WO2010032505A1 - コンバイン - Google Patents
コンバイン Download PDFInfo
- Publication number
- WO2010032505A1 WO2010032505A1 PCT/JP2009/055056 JP2009055056W WO2010032505A1 WO 2010032505 A1 WO2010032505 A1 WO 2010032505A1 JP 2009055056 W JP2009055056 W JP 2009055056W WO 2010032505 A1 WO2010032505 A1 WO 2010032505A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- turning
- transmission
- shaft
- link
- hydraulic cylinder
- Prior art date
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D11/00—Steering non-deflectable wheels; Steering endless tracks or the like
- B62D11/001—Steering non-deflectable wheels; Steering endless tracks or the like control systems
- B62D11/006—Mechanical control systems
-
- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01D—HARVESTING; MOWING
- A01D41/00—Combines, i.e. harvesters or mowers combined with threshing devices
- A01D41/12—Details of combines
- A01D41/127—Control or measuring arrangements specially adapted for combines
-
- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01D—HARVESTING; MOWING
- A01D69/00—Driving mechanisms or parts thereof for harvesters or mowers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D11/00—Steering non-deflectable wheels; Steering endless tracks or the like
- B62D11/02—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides
- B62D11/06—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source
- B62D11/10—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears
- B62D11/14—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears differential power outputs being effected by additional power supply to one side, e.g. power originating from secondary power source
- B62D11/18—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears differential power outputs being effected by additional power supply to one side, e.g. power originating from secondary power source the additional power supply being supplied hydraulically
Definitions
- the present invention relates to a combine equipped with a reaping device and a threshing device. More specifically, the traveling body is steered to move along a row of uncut cereal rows in a field, and the grains are continuously fed. It relates to the combine harvester.
- Patent Document 1 An example of a combine having such a configuration is disclosed in Patent Document 1.
- the drive output amount of the linear transmission that is, the linear velocity of the traveling machine body is adjusted according to the operation amount of the linear manual operation tool such as the main transmission lever provided in the control unit.
- the traveling machine body does not go straight if the straight forward manual operating tool is in the neutral position, but by moving the straight forward manual operating tool, it travels forward or backward at a speed corresponding to the amount of operation.
- the drive output amount of the turning transmission that is, the turning direction and the turning speed of the traveling vehicle body are the operation direction and operation of the turning manual operation tool such as a steering handle disposed in front of the control seat in the control unit. Adjusted according to the amount.
- the manual operation tool for rectilinear movement and the manual operation tool for swivel travel straight through a mechanical interlocking mechanism using many rods, arms, pivot pins, etc., as described in Patent Document 1. It is interlocked and connected to the transmission for turning and turning, and by the action of this mechanical interlocking mechanism, it is possible to drive (maneuver) at the same operation interval as that of a four-wheeled vehicle, though it is of a crawler type.
- the present invention has a technical problem to solve these problems.
- claim 1 provides: “A linear transmission that transmits the power of the engine mounted on the traveling machine body to the left and right traveling units, a turning transmission that transmits the power to the left and right traveling units in a reverse rotation, and a linear manual transmission for the linear transmission
- the control body is configured to shift the linear transmission by forward and reverse rotation about the second axis in the control body, and further includes a steering box in which the control body is disposed, and the turning transmission. And an actuator configured to operate rotating, the actuator is assembled to the steering box.
- a hydraulic cylinder is provided as the actuator, and the hydraulic cylinder is a three-position cylinder having a neutral position that does not turn the turning transmission.” It is characterized by that.
- Claim 3 “In claim 2, the turning operation of the turning transmission by the hydraulic cylinder is regulated so as not to exceed a predetermined turning angle.” It is characterized by that.
- Claim 4 “In the description of claim 2 or 3, a connecting mechanism for connecting the hydraulic cylinder to the turning interlock mechanism is provided, the connecting mechanism is assembled to the steering box, and the hydraulic cylinder is connected to the connecting mechanism and the turning interlock mechanism.
