JP2011130671A - Combine harvester - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a combine harvester that takes advantage of a counter case, simply installs a threshing cylinder gear shift mechanism, simplifies the drive structure of the threshing cylinder and reduces a production cost. <P>SOLUTION: In the combine harvester equipped with a running machine body loaded with an engine, a reaping device having a cutting blade, a thresher having the threshing cylinder and a grain separation mechanism and the counter case 89 for transmitting power of the engine to the reaping device or the thresher, the counter case 89 has a main case 91 in which a reaping gear shift mechanism 108 for transmitting power of the engine to the reaping device is arranged and a subcase 92 in which the threshing cylinder gear shift mechanism 389 for transmitting power of the engine to the threshing cylinder is arranged. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a combine such as a harvester that harvests cereals planted in a field and collects grains, or a combine such as a feed combine that harvests cereals for feed and collects as feed, and more particularly, a harvester or It is related with the combine provided with the counter case which transmits the motive power of an engine to a threshing apparatus.

  Conventionally, a combine is provided with a traveling machine body on which an engine is mounted, 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. 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 cereals are threshed to collect the grains (see, for example, Patent Document 1). Conventionally, a continuously variable transmission that transmits driving force to the handling cylinder of the threshing device is provided, and the rotation speed of the handling cylinder is changed steplessly (see, for example, Patent Document 1 and Patent Document 2). ). Furthermore, the technique provided with the counter case which transmits the motive power of an engine to a reaping apparatus or a threshing apparatus is also well-known (refer patent document 3).

No. 2-12841 JP-A-6-14639 JP 2004-138166 A

  In the prior art (Patent Document 1), the rotational torque of the handling cylinder can be increased when the threshing load increases. In the prior art (Patent Document 2), the rotational speed of the handling cylinder is increased when the vehicle speed is reduced. However, when adapting the rotation speed of the barrel to the characteristics of the harvested cereal, the rotation speed of the barrel is changed steplessly by the operator's manual operation based on the operator's experience. Since it is necessary to adjust the number of rotations of the cylinder to an appropriate number of rotations, the operator's mistaken operation (judgment error in determining the characteristics of the harvested corn straw) determines the characteristics of the harvested corn straw. The number of rotations may be set improperly, and it is not possible to easily prevent the occurrence of stab grains where grains are mixed into the waste, or the occurrence of breaks where the grains are cut and mixed into the grains. There's a problem. Further, in the structure in which the handle cylinder transmission mechanism is provided on the outer side of the counter case, there is a problem that simplification of the drive structure of the handle cylinder or reduction in manufacturing cost cannot be easily achieved.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a combine that makes it possible to easily install a handling cylinder transmission mechanism by using a counter case, simplify the handling structure of the handling cylinder, and reduce the manufacturing cost.

  In order to achieve the object, a combine of an invention according to claim 1 includes a traveling machine body equipped with an engine, a cutting device having a cutting blade, a threshing device having a handling cylinder and a grain sorting mechanism, and the cutting device or the In the combine provided with a counter case for transmitting the power of the engine to the threshing device, the counter case includes a main case body in which a cutting speed change mechanism for transmitting the power of the engine to the cutting device is provided, and the engine And a sub case body having a handle transmission mechanism for transmitting power to the handle cylinder.

  According to a second aspect of the present invention, in the combine according to the first aspect, the barrel transmission mechanism is configured to be assembled in the sub case body before being combined with the main case body, and the barrel transmission mechanism A barrel shift operation shaft for shifting the gear is projected upward from the upper surface of the sub case body.

  According to a third aspect of the present invention, in the combine according to the first aspect, a barrel shift operation lever is disposed between the reaping device and the driver's seat, and the barrel shift operation shaft on the upper surface of the counter case is viewed from above. The barrel shifting operation lever is connected.

  The invention according to claim 4 is the combine according to claim 1, wherein the threshing drive pulley to which the power of the engine is transmitted via the threshing clutch, the threshing input actuator for switching the threshing clutch, and the grain sorting mechanism. And a sorting drive shaft for transmitting the power of the engine to the counter case. The sorting drive shaft is rotatably supported on the counter case, and the threshing drive pulley is disposed on the sorting drive shaft, The counter case and the threshing input actuator are arranged with a drive pulley interposed therebetween.

  According to the first aspect of the present invention, a traveling machine body equipped with an engine, a reaping device having a cutting blade, a threshing device having a handling cylinder and a grain sorting mechanism, and the motive power of the engine in the reaping device or the threshing device. In the combine provided with a counter case for transmitting the power, the counter case transmits a main case body in which a cutting speed change mechanism for transmitting the power of the engine to the cutting device is installed, and transmits the power of the engine to the handling cylinder. The main case body in which the cutting transmission mechanism is installed is changed when the specifications such as the presence / absence of the handling cylinder transmission mechanism are changed. It can be used without modification, and many components can be used for multiple specifications. Further, the barrel shifting mechanism can be easily connected to a barrel shifting lever or the like operated by the operator of the driver seat. The manufacturing cost of the counter case and the like can be reduced, and the assembly workability can be improved.

  According to a second aspect of the present invention, the barrel transmission mechanism is configured so that it can be assembled in the sub case body before being combined with the main case body, and the barrel for performing a shift operation of the barrel transmission mechanism. Since the speed change operation shaft protrudes upward from the upper surface of the sub case body, a barrel speed change operation shaft can be provided toward the driver seat and the like disposed obliquely forward of the threshing device, A barrel shift operation lever or the like can be installed at a position where the operator of the driver's seat can easily operate. That is, a barrel shift operation lever (or barrel shift switch) or the like can be easily connected to the counter case at a relatively short distance, and a barrel shift operation link mechanism (or barrel shift link) to be coupled to the barrel shift operation lever or the like. Electrical wiring) and the like can be constructed at low cost and assembled compactly.

