JP2008141985A - Steering device for combine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a steering device for combine, capable of visually observing down rice paddy surface in the lower directional side of a reaping device by an operator at a sitting posture, capable of operating a steering handle by the operator in a standing posture as a stable posture, and making the operator steer, while enabling clear recognition of the difference, from the steering of a four-wheel drive vehicle. <P>SOLUTION: This steering device of the combine is constituted so as to change the circling radii of traveling crawlers to the left and the right by the rotary operation of a steering handle 13 is provided, by forming the steering handle 13 with a rear-half wheel body 312 having a semicircular shape as viewed from above and linked with a handle shaft 86; and a front half-wheel body 313 having a semicircular shape, as viewed from above, and linked with the rear half wheel body 312, and by constituting the front-half wheel body 313 as capable of moving to a circular handle-forming position A, that extends from the rear-half wheel body 312 in the frontal direction, or to a semicircular handle-forming position B, with it being folded in the lower directional side of the rear-half wheel body 312. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a combine that harvests unharvested cereals in a field by a reaping device, threshs the harvested cereals by a threshing device, and collects grains, and more specifically, left and right traveling that supports a traveling machine body The present invention relates to a combine control device including a crawler and a control handle for changing a course of a traveling machine body.

  Conventionally, like a steering wheel of a general four-wheeled vehicle, the steering wheel is formed in a round handle shape, and the steering wheel is rotated by an operator sitting on the driver's seat to change the traveling route of the combine. (For example, refer patent document 1).

In this case, in the conventional combine control device, the control moves (tracking operation) following the uncut grain row of the field, and the control moves to the cutting operation position of the next stroke on the headland of the field (90 Or a 180 degree turning operation). In addition, a configuration in which a steering handle is formed from a lateral handle rod extending in the left-right direction and left and right grips provided on both ends of the lateral handle rod (for example, see Patent Document 2) is also known.
JP 2002-274421 A JP 2000-308409 A

  In the prior art, as shown in Patent Document 1, when the steering handle is formed in a round handle shape, the front portion of the steering handle is disposed between the operator sitting on the driver's seat and the lower part of the cutting device. Therefore, there is a problem that an operator's view for visually observing the lower side of the reaping device cannot be secured.

  Therefore, as shown in Patent Document 2, when the steering handle is formed in a shape in which the front side portion of the round handle is missing, it is possible to secure an operator's field of view for viewing the lower side of the reaping device. However, as a harvesting operation mode of the combine, there is a swallowing work, and when the uncut cereal is harvested by the turning mowing work that moves along the edge of the field or the like, the operator stands in a posture standing from the driver's seat. Move while checking. In that case, in the steering handle shown in Patent Document 2, the left and right grips provided at both ends of the lateral handle bar are located near the waist or thigh of the operator in a standing posture. It was necessary to grasp the left and right grips in an unstable posture close to the part.

  On the other hand, compared to general four-wheeled vehicle operation (the maximum steering angle of the steering wheel is one rotation or more), the steering of the combine reduces the steering angle of the steering wheel and follows the uncut grain line. And the burden on the operator is reduced. As shown in Patent Document 1, in the operation of the combine, the maximum turning angle of the control handle is set to about 135 degrees. Maneuvering to move following the uncut grain rows in the field (turning and adjusting operations with a steering handle angle of about 15 degrees or less), and maneuvering to move to the cutting operation position for the next stroke on the field headland (The turning operation of the steering wheel having a turning angle of about 100 degrees or about 135 degrees, the direction changing operation at the headland) is executed. Therefore, for example, when the operator takes a light truck (small lorry) and reciprocates between the field and the house during a lunch break, he / she operates the combine with the steering handle of the light truck as if it were a light truck. By misoperation, the turning angle of the steering wheel becomes larger than necessary, the course of the combine is greatly changed with respect to the uncut grain row in the field, and the combine is skewed with respect to the uncut row line, etc. There is a problem.

  The object of the present invention is to allow the operator in the sitting position to visually observe the lower surface of the reaping device, so that the operator in the standing position can operate the control handle in a stable position, and the operator is different from the control of the four-wheeled vehicle. It is intended to provide a combine control device that can clearly recognize and control the vehicle.

  In order to achieve the above object, a combine steering apparatus according to a first aspect of the present invention includes a traveling machine body equipped with a reaping device and a threshing device, left and right traveling crawlers that support the traveling machine body, a steering handle, and a driver seat. A combined driving device configured to change a turning radius of the left and right traveling crawlers by a turning operation of the steering handle, wherein the steering handle is connected to a handle shaft in a plan view. A round handle forming position that is formed by a semi-circular rear wheel body and a front-half semi-circular front wheel body that is coupled to the rear wheel body and that extends forward from the rear wheel body, The front half wheel body is configured to be movable to a semicircular handle forming position that is folded downward.

  According to a second aspect of the present invention, there is provided the combine steering apparatus according to the first aspect, wherein both end sides of the front half wheel body are connected to both end sides of the rear half wheel body by left and right connecting shaft bodies, The front half wheel is configured to rotate around the body.

  According to a third aspect of the present invention, there is provided the combine steering apparatus according to the first aspect, further comprising a lock mechanism that maintains a support posture of the front half wheel, and a round handle forming position on the front side of the rear half wheel, or the The front half wheel is configured to be supported via the locking mechanism at a semicircular handle forming position on the lower front side of the rear half.

  According to the first aspect of the present invention, the steering handle includes a traveling machine body on which a reaping device and a threshing device are mounted, left and right traveling crawlers that support the traveling machine body, and a driving unit having a steering handle and a driving seat. In the combine steering apparatus configured to change the turning radius of the left and right traveling crawlers by a turning operation of the steering wheel, the steering handle includes a semi-circular rear half wheel coupled to a handle shaft, and the A round handle forming position that is formed by a front half ring having a semicircular shape in plan view connected to the rear half wheel, and extends forward from the latter half wheel, or a semi-circular handle formation position that is folded to the lower side of the latter half wheel. Further, the front half wheel body is configured to be movable. Therefore, by moving the front half wheel to a semicircular handle forming position that folds down to the lower half of the latter half, the field of view of the operator in the sitting position is secured, and the operator of the sitting position The bottom surface can be easily seen. Further, by moving the front half wheel body to a position where a round handle is formed to extend forward from the latter half wheel body, a standing posture operator grasps the front half wheel body, and the standing posture operator controls in a stable posture. The handle can be easily operated. In addition, by moving the front half wheel to a semicircular handle forming position that folds down to the lower half of the rear wheel, the operator in a sitting position grasps the latter wheel and the operator It can be operated by clearly recognizing the difference from the steering handle.

  According to the invention which concerns on Claim 2, the both ends of the said front half ring body are connected with the both ends of the said latter half ring body by a right-and-left connection shaft body, and the said front half ring body rotates around the said connection shaft body. Thus, the front half wheel can be easily connected to the latter half wheel via the left and right connecting shafts, and between the left and right connecting shafts, that is, both ends of the latter half wheel. A space for securing the operator's field of view can be easily formed between the two.

  According to the third aspect of the present invention, a lock mechanism for maintaining the support posture of the front half wheel body is provided, and a round handle forming position on the front side of the rear wheel body or a semicircular handle on the lower front side of the rear wheel body is provided. Since the front half wheel is supported at the formation position via the lock mechanism, the front half ring is highly rigid by the lock mechanism at the round handle formation position on the front side of the rear half wheel. The front half wheel can be easily prevented from falling off from the round handle forming position on the front side of the rear half wheel. In addition, the front half wheel can be reliably supported by the locking mechanism at a semicircular handle forming position on the lower front side of the rear half wheel body, and the front half wheel body at the semicircular handle forming position on the lower front side of the rear wheel body. Interference with other components can be easily prevented. It is possible to omit the trouble of detaching the front half ring from the latter half ring.

  DESCRIPTION OF EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings. 1 is a left side view of a combine, FIG. 2 is a plan view of the combine, FIG. 3 is a skeleton diagram of a power transmission system, and FIG. 4 is a perspective explanatory view showing a connection relationship between a main transmission lever, a steering handle, and a hydraulic drive device. 5 is a plan view of the driving unit, FIG. 6 is a plan view of the steering column, FIG. 7 is a side view of the steering handle, and FIG. 8 is a plan view of the steering handle. The overall structure of the combine will be described with reference to FIGS. 1 and 2. In the following description, the left side in the traveling direction of the traveling machine body 1 is simply referred to as the left side, and the right side in the traveling direction is also simply referred to as the right side.

  The combine of this embodiment includes a traveling machine body 1 supported by a pair of left and right traveling crawlers 2. At the front part of the traveling machine body 1, a four-row mowing device 3 that takes in while harvesting cereals is mounted by a single-acting lifting hydraulic cylinder 4 so as to be movable up and down around the mowing rotation fulcrum shaft 4a. Yes. A threshing device 5 having a feed chain 6 and a grain tank 7 for storing grain after threshing are mounted on the traveling machine body 1 side by side. In this embodiment, the threshing device 5 is disposed on the left side in the traveling direction of the traveling machine body 1, and the grain tank 7 is disposed on the right side in the traveling direction of the traveling machine body 1. A swivelable discharge auger 8 is provided at the rear part of the traveling machine body 1, and the grains inside the grain tank 7 are discharged from the throat throw 9 of the discharge auger 8 to a truck bed or a container. ing. An operation unit 10 is provided on the right side of the reaping device 3 and on the front side of the grain tank 7.

  The driving unit 10 includes a step 11 on which the operator gets on, a steering handle 13 provided on the handle column 12 on the step 11, a driving seat 14 provided behind the steering handle 13, and a lever on the left side of the driving seat 14. A main transmission lever 16, a sub transmission lever 17, a threshing clutch lever 18, and a cutting clutch lever 19 provided in the column 15 are arranged. An engine 20 as a power source is arranged below the driver seat 14.

  A clipper-type cutting blade device 222 that cuts the stock of uncut grain culm in the field is provided below the cutting frame 221 connected to the cutting rotation fulcrum shaft 4a of the cutting device 3. In front of the harvesting frame 221, a grain culling pulling device 223 for four ridges that raises an uncut grain culm in the field is arranged. Between the culm pulling device 223 and the front end (feed start side) of the feed chain 6, a culm conveying device 224 that conveys the chopped culm harvested by the cutting blade device 222 is arranged. In addition, in front of the lower part of the cereal habit raising device 223, a weeding body 225 for four ridges for weeding the uncut cereal in the field is projected. While the traveling crawler 2 is driven by the engine 20 to move within the field, the reaping device 3 is driven to continuously shave the uncut cereals on the field.

  In the threshing device 5, a handling cylinder 226 for threshing threshing, a rocking sorter 227 and a tang fan 228 for selecting a shed product falling below the handling cylinder 26, and a threshing taken out from the rear part of the handling cylinder 226. A processing cylinder 229 for reprocessing the discharged matter and a dust exhaust fan (not shown) for discharging dust at the rear portion of the swing sorter 227 are provided. In addition, the rotating shaft of the handling cylinder 226 extends along the conveying direction of the cereal by the feed chain 6 (in other words, the traveling direction of the traveling machine body 1). The stock source side of the corn straw conveyed from the reaping device 3 by the corn straw conveying device 224 is inherited by the feed chain 6 and is nipped and conveyed. Then, the tip side of the cereal cocoon is carried into the handling chamber of the threshing device 5 and threshed by the handling drum 226.

  On the lower side of the swing sorter 227, a first conveyor 231 that takes out the grain (first thing) sorted by the swing sorter 227, and a second that takes out a second thing such as a grain with a branch raft. A conveyor 232 is provided. The two conveyors 231 and 232 of this embodiment are arranged in the order from the front side in the traveling direction of the traveling machine body 1 to the upper surface side of the traveling machine body 1 above the rear part of the traveling crawler 2 in a side view in order of the first conveyor 231 and the second conveyor 232. It is installed.

  The swing sorter 227 is configured such that the cereals that have leaked from a receiving net (not shown) stretched below the handling cylinder 226 are subjected to peristaltic sorting (specific gravity sorting) by a feed pan, a chaff sheave, or the like (not shown). is doing. In addition, the grain dropped from the grain sieve (not shown) of the rocking sorter 227 is removed by the sorting wind from the tang fan 228 and falls first onto the conveyor 231.

