CN115443802A - Combine harvester - Google Patents

Abstract

The combine harvester of the invention comprises: a threshing unit (9) provided with a threshing cylinder (21); and a traveling machine body (1) on which an engine (7) and a transmission (63) are mounted, wherein a harvesting unit (3) is provided in front of the threshing unit (9), and the harvesting stalks conveyed from the harvesting unit (3) through the supply chamber (11) are fed to the threshing unit (9) by means of a drum (18) provided on the end side of the supply chamber (11). A working oil tank (57) for storing working oil is provided on the traveling machine body (1) and at a spatial position surrounded by the supply chamber (11) and the drum (18), and the engine (7) and the working oil tank (57) are arranged in the left-right direction in front of the traveling machine body (1).

Description

combine harvester

This application is a divisional application of an invention patent application with the application number 201780024287.3 (international application number PCT/JP2017/022380), the application date is June 16, 2017, and the invention name is "Combine Harvester".

technical field

This invention relates to the combine harvester equipped with the reaping part which reaps the uncut fringe stalk of a field, and the threshing part which threshes the grain which reaped the fringe stem.

Background technique

Conventionally, there is a technique in which, in an ordinary combine harvester provided with a feeding chamber for conveying the ear stalks harvested by the harvesting unit to the threshing cylinder, the ear stalks are fed between the end of the feeding chamber and the inlet of the threshing cylinder. The drum is installed in the reaping section, thereby improving the take-in property of the reaped fringe stalks toward the threshing cylinder (see Patent Document 1). In addition, it has been proposed that, in a self-detaching combine harvester equipped with a supply chain for conveying the stalks harvested by the harvesting unit to the threshing barrel, the working oil supplied to the continuously variable transmission for driving is stored in the working oil tank. (Refer to Patent Documents 2 and 3). Moreover, there exists a technique which drives a right-and-left traveling part by providing a hydraulic pump and a hydraulic motor in an ordinary type combine (refer patent document 4).

patent documents

Patent Document 1: Japanese Patent Laid-Open No. 2000-037126

Patent Document 2: Japanese Patent Laid-Open No. 2004-058824

Patent Document 3: Japanese Patent Laid-Open No. 2015-084709

Patent Document 4: Japanese Patent Laid-Open No. 2010-239980

Contents of the invention

With the prior art shown in Patent Documents 1, 2, and 4, there is a certain distance between the engine and the working oil tank, and the cooling wind toward the engine is not supplied to the working oil tank. The cooling effect is not exerted. In addition, in the prior art disclosed in Patent Document 3, although the cooling air from the engine is configured to flow toward the hydraulic oil tank, a sufficient cooling effect cannot be obtained, and the configuration requires an oil cooler for cooling.

Therefore, this application invention intends to provide the combine harvester which studied these present conditions and implemented improvement.

In order to achieve the above object, the combine harvester of the invention of the present application is equipped with: a threshing part, the threshing part is equipped with a threshing cylinder; The harvesting part feeds the harvested ear stalks conveyed from the harvesting part through the feeding chamber to the threshing part by means of a roller provided at the end side of the feeding chamber, and the combine harvester is characterized in that The working oil tank for storing the working oil is arranged on the traveling body and in the space surrounded by the feeding chamber and the drum, the engine and the working oil tank are arranged in front of the traveling body Arranged in a left-right manner.

In the above-mentioned combine harvester, the hydraulic oil tank may have an oil supply port protruding toward the outside of the harvester on the side outside the harvester, and may incorporate an oil filter that can be inserted and removed from the outside of the harvester.

In the above-mentioned combine harvester, the hydraulic piping connected to the hydraulic oil tank may be arranged so as to extend left and right in front of the hydraulic oil tank and the engine, and a part of the hydraulic piping may be disposed on the hydraulic piping. The hydraulic pump at the front of the engine communicates with the oil filter.

In the above-mentioned combine harvester, the machine housing may include: front and rear pillar frames erected from the traveling body at the front and rear of the drum; and upper and lower beam frames erected respectively. At the upper end and the middle part of the front and rear pillar frames, the first counter-rotating shaft receiving the driving force from the engine is pivotally supported by the rear pillar frame, and the roller bearing body connected to the upper and lower beam frames is used to The drum shaft of the drum is shaft-supported, and the reaping input shaft, which is shaft-supported at a position further forward than the front pillar frame, penetrates the feeding chamber, and is provided with a first power transmission mechanism, the second a power transmission mechanism that transmits the rotational power of the first counter shaft to the drum shaft; and a second power transmission mechanism that transmits the rotational power of the drum shaft to the harvesting input shaft In other words, the oil supply port and the oil filter of the operating oil tank are arranged in an area surrounded by the first power transmission mechanism and the second power transmission mechanism and the front pillar frame.

In the above-mentioned combine harvester, the threshing unit may be configured to support the grain lifter on the rear side of the rear pillar frame in a shaft-supported manner, so that the grain lifter shaft of the valley lifter can The second counter-rotating shaft that performs relative rotation penetrates the shaft of the grain lifter, the second counter-rotating shaft receives power from the engine and transmits power to the first counter-rotating shaft, and the The rotational power of the first counter-rotating shaft is split and transmitted to the grain lifter shaft and the drum shaft respectively.

Invention effect

According to the invention of the present application, the operating oil tank is arranged in the space surrounded by the feed chamber and the casing of the threshing section, so that dust from the reaping section can be suppressed from accumulating in the operating oil tank, and the operating oil can also be prevented from being leaked from the oil supply port, etc. Invasive dust pollution. In addition, the cooling air from the engine flows into the installation space of the hydraulic oil tank, thereby suppressing an increase in the temperature of the hydraulic oil even without installing an oil cooler on the hydraulic circuit, and appropriately driving each hydraulic component.

According to the invention of the present application, the oil supply port and the oil filter are provided on the harvester outer side of the operating oil tank, therefore, by removing the threshing cover provided on the harvester outer side of the threshing section, the oil supply port and the oil filter can be easily installed. The filter operates. Therefore, the work of supplying oil to the hydraulic oil tank and the work of replacing the oil filter are facilitated, and the maintainability of the hydraulic circuit can be improved.

According to the invention of the present application, the hydraulic piping bypasses the front of the engine, extends toward the hydraulic oil tank, and extends along the output shaft of the engine. Therefore, the hydraulic piping is arranged so that the length of the piping is hardly affected by the radiant heat from the engine. The shortened position can suppress the temperature rise of the working oil flowing in the hydraulic piping.

According to the invention of the present application, the oil supply port and the oil filter of the working oil tank are arranged in the area surrounded by the first and second power transmission mechanisms and the front pillar frame. (Chain or belt) can be detached to carry out the operation of oil supply to the working oil tank and the replacement of the oil filter.

According to the present invention, the drive system for driving the reaping unit, the grain lifter, etc. is collectively installed outside the harvester of the threshing unit, so that the inside front of the harvester of the threshing unit can be opened. Therefore, the hydraulic oil tank installation space on the lower side in front of the threshing unit is opened toward the inside of the harvester, and a large amount of cooling air can be guided to the hydraulic oil tank installation space.

Description of drawings

Fig. 1 is a left side view showing a combine harvester according to a first embodiment of the present invention.

Fig. 2 is a right side view of the above-mentioned combine harvester.

Fig. 3 is a plan view of the above-mentioned combine harvester.

Fig. 4 is a drive system diagram of the combine harvester.

Fig. 5 is a perspective view of the combine seen obliquely from the front.

Fig. 6 is a partial top sectional view of a threshing unit.

Figure 7 is a drive system diagram of the gearbox.

It is a front view which shows the structure of an engine room and a threshing part.

Fig. 9 is a hydraulic circuit diagram showing the configuration of the working system hydraulic circuit.