  According to the invention which concerns on Claim 3, a barrel shift operation lever is arrange | positioned between the said cutting device and a driver's seat, and the said barrel shift operation lever is connected from the upper side to the said barrel shift operation shaft of the said counter case upper surface. Therefore, the barrel shift operation lever can be easily connected to the barrel shift operation shaft at the shortest distance by effectively utilizing the dead space between the cutting device and the driver's seat. For example, the barrel shift operation lever can be arranged on the outside of a cabin or the like on which an operator is boarded, and the maintenance workability of an engine or the like that requires opening / closing (detaching) of the cabin can be improved.

  According to the invention which concerns on Claim 4, the power of the said engine is transmitted to the threshing drive pulley which switches the power of the said engine via a threshing clutch, the threshing input actuator which switches the said threshing clutch, and the said grain selection mechanism A counter drive shaft, wherein the counter drive case is rotatably supported by the counter case, the threshing drive pulley is disposed on the selection drive shaft, and the counter case sandwiches the threshing drive pulley. Since the threshing input actuator is arranged, compared to a structure in which the threshing input actuator is provided in the counter case, the large diameter of the counter case is not restricted by the threshing input actuator. The threshing drive pulley can be easily supported. In addition, since the threshing input actuator can be arranged close to the threshing drive pulley, the threshing input actuator can be easily connected to the threshing clutch of a tension pulley type that tensions the threshing drive belt.

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 sectional drawing of a counter case. It is a left view of an engine and a transmission case. It is a top view of an engine and a mission case. It is a rear view perspective view of an engine and a transmission case. It is a front view perspective view of an engine and a transmission case. It is transmission explanatory drawing of an engine and a mission case. It is decomposition | disassembly explanatory drawing of a counter case. It is assembly | attachment explanatory drawing of a counter case.

  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 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 cereals (grain culms) 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.

Further, the cereal carrying device 224 has a right stock former transport chain 133R that feeds back the stock side of the right two reaped harvested rice straws that have been scraped by the right side two pieces of star foil 130R and the rake belt 131R. And the left stock transport that joins the stock side of the two left-handed harvested cereals that have been scraped by the star foil 130L and the scraping belt 131L to the left hand stock feed chain 133R. The chain 133L, the central two-segment star foil 130C, and the central two-segment harvested cereal rice bran that has been scraped by the scraping belt 131C are transported rearward while the right stock transport chain 133R is being transported. 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 six strips from the right stocker transport chain 133R, and fed from the transport terminal end 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. The stocks of the harvested cereals for 6 lines are sandwiched and conveyed by the vertical conveying chain 134, and the tip side of the harvested cereals for 6 lines is conveyed at the feed end side of the right-handed conveyance tine 137R. The tip side of the harvested cereal stalks for the six strips harvested by the reaping device 3 is conveyed into the trunk 226 installation chamber, and the grain is shed.

  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 base transport chain 135 and the right tip transport tine 137R are driven via the vertical transmission shaft 140 and the rear transport drive shaft 147. The auxiliary stock former transport chain 136 receives driving force from the feed chain 6 side.

  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. The grain sorting mechanism 245 is configured by the above-described swing sorter 227, the red pepper fan 228, the first conveyor 231, the second conveyor 232, the dust discharge fan 230, the sorting fan 241, and the like.

  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 the second thing such as the grain with branch stems from the chaff sheave 239 onto the second conveyor 232 by rocking sorting (specific gravity sorting, Kara style sorting). It is composed. A sorting fan 241 for wind-selecting the second thing falling below the chaff sheave 239 is provided. As for the second thing dropped from the chaff sheave 239, the dust and swarf in the grain are removed by the sorting air from the sorting fan 241 (tangy wind) 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 transmission case 88 is connected to the output shaft 150 of the engine 14 via the traveling drive belt 151, and the rotational driving force of the engine 14 is transmitted from the front output shaft 150 to the transmission case 88 and shifted. 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.

  Next, a power transmission structure such as a counter case (gear case) 89 will be described with reference to FIGS. 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 driving force of the threshing selection work input shaft 165 to the handling cylinder 226 and the processing cylinder 230. A handling cylinder drive shaft 160 is provided. A threshing sorting operation input shaft 165 is connected to the output shaft 150 on the left side of the engine 14 via a tension roller type threshing clutch 161 and a threshing drive belt 162. A barrel low speed gear 115 and a barrel high speed gear 116 as a barrel shift gear mechanism 389 are arranged on the barrel drive shaft 160. The rotational force of the threshing selection work input shaft 165 is transmitted to the barrel drive shaft 160 via the barrel low speed gear 115 or the barrel high speed gear 115.

  As shown in FIGS. 1, 2, and 7, a handling cylinder low-speed gear 115 is supported on a handling cylinder drive shaft 160 through a spline 394 so as to be slidable in the axial direction. A barrel shift operation arm 395 is connected to the barrel low speed gear 115. A barrel shift operation shaft 396 is connected to the barrel shift operation arm 395 via a barrel shift operation link 396a. A barrel shift lever 398 is connected to the barrel shift operation shaft 396 via a barrel shift link mechanism 397. The barrel shift lever 398 is disposed between the cutting device 3 and the driving cabin 10, that is, on the left outer side of the driving cabin 10 facing the right side of the cutting device 3. An operator who sits on the driver's seat 12 puts his hand out of the left window of the driver's cabin 10 and operates the barrel shift lever 398 to slide the barrel low speed gear 115 on the barrel drive shaft 160 for handling. The barrel low speed gear 115 is engaged with and disengaged from the barrel high speed gear 116. When the handling cylinder low speed gear 115 is engaged with the handling cylinder high speed gear 116, the handling cylinder 226 and the processing cylinder are interposed via the handling cylinder driving belt 117 wound around the handling cylinder driving pulley 402 provided on the handling cylinder driving shaft 160. 229 rotates at a high speed, and is conveyed by the feed chain 6 while suppressing the occurrence of stabbed grains (grains are mixed into the waste and discharged from the waste cutter 235). It is configured to perform threshing work for cereals.

  Further, the cylinder driving shaft 160 includes a cylinder barrel 163 that supports the cylinder 226 via a cylinder driving pulley 402 and a cylinder driving belt 117, and a processing cylinder shaft 164 that supports the processing cylinder 230. Link. 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 7, a counter case 89 is provided on the left side of the engine 14 on the traveling machine body 1 on the front side of the threshing device 5. The counter case 89 includes a handle driving shaft 160 described above, a threshing sorting operation input shaft 165 coupled to the handling barrel drive shaft 160, a vehicle speed tuning shaft 100 coupled to the PTO shaft 99, and a threshing sorting operation input shaft 165 or A cutting transmission shaft 101 connected to the vehicle speed tuning shaft 100, a cutting drive shaft 102 connected to the cutting input shaft 17, and a feed chain driving shaft 103 for driving the feed chain 6 are arranged. An output shaft 15 of the engine 14 is connected to a threshing selection work input shaft 165 via a threshing drive pulley 118 and a threshing drive belt 162. The reaping driving force and the threshing driving force are transmitted from the threshing selection work input shaft 165 to the reaping device 3 and the threshing device 5. The PTO shaft 119 of the transmission case 88 is connected to the vehicle speed tuning shaft 100 via the PTO pulley 119, the PTO belt 120, the PTO counter pulleys 122a and 122b on the PTO counter shaft 121, the vehicle speed tuning pulley 104, and the vehicle speed tuning belt 123. A vehicle speed tuning drive force is transmitted from the PTO shaft 99 to the counter case 89.

  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 to the reaping device 3 is provided on the vehicle speed tuning shaft 100 in the counter 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 used as 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 and a cutting speed change slider 108a. It is configured to be engaged so that a cutting shift output is transmitted from the vehicle speed tuning shaft 100 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. A constant rotation speed change operation means (not shown) for performing constant rotation shifts of low speed, neutral (zero rotation) and high speed and a constant rotation switching slider 111a connect the low speed side constant rotation gear 109 or the high speed side constant rotation gear 110 to the cutting transmission shaft 101. And a constant rotational speed change output is transmitted from the threshing sorting operation input shaft 165 to the cutting transmission shaft 101 via the constant rotational mechanism 111.

  Further, the cutting drive shaft 102 is connected to the cutting transmission shaft 101 via a torque limiter 114. The cutting input shaft 17 is connected to the cutting drive shaft 102 via the cutting drive pulley 124 and the cutting drive belt 125, and the cutting drive force is transmitted from the cutting drive shaft 102 to the cutting device 3. A rotation output at a constant rotational speed necessary for maintaining the cutting operation is transmitted from the threshing selection operation input shaft 165 to the cutting transmission shaft 101 via the low-speed constant rotation gear 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. Can be improved. The threshing sorting operation input shaft 165 is connected to the tangle fan 228 or the first conveyor 231 through the threshing sorting pulley 126 and the sorting drive belt 127, and threshing and sorting is performed by the grain sorting mechanism 245 (such as the tanglet fan 228) of the threshing device 5. A threshing driving force is transmitted from the work input shaft 165.

  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 case 89 is provided with a planetary gear-type shift structure feed chain tuning mechanism 112 that connects the feed chain drive shaft 103 to the threshing selection work 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.

  Next, a power transmission structure such as the mission case 88 will be described with reference to FIGS. As shown in FIGS. 5 and 6, the transmission case 88 has a pair of first straight hydraulic pumps (HST travel pumps) 55 and a first straight hydraulic motor (HST travel motor) 56 for straight travel (travel main shift). Hydraulic continuously variable transmission mechanism 53, a swing hydraulic continuously variable transmission mechanism having a pair of swing second hydraulic pump (HST swing pump) 57 and swing second hydraulic motor (HST swing motor) 58. 54. The travel input shaft 152 of the mission case 88 is connected to the pump shafts 59 of the first hydraulic pump 55 and the second hydraulic pump 57, respectively, and is driven. A travel input pulley 155 is provided on the travel input shaft 152, and the travel drive belt 151 is wound around the travel input pulley 155. The output of the engine 14 is transmitted to the travel input pulley 155 via the travel drive belt 151. A PTO shaft 99 is disposed in the mission case 88. The PTO shaft 99 is driven by a first hydraulic motor 56 via a straight traveling motor shaft 60 and a main transmission output counter shaft 70. One end side of the PTO shaft 99 protrudes from the transmission case 88 to the left outer side. A PTO pulley 119 is provided on the PTO shaft 99, and a vehicle speed tuning belt 123 is wound around the PTO pulley 119.

  As shown in FIGS. 5 and 6, the driving force output from the output shaft 150 of the engine 14 is supplied to the pump shaft 59 and the second hydraulic pump of the first hydraulic pump 55 via the travel drive belt 151 and the travel input shaft 152. 57 are respectively transmitted to the pump shafts 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 charge pump 251 for supplying hydraulic oil to the hydraulic pumps 55 and 57 and the hydraulic motors 56 and 58 is attached to the pump shaft 59. The 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.

  As shown in FIG. 6, the rotational power of the linear motor shaft 60 is transmitted from the linear transmission gear mechanism 50 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 between the low speed and the high speed of the sub-shift. The sub-shift switch 44 is provided with a low speed switching button, a neutral switching button, and a high speed switching button. By pressing the low speed switching button, the neutral switching button, or the high speed switching button, the sub-shift output is alternatively switched to the ultra low speed output, the low speed output, the neutral, or the high speed output.