- the turning transmission is configured to be turned via the ".” It is characterized by that.
- the connecting mechanism includes a turning link, and a turning output arm that turns an intermediate portion of the turning link in conjunction with forward / reverse turning about the first axis in the control body. It is pivotally attached, and one end of the turning link is connected to the turning transmission, and the other end of the turning link is connected to the hydraulic cylinder. It is characterized by that.
- the controller includes a control body that can rotate around two axes that are orthogonal to each other, and the control body is a positive body around the first axis that accompanies the turning operation of the turning manual operation tool.
- the turning transmission is operated to rotate by reverse rotation, and the linear transmission is operated to change speed by forward / reverse rotation around the second axis in accordance with the speed change operation of the straight advance manual operation tool.
- the control body has a function of turning the turning transmission in conjunction with a turning operation of the turning manual operation tool, and a function of turning the turning manual operation tool in conjunction with a speed change operation of the straight traveling manual operation tool.
- the turning transmission can be turned by an actuator, it can be turned left and right by the actuator separately from or in addition to the turning operation of the turning manual operation tool.
- the degree of turning can be freely adjusted by the actuator, so that the turning performance in the traveling machine body can be greatly improved and the turning can be made finely, especially in the combine The alignment operation can be performed accurately.
- the actuator since the actuator is assembled not in the vicinity of the turning transmission but in the steering box in which the control body is arranged, the transmission case can be easily configured, and the arrangement space is reduced. be able to.
- the actuator and the steering box can be configured as a unit, and since the unit can be assembled or replaced, maintenance can be easily performed.
- the actuator by using a hydraulic cylinder as the actuator, it is possible to reduce the size and weight.
- the turning operation by the hydraulic cylinder can be stopped by positioning the hydraulic cylinder in a neutral position, operability can be improved.
- the turning by the hydraulic cylinder can be regulated within the range of the predetermined turning angle, the erroneous excessive turning by the hydraulic cylinder can be surely avoided, and it is safe.
- the hydraulic cylinder since the hydraulic cylinder is connected to the turning interlocking mechanism by the connecting mechanism, the hydraulic cylinder can turn the turning transmission via the turning interlocking mechanism. Since the turning interlock mechanism is provided to transmit the operation of the control body to the turning transmission, the structure for transmitting the operation of the hydraulic cylinder to the turning transmission by using the turning interlock mechanism. The number of parts can be reduced. Therefore, the hydraulic cylinder and the coupling mechanism can be assembled in a compact manner in the steering box. Further, since the connecting structure of the hydraulic cylinder is assembled not on the turning transmission side but on the steering box side, the structure around the transmission case can be simplified, and the arrangement space can be reduced.
- FIG. 11 is a side sectional view taken along line XII-XII in FIG. 10.
- FIG. 13 is a plan sectional view taken along line XIII-XIII in FIGS. 11 and 12.
- FIG. 14 is a cross-sectional plan view taken along line XIV-XIV in FIGS. 11 and 12.
- FIG. 13 is a cross-sectional plan view taken along the line XV-XV in FIGS. 11 and 12.
- FIG. 13 is a side sectional view taken along line XVI-XVI in FIGS. 11 and 12.
- FIG. 14 is a side sectional view taken along line XVII-XVII in FIGS. 10 and 13. It is a principal part enlarged view of FIG. It is a principal part enlarged view of FIG. FIG.
- FIG. 16 is a side view taken along line XX-XX in FIG. 15. It is a figure which shows the 1st action state of FIG. It is a figure which shows the 2nd action state of FIG. It is a functional block diagram of a steering controller. It is a flowchart of the alignment control. It is a plane explanatory view showing an arrangement mode of a steering box in a modified structure. It is a principal part enlarged plan view of FIG. It is explanatory drawing which shows a mechanical interlocking mechanism typically. It is a plane sectional view of a steering box.
- FIG. 29 is a side view of XXXI-XXXI in FIG. