JP7453074B2 - combine - Google Patents

Description

The present invention relates to a combine harvester equipped with a threshing section that uses a handling barrel to thresh grain culms that have been harvested at a reaping section and transported by a transport device.

BACKGROUND ART Conventionally, there is a combine harvester having a structure in which grain culms cut by a cutting blade device are transported by a transport device and supplied to a threshing section having a handling barrel. Some of these combine harvesters are equipped with a threshing transmission, which is a transmission that changes the rotational speed of the rotating handling drum depending on the type and amount of crops to be harvested (for example, a patented (See Reference 1).

The threshing transmission is installed between the handling drum input shaft, which rotates when receiving power transmitted from a drive source such as an engine, and the handling drum shaft, which is the rotation axis of the handling drum whose axial direction is the longitudinal direction of the machine. It will be done. The threshing transmission changes the rotational speed of the rotational power transmitted to the handling drum shaft by changing the combination of gears that mesh with each other in the transmission mechanism from the handling drum input shaft to the handling drum shaft.

Patent Document 1 discloses a threshing transmission in which a movable body in which a speed change gear is formed is movable in the axial direction by spline fitting on a handling cylinder input shaft whose axial direction is in the left-right direction of the machine body. A configuration is disclosed in which the intermediate shaft is disposed parallel to the cylinder input shaft and meshes with the handling cylinder shaft via a bevel gear. The threshing transmission transmits the rotational power of the handling cylinder input shaft to the handling cylinder shaft via the intermediate shaft, and receives the movement operation of the movable body to perform three speed changes: high speed, medium speed, and low speed. A speed change operation for the threshing transmission device is performed by operating a speed change lever that moves the movable body.

In the configuration disclosed in Patent Document 1, the threshing transmission is provided in front of the front wall of the handling chamber that accommodates the handling barrel in the threshing section. That is, the handling barrel shaft extends forward from the front wall of the threshing section, and is configured to receive rotational power via the threshing transmission at the portion protruding from the front wall. A transmission case that supports and accommodates shafts and the like constituting a transmission mechanism including a threshing transmission is supported and fixed to the front wall of the threshing section. Note that the speed change lever is provided on the upper side of the transmission case.

JP2018-085942A

The front wall of the threshing section is a part that supports the handling drum, which is a heavy object, via the handling drum shaft, and is subjected to a large load as the handling cylinder is frequently turned on and off. For this reason, when the transmission case is supported on the front wall of the threshing section, as in the configuration disclosed in Patent Document 1, there is a problem in that the load on the front wall increases.

In this way, according to the conventional configuration, the transmission case is supported against the front wall of the threshing section that receives the support load of the handling cylinder, so if sufficient support strength cannot be obtained on the front wall of the threshing section, the The load on the wall becomes excessive. An excessive load on the front wall of the threshing section may cause problems such as deformation of the front wall and tilting of the transmission case.

The present invention has been made in view of the above-mentioned problems, and is capable of reducing the burden on the front wall of the threshing section, firmly supporting the handling cylinder transmission case, and improving the speed change operation. It is an object of the present invention to provide a combine harvester capable of stably transmitting rotational power to an accompanying handling barrel.

The combine harvester according to the present invention is a combine harvester in which grain culms cut by a cutting blade device are transported by a transport section and supplied to a threshing section having a handling barrel in a handling chamber, and the combine is rotated by receiving power transmitted from a drive source. a threshing transmission device having a handling drum input shaft, an intermediate shaft for changing the rotational speed transmitted from the handling drum input shaft to the handling drum shaft, the handling drum input shaft, the intermediate shaft, and the handling drum. The handling cylinder transmission case supports a portion of the shaft extending from the front wall of the handling chamber, and the handling cylinder transmission case is supported by the front wall and the conveying section.

In the combine harvester according to another aspect of the present invention, the handling drum transmission case is supported by an upper surface of the transport section with respect to the transport section.

In the combine harvester according to another aspect of the present invention, in the combine harvester, the handling barrel transmission case has a speed change case portion that supports the intermediate shaft, and the speed change case portion is arranged with respect to an upper surface portion of the conveyance portion. It has a support leg portion that supports the handling trunk transmission case.

In the combine harvester according to another aspect of the present invention, in the combine harvester, the threshing transmission device has a speed change lever extending from the speed change case portion toward one side in the left-right direction of the machine body, and is provided in the conveying portion. The gear shift lever includes a lever support portion that supports the gear shift lever, and a lever movement restriction portion that is provided on the lever support portion and restricts movement of the gear shift lever at least in a shift operation direction.

According to the present invention, it is possible to reduce the burden on the front wall of the threshing section, and also to firmly support the handling cylinder transmission case, thereby stably transmitting rotational power to the handling cylinder that accompanies speed change operation. It can be carried out.

It is a left side view of a combine concerning one embodiment of the present invention. FIG. 1 is a right side view of a combine harvester according to an embodiment of the present invention. FIG. 1 is a plan view of a combine harvester according to an embodiment of the present invention. 1 is a diagram showing a power transmission configuration in a combine harvester according to an embodiment of the present invention. FIG. 1 is a perspective view showing a structure of a handling trunk transmission case and its vicinity according to an embodiment of the present invention. FIG. 2 is a plan view showing a configuration of a handling trunk transmission case and its vicinity according to an embodiment of the present invention. FIG. 2 is a left side view showing a configuration of a handling trunk transmission case and its vicinity according to an embodiment of the present invention. FIG. 2 is a right side view showing a structure of a handling trunk transmission case and its vicinity according to an embodiment of the present invention. FIG. 2 is a front view showing the configuration of a handling trunk transmission case and its vicinity according to an embodiment of the present invention. 1 is a plan sectional view showing the configuration of a handling barrel transmission case according to an embodiment of the present invention. 11 is a sectional view taken along line BB in FIG. 10. FIG. 1 is a front sectional view showing the configuration of a handling trunk transmission case according to an embodiment of the present invention. 13 is a sectional view taken along line DD in FIG. 12. FIG. FIG. 2 is a plan partial cross-sectional view showing a connection structure of a speed change lever according to an embodiment of the present invention. It is a front view showing the composition of the lever support part concerning one embodiment of the present invention. FIG. 2 is a plan partial cross-sectional view showing the configuration of a lever support portion according to an embodiment of the present invention.

The present invention reduces the burden on the front wall of the threshing section by devising the support structure of the handling drum transmission case that houses the power transmission mechanism to the handling drum including the threshing transmission. The aim is to strengthen the support and stabilize the transmission of rotational power to the handling cylinder, which is accompanied by speed change operations. Embodiments of the present invention will be described below.

[Overall configuration of combine harvester]
First, the overall configuration of a combine harvester 1 according to this embodiment will be described using FIGS. 1 to 4. In addition, in the following description, the left side (the lower side in FIG. 3) and the right side (the upper side in FIG. 3) when facing the front of the combine 1 are referred to as the left side and right side of the combine 1, respectively.

As shown in FIGS. 1 and 2, a combine harvester 1 according to the present embodiment is a harvester that can scoop harvested crops from a field into the machine body, thresh, sort, and store grains, and carry them out of the machine as appropriate. It is a normal type combine harvester. The combine 1 has a self-propelled traveling body 2 and a reaping section 3 provided at the front end of the traveling body 2. The reaping section 3 is configured as a reaping device that takes in uncut grain culms such as rice and wheat while reaping them, and is attached to the traveling machine body 2 so as to be movable up and down.

The traveling body 2 includes a traveling section 4 configured as a crawler-type traveling device having a pair of left and right crawler sections 5, 5. A body frame 6 is installed between the left and right crawler sections 5, 5. Each crawler section 5 has a plurality of rotating bodies including a driving sprocket 5a provided at its front end, and a crawler belt 5c wound around these rotating bodies. The drive sprocket 5a receives power from the engine 25 included in the combine 1 and is driven to rotate.

On the left side of the machine frame 6, there are provided a threshing section 7 that threshes the grain culms cut and supplied by the reaping section 3, and a sorting section 8 that sorts the grains threshed by the threshing section 7. . The threshing section 7 and the sorting section 8 are arranged in such a manner that the threshing section 7 is on the upper stage and the sorting section 8 is on the lower stage.

On the machine frame 6, on the right side of the threshing section 7 and the sorting section 8, there is provided a grain storage section 9 having a grain tank 10 for storing grains (fine grains) sorted by the sorting section 8. . A lower discharge conveyor 11 is provided in the grain tank 10 to convey the stored grain toward the discharge port of the grain tank 10 (see FIG. 4). A vertical conveyor 12 is vertically provided so as to communicate with the discharge port of the grain tank 10. A grain discharge conveyor 13 is connected to the upper end of the vertical conveyor 12 . The grain discharge conveyor 13 is provided so as to be able to turn in the horizontal direction and to be able to swing up and down around a horizontal axis. The grains in the grain tank 10 are transported by these conveyors, and are discharged from the paddy dumping port 14 provided at the tip of the grain discharge conveyor 13 into a truck bed, a container, or the like.

The combine 1 includes a driving section 15 on which an operator rides. The driving section 15 is provided on the body frame 6 at a position in front of the grain storage section 9, that is, at a position on the front right side of the body frame 6. Therefore, the driving section 15 is provided on one side (right side) of the threshing section 7 in the left-right direction of the machine.

The driving section 15 is covered by a cabin 16. The driver's seat 15 is provided with a driver's seat 17, a control handle 18 located in front of the driver's seat 17, and various operating parts such as a main gear shift lever 19, an auxiliary gear shift lever, and a working clutch lever (see FIG. (see 2). The working clutch lever is a working operating tool for turning on and off the threshing clutch 57 and the reaping clutch 75 (see FIG. 4).

An engine 25 serving as a driving source is provided below the driving section 15 on the body frame 6. The engine 25 uses the space below the driver section 15 and is installed in the front right space on the fuselage frame 6. Engine 25 is, for example, a diesel engine.

The reaping section 3 will be explained. The reaping section 3 includes a feeder 30 as a conveying device, a grain header (platform) 31, a cutting blade device 32, a pair of left and right weeding bodies 33, 33, and a raking reel 34.

The feeder 30 transports the grain culm cut by the reaping section 3 and supplies it to the threshing section 7 . The feeder 30 includes a feeder house 35 as a housing, and a conveyor 36 (see FIG. 4) for conveying grains provided inside the feeder house 35. The feeder 30 is located on the left side of the cabin 16, and has a rear end opening of a feeder house 35, which has a substantially rectangular cylindrical shape whose longitudinal direction is the front-rear direction when viewed from above, into a handling opening 7a on the front side of the threshing section 7. They are placed in communication.

