JP6747887B2 - combine - Google Patents

Description

The present invention relates to a combine equipped with a mowing unit for mowing uncut grain culms in a field and a threshing unit for slashing grains of the mowing grain culm.

Conventionally, in a normal combine harvester equipped with a feeder house that conveys grain culms cut by the mowing section to the handling barrel, a beater for throwing grain culms is provided in the harvesting unit between the end of the feeder house and the inlet of the handling barrel to the handling barrel. There is a technique for improving the uptake property of the harvested grain rod (see Patent Document 1). Further, in a self-removing combine equipped with a feed chain that conveys the culms cut by the reaping section to the handling cylinder, it has been proposed that the hydraulic oil to be supplied to the continuously variable transmission for traveling be stored in the hydraulic oil tank. (See Patent Documents 2 and 3). Further, there is a technique of driving a left and right traveling unit by providing a hydraulic pump and a hydraulic motor in the left and right traveling units in a normal combine (see Patent Document 4).

JP, 2000-037126, A JP, 2004-058824, A JP, 2005-084709, A JP, 2010-239980, A

In the prior arts shown in Patent Documents 1, 2 and 4, there is a distance between the engine and the hydraulic oil tank, cooling air to the engine is not supplied to the hydraulic oil tank, and The cooling effect by the engine cooling air is not exerted. Further, although the conventional technique disclosed in Patent Document 3 has a configuration in which cooling air from the engine flows toward the hydraulic oil tank, a sufficient cooling effect cannot be obtained, and cooling with an oil cooler is required. ing.

Therefore, the present invention is intended to provide a combine that has been improved by examining these present conditions.

In order to achieve the above-mentioned object, the combine of the present invention comprises a threshing section equipped with a handling cylinder, a traveling machine body on which an engine and a mission case are mounted, and a mowing section is provided at a front part of the threshing section. In a combine that throws the cut culm transported through the feeder house into the threshing section by a beater provided on the terminal side of the feeder house, a hydraulic oil tank that stores hydraulic oil is on the traveling machine body, and It is installed in a space position surrounded by a feeder house and the beater, and is arranged side by side in front of the traveling machine body so that the engine and at least a part of the hydraulic oil tank overlap in a side view of the traveling machine body. , The threshing part pivotally supports Kara-miso, and a second counter shaft rotatable relative to the Kara-mitsu shaft of the Kara-mitsu penetrates the Kara-mitsu shaft, and the second counter-shaft extends from the engine. Is transmitted to the first counter shaft, and the rotational power of the first counter shaft is branched and transmitted to each of the Karako shaft and the beater shaft of the beater .

In the above combine, the hydraulic oil tank may have an oil supply port projecting toward the outside of the machine on the side surface of the outside of the machine, and may internally include an oil filter that can be inserted and removed from the outside of the machine.

In the combine, the hydraulic pipe connected to the hydraulic oil tank is provided by extending the front of the hydraulic oil tank and the engine to the left and right, and a part of the hydraulic pipe is a hydraulic pump arranged in front of the engine. It may be in communication with the oil filter.

In the combine, the machine housing includes front and rear support frames standing upright from the traveling machine body before and after the beater, and upper and lower beam frames that erect upper and middle parts of the front and rear support frames, respectively. A first counter shaft that receives a driving force from an engine is pivotally supported by the rear support frame, and a beater bearing body connected to the upper and lower beam frames supports the beater shaft of the beater at a position in front of the front support frame. A shaft-supported mowing input shaft penetrates the feeder house, a first power transmission mechanism that transmits the rotational power of the first counter shaft to the beater shaft, and the rotational power of the beater shaft is the mowing input shaft. And a second power transmission mechanism for transmitting the power to the hydraulic oil tank, and the oil supply port and the oil filter of the hydraulic oil tank are arranged in a region surrounded by the first and second power transmission mechanisms and the front support frame. It may be one.

In the above combine, the threshing portion pivotally supports Kara-mino on the rear side of the rear support frame, and a second counter shaft capable of relative rotation with respect to the Kara-mitsu shaft of the Kara-mino penetrates the Kara-mitsu shaft. The second counter shaft receives the power from the engine and transmits the power to the first counter shaft, and the rotational power of the first counter shaft is branched and transmitted to each of the Karako shaft and the beater shaft. It may be one.

According to the present invention, the hydraulic oil tank is arranged in the space surrounded by the feeder house and the machine casing of the threshing unit, and it is possible to prevent dust from the cutting unit from accumulating in the hydraulic oil tank, and to refuel. It is also possible to prevent contamination of hydraulic oil due to intrusion of dust from the mouth and the like. Further, since the cooling air from the engine flows into the installation space of the hydraulic oil tank, it is possible to suppress the rise of the hydraulic oil temperature without providing an oil cooler on the hydraulic circuit, and it is possible to drive each hydraulic member appropriately.

According to the present invention, since the oil supply port and the oil filter are provided on the outer side surface of the hydraulic oil tank, it is possible to easily access the oil supply port and the oil filter by removing the threshing cover provided on the outer side of the threshing unit. it can. As a result, the work of refueling the hydraulic oil tank and the work of replacing the oil filter can be facilitated, and the maintainability of the hydraulic circuit can be improved.

According to the invention of the present application, since the hydraulic pipe extends around the front of the engine toward the hydraulic oil tank and extends along the output shaft of the engine, the hydraulic pipe is less likely to be affected by radiant heat from the engine. Since the pipe length is arranged to be short at the position, it is possible to suppress the temperature rise of the hydraulic oil flowing through the hydraulic pipe.

According to the present invention, since the oil supply port and the oil filter of the hydraulic oil tank are arranged in the area surrounded by the first and second power transmission mechanisms and the front support frame, the transmission in the first and second power transmission mechanisms is performed. It is possible to refuel the working oil tank and replace the oil filter without removing the material (chain or belt).

According to the invention of the present application, the drive system for driving the mowing part, the sardines and the like is concentratedly installed outside the machine of the threshing part, so that the front side of the threshing part inside the machine can be opened. Therefore, the hydraulic oil tank installation space on the lower front side of the threshing unit is opened toward the inside of the machine, and a large amount of cooling air can be guided to the hydraulic oil tank installation space.

It is a left side view of the combine which shows a 1st embodiment of the present invention. It is a right view of the combine. It is a top view of the combine. It is a drive system diagram of a combine. It is a perspective view of the combine seen from diagonally front. It is a partial plane sectional view of a threshing part. It is a drive system diagram of a mission case. It is a front view which shows the structure of an engine room and a threshing part. It is a hydraulic circuit diagram which shows the structure of a work system hydraulic circuit. It is a perspective view showing composition of a work system hydraulic circuit. It is a perspective view of the threshing part seen from diagonally forward. It is a left side enlarged view of a threshing part. It is a plane sectional view showing composition of an engine room and a threshing part. It is a front view which shows the arrangement structure of a hydraulic circuit component. It is a hydraulic circuit diagram showing a configuration of a traveling hydraulic circuit. It is a top view which shows the piping structure of a hydraulic circuit.

Embodiments embodying the present invention will be described below with reference to the drawings (FIGS. 1 to 10) applied to a normal combine. 1 is a left side view of the combine, FIG. 2 is a right side view thereof, and FIG. 3 is a plan view thereof. First, a schematic structure of a combine will be described with reference to FIGS. 1 to 3. 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 to 3, the ordinary combine in the embodiment includes a traveling machine body 1 supported by a pair of right and left crawler tracks 2 made of rubber crawlers as a traveling portion. At the front part of the traveling machine body 1, a reaping unit 3 for taking in uncut rice culms such as rice (or wheat, soybeans, or corn) while mowing is attached by a single-acting hydraulic cylinder 4 for raising and lowering. ing.