Fig. 10 is a perspective view showing the structure of the working system hydraulic circuit.

It is a perspective view of the threshing part seen from obliquely front.

Fig. 12 is an enlarged left view of a threshing unit.

Fig. 13 is a plan cross-sectional view showing the structure of an engine room and a threshing unit.

Fig. 14 is a front view showing an arrangement structure of hydraulic circuit components.

Fig. 15 is a hydraulic circuit diagram showing the configuration of the travel system hydraulic circuit.

Fig. 16 is a plan view showing a piping structure of a hydraulic circuit.

detailed description

Hereinafter, based on drawing (FIGS. 1-10) applied to the common type combine, embodiment which actualized this invention is demonstrated. Fig. 1 is a left view of the combine, Fig. 2 is a right view of the above-mentioned combine, and Fig. 3 is a top view of the above-mentioned combine. First, the schematic structure of a combine is demonstrated with reference to FIGS. 1-3. In addition, in the following description, the left side when facing the advancing direction of the traveling body 1 is simply called the left side, and similarly, the right side when facing the advancing direction is simply called the right side.

As shown in FIGS. 1-3, the ordinary type combine harvester of embodiment is equipped with the traveling body 1 supported by the right and left pair of crawlers 2 made of rubber crawlers as a running part. Using a single-acting hydraulic cylinder 4 for lifting, the harvesting part 3 that takes in uncut ear stalks such as rice (or wheat, soybeans, or corn) while harvesting can be mounted on the traveling machine in a manner that can be adjusted by lifting. The front part of the body 1.

On the left side of the traveling body 1 , a threshing unit 9 for threshing the harvested ear stalks supplied from the harvesting unit 3 is mounted. The lower part of the threshing part 9 is arrange|positioned the grain screening mechanism 10 for swing screening and wind force screening. On the front right side of the traveling body 1, a driver's cab 5 on which an operator boards is mounted. An engine 7 serving as a power source is disposed on the cab 5 (below the driver's seat 42 ). Behind the driver's platform 5 (on the right side of the traveling body 1) are arranged: a grain tank 6, which takes out grains from the threshing unit 9; and a grain discharge conveyor 8, which directs the grains in the grain tank 6 toward The truck box (or container, etc.) is discharged. It is comprised so that the grain in the grain tank 6 may be output by the grain discharge conveyor 8 by inclining the grain discharge conveyor 8 to the harvester outer side.

The reaping part 3 is equipped with: a feeding chamber 11, which communicates with the threshing port 9a at the front part of the threshing part 9; 11 front-end connections. A raking auger 13 (flat auger) is pivotally supported in the grain header 12 so as to be rotatable. Above the front portion of the raking auger 13, the raking and pulling grain wheel 14 with the arm tooth beam is configured. A clipper-shaped cutting blade 15 is arranged on the front portion of the grain header 12 . The left and right sides of the grain harvesting platform 12 front are protrudingly provided with left and right dividing grain bodies 16 . In addition, a supply conveyor 17 is provided in the supply chamber 11 . The drum 18 (front rotator) for harvested fringe stalk feeding is installed in the conveyance end (threshing port 9a) of the supply conveyor 17. As shown in FIG. In addition, the lower surface portion of the feed chamber 11 and the front end of the traveling body 1 are connected by the hydraulic cylinder 4 for lifting, and the hydraulic cylinder 4 for lifting is used to make the reaping part 3 be reaped by the reaping input shaft 89 (supplied later) Material chamber conveyor shaft) is used as the lifting fulcrum to move up and down.

According to the above-mentioned structure, the ear side of the uncut ear stalk between the left and right grain dividing bodies 16 is raked up by the rake puller 14, and the root side of the uncut ear stalk is cut by the cutting knife 15. Picking, by the rotation driving of the raking auger 13, the harvested ear stalks are collected near the entrance of the feed chamber 11 near the center in the left and right width direction of the grain harvesting platform 12 . All the harvested ear stems of the grain header 12 are conveyed by the supply conveyor 17, and these harvested ear stems are fed to the threshing port 9a of the threshing part 9 by the drum 18. In addition, a horizontal control hydraulic cylinder (not shown) that rotates the grain harvesting head 12 around a horizontal control fulcrum shaft may be provided, and the inclination of the grain harvesting head 12 in the left-right direction may be adjusted by the horizontal control hydraulic cylinder. , so that the grain harvesting platform 12, the cutting knife 15 and the raking and pulling reel 14 are supported horizontally with respect to the field ground.

Moreover, as shown in FIG.1, FIG.3, the threshing cylinder 21 is installed in the threshing chamber of the threshing part 9 so that rotation is possible. The threshing cylinder 21 is pivotally supported by the threshing cylinder shaft 20 (refer FIG. 4) extended in the front-back direction of the traveling body 1. As shown in FIG. Under the threshing cylinder 21, the tension frame is provided with a receiving net 24 that allows the grain to leak downward. Moreover, the helical helical-blade-shaped intake blade 25 is protrudingly provided in the outer peripheral surface of the front part of the barrel 21 so that it may go radially outward.

According to the above structure, the harvested fringe stalk fed by the drum 18 from the threshing port 9a is conveyed toward the rear of the traveling body 1 by the rotation of the threshing cylinder 21, and kneading is performed between the threshing cylinder 21 and the receiving net 24, etc. , Threshing. Thresholds such as grains smaller than the mesh of the receiving net 24 leak downward from the receiving net 24 . Through the conveying action of the threshing cylinder 21 , the stalk chips and the like that do not leak downward from the receiving net 24 are discharged to the field from the dust outlet 23 at the rear of the threshing unit 9 .

Moreover, several dust delivery valves (illustration omitted) which adjust the conveyance speed of the threshed material in a threshing chamber are pivotally attached to the upper side of the threshing cylinder 21 so that rotation is possible. The conveying speed (residence time) of the threshed matter in the threshing chamber can be adjusted according to the species and properties of the harvested ear stalks and by adjusting the angle of the dust conveying valve. On the other hand, as the grain screening mechanism 10 arranged below the threshing unit 9, a swing screening pan 26 for specific gravity screening is provided. .

Moreover, as the grain sorting mechanism 10, the blower fan shape wind blower 29 etc. which supply the swing sorting pan 26 with sorting wind are provided. For the threshing that utilizes the threshing cylinder 21 and leaks downward from the receiving net 24, the grains (fine grains, etc.) first-class product), a mixture of grains and straw (second-class products such as grains with branches), straw chips, etc., and take them out.

The lower side of the swing sorting pan 26 is equipped with the first-class conveyance mechanism 30 and the second-class conveyance mechanism 31 as the grain sorting mechanism 10 . For the grain (first-class product) that falls from the swinging screening dish 26 by the screening of the swaying screening dish 26 and the blower fan-shaped grain lifter 29, utilize the first-class product conveying mechanism 30 and the grain raising conveyor 32 to convey It is collected into the grain bin 6 . For the mixture (second-class product) of grain and stalk, it is returned to the screening starting end side of the swinging screening disc 26 by means of the second-ranking product conveying mechanism 31 and the second-ranking product reduction conveyor 33 etc. to re-screen. It is configured to discharge straw chips and the like to the field from the dust discharge port 23 at the rear of the traveling body 1 .

In addition, as shown in FIGS. 1 to 3 , a control column 41 and a driver's seat 42 on which an operator sits are disposed on the cab 5 . The control column 41 is provided with: an accelerator lever 40, which adjusts the rotational speed of the engine 7; a circular steering wheel 43, which is operated by the operator to change the traveling route of the traveling body 1; a main shift lever 44 and the auxiliary transmission lever 45, they switch the moving speed of the traveling body 1; the reaping clutch lever 46, which drives or stops the reaping part 3; and the threshing clutch lever 47, which drives or stops the threshing part 9; stop operation. Moreover, it is comprised so that the roof body 49 for sunshades may be attached to the front upper surface side of the grain tank 6 via the roof support 48, and the upper side of the cab 5 shall be covered by the roof bodies 49 for sunshades.