  As shown in FIG. 6, the parking brake shaft 65 (subtransmission output shaft) provided on the output side of the auxiliary transmission gear mechanism 51 is provided with a drum type parking brake 66. Rotational power from the auxiliary transmission gear mechanism 51 is transmitted from the auxiliary transmission output gear 67 fixed to the parking brake shaft 65 to the left and right differential mechanisms 52. The left and right differential mechanisms 52 are each provided with a planetary gear mechanism 68. Further, a rectilinear pulse generating rotating wheel 92 is provided on the parking brake shaft 65, and a rectilinear pick-up rotation sensor 93 (straight vehicle speed sensor) is disposed facing the rectilinear pulse generating rotating wheel 92. The rotational speed of the straight traveling output (straight traveling vehicle speed, auxiliary transmission output gear 67 output) is detected.

  As shown in FIG. 6, each of the left and right planetary gear mechanisms 68 includes one sun gear 71, a plurality of planetary gears 72 that mesh with the sun gear 71, a ring gear 73 that meshes with the planetary gear 72, and a plurality of planetary gears 72. And a carrier 74 rotatably disposed on the circumference. The carriers 74 of the left and right planetary gear mechanisms 68 are arranged on the same axis so as to 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. Each of the left and right ring gears 73 is connected to the relay shaft 85 with the outer teeth of the outer peripheral surface meshing with the left and right turning output gear 86. Each ring gear 73 is rotatably supported by left and right forced differential output shafts 77 projecting left and right outward from the outer surface of the carrier 74. Left and right axles 153 are connected to the left and right forced differential output shafts 77 via final gears 78a and 78b. Left and right drive sprockets 22 are attached to the left and right axles 153. 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 left and right axles 153 to the respective drive sprockets 22 at the same rotational speed in the same direction, and the left and right traveling crawlers 2 are transmitted to the same. Driven at the same number of rotations in the direction, the traveling machine body 1 moves straight (forward, backward).

  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 turning pulse generating rotary wheel 94 is provided on a steering counter shaft 80 to be described later, and a turning pickup rotation sensor 95 is arranged to face the turning pulse generating rotary wheel 94, and the rotation sensor 95 (turning vehicle speed) is arranged. Sensor) is configured to detect the rotational speed (turning vehicle speed) of the steering output of the second hydraulic motor 58.

  Further, in the transmission case 88, a wet multi-plate swivel brake 79 (steering brake) provided on the turning motor shaft 61 (steering input shaft), and the turning motor shaft 61 via a reduction gear 81 are provided. A steering counter shaft 80 to be connected, a steering output shaft 85 to be connected to the steering counter shaft 80 via a reduction gear 86, and a left input to connect the steering output shaft 85 to a left ring gear 73 via a reverse gear 84. A gear mechanism 82 and a right input gear mechanism 83 that connects the steering output shaft 85 to the right ring gear 73 are provided. The rotational power of the turning motor shaft 61 is transmitted to the steering counter shaft 80. The rotational power transmitted to the steering countershaft 80 is transmitted as the reverse rotational power through the left intermediate gear 87 and 86 reverse gear 84 of the left input gear mechanism 82 via the right intermediate gear 87 of the right input gear mechanism 83. Then, it is transmitted to the left and right ring gears 73 as normal rotation power.

  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 output of the second hydraulic pump 57 is in the neutral state and the turning brake 79 is in the on state, power transmission from the second hydraulic motor 58 to the left and right planetary gear mechanisms 68 is blocked. When the output of the second hydraulic pump 57 is set to a state other than neutral and the turning brake 79 is turned off, the rotational power of the second hydraulic motor 58 is transmitted to the left ring gear through the left input gear mechanism 82 and the reverse gear 84. On the other hand, it is transmitted to the right ring gear 73 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 ring gear 73 rotates reversely (forward rotation) and the right ring gear 73 rotates forward (reverse rotation) at the same rotation speed in the opposite directions. That is, the shift output from the motor shafts 60 and 61 is transmitted to the drive sprockets 22 of the left and right traveling crawlers 2 via the auxiliary transmission gear mechanism 51 or the differential mechanism 52, respectively, and the vehicle speed ( Travel speed) and direction of travel 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 ring gears 73 are stationary, the rotational output from the linear motor shaft 60 is output to the left and right sun gears 71 at the same left and right rotational speed. The left and right traveling crawlers 2 are driven at the same rotational speed in the same direction via the planetary gear 72 and the carrier 74, and the traveling machine body 1 travels straight.

  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 sun gears 71 are stationary, the left ring gear 73 is rotated by the rotational power from the turning motor shaft 61. The ring gear 73 rotates forward (reverse) and the right ring gear 73 rotates reverse (forward). As a result, one of the driving sprockets 22 of the left and right traveling crawlers 2 rotates forward, the other rotates backward, and the traveling machine body 1 changes its direction on the spot (reliable turning spin turn).

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

  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.

  On the other hand, an electro-hydraulic steering valve 270 that is electrically switched by a manual switch remote operation of the steering handle 11 and a steering cylinder 271 that is connected to the charge pump 251 via the steering valve 270 are provided. When the steering handle 11 is operated, when the steering angle of the steering handle 11 is detected by a steering angle sensor (not shown) or the like and the steering valve 270 is switched, the steering cylinder 271 is activated and the second The angle of the swash plate 57a of the hydraulic pump 57 is changed to change the rotational speed of the turning motor shaft 61 of the second hydraulic motor 58 steplessly or to perform a left / right steering operation that reverses the rotation (moving) direction. Change to left and right to change direction or correct course. Further, a steering hydraulic servo mechanism 275 is formed. The hydraulic servomechanism 275 performs a feedback operation in which the steering valve 270 returns to neutral by the angle adjustment operation of the swash plate 57a, changes the angle of the swash plate 57a in proportion to the operation amount of the steering handle 11, and the second hydraulic motor The number of revolutions 58 is changed.