A threshing unit 9 for threshing the cut culm supplied from the reaping unit 3 is mounted on the left side of the traveling machine body 1. Below the threshing section 9, a grain selection mechanism 10 for performing swing selection and wind selection is arranged. An operator's cab 5 on which an operator rides is mounted on the front right side of the traveling machine body 1. The engine 7 as a power source is arranged in the driver's cab 5 (below the driver's seat 42). Behind the driver's cab 5 (on the right side of the traveling machine body 1), a grain tank 6 for extracting grains from the threshing unit 9 and a grain for discharging the grains in the grain tank 6 toward a truck carrier (or container, etc.) Arrange the discharge conveyor 8. The grain discharge conveyor 8 is tilted to the outer side of the machine, and the grains in the grain tank 6 are carried out by the grain discharge conveyor 8.

The mowing unit 3 includes a feeder house 11 that communicates with a handling port 9a at the front of the threshing unit 9, and a horizontally long bucket-shaped grain header 12 that is continuously provided at the front end of the feeder house 11. A scraping auger 13 (platform auger) is rotatably supported in the grain header 12. A take-in reel 14 with a tine bar is arranged above the front part of the take-in auger 13. A clipper-shaped cutting blade 15 is arranged at the front of the grain header 12. Left and right grass bodies 16 are provided on both left and right sides of the front part of the grain header 12. Further, a supply conveyor 17 is installed inside the feeder house 11. A cutting grain culm charging beater 18 (front rotor) is provided on the feeding end side (handle 9a) of the supply conveyor 17. The lower surface of the feeder house 11 and the front end of the traveling machine body 1 are connected to each other through a lifting hydraulic cylinder 4, and the mowing unit 3 uses the mowing input shaft 89 (feeder house conveyor shaft) described below as a lifting fulcrum. It is moved up and down by the lifting hydraulic cylinder 4.

With the above configuration, the tip end side of the uncut grain culm between the left and right grass bodies 16 is scraped by the scraping reel 14, the culm side of the uncut grain culm is cut by the cutting blade 15, and the scraped auger 13 is cut. Due to the rotation drive, the cut grain culms are collected near the entrance of the feeder house 11 near the center of the width of the grain header 12. The whole amount of the cut grain culm of the grain header 12 is conveyed by the supply conveyor 17, and is introduced into the handle 9a of the threshing unit 9 by the beater 18. In addition, a horizontal control hydraulic cylinder (not shown) for rotating the grain header 12 around a horizontal control fulcrum axis is provided, and the horizontal inclination of the grain header 12 is adjusted by the horizontal control hydraulic cylinder to control the grain header. It is also possible to support 12, the cutting blade 15, and the take-up reel 14 horizontally with respect to the field scene.

Further, as shown in FIGS. 1 and 3, a handling barrel 21 is rotatably provided in the handling room of the threshing unit 9. A handling barrel 21 is supported on a handling barrel shaft 20 (see FIG. 4) extended in the front-rear direction of the traveling vehicle body 1. On the lower side of the handling cylinder 21, a receiving net 24 that stretches down the grains is stretched. A spiral screw blade-shaped intake blade 25 is provided on the outer peripheral surface of the front portion of the handling cylinder 21 so as to project radially outward.

With the above-described configuration, the harvested culm thrown from the handling port 9a by the beater 18 is conveyed toward the rear of the traveling machine body 1 by the rotation of the handling drum 21, while being transferred between the handling drum 21 and the receiving net 24 and the like. Are kneaded and threshed. Grains such as grains smaller than the mesh of the receiving net 24 leak from the receiving net 24. Straws and the like that do not leak from the net 24 are discharged to the field from the dust outlet 23 at the rear of the threshing unit 9 by the conveying action of the handling cylinder 21.

In addition, a plurality of dust-sending valves (not shown) for adjusting the transfer speed of the grain removal inside the handling chamber are rotatably mounted on the upper side of the handling cylinder 21. By adjusting the angle of the dust delivery valve, the transport speed (residence time) of the grain-removed grains in the handling chamber can be adjusted according to the variety and the nature of the cut grain culms. On the other hand, as a grain selection mechanism 10 arranged below the threshing unit 9, a swing sorting disc 26 for specific gravity sorting having a Glen pan, a chaff sheave, a Glen sieve, a Straw rack, etc. is provided.

Further, as the grain selection mechanism 10, a blower fan-shaped Kara 29 or the like for supplying the selection wind to the swinging selection board 26 is provided. The threshing that has been threshed by the handling cylinder 21 and has leaked from the net 24 is carried out by the specific gravity sorting action of the swing sorting board 26 and the wind sorting action of the blast fan-shaped Kara 29, which causes No.), a mixture of grains and straw (a second product such as a grain with a branch stem), and straw waste, etc. are selected and taken out.

As the grain selection mechanism 10, a first conveyor mechanism 30 and a second conveyor mechanism 31 are provided on the lower side of the swing selection board 26. Grain (first product) dropped from the swing sorting disc 26 by the swing sorting disc 26 and the blast fan-shaped Kara 29 is collected in the grain tank 6 by the first conveyor mechanism 30 and the lifting grain conveyor 32. It The mixture of grain and straw (second) is returned to the sorting start end side of the swing sorting board 26 via the second conveyor mechanism 31 and the second reduction conveyor 33, and re-sorted by the swing sorting board 26. It Straws and the like are configured to be discharged to the field from the dust outlet 23 at the rear of the traveling machine body 1.

Further, as shown in FIGS. 1 to 3, the driver's cab 5 is provided with a control column 41 and a driver's seat 42 on which an operator sits. The steering column 41 includes an accelerator lever 40 for adjusting the number of revolutions of the engine 7, a round-shaped steering handle 43 for changing the course of the traveling body 1 by an operator's rotation operation, and a main for switching the traveling speed of the traveling body 1. A shift lever 44 and an auxiliary shift lever 45, a harvesting clutch lever 46 that drives or stops the harvesting unit 3, and a threshing clutch lever 47 that drives or halts the threshing unit 9 are arranged. Further, a sunshade roof body 49 is attached to the front upper surface side of the Glen tank 6 via a sun visor support 48, and the sunshade roof body 49 covers the upper side of the cab 5.

As shown in FIGS. 1 and 2, left and right track frames 50 are arranged on the lower surface side of the traveling machine body 1. The track frame 50 has a drive sprocket 51 that transmits the power of the engine 7 to the crawler belt 2, a tension roller 52 that maintains the tension of the crawler belt 2, and a plurality of track rollers 53 that keeps the ground side of the crawler belt 2 in a grounded state. An intermediate roller 54 that holds the non-grounded side of the crawler belt 2 is provided. The front side of the crawler belt 2 is supported by the drive sprocket 51, the rear side of the crawler belt 2 is supported by the tension roller 52, the ground side of the crawler belt 2 is supported by the track roller 53, and the non-ground side of the crawler belt 2 is supported by the intermediate roller 54. Configure to allow.

Next, the drive structure of the combine will be described with reference to FIGS. As shown in FIG. 4 and FIG. 7, the transmission case 63 is provided with a straight traveling hydraulic continuously variable transmission 64 for traveling speed change, which has a hydraulic straight traveling pump 64a and a hydraulic straight traveling motor 64b. The engine 7 is mounted on the right upper surface of the front part of the traveling body 1, and the mission case 63 is arranged on the front part of the traveling body 1 on the left side of the engine 7. An output shaft 65 protruding leftward from the engine 7 and a mission input shaft 66 protruding leftward from the mission case 63 are connected via an engine output belt 67, an engine output pulley 68, and a mission input pulley 69. There is.

Further, a steering swing hydraulic continuously variable transmission 70 having a hydraulic swing pump 70a and a hydraulic swing motor 70b is provided in the mission case 63, and a straight traveling hydraulic continuously variable transmission 64 and a swing hydraulic type are provided via a mission input shaft 66. While transmitting the output of the engine 7 to the continuously variable transmission 70, the steering handle 43, the main speed change lever 44, and the auxiliary speed change lever 45 output the straight traveling hydraulic type continuously variable transmission 64 and the turning hydraulic type continuously variable transmission 70. The crawler belts 2 on the right and left sides are controlled and driven through the straight traveling hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 so as to travel and move in a field or the like.

Further, as shown in FIG. 4 to FIG. 6 and FIG. 8, a handling barrel drive case 71 that pivotally supports the front end side of the handling barrel shaft 20 is provided. A handling cylinder drive case 71 is arranged on the front side of the threshing unit 9. A handling cylinder input shaft 72 for driving the reaping unit 3 and the handling barrel 21 is pivotally supported on the handling barrel drive case 71. Further, a main counter shaft 76 is provided as a constant rotation shaft that penetrates the threshing unit 9 to the left and right. A working unit input pulley 83 is provided at the right end of the main counter shaft 76. The right end of the main counter shaft 76 is connected to the engine output pulley 68 on the output shaft 65 of the engine 7 via a threshing clutch 84 that also serves as a tension roller and a working unit drive belt 85.

In front of the handling barrel 21, a handling barrel input shaft 72 extending in the lateral direction of the traveling machine body 1, a beater 18 disposed in the lateral direction of the traveling machine body 1, and a reaping input shaft extending in the lateral direction of the traveling machine body 1 are provided. 89 is provided. As the handling cylinder input mechanism 90 for transmitting the driving force of the main counter shaft 76 to the handling barrel input shaft 72, the handling barrel driving pulleys 86, 87 and the handling barrel driving belt 88 are provided, and the driving force from the engine 7 is transmitted. The handling cylinder input mechanism 90 (the handling body drive pulleys 86, 87 and the handling body drive belt 88) is arranged at one end of the counter shaft 76 on the engine 7 side, and the handling body 21 is driven to rotate at a constant rotation output with a constant rotation output of the engine 7. Is configured as follows.

A beater drive mechanism and a cutting drive mechanism for transmitting the driving force of the main counter shaft 76 to the beater shaft 82 and the cutting input shaft 89 are provided on the other end side of the main counter shaft 76. Further, the sub counter shaft 104 is disposed between the beater shaft 82 and the main counter shaft 76, and the power relay belt 113 is wound around the power relay pulleys 105 and 106 provided on the main counter shaft 76 and the sub counter shaft 104. It constitutes a power relay mechanism that is rotated to transmit power to the reaping drive mechanism.

The mowing drive belt 114 is wound around the mowing drive pulleys 107 and 108 provided on the sub-counter shaft 104 and the beater shaft 82, respectively, to form a beater drive mechanism. The reaping drive belt 114 is stretched by the reaping clutch 109 that also serves as a tension roller, so that the rotational power from the engine 7 transmitted to the main counter shaft 76 is transmitted to the beater via the power relay mechanism and the beater drive mechanism. Input to the shaft 82. Further, a cutting drive mechanism is configured so that the cutting drive force from the engine 7 is transmitted from the beater shaft 82 on which the beater 18 is axially supported to the cutting input shaft 89 via the cutting drive chain 115 and the sprockets 116 and 117. ing. As a result, the mowing unit 3 is driven to rotate with the beater 18 at a constant rotation output of the engine 7.

The Karato shaft 100, which is the rotating shaft of the fan-shaped Karato 29, has a hollow tube shape, and the main counter shaft 76 is inserted in the hollow portion of the Karato shaft 100. That is, the main counter shaft 76 and the Karako shaft 100 have a double shaft structure, and the main counter shaft 76 and the Karako shaft 100 are rotatably supported relative to each other. Further, the Karato drive belt 103 is wound around the Karato drive pulleys 101 and 102 provided on the sub-counter shaft 104 and the Karato shaft 100, respectively, to form a Karato drive mechanism. Therefore, the rotational power from the engine 7 transmitted to the main counter shaft 76 is input to the beater shaft 82 via the power relay mechanism and the Karako drive mechanism, and the Karako 29 is driven to rotate at a constant rotation output of the engine 7.

Further, the machine casing 9b of the threshing unit 9 has the cutting support frame 36 installed on the upper surface side of the front portion of the threshing machine housing support column 34 on the upper surface side of the traveling machine body 1. A mowing bearing body 37 is attached to the right front side of the mowing support frame 36, and a forward/reverse switching case 121 described later is attached to the left front side of the mowing support frame 36. Then, a cutting input shaft 89 is rotatably supported on the front surface side of the cutting support frame 36 via the cutting bearing body 37 and the forward/reverse switching case 121 so as to be rotatable in the left-right direction of the traveling machine body 1, and the cutting support frame 36 is also provided. A left-right oriented beater shaft 82 (beater 18) is rotatably supported in the interior of the via a beater bearing body 38. Further, a handling cylinder drive case 71 is attached to the upper surface side of the mowing support frame 36, and a handling cylinder input shaft 72 is pivotally supported by the handling cylinder drive case 71.

On the other hand, it is provided with a right and left reaping input shaft 89 that drives the supply conveyor 17 in the feeder house 11. The cutting drive force transmitted from the engine 7 to one end of the main counter shaft 76 on the engine 7 side is transmitted from the other end of the main counter shaft 76 on the opposite side of the engine 7 to the forward/reverse rotation of the cutting forward/reverse rotation switching case 121. It is transmitted to the shaft 122. The reaping input shaft 89 is driven via the forward rotation bevel gear 124 or the reverse rotation bevel gear 125 of the reaping forward/reverse rotation switching case 121.

Further, a left and right handling cylinder input shaft 72 is provided on the front side of the threshing unit 9, and the driving force transmitted from the engine 7 to one end portion of the main counter shaft 76 on the engine 7 side is the one end of the handling barrel input shaft 72 on the engine 7 side. Transmitted to the department. In addition, the handling barrel input shaft 72 provided on the front side of the threshing unit 9 is arranged in the lateral direction of the traveling machine body 1, while the handling barrel 21 is pivotally supported by the handling body shaft 20 arranged in the front and rear direction of the traveling machine body 1. The front end side of the handle barrel shaft 20 is connected to the other left and right ends of the handle barrel input shaft 72 opposite to the engine 7 via a bevel gear mechanism 75. The driving force of the engine 7 is transmitted from the other left and right ends of the main counter shaft 76, which are opposite to the engine 7, to the grain selecting mechanism 10 for selecting the grains after threshing or the cutting unit 3. ..

That is, the right end of the handle barrel input shaft 72 is connected to the right end of the main counter shaft 76 near the engine 7 via the handle barrel drive pulleys 86, 87 and the handle barrel drive belt 88. A front end side of the handling barrel shaft 20 is connected to a left end portion of the handling barrel input shaft 72 extending in the left-right direction via a bevel gear mechanism 75. The power of the engine 7 is transmitted from the right end portion of the main counter shaft 76 to the front end side of the handling barrel shaft 20 via the handling barrel input shaft 72, and the handling barrel 21 is rotationally driven in one direction. On the other hand, the driving force of the engine 7 is transmitted from the left end of the main counter shaft 76 to the grain selection mechanism 10 arranged below the threshing unit 9.

