 382 that detects a relative interval (a front-rear direction inclination angle of the track frame 21), and a manual dial-switching potentiometer that initially sets a reference value of the front-rear direction inclination angle of the traveling body 1 A anteroposterior tilt setter 383 is connected.

  Further, the work controller 371 is connected with a forward / backward tilting electromagnetic valve 266. With this configuration, the front / rear tilting hydraulic valve 266 is switched based on the detected value of the front / rear tilt sensor 381, the detected value of the main unit tilt sensor 382, and the set value of the front / rear tilt setter 383, and the front / rear tilt hydraulic cylinder 177 is switched. Is operated, the inclination of the traveling body 1 in the front-rear direction is corrected, and the traveling body 1 is automatically controlled so as to be substantially horizontal.

  On the other hand, as shown in FIG. 18, the work controller 371 includes a vehicle speed sensor 385 that detects the rotational speed (vehicle speed) of the traveling crawler 2, and a potentiometer-type cutting height sensor 386 that detects the ground height of the cutting device 3. A manual dial switching potentiometer type cutting height setting device 387 for initial setting of a ground height reference value of the cutting device 3 is connected.

  The work controller 371 is connected with a cutting lift electromagnetic valve 260. With this configuration, the cutting lift solenoid valve 260 is switched based on the detection value of the vehicle speed sensor 385, the detection value of the cutting height sensor 386, and the setting value of the cutting height setting device 387, and the cutting lift hydraulic cylinder 4 Is operated, the ground height of the reaping device 3 is corrected, and the grain reaper cutting height of the reaping device 3 is automatically controlled so as to be substantially constant.

  Next, referring to the posture control explanatory diagram shown in FIG. 17, the functional block diagram shown in FIG. 18, and the flowcharts shown in FIGS. 19 to 21, the culm cutting height control mode of the reaping device 3 and the combine (running vehicle body) 1) The aspect of tilt control in the left-right direction and the front-rear direction will be described. As shown in the flowchart of FIG. 19, when the engine 20 is started, the crop sensor 372 value, the left / right tilt sensor 374 value, the left vehicle height sensor 375 value, the right vehicle height sensor 376 value, the left / right tilt setter 377 value, the front / rear tilt Sensor 381 value, machine inclination sensor 382 value, front / rear inclination setting device 383 value, vehicle speed sensor 385 value, cutting height sensor 386 value, and cutting height setting device 387 value are read. During the cutting operation in which the work switch 373 is on, the cutting height control shown in the flowchart of FIG. 20 is executed. Further, the tilt control shown in the flowchart of FIG. 21 is executed regardless of whether the work switch 373 is on or off.

  As shown in the flowchart of FIG. 20, if the crop sensor 372 is turned on during the cutting operation with the work switch 373 turned on, the vehicle speed sensor 385 value, the cutting height sensor 3386 value, and the cutting height setting device 87 When it is determined that the harvesting height of the harvesting device 3 is low based on the value, the harvesting lifting / lowering solenoid valve 260 is switched, and the harvesting lifting hydraulic cylinder 4 is operated to control the lifting of the harvesting device 3 so that the harvesting is performed. The ground height of the device 3 is corrected. On the other hand, when it is determined that the harvesting height of the harvesting device 3 is high, the harvesting lifting / lowering electromagnetic valve 260 is switched, the harvesting lifting hydraulic cylinder 4 is operated to lower the harvesting device 3, and the harvesting device 3 Correct the height of the ground. The cutting height control of FIG. 20 can automatically maintain the grain cutting height of the cutting device 3 set by the cutting height setting unit 387. When the cutting height setting unit 87 is operated by the operator, the cutting device 3 is supported by the manual operation at the culm cutting height set by the cutting height setting unit 387.

  As shown in the flowchart of FIG. 21, the traveling machine body 1 is tilted to the left based on the left / right tilt sensor 374 value, the left vehicle height sensor 375 value, the right vehicle height sensor 376 value, and the left / right tilt setter 377 value. Is determined, the left tilting solenoid valve 261 or the right tilting solenoid valve 262 is switched, and the left vehicle height adjustment hydraulic cylinder 38 or the right vehicle height adjustment hydraulic cylinder 38 is operated to raise the left side of the traveling machine body 1 or Alternatively, the right side of the traveling machine body 1 is lowered. On the other hand, when it is determined that the traveling machine body 1 is tilted to the right, the left tilting solenoid valve 261 or the right tilting solenoid valve 262 is switched to operate the left vehicle height adjustment hydraulic cylinder 38 or the right vehicle height adjustment hydraulic cylinder 38. Then, the right side of the traveling machine body 1 is raised or the left side of the traveling machine body 1 is lowered. The left-right inclination angle of the traveling machine body 1 is automatically corrected by the left-right inclination control of the combine (traveling machine body 1) in FIG. Based on the value of the left / right tilt setting device 377, the traveling posture of the traveling machine body 1 in the left / right direction can be maintained. When the left / right inclination setting device 377 is operated by the operator, the traveling machine body 1 is supported by the manual operation in the left / right inclination angle posture (horizontal ground posture) set by the left / right inclination setting device 377.