The grain header 31 is configured in the shape of a horizontally long bucket, and is connected to the front side of the feeder 30 so as to communicate with the front end opening of the feeder house 35 . A raking auger (platform auger) 37 is provided within the grain header 31 . The scraping auger 37 is rotatably mounted on a shaft with the left-right direction as the rotation axis direction.

The cutting blade device 32 is provided at the lower front edge of the grain header 31 and is configured in the shape of a clipper. The pair of left and right grass dividers 33, 33 are provided so as to protrude forward from the left and right side portions of the front side of the grain header 31. The scraping reel 34 is a reel with tine bars, and is provided at a position above and in front of the scraping auger 37. The raking reel 34 is rotatably supported between the distal end portions of a pair of left and right reel support arms 34a, 34a whose base end portions are pivotally supported on the grain header 31, with the left-right direction as the rotation axis direction. The raking reel 34 continuously acts on the pod-bearing portion of the grain culm while rotating, and rakes the pod-wearing portion of the grain culm toward the raking auger 37 side. For the operation of each part of the reaping section 3, power from the engine 25 transmitted through various transmission mechanisms is used.

The conveyor 36 in the feeder house 35 has a reaping input shaft (feeder house conveyor shaft) 38, which is provided at the front of the threshing section 7 and has an axial direction in the left-right direction, as a drive shaft that pivotally supports its feed end side. The rear end portion of the feeder 30 is rotatably supported with respect to the traveling machine body 2 side using a reaping input shaft 38 as a rotation axis. Furthermore, an elevating cylinder 39, which is a hydraulic cylinder, is interposed between the lower surface of the feeder house 35 and the body frame 6.

The reaping section 3 is provided to move up and down as the feeder 30 rotates relative to the traveling machine body 2 as the lifting cylinder 39 expands and contracts. The height of the reaping section 3 is adjusted by raising and lowering the reaping section 3. The raising and lowering operation of the reaping section 3 is operated by a predetermined operation section provided in the driving section 15.

A front rotor 26 is provided on the rear side of the feeder 30 to send the grain culm conveyed by the conveyor 36 to the handling port 7a. The front rotor 26 is provided between the terminal end of the conveyor 36 and the handling port 7a. The front rotor 26 has a substantially cylindrical rotor main body 27 called a beater or the like, and a front rotor shaft 28 whose axial direction extends in the left-right direction. The front rotor shaft 28 is disposed at the central shaft portion of the rotor body 27 and rotates integrally with the rotor body 27. The front rotor 26 is provided in a front rotor chamber 29 (see FIG. 7) formed above the left front side portion of the traveling body 2.

The grain culm conveyed by the feeder 30 is fed from the end of the conveyor 36 into the handling chamber 7b of the threshing section 7 through the handling port 7a by the front rotor 26. The structure in which the front rotor 26 is provided in the front rotor chamber 29 constitutes the conveying section 20 in the combine harvester 1 together with the feeder 30.

The threshing section 7 and the sorting section 8 will be explained. The threshing section 7 includes a handling drum 40 provided in a handling chamber 7b with a handling opening 7a opened to the front, and a receiving net 42 arranged below the handling drum 40. The handling room 7b is formed by a machine frame provided on the machine body frame 6.

The handling cylinder 40 is rotatably supported by a handling cylinder shaft 41 whose axial direction is the front-rear direction. The handling cylinder 40 has a cylindrical main body with the handling cylinder axis 41 along the central axis, and spiral blades are provided on the outer peripheral surface of the main body. On the upper side of the handling cylinder 40, a plurality of dust feeding valves are provided whose angle can be adjusted to adjust the conveyance speed (residence time) of the threshed grains in the handling chamber. The receiving net 42 allows the grains to leak out, and is provided along the outer circumferential surface of the lower part of the handling barrel 40 .

The sorting unit 8 includes a swinging sorting board 43 as a swinging part disposed below the receiving net 42, and a swinging shaft 44a that swings the swinging sorting board 43 by rotational power from a drive source. It has a mechanism 44, a first conveyor 45, a second conveyor 46, and a winnow 47. As shown in FIG. 4, a pre-fan 71 is provided in front of the winnow 47, and a second fan 72 is provided behind the winch 47.

The swing sorting board 43 has a structure for specific gravity sorting, such as a feed pan, a chaff sieve arranged behind the feed pan to adjust the amount of grain leakage, and a grain sieve arranged below the chaff sieve. The first conveyor 45 is arranged in the first gutter extending in the width direction of the machine so as to collect the most grains. The No. 2 conveyor 46 is disposed at a position behind the No. 1 conveyor 45 in a No. 2 gutter extending in the width direction of the machine body so as to collect the No. 2 grains. The winnower 47 sends sorting air to the swinging sorting board 43 from the lower front to the upper rear.

Further, a return conveyor 48 is provided on the right side of the machine where the threshing section 7 and sorting section 8 are disposed (see FIG. 4). The return conveyor 48 has a lower end located near the second conveyor 46 and is connected to the second conveyor 46, an upper end located near the front end of the handling cylinder 40, and extends in an upwardly inclined manner. It is set up. A grain frying conveyor 49 extending in the vertical direction is provided on the right side of the return conveyor 48. The grain frying conveyor 49 conveys the first grains sent by the first conveyor 45 into the grain tank 10.

The combine harvester 1 having the above-mentioned configuration is capable of raising and lowering the reaping part 3 to a desired height above the ground (a harvested crop The grain culm reaping height) is raised, the non-working state changes to the working state, and the traveling machine body 2 travels in this state. As a result, the combine harvester 1 divides the harvested crop into crops to be harvested and crops not to be harvested using the left and right dividing bodies 33, 33, and rakes the pod-bearing part on the ear side of the grain culm to be harvested using the raking reel 34. At the same time, the pod-bearing part of the grain culm is cut off by the cutting blade device 32.

The podded portion of the grain culm that has been harvested at the desired reaping position is scraped into the grain header 31 by a rotatably driven scraping auger 37, and collected near the entrance of the feeder house 35 at the left and right center of the grain header 31. The grains are passed through the feeder house 35 by the conveyor 36 in the feeder house 35, are thrown into the handling port 7a by the front rotor 26, and are supplied to the threshing section 7.

The podded portion of the grain culm supplied to the threshing section 7 is threshed by the threshing section 7. Specifically, the grain culms supplied to the threshing section 7 are threshed mainly between the handling drum 40 and the receiving net 42 while being conveyed rearward by the rotating handling drum 40. Threshed grains such as grains smaller than the mesh of the receiving net 42 leak from the receiving net 42. The straw waste that does not leak from the receiving net 42 is discharged into the field from a dust outlet provided at the rear of the sorting section 8 by the conveying action of the handling cylinder 40.

On the other hand, the grains that have been threshed in the threshing section 7 and leaked from the receiving net 42 are sorted by the sorting section 8. Specifically, the threshed grains that have been threshed by the handling drum 40 and leaked from the receiving net 42 are separated into grains such as fine grains by the specific gravity sorting effect by the swing sorting board 43 and the wind sorting effect by the chisel 47. (first product), a mixture of grains such as kernels with stems and straw (second product), and straw waste and the like.

The grains (first grains) that have fallen from the swing sorting board 43 due to sorting in the sorting section 8 are conveyed to the grain tank 10 by the first conveyor 45 and the grain frying conveyor 49 connected thereto. The second grain is returned to the threshing start end side of the handling cylinder 40 by the second conveyor 46 and the return conveyor 48 connected thereto, and undergoes the threshing process again. Straw waste and the like are discharged into the field from a dust outlet provided at the rear of the sorting section 8.

Next, the power transmission configuration of the combine harvester 1 according to this embodiment will be explained using FIG. 4. The combine 1 drives the reaping section 3 , the running section 4 , the threshing section 7 , the sorting section 8 , and the grain storage section 9 using the rotational power of the engine 25 .

Engine 25 has a first output shaft 25a and a second output shaft 25b. The rotational power of the first output shaft 25a is transmitted to the running section 4, the threshing section 7, the sorting section 8, and the reaping section 3. The rotational power of the second output shaft 25b is transmitted to the grain storage section 9. Note that the rotational power of the second output shaft 25b is transmitted to the fan shaft of a cooling fan 25d provided for the engine 25. Further, the engine 25 has a work equipment pump shaft that drives a charge pump 54 that operates the lifting cylinder 39 and the like.

Regarding the power transmission system to the traveling section 4, the rotational power of the first output shaft 25a is transmitted to the HST input shaft 52 by the first belt transmission mechanism 51, and is input to the transmission 53 including the traveling HST and the turning HST. . Here, "HST" is a hydraulic continuously variable transmission that employs a method in which hydraulic pressure generated by driving a hydraulic pump is converted back into rotational force by a hydraulic motor. The driving force of the transmission 53 rotates the drive sprocket 5a of the crawler section 5 that constitutes the traveling section 4.

Regarding the power transmission system to the threshing section 7, the rotational power of the first output shaft 25a is transmitted to the threshing section input shaft 56 by the second belt transmission mechanism 55. The second belt transmission mechanism 55 is provided with a threshing clutch 57 that arbitrarily intermittently transmits the rotational power of the first output shaft 25a to the threshing unit input shaft 56.

The rotational power of the threshing section input shaft 56 is transmitted to the handling barrel input shaft 59 by a third belt transmission mechanism 58. The rotational power of the handling cylinder input shaft 59 is transmitted to the handling cylinder shaft 41 via the threshing transmission 60. The threshing transmission 60 performs two-stage speed change, high speed and low speed, on the rotational power input from the handling drum input shaft 59 to the handling drum shaft 41.

With such a configuration, the driving force of the engine 25 is transmitted to the threshing section 7. Then, by operating a working clutch lever provided in the driving section 15, the threshing clutch 57 is turned ON/OFF, and the power transmission to the threshing section 7 is interrupted or interrupted.

Regarding the power transmission system to the sorting section 8, the threshing section input shaft 56 has a support shaft section for the winnowing machine 47, and the rotational power of the threshing section input shaft 56 is transmitted to the threshing intermediate shaft 62 by a fourth belt transmission mechanism 61. The signal is transmitted to a pulley rotating body 63 that is supported by the shaft. The rotational power of the pulley rotating body 63 is transmitted to the pre-fan 71 and the winnower 47 by a predetermined transmission mechanism. Further, the rotational power of the threshing unit input shaft 56 is transmitted by a predetermined transmission mechanism to the first conveyor shaft 45a that rotates the first conveyor 45, the second fan shaft 72a that rotates the second fan 72, and the second conveyor 46. The signals are respectively transmitted to the second conveyor shaft 46a.

The rotational power of the first conveyor shaft 45a is transmitted to the grain frying conveyor 49 by a predetermined transmission mechanism. The rotational power of the second conveyor shaft 46a is transmitted to the swing shaft 44a of the swing mechanism 44 by the fifth belt transmission mechanism 64. The rotational power of the second conveyor shaft 46a is transmitted to the return conveyor 48 via a bevel gear.

Regarding the power transmission system to the reaping section 3, the rotational power of the pulley rotating body 63 is transmitted to the front rotor shaft 28 by the sixth belt transmission mechanism 73. The sixth belt transmission mechanism 73 is provided with a reaping clutch 75 that transmits the rotational power of the pulley rotating body 63 to the front rotor shaft 28 intermittently as desired. The rotational power of the front rotor shaft 28 is transmitted to the reaping input shaft 38 by the first chain transmission mechanism 65. The rotation of the reaping input shaft 38 causes the conveyor 36 in the feeder house 35 to operate.

The rotational power of the reaping input shaft 38 is transmitted to a PF (platform) drive shaft 67 by a second chain transmission mechanism 66 . The rotational power of the PF drive shaft 67 is transmitted via the third chain transmission mechanism 68 to the PF auger shaft 37a that rotates the scraping auger 37. Further, the rotational power of the PF drive shaft 67 is transmitted via the seventh belt transmission mechanism 69 to the cutting blade drive shaft 32a that drives the cutting blade device 32. Further, the rotational power of the PF drive shaft 67 is transmitted to the reel shaft 34b that rotates the scraping reel 34 by a fourth chain transmission mechanism 76 including a reel counter shaft 70.

With such a configuration, the driving force of the engine 25 is transmitted to the reaping section 3. Then, the reaping clutch 75 is turned ON/OFF by operating a working clutch lever provided in the driving section 15, and power transmission to the reaping section 3 is interrupted or interrupted.

Regarding the power transmission system to the grain storage section 9, the rotational power of the second output shaft 25b is transmitted to the rotation shaft 11a of the lower discharge conveyor 11 by a power transmission mechanism including the grain tank intermediate shaft 77, and the rotational power of the second output shaft 25b is transmitted to the rotation shaft 11a of the lower discharge conveyor 11. The rotational power is transmitted to the rotating shaft 12a of the vertical conveyor 12 via a bevel gear. The rotational power of the rotating shaft 12a is transmitted to the rotating shaft 13a of the grain discharge conveyor 13 by a predetermined transmission mechanism. The grain storage section 9 includes a suction fan 78 having a suction fan shaft 78a and a compressor 79 having a compressor shaft 79a, which are driven by receiving the rotational power of the grain tank intermediate shaft 77.

As described above, in the combine harvester 1 according to the present embodiment, the grain culm cut by the cutting blade device 32 of the reaping part 3 is transported by the transport part 20, and the grain culm is transported by the transport part 20 to the threshing part 7 having the handling barrel shaft 41 in the handling chamber 7b. supply. The combine 1 has a power transmission structure to the handling cylinder 40 including a handling cylinder input shaft 59 that rotates upon receiving power transmitted from the engine 25, and a handling cylinder input shaft 59 that rotates from the handling cylinder input shaft 59 to the handling cylinder 40. A threshing transmission 60 having an intermediate shaft 125 for changing the rotational speed transmitted to the trunk shaft 41 and a handling trunk transmission case 80 are provided. The configuration for transmitting power to the handling cylinder 40 will be explained using FIGS. 5 to 14.

As shown in FIGS. 5 to 14, the handling barrel transmission case 80 is provided on the front side of the upper part of the front wall 81 that forms the handling chamber 7b. The front wall 81 is a vertical plate-shaped portion whose thickness direction is the front-rear direction, and is located in front of the handling barrel 40 . The front wall 81 has a front surface 81a that is a vertical plane. The front wall 81 supports the handling cylinder 40 via the handling cylinder shaft 41 together with a rear wall 82 (see FIGS. 1 and 3) of the handling chamber 7b located at the rear of the handling cylinder 40.

The front wall 81, together with the rear wall 82, the left side wall surface 83, and the right side wall surface 84, forms the handling chamber 7b, which is a rectangular space whose longitudinal direction is the front-rear direction in plan view. Each of the front, rear, left and right walls forming the handling chamber 7b is composed of a plurality of plate-like members and the like.

The handling cylinder transmission case 80 is a case that accommodates the handling cylinder input shaft 59, the threshing transmission device 60, and the handling cylinder shaft extension part 41a, which is the forward extension part of the handling cylinder shaft 41 (see FIG. 10). The handling cylinder transmission case 80 supports the handling cylinder input shaft 59, the intermediate shaft 125 of the threshing transmission 60, and the handling cylinder shaft extension part 41a. The handling cylinder shaft extension portion 41a is a front end portion of the handling cylinder shaft 41, and is a portion of the handling cylinder shaft 41 extending from the front wall 81 of the handling chamber 7b that accommodates the handling cylinder 40.

The handling cylinder transmission case 80 includes a main transmission case part 85 that accommodates the handling cylinder input shaft 59, and a transmission case part 86 that is provided integrally with the main transmission case part 85 and houses the threshing transmission 60. The transmission case portion 86 includes a portion that supports the intermediate shaft 125 of the threshing transmission 60. Further, the handling cylinder transmission case 80 has a vertical case part 87 as a case part provided integrally with the transmission case part 86, which accommodates the handling cylinder shaft extension part 41a.

The main transmission case portion 85 is a case portion that follows a substantially cylindrical outer shape with the center axis direction in the left-right direction. The main transmission case portion 85 has its left end located near the right side of the handling cylinder shaft extension portion 41a in the left-right direction, and its right end located at approximately the same position as the right side wall surface 84. . The main transmission case portion 85 has the handling cylinder input shaft 59 located at its central shaft portion.

The transmission case portion 86 is provided as a portion with an enlarged diameter relative to the main transmission case portion 85 at a position on the right side of the main transmission case portion 85 . The transmission case portion 86 is an eccentric flange-shaped case portion whose upper side protrudes relatively largely from the main transmission case portion 85 . The transmission case portion 86 has a substantially elliptical outer shape with the vertical direction as the longitudinal direction when viewed from the side.

The transmission case portion 86 has an upwardly protruding portion 86a that protrudes upward from the main transmission case portion 85 at a substantially upper half thereof. The transmission case section 86 separates the main transmission case section 85 from a left case section 85a, which is a portion to the left of the transmission case section 86 and forms the majority of the main transmission case section 85 in the left-right direction, and a left case section 85a, which is a portion to the left of the transmission case section 86 and forms the majority of the main transmission case section 85; It is also divided into a right case portion 85b, which is a right side portion.

The vertical case portion 87 is a case portion having a substantially cylindrical outer shape with the central axis direction in the front-rear direction. The vertical case portion 87 has a base case portion 87a forming the rear portion thereof, and an enlarged diameter case portion 87b forming the front portion of the vertical case portion 87. The enlarged diameter case portion 87b is a diameter enlarged portion relative to the base case portion 87a, and has a substantially semi-elliptic cylindrical outer shape. The vertical case portion 87 has a handling barrel shaft extension portion 41a located at its central shaft portion.

The handling trunk transmission case 80 is configured to have a substantially "L" shape in plan view, including a main transmission case section 85, a transmission case section 86, and a vertical case section 87. The handling cylinder input shaft 59, which is mainly housed and supported within the main transmission case section 85 and the transmission case section 86, has its axial direction in the left-right direction. The handling cylinder input shaft 59 has its axis center line located on a common horizontal plane with the axis center line of the handling cylinder shaft 41 that accommodates and supports the handling cylinder shaft extension part 41a in the vertical case part 87, It is located at the same height as the handling cylinder axis 41.

As described above, the handling barrel transmission case 80 provided in front of the handling chamber 7b is covered by the transmission case cover 89 and the left side cover 90 that form the exterior of the combine 1 (see FIGS. 1 and 3). The transmission case cover 89 and the left side cover 90, together with the front wall 81 and the like, form an accommodation space that accommodates the handling trunk transmission case 80 and the components provided around it.

The transmission case cover 89 is a cover that mainly covers the upper side and front side of the handling trunk transmission case 80. The left side cover 90 is a cover that covers the left side of the handling trunk transmission case 80, the left side of the front end of the handling chamber 7b, etc., and is provided so as to be detachable with one touch.

The structure for transmitting power to the handling cylinder transmission case 80 and the handling cylinder 40 will be described in detail with reference to FIGS. 10 to 13. FIG. 10 is a plan sectional view taken along line AA in FIG. 11. FIG. 11 is a cross-sectional view taken along line BB in FIG. FIG. 12 is a front sectional view taken along the line CC in FIG. 11. FIG. 13 is a sectional view taken along line DD in FIG. 12.

The main components of the handling trunk transmission case 80 include a first case member 91 that forms the vertical case part 87, a left case part 85a of the main transmission case part 85, and a left side part of the transmission case part 86. It has a second case member 92 and a third case member 93 that forms the right side portion of the transmission case portion 86 and the right case portion 85b of the main transmission case portion 85. These case members are, for example, cast products, and are fixed to each other with bolts or the like to constitute an integrated handling trunk transmission case 80.

The left side of the second case member 92 is fixed to the right side of the front part of the first case member 91. A flange portion 91a having a substantially hexagonal shape when viewed from the side is formed on the right side of the front portion of the first case member 91. A flange portion 92a having a substantially hexagonal shape when viewed from the side is formed on the left edge of the second case member 92. The first case member 91 and the second case member 92 are fixed to each other by a plurality of (ten in this embodiment) bolts 94 with the end faces of the flanges 91a and 92a aligned with each other.