Further, on the left end of the first conveyor shaft 77 of the first conveyor mechanism 30 and the left end of the second conveyor shaft 78 of the second conveyor mechanism 31, the left side of the main counter shaft 76 via the conveyor drive belt 111. The ends are connected. The left end of the second conveyor shaft 78 is connected to the left end of a crank-shaped swing drive shaft 79, which pivotally supports the rear part of the swing sorting board 26, via a swing sorting belt 112. That is, the threshing clutch 84 is controlled to be turned on/off by the operator's operation of the threshing clutch lever 47. Each part of the grain selection mechanism 10 and the handling cylinder 21 are configured to be driven by the operation of engaging the threshing clutch 84.

The fried grain conveyor 32 is driven via the first conveyor shaft 77, and the most selected grain of the most conveyor mechanism 30 is collected in the grain tank 6. In addition, the second reduction conveyor 33 is driven via the second conveyor shaft 78, and the second selection grain (second material) of the second conveyor mechanism 31 in which the straw waste is mixed is the upper surface side of the swing selection board 26. Returned to. Further, in the structure in which a spreader (not shown) for scattering straw is provided at the dust outlet 23, the spreader driving pulley (not shown) and the spreader driving belt (not shown) are provided to the left side of the main counter shaft 76 to the spreader. Connect the ends.

A cutting input shaft 89 is provided as a conveyor input shaft that pivotally supports the feed end side of the supply conveyor 17. A header drive shaft 91 is rotatably supported on the right side rear surface side of the grain header 12. The left end portion of the forward/reverse rotation transmission shaft 122 is connected to the left end portion of the beater shaft 82 via the mowing drive chain 115 and the sprockets 116 and 117, and the mowing input shaft 89 transmits forward/reverse rotation through the forward/reverse switching case 121. It is connected to the shaft 122. Also, the right end of the reaping input shaft 89 is connected to the left end of the header drive shaft 91 extending in the left-right direction via the header drive chain 118 and the sprockets 119 and 120. A scraping shaft 93 that supports the scraping auger 13 is provided. An intermediate portion of the header drive shaft 91 is connected to the right side portion of the scraping shaft 93 via a scraping drive chain 92.

Further, a reel shaft 94 that pivotally supports the take-in reel 14 is provided. The right end of the take-up shaft 93 is connected to the right end of the reel shaft 94 via an intermediate shaft 95 and reel drive chains 96 and 97. The cutting blade 15 is connected to the right end of the header drive shaft 91 via a cutting blade drive crank mechanism 98. The supply conveyor 17, the scraping auger 13, the scraping reel 14, and the cutting blade 15 are drive-controlled by the turning operation of the cutting clutch 109 to continuously cut the tip side of the uncut grass culm in the field. Is configured.

A forward rotation bevel gear 124 integrally formed with the forward and reverse rotation transmission shaft 122, a reverse rotation bevel gear 125 rotatably supported on the cutting input shaft 89, and an intermediate bevel gear 126 connecting the forward rotation bevel gear 125 to the reverse rotation bevel gear 125. , Is installed in the forward/reverse switching case 121. The intermediate bevel gear 126 is always meshed with the forward bevel gear 124 and the reverse bevel gear 125. On the other hand, a slider 127 is slidably supported on the reaping input shaft 89 by a spline engagement shaft. The forward rotation bevel gear 124 is releasably engageable with the forward rotation bevel gear 124 via the claw clutch-shaped forward rotation clutch 128, and the slider 127 is engaged with the reverse rotation bevel gear 125 via the claw clutch-shaped reverse rotation clutch 129. It is configured to be detachably engageable.

Further, a forward/reverse switching shaft 123 for slidingly operating the slider 127 is provided, a forward/reverse switching arm 130 is provided on the forward/reverse switching shaft 123, and a forward/reverse switching arm 130 is operated by operating a forward/reverse switching lever 212 (forward/reverse operating tool). To rotate the forward/reverse switching shaft 123 to bring the forward rotation bevel gear 124 or the reverse rotation bevel gear 125 into contact with or separate from the slider 127, and to rotate the forward rotation bevel gear 124 or the reverse rotation clutch 129 via the forward rotation clutch 128 or the reverse rotation clutch 129. The slider 127 is selectively locked to the bevel gear 125 for use, and the cutting input shaft 89 is connected to the forward/reverse rotation transmission shaft 122 in the forward or reverse direction.

The structure is provided with a forward/reverse switching case 121 as a forward/reverse switching mechanism for driving the supply conveyor 17 in the forward or reverse direction, and the supply conveyor 17 is connected to the beater shaft 82 via the forward/reverse switching case 121. Therefore, the supply conveyor 17 of the feeder house 11 and the like can be reversed by the reverse rotation switching operation of the forward/reverse switching case 121, and the clogged straw in the feeder house 11 or the like can be quickly removed.

The right end of the auger drive shaft 158 is connected to the output shaft 65 of the engine 7 via the tension pulley-shaped auger clutch 156 and the auger drive belt 157. The front end side of the lateral feed auger 160 at the bottom of the Glen tank 6 is connected to the left end of the auger drive shaft 158 via a bevel gear mechanism 159. The vertical feed auger 162 of the grain discharge conveyor 8 is connected to the rear end side of the horizontal feed auger 160 via the bevel gear mechanism 161, and the grain of the grain discharge conveyor 8 is connected to the upper end side of the vertical feed auger 162 via the bevel gear mechanism 163. The grain discharge auger 164 is connected. In addition, a grain discharge lever 155 for turning on and off the auger clutch 156 is provided. A grain discharging lever 155 is attached to the front of the Glen tank 6 behind the driver's seat 42 so that an operator can operate the grain discharging lever 155 from the driver's seat 42 side.

Next, a power transmission structure such as the mission case 63 will be described with reference to FIGS. 4 and 7. As shown in FIG. 4 and FIG. 7, etc., the transmission case 63 includes a pair of rectilinear pumps 64a and a rectilinear motor 64b for a straight (hydraulic main speed change) hydraulic continuously variable transmission 64, and a pair of swing pumps 70a. And a hydraulic hydraulic continuously variable transmission 70 having a swing motor 70b. The transmission input shafts 66 of the transmission case 63 are connected to the respective pump shafts 258 and 259 of the linear pump 64a and the orbiting pump 70a by gears to be driven. An engine output belt 67 is wound around a mission input pulley 69 on the mission input shaft 66. The output of the engine 7 is transmitted to the mission input pulley 69 via the engine output belt 67 to drive the linear pump 64a and the swing pump 70a.

The driving force output from the output shaft 65 of the engine 7 is transmitted to the pump shaft 258 of the linear pump 64a and the pump shaft 259 of the swing pump 70a via the engine output belt 67 and the mission input shaft 66, respectively. In the straight traveling hydraulic continuously variable transmission 64, the hydraulic oil is appropriately sent from the straight traveling pump 64a toward the straight traveling motor 64b by the power transmitted to the pump shaft 258. Similarly, in the swing hydraulic continuously variable transmission 70, the hydraulic oil is appropriately sent from the swing pump 70a toward the swing motor 70b by the power transmitted to the pump shaft 259.

A transmission charge pump 151 for supplying hydraulic oil to the hydraulic pumps 64a and 70a and the hydraulic motors 64b and 70b is attached to the pump shaft 259. The rectilinear hydraulic continuously variable transmission 64 adjusts the inclination angle of the rotary swash plate in the rectilinear pump 64a in accordance with the operation amount of the main transmission lever 44 and the steering handle 43 arranged on the steering column 41 to adjust the rectilinear motor. By changing the discharge direction and discharge amount of the hydraulic oil to 64b, the rotation direction and the rotation speed of the straight-moving motor shaft 260 protruding from the straight-moving motor 64b are arbitrarily adjusted.