  A whipping cylinder 233 extending in the vertical direction is connected to a terminal portion of the first conveyor 231 that protrudes outward from one side wall (in the embodiment, the right side wall) near the grain tank 7 in the threshing device 5. . The grain taken out first from the conveyor 231 is carried into the grain tank 7 via the whipping cylinder 233 and collected in the grain tank 7. In addition, the terminal part which protruded outward from the one side wall near the grain tank 7 in the threshing device 5 in the second conveyor 232 is rocked via a reduction cylinder 236 that intersects the milling cylinder 233 and extends in the front-rear direction. The second sorter is connected to the upper surface side of the feed pan of the dynamic sorter 227 and is configured to return to the upper side of the feed pan of the swing sorter 227 for re-sorting.

  On the other hand, a waste chain 234 is disposed on the rear end side (feed end side) of the feed chain 6. The slag passed from the rear end side of the feed chain 6 to the sewage chain 234 (the slag from which the grain has been threshed) is discharged to the rear of the traveling machine body 1 in a long state, or the rear side of the threshing device 5 After being cut to a suitable length by the waste cutter 235 provided on the rear, the machine is discharged to the lower rear side of the traveling machine body 1.

  As shown in FIG. 3, the transmission case 22 that drives the traveling crawler 2 includes a straight-travel HST continuously variable transmission mechanism 25 (straight-travel hydraulic drive device) including a straight-travel hydraulic pump 23 and a straight-drive hydraulic motor 24, and a swing hydraulic pump 26. And a turning HST continuously variable transmission mechanism 28 (turning hydraulic drive device) including a turning hydraulic motor 27. In both of these HST type continuously variable transmission mechanisms 25 and 28, the input shafts 29 a and 29 b of the straight and turning hydraulic pumps 23 and 26 are connected to the output shaft 21 of the engine 20 by transmission belts 30 a and 30 b, respectively. 26 is driven.

  The drive wheels 34 of the left and right traveling crawlers 2 are linked and connected to the output shaft 31 of the straight hydraulic motor 24 via a subtransmission mechanism 32 and a differential mechanism 33. The differential mechanism 33 has a pair of planetary gear mechanisms 35 and 35 arranged symmetrically. Each planetary gear mechanism 35 is formed by one sun gear 36, three planetary gears 37 that mesh with the outer periphery of the sun gear 36, and a ring gear 38 that meshes with these planetary gears 37.

  The planetary gear 37 is rotatably supported by a carrier 41 of a carrier shaft 40 positioned on the same axis as the sun gear shaft 39, and the left and right carriers 41 are disposed opposite to each other with the left and right sun gears 36, 36 therebetween. The ring gear 38 has internal teeth 38 a that mesh with the planetary gears 37, and is rotatably supported by the carrier shaft 40. The carrier shaft 40 extends outward in the left-right direction to form an axle, and a drive wheel 34 is attached to the tip portion thereof.

  The rectilinear HST type continuously variable transmission mechanism 25 controls forward / reverse rotation and rotational speed of the rectilinear hydraulic motor 24 by adjusting and changing the angle of the rotary swash plate of the rectilinear hydraulic pump 23. In this case, the rotation output of the straight hydraulic motor 24 is transmitted from the transmission gear 42 of the output shaft 31 to the center gear 46 fixed to the sun gear shaft 39 via the gears 43, 44, 45 and the auxiliary transmission mechanism 32, and as a result. The sun gear 36 is configured to rotate.

  The sub-transmission mechanism 32 includes a sub-transmission shaft 47 having a gear 44 and a parking brake shaft 49 having a gear 48 (for high speed) that meshes with the center gear 46 via the gear 45. A pair of low speed gears 50 and 51, medium speed gears 52 and 53, and high speed gears 54 and 48 are provided between the sub-transmission shaft 47 and the brake shaft 49. The sub-shift is configured to be switched between low speed, medium speed, and high speed by a slide operation of the slider 56.

  Note that there is a neutral position (a position where the output of the sub-shift becomes zero) between the low speed and medium speed of the sub-shift and between the medium speed and high speed. A parking brake 57 is provided on the parking brake shaft 49. Further, a sub-transmission shaft 47 is connected to a cutting PTO shaft 58 that transmits a rotational force to the cutting unit 3 via gears 59 and 60 and a one-way clutch 61 to drive the cutting unit 3 at a vehicle speed synchronization speed. .

  As described above, the driving force of the rectilinear hydraulic motor 24 transmitted from the center gear 46 to the sun gear shaft 39 is transmitted to the left and right carrier shafts 40 via the left and right planetary gear mechanisms 35 and also transmitted to the left and right carrier shafts 40. Rotational power is transmitted to the left and right drive wheels 34 to drive the left and right traveling crawlers 2.

  The turning HST type continuously variable transmission mechanism 28 performs forward / reverse rotation and rotation speed control of the turning hydraulic motor 27 by adjusting and changing the angle of the rotary swash plate of the turning hydraulic pump 26. In this case, in the transmission case 22, the brake shaft 63 having the steering output brake 62, the clutch shaft 65 having the steering output clutch 64, and the left and right input gears that are always meshed with the external teeth 38 b of the left and right ring gears 38. 66, 67.

  A clutch shaft 65 is connected to the output shaft 68 of the swing hydraulic motor 27 via the brake shaft 63 and the steering output clutch 64, and a right input gear 67 is connected to the clutch shaft 65 via a normal rotation gear 69. A left input gear 66 is connected to the clutch shaft 65 via a forward rotation gear 69 and a reverse rotation gear 70.

  By turning the low and medium speed and high speed sliders 55 and 56 to neutral and turning on the steering output brake 62 and turning off the steering output clutch 64, transmission of rotational power from the swing hydraulic motor 27 is prevented.

  Further, by turning off the steering output brake 62 and turning on the steering output clutch 64 at the time of the sub-shift output other than the neutral, the rotational power of the turning hydraulic motor 27 is transferred to the right ring gear via the normal rotation gear 69. 38 and is transmitted to the outer teeth 38b of the left ring gear 38 via the forward rotation gear 69 and the reverse rotation gear 70. As a result, when the swing hydraulic motor 27 rotates in the forward direction (reverse rotation), the left ring gear 38 rotates in the reverse direction (forward rotation) and the right ring gear 38 rotates in the forward direction (reverse rotation) at the same number of rotations in the opposite directions.