The left side of the third case member 93 is fixed to the right side of the second case member 92. On the right side of the second case member 92, a shift left case portion 92b, which forms the left side portion of the shift case portion 86, is formed. The left shift case portion 92b is a flange-shaped portion that corresponds to the outer shape of the shift case portion 86 in a side view and has a substantially elliptical outer shape with the vertical direction as the longitudinal direction when viewed from the side. The left side portion of the third case member 93 serves as a shift right case portion 93a that constitutes most of the right side of the shift case portion 86. Like the left transmission case part 92b, the transmission right case part 93a has a substantially elliptical outer shape with the vertical direction as the longitudinal direction when viewed from the side. The second case member 92 and the third case member 93 are fixed to each other by a plurality of (nine in this embodiment) bolts 95 with the end surfaces of the left gear case part 92b and the right gear case part 93a aligned with each other. has been done.

As shown in FIG. 10, the handling barrel shaft extension portion 41a is rotatably supported by bearings 101 and 102 at two locations, front and rear, with respect to the first case member 91. The front bearing 101 is provided so as to fit into the flat front wall portion 91b of the first case member 91, and supports the front end portion of the handling barrel shaft extension portion 41a. The rear bearing 102 is provided approximately at the front and rear center of the first case member 91, and supports an approximately central portion of the handling barrel shaft extension portion 41a in the axial direction. The handling barrel shaft 41 is rotatably supported by the front wall 81 of the handling chamber 7b via a bearing 103 or the like.

The handling cylinder input shaft 59 is arranged in the lower part of the transmission case part 86 and in the main transmission case part 85, and is connected to the second case member 92 and the third case member 93 by bearings 105, 106, 107, and 108. It is rotatably supported at four locations. The left bearing 105 is provided at the left end of the second case member 92 and supports the left end of the handling cylinder input shaft 59. The two intermediate bearings 106 and 107 are provided on the right side of the second case member 92 and support the intermediate portion of the handling cylinder input shaft 59. The right bearing 108 is provided on the right side of the third case member 93 and supports the right side of the handling cylinder input shaft 59.

The right end of the handling cylinder input shaft 59 projects outward from the case from the right side of the third case member 93 toward the right, and serves as an external case protrusion 59a. A handling cylinder input pulley 110 is fixed to the case-external protrusion 59a of the handling cylinder input shaft 59. The handling cylinder input pulley 110 constitutes the third belt transmission mechanism 58 together with the pulley 111 pivotally supported by the threshing section input shaft 56 and the belt 112 wound around the handling cylinder input pulley 110 and the pulley 111 ( (See Figures 4 and 8).

The rotational power of the handling barrel input shaft 59 is transmitted to the handling barrel shaft 41 by the first bevel gear 115 and the second bevel gear 116 that mesh with each other. The first bevel gear 115 is fixed to the left end of the handling cylinder input shaft 59 located inside the enlarged diameter case portion 87b of the vertical case portion 87. The handling cylinder input shaft 59 is supported by a bearing 105 via a cylindrical portion 115a that forms the base of the first bevel gear 115. The second bevel gear 116 is fixed at the center of the handling cylinder shaft extension portion 41a in the axial direction. The handling cylinder shaft extension portion 41 a is supported by the bearing 102 via a cylindrical portion 116 a that forms the base of the second bevel gear 116 .

An oil filler port 117 for supplying oil into the vertical case part 87 is provided on the upper surface of the enlarged diameter case part 87b of the vertical case part 87. The oil filler port 117 is opened and closed by attaching and detaching a cap member 117b screwed into a screw hole 117a formed through the upper surface of the enlarged diameter case portion 87b.

Inside the handling barrel transmission case 80, oil passages 118 are formed at two locations, upper and lower, in the support portion of the lower side shaft portion 122. The oil passage 118 extends in the axial direction of the handling cylinder input shaft 59 (hereinafter referred to as "input shaft direction") so as to form a substantially semicircular recess in the inner peripheral surface of the second case member 92 when viewed in cross section. It is formed as a linear groove along the . The upper and lower oil passages 118 are provided so as to be vertically symmetrical about the axis of the handling cylinder input shaft 59 when viewed in the input shaft direction.

The oil passage 118 is formed throughout the second case member 92 in the left-right direction, and is open facing into the enlarged diameter case portion 87b on the left side, and opens into the transmission case portion 86 on the right side. It is open and open. With this configuration, oil supplied into the vertical case part 87 from the oil filler port 117 is routed from inside the left case part 85a of the main transmission case part 85 into the transmission case part 86 mainly through the lower oil passage 118. and is guided into the right case portion 85b. The upper oil passage 118 mainly functions as an air passage.

Further, a drain bolt 119 is provided at the lower part of the transmission case portion 86. The drain bolt 119 is provided at the lower end of the shift left case section 92b of the second case member 92 so as to be removably attached to the drain hole 92c communicating with the inside of the shift case section 86. Note that a drain bolt 120 is similarly provided at the lower end of the front surface of the vertical case portion 87 (see FIG. 9).

The threshing transmission 60 will be described with reference to FIGS. 10, 12, and 14. The handling cylinder input shaft 59 has two shaft parts, an upper side shaft part 121 that forms approximately the right half of the handling cylinder input shaft 59, and a lower side shaft part 122 that forms approximately the left half of the handling cylinder input shaft 59. It is divided into. The upper shaft portion 121 and the lower shaft portion 122 are arranged coaxially, and their end surfaces are closely opposed to each other at a position near the bearing 107 provided on the right side of the second case member 92. ing.

The upper shaft portion 121 is a shaft portion that is fixed to the handling cylinder input pulley 110 at the case external protrusion 59a and is supported by the bearing 108 at approximately the center in the axial direction. The lower shaft portion 122 is a shaft portion that is fixed to the first bevel gear 115 at its left end and is supported by bearings 105, 106, and 107.

The threshing transmission 60 meshes with an input shaft side gear provided on the handling cylinder input shaft 59, an intermediate shaft 125 provided parallel to the handling cylinder input shaft 59, and an input shaft side gear provided on the intermediate shaft 125. and an intermediate shaft side gear. The threshing transmission 60 has a first gear 131 and a fourth gear 134 as input shaft side gears, and a second gear 132 and a third gear 133 as intermediate shaft side gears.

As shown in FIG. 12, the intermediate shaft 125 is located above the handling cylinder input shaft 59, and is rotatably supported within the upper protrusion 86a of the transmission case portion 86 with the left-right direction as the axial direction. . The intermediate shaft 125 is located above the left side portion of the upper shaft portion 121 of the handling cylinder input shaft 59 located at the lower part of the transmission case portion 86.

The intermediate shaft 125 is supported between the left and right walls of the upper protrusion 86a. The intermediate shaft 125 has its right end supported by a bearing 126 fitted to the right wall of the upper protrusion 86a, and its left end supported by a bearing 126 fitted to the left wall of the upper protrusion 86a. It is supported by a bearing 127 that is fitted into the section.

A second gear 132 is fixed to the right side of the intermediate shaft 125, and a third gear 133 is fixed to the left side of the intermediate shaft 125. The second gear 132 and the third gear 133 are provided at positions close to the left and right side walls of the upper protrusion 86a, respectively, and rotate integrally with the intermediate shaft 125.

The first gear 131 is provided at a position corresponding to the second gear 132 on the upper shaft portion 121. The first gear 131 is supported so as to be rotatable relative to the upper shaft portion 121, and has a gear main body meshing with the second gear 132.

The fourth gear 134 is fixed to the right end of the lower shaft portion 122 and is provided so as not to rotate relative to the lower shaft portion 122 . The fourth gear 134 has a gear main body meshing with the third gear 133, and has a cylindrical support tube 134a on the left side of the gear main body into which the right end of the lower shaft portion 122 is inserted. have The handling cylinder input shaft 59 is supported by bearings 106 and 107 at the right end of the lower shaft portion 122 via a support cylinder portion 134a. The lower shaft portion 122 rotates integrally with the fourth gear 134.

A circular opening 134b communicating with the support tube 134a is formed in the center of the gear main body of the fourth gear 134. The upper shaft portion 121 has its left end inserted into the opening 134b, and is provided so as to be rotatable relative to the fourth gear 134.

In the upper shaft portion 121, a guide ring 135, which is an annular member, is fixed at a position between the first gear 131 and the fourth gear 134. The guide ring 135 forms an enlarged diameter portion in the upper shaft portion 121 and is a portion that rotates integrally with the upper shaft portion 121 . A spline groove is formed in the outer peripheral surface of the guide ring 135 along the input shaft direction.

A locking protrusion 131c is formed on the left side of the gear main body of the first gear 131. The locking protrusion 131c is an annular portion having approximately the same diameter as the guide ring 135, and contacts the guide ring 135 from the right side. An outer periphery uneven portion is formed on the outer periphery of the locking protrusion 131c and forms a groove continuous with the spline groove by aligning with the spline groove on the outer periphery of the guide ring 135.

On the other hand, a locking protrusion 134c is formed on the right side of the gear main body of the fourth gear 134. The locking protrusion 134c is an annular portion having approximately the same diameter as the guide ring 135, and contacts the guide ring 135 from the left side. An outer periphery uneven portion is formed on the outer periphery of the locking protrusion 134c, which aligns with the spline groove on the outer periphery of the guide ring 135 to form a groove continuous to the spline groove.

A speed change slider 137 as a moving body is provided outside the guide ring 135. The speed change slider 137 is an annular member, and has a concavo-convex portion on the inner circumferential side that is spline-fitted into a spline groove of the guide ring 135. In other words, the speed change slider 137 is fitted onto the guide ring 135 in such a manner that it cannot rotate relative to the guide ring 135 and is movable in the direction of the input shaft. The speed change slider 137 has a width dimension that is approximately the same as the width dimension (length in the input shaft direction) of the guide ring 135.

The speed change slider 137 has enlarged diameter portions 137b on both sides in the input shaft direction, and the portion between these enlarged diameter portions 137b is a slider intermediate portion 137c that forms an outer peripheral surface along the cylindrical surface (see FIG. 14). . The speed change slider 137 has an outer circumferential groove 137a formed by the enlarged diameter portions 137b on both sides and the slider intermediate portion 137c so as to have a substantially “U”-shaped cross-sectional shape when viewed in cross-section through the central axis.