As shown in FIGS. 1 and 2 , left and right crawler frames 50 are arranged on the lower surface side of the traveling body 1 . The crawler frame 50 is provided with: a drive sprocket 51, which transmits the power of the engine 7 to the crawler belt 2; a tension roller 52, which maintains the tensioned state of the crawler belt 2; grounded; and intermediate rollers 54 that hold the non-grounded side of the crawler belt 2 . 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 contact side of the crawler belt 2 is supported by the crawler roller 53, and the non-contact position of the crawler belt 2 is supported by the intermediate roller 54. The ground side is supported.

Next, the drive structure of a combine is demonstrated with reference to FIGS. 4-8. As shown in FIGS. 4 and 7 , a straight hydraulic continuously variable transmission 64 for traveling speed change having a hydraulic straight pump 64 a and a hydraulic straight motor 64 b is provided in the transmission case 63 . The engine 7 is mounted on the right upper surface of the front part of the traveling body 1 , and the gearbox 63 is disposed 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 transmission input shaft 66 protruding leftward from the transmission 63 are connected by an engine output belt 67 , an engine output pulley 68 , and a transmission input pulley 69 .

In addition, a steering hydraulic continuously variable transmission 70 having a hydraulic swing pump 70 a and a hydraulic swing motor 70 b is provided in the transmission case 63 , and the output of the engine 7 is sent to the straight hydraulic continuously variable transmission 64 via the transmission input shaft 66 . And rotary hydraulic continuously variable transmission 70 transmission, on the other hand, utilize steering wheel 43, main transmission lever 44 and sub-transmission lever 45 to carry out output control to straight traveling hydraulic type continuously variable transmission 64 and rotary hydraulic continuously variable transmission 70, by means of straight traveling The hydraulic continuously variable transmission 64 and the rotary hydraulic continuously variable transmission 70 drive the crawler belts 2 on the left and right, so that the combine travels in a field or the like.

Moreover, as shown in FIGS. 4-6 and FIG. 8, the barrel drive case 71 which axially supports the front-end side of the barrel shaft 20 is provided. The cylinder drive case 71 is arrange|positioned at the front surface side of the threshing part 9. As shown in FIG. The threshing cylinder input shaft 72 for driving the said reaping part 3 and the threshing cylinder 21 is pivotally supported by the threshing cylinder drive box 71. Moreover, the main reverse shaft 76 which is a constant rotation axis which penetrates the left-right direction of the threshing part 9 is provided. A working part input pulley 83 is provided at the right end of the main countershaft 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 the threshing clutch 84 and the work part drive belt 85 which also serve as a tension roller.

The front of the threshing cylinder 21 is provided with: the threshing cylinder input shaft 72, which extends along the left and right direction of the traveling body 1; the drum 18, which is arranged on the left and right direction of the traveling body 1; The left and right directions of the body 1 are extended. As the barrel input mechanism 90 that transmits the driving force of the main countershaft 76 to the barrel input shaft 72, barrel drive pulleys 86, 87 and barrel drive belt 88 are provided, and the barrel input mechanism 90 ( The barrel driving pulleys (86, 87 and the barrel driving belt 88) are arranged at one end of the main countershaft 76 on the side of the engine 7, and the driving force from the engine 7 is transmitted to the main countershaft 76, and the constant rotation of the engine 7 output, the threshing cylinder 21 is driven in constant rotation.

A drum drive mechanism and a reaping drive mechanism for transmitting the driving force of the main counter shaft 76 to the drum shaft 82 and the harvesting input shaft 89 are provided on the other end side of the main counter shaft 76 . In addition, a sub-rotation shaft 104 is arranged between the drum shaft 82 and the main counter-rotation shaft 76 , and the power relay pulleys 105 and 106 provided on the main counter-rotation shaft 76 and the sub-rotation shaft 104 are wound with power. The following belt 113 constitutes a power relay mechanism that transmits power to the cutting drive mechanism.

The reaping drive belt 114 is wound around the reaping drive pulleys 107 and 108 respectively provided on the sub-rotating shaft 104 and the drum shaft 82, and a reel drive mechanism is comprised. Furthermore, the reaping drive belt 114 is tensioned and erected by the reaping clutch 109 also serving as a tension roller, whereby the rotational power from the engine 7 transmitted to the main counter shaft 76 is driven through the power relay mechanism and the drum. The mechanism is input to the drum shaft 82. Moreover, the harvesting drive mechanism is comprised so that the harvesting driving force from the engine 7 may be transmitted from the drum shaft 82 which axially supports the drum 18 to the harvesting input shaft 89 via the harvesting drive chain 115 and the sprockets 116 and 117. Thereby, the harvesting part 3 and the drum 18 are driven to constant rotation by the constant rotation output of the engine 7.

The grain lifter shaft 100 which is the rotating shaft of the blower fan shape lifter 29 has a hollow pipe shape, and the main reverse shaft 76 is inserted in the hollow part of the grain lifter shaft 100. As shown in FIG. That is, it has the biaxial structure of the main counter-rotation shaft 76 and the grain lifter shaft 100, and the main counter-rotation shaft 76 and the grain lifter shaft 100 are pivotally supported so that relative rotation is possible. Moreover, the grain lifter drive belt 103 is wound around the grain lifter drive pulley 101,102 respectively provided in the sub counter rotation shaft 104 and the grain lifter shaft 100, and the grain lifter drive mechanism is comprised. Therefore, the rotational power from the engine 7 transmitted to the main countershaft 76 is input to the drum shaft 82 via the power relay mechanism and the grain lifter driving mechanism, and the constant rotation of the grain lifter 29 is performed by the constant rotation output of the engine 7. drive.

Moreover, the machine case 9b of the threshing part 9 is provided with the reaping support frame 36 in the upper surface side of the front part of the threshing machine frame pillar 34 of the traveling body 1 upper surface side. On the right side of the front surface of the support frame body 36, a reaping bearing body 37 is installed, and on the left side of the front surface of the support frame body 36, a forward and reverse switching box 121 described later is installed. And, the reaping input shaft 89 is pivotally supported on the front surface side of the reaping support frame body 36 in a rotatable manner on the traveling body 1 left-right direction via the reaping bearing body 37 and the forward and reverse switching case 121, and the left-right direction The drum shaft 82 (drum 18) is pivotally supported inside the reaping support frame 36 via the drum bearing body 38 so as to be rotatable. Moreover, the barrel drive case 71 is attached to the upper surface side of the reaping support frame 36, and the barrel input shaft 72 is pivotally supported by the barrel drive box 71. As shown in FIG.

On the other hand, the harvesting input shaft 89 of the left-right direction which drives the supply conveyor 17 in the supply chamber 11 is provided. For the reaping driving force transmitted from the engine 7 to the engine 7 side one end of the main reversing shaft 76, it is transferred from the other end of the main reversing shaft 76 on the opposite side of the engine 7 to the reaping forward and reverse switching case 121. The forward and reverse transmission shaft 122 is transmitted. The reaping input shaft 89 is driven via the bevel gear 124 for forward rotation of the reaping forward and reverse switching case 121 or the bevel gear 125 for reverse rotation.