  Further, as shown in the flowchart of FIG. 21, based on the front / rear tilt sensor 381 value, the main unit tilt sensor 382 value, and the front / rear tilt setter 383 value, If it is determined that the vehicle is within the vehicle height range shown in FIG. 17 (vehicle height range in which the front / rear tilt angle can be corrected), the front / rear tilting solenoid valve 266 is switched to operate the left / right front / rear tilt hydraulic cylinders 177. Then, the rear end side of the traveling machine body 1 is lowered. On the other hand, when it is not within the vehicle height range of FIG. 17 (the vehicle height range in which the front / rear inclination angle can be corrected), that is, outside the vehicle height range of FIG. The hydraulic cylinder 38 is operated, and the right or left side of the traveling machine body 1 is moved up and down to change the vehicle height of the traveling machine body 1 within the vehicle height range of FIG. 17 (the vehicle height range in which the front / rear inclination angle can be corrected). Thereafter, the front / rear tilting electromagnetic valve 266 is switched to operate the left / right front / rear tilt hydraulic cylinders 177 to lower the rear end side of the traveling machine body 1. As a result, the rearward tilt angle of the traveling machine body 1 is automatically corrected by the rearward inclination control of the combine (traveling machine body 1) in FIG. Based on the value of the front / rear tilt setting device 383, the rearward tilt posture (ground horizontal posture) of the traveling machine body 1 can be maintained.

  Further, when it is determined that the traveling body 1 is in a rearward tilting posture in which the traveling vehicle body 1 is tilted downward to the rear side, when the vehicle body is within the vehicle height range in FIG. The electromagnetic valve 266 is switched to operate the left and right front / rear tilt hydraulic cylinders 177 to raise the rear end side of the traveling machine body 1. On the other hand, when it is not within the vehicle height range of FIG. 17 (the vehicle height range in which the front / rear inclination angle can be corrected), that is, outside the vehicle height range of FIG. 17, the left vehicle height adjustment hydraulic cylinder 38 or the right vehicle height adjustment. The hydraulic cylinder 38 is operated and the right or left side of the traveling machine body 1 is raised, and the vehicle height of the traveling machine body 1 is changed within the vehicle height range of FIG. 17 (the vehicle height range in which the front / rear inclination angle can be corrected). Thereafter, the front / rear tilting electromagnetic valve 266 is switched to operate the left / right front / rear tilting hydraulic cylinders 177 to raise the rear end side of the traveling machine body 1. That is, the front-rear direction inclination angle of the traveling machine body 1 is automatically corrected by the front-rear direction inclination control of the combine (traveling machine body 1) in FIG. Based on the value of the front / rear tilt setting device 383, the traveling posture of the traveling machine body 1 can be maintained. In addition, when the front / rear inclination setter 383 is operated by the operator, the traveling machine body 1 is supported by the manual operation at the front / rear inclination angle posture set by the front / rear inclination setter 383.

  During the harvesting operation of the cereal, the cutting height control of FIG. 20 is executed in preference to the horizontal tilt control or the front / rear tilt control of the combine (running machine body 1) of FIG. 225 can be prevented from plunging into the mud on the surface. After the cutting height control shown in FIG. 20 is executed, the left and right direction tilt control or the front and back direction tilt control of the combine (running vehicle body 1) shown in FIG. Can prevent the weed body 225 from entering the mud. Even when the ground height of the traveling machine body 1 is increased by executing the left-right inclination control or the front-rear inclination control of the combine (traveling machine body 1) of FIG. 21 (see FIGS. 9 to 16), The ground crawler angle of the traveling crawler 2 supported by the tension roller 23 and the last track roller 24 is maintained at an appropriate size, and the traveling performance of the traveling crawler 2 is maintained.

  21 is performed in preference to the forward / backward inclination control of the combine (traveling machine body 1) in FIG. The tilt control in the front-rear direction of the combine (traveling machine body 1) can be executed while maintaining the ground height of the right weed body 225 at a predetermined level or higher. As a result, the herb body of the reaping device 3 is also controlled by the tilt control in the front-rear direction even in the mowing operation in the wet field where the ground height of the supporting herb body 225 is lowered while the ground height of the traveling machine body 1 is increased. While being able to prevent the 225 or the cutting blade device 222 and the like from entering the mud on the paddy surface, the stock of uncut cereal can be cut at a low position, and the length of the stock after cutting can be formed short.

  As shown in FIGS. 17, 18, and 21, a traveling machine body 1 having a traveling crawler 2 as a traveling unit, a vehicle height adjusting hydraulic cylinder 38 as a rolling actuator that corrects the tilting posture of the traveling machine body 1 in the left-right direction, In a traveling vehicle equipped with a forward / backward tilting hydraulic cylinder 177 as a pitching actuator for correcting the forward / backward tilting posture of the traveling body 1, when the traveling body 1 is supported at the lowest position, the vehicle height adjusting hydraulic cylinder 38. Is configured such that the forward / backward tilt hydraulic cylinder 177 is moved forwardly or backwardly with the traveling body 1 supported at a predetermined height position. Therefore, the connecting structure of the traveling machine body 1 and the traveling crawler 2 (track frame or the like) can be easily configured as compared with the conventional structure. Further, it is possible to easily prevent the traveling crawler 2 (such as a traveling crawler attached to the track frame) and the traveling machine body 1 from interfering with each other. For example, the traveling machine body 1 can be tilted forward without being restricted by the lowest-lowering stoppers 185 and 186 that set the lower limit of the vehicle height adjustment range of the vehicle height adjustment hydraulic cylinder 38. Further, when the forward / backward tilting hydraulic cylinder 177 is tilted backward, it is possible to prevent the traveling crawler 2 and the like from interfering with the traveling machine body 1 and to smoothly operate the traveling machine body 1 in the backward tilted posture.

  As shown in FIGS. 17, 18, and 21, a left / right inclination sensor 374 that detects a left / right inclination of the traveling machine body 1, a left vehicle height sensor 375 that detects a left ground height and a right ground height of the traveling machine body, and A right vehicle height sensor 376 and a front / rear inclination sensor 381 for detecting the inclination of the traveling machine body 1 in the front / rear direction are provided, and the vehicle height adjusting hydraulic cylinder 38 is operated to raise or lower the vehicle height to move the vehicle body 1 in the left / right direction. The structure is configured so that the inclination can be changed, and based on the detection result of the left vehicle height sensor 375 and the right vehicle height sensor 376 and the detection result of the front / rear inclination sensor 381, the front / rear inclination hydraulic cylinder 177 can be operated to be inclined forward / backward. It is composed. Therefore, when the forward / backward tilt hydraulic cylinder 177 is operated to be tilted forward or backward, the traveling crawler 2 or the like can be prevented from interfering with the traveling machine body 1, and the traveling machine body 1 can be smoothly tilted back and forth.

  As shown in FIGS. 17, 18, and 21, the forward / backward tilt hydraulic cylinder 177 is configured to be able to tilt forward when the traveling machine body 1 is supported at the highest position. Therefore, it is possible to easily change the traveling machine body 1 to the predetermined forward tilting posture while maintaining the traveling machine body 1 at the highest position. That is, the traveling machine body 1 can be smoothly operated in the forward tilted posture without lowering the vehicle height.

  As shown in FIGS. 17, 18, and 21, when the traveling machine body 1 is supported at the highest position, the vehicle height adjusting hydraulic cylinder 38 is operated to lower the vehicle height to bring the traveling machine body 1 to a predetermined height position. In the supported state, the forward / backward tilt hydraulic cylinder 177 is configured to be able to tilt backward. Accordingly, when the forward / backward tilt hydraulic cylinder 177 is operated to be tilted backward, the traveling crawler 2 or the like can be prevented from interfering with the traveling machine body 1, and the traveling machine body 1 can be smoothly operated in the backward tilted posture.

1 traveling machine body 2 traveling crawler (traveling section)
38 Vehicle height adjustment hydraulic cylinder (rolling actuator)
177 Hydraulic cylinder for forward / backward tilting (pitching actuator)
374 Left / right tilt sensor 375 Left vehicle height sensor 376 Right vehicle height sensor 381 Front / back tilt sensor

Claims (4)

In a combine provided with a rolling actuator (38) for correcting the tilting posture in the left-right direction of the traveling machine body (1) and a pitching actuator (177) for correcting the tilting attitude in the front-rear direction of the traveling machine body (1),
When the traveling machine body (1) is supported at the lowest position, the rolling actuator (38) is operated to raise the vehicle height, and the traveling machine body (1) is supported at a predetermined height position. A structure for causing the pitching actuator (177) to move forward or backward ,
The maximum forward tilt angle (F) of the traveling machine body (1) by the pitching actuator (177) is set larger than the maximum backward inclination angle (R) of the traveling machine body (1) by the pitching actuator (177). ing,
Combine . A left / right inclination sensor (374) for detecting a left / right inclination of the traveling machine body (1), a left vehicle height sensor (375) for detecting a left ground height and a right ground height of the traveling machine body (1), and a right A vehicle height sensor (376), and a front / rear inclination sensor (381) for detecting the inclination of the traveling body (1) in the front / rear direction, the rolling actuator (38) is operated to raise or lower the vehicle height, The left and right vehicle height sensors (375) and 376 are detected by the left vehicle height sensor (376) and the front and rear inclination sensor (381). The combine according to claim 1, wherein the pitching actuator (177) is configured to be capable of tilting back and forth based on the result. The combine according to claim 1, wherein the pitching actuator (177) is configured to be able to tilt forward when the traveling machine body (1) is supported at the highest position. When the traveling machine body (1) is supported at the highest position, the rolling actuator (38) is lowered to support the traveling machine body (1) at a predetermined height position. The combine according to claim 1, wherein the pitching actuator (177) is configured to be capable of backward tilting operation.

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