The speed change slider 137 can be fitted to each of the locking protrusion 131c of the first gear 131 and the locking protrusion 134c of the fourth gear 134 in a manner similar to the manner in which it is fitted to the guide ring 135. ing. By fitting into the locking protrusion 131c of the first gear 131, the speed change slider 137 becomes engaged with the first gear 131 and becomes unable to rotate relative to the first gear 131. Similarly, the speed change slider 137 becomes engaged with the fourth gear 134 by fitting into the locking protrusion 134c of the fourth gear 134, and becomes unable to rotate relative to the fourth gear 134. .

By moving in the direction of the input shaft, the speed change slider 137 becomes engaged with the first gear 131 or the fourth gear 134 while maintaining the fitted state with the guide ring 135. That is, the shift slider 137 is located on the right side of its movement range, so that the left side portion is engaged with the guide ring 135 and the right side portion is engaged with the locking protrusion 131c of the first gear 131. state. On the other hand, the shift slider 137 is located on the left side of its movement range, so that the right side portion is engaged with the guide ring 135 and the left side portion is engaged with the locking protrusion 134c of the fourth gear 134. state.

In such a configuration, since the speed change slider 137 is located on the right side, the rotational power of the upper shaft portion 121 is transmitted to the first gear 131 via the guide ring 135 and the speed change slider 137. That is, the first gear 131 is in a state of rotating integrally with the upper shaft portion 121. As a result, the rotational power of the upper shaft portion 121 is shifted from the first gear 131 through the second gear 132, the intermediate shaft 125, the third gear 133, and the fourth gear 134, and is transmitted to the lower shaft portion 122. communicated. The rotational power of the lower shaft portion 122 is transmitted to the handling barrel shaft extension portion 41a via the first bevel gear 115 and the second bevel gear 116. Note that when the speed change slider 137 is located on the right side, the upper shaft portion 121 and the lower shaft portion 122 are in a state where they are edged off from each other.

In this manner, a state in which the speed change slider 137 is located on the right side and the rotational power of the upper shaft portion 121 is changed in speed and transmitted to the lower shaft portion 122 is referred to as a “first engaged state”. A first engaged state is shown in FIGS. 10, 12 and 14.

On the other hand, since the speed change slider 137 is located on the left side, the rotational power of the upper shaft portion 121 is transmitted to the fourth gear 134 via the guide ring 135 and the speed change slider 137. In other words, the fourth gear 134 rotates integrally with the upper shaft 121, and the lower shaft 122, which fixedly supports the fourth gear 134, rotates integrally with the upper shaft 121 (synchronized). (rotating state). Thereby, the rotational power of the upper shaft portion 121 is transmitted to the lower shaft portion 122 without being changed in speed.

In this manner, a state in which the speed change slider 137 is located on the left side and the rotational power of the upper shaft portion 121 is transmitted to the lower shaft portion 122 in a 1:1 relationship is referred to as a “second engaged state”. In addition, in FIG. 14, the second engagement state is shown by a chain double-dashed line.

Regarding the first engaged state, the first gear 131 has a smaller diameter than the second gear 132 and functions as a pinion with respect to the second gear 132. The third gear 133 has a smaller diameter than the second gear 132 and the fourth gear 134, and functions as a pinion with respect to the fourth gear 134. For example, the number of teeth of the first gear 131 and the third gear 133 is 19, and the number of teeth of the second gear 132 and the fourth gear 134 is 28.

Therefore, in the first engaged state, the rotation of the upper shaft portion 121 is reduced in speed and transmitted to the intermediate shaft 125 via the first gear 131 and the second gear 132, and the rotation of the intermediate shaft 125 is transmitted to the intermediate shaft 125 through the first gear 131 and the second gear 132. The speed is reduced and transmitted to the lower shaft portion 122 via the gear 133 and the fourth gear 134 . On the other hand, in the second engaged state, the rotation of the upper shaft portion 121 is transmitted to the lower shaft portion 122 without being decelerated, and these shaft portions rotate integrally at a constant speed.

In this way, in the threshing transmission 60 of this embodiment, the first engaged state in which the speed change slider 137 is located on the right side is such that the rotational power input to the upper shaft portion 121 is decelerated and the handling barrel shaft extends. This is a low speed state that is transmitted to the section 41a. On the other hand, the second engaged state in which the speed change slider 137 is located on the left side is a high-speed state in which the rotational power input to the upper shaft portion 121 is transmitted to the handling barrel shaft extension portion 41a without being changed in speed. Become. Note that the number of teeth of each gear that constitutes the threshing transmission 60, the reduction ratio between the gears, etc. are not limited to the configuration of this embodiment.

As described above, the threshing transmission device 60 is configured to be able to change the rotation speed of the rotational power input to the handling drum shaft 41 in two steps by using the movement operation of the speed change slider 137 as a speed change operation. A configuration for performing a speed change operation of the threshing transmission device 60 will be described later.

In the structure for transmitting power to the handling cylinder 40 having the above-described configuration, the support structure of the handling cylinder transmission case 80 will be explained. The handling trunk transmission case 80 is supported by the front wall 81 of the threshing section 7 and the conveying section 20. In this embodiment, the handling cylinder transmission case 80 is supported against the front wall 81 of the threshing section 7 and has a lower support section that is a support section for the upper surface of the conveyance section 20. In other words, the handling trunk transmission case 80 is fixedly supported on the main body side of the combine 1 by two supporting parts: a rear supporting part for the front wall 81 and a lower supporting part for the upper surface of the conveying part 20. There is.

The rear support part which is the first support part of the handling cylinder transmission case 80 will be explained. The handling trunk transmission case 80 has a plate-shaped flange part 141, which serves as a rear support part, at the rear end of the vertical case part 87 and has a substantially square outer shape when viewed from the front. The flange portion 141 is provided on the rear side of the base case portion 87a of the vertical case portion 87, and is formed in a brim shape with respect to the base case portion 87a. The flange portion 141 has a size such that substantially the entire portion overlaps the enlarged diameter case portion 87b when viewed from the front, and the left upper and lower corners protrude from the enlarged diameter case portion 87b when viewed from the front.

The handling trunk transmission case 80 is fixed to the front wall 81 by fixing bolts 142 passing through the flange portion 141. The fixing bolt 142 passes through holes formed in the flange portion 141 and the front wall 81 from the front side, and is screwed into a screw hole 143 provided on the rear surface 81b side of the front wall 81. The screw hole portion 143 is a fastening portion having a screw hole into which the fixing bolt 142 is screwed, and is provided by, for example, fixing a nut-shaped member to the rear surface 81b of the front wall 81 by welding or the like.

In this way, the handling trunk transmission case 80 is fastened and fixed to the front wall 81 by the fixing bolts 142 and the screw holes 143 at the flange portion 141. Note that instead of the screw hole portion 143, a fastening member such as a nut that is threadedly engaged with the fixing bolt 142 may be used.

The fixing portions by the fixing bolts 142 are provided at the four corners of the flange portion 141, which has a substantially square shape when viewed from the front. That is, the flange portion 141 is fixed to the front wall 81 with four fixing bolts 142. In the support portion on the rear side of the handling drum transmission case 80 , the front surface 81 a of the front wall 81 becomes a contact surface for the flange portion 141 and serves as a support surface for the handling drum transmission case 80 .

The lower support part which is the second support part of the handling cylinder transmission case 80 will be explained. The handling trunk transmission case 80 has a support leg part 150 that forms a lower support part on the lower side of the transmission case part 86. The support leg portion 150 is a base portion having an outer shape of an isosceles triangular lower portion when viewed from the side.

The support leg portion 150 is a portion formed integrally with the transmission case portion 86 of the handling trunk transmission case 80. That is, the transmission case section 86 has a case main body section 86A that forms a housing space for accommodating the threshing transmission device 60, and has support leg sections 150 formed integrally with the case main body section 86A. In this embodiment, the support leg portion 150 is provided as a part of the third case member 93.

The support leg section 150 has a right side section 151, a left side section 152, and a bottom section 153. The right side part 151 and the left side part 152 are parts formed to extend downward from the lower part of the case main body part 86A, overlap each other in a side view, and form the outer shape of the support leg part 150 in a side view. The bottom surface portion 153 is a planar surface portion that connects the lower ends of the right side surface portion 151 and the left side surface portion 152, and has a rectangular outer shape whose longitudinal direction is the front-rear direction in a plan view. I am doing it.

The right side portion 151 is a vertical plate-shaped portion. On the other hand, as shown in FIG. 13, the left side surface portion 152 has a front oblique side portion 152a, a rear oblique side portion 152b, and a center side portion 152c. Therefore, in the left side part 152, a front opening 152d is formed by the front oblique side part 152a and the central side part 152c together with the lower part of the case main body part 86A of the transmission case part 86, and the central side part 152c and the rear oblique side part 152b forms a rear opening 152e.

An intermediate wall portion 155 whose thickness direction is in the front-rear direction is formed between the right side portion 151 and the left side portion 152 at the front-rear center portion on the bottom portion 153 . Further, a rib portion 156 having a substantially triangular shape when viewed from the front is formed between the right outer surface of the right side portion 151 and the right cylindrical portion of the third case member 93.

The handling cylinder transmission case 80 is supported on the upper surface of the transport section 20 . That is, the handling trunk transmission case 80 is fixed to the right upper surface part 161 that constitutes the upper surface part of the conveyance section 20 by a fixing bolt 160 that passes through the bottom surface part 153 of the support leg part 150. The right upper surface portion 161 is the upper surface portion of the right support arm member 162 horizontally arranged forward from the right side portion of the front wall 81 .

The right upper surface portion 161 is a horizontal plate-shaped portion and is located below the transmission case portion 86 of the handling trunk transmission case 80. The right upper surface portion 161 has an upper surface 161a that is a horizontal plane. In plan view, the right side upper surface portion 161 has a substantially trapezoidal shape with the left and right outer sides (right side) being hypotenuses and the width gradually becoming narrower from the rear side to the front side.

The right support arm member 162 is installed between a right front wall forming member 163 that constitutes the right side portion of the front wall 81 and a right front support column 164 provided in front of the right front wall forming member 163. The right support arm member 162, the right front wall forming member 163, and the right front support column 164 are used as frame members that form the front rotor chamber 29 on the right side of the front rotor 26.

The right front wall forming member 163 is a columnar member erected on the fuselage frame 6, and its upper portion forms the upper right portion of the front wall 81. The right front support column 164 is erected on the body frame 6 at a lower height than the right front wall forming member 163, and is located between the front rotor 26 and the reaping input shaft 38 in the front-rear direction. The right front support column 164 is located near the right side of the feeder house 35 in the left-right direction.