Rotational power of the straight-travel motor shaft 260 is transmitted from the straight-travel transmission gear mechanism 250 to the auxiliary transmission gear mechanism 251. The sub-transmission gear mechanism 251 includes a sub-transmission low speed gear 254, a sub-transmission medium speed gear 255, and a sub-transmission high speed gear 256 that are switched by the sub-transmission shifters 252 and 253. By operating the sub-transmission lever 45 arranged on the control column 41, the output rotation speed of the straight-moving motor shaft 260 is selectively switched to a three-stage gear position of low speed, medium speed, or high speed. .. There is a neutral position (a position where the output of the auxiliary shift becomes zero) between the low speed, the medium speed, and the high speed of the auxiliary shift.

The parking brake shaft 265 (auxiliary shift output shaft) provided on the output side of the auxiliary transmission gear mechanism 251 is provided with a drum-type parking brake 266. Rotational power from the sub transmission gear mechanism 251 is transmitted to the left and right differential mechanisms 257 from the sub transmission output gear 267 fixed to the parking brake shaft 265. The left and right differential mechanisms 257 are respectively provided with planetary gear mechanisms 268. Further, a straight traveling pulse generating rotary wheel 292 is provided on the parking brake shaft 265, and a straight traveling vehicle speed sensor (not shown) detects the rotation speed of the straight traveling output (straight traveling vehicle speed=shift output of the auxiliary transmission output gear 267). doing.

Each of the left and right planetary gear mechanisms 268 is capable of rotating one sun gear 271, a plurality of planet gears 272 that mesh with the sun gear 271, a ring gear 273 that meshes with the planet gears 272, and a plurality of planet gears 272 on the same circumference. And a carrier 274 to be arranged. The carriers 274 of the left and right planetary gear mechanisms 268 are arranged to face each other at appropriate intervals on the same axis. A center gear 276 is fixed to a sun gear shaft 275 provided with the left and right sun gears 271.

The left and right ring gears 273 are concentrically arranged on the sun gear shaft 275 in a state where the inner teeth of the inner peripheral surface thereof are meshed with the plurality of planet gears 272. Further, the outer teeth of the outer peripheral surface of each of the left and right ring gears 273 are connected to the steering output shaft 285 via intermediate gears 287 and 288 for left and right turning outputs, which will be described later. Each ring gear 273 is rotatably supported by the left and right forced differential output shafts 277 that project outward in the left and right directions from the outer surface of the carrier 274. The left and right axle shafts 278 are connected to the left and right forced differential output shafts 277 via final gears 278a and 278b. Left and right drive sprockets 51 are attached to the left and right axles 278. Therefore, the rotational power transmitted from the sub-transmission gear mechanism 251 to the left and right planetary gear mechanisms 268 is transmitted from the left and right axles 278 to each drive sprocket 51 at the same rotational speed in the same direction, and the left and right crawler belts 2 in the same direction. The traveling machine body 1 is moved straight ahead (forward or backward) by being driven at the same number of revolutions.

The swing hydraulic continuously variable transmission 70 changes and adjusts the tilt angle of the rotary swash plate in the swing pump 70a in accordance with the rotation operation amount of the main transmission lever 44 and the steering handle 43 arranged in the steering column 41, By changing the discharge direction and discharge amount of the hydraulic oil to the swing motor 70b, the rotation direction and the rotation speed of the swing motor shaft 261 protruding from the swing motor 70b are arbitrarily adjusted. Further, a turning pulse generating rotary wheel 294 is provided on a steering counter shaft 280, which will be described later, and a turning rotation sensor (turning vehicle speed sensor) (not shown) rotates the turning output of the turning motor 70b (turning vehicle speed). Is configured to detect.

Further, in the mission case 63, a wet multi-plate turning brake 279 (steering brake) provided on the turning motor shaft 261 (steering input shaft) and a turning motor shaft 261 via a reduction gear 281. The steering counter shaft 280 to be connected, the steering output shaft 285 to be connected to the steering counter shaft 280 via the reduction gear 286, and the left input to be connected to the left ring gear 273 via the reverse rotation gear 284. A gear mechanism 282 and a right input gear mechanism 283 that connects the steering output shaft 285 to the right ring gear 273 are provided. The rotational power of the turning motor shaft 261 is transmitted to the steering counter shaft 280. The rotational power transmitted to the steering counter shaft 280 is transmitted to the left ring gear 273 as reverse rotational power via the left intermediate gear 287 and the reverse rotation gear 284 on the steering output shaft 285 in the left input gear mechanism 282. On the other hand, the normal rotation power is transmitted to the right ring gear 273 via the right intermediate gear 288 on the steering output shaft 285 in the right input gear mechanism 283.

When the sub-transmission gear mechanism 251 is set to the neutral position, the power transmission from the linear motor 64b to the left and right planetary gear mechanisms 268 is blocked. When the auxiliary transmission gear mechanism 251 outputs an auxiliary transmission other than neutral, power is transmitted from the linear motor 64b to the left and right planetary gear mechanisms 268 via the auxiliary transmission low speed gear 254, the auxiliary transmission medium speed gear 255, or the auxiliary transmission high speed gear 256. .. On the other hand, when the output of the swing pump 70a is in the neutral state and the swing brake 279 is in the on state, power transmission from the swing motor 70b to the left and right planetary gear mechanisms 268 is blocked. When the output of the turning pump 70a is set to a state other than neutral and the turning brake 279 is turned off, the rotational power of the turning motor 70b is transmitted to the left ring gear 273 via the left input gear mechanism 282 and the reverse rotation gear 284. On the other hand, it is transmitted to the right ring gear 273 via the right input gear mechanism 283.

As a result, when the turning motor 70b rotates in the normal direction (reverse rotation), the left ring gear 273 rotates in the reverse direction (normal rotation) and the right ring gear 273 rotates in the normal direction (reverse rotation) at the same number of rotations in opposite directions. That is, the shift output from each of the motor shafts 260 and 261 is transmitted to the drive sprocket 51 of the left and right crawler belts 2 via the auxiliary transmission gear mechanism 251 or the differential mechanism 257, respectively, and the vehicle speed of the traveling machine body 1 (traveling). The speed) and the direction of travel are determined.

That is, when the straight advance motor 64b is driven in a state where the turning motor 70b is stopped and the left and right ring gears 273 are stationary and fixed, the rotation output from the straight advance motor shaft 260 is transmitted to the left and right sun gears 271 at the same left and right rotation speeds. The left and right crawler belts 2 are driven at the same rotational speed in the same direction via the gear 272 and the carrier 274, and the traveling machine body 1 travels straight.

On the contrary, when the turning motor 70b is driven in a state where the straight-moving motor 64b is stopped and the left and right sun gears 271 are stationary and fixed, the left ring gear 273 is normally rotated (reverse rotation) by the rotational power from the turning motor shaft 261. The right ring gear 273 rotates in the reverse direction (forward rotation). As a result, one of the drive sprockets 51 of the left and right crawler belts 2 rotates forward and the other rotates backward, so that the traveling vehicle body 1 changes its direction on the spot (spin turn spin turn).

Further, by driving the left and right sun gears 271 by the straight-ahead motor 64b and driving the left and right ring gears 273 by the turning motor 70b, a speed difference between the left and right crawler belts 2 occurs, and the traveling vehicle body 1 moves forward or backward while turning the ground. Turn left or right (U-turn) with a turning radius larger than the radius. The turning radius at this time is determined according to the speed difference between the left and right crawler belts 2. The vehicle 7 turns left or right while the traveling driving force of the engine 7 is always transmitted to the left and right crawler belts 2.