  Thus, when the rectilinear hydraulic motor 24 is driven in a state in which the swing hydraulic motor 27 is stopped and the left and right ring gears 38 are stationary, the rotational output from the rectilinear hydraulic motor 24 is the same from the center gear 46 to the left and right sun gears 36. The left and right traveling crawlers 2 are driven at the same rotational speed in the same rotational direction in the left and right directions through the planetary gear 37 and the carrier 41 of the left and right planetary gear mechanisms 35, and the aircraft travels straight forward and backward. .

  On the other hand, when the swing hydraulic motor 27 is driven to rotate in the forward and reverse directions while the straight hydraulic motor 24 is stopped and the left and right sun gears 36 are stationary and fixed, the left planetary gear mechanism 35 is rotated forward or reverse and the right planetary gear is rotated. The mechanism 35 rotates reversely or forwardly, drives the left and right traveling crawlers 2 in the reverse direction, and turns the aircraft to the left or right.

  Further, by driving the swing hydraulic motor 27 while driving the straight hydraulic motor 24, the aircraft turns left and right to correct the course. The turning radius of the airframe is determined by the output rotational speed of the turning hydraulic motor 27.

  Next, the structure around the driving unit 10 will be described with reference to FIGS. 4 and 5. As shown in FIG. 5, a handle column 12 is erected and fixed on the upper surface of the front portion of the operation unit 10. A steering handle 13 is disposed above the handle column 12 so as to be horizontally rotatable. A lever column 15 is provided on the left side of the driving unit 10, and a mission 22 is disposed below the lever column 15. The lever column 15 is provided with a main transmission lever 16, a sub transmission lever 17, a harvesting clutch lever 19, and a threshing clutch lever 18 as straight operation bodies. Further, the handle column 12 is formed by molding an aluminum alloy casting, and has a split structure that can be divided into left and right. The handle column 12 having a split structure is formed in a box shape by fastening with a plurality of bolts.

  As shown in FIGS. 4 and 5, the handle column 12 includes a tilt base 78 as a support member formed on the handle column 12, a handle shaft 86 rotatably supported on the tilt base 78, and a handle shaft. The above-mentioned steering handle 13 attached to the upper end of 86 is provided. On the tilt base 78, an upper end portion of the steering input shaft 87 extending in the vertical direction at the approximate center inside the handle column 12 is also rotatably supported. By engaging the gear 88 of the handle shaft 86 and the sector gear 89 of the steering input shaft 87, the steering handle 13 and the steering input shaft 87 are connected so that power can be transmitted.

  Next, referring to FIG. 4, the main transmission lever 16 and the steering handle 13, the straight HST continuously variable transmission mechanism 25 (straight forward hydraulic drive device) and the turning HST continuously variable transmission mechanism 28 (turning hydraulic pressure). A connection structure with the drive device) will be described. The steering input shaft 87 and the main speed change lever 16 connected to the handle shaft 86 of the steering handle 13 so as to be able to transmit power are linked to mechanical switching means 101 arranged in the handle column 12.

The mechanical switching means 101 is
1. When the steering handle 13 is rotated to a position other than the neutral position while the main transmission lever 16 is tilted to a position other than the neutral position, the aircraft moves to the left or right with a smaller turning radius as the rotation operation amount increases. As the vehicle turns and the turning radius is smaller, the vehicle speed (turning speed when moving forward and backward) decreases.
2. Even when the main transmission lever 16 is tilted in either the forward or reverse direction, the turning operation direction of the steering handle 13 and the turning direction of the aircraft coincide (the steering handle 13 in both forward and reverse). To the right, the aircraft turns to the right, and to the left, the aircraft turns to the left)
3. If the main transmission lever 16 is in the neutral position, it will not function even if the steering handle 13 is operated.
In order to execute various operations, the operating force from the main transmission lever 16 and the steering handle 13 is appropriately converted and transmitted to double shafts 125 and 126 (details will be described later) provided at the bottom of the handle column 12. Is configured to do.

  The mechanical switching means 101 of the embodiment includes a steering mechanism 118 for changing the traveling direction of the airframe, and a speed change mechanism 124 for changing the vehicle speed (traveling speed) of the airframe and switching between forward and backward travel. Yes. First, the specific structure of the mechanical switching means 101 will be described. As shown in FIGS. 9 and 12, a bearing member 90 is detachably fixed to the left side surface of the handle column 12 approximately in the middle of the vertical width. The bearing member 90 cantilever-supports one end portion of the speed change input shaft 91 via a bearing 92, and the speed change input shaft 91 is supported by the bearing member 90 in a substantially horizontal posture in the left-right direction. Yes.

  As shown in FIG. 4, the lower end of the steering input shaft 87 is connected to the upper end side of the input fulcrum shaft 94 via a universal joint 93. A steering input member 95 is fixed to the input fulcrum shaft 94. The steering input member 95 is rotatably connected to the transmission input shaft 91 via a bearing. The universal joint 93 is located at an intersection point where the axis of the substantially vertical steering input shaft 87 and the axis of the substantially horizontal shift input shaft 91 are orthogonal to each other.

  That is, the steering input member 95 rotates forward and backward around the same and substantially vertical axis as the steering input shaft 87 when the steering input shaft 87 rotates forward and backward. By reverse rotation, it is configured to tilt in the front-rear direction together with the input fulcrum shaft 94 about the same horizontal axis as the speed change input shaft 91. Further, when the steering input shaft 87 is rotated forward and backward about its axis by the turning operation of the steering handle 13, the steering input member 95 rotates forward and backward around the steering input shaft 87.

  As shown in FIG. 4, a horizontally long main transmission shaft 99 as a first transmission shaft is rotatably supported on the lower front side of the handle column 12. The left end of the main transmission shaft 99 protrudes outward from the left side of the handle column 12, and this protruding end is connected to the main transmission lever 16 on the lever column 15 via the main transmission link 100. The main transmission lever 16 is used to move the vehicle body 1 forward, stop, reverse, and to change the vehicle speed steplessly. When the main transmission lever 16 is tilted in the front-rear direction, the operating force is applied to the main transmission link 100. Is transmitted to the main transmission shaft 99, and the main transmission shaft 99 is rotated forward and backward about its axis.