  Further, as shown in FIG. 8, an electrohydraulic shift valve 272 that is electrically switched by a manual switch remote operation of the main shift lever 43 and a shift cylinder 273 that is connected to the charge pump 251 via the shift valve 272 are provided. When the main speed change lever 43 is operated, when the operation amount of the main speed change lever 43 is detected by a main speed change sensor (not shown) or the like and the speed change valve 272 is switched, the speed change cylinder 273 is operated and the first speed change cylinder 273 is operated. The angle of the swash plate 55a of the hydraulic pump 55 is changed to change the rotational speed of the linearly traveling motor shaft 60 of the first hydraulic motor 56 steplessly or to perform a traveling speed change operation that reverses the speed. A servo mechanism 277 is formed. The hydraulic servo mechanism 277 performs a feedback operation in which the transmission valve 272 returns to neutral by the angle adjustment operation of the swash plate 55a, changes the angle of the swash plate 55a in proportion to the operation amount of the main transmission lever 43, and the first hydraulic motor The rotational speed of 56 is changed, and the linear motor shaft 60 is rotated forward and backward by operating the main transmission lever 43.

  Further, as shown in FIG. 8, a cutting speed change cylinder 280 that operates the cutting speed change slider 108 a of the cutting speed change mechanism 108 and a constant cutting speed cylinder 281 that operates the constant rotation switching slider 111 a of the constant rotation mechanism 111 are provided. The cutting gear shift cylinder 280 and the cutting constant speed cylinder 281 are arranged on the inner surface side of the upper surface lid (oil path base) of the counter case 89. An electromagnetic hydraulic type cutting shift valve 282 that operates the cutting gear shift cylinder 280 and an electromagnetic hydraulic type cutting constant speed valve 283 that operates the cutting constant speed cylinder 281 are respectively hydraulically connected in parallel to the charge pump 251.

  An upper surface lid (oil passage base) 90 is detachably bolted to the upper surface of the main case body 91 of the counter case 89 to close the upper surface opening of the main case body 91 and to the upper surface side of the upper surface lid 90. The valves 282 and 283 are arranged, the cylinders 280 and 281 are arranged on the lower surface side of the upper surface lid 90, and the cylinders 280 and 281 are installed inside the main case body 91. Further, a speed change fork (not shown) for switching the cutting speed change slider 108a and a constant speed fork (not shown) for switching the constant rotation switching slider 111a to the fork shaft (not shown) in the counter case 89 are slidable in the axial direction. The pistons of the cylinders 280 and 281 are advanced or retracted by controlling the valves 282 and 283, and the shift fork is switched from neutral to high speed or standard (low speed) output side, while the constant speed fork is It is configured to switch from neutral to high speed constant rotation side or low speed constant rotation side.

  When the valves 282 and 283 are neutral, the piston rods of the cylinders 280 and 281 are moved back to the neutral position by the hydraulic pressure of the charge pump 251 to pressurize the sliders 108a and 111a without providing a spring or the like. It can be supported by returning to the neutral position in the state. The double-acting cylinders 280 and 281 can appropriately switch the three positions, can form a compact and reliable switching mechanism, and can simplify the switching structure of one or both of the mowing transmission mechanism 108 and the constant rotation mechanism 111. And improve operability.

  Next, referring to FIGS. 7 and 9, a transmission structure of the handling cylinder 226 that switches the rotation speed of the handling cylinder 226 via the handling cylinder low speed gear 115 or the handling cylinder high speed gear 116 will be described. As shown in FIGS. 7 and 9, a handling cylinder transmission gear mechanism 389 such as a handling cylinder high speed gear 116 or a handling cylinder low speed gear 115 is provided in the sub case body 92 of the counter case 89. One end side of a barrel shift counter shaft 391 is connected to the threshing sorting operation input shaft 165 via a barrel driving bevel gear 390. Of the cylinder drive shaft 160, a cylinder shift counter shaft 391 is disposed substantially parallel to the lower side of the cylinder drive shaft 160 in the sub case body 92. A high-speed transmission gear 392 and a low-speed transmission gear 393 are fixed on the barrel shift counter shaft 391. Between the high-speed transmission gear 392 and the low-speed transmission gear 393, the vehicle speed tuning shaft 100 in the counter case 89 extends in a direction orthogonal (crossed) to the cylinder shifting counter shaft 391 on the lower side of the cylinder shifting counter shaft 391. Has been.

  Further, as shown in FIGS. 1, 2, 7, and 9, a handling cylinder high-speed gear 116 is pivotally supported on the handling cylinder drive shaft 160 through a spline 394 so as to be slidable in the axial direction. A speed change operation shaft 396 is connected to the barrel high speed gear 116 via a speed change shifter 395. A barrel shift lever 398 is connected to the shift operation shaft 396 via a barrel shift link mechanism 397. The barrel shift lever 398 is disposed between the cutting device 3 and the driving cabin 10, that is, on the left outer side of the driving cabin 10 facing the right side portion of the cutting device 3. An operator who sits on the driver's seat 12 puts his hand out of the left window of the driver's cabin 10 and operates the barrel shift lever 398 to slide the barrel high-speed gear 116 on the barrel drive shaft 160, thereby speeding up the operation. The transmission gear 392 is configured to engage and disengage the barrel high speed gear 116. When the handling cylinder high-speed gear 116 is engaged with the high-speed transmission gear 392, the handling cylinder 226 and the processing cylinder 229 are disposed via the handling cylinder driving belt 117 wound around the handling cylinder driving pulley 402 provided on the handling cylinder driving shaft 160. Is configured to thresh while suppressing the occurrence of stabbed grains (grains are mixed in the waste and discharged from the waste cutter 235 part).