The fixing bolt 160 that fixes the support leg part 150 passes through the holes formed in the bottom part 153 and the right upper part 161 from above, and into the screw hole 165 provided in the lower face 161b of the right upper part 161. It is screwed in. The screw hole portion 165 is a fastening portion having a screw hole into which the fixing bolt 160 is screwed, and is provided by, for example, fixing a nut-like member to the lower surface 161b of the right upper surface portion 161 by welding or the like.

In this manner, the support leg portion 150 is fastened and fixed to the right upper surface portion 161 at the bottom surface portion 153 by the fixing bolt 160 and the screw hole portion 165. Note that instead of the screw hole portion 165, a fastening member such as a nut that is threadedly engaged with the fixing bolt 160 may be used.

Fixing portions using fixing bolts 160 are provided at both front and rear ends of the bottom surface portion 153. That is, the bottom surface portion 153 is fixed to the right upper surface portion 161 by two fixing bolts 160. In the lower support section of the handling trunk transmission case 80, the upper surface 161a of the right upper surface section 161 is a contact surface for the bottom surface section 153 and serves as a support surface for the support leg section 150.

As described above, the handling trunk transmission case 80 is fixed to the front wall 81 of the threshing section 7 and the right upper surface section 161 which is the upper surface section of the conveyance section 20 at the upper front position of the threshing section 7. Supported. The transmission case section 86 has a support leg section 150 that supports the handling trunk transmission case 80 with respect to the right upper surface section 161, as a part formed integrally with the case main body section 86A.

A configuration for performing a speed change operation of the threshing transmission device 60 will be described. A speed change operation of the threshing transmission device 60 is performed by operating a speed change lever 170 extending from the handling barrel transmission case 80. The threshing transmission 60 has a speed change lever 170 extending from the speed change case portion 86 toward one side (left side) in the left-right direction of the machine body. That is, by operating the speed change lever 170, the speed change slider 137 of the threshing transmission device 60 is moved, and the first engagement state and the second engagement state are switched. The shift lever 170 is connected to the shift slider 137 via a shift fork 171 and a shift support shaft 172.

The variable speed fork 171 is a plate-shaped member whose plate thickness direction is the input shaft direction (left-right direction), and includes a bifurcated fork body portion 171a and a fork extension portion extending forward from the fork body portion 171a. 171b (see FIG. 14). The speed change fork 171 is engaged with the speed change slider 137 with the fork body portion 171a fitted into the outer circumferential groove 137a of the speed change slider 137. As the speed change fork 171 moves in the input shaft direction, the speed change slider 137 moves in the input shaft direction together with the speed change fork 171.

The fork main body portion 171a is a semicircular concave portion when viewed in the direction of the input shaft, and is fitted into the outer circumferential groove 137a of the speed change slider 137 with the open side facing the rear side. That is, the semicircular concave portion of the fork body portion 171a matches the curved shape of the outer peripheral surface of the slider intermediate portion 137c of the speed change slider 137, and the fork body portion 171a sandwiches the slider intermediate portion 137c. It fits into the speed change slider 137. The width of the outer circumferential groove 137a, that is, the interval between the left and right expanded diameter portions 137b, is slightly larger than the plate thickness of the variable speed fork 171, and there is a gap between the fork body portion 171a and the expanded diameter portion 137b. There is. Thereby, the speed change fork 171 can move relative to the speed change slider 137 in the input shaft direction by the amount of the gap.

The fork extension portion 171b has a substantially triangular shape with the front side being the top side when viewed in the direction of the input shaft. A speed change support shaft 172 passes through the front end of the fork extension portion 171b.

The speed change fork 171 is provided so as to be rotatable relative to the speed change slider 137. With respect to the speed change slider 137 that rotates with the rotation of the handling cylinder input shaft 59, the speed change fork 171 is supported by the speed change slider 137 and the speed change support shaft 172, and maintains its posture in the rotation direction (orientation). (so as not to change).

During the rotational movement of the speed change slider 137, the inner circumferential surface of the recessed portion of the fork main body portion 171a becomes a sliding surface with respect to the outer circumferential surface of the slider intermediate portion 137c. Furthermore, when the speed change slider 137 moves in the input shaft direction as the speed change fork 171 moves, the left and right side surfaces (plate surfaces) of the fork body portion 171a become contact surfaces with the inner surface of the enlarged diameter portion 137b.

The speed change support shaft 172 is a rod-shaped member having a circular cross-sectional shape, and is provided at a position above and in front of the handling cylinder input shaft 59 with the input shaft direction as the axial direction. The speed change support shaft 172 is fixed to the speed change fork 171 by welding or the like, passing through a hole 171c formed at the front end of the fork extension 171b.

The speed change support shaft 172 is supported by the speed change case portion 86 and is provided so as to be movable in the axial direction at a predetermined position when viewed in the direction of the input shaft. The speed change support shaft 172 is located at the front of the case main body 86A of the speed change case 86, approximately at the center in the vertical direction.

As shown in FIG. 14, the right side portion of the shift support shaft 172 is inserted into a guide hole 175 formed in the shift right case portion 93a forming the case main body portion 86A. The guide hole portion 175 is a hole portion with the left side as the opening side, and has a hole diameter that is approximately the same as the outer diameter of the speed change support shaft 172. When the shift support shaft 172 moves in the axial direction, the inner circumferential surface of the guide hole 175 becomes a sliding surface with respect to the outer circumferential surface 172a of the shift support shaft 172.

The left side portion of the shift support shaft 172 is supported by a support hole 176 formed in the shift left case portion 92b forming the case main body portion 86A. The speed change support shaft 172 is supported so as to be movable in the axial direction in the support hole 176 via a shaft supporting member such as a collar 177 which is a cylindrical member.

The speed change support shaft 172 has the speed change fork 171 fixed to a shaft portion between the insertion portion into the guide hole portion 175 and the support portion into the support hole portion 176. That is, the speed change fork 171 is supported with respect to the speed change support shaft 172 at a position where it does not interfere with the speed change case portion 86 within the movement range of the speed change support shaft 172 in the axial direction.

The left end of the speed change support shaft 172 projects outside the speed change case portion 86 through the support hole 176, and the projecting portion is defined as a projecting shaft portion 172b. A speed change lever 170 is fixed to the protruding shaft portion 172b.

The shift lever 170 includes a lever main body 181 and a support plate 182 provided at the base end of the lever main body 181. The shift lever 170 has a support plate portion 182 fixed to a protruding shaft portion 172b of the shift support shaft 172, and a lever body portion 181 extending leftward from the support plate portion 182. That is, the shift lever 170 extends from the support portion for the shift support shaft 172 toward the left side of the body.

Most of the lever main body part 181 except for the tip side (left side) part is a straight part 181a that is a straight rod-shaped part extending in the left-right direction. Substantially the entire lever body portion 181 is a round bar-shaped portion having a circular cross-sectional shape. A support plate portion 182 is provided horizontally behind the base end (right end) of the straight portion 181a. The support plate portion 182 is provided by fixing a plate-shaped member to the straight portion 181a by welding or the like.

The support plate portion 182 has a substantially triangular or trapezoidal outer shape in plan view, and is fixed to the protruding shaft portion 172b of the speed change support shaft 172 at the rear end. The support plate portion 182 is fixed to the protruding shaft portion 172b by a fixing pin 183. The fixing pin 183 vertically passes through holes formed in the support plate part 182 and the protruding shaft part 172b from above, and is fixed by a locking member 184 such as a retaining ring (see FIG. 13).

As described above, in the combine harvester 1, as an operation part of the threshing transmission 60, a transmission lever is provided which extends from the transmission case part 86 and extends toward the left side, which is the side opposite to the driving part 15 side in the left-right direction of the machine. It has 170. The lever main body part 181 of the gear shift lever 170 extends leftward from the front part of the case main body part 86A, passes in front of the left case part 85a of the main transmission case part 85 and the vertical case part 87, and is connected to the front wall 81. It extends to the left edge.

A grip portion 181b is provided at the tip of the lever body portion 181. The grip portion 181b is a rod-shaped portion bent downward with respect to the straight portion 181a so as to form a substantially right-angled corner with the straight portion 181a. By grasping the grip portion 181b and pushing and pulling the shift lever 170 in the left and right directions (see arrow A1 in FIG. 14), the shift lever 170, shift support shaft 172, shift fork 171, and shift slider 137 are integrated. The threshing transmission device 60 is operated.

As shown in FIG. 14, a ball detent mechanism 190, which is a positioning mechanism, is provided for the speed change support shaft 172. The ball detent mechanism 190 holds the speed change support shaft 172 at a position corresponding to the first engaged state and the second engaged state as the threshing transmission 60 changes speed. The ball detent mechanism 190 positions the speed change support shaft 172 by fitting a ball 193 biased by a coil spring 192 into one of two outer circumferential grooves 191 formed in the speed change support shaft 172. .

The outer circumferential groove 191 is a reduced diameter portion that forms a semicircular recess with respect to the outer circumferential surface 172a of the speed change support shaft 172 in a longitudinal cross-sectional view passing through the axis of the speed change support shaft 172. Of the two outer circumferential grooves 191, one outer circumferential groove 191a located on the left side is formed at a position corresponding to the position of the speed change support shaft 172 in the first engaged state, and is located near the right end. The other outer circumferential groove 191b is formed at a position corresponding to the position of the speed change support shaft 172 in the second engaged state.

The coil spring 192 is inserted into a support hole 195 formed in the front side of the transmission support shaft 172 in the transmission right case portion 93a so as to penetrate in the front-rear direction. The coil spring 192 is supported by a support bolt 196 screwed into the support hole 195, and is oriented such that its expansion and contraction direction is orthogonal to the axial direction of the speed change support shaft 172 (in this embodiment, the front-rear direction). It is provided.

The support hole portion 195 is formed to penetrate in the front-rear direction within the boss portion 93b formed on the front wall portion of the transmission right case portion 93a so as to communicate with the guide hole portion 175 from the front side. The front part of the support hole 195 has a threaded surface, and the support bolt 196 is screwed into the support hole 195 and supports the coil spring 192 at its tip end.

Ball 193 is sandwiched between coil spring 192 and speed change support shaft 172. The ball 193 is biased toward the speed change support shaft 172 by the coil spring 192, faces into the guide hole 175, partially protrudes, and fits into the outer circumferential groove 191 of the speed change support shaft 172.