  The main transmission shaft 99 is linked to the transmission input shaft 91 through a rod-type main transmission member 110, an upper link 111, and a lower link 112. For this reason, when the main transmission shaft 99 is rotated forward and backward about its axis by the forward / backward tilting operation of the main transmission lever 16, the transmission input shaft 91 is rotated forward and backward about its axis, resulting in steering. The input member 95 tilts back and forth together with the input fulcrum shaft 94.

  A cylindrical steering output shaft 113 is rotatably fitted on the outer periphery of the main transmission shaft 99. The link type steering output member 114 fixed to the steering output shaft 113 is connected to the lower end portion of the rod type steering coupling member 115 via a ball joint type steering output connecting portion 117. The upper end portion of the rod type steering coupling member 115 is connected to the steering input member 95 via a universal joint type steering input connecting portion 116. In the embodiment, the combination of the steering output shaft 113, the link type steering output member 114, the rod type steering coupling member 115, the universal joint type steering input connecting portion 116, and the ball joint type steering output connecting portion 117 is The steering mechanism 118 for changing the traveling path of the aircraft is configured.

  A shift output shaft 119 serving as a second shift shaft extending parallel to the main output shaft 99 and the steering output shaft 113 is rotatably supported at a position above the steering output shaft 113 in the handle column 12. Yes. The link type transmission output member 120 fixed to the transmission output shaft 119 is connected to the lower end portion of the transmission coupling member 121 via a ball joint type transmission output connection part 123. The upper end portion of the rod-type transmission coupling member 121 is connected to the steering input member 95 via a universal joint type transmission input connection portion 122. In the embodiment, the combination of the speed change output shaft 119, the link type speed change output member 120, the rod type speed change coupling member 121, the universal joint type speed change input connection portion 122, and the ball joint type speed change output connection portion 123 is determined by the vehicle speed ( A speed change mechanism 124 for changing the travel speed) and switching between forward and backward travel is configured.

  Next, a connection structure from the double shafts 125 and 126 to the straight HST continuously variable transmission mechanism 25 (straight forward hydraulic drive device) and the turning HST continuously variable transmission mechanism 28 (turn hydraulic drive device) will be described. . As shown in FIG. 4, a double shaft comprising an outer turning transmission cylinder shaft 125 and an inner straight transmission shaft 125 is provided at a bearing portion provided at the bottom portion of the handle column 12 and near the center of the left and right width. The shafts are vertically concentric and are rotatably supported independently of each other. The upper ends of the double shafts 125 and 126 protrude into the handle column 12, while the lower ends of the double shafts 125 and 126 protrude to the lower surface side of the operating unit 10.

  The upper end of the turning transmission cylinder shaft 126 is connected to the upper link member 133 for turning protruding from the turning transmission cylinder shaft 126, the steering output link 132 protruding from the steering output shaft 113, and the joint shaft 131 connecting them. The steering output shaft 113 is linked and connected. A lower end portion of the turning transmission cylinder shaft 125 is linked to a turning control shaft (not shown) protruding from the turning HST continuously variable transmission mechanism 28 via a turning link mechanism 138 and a turning link 139.

  The turning transmission cylinder shaft 125 (turning control shaft) is for adjusting the inclination angle (swash plate angle) of the rotating swash plate of the turning hydraulic pump 26 in the turning HST transmission mechanism 28. It functions as an adjusting unit that adjusts the shift output of the mechanism 28. That is, by adjusting the swash plate angle of the swing hydraulic pump 26 by forward / reverse rotation of the swing transmission cylinder shaft 125 (swing control shaft), the rotational speed control and forward / reverse switching of the swing hydraulic motor 27 are executed. Stepless change of steering angle (turning radius) and switching of left and right turning directions are performed.

  On the other hand, the upper and lower ends of the straight transmission shaft 125 protrude further upward and downward from the turning transmission cylinder shaft 125. A link 130 is fixed to the upper end portion of the linear transmission shaft 125. The link 130 is connected to a speed change output link 129 protruding from the speed change output shaft 119 via a joint shaft 128. The lower end portion of the rectilinear transmission shaft 125 is coupled to a rectilinear control shaft (not shown) protruding from the rectilinear HST continuously variable transmission mechanism 25 via a rectilinear link mechanism 143 and a rectilinear link 144. The rectilinear transmission shaft 125 (straight control axis) is for adjusting the inclination angle (swash plate angle) of the rotary swash plate of the rectilinear hydraulic pump 23 in the rectilinear HST continuously variable transmission mechanism 25. The rectilinear HST type It functions as an adjustment unit for adjusting the shift output of the transmission mechanism 25. That is, by adjusting the swash plate angle of the rectilinear hydraulic pump 23 by forward / reverse rotation of the rectilinear transmission shaft 125 (straight forward control shaft), the rotational speed control and forward / reverse switching of the rectilinear hydraulic motor 24 are executed, and the traveling speed ( Stepless change of vehicle speed) and forward / reverse switching.

  Next, the behavior of the connecting structure when the main transmission lever 16 and the steering handle 13 are operated will be described with reference to FIG.

  When the main transmission lever 16 is in the neutral position, the steering input member 95, the rod-type steering coupling member 115, and the rod-type transmission coupling member 121 are not connected to the steering input shaft 87 even if the steering handle 13 is rotated left and right. Since it moves along the conical locus C around the axis, the link type steering output member 114, the link type transmission output member 120, the steering output shaft 113, and the transmission output shaft 119 are maintained in a stopped state.

  When a forward (reverse) operation is performed to tilt the main transmission lever 16 forward (rearward), the steering input member 95 is shifted by the operation force from the main transmission shaft 99 via the lower link 112 and the rod-type main transmission member 110. While tilting forward (rearward) around the input shaft 91 and holding the state where the universal joint type steering input connection part 116 is stopped at a predetermined position, the universal type transmission input connection part 122 is moved upward (downward), The shift output shaft 119 is rotated forward (reversely) by swinging the link-type shift output member 120 upward (downward).

  Then, the linear transmission shaft 125 rotates forward (reversely) around its axis by the operation force from the shift output shaft 119 via the link members 128 to 130 on the shift output shaft 119 side. ), The link mechanism 143 for rectilinear movement is pushed and pulled, and the rectilinear control shaft of the rectilinear hydraulic pump 23 is rotated forward and backward. As a result, the machine body (the left and right traveling crawlers 2) performs a forward (reverse) operation in proportion to the forward / backward tilting operation amount of the main transmission lever 16.