In addition, a threshing cylinder input shaft 72 facing left and right is provided on the front side of the threshing unit 9, and the driving force transmitted from the engine 7 to the engine 7 side end portion of the main counter shaft 76 is transmitted to the engine 7 side end portion of the threshing cylinder input shaft 72. transfer. In addition, the barrel input shaft 72 provided on the front side of the threshing unit 9 is arranged in the left-right direction of the traveling body 1 , while the barrel 21 is pivotally supported by the barrel shaft 20 arranged in the front-rear direction of the traveling body 1 . And the barrel shaft 20 front-end|tip side and the left and right other end part of the opposite side of the motor 7 of the barrel input shaft 72 are connected via the bevel gear mechanism 75. As shown in FIG. It is comprised so that the driving force of the engine 7 may be transmitted to the grain sorting mechanism 10 which sorts the grain after threshing, or the harvesting part 3 from the left and right other end part of the opposite side of the main countershaft 76 to the motor 7.

That is, the right end of the barrel input shaft 72 and the right end of the main countershaft 76 near the engine 7 are connected via the barrel drive pulleys 86 and 87 and the barrel drive belt 88 . The front-end|tip side of the barrel shaft 20 and the left side end part of the barrel input shaft 72 extended in the left-right direction are connected via the bevel gear mechanism 75. As shown in FIG. The power of the engine 7 is transmitted to the front-end side of the barrel shaft 20 from the right end part of the main countershaft 76 via the barrel input shaft 72, and the barrel 21 is driven to rotate in one direction. On the other hand, it is comprised so that the driving force of the engine 7 may be transmitted to the grain sorting mechanism 10 arrange|positioned below the threshing part 9 from the left end part of the main countershaft 76. As shown in FIG.

In addition, the left end portion of the main reversing shaft 76 is connected to the left end portion of the first-grade product conveyor shaft 77 of the first-grade product conveying mechanism 30 and the second grade of the second-grade conveying mechanism 31 by means of the conveyor driving belt 111 . The left end of the product conveyor shaft 78 is connected. The left end portion of the second-grade product conveyor shaft 78 is connected to the left end portion of a crank-shaped swing drive shaft 79 that pivotally supports the rear portion of the swing sorting pan 26 via the swing sorting belt 112 . That is, it is comprised so that the on-off control of the threshing clutch 84 may be performed by an operator's operation of the threshing clutch lever 47. As shown in FIG. Each part of the grain screening mechanism 10 and the threshing cylinder 21 are driven by engaging operation of the threshing clutch 84 .

Moreover, the grain lifting conveyor 32 is driven via the first-class product conveyor shaft 77, and the first-class screening grain of the first-class product conveyance mechanism 30 is collected in the grain tank 6 by this. In addition, the second-grade product reduction conveyor 33 is driven by the second-grade product conveyor shaft 78, thereby making the second-grade screening grains (second-grade product) mixed with the straw scraps of the second-grade product conveying mechanism 31 to swing and screen The upper surface side of the disc 26 is returned. In addition, in the structure in which the dust outlet 23 is provided with a spreader (spreader, not shown) for scattering straw chips, the spreader drive pulley (not shown) and the spreader drive belt (not shown) are used to drive the straw. The left end of the main countershaft 76 is connected to the spreader.

A harvesting input shaft 89 serving as a conveyor input shaft that pivotally supports the conveyance end side of the supply conveyor 17 is provided. The header drive shaft 91 is rotatably supported on the back side of the right side of the grain header 12 . By cutting drive chain 115 and sprocket wheel 116,117, the left side end of forward and reverse transmission shaft 122 is connected with the left side end of drum shaft 82, and cutting input shaft 89 is connected with forward and reverse switching box 121 by means of forward and reverse switching box 121. The forward and reverse transmission shaft 122 is connected. Moreover, the right end part of the reaping input shaft 89 and the left end part of the header drive shaft 91 extended in the left-right direction are connected via the header drive chain 118 and sprockets 119 and 120. A raking shaft 93 for pivotally supporting the raking auger 13 is provided. The middle part of the head drive shaft 91 and the right side part of the raking shaft 93 are connected via the raking drive chain 92.

Moreover, the reel shaft 94 which axially supports the raking reel 14 is provided. The right end of the raking shaft 93 and the right end of the reel shaft 94 are connected via the intermediate shaft 95 and the reel drive chains 96 and 97 . The cutter blade 15 is connected to the right end part of the header drive shaft 91 via the cutter blade drive crank mechanism 98 . It is constituted as follows: through the engagement and disconnection operation of the harvesting clutch 109, the supply conveyor 17, the raking auger 13, the raking and plucking wheel 14 and the cutting knife 15 are driven and controlled, so as to continuously remove the unharvested parts of the field. The ear of the ear stalk is cut slightly sideways.

In addition, in the forward and reverse switching box 121, there are: a bevel gear 124 for forward rotation, which is integrally formed with the forward and reverse transmission shaft 122; a bevel gear 125 for reverse rotation, which is rotatably supported on the cutting input shaft 89; And the intermediate bevel gear 126 which connects the bevel gear 125 for reverse rotation and the bevel gear 124 for normal rotation. The intermediate bevel gear 126 is always meshed with the forward rotation bevel gear 124 and the reverse rotation bevel gear 125 . On the other hand, the slider 127 is slidably supported by the reaping input shaft 89 by spline engagement. The slider 127 is configured to be capable of engaging and disengaging with the forward rotation bevel gear 124 via the forward rotation clutch 128 in the shape of a dog clutch, and is configured to be capable of engaging with the reverse rotation clutch in the shape of a dog clutch. 129 so that the slider 127 engages with the reversing bevel gear 125 in a detachable manner.

In addition, it is configured to include a forward and reverse switching shaft 123 for sliding operation on the slider 127, a forward and reverse switching arm 130 is provided on the forward and reverse switching shaft 123, and the forward and reverse switching lever 212 (forward and reverse operation) part) to make the forward and reverse switching arm 130 swing, so that the forward and reverse switching shaft 123 rotates, so that the slider 127 contacts and separates from the forward rotation bevel gear 124 or the reverse rotation bevel gear 125, and the forward rotation clutch 128 Or the clutch 129 is reversed so that the slider 127 is selectively locked on the bevel gear 124 for forward rotation or the bevel gear 125 for the reverse rotation, so that the cutting input shaft 89 and the forward and reverse transmission shaft 122 are forwardly connected or reversely rotated. Turn link.

A kind of structure that is equipped with the forward and reverse switching box 121 of forward rotation driving or reverse driving as the forward and reverse switching mechanism to the supply conveyor 17, wherein, the supply conveyor 17 and the roller are connected by the forward and reverse switching box 121 The shaft 82 is connected. Therefore, the supply conveyor 17 etc. of the supply chamber 11 can be reversed by the reverse switching operation of the forward-reverse switch box 121, and the clogging straw in the supply chamber 11 etc. can be removed rapidly.

The right end of the auger drive shaft 158 is connected to the output shaft 65 of the engine 7 via a tension pulley type auger clutch 156 and an auger drive belt 157 . The front-end side of the horizontal conveyance auger 160 of the bottom of the grain tank 6 is connected with the left end part of the auger drive shaft 158 via the bevel gear mechanism 159. The longitudinal conveying auger 162 of the grain discharge conveyor 8 is connected to the rear end side of the horizontal conveying auger 160 by means of a bevel gear mechanism 161, and the grains of the grain discharge conveyor 8 are discharged from the auger by means of a bevel gear mechanism 163. 164 is connected to the upper end side of the vertical transport auger 162 . Moreover, the grain discharge lever 155 which engages and disconnects the auger clutch 156 is provided. It is comprised so that the grain discharge lever 155 may be attached to the grain tank 6 front surface behind the driver's seat 42, and an operator may operate the grain discharge lever 155 from the driver's seat 42 side.