  As shown in FIG. 9, a handling cylinder low-speed gear 115 is rotatably supported on a handling cylinder drive shaft 160 via a bearing bearing 399. The barrel low speed gear 115 and the low speed transmission gear 393 are always meshed. Clutch claws 400 and 401 that can be engaged and disengaged are integrally formed on opposite side surfaces of the barrel high speed gear 116 and the barrel low speed gear 115, respectively. An operator who sits on the driver's seat 12 puts his hand out of the left window of the driver's cabin 10 and operates the barrel shift lever 398 to slide the barrel high-speed gear 116 on the barrel drive shaft 160, thereby speeding up the operation. When the barrel high speed gear 116 is disengaged from the transmission gear 392, the clutch pawl 400 of the barrel fast gear 116 is locked to the clutch pawl 401 of the barrel low speed gear 115, and the barrel via the clutch pawls 400, 401. A barrel high speed gear 116 is connected to the low speed gear 115. The handling cylinder 226 and the processing cylinder 229 are driven at a low speed through the handling cylinder low speed gear 115 and the handling cylinder high speed gear 116.

  As shown in FIG. 9, when the barrel high speed gear 116 is engaged with the high speed transmission gear 392, the barrel drive belt 117 wound around the barrel drive pulley 402 provided on the barrel drive shaft 160 is interposed. The handling cylinder 226 and the processing cylinder 229 rotate at a high rotational speed, and are configured to thresh while suppressing the occurrence of stabbed grains (such as being discharged out of the machine when grains are mixed in the waste). ing. On the other hand, when the cylinder high speed gear 116 is connected to the cylinder low speed gear 115 via the clutch claws 400 and 401, the cylinder driving belt 117 wound around the cylinder driving pulley provided on the cylinder driving shaft 160. , The handling cylinder 226 and the processing cylinder 229 rotate at a low speed, and the occurrence of slag breakage (a lot of swarf is mixed in the selected grain on the swinging sorter 227 and the sorting accuracy decreases. Etc.) and threshing.

  As shown in FIGS. 1, 5, 7, and 9, a traveling machine body 1 on which an engine 14 is mounted, a threshing device 5 having a handling cylinder 226, and a handling cylinder transmission gear that transmits the power of the engine 14 to the handling cylinder 226. A mechanism transmission gear mechanism 389 is provided with a cylinder high-speed gear 116 and a cylinder low-speed gear 115 row as a cylinder transmission gear capable of selecting the number of rotations of the cylinder 226 in multiple stages based on harvesting work conditions. It is composed. Therefore, by switching the rotation speed of the handling cylinder 226 in multiple stages via the handling cylinder transmission gear mechanism 389, the degranulation function of the handling cylinder 226 can be easily changed according to a plurality of work conditions.

  As shown in FIGS. 5, 7, and 9, the cutting transmission mechanism 108, the high-speed constant rotation gear 110 (high-speed cut transmission mechanism) of the constant rotation mechanism 111, or the low-speed constant rotation gear 109 (casting) of the constant rotation mechanism 111. A transmission case), a feed chain tuning mechanism 112 (feed chain driving mechanism), or a counter case 89 incorporating a threshing sorting operation input shaft 165 (sorting driving mechanism), and a vehicle speed tuning shaft 100 (cutting speed change) in the counter case 89. A handling cylinder high-speed gear 116, a handling cylinder low-speed gear 115, a high-speed transmission gear 392, and a low-speed transmission gear 393 line are arranged so as to straddle the shaft. Further, a barrel shift counter shaft 391 provided with a high-speed transmission gear 392 and a low-speed transmission gear 393 is substantially parallel to a lower side of the barrel driving shaft 160 provided with the barrel high-speed gear 116 and the barrel low-speed gear 115. Has been placed. A vehicle speed tuning shaft 100 is extended on the lower side of the barrel shift counter shaft 391 in a direction crossing the barrel shift counter shaft 391. In other words, the barrel high speed gear 116 and the barrel low speed gear 115 are supported above the barrel shift counter shaft 391 via the barrel drive shaft 160 and fixed to a fixed position on the barrel shift counter shaft 391. Between the high-speed transmission gear 392 and the low-speed transmission gear 393, the vehicle speed tuning shaft 100 is disposed below the barrel shift counter shaft 391.

  With the configuration described above, the vehicle speed tuning shaft 100 is brought close to the barrel drive shaft 160 and the barrel shift counter shaft 391, and the cutting gear shift mechanism 108 or the barrel shift speed is set in the counter case 89 via the shafts 100, 160, 391. Although the gear mechanism 389 can be supported in a compact manner, the speed change operation of the barrel high speed gear 116 is not limited by the vehicle speed tuning shaft 100. That is, the drive mechanism of the working unit such as mowing, threshing, and sorting can be integrated in the counter case 89. The maintenance workability of the transmission structure can be improved. The low speed side transmission gear 106 and the high speed side transmission gear 107 (cutting transmission gear) train of the cutting transmission mechanism 108, the handling cylinder high speed gear 116, the handling cylinder low speed gear 115, the high speed transmission gear 392, the low speed transmission of the handling cylinder transmission gear mechanism 389. The gears 393 can be crossed so that the gears 106, 107, 115, 116, 392, and 393 can be arranged compactly in the counter case 89. The counter case 89 can be configured at low cost without increasing the size.

  As shown in FIGS. 1, 2, 7, and 9, a cylinder shift lever 398 (cylinder transmission operation tool) that switches between the high speed cylinder 116 and the low speed gear 115 of the cylinder transmission gear mechanism 389. And a barrel shift lever 398 is disposed between the driver's seat 12 and the cutting device 3. Therefore, between the driver's seat 12 disposed obliquely in front of the threshing device 5 and the counter case 89 disposed at the front of the threshing device 5, the handle shift lever 398 is placed at a position where the operator of the driver's seat 12 can easily operate. Although it can be installed, the barrel shift lever 398 can be easily connected to the counter case 89 at a relatively short distance, and the barrel shift link mechanism 397 (the barrel shift operation link mechanism) linked to the barrel shift lever 398, etc. Can be assembled at a low cost and compactly.