Next, the working hydraulic circuit 180 and the traveling hydraulic circuit 200 in the normal combine of the present embodiment will be described with reference to FIGS. 9 to 16. As shown in FIGS. 9 to 14, the working hydraulic circuit 180 includes, as hydraulic actuators, a reaper lifting hydraulic cylinder 4 and left and right reel lifting hydraulic cylinders 27L and 27R that support the take-up reel 14 so as to move up and down. An auger lifting hydraulic cylinder 55 that supports the grain discharge auger 164 so that it can be lifted, left and right machine body lifting hydraulic cylinders 56L and 56R that lifts the traveling machine body 1, a hydraulic oil tank 57 that stores hydraulic oil, and a hydraulic oil. A hydraulic pump 59 connected to the tank 57 via an oil filter 58 and hydraulic valves 60A to 60E for switching the flow of hydraulic oil are provided. The hydraulic valves 60A to 60E are incorporated in the hydraulic valve unit 60 mounted on the traveling machine body 1.

The hydraulic pump 59 is hydraulically connected to the hydraulic cylinder 4 for raising and lowering the mowing through the hydraulic valve 60A for raising and lowering the mowing. The operation of tilting a mowing posture lever (not shown) in the driving operation unit (driver's cab) 5 in the front-rear direction activates the mowing lifting hydraulic cylinder 4 so that the operator can move the mowing unit 3 to an arbitrary height (for example, mowing work height). Or it is configured to be moved up and down to a non-working height, etc.). On the other hand, the working hydraulic pump 59 is hydraulically connected to the reel lifting hydraulic cylinders 27L and 27R via the reel lifting hydraulic valve 60B. The reel lifting hydraulic cylinders 27L and 27R are operated by the operation of tilting the mowing posture lever (not shown) in the left and right directions, and the operator moves the take-up reel 14 up and down to an arbitrary height, and the uncut grain in the field is cut. It is configured to reap culms.

The working hydraulic pump 59 is hydraulically connected to the auger lifting hydraulic cylinder 55 via the auger lifting hydraulic valve 60C. By the operation of tilting the grain discharging lever 155 in the driving operation unit (driver's cab) 5 in the front-rear direction, the hydraulic cylinder 55 for raising and lowering the auger is operated, and the operator throws the grain from the grain discharging auger 164 in the grain discharging conveyor 8. Raise and lower to an arbitrary height. It should be noted that the electric motor 165 horizontally rotates the vertical feed auger 162 and the bevel gear mechanism 163 together with the grain discharge auger 164 to horizontally move the paddy throwing port. That is, the paddy throwing port is located above the truck bed or container, and the grains in the grain tank 6 are discharged into the truck bed or container.

The hydraulic oil tank 57 and the working hydraulic pump 59 are hydraulically connected to the left-body raising/lowering hydraulic cylinder 56L via the left-body raising/lowering hydraulic valve 60D. On the other hand, the hydraulic oil tank 57 and the work hydraulic pump 59 are hydraulically connected to the right machine body lifting hydraulic cylinder 56R via the right machine body lifting hydraulic valve 60E. The left and right machine body lifting hydraulic cylinders 56L and 56R are operated independently of each other, so that the left and right machine bodies 1 are independently lifted and lowered.

Therefore, when the hydraulic cylinders 56L and 56R for raising and lowering the vehicle body on both the left and right sides are simultaneously actuated to lower the left and right track frames 50, 50 relative to the traveling vehicle body 1 at the same time, the traveling vehicle body 1 will have the crawler tracks 2 and 2 grounding portions on both the left and right sides. As a result, the relative height (vehicle height) of the traveling machine body 1 with respect to the crawler tracks 2 and 2 grounding portions becomes higher as the vehicle separates (raises) upward. On the contrary, when the left and right track frames 50, 50 are simultaneously raised with respect to the traveling vehicle body 1, the traveling vehicle body 1 approaches (lowers) the crawler belts 2, 2 on the left and right sides, and the crawler belt 2 of the traveling vehicle body 1 is approached. , 2 Relative height (vehicle height) to the ground contact part is low.

Then, the left machine body lifting hydraulic cylinder 56L is operated to lower the left track frame 50 with respect to the traveling machine body 1, or the right machine body lifting hydraulic cylinder 56R is operated to raise the right truck frame 50 with respect to the traveling machine body 1. And (or even if both operations are executed at the same time), the traveling machine body 1 tilts downward to the right. On the contrary, the right machine body lifting hydraulic cylinder 56R is operated to lower the right track frame 50 with respect to the traveling machine body 1, or the left machine body lifting hydraulic cylinder 56L is operated to move the right truck frame 50 to the traveling machine body 1. When it is raised (or both operations are executed at the same time), the traveling machine body 1 tilts downward to the left.

The hydraulic oil tank 57, the hydraulic pump 59, and the hydraulic valve unit 60 are mounted on the traveling machine body 1 and are connected to each other via hydraulic pipes 181 to 183. On the traveling vehicle body 1, the hydraulic oil tank 57 is installed on the front left side, while the hydraulic pump 59 is fixed to the front surface of the engine 7 mounted on the front right side, and the hydraulic oil tank 58 and the hydraulic filter 58 installed inside the hydraulic oil tank 57 are installed. The pump 59 is connected by a hydraulic pipe 181. Further, on the traveling machine body 1, a hydraulic valve unit 60 is arranged at a position behind the engine 7, and the discharge side of the hydraulic pump 59 is connected to the hydraulic valve unit 60 via a hydraulic pipe 182. Further, the hydraulic valve unit 60 is connected to the hydraulic oil tank 57 via a hydraulic pipe 183 which serves as a hydraulic oil return pipe.

The hydraulic oil tank 57 is installed on the traveling machine body 1 in a space position surrounded by the feeder house 11 and the beater 18, and the engine 7 and the hydraulic oil tank 57 are arranged side by side in front of the traveling machine body 1. There is. That is, the hydraulic oil tank 57 is arranged in the space surrounded by the feeder house 11 and the machine casing of the threshing unit 9, and it is possible to prevent dust from the cutting unit 3 from being accumulated in the hydraulic oil tank 57. It is also possible to prevent the operating oil from being contaminated due to the intrusion of dust from the oil supply port 184 or the like. Further, since the cooling air from the engine 7 flows into the installation space of the hydraulic oil tank 57, the hydraulic oil temperature can be suppressed from increasing without providing an oil cooler on the working hydraulic circuit 180, and each hydraulic member can be controlled. It can be driven properly.

The hydraulic oil tank 57 has an oil supply port 184 protruding toward the left side (outside of the machine) on the left side surface (side surface on the outside of the machine), and has an oil filter 58 that can be inserted and removed from the left side installed therein. Therefore, by removing the threshing cover 185 provided on the left side (the outer side of the machine) of the threshing unit 9, the oil filler port 184 and the oil filter 58 can be easily accessed. Therefore, the work of refueling the hydraulic oil tank 57 and the work of replacing the oil filter 58 are facilitated, and the maintainability of the working hydraulic circuit 180 can be improved.

Further, the hydraulic pipes 181 and 183 connected to the hydraulic oil tank 57 are provided so as to extend to the left and right in front of the hydraulic oil tank 57 and the engine 7, and the hydraulic pipe 182 and the hydraulic pump 59 arranged in front of the engine 7 and oil. It communicates with the filter 58. That is, the hydraulic pipes 181 and 183 extend around the front of the engine 7 toward the hydraulic oil tank 57 along the output shaft 65 of the engine 7. Further, the hydraulic pipes 182 and 183 extend rearward below the cooling fan provided on the right side of the engine 7 and are connected to the hydraulic valve unit 60. Therefore, the hydraulic pipes 181 to 183 are arranged such that the pipe length is shortened at a position where they are less likely to be affected by the radiant heat from the engine 7, and the temperature of the hydraulic oil flowing through the hydraulic pipes is suppressed from increasing. it can.