  When the steering handle 13 is rotated leftward (rightward) with the main shift lever 16 moving forward (reverse), the steering input member 95 moves forward (rearward) around the shift input shaft 91. In a tilted position, the steering input shaft 87 is rotated forward (reversely) to move the universal joint type steering input connecting portion 116 downward (upward), and the link type steering output member 114 swings downward (upward). The steering output shaft 113 is rotated forward (reversely) by the movement.

  Then, the turning transmission cylinder shaft 126 rotates forward (reversely) about its axis by the operating force from the steering output shaft 113 via the ball joint shaft 131, the steering output link 132, and the upper link member 133 for turning. In this normal rotation (reverse rotation), the turning link mechanism 138 is pushed and pulled, and the turning control shaft of the turning hydraulic pump 26 is rotated forward and backward. As a result, the left traveling crawler 2 is driven in the deceleration (acceleration) direction in proportion to the amount of turning operation of the steering handle 13, while the right traveling crawler 2 is driven in the acceleration (deceleration) direction and left (right) ) Turn the aircraft in the direction to correct its travel path.

  In this case, the steering input member 95 is steered forward (rear) around the speed change input shaft 91 by the left (right) turning operation of the steering handle 13 simultaneously with the travel course correcting operation. Forward rotation (reverse rotation) about the shaft 87 moves the universal joint type shift input connecting portion 122 downward (upward), and the shift output shaft 119 reverses when the link type shift output member 120 swings downward (upward). (Forward).

  For this reason, the rectilinear transmission shaft 125 is reversely rotated (forward rotation) about its axis by the return operation force from the transmission output shaft 119, and the rectilinear link mechanism 143 is proportional to the rotation operation amount of the steering handle 13. Then, the rectilinear control shaft is reversely rotated (forward rotation), and the forward (reverse) rectilinear speed of the aircraft is decelerated in accordance with the turning radius at that time.

  That is, in the normal case, when the steering handle 13 is rotated in a state where the main shift lever 16 is operated forward (reverse), the turning radius for correcting the course in proportion to the rotational operation amount of the steering handle 13 is set. As the amount of deceleration of the traveling speed changes and the amount of turning operation of the control handle 13 increases, the speed difference between the left and right traveling crawlers 2 increases, the turning radius decreases, and the amount of deceleration of the traveling speed increases to increase the vehicle speed ( (Straight speed) becomes slower.

  In addition, the movement of the universal joint type swivel input connecting portion 116 is reversed with respect to the turning operation of the steering handle 13 at the time of forward movement and backward movement, and the direction of the turning operation of the steering handle 13 is determined in both forward and backward movements. The turning direction of the aircraft matches.

  Next, the structure of the steering handle 13 will be described with reference to FIGS. As shown in FIGS. 7 and 8, the steering handle 13 has a handle boss body 310 fixed to the upper end side of the handle shaft 86, a handle spoke body 311 connected to the handle boss body 310, and a plane as a grip (grip part). The rear half ring 312 having a semi-circular shape in view and the front half ring 313 having a semi-circular shape in plan view as a grip (grip part) connected to the second half ring 312 are formed. The rear half body 312 and the front half body 313 are arranged on the same circumference, so that a ring-shaped grip (grip part) of a substantially circular round handle is formed.

  The steering handle 13 forms a grip of a substantially circular round handle by the latter half wheel body 312 and the front half wheel body 313, and the round handle has an annular shape by the latter half wheel body 312 and the front half wheel body 313. A grip or a long elliptical ring-shaped grip may be formed, or a polygonal ring-shaped grip may be formed.

  Both end sides 313 a of the front half ring 313 are connected to both end sides 312 a of the rear half ring 312 by left and right connecting shaft bodies 314. By rotating the front half wheel 313 around the left and right connecting shaft bodies 314, a round handle forming position A extending forward from the rear half wheel body 312 and a standing posture position B through the second half projecting upward from the rear half wheel body 312 are shown. The front half ring body 313 is configured to be movable to a semicircular handle forming position C that is folded to the lower side of the ring body 312.

  That is, when the front half-wheel body 313 is supported at the semicircular handle forming position C that is folded below the rear half-wheel body 312, the latter half-wheel body 312 has a half-circle handle shape (semi-half) similar to an airplane (or bicycle), for example. A steering handle 13 having a circular grip shape is formed. As a result, the front half wheel body 313 is supported at a position deviated from the line of sight P (front view) (see FIG. 1) of the operator seated on the driver seat 14, and the forward view of the operator seated on the driver seat 14 is secured. By the sitting posture operator, the field on the lower side of the cutting device 3 can be easily visually observed. In addition, when the operator in the sitting posture grasps the grip portion 312b of the rear wheel body 312, the operator can clearly recognize the difference from the round handle of the four-wheeled vehicle and can steer the control handle 13.

  Therefore, a sudden steering operation that increases the turning angle of the steering handle 13 can be prevented in the sense of operating a round handle of a four-wheeled vehicle. For example, in a row cutting operation that moves along a substantially straight uncut grain row 315, the operator grasps the grip portion 312b of the rear wheel body 312 while recognizing a difference from a round handle of a four-wheeled vehicle. Thus, the steering handle 13 can be turned, the turning angle of the steering handle 13 changes suddenly, and the steering handle 13 is erroneously operated, for example, the course of the traveling machine body 1 greatly deviates from the substantially straight uncut grain row 315. Is prevented, and the alignment operation of rotating the steering handle 13 at a cutting angle of about 20 degrees or less is executed.

  On the other hand, when the front half wheel 313 is supported at a round handle forming position A that extends forward from the rear half wheel 312, the round handle similar to a general four-wheeled vehicle or the like is formed by the rear half body 312 and the front half wheel 313. A steering handle 13 having a shape (circular grip shape) is formed. For example, an operator standing on step 11 in a cutting operation or a mowing operation at the time of harvesting a grain culm at the edge of a farm field, with a line of sight R that is not obstructed by the steering handle 13 (see FIG. 1), While grasping the grip portion 313a of 313 and maintaining the posture, the lower part of the front side of the traveling machine body 1 is visually observed, and the steering handle 13 (the second wheel body 312 and the first half wheel body 313) is rotated and operated to travel. The course of the airframe 1 is corrected to match the uncut grain row.