Next, power transmission structures such as the transmission case 63 will be described with reference to FIGS. 4 and 7 . As shown in Fig. 4 and Fig. 7, etc., the gearbox 63 is provided with: a hydraulic continuously variable transmission 64 for straight travel (travel main transmission), which has a straight travel pump 64a and a straight travel motor 64b constituting a pair; The hydraulic continuously variable transmission 70 has a swing pump 70a and a swing motor 70b constituting a pair. The transmission input shaft 66 of the transmission case 63 is connected to the pump shaft 258 of the linear pump 64 a and the pump shaft 259 of the rotary pump 70 a through gears, respectively, and is configured to be driven. An engine output belt 67 is wound around a transmission input pulley 69 on the transmission input shaft 66 . The output of the engine 7 is transmitted to the transmission input pulley 69 via the engine output belt 67, thereby driving the straight pump 64a and the rotary pump 70a.

The drive force output from the output shaft 65 of the engine 7 is transmitted to the pump shaft 258 of the straight pump 64 a and the pump shaft 259 of the rotary pump 70 a via the engine output belt 67 and the transmission input shaft 66 . In the straight hydraulic continuously variable transmission 64 , hydraulic fluid is appropriately sent from the straight pump 64 a toward the straight motor 64 b using the power transmitted to the pump shaft 258 . Similarly, in the swing hydraulic continuously variable transmission 70 , hydraulic fluid is appropriately sent from the swing pump 70 a toward the swing motor 70 b using the power transmitted to the pump shaft 259 .

Moreover, the transmission supply pump 151 which supplies hydraulic fluid to each hydraulic pump 64a, 70a and each hydraulic motor 64b, 70b is attached to the pump shaft 259. The straight hydraulic continuously variable transmission 64 is configured to change and adjust the inclination angle of the swash plate of the straight pump 64a according to the operation amount of the main shift lever 44 arranged on the control column 41 and the steering wheel 43, thereby adjusting the direction of the straight motor to the straight motor. The discharge direction and the discharge amount of hydraulic oil at 64b are changed to arbitrarily adjust the rotation direction and rotational speed of the straight motor shaft 260 protruding from the straight motor 64b.

The rotational power of the motor shaft 260 for straight travel is transmitted from the straight travel transmission gear mechanism 250 to the auxiliary transmission gear mechanism 251 . The auxiliary transmission gear mechanism 251 has an auxiliary transmission low gear 254 , an auxiliary transmission medium gear 255 , and an auxiliary transmission high gear 256 switched by auxiliary transmission shifters 252 and 253 . It is configured to alternately switch the output rotation speed of the motor shaft 260 for straight travel to any one of the three-stage transmission speeds of low speed, middle speed or high speed by operating the auxiliary transmission lever 45 arranged on the control column 41 . In addition, there is a neutral position (position where the output of the auxiliary transmission is zero) among the low speed, middle speed, and high speed of the auxiliary transmission.

A cylindrical parking brake 266 is provided on a parking brake shaft 265 (sub-transmission output shaft) provided on the output side of the sub-transmission gear mechanism 251 . Rotational power from the auxiliary transmission gear mechanism 251 is transmitted from the auxiliary transmission output gear 267 fixed to the parking brake shaft 265 to the left and right differential mechanisms 257 . The left and right differential mechanisms 257 each include a planetary gear mechanism 268 . In addition, the parking brake shaft 265 is provided with a pulse generating rotary wheel body 292 for straight travel, and the rotation speed of the straight travel output (straight travel speed = the speed change output of the sub-transmission output gear 267) is measured by a straight travel speed sensor (not shown). detection.

Each of the left and right planetary gear mechanisms 268 is equipped with: a sun gear 271; a plurality of planetary gears 272 meshing with the sun gear 271; a ring gear 273 meshing with the planetary gears 272; The carrier 274 is arranged to be rotatable on the same circumference. The planetary carriers 274 of the left and right planetary gear mechanisms 268 are arranged facing each other on the same axis with an appropriate interval therebetween. A center gear 276 is fixedly connected to a sun gear shaft 275 provided with left and right sun gears 271 .

Each of the left and right ring gears 273 is arranged concentrically with the sun gear shaft 275 in a state in which internal teeth on the inner peripheral surfaces mesh with the plurality of planetary gears 272 . In addition, the external teeth on the outer peripheral surfaces 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 rotation output, which will be described later. Each ring gear 273 is rotatably supported by left and right forced differential output shafts 277 protruding from the outer surface of the carrier 274 toward the left and right outer sides. 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 auxiliary transmission gear mechanism 251 to the left and right planetary gear mechanisms 268 is transmitted from the left and right axle shafts 278 to the respective drive sprockets 51 at the same rotational speed in the same direction, and is transmitted to the left and right crawler belts at the same rotational speed in the same direction. 2 is driven, thereby causing the traveling body 1 to move straight (forward, backward).

The swing hydraulic continuously variable transmission 70 is configured to change and adjust the inclination angle of the swash plate of the swing pump 70a according to the rotation operation amount of the main shift lever 44 arranged on the control column 41 and the steering wheel 43, thereby adjusting the direction of the swing. By changing the discharge direction and discharge amount of hydraulic oil from the motor 70b, the rotation direction and rotational speed of the swivel motor shaft 261 protruding from the swivel motor 70b are arbitrarily adjusted. In addition, a swivel pulse generating rotating wheel body 294 is provided on the steering reversing shaft 280 described later, and the rotation speed (swing speed) of the steering output of the swivel motor 70b is controlled by a swivel rotation sensor (swing speed sensor) not shown in the figure. to test.

In addition, the gearbox 63 is provided with: a wet multi-plate type swing brake 279 (steering brake), which is set on the swing motor shaft 261 (steering input shaft); It is connected with the motor shaft 261 for turning; the steering output shaft 285 is connected with the steering counter shaft 280 by means of a reduction gear 286; gear 273; and a right input gear mechanism 283 that couples the steering output shaft 285 with the right ring gear 273. 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 rotation shaft 280 is transmitted to the left ring gear 273 as counter rotational power through the left intermediate gear 287 and the counter gear 284 on the steering output shaft 285 of the left input gear mechanism 282 . , and on the other hand, it is transmitted to the right ring gear 273 as normal rotational power via the right intermediate gear 288 on the steering output shaft 285 of the right input gear mechanism 283 .

When the auxiliary transmission gear mechanism 251 is brought into a neutral state, transmission of power from the linear motor 64b to the left and right planetary gear mechanisms 268 is prevented. When the auxiliary transmission gear mechanism 251 is set to an auxiliary transmission output other than neutral, power is transmitted from the linear motor 64b to the planetary gear mechanism 268 on the left and right via the auxiliary transmission low gear 254, the auxiliary transmission intermediate gear 255, or the auxiliary transmission high gear 256. transfer. On the other hand, when the output of the swing pump 70a is neutralized and the swing brake 279 is engaged, transmission of power from the swing motor 70b to the left and right planetary gear mechanisms 268 is blocked. When the output of the swing pump 70 a is set to a state other than neutral and the swing brake 279 is turned off, the rotational power of the swing motor 70 b is transferred to the left side via the left input gear mechanism 282 and the counter gear 284 . The transmission is transmitted by the ring gear 273 , and on the other hand, the transmission is transmitted to the right ring gear 273 via the right input gear mechanism 283 .

As a result, when the swing motor 70b rotates forward (reverse rotation), the left ring gear 273 and the right ring gear 273 rotate at the same rotational speed in opposite directions. The right ring gear 273 rotates forward (reverse). That is, the speed change output from each motor shaft 260, 261 is respectively transmitted to the drive sprockets 51 of the left and right crawler belts 2 through the auxiliary transmission gear mechanism 251 or the differential mechanism 257, thereby determining the vehicle speed (travel speed) of the traveling body 1 and direction of travel.

That is, if the swing motor 70b is stopped and the straight motor 64b is driven in a state where the left and right ring gears 273 are stationary, the rotational output from the straight motor shaft 260 is transmitted to the left and right sun gears 271 at the same rotational speed on the left and right, and The crawler belts 2 on the left and right are driven at the same rotational speed in the same direction via the planetary gear 272 and the carrier 274 , thereby causing the traveling body 1 to travel straight.