As shown in FIGS. 14 to 16, the traveling hydraulic circuit 200 includes a straight-line pump 64a, a straight-line motor 64b, a swing pump 70a, a swing motor 70b, a transmission charge pump 151, an oil filter 152, and an oil cooler 153. .. The straight traveling pump 64a and the straight traveling motor 64b in the straight traveling hydraulic continuously variable transmission 64 are connected in a closed loop by a straight traveling closed oil passage 201. On the other hand, the swing pump 70 a and the swing motor 70 b in the swing hydraulic continuously variable transmission 70 are connected in a closed loop by a swing oil passage 202. The straight pump 64a and the swing pump 70a are driven by the rotational power of the engine 7, and the swash plate angles of the straight pump 64a and the swing pump 70a are controlled, whereby the discharge direction and discharge of the hydraulic oil to the straight motor 64b and the swing motor 70b are controlled. The amount is changed, and the rectilinear motor 64b and the swing motor 70b are operated in the forward and reverse directions.

The traveling hydraulic circuit 200 is provided with a rectilinear valve 203 that is switched and operated in response to a manual operation of the main shift lever 44, and a rectilinear cylinder 204 connected to the transmission charge pump 151 via the rectilinear valve 203. When the rectilinear valve 203 is switched and operated, the rectilinear cylinder 204 is actuated to change the swash plate angle of the rectilinear pump 64a, and the rotation speed of the rectilinear motor shaft 260 of the rectilinear motor 64b is continuously changed or reversed. A straight shift operation is executed.

The traveling system hydraulic circuit 200 includes a swing valve 206 that is switched and operated in response to a manual operation of the steering handle 43, and a swing cylinder 207 connected to the transmission charge pump 151 via the swing valve 206. When the revolving valve 206 is switched and operated, the revolving cylinder 207 is operated to change the swash plate angle of the revolving pump 70a, and the number of revolutions of the revolving motor shaft 261 of the revolving motor 70b is continuously changed or reversed. The left-right turning operation is executed, and the traveling machine body 1 changes the traveling direction to the left or right to change the direction or correct the course in the field headland.

The suction side of the transmission charge pump 151 is connected to a strainer 217 in the mission case 63 via a hydraulic pipe 208. A charge introducing oil passage 218 is connected to the discharge side of the transmission charge pump 151 via a hydraulic pipe 209, and an oil filter 152 is installed in the middle of the hydraulic pipe 209. A charge branch oil passage 219 connected to both the closed oil passages 201 and 202 is connected to the downstream side of the charge introduction oil passage 218. Therefore, while the engine 7 is being driven, the hydraulic oil from the transmission charge pump 151 is constantly replenished in both oil closed paths 201 and 202.

Further, the charge branch oil passage 219 is connected to the straight traveling cylinder 204 via the straight traveling valve 203, and is connected to the swing cylinder 207 via the swing valve 206. Further, the charge branch oil passage 219 is connected to the mission case 63 via an excess relief valve 220 and a hydraulic pipe 210, and an oil cooler 153 is installed in the middle of the hydraulic pipe 210. Therefore, the excess amount of hydraulic oil from the transmission charge pump 151 is cooled by the oil cooler 153 when returning to the inside of the transmission case 63 via the excess relief valve 220.

Next, the engine room 146 in which the engine 7 is installed will be described with reference to FIGS. 8, 13 and 14. As shown in FIG. 8, FIG. 13 and FIG. 14, a pair of left and right engine room support columns 147 are erected on the rear side of the cab 5 on the upper surface of the traveling machine body 1, and a back plate 148 is provided between the left and right engine room support columns 147. It is stretched to cover the rear of the engine room 146 below the driver's seat 42. Further, a box-shaped wind tunnel case 170 is erected on a right engine room pillar 147 provided at the right end portion of the cab 5 of the traveling machine body 1 via an opening/closing fulcrum shaft 171. A dust-removing net is stretched over the outer side opening on the right side of the wind tunnel case 170, and the presence of the dust-removing net prevents the intrusion of straw debris into the inside of the wind tunnel case 170 and further into the engine room 146.

A radiator 154 for water cooling is erected inside the wind tunnel case 170 on the upper surface side of the traveling machine body 1, and the radiator 154 faces the cooling fan 149 of the engine 7. A shroud 150 that covers the entire ventilation range of the radiator 154 is installed, and a cooling fan 149 is arranged in the opening formed in the shroud 150. An oil cooler 153 is installed inside the wind tunnel case 170. By the rotation of the cooling fan 149, the outside air (cooling air) is taken into the wind tunnel case 170 from the outer side opening on the right side of the wind tunnel case 170, and the dust-free cooling air is supplied from the inner side opening on the left side of the wind tunnel case 170 into the engine room 146. Send to. As a result, the oil cooler 153, the radiator 154, the engine 7, and the like are cooled by the cooling air that flows into the engine room 146.

Next, the configuration of the periphery of the mowing support frame 36 that is a part of the machine casing 9b of the threshing unit 9 will be described with reference to FIGS. 5, 6, 8 and 11 to 14. As shown in FIG. 5, FIG. 6, FIG. 8, and FIG. 11 to FIG. The left and right mowing support columns (front column frames) 36a, and the upper and lower mowing supporting frame beam frames 36b and 36c that connect the left and right threshing machine casing columns 34 and the left and right mowing supporting columns 36a in the front-rear direction Have. The beam frames 36b and 36c for the reaping support frame are installed on the upper ends and the middle portions of the stanchion support struts 36a and the threshing machine casing struts 34 arranged in the front and rear.

Both ends of the left and right beater bearing bodies 38 are connected to the middle portions of the beam frames 36b and 36c for the upper and lower cutting support frames provided on the left and right, and the beater 18 is pivotally supported in the cutting support frame body 36 by the left and right beater bearing bodies 38. To be done. The cutting support frame 36 is provided with side plates 186 that cover the left and right sides of the beater 18, a top plate 187 that covers the upper part of the beater 18, a front plate 188 that covers the front surface of the beater 18, and a bottom plate 189 that covers the lower part of the beater 18. That is, the reaping support frame 36 has a closed space above the lower beam frame 36c that connects the rear end of the feeder house 11 and the handling port 9a. Then, a beater 18 that smoothly guides the grain rod from the supply conveyor 17 to the handling port 9a is installed in the closed space.

The side plate 186 is installed so as to seal the region surrounded by the columns 34, 36a and the beam frames 36b, 36c, and the beater shaft 82 pivotally supported by the beater bearing body 38 arranged outside the side plate 186. Has a hole for passing through. The top plate 187 is installed on the left and right beam frames 36b, and the handling cylinder drive case 71 is installed on the upper surface thereof. The front plate 188 is connected to the front edge and the upper edge of the top plate 187 and extends downward toward the upper part of the feeder house 11. The front edge of the bottom plate 189 is connected to the rear edge of the bottom plate 190 of the feeder house 11, and the rear edge of the bottom plate 189 is connected to the front edge of the bottom face of the handling mouth 9a in front of the handling cylinder 21. It acts as a guide plate for the grain rod from the handle to the handle 9a.

A hydraulic oil tank 57 is installed in a space below the beater 18 installation space of the mowing support frame 36, and an upper part of the hydraulic oil tank 57 is covered with a bottom plate 189. The front of the hydraulic oil tank 57 is covered with a front cover plate 191 connected to the bottom plate 189. A blast fan-shaped Kara 29 is provided behind the hydraulic oil tank 57, and the outer periphery of the Kara 29 is covered with a Kara cover plate 192. Therefore, in the cutting support frame 36, the hydraulic oil tank 57 is installed in the space surrounded by the bottom plate 189, the front cover plate 191, and the Karako cover plate 192.