  Further, when the front half wheel 313 is supported at the standing posture position B protruding above the rear half wheel 312, the latter half wheel body 312 and the front half wheel body 313 form a round handle similar to a general four-wheeled vehicle or the like. Since the middle part of the left and right widths of the semicircular grip-shaped front half wheel 313 is supported at a position higher than the round handle forming position A while forming the (circular grip-shaped) steering handle 13, for example, an operator with a high height Even so, the operator standing on the step 11 can rotate the steering handle 13 by gripping the grip portion 313a at the middle portion of the left and right widths of the front half wheel 313 without greatly bending the waist.

  As shown in FIGS. 7 and 8, a lock mechanism 316 that maintains the support posture of the front half wheel body 313 is disposed on the above-described left and right connecting shaft bodies 314. The lock mechanism 316 includes a lock case 317 that is fixed to the rear half ring body 312, a lock gear 318 that is fitted to the connecting shaft body 314 in the lock case 317, a lock claw 319 that is detachably engaged with the lock gear 318, and a lock gear And a release lever 320 for releasing the lock claw 319 from 318. The lock gear 318 is fixed to the connecting shaft body 314. The lock claw 319 is pivotally supported by the lock case 317 so as to be rotatable. The release lever 320 is slidably supported by the lock case 317.

  The lock claw 319 is locked and held on the lock gear 318 by a spring (not shown). Therefore, a round handle forming position A that extends forward from the rear half wheel body 312, a standing posture position B that protrudes above the rear half wheel body 312, or a semicircular handle formation position C that folds downward on the lower half wheel body 312. On either side, the front half wheel body 313 is supported via the lock mechanism 316 by the engagement of the lock gear 318 and the lock claw 319. On the other hand, when the release lever 320 is operated, the lock claw 319 is disengaged from the lock gear 318 against a spring (not shown), thereby rotating the front half ring body 313 around the connecting shaft body 314 in a multistage manner. The front half wheel body 313 can be moved to the handle forming position A, the standing posture position B, or the semicircular handle forming position C.

  A work switch 321 for raising and lowering the cutting device 3 and finely adjusting the course of the traveling machine body 1 is disposed on the right end side 312a of the rear half body 312. In addition, a horn switch 322 is provided on the left end side 312a of the rear half body 312 to sound a horn and warn the surroundings.

  With the above configuration, in the four-row harvesting combine shown in FIGS. 1 and 2, the front half-wheel body 313 is supported at the semicircular handle forming position C that is folded below the rear-half wheel body 312 in the trimming work or the like. Under the condition, the rightmost weed body 225 can be visually observed by the line of sight P of the operator sitting on the driver's seat 14. Further, the front half wheel 313 is supported at a round handle forming position A extending forward from the rear half wheel 312, or the front half wheel 313 is supported at a standing posture position B protruding above the rear half wheel 312. However, in the cutting or turning operation, the rightmost herb body 225 passes through the pulling gate 223a on the upper end side of the grain pulling device 223 by the operator's line of sight standing from the driver seat 14 and the like. The rightmost uncut grain row 315 between the adjacent weed bodies 225 can be visually observed.

  Further, when the front half wheel 313 is supported at the round handle forming position A extending forward from the rear half wheel 312 or the front half wheel 313 is supported at the standing posture position B protruding above the rear half wheel 312, An operator standing in a standing position from the seat 14 can hold the front half wheel body 313 and maintain a stable standing posture.

  Next, referring to FIGS. 9 and 10, the steering structure of the two-stripe combine according to the second embodiment of the present invention will be described. As shown in FIG. 9 and FIG. 10, the two-row mowing device 3 a includes two rows of grain raising devices 223 that cause uncut grain cereals in the field, and two portions for dividing the grains. A grass body 225 is arranged. In addition, the same code | symbol is attached | subjected to the location of the same component name as the combine for 4 cuttings shown in FIG.1 and FIG.2, and the description is abbreviate | omitted. Similarly to the above-described four-row harvesting combine, in the two-row harvesting combine, the front half-wheel body 313 is supported at the semicircular handle forming position C that folds below the rear-half wheel body 312 in the trimming operation or the like. Below, the rightmost end weed body 225 can be visually observed by the line of sight P of the operator seated on the driver's seat 14. Moreover, the uncut culm row 315 on the rightmost end side can be visually observed by the operator's line of sight standing in a standing posture standing from the driver seat 14 in the time of cutting or turning. In addition, an operator in a standing posture standing from the driver's seat 14 can maintain a stable standing posture by grasping the front half wheel body 313 at the round handle forming position A or the standing posture position B.

  Next, the structure of the steering handle 13 according to the third embodiment of the present invention will be described with reference to FIGS. 11 and 12. As shown in FIGS. 11 and 12, the auxiliary handle 13 a is disposed on the grip portion 313 b of the front half wheel body 313. The auxiliary handle 13a includes left and right bar-shaped handle arms 325 and left and right grips 326 that the operator holds with left and right hands. The handle arm 325 is formed in an axial shape extending in the left-right direction, and a grip 326 is fixed to the outer end side of the handle arm 325. Further, the inner end side of the handle arm 325 is inserted into the grip portion 313b of the front half ring 313 so as to be able to enter and exit. A dedent mechanism 327 is disposed on the grip portion 313b. That is, the handle arm 325 is supported by the dedent mechanism 327 at a position where the inner end side of the handle arm 325 is retracted into the grip portion 313b and a position where the inner end side of the handle arm 325 is advanced from the grip portion 313b. It is configured.

  With the above configuration, in row cutting work or the like, the driver sits on the driver's seat 14 while supporting the front half wheel 313 and the auxiliary handle 13a at the semicircular handle forming position C that is folded below the rear half wheel 312. The weed body 225 on the rightmost end side can be seen with the operator's line of sight P. Further, the front half wheel 313 and the auxiliary handle 13a are supported at a round handle forming position A that extends forward from the rear half wheel 312, or the front half wheel 313 and the auxiliary are at a standing posture position B that protrudes above the rear half wheel 312. Even in a state where the handle 13a is supported, the operator's line of sight standing from the driver seat 14 in the cutting or turning operation, over the pulling gate 223a on the upper end side of the grain raising device 223, The rightmost uncut grain row 315 between the rightmost end weed body 225 and the adjacent weed body 225 can be visually observed.