Conversely, when the straight motor 64b is stopped and the left and right sun gears 271 are stationary and the swing motor 70b is driven, the left ring gear 273 is rotated forward (reverse rotation) by the rotational power from the swing motor shaft 261. ), and causes the right ring gear 273 to rotate in reverse (forward rotation). As a result, one of the driving sprockets 51 of the left and right crawler belts 2 rotates forward and the other rotates backward, and the traveling body 1 changes directions (turning in place, turning sideways) at this time.

In addition, the left and right sun gears 271 are driven by the linear motor 64b, and the left and right ring gears 273 are driven by the swing motor 70b, whereby the speed of the left and right crawler belts 2 is different, and the traveling body 1 moves forward or backward. , One side turns to the left or right with a turning radius greater than the original turning radius (U-shaped turn). The turning radius at this time depends on the speed difference between the left and right crawler belts 2 . In a state where the running driving force of the engine 7 is always transmitted to the left and right crawler belts 2, the turning movement is performed to the left or right.

Next, the working system hydraulic circuit 180 and the traveling system hydraulic circuit 200 in the common type combine of this embodiment are demonstrated, referring FIGS. 9-16. As shown in FIGS. 9 to 14 , the working system hydraulic circuit 180 is configured as a hydraulic actuator and includes: the hydraulic cylinder 4 for lifting and lowering; The grain wheel 14 is supported to be able to lift; the hydraulic cylinder 55 for lifting the auger, which supports the grain discharge auger 164 to be able to lift; the left and right body lifting hydraulic cylinders 56L, 56R, which make the traveling body 1 lift; the working oil tank 57 , which stores hydraulic oil; hydraulic pump 59, which is connected to hydraulic oil tank 57 via oil filter 58; and hydraulic valves 60A to 60E, which switch the flow of hydraulic oil. In addition, the hydraulic valves 60A to 60E are incorporated in the hydraulic valve unit 60 mounted on the traveling body 1 .

The hydraulic pump 59 is connected to the hydraulic cylinder 4 for harvesting elevation via 60 A of hydraulic pressure valves for harvesting elevation, and hydraulic pressure is transmittable. The configuration is such that the operator tilts the harvesting posture lever (not shown) in the driving operation unit (cabin) 5 in the front-rear direction, so that the harvesting and lifting hydraulic cylinder 4 is operated to make the harvesting The part 3 moves up and down to any height (such as harvesting operation height or non-operation height, etc.). On the other hand, the working hydraulic pump 59 is connected to the hydraulic cylinders 27L, 27R for reel raising and lowering so as to be able to transmit hydraulic pressure via the hydraulic valve 60B for reel raising and lowering. The structure is such that the operator operates the hydraulic cylinders 27L, 27R for raising and lowering the tucker by operating the above-mentioned reaping posture lever (not shown) in the left and right direction, thereby raising and lowering the raking tucker 14. Move to any height, thereby harvesting the uncut ear stalks of the field.

The working hydraulic pump 59 is connected to the auger raising and lowering hydraulic cylinder 55 via a hydraulic valve 60C for auger raising and lowering so as to transmit hydraulic pressure. The operator tilts the grain discharge lever 155 in the driving operation part (cabin) 5 in the front-rear direction, and the hydraulic cylinder 55 for lifting and lowering the auger is operated to discharge the grain into the grain in the conveyor 8. The paddy input port lifting of grain discharge auger 164 moves to arbitrary height. Moreover, the grain discharge auger 164 is rotated in the horizontal direction together with the longitudinal conveyance auger 162 and the bevel gear mechanism 163 by the electric motor 165, and the rice input port is moved laterally. That is, it is comprised so that the paddy input opening may be located above a truck bed or a container, and the grain in the grain tank 6 is discharge|emitted in a truck bed or a container.

The hydraulic oil tank 57 and the working hydraulic pump 59 are connected to the left hydraulic cylinder 56L for hydraulic cylinder 56L via the left hydraulic valve 60D for hydraulic pressure transmission. On the other hand, the hydraulic oil tank 57 and the working hydraulic pump 59 are connected to the right hydraulic cylinder 56R for hydraulic pressure transmission through the right hydraulic valve 60E for body elevation. The right and left hydraulic cylinders 56L, 56R for body elevation operate independently of each other, whereby the left and right sides of the traveling body 1 are independently raised and lowered.

Therefore, if the body lifting hydraulic cylinders 56L, 56R on the left and right sides are operated simultaneously so that the crawler frames 50, 50 on the left and right are simultaneously lowered relative to the traveling body 1, the traveling body 1 will be lowered relative to the crawlers 2, 2 on the left and right sides. The grounding portion moves away (rises) upward, and the relative height (vehicle height) of the traveling body 1 with respect to the crawler belts 2 and 2 grounding portions rises. Conversely, if the left and right crawler frames 50, 50 are raised simultaneously with respect to the traveling body 1, the traveling body 1 approaches (falls) with respect to the crawler belts 2, 2 ground contact parts on the left and right sides, so that the traveling body 1 moves closer to the crawler belts 2, 2, and 2. 2 The relative height (vehicle height) of the ground contact portion is lowered.

And, if the left side body lifting hydraulic cylinder 56L is operated to lower the left crawler frame 50 relative to the traveling body 1, or the right side body lifting hydraulic cylinder 56R is operated to make the right crawler frame 50 move relative to the traveling body 1 Body 1 rises (or performs the action of both simultaneously), then traveling body 1 tilts to right bottom. Conversely, if the right side body lifting hydraulic cylinder 56R is actuated to lower the right crawler frame 50 relative to the traveling body 1, or the left side body lifting hydraulic cylinder 56L is actuated to make the right crawler frame 50 move relative to the traveling body 1 Body 1 rises (or carries out the action of both simultaneously), then traveling body 1 tilts to left lower.

The hydraulic oil tank 57, the hydraulic pump 59, and the hydraulic valve unit 60 are respectively mounted on the traveling body 1, and are connected to each other through hydraulic piping 181-183. On the traveling body 1, the operating oil tank 57 is arranged on the front left side. On the other hand, a hydraulic pump 59 is fixed on the front surface of the engine 7 mounted on the front right side, and the oil installed in the operating oil tank 57 is filtered by the hydraulic piping 181. The device 58 and the hydraulic pump 59 are connected. In addition, on the traveling 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 piping 182 . In addition, the hydraulic valve unit 60 is connected to the hydraulic oil tank 57 via the hydraulic piping 183 which is a hydraulic oil return pipe.

The operating oil tank 57 is arranged on the traveling body 1 and is arranged in a space surrounded by the material supply chamber 11 and the drum 18 , and the engine 7 and the operating oil tank 57 are arranged in front of the traveling body 1 in a horizontal arrangement. That is, the working oil tank 57 is arranged in the space surrounded by the machine housing of the feeding chamber 11 and the threshing part 9, and the dust from the reaping part 3 can be suppressed from accumulating in the working oil tank 57, and the working oil can also be prevented from being drawn from the oil supply port. 184 and other intrusive dust pollution. In addition, since the cooling air from the engine 7 flows into the installation space of the hydraulic oil tank 57, even if an oil cooler is not provided in the working system hydraulic circuit 180, the increase in the temperature of the hydraulic oil can be suppressed, and each hydraulic component can be properly controlled. drive.

The operating oil tank 57 is configured to have an oil supply port 184 projecting toward the left side (the outside of the harvester) on the left side (the outside of the harvester), and an oil filter 58 that can be inserted and removed from the left side is attached inside. Therefore, the oil supply port 184 and the oil filter 58 can be easily handled by removing the threshing cover 185 provided in the left side (the harvester outside) of the threshing part 9. Therefore, the work of supplying oil to the hydraulic oil tank 57 and the work of replacing the oil filter 58 are facilitated, and the maintainability of the working system hydraulic circuit 180 can be improved.