In the above configuration, the ball 193 is pushed by the shift support shaft 172 from the state where it is fitted in one of the outer circumferential grooves 191 as the shift support shaft 172 moves by operating the shift lever 170, and the coil spring 192 is pushed by the shift support shaft 172. It sinks into the support hole 195 against the urging force of , and comes into contact with the outer circumferential surface 172a of the speed change support shaft 172. That is, as the shift support shaft 172 moves, the engagement of the ball 193 with the shift support shaft 172 is automatically released. Then, as the shift support shaft 172 moves, one of the outer circumferential grooves 191 reaches a position corresponding to the ball 193, and the ball 193 is automatically fitted into the outer circumferential groove 191 by the urging force of the coil spring 192, and the shift support shaft 172 is moved. The support shaft 172 is now positioned.

The speed change lever 170 is fixedly supported on the main unit side of the combine harvester 1 near the grip portion 181b thereof. That is, the combine harvester 1 includes a lever support section 200 that is provided on the conveyance section 20 and supports the speed change lever 170, and a lever fixing section 220 that is provided on the lever support section 200 and fixes the speed change lever 170.

The lever support section 200 is provided on the left upper surface section 201 that constitutes the upper surface section of the conveyance section 20 . The left upper surface portion 201 is provided to have a substantially bilaterally symmetrical configuration with the right upper surface portion 161 that supports the transmission case portion 86 . The left upper surface portion 201 is the upper surface portion of the left support arm member 202 that is disposed horizontally toward the front from the left side portion of the front wall 81 .

The left upper surface portion 201 is a horizontal plate-shaped portion and is located below the left end of the gear shift lever 170. The left upper surface portion 201 has an upper surface 201a that is a horizontal plane. The left upper surface portion 201 has a substantially trapezoidal shape in plan view, with the left and right outer sides (left side) being oblique sides, and the width gradually becoming narrower from the rear side to the front side.

The left support arm member 202 is installed between a left front wall forming member 203 that constitutes the left side portion of the front wall 81 and a left front support column 204 provided in front of the left front wall forming member 203. The left support arm member 202, the left front wall forming member 203, and the left front support column 204 are used as frame members that form the front rotor chamber 29 on the left side of the front rotor 26.

The left front wall forming member 203 is a columnar member erected on the fuselage frame 6, and its upper portion forms the upper left portion of the front wall 81. The left front support column 204 is erected on the body frame 6 at a lower height than the left front wall forming member 203, and is located between the front rotor 26 and the reaping input shaft 38 in the front-rear direction. The left front support column 204 is located near the left side of the feeder house 35 in the left-right direction.

The lever support section 200 includes a support base section 210 provided on the left upper surface section 201 and a hook section 218 provided on the support base section 210.

The support base portion 210 has four surface portions: a bottom surface portion 211 , a left side surface portion 212 , a front surface portion 213 , and a top surface portion 214 . The bottom surface portion 211 is a rectangular plate-shaped portion whose longitudinal direction is the front-rear direction when viewed from above, and forms the bottom portion of the support base portion 210 . The left side portion 212 is a vertical plate-like portion, and has a substantially trapezoidal shape with a vertical front side when viewed from the side.

The front part 213 is a vertical plate-like part, and has a substantially trapezoidal shape that is vertically long and vertically long with the left side being vertical when viewed from the front. The upper surface portion 214 is a horizontal plate-shaped portion having a substantially triangular shape in plan view, and is provided in such a manner that it is constructed between the upper sides of the left side portion 212 and the front portion 213, respectively. The support base portion 210 is made of, for example, a member made of a single steel plate with the left side portion 212 as a base and the other side portions bent.

A multifaceted member forming the support base portion 210 is fixed to the left upper surface portion 201 by a fixing bolt 216 passing through the bottom surface portion 211. The fixing bolt 216 passes through holes formed in the bottom surface part 211 and the left upper surface part 201 from above, and is screwed into a screw hole 217 provided on the lower surface 201b side of the left upper surface part 201. The screw hole portion 217 is a fastening portion having a screw hole into which the fixing bolt 216 is screwed, and is provided by, for example, fixing a nut-like member to the lower surface 201b of the left upper surface portion 201 by welding or the like.

In this way, the multifaceted member forming the support base portion 210 is fastened and fixed to the left upper surface portion 201 at the bottom surface portion 211 by the fixing bolt 216 and the screw hole portion 217. Note that instead of the screw hole portion 217, a fastening member such as a nut that is threadedly engaged with the fixing bolt 216 may be used.

Fixing parts by fixing bolts 216 are provided on both front and rear sides of the bottom part 211. That is, the bottom surface portion 211 is fixed to the left upper surface portion 201 by two fixing bolts 216.

The hook portion 218 is a support portion that supports the lever body portion 181 extending leftward from below so as to maintain its horizontal state and to be movable in the left-right direction. The hook portion 218 is provided by fixing a rod-shaped member bent in a substantially “L” shape to the upper part of the left side surface portion 212 of the support base portion 210 by welding or the like.

The hook portion 218 has one side as a horizontal shaft portion 218a that runs in the front-rear direction, and the other side as a vertical shaft portion 218b that runs in the up-down direction. The hook portion 218 has a horizontal shaft portion 218a as a fixing portion to the left side surface portion 212, a right-angled corner formed by both shaft portions is located forward of the front surface portion 213 of the support base portion 210, and a front end of the horizontal shaft portion 218a. A vertical shaft portion 218b is erected upward from the portion. The lever main body part 181 is located between the front part 213 and the vertical shaft part 218b.

According to the lever support section 200 configured as described above, the lever main body section 181 is supported from below by the horizontal shaft section 218a of the hook section 218, and its forward and backward movement is restricted by the front section 213 and the vertical shaft section 218b. It is supported in a state where movement in the left and right direction is allowed. Note that the shape of the hook portion 218 is not limited to this embodiment, and may be, for example, an annular portion when viewed from the side. That is, the hook portion 218 may be any hook portion as long as it can restrict the back and forth movement of the lever body portion 181 together with the support base portion 210 while allowing the lever body portion 181 to move in the left and right direction.

As shown in FIGS. 15 and 16, the lever fixing part 220 is provided on the lever support part 200 and functions as a lever movement restricting part that restricts movement of the shift lever 170 at least in the left-right direction, which is the shift operation direction. In this embodiment, the lever fixing part 220 is a part that fixes the lever body part 181 to the front part 213 of the support base part 210.

The lever fixing section 220 fixes the lever body section 181 to the front surface section 213 of the support base section 210 using the lever fixing member 230 . The lever fixing member 230 is a so-called bolt with a handle, and has a handle portion 230a having a plurality of recesses on its outer periphery, and a shaft-shaped bolt portion 230b having a male threaded portion.

The lever fixing member 230 is configured by passing a bolt part 230b from the front side through a locking hole 181c formed in the lever body part 181 and a hole 213a formed in the front part 213, and then inserting a screw provided on the back side of the front part 213. It is screwed into the hole 231. The screw hole portion 231 is a fastening portion having a screw hole into which the bolt portion 230b is screwed, and is provided by, for example, fixing a nut-like member to the back surface of the front portion 213 by welding or the like.

The lever main body portion 181 has a plate-like portion 181d in which the locking hole 181c is formed with the thickness direction extending in the front-rear direction. The plate-shaped portion 181d has a thickness smaller than the outer diameter of the round bar-shaped portion of the straight portion 181a, and a vertical dimension larger than the outer diameter. The plate-like portion 181d is a flat portion of the straight portion 181a that extends upward and downward relative to the shaft-like portion.

In the lever fixing part 220, by rotating and tightening the lever fixing member 230, the plate-shaped part 181d is held between the handle part 230a of the lever fixing member 230 and the front part 213 of the support base part 210. , the lever body portion 181 is supported and fixed. The lever fixing member 230 is attached to and detached from the lever body 181 and the support base 210 by manual rotation using the handle 230a as a grip.

A hole 213a and a screw hole 231 are provided in the front surface 213 of the support base 210 at two locations spaced apart from each other by a predetermined distance in the left-right direction, as attachment portions for the lever fixing member 230. The hole 213a and the screw hole 231 on the right side are attachment parts corresponding to the first engagement state (low speed state) of the threshing transmission 60, and the hole 213a and the screw hole 231 on the left side are the attachment parts corresponding to the first engagement state (low speed state) of the threshing transmission 60. 60, which corresponds to the second engagement state (high speed state). Note that in this embodiment, two attachment portions for the lever fixing member 230 are provided on the support base portion 210 side, one for low speed and one for high speed. For example, the attachment portion on the support base portion 210 side It may be configured such that two locking holes 181c are formed on the lever body 181 side, one for low speed and one for high speed.

In the above configuration, when changing the speed of the threshing transmission 60, first remove the left side cover 90 that covers the left side of the handling cylinder transmission case 80, so that the lever fixing part 220 can be accessed. . When changing the speed of the threshing transmission 60, with the lever fixing member 230 removed, the grip portion 181b is gripped and the speed change lever 170 is moved in the left and right direction, thereby changing the speed between the first engagement state and the second engagement state. The engagement state is switched.

Here, when changing from the first engagement state to the second engagement state, that is, when switching from a low speed state to a high speed state, the shift lever 170 is pulled to the left as a shift operation. On the other hand, when changing from the second engagement state to the first engagement state, that is, when switching from a high speed state to a low speed state, the shift lever 170 is pushed to the right as a shift operation.

After switching between the first engagement state and the second engagement state, the lever body 181 of the gear shift lever 170 is supported and fixed at the left side of the aircraft body by attaching and tightening the lever fixing member 230. state. Further, the shift support shaft 172 that moves the shift lever 170 integrally is subjected to a positioning action by the ball detent mechanism 190 in each of the first engaged state and the second engaged state. The ball detent mechanism 190 allows the operator to sense that the shift lever 170 has reached the position corresponding to each engagement state to be changed, as a feeling of operation accompanying the engagement of the ball 193 with the shift support shaft 172. be able to.

The speed change operation of the threshing transmission device 60 as described above is performed in a state where the rotation of the handling cylinder input shaft 59 is stopped, such as when the engine 25 is stopped, for example. The rotational speed of the handling drum 40 is switched by the threshing transmission 60 in accordance with, for example, the type and amount of crops to be harvested, in order to perform an efficient threshing process in the threshing section 7. For example, a high speed state in which the handling cylinder 40 rotates at a relatively high speed is used for harvesting rice or wheat, and a low speed state in which the handling cylinder 40 rotates at a relatively low speed is used for harvesting soybeans.