  Further, the front half wheel 313 and the auxiliary handle 13a are supported at a round handle forming position A that extends forward from the rear half wheel 312, or the front half wheel 313 and the auxiliary are at a standing posture position B that protrudes above the rear half wheel 312. When the handle 13a is supported, an operator standing from the driver's seat 14 can maintain a stable standing posture by grasping the grip 326 of the handle arm 325 provided on the front half wheel 313. By moving the handle arm 325 in and out of the grip portion 313b, the left and right grips 326 can be moved in the left-right direction.

  That is, one or both of the left and right grips 326 can be moved in the left-right direction to enlarge or reduce the distance between the left and right grips 326. The left and right grips 326 can be supported at an easy-to-use position according to the physique of the operator. In particular, when the front half-wheel body 313 and the auxiliary handle 13a are supported at the standing posture position B protruding above the rear-half wheel body 312, the handle arm 325 and the left and right grips 326 are the same as the one-character handle of a motorcycle (motorcycle). Since it is formed into a shape, the operator 13 in a standing posture can easily operate the steering handle 13 by grasping the left and right grips 326.

  As is clear from the above description and FIGS. 1, 7, and 8, the traveling machine body 1 on which the reaping devices 3, 3 a and the threshing device 5 are mounted, the left and right traveling crawlers 2 that support the traveling machine body 1, and the steering handle 13 and a driving unit 10 having a driver's seat 14, and in a combine steering apparatus configured to change the turning radius of the left and right traveling crawlers 2 by a turning operation of the steering handle 13, the steering handle 13 includes: A round half-circular shape 312 connected to the handle shaft 86 and a semi-circular front half-shape 313 connected to the rear half wheel 312 and extending forward from the rear half 312. The front half-wheel body 313 is configured to be movable to a handle-forming position A or a semi-circular handle-forming position B that is folded below the rear half-wheel body 312. Therefore, by moving the front half wheel body 313 to the semicircular handle forming position B that folds to the lower side of the rear half wheel body 312, the visibility of the operator in the sitting posture is secured, and the cutting device is operated by the operator in the sitting posture. The rice field on the lower side of 3, 3a can be easily seen. Further, by moving the front half wheel body 313 to the round handle forming position A extending forward from the rear half wheel body 312, the standing posture operator grasps the front half wheel body 313, and the standing posture operator has a stable posture. The steering handle 13 can be easily operated. Further, by moving the front half wheel body 313 to a semicircular handle forming position B that folds to the lower side of the rear half wheel body 312, the operator in the sitting posture grasps the latter half wheel body 312, and the operator moves the four-wheeled vehicle. The difference between the steering handle with the round handle shape and the steering handle 13 can be clearly recognized and operated.

  As is apparent from the above description and FIGS. 7 and 8, both end sides of the front half wheel body 313 are connected to both end sides of the rear half wheel body 312 by the left and right connecting shaft bodies 314, and the front half wheels are rotated around the connecting shaft body 314. Since the body 313 is configured to rotate, the front half ring body 313 can be easily connected to the rear half ring body 312 via the left and right connection shaft bodies 314, and between the left and right connection shaft bodies 314, that is, A space for ensuring the field of view of the operator can be easily formed between both ends of the rear half body 312.

  As is clear from the above description and FIGS. 7 and 8, the lock mechanism 316 is maintained to maintain the support posture of the front half wheel 313, the round handle forming position A on the front side of the rear half wheel 312, or the rear ring body 312. Since the front half wheel body 313 is supported via the locking mechanism 316 at the front lower semicircular handle forming position B, the locking mechanism is provided at the front circular handle forming position A of the rear half wheel 312. The front half ring body 313 can be supported with high rigidity by 316, and the front half ring body 313 can be easily prevented from falling off from the round handle forming position A on the front side of the rear half ring body 312. Further, the front half wheel 313 can be reliably supported by the lock mechanism 316 at the semicircular handle forming position B on the lower front side of the rear half wheel 312, and the front half wheel at the semicircular handle forming position B on the lower front side of the rear half wheel 316. Interference between the body 313 and other components can be easily prevented. The trouble of detaching the front half ring 313 from the rear half ring 312 can be omitted.

It is a side view of the combine for 4 thread cutting of 1st Embodiment of this invention. It is the same top view. It is a skeleton figure of a power transmission system. It is a perspective explanatory view showing the connection relationship between the main transmission lever and the steering handle and the hydraulic drive device. It is a top view of an operation part. It is a top view of a steering column. It is a side view of a steering handle. It is a top view of a steering handle. It is a side view of the combine for 2 line cutting of 2nd Embodiment of this invention. It is the same top view. It is a side view of the steering handle of a 3rd embodiment of the present invention. It is the same top view.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Traveling machine body 2 Traveling crawler 3 Harvesting device 5 Threshing device 10 Driving part 13 Steering handle 14 Driving seat 86 Handle shaft 312 Rear wheel body 313 Front half wheel body 314 Connection shaft body 316 Lock mechanism A Round handle formation position B Semicircular handle formation position

Claims (3)

A left and right traveling crawler provided with a traveling machine body mounted with a reaping device and a threshing device, left and right traveling crawlers supporting the traveling machine body, and a driving unit having a steering handle and a driving seat. In the combine steering apparatus configured to change the turning radius of
The steering handle is formed by a semi-circular rear half wheel connected to a handle shaft and a front semi-circular wheel semi-circular connected to the rear wheel,
Combining operation characterized in that the front half wheel can be moved to a round handle forming position extending forward from the latter half wheel body, or a semicircular handle forming position folding the lower half wheel body downward. apparatus.   The both end sides of the front half ring body are connected to both end sides of the rear half ring body by left and right connecting shaft bodies, and the front half wheel body is configured to rotate around the connecting shaft body. Item 2. A combine control device according to Item 1.   A locking mechanism for maintaining the support posture of the front half wheel body, and a round handle forming position on the front side of the rear half wheel body or a semicircular handle forming position on the lower front side of the rear half wheel body via the lock mechanism The combine steering apparatus according to claim 1, wherein the combiner is configured to support the front half wheel.

Images