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

As shown in FIGS. 14 to 16 , the traveling system hydraulic circuit 200 includes a straight pump 64 a , a straight motor 64 b , a swing pump 70 a , a swing motor 70 b , a transmission supply pump 151 , an oil filter 152 , and an oil cooler 153 . The straight pump 64 a and the straight motor 64 b in the straight hydraulic continuously variable transmission 64 are connected in a closed loop through the straight 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 the swing closed oil passage 202 . The straight pump 64a and the rotary pump 70a are driven by the rotational power of the engine 7, and the swash plate angles of the straight pump 64a and the rotary pump 70a are controlled to change the discharge direction of the hydraulic oil toward the straight motor 64b and the rotary motor 70b and The amount of discharge makes the straight motor 64b and the swing motor 70b perform forward rotation and reverse rotation.

The travel system hydraulic circuit 200 is provided with a straight valve 203 that is switched in response to manual operation of the main shift lever 44 , and a straight cylinder 204 connected to the transmission supply pump 151 via the straight valve 203 . When the straight travel valve 203 is switched, the straight travel speed change operation is performed: the straight travel cylinder 204 is operated to change the angle of the swash plate of the straight travel pump 64a, so that the rotation speed of the straight travel motor shaft 260 of the straight travel motor 64b is continuously changed. Or reverse.

Travel system hydraulic circuit 200 includes a rotary valve 206 that is switched in response to manual operation of steering wheel 43 , and a rotary cylinder 207 that is connected to transmission supply pump 151 via rotary valve 206 . If the swing valve 206 is switched, the left and right swing action is performed: the swing cylinder 207 is activated to change the angle of the swash plate of the swing pump 70a, so that the rotation speed of the swing motor shaft 261 of the swing motor 70b is continuously increased. Change or reverse, and the travel body 1 changes the travel direction to the left and right to change the direction or correct the travel route at the uncultivated land in the field.

The suction side of the transmission feed pump 151 is connected to a strainer 217 inside the transmission 63 via hydraulic piping 208 . A supply and introduction oil passage 218 is connected to a discharge side of the transmission supply pump 151 via a hydraulic piping 209 , and an oil filter 152 is provided in the middle of the hydraulic piping 209 . A supply branch oil passage 219 connected to the two closed oil passages 201 and 202 is connected to the downstream side of the supply introduction oil passage 218 . Therefore, while the engine 7 is being driven, the two closed oil passages 201 and 202 are always replenished with hydraulic oil from the transmission feed pump 151 .

In addition, the supply branch oil passage 219 is connected to the straight cylinder 204 through the straight valve 203 , and is connected to the swing cylinder 207 through the swing valve 206 . In addition, the supply branch oil passage 219 is connected to the transmission case 63 via the remaining relief valve 220 and hydraulic piping 210 , and an oil cooler 153 is provided in the middle of the hydraulic piping 210 . Therefore, when the remaining operating oil from the transmission feed pump 151 is returned to the transmission 63 via the remaining relief valve 220 , the operating oil is cooled by the oil cooler 153 .

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, etc., a pair of left and right engine room pillars 147 are erected on the rear side of the driver's platform 5 on the upper surface of the traveling body 1, and a backrest is tensioned between the left and right engine room pillars 147. The panel body 148 thus covers the rear of the engine room 146 below the driver's seat 42 . In addition, the box-shaped wind tunnel box 170 is erected on the right engine room pillar 147 provided at the right end of the cab 5 on the traveling body 1 via the opening and closing fulcrum shaft 171 . The outside opening of the harvester on the right side of the wind tunnel box 170 is tensioned with a dust removal net, which prevents straw chips from entering the wind tunnel box 170 and the engine room 146 due to the existence of the dust removal net.

The water-cooling radiator 154 is erected on the harvester inside of the wind tunnel box 170 on the upper surface side of the traveling body 1 , and the radiator 154 faces the cooling fan 149 of the engine 7 . In addition, a shroud 150 is provided to cover the entire ventilation range of the radiator 154 , and the cooling fan 149 is disposed in an opening formed in the shroud 150 . In addition, an oil cooler 153 is provided in the wind tunnel box 170 . By the rotation of the cooling fan 149, outside air (cooling wind) is introduced into the wind tunnel box 170 from the outside opening of the harvester on the right side of the wind tunnel box 170, and the dust removal is completed from the opening on the inside of the harvester on the left side of the wind tunnel box 170. The cooling air is sent into the engine room 146. Accordingly, the oil cooler 153 , the radiator 154 , the engine 7 , and the like are cooled by the cooling air flowing into the engine room 146 .

Next, the structure around the harvesting support frame 36 which comprises a part of machine case 9b of the threshing part 9 is demonstrated, referring FIG. 5, FIG. 6, FIG. 8, FIG. 11-14 etc. FIG. As shown in Fig. 5, Fig. 6, Fig. 8, and Fig. 11～Fig. (Rear strut frame) 34 respective front positions are erected from the traveling body 1 upper surface; The reaping support is connected with the pillar 36a. The beam frames 36b and 36c for reaping support frames are erected on the upper end and the middle part of the prop 36a for reaping support arrange|positioned back and forth, and the threshing machine frame prop 34, respectively.

Both ends of the left and right roller bearing bodies 38 are connected to the midway parts of the beam frames 36b, 36c for the upper and lower reaping support frames arranged on the left and right, and the roller 18 is pivotally supported in the reaping support frame 36 by the left and right roller bearing bodies 38 . The support frame 36 is provided with: side plates 186, which cover the left and right sides of the drum 18; top plates 187, which cover the top of the drum 18; front plates 188, which cover the front surface of the drum 18; The bottom of the drum 18 is covered. That is, the reaping support frame 36 constitutes a closed space that communicates with the rear end of the feeding chamber 11 and the threshing port 9a at a position above the beam frame 36c on the lower side. And the drum 18 which guides the fringe stalk from the supply conveyor 17 smoothly to the threshing opening 9a is provided in this closed space.

The side plate 186 is provided so as to seal the area surrounded by the pillars 34, 36a and the beam frames 36b, 36c, and has a hole through which the roller shaft 82 penetrates. The drum shaft 82 is pivotally supported. The top plate 187 is spanned over the beam frame 36b on either side, and the barrel drive box 71 is provided in the upper surface. The upper edge of the front plate 188 is connected to the front edge of the top plate 187 , and extends upward and downward toward the supply chamber 11 . The front edge of the bottom plate 189 is connected with the rear edge of the bottom plate 190 of the feed chamber 11, and the rear edge of the bottom plate 189 is connected with the front edge of the bottom front edge of the threshing opening 9a in front of the threshing cylinder 21. 9a functions as a guide plate for guiding the fringe stalk.

A working oil tank 57 is provided in the space below the installation space of the drum 18 where the cutting support frame 36 is installed, and the upper side of the working oil tank 57 is covered by a bottom plate 189 . In addition, the front of the hydraulic oil tank 57 is covered by a front cover 191 connected to the bottom plate 189 . The rear of the operating oil tank 57 is provided with a blower fan-shaped grain lifter 29 , and the outer circumference of the grain lifter 29 is covered by a grain lifter cover plate 192 . Therefore, in the reaping support frame 36, the hydraulic oil tank 57 is provided in the space surrounded by the bottom plate 189, the front cover 191, and the grain lifter cover 192. As shown in FIG.