The working oil tank 57 installation space formed by the bottom plate 189, the front cover plate 191, and the Kara no Mamoru cover plate 192 constitutes a passage having left and right openings, and communicates with the engine room 146 on the right side. Further, the machine casing 9b of the threshing section 9 includes left and right threshing side plates 193, and the right threshing side plate 193 front edge is fixed to the right threshing machine casing support post 34 located in front of the engine room support post 147. .. Therefore, a part of the cooling air taken from the outside air from the cooling fan 149 passes through the engine room 146 and flows into the installation space for the hydraulic oil tank 57 in the cutting support frame 36 to cool the hydraulic oil tank 57.

In addition, a part of the cooling air passing through the engine room 146 flows into the air passage formed by the Karamoru cover plate 192 behind the hydraulic oil tank 57 installation space by the rotation of the Karamotsu 29. As a result, an air flow that flows in the front-rear direction in the space between the engine room 146 and the threshing unit 9 is formed. Therefore, the outside air also flows in from the front of the traveling machine body 1 by being guided by the air flow in the front-rear direction. Outside air flows into the working oil tank 57 installation space from the front of the traveling machine body 1 and cools the working oil tank 57 together with a part of the cooling air from the engine room 146. That is, since the exhaust air from the engine 7 positively flows toward the Kara 29 side, outside air flows into the installation space of the hydraulic oil tank 57 together with a part of the cooling air of the engine 7, thereby improving the cooling effect of the hydraulic oil tank 57. Increase.

As described above, the configuration in which the cooling air from the engine room 146 passes through the hydraulic oil tank 57 prevents the temperature of the working oil circulating in the working hydraulic circuit 180 including the hydraulic oil tank 57 from rising. it can. Therefore, it is not necessary to provide an oil cooler in the work system hydraulic circuit 180, and the work system hydraulic circuit 180 and the traveling system hydraulic circuit 200 are provided as separate systems, so that the oil cooler 153 is provided only in the traveling system hydraulic circuit 200. It can be configured to be provided. As a result, the capacity of the oil cooler 153 can be reduced, and the cooling efficiency of the radiator 154 and the engine 7 located downstream of the oil cooler 153 in the cooling air flow can be improved.

Further, the sub-counter shaft 104 that receives the driving force from the engine 7 is pivotally supported by the threshing machine casing support (rear support frame) 34, and the beater bearing body 38 connected to the beam frames 36b and 36c for the upper and lower cutting support frames is used to operate the beater 18 The beater shaft 82 of is pivotally supported. A mowing input shaft 89 pivotally supported at a position in front of the mowing support mast (front mast frame) 36a penetrates the feeder house 11. The first power transmission mechanism (the beater drive mechanism by the drive pulleys 107 and 108 and the cutting drive belt 114) that transmits the rotation power of the sub-counter shaft 104 to the beater shaft 82, and the rotation power of the beater shaft 82 to the cutting input shaft 89. The second power transmission mechanism (the cutting drive chain 115 and the cutting drive mechanism by the sprockets 116 and 117). The oil supply port 184 and the oil filter 58 of the hydraulic oil tank 57 are arranged in a region surrounded by the first and second power transmission mechanisms and the front cutting support column 36a. As a result, the work of supplying oil to the hydraulic oil tank 57 and the work of exchanging the oil filter 58 can be performed without removing the transmission material (chain or belt) in the first and second power transmission mechanisms. The maintainability can be improved.

Further, the threshing unit 9 pivotally supports the Karako 29 on the rear side of the threshing machine casing support (rear support frame) 34, and the main counter shaft 76 rotatable relative to the Karasu shaft 100 of the Karasu 29 is the Karasu shaft 100. Penetrates inside. Then, the main counter shaft 76 receives the power from the engine 7 and transmits the power to the sub counter shaft 104, and the rotational power of the sub counter shaft 104 is branched and transmitted to each of the Kara shaft 100 and the beater shaft 82. The cutting system 3, the grain selection mechanism 10, and the drive system for driving the Kara 29 are concentratedly installed on the left side (outside of the machine) of the threshing unit 9 so that the right side (inside of the machine) of the threshing unit 9 is installed. The front can be opened. Therefore, the right side of the hydraulic oil tank 57 installation space on the lower front side of the threshing unit 9 can be opened, and a large amount of cooling air can be guided to the hydraulic oil tank 57 installation space.

DESCRIPTION OF SYMBOLS 1 Traveling machine 3 Mowing section 5 Driver's cab 7 Engine 9 Threshing section 9a Handling mouth 9b Machine housing 11 Feeder house 17 Supply conveyor 18 Beater 21 Handling barrel 29 Kara mine 34 Threshing machine housing support 35 Cutting support frame 36a Cutting support frame support 36b Beam frame for mowing support frame 36c Beam frame for mowing support frame 37 Mowing bearing body 38 Beater bearing body 57 Hydraulic oil tank 58 Oil filter 59 Hydraulic pump 63 Mission case 76 Kara shaft (constant rotation shaft)
82 beater shaft (front rotor shaft)
89 Mowing input shaft 184 Refueling port 185 Threshing cover 186 Side plate 187 Top plate 188 Front plate 189 Bottom plate 190 Bottom plate (feeder house)
191 Front cover plate 192 Kara Minato cover plate 193 Threshing side plate

Claims (4)

A threshing unit having a handling barrel, a traveling machine body equipped with an engine and a mission case, a mowing unit is provided in front of the threshing unit, and the mowing grain culm is conveyed from the mowing unit through a feeder house. In the combine that is put into the threshing section by the beater provided on the terminal side of the feeder house,
A hydraulic oil tank for storing hydraulic oil is installed in a space position on the traveling machine body and surrounded by the feeder house and the beater, and the engine and at least a part of the hydraulic oil tank are of the traveling machine body. Arranged side by side in front of the traveling aircraft so as to overlap in a side view ,
The threshing section pivotally supports Kara-miso, and a second counter shaft capable of relative rotation with respect to the Kara-mitsu axis of the Kara-mino penetrates through the Kara-mitsu-axis.
The second counter shaft receives power from the engine and transmits the power to the first counter shaft, and the rotational power of the first counter shaft is branched and transmitted to each of the Karako shaft and the beater shaft of the beater. combine, characterized in that that. The combiner according to claim 1, wherein the hydraulic oil tank has an oil supply port projecting toward the outside of the machine on a side surface of the outside of the machine, and an oil filter that can be inserted and removed from the outside of the machine is installed therein. A hydraulic pipe connected to the hydraulic oil tank is provided so as to extend left and right in front of the hydraulic oil tank and the engine, and a part of the hydraulic pipe is disposed in front of the hydraulic pump and the oil filter. 3. The combine according to claim 2, wherein the combine is communicated with each other. The machine casing includes front and rear pillar frames that are erected from the traveling body before and after the beater, and upper and lower beam frames that bridge the upper and middle portions of the front and rear pillar frames, respectively.
Said first counter shaft for receiving a driving force from the engine is rotatably supported on the rear post frame, the beater shaft by beater bearing body which is connected to the upper and lower beam frame is rotatably supported, at a forward position than the front post frame The axially supported cutting input shaft penetrates the feeder house,
A first power transmission mechanism for transmitting the rotational power of the first counter shaft to the beater shaft; and a second power transmission mechanism for transmitting the rotational power of the beater shaft to the reaping input shaft,
The oil supply port and the oil filter of the hydraulic oil tank are arranged in a region surrounded by the first and second power transmission mechanisms and the column frame in front. Combine.

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