According to the combine harvester 1 according to the present embodiment having the above configuration, the burden on the front wall 81 of the threshing section 7 can be reduced, and the handling trunk transmission case 80 can be firmly supported. Rotational power can be stably transmitted to the handling cylinder 40, which involves a speed change operation.

In the combine harvester 1 of this embodiment, the handling trunk transmission case 80 is configured to have a main transmission case part 85 and a transmission case part 86, and a support part on the rear side for the front wall 81 of the handling chamber 7b, and a conveying part 20. and a lower support portion for the upper surface portion of the device. In other words, the handling cylinder transmission case 80 is supported by both the vertical surface by the front wall 81 and the horizontal surface by the upper surface of the transport section 20.

With such a configuration, the supporting load of the handling barrel transmission case 80 can be shared by the plurality of support parts, so that the load acting on the front wall 81 of the handling chamber 7b can be reduced. In particular, since the handling cylinder transmission case 80 includes a transmission case part 86 that houses the threshing transmission 60, it is relatively large and heavy compared to the configuration of the handling cylinder transmission case without the threshing transmission 60. becomes. Therefore, according to the support structure of the handling barrel transmission case 80 according to the present embodiment, the burden on the front wall 81 of the handling chamber 7b can be effectively reduced.

As a result, problems such as deformation of the front wall 81 and inclination of the handling cylinder transmission case 80 can be suppressed, and rotational power is transmitted to the handling cylinder 40 by the power transmission mechanism provided in the handling cylinder transmission case 80. can be performed stably, and the speed of the handling cylinder 40 can be reliably changed by the threshing transmission 60. In particular, when the input to/from the handling cylinder 40 is turned on/off, the load on the front wall 81 becomes large due to the vibration of the handling cylinder transmission case 80. According to the support structure of the case 80, it becomes possible to firmly and stably support the handling trunk transmission case 80.

Furthermore, in the handling trunk transmission case 80 according to the present embodiment, the transmission case section 86 includes a case main body section 86A and a support leg section 150 formed integrally with the case main body section 86A.

According to such a configuration, a part of the handling drum transmission case 80 can be used as a lower support portion, so that the supporting structure of the handling drum transmission case 80 can be made simple. Thereby, it is possible to avoid an increase in the number of parts and the number of assembly steps when providing the lower support portion of the handling cylinder transmission case 80.

In addition, the combine harvester 1 according to the present embodiment has a shift lever 170 that is extended from the shift case section 86 and extends toward the left, which is the opposite side to the driving section 15, as the operation section of the threshing transmission device 60. It also has a lever support section 200 provided on the upper surface of the conveyance section 20, and a lever fixing section 220 provided on the lever support section 200.

According to such a configuration, the operability of the speed change operation of the handling cylinder 40 can be improved. That is, since the gear shift operation of the handling barrel 40 can be performed by a simple operation of pushing and pulling the gear shift lever 170 from a position away from the gear shift case part 86 on the side (left side) of the main body of the combine harvester 1, Good operability can be obtained. Further, by removing the left side cover 90, which can be attached and detached with one touch, the shift lever 170 can be operated, so that the shift operation can be easily performed.

Further, a configuration for changing the speed of the handling cylinder 40 is provided by connecting a speed change lever 170 to the speed change slider 137 of the threshing transmission 60 via a speed change fork 171 and a speed change support shaft 172, and manually operating the speed change lever 170. can be realized with an inexpensive and simple configuration. Moreover, since the handling trunk transmission case 80 can be supported firmly and stably, a stable operational feeling can be obtained when pushing and pulling the gear shift lever 170 extending from the handling trunk transmission case 80.

In the threshing transmission 60 according to the present embodiment, the upper shaft portion 121 to which the handling cylinder input pulley 110 is attached and the lower shaft portion 122 to which the second bevel gear 116 is attached are coaxially arranged. ing. That is, the input shaft portion and the output shaft portion of the threshing transmission 60 are coaxially arranged.

According to such a configuration, the position of the input shaft portion and the position of the output shaft portion are made common between a configuration including the threshing transmission 60 as in this embodiment and a configuration not including the threshing transmission 60. be able to. As a result, the handling barrel transmission case 80 according to the present embodiment can be applied to an existing configuration that does not include the threshing transmission 60, for example, without changing the positions of the handling barrel input pulley 110, the second bevel gear 116, etc. becomes possible.

In addition, in the handling cylinder transmission case 80 according to the present embodiment, the intermediate shaft 125 that constitutes the threshing transmission 60 is provided at a position above the handling cylinder input shaft 59, and the transmission case portion 86 It is provided as a vertically elongated case part whose longitudinal direction is the vertical direction.

According to such a configuration, the handling trunk transmission case 80 can be configured compactly in the front-rear direction. Thereby, it is possible to easily prevent the handling cylinder transmission case 80 from interfering with the transmission case cover 89. Furthermore, compared to, for example, a configuration in which the intermediate shaft 125 is disposed in front of the handling cylinder input shaft 59, stress acting on the support portion of the handling cylinder transmission case 80, particularly the lower support portion, can be reduced. Therefore, it is possible to make the lower support portion of the handling cylinder transmission case 80 compact.

Further, according to the configuration having the lower support part as the support part of the handling cylinder transmission case 80, the support strength of the handling cylinder transmission case 80 against the tension that the handling cylinder input shaft 59 receives from the belt 112 via the handling cylinder input pulley 110 is reduced. Can be easily secured.

That is, as shown in FIG. 8, the pulley 111, which receives the winding of the belt 112 together with the handling cylinder input pulley 110, is located at the lower rear with respect to the handling cylinder input pulley 110, and In this case, the downward tension mainly acts as the tension caused by the belt 112. The tension acting downwardly on the handling barrel input pulley 110 in this manner is supported at the lower support portion of the handling barrel transmission case 80 by the support leg portion 150 via the handling barrel input shaft 59. In other words, the support leg portion 150 supports the right side upper surface portion 161 by being stretched against the tensile force exerted downwardly on the handling cylinder input pulley 110 by the belt 112.

As a result, the lower support part that supports the handling cylinder transmission case 80 from below can receive the downward tension of the belt 112 on the handling cylinder input pulley 110, so that the handling cylinder transmission case 80 can be efficiently supported. becomes possible. Note that a tension pulley 113 that comes into contact with the belt 112 from the outer circumferential side is provided at the lower rear of the handling cylinder input pulley 110.

As described above, according to the support structure of the handling cylinder transmission case 80 according to the present embodiment, in relation to the arrangement configuration of the pulley 111 with respect to the handling cylinder input pulley 110, the handling cylinder transmission case 80 is improved in terms of support strength against the tension of the belt 112. It becomes possible to stably support the trunk transmission case 80.

The combine harvester according to the present invention described using the embodiments as described above is not limited to the above-described embodiments, and various aspects can be adopted within the scope of the spirit of the present invention.

In the embodiment described above, the front rotor 26 is provided at the rear of the feeder 30, but the conveyance section 20 has a configuration in which the grain culm is input into the handling port 7a by the conveyor 36 of the feeder 30, etc. It is also possible to have a configuration that does not have this.

In the embodiment described above, the threshing transmission 60 is configured to reduce the speed and transmit the rotational power transmitted through the intermediate shaft 125, but it is configured to speed up the rotational power transmitted through the intermediate shaft 125 and transmit it. It may also be configured to transmit information.

In the embodiment described above, the handling trunk transmission case 80 has a support leg portion 150 on the right upper surface portion 161 of the right support arm member 162, which is one of the frame members forming the front rotor chamber 29, with respect to the transport portion 20. is supported by, but is not limited to this configuration. That is, the supporting position of the handling trunk transmission case 80 with respect to the conveyance section 20 may be, for example, an intermediate portion between the right side upper surface section 161 and the left side upper surface section 201 of the upper surface section of the front rotor chamber 29.

1 Combine harvester 2 Traveling machine body 3 Reaping section 7 Threshing section 7b Handling room 15 Driving section 20 Conveying section 25 Engine (drive source)
30 Feeder 26 Front rotor 29 Front rotor chamber 32 Cutting blade device 40 Handling cylinder 41 Handling cylinder shaft 41a Handling cylinder shaft extension part 59 Handling cylinder input shaft 60 Threshing transmission 80 Handling cylinder transmission case 81 Front wall 85 Main transmission case part 86 Shift case portion 86A Case main body portion 125 Intermediate shaft 141 Flange portion 150 Support leg portion 161 Right side upper surface portion (upper surface portion)
162 Right support arm member 170 Shift lever 200 Lever support portion 201 Left upper surface portion 210 Support base portion 220 Lever fixing portion (lever movement restriction portion)
230 Lever fixing member

Claims (4)

A combine harvester in which grain culms cut by a cutting blade device are transported by a transport section and supplied to a threshing section having a handling barrel in a handling chamber,
a handling cylinder input shaft that rotates upon receiving power transmitted from the drive source;
a threshing transmission having an intermediate shaft for changing the rotational speed transmitted from the handling cylinder input shaft to the handling cylinder shaft;
A handling cylinder transmission case that supports the handling cylinder input shaft, the intermediate shaft, and a portion of the handling cylinder shaft extending from the front wall of the handling chamber,
The handling trunk transmission case is supported by the front wall and the conveyance section,
The handling barrel input shaft has an upper shaft portion as an input shaft portion of the threshing transmission, and an output shaft portion of the threshing transmission to transmit rotational power of the upper shaft portion through the threshing transmission. It has a configuration in which the receiving shaft part and the lower shaft part are arranged coaxially.
A combine harvester characterized by: The combine harvester according to claim 1, wherein the handling barrel transmission case is supported by an upper surface of the transport section with respect to the transport section. The handling barrel transmission case has a transmission case portion that supports the intermediate shaft,
The combine harvester according to claim 1 or 2, wherein the speed change case section has a support leg section that supports the handling trunk transmission case with respect to an upper surface section of the conveyance section. The threshing transmission has a speed change lever extending from the speed change case portion toward one side in the left-right direction of the machine,
a lever support part provided in the conveyance part and supporting the speed change lever;
The combine harvester according to claim 3, further comprising a lever movement regulating section that is provided on the lever support section and that regulates movement of the shift lever at least in a shift operation direction.

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