  Next, the transmission structure of the engine 14, the transmission case 88, and the counter case 89 will be described with reference to FIGS. 5, 7, and 10 to 16. As shown in FIGS. 5, 7, and 10 to 13, the engine 14 is mounted on the right side of the upper surface of the traveling machine body 1, and a transmission case 88 is installed in front of the center of the left and right width of the traveling machine body 1. A counter case 89 is disposed on the left side of the upper surface. An output pulley 149 is pivotally supported on the left end portion of the output shaft 150 of the engine 14 extended in the left-right direction, and a traveling drive belt 151 is hung between the traveling input pulley 155 and the output pulley 149 on the upper left side of the transmission case 88. It is turning. With this configuration, the output of the engine 14 is transmitted to the continuously variable transmission mechanisms 53 and 54 of the mission case 88.

  On the other hand, a columnar frame 290 that supports the discharge auger 8 in a storage (non-working) position is erected on the upper surface of the traveling machine body 1, and a PTO countershaft 121 is mounted on the front surface of the base end portion of the columnar frame 290 via a bearing body 291. Is rotatably supported. The PTO belt 120 is wound around between the PTO counter pulley 122 a and the PTO pulley 119 on the PTO counter shaft 121. Further, a vehicle speed tuning belt 123 is wound around the PTO counter pulley 122 b on the PTO counter shaft 121 and the vehicle speed tuning pulley 104. With this configuration, the vehicle speed tuning drive force of the transmission case 88 is transmitted from the PTO shaft 99 to the vehicle speed tuning shaft 100.

  Further, a threshing drive belt 162 is wound around between an output pulley 149 on the output shaft 150 of the engine 14 and a threshing drive pulley 118. In addition, a threshing clutch electric motor 175 as a threshing input actuator for switching the threshing clutch 161 and a threshing sorting operation input shaft 165 as a sorting drive shaft for transmitting the power of the engine 14 to the grain sorting mechanism 245 are provided. By operating the threshing clutch electric motor 175 to engage and operate the threshing clutch 161, the threshing drive belt 162 is maintained in a tension state, and the output of the engine 14 is transmitted to the counter case 89, while the threshing clutch 161 is turned off. By the operation, the threshing drive belt 162 is maintained in a relaxed state.

  A clutch unit chassis 176 is disposed on the upper surface of the traveling machine body 1 at the rear of the engine 14, a threshing clutch on / off mechanism 177 is assembled to the clutch unit chassis 176, and an electric motor 175 for threshing clutch is provided on the clutch unit chassis 176. A threshing clutch electric motor 175 is connected to a tension arm (not shown) that supports the threshing clutch 161 via a threshing clutch on / off mechanism 177. A threshing clutch electric motor 175 is arranged on the opposite side of the counter case 89 with a threshing drive pulley 118 on the threshing selection work input shaft 165 supported by the counter case 89 interposed therebetween.

  That is, since it is not necessary to secure a space on the counter case 89 side where the threshing clutch electric motor 175 or the threshing clutch on / off mechanism 177 is installed, the threshing driving pulley 118 can be supported close to the right side of the counter case 89. Without being restricted by the threshing clutch electric motor 175 or the threshing clutch insertion / cutting mechanism 177, the rigidity of the bearing structure accompanying the extension of the threshing selection work input shaft 165 is not required, and a large gear ratio (reduction ratio) is obtained. A settable large-diameter threshing drive pulley 118 can be easily installed.

  Further, as shown in FIGS. 12, 15, and 16, the counter case 89 includes an upper cover 90, a main case body 91, a right subcase body 92, and a left subcase body 93. An upper surface lid 90 is fastened to the upper surface of the main case body 91 so as to close the upper surface opening. The right subcase body 92 is fastened to the right side surface of the main case body 91 so as to close the right side surface opening. The left subcase body 93 is fastened to the left side surface of the main case body 91 so as to close the left side surface opening. Further, in the main case body 91, a cutting transmission mechanism 108, a constant rotation mechanism 111, and the like are arranged. On the other hand, a barrel transmission gear mechanism 389 and the like are disposed in the right subcase body 92. A barrel shift operation shaft 396 is projected upward from the upper surface of the right subcase body 92, and a barrel shift lever 398 is coupled to the barrel shift operation shaft 396 via a barrel shift link mechanism 397. On the other hand, the feed chain tuning mechanism 112 or the torque limiter 114 is disposed in the left subcase body 9 3.

  A plurality of case pedestals 94 are projected from the upper surface of the traveling machine body 1, while a plurality of cases are provided on the front and rear surfaces of the left end portion of the main case body 91 and the front and rear surfaces of the left end portion of the right subcase body 92. The support legs 95 and 96 are integrally formed. The support legs 95 and 96 are placed on the upper surface of each case support 94, and the support legs 95 and 96 are fastened to the case support 94 with case support bolts 97, respectively. That is, the counter case 89 is configured to be attached to and detached from the traveling machine body 1 in a state where the right sub case body 92 and the left sub case body 93 are integrally combined with the main case body 91.

  With the above configuration, by forming the right subcase body in which the handling cylinder transmission gear mechanism 389 and the like are not disposed, the right side subcase body 92 in which the handling cylinder transmission gear mechanism 389 and the like are disposed is substituted for the handling cylinder transmission. The right subcase body in which the gear mechanism 389 or the like is not disposed can be integrally combined with the main case body 91. That is, by sharing the main case body 91 and the left subcase body 93 and replacing the right subcase body 92 as described above, the specification of the counter case 89 having the barrel transmission gear mechanism 389 and the like is changed to the barrel transmission gear mechanism 389. It is possible to easily change to the specification of the counter case 89 that does not have the above.