The operating oil tank 57 setting space surrounded by the bottom plate 189, the front cover plate 191 and the grain lifter cover plate 192 constitutes a passage of left and right openings, and communicates with the engine room 146 on the right side. Moreover, the machine case 9b of the threshing part 9 is equipped with the left and right threshing side plates 193, and the front edge of the right threshing side plate 193 is fixed to the right side threshing frame support 34 located ahead rather than the engine room support 147. Therefore, part of the cooling air taken in from outside air by the cooling fan 149 passes through the engine room 146 and flows into the hydraulic oil tank 57 installation space in the harvesting support frame 36 to cool the hydraulic oil tank 57 .

Moreover, a part of the cooling air which passed from the engine room 146 flows into the air path formed by the grain lifter cover plate 192 behind the hydraulic oil tank 57 installation space by the rotation of the grain lifter 29. Thereby, the space between the engine room 146 and the threshing part 9 forms the airflow which flows along the front-back direction, Therefore External air is also guided by the airflow of this front-back direction, and flows in from the traveling body 1 front. External air flows into the hydraulic oil tank 57 installation space from the front of the traveling body 1 , and cools the hydraulic oil tank 57 together with a part of the cooling air from the engine room 146 . That is, the exhaust air from the engine 7 actively flows toward the valley lifter 29 side, whereby the external air flows into the space where the operating oil tank 57 is installed together with a part of the cooling air of the engine 7, thereby improving the cooling effect of the operating oil tank 57. .

As described above, the cooling air from engine room 146 is configured to pass through hydraulic oil tank 57 , thereby suppressing temperature rise of the working oil circulating in working system hydraulic circuit 180 including hydraulic oil tank 57 . Therefore, not only does it not need to install an oil cooler in the working system hydraulic circuit 180, but also, by setting the working system hydraulic circuit 180 and the travel system hydraulic circuit 200 as different systems, it is possible to provide an oil cooler only in the travel system hydraulic circuit 200. The structure of device 153. As a result, the capacity of oil cooler 153 can be reduced, and the cooling efficiency of radiator 154 and engine 7 located on the downstream side of oil cooler 153 in the cooling air flow can be improved.

In addition, the secondary counter-rotating shaft 104, which receives the driving force from the engine 7, is pivotally supported on the threshing frame pillar (rear pillar frame) 34, and is aligned with the roller bearing body 38 connected with the beam frames 36b, 36c for the upper and lower reaping support frames. The drum shaft 82 of the drum 18 is pivotally supported. The harvesting input shaft 89 pivotally supported at the front position rather than the pillar (front pillar frame) 36a for harvesting support penetrates the supply chamber 11. As shown in FIG. Equipped with: a first power transmission mechanism (drum drive mechanism composed of driving pulleys 107, 108 and harvesting drive belt 114) that transmits the rotational power of the sub-rotating shaft 104 to the drum shaft 82; and a second power transmission mechanism (the harvesting driving mechanism constituted by the harvesting drive chain 115 and the sprockets 116 and 117 ) transmits the rotational power of the drum shaft 82 to the harvesting input shaft 89 . Furthermore, the oil supply port 184 of the hydraulic oil tank 57 and the oil filter 58 are arrange|positioned in the area|region surrounded by the said 1st power transmission mechanism, the 2nd power transmission mechanism, and the support post 36a for harvesting in front. Thus, oil supply to the hydraulic oil tank 57 and replacement of the oil filter 58 can be performed without removing the transmission members (chains or belts) in the first power transmission mechanism and the second power transmission mechanism. Therefore, it is possible to improve the maintainability of the working system hydraulic circuit 180 .

In addition, the threshing unit 9 is configured such that the grain lifter 29 is pivotally supported on the rear side of the threshing frame support (rear support frame) 34, and the main countershaft 76 is capable of relative rotation with respect to the grain lifter shaft 100 of the grain lifter 29. Penetrate the valley lifter shaft 100. And the main counter-rotating shaft 76 receives the power from the engine 7, and transmits power to the sub-rotating shaft 104, and the rotational power of the sub-rotating shaft 104 is split and transmitted to the grain lifter shaft 100 and the drum shaft 82, respectively. The driving system for driving the reaping section 3, the grain sorting mechanism 10, and the grain lifter 29 is collectively arranged on the left side of the threshing section 9 (the outside of the harvester), whereby the right side of the threshing section 9 can be (inside the harvester) front opening. Therefore, the right side of the hydraulic oil tank 57 installation space on the front lower 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.

Explanation of reference signs

1 traveling body

3 Harvesting Department

5 bridge

7 engine

9 Threshing Department

9a Thresher port

9b Housing

11 Feed room

17 Feed Conveyor

18 rollers

21 Thresher

29 Grain raising machine

34 Threshing Rack Struts

35 Cutting off the support frame

36a Struts for cutting support frames

36b Beam frame for cutting supporting frame

36c Beam frame for cut support frame

37 Cut bearing body

38 roller bearing body

57 working oil tank

58 oil filter

59 hydraulic pump

63 gearbox

76 Grain lifter shaft (constant rotation shaft)

82 Roller shaft (front rotating shaft)

89 Reap input shaft

184 oil supply port

185 threshing cover

186 side panels

187 top plate

188 front panel

189 bottom plate

190 bottom plate (feeding room)

191 Front cover

192 Grain lifter cover

193 Threshing side panels

Claims (7)

1. A combine harvester comprises a traveling machine body, a threshing part with a threshing cylinder and an engine,

a harvesting part is arranged at the front part of the threshing part, the harvesting ear stalks conveyed from the harvesting part through a feeding chamber are fed to the threshing part arranged at the tail end side of the feeding chamber,

the combine-harvester is characterized in that,

a working oil tank for storing working oil is disposed on the traveling machine body and in a space surrounded by the feed chamber and the threshing device,

the working oil tank is arranged on the side of the engine and in front of the grain lifter.

2. A combine harvester according to claim 1,

the hydraulic oil tank and the engine are disposed at positions that overlap in height when viewed in side elevation.

3. A combine harvester according to claim 1 or 2,

the winnowing machine is arranged below the threshing part,

the height position of the upper end of the working oil tank is configured as follows: is positioned between the upper end and the lower end of the winnowing machine.

4. A combine harvester comprises a traveling machine body, a threshing part with a threshing cylinder and an engine,

a harvesting part is arranged at the front part of the threshing part, and the harvesting ear stalks conveyed from the harvesting part through a feeding chamber are fed to the threshing part arranged at the tail end side of the feeding chamber,

the combine-harvester is characterized in that,

a working oil tank is arranged in a space surrounded by the feeding chamber and the threshing device,

the working oil tank is arranged on the side of the engine,

a radiator and a cooling fan which supplies air towards the other side of the width direction of the engine body are arranged on one side of the width direction of the engine body,

the radiator, the cooling fan, the engine, and the hydraulic oil tank are arranged in a left-right direction so as to overlap each other when the travel machine body is viewed in a side view, and an oil supply port of the hydraulic oil tank is arranged outside a harvester of the travel machine body.

5. A combine harvester according to claim 4,

disposing the oil supply port in: the threshing part is arranged on the inner side of the threshing cover arranged on the outer side of the machine body.

6. A combine harvester according to claim 3,

the threshing cover is configured to be detachable.

7. A combine harvester comprises a traveling machine body, a threshing part with a threshing cylinder and an engine,

a harvesting part is arranged at the front part of the threshing part, and the harvesting ear stalks conveyed from the harvesting part through a feeding chamber are fed to the threshing part arranged at the tail end side of the feeding chamber,

the combine-harvester is characterized in that,

a working oil tank is arranged in a space surrounded by the feeding chamber and the threshing device,

the engine and the operating oil tank are arranged in a left-right direction so as to overlap each other when the travel machine body is viewed in a side view, and a power relay mechanism that transmits power from the threshing unit to the harvesting unit is arranged: the working oil tank is arranged outside the harvester.

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