  As shown in FIGS. 1, 7, 13, 15, and 16, a threshing device having a traveling machine body 1 on which an engine 14 is mounted, a cutting device 35 having a cutting blade 132, a handling drum 226, and a grain sorting mechanism 245. 5 and the counter case 89 that transmits the power of the engine 14 to the reaping device 3 or the threshing device 5, the counter case 89 includes a cutting speed change mechanism 108 that transmits the power of the engine 14 to the reaping device 3. The main case body 91 is provided, and a right subcase body 92 in which a barrel transmission gear mechanism 389 as a barrel transmission mechanism for transmitting the power of the engine 14 to the barrel 226 is provided. Therefore, when changing specifications such as the presence or absence of the barrel transmission gear mechanism 389, the main case body 91 in which the cutting transmission mechanism 108 is installed can be used without changing, and many components can be shared by a plurality of specifications. Further, the barrel transmission gear mechanism 389 can be easily connected to the barrel shift lever 398 and the like operated by the operator of the driver seat 12. The manufacturing cost of the counter case 89 and the like can be reduced, and the assembly workability can be improved.

  As shown in FIGS. 7, 9, 15, and 16, a barrel transmission gear mechanism 389 is configured to be assembled in the right subcase body 92 before being joined to the main case body 91, and the barrel transmission gear mechanism is configured. A barrel shift operation shaft 396 for shifting the gear 389 is projected upward from the upper surface of the right subcase body 92. Therefore, the barrel shift operation shaft 396 can be provided toward the driver's seat 12 and the like disposed obliquely forward of the threshing device 5, and the barrel shift operation lever 398 and the like are placed at a position where the operator of the driver seat 12 can easily operate. Can be installed. That is, the barrel shift operation lever 398 (or barrel shift switch) or the like can be easily connected to the counter case 89 at a relatively short distance, and the barrel shift operation link mechanism 397 (or the link to the barrel shift operation lever 398 or the like). It is possible to construct a low-cost electrical wiring for handling cylinder shifting) and to assemble it in a compact manner.

  As shown in FIGS. 1, 2, and 9, a barrel shift operation lever 398 is disposed between the cutting device 3 and the driver seat 12, and a barrel shift operation shaft 396 on the upper surface of the counter case 89 is operated from above. The lever 398 is connected. Therefore, the barrel shift operation lever 398 can be easily connected to the barrel shift operation shaft 396 at the shortest distance by effectively utilizing the dead space between the reaping device 3 and the driver seat 12. For example, a barrel shift operation lever 398 can be disposed on the outer side of the cabin 10 or the like on which the operator is boarded, and maintenance workability of the engine 14 or the like that requires opening / closing (detaching) of the cabin 10 can be improved.

  As shown in FIGS. 11, 13, and 14, the threshing drive pulley 118 to which the power of the engine 14 is transmitted through the threshing clutch 161, and the threshing clutch electric motor 175 as a threshing input actuator for switching the threshing clutch 161. And a threshing sorting operation input shaft 165 as a sorting drive shaft for transmitting the power of the engine 14 to the grain sorting mechanism 245, and the counter case 89 rotatably supports the threshing sorting operation input shaft 165. The threshing drive pulley 118 is disposed on the threshing selection work input shaft 165, and the counter case 89 and the threshing clutch electric motor 175 are disposed with the threshing drive pulley 118 interposed therebetween. Therefore, the threshing drive pulley 118 having a large diameter is provided on one side of the counter case 89 without being restricted by the threshing clutch electric motor 175, compared to the structure in which the counter case 89 is provided with the electric motor 175 for threshing clutch. Easy to support. Further, since the threshing clutch electric motor 175 can be disposed in the vicinity of the threshing driving pulley 118, the threshing clutch electric motor 175 can be easily connected to the tension pulley type threshing clutch 161 for tensioning the threshing driving belt 162.

1 traveling machine body 3 reaping device 5 threshing device 12 driving seat 14 engine 88 transmission case 89 counter case 91 main case body 92 right subcase body 108 reaping transmission mechanism 118 threshing drive pulley 132 threshing blade 161 threshing clutch 165 threshing selection work input shaft ( Sorting drive shaft)
175 Electric motor for threshing clutch (threshing input actuator)
226 Handling cylinder 245 Grain sorting mechanism 389 Handling cylinder transmission gear mechanism (handling transmission mechanism)
396 Handle cylinder speed change operation shaft 398 Handle cylinder speed change lever

Claims (4)

In a combine equipped with a traveling machine body equipped with an engine, a reaping device having a cutting blade, a threshing device having a handling cylinder and a grain sorting mechanism, and a counter case for transmitting the power of the engine to the reaping device or the threshing device ,
The counter case includes a main case body in which a cutting transmission mechanism for transmitting the power of the engine to the cutting device is provided, and a sub-case in which a handling cylinder transmission mechanism for transmitting the power of the engine to the handling cylinder is provided. A combine having a case body.   The barrel transmission mechanism is configured so that it can be assembled in the sub case body before being combined with the main case body, and a barrel transmission operation shaft for shifting the barrel transmission mechanism is provided on the upper surface of the sub case body. The combine according to claim 1, wherein the combine is made to protrude upward.   2. A barrel shift operation lever is disposed between the cutting device and a driver seat, and the barrel shift operation lever is connected from above to the barrel shift operation shaft on the upper surface of the counter case. Combine as described.   The counter case includes a threshing drive pulley to which the power of the engine is transmitted via a threshing clutch, a threshing input actuator for switching the threshing clutch, and a sorting drive shaft for transmitting the engine power to the grain sorting mechanism. The sorting drive shaft is rotatably supported, the threshing drive pulley is arranged on the sorting drive shaft, and the counter case and the threshing input actuator are arranged across the threshing drive pulley. The combine according to claim 1, characterized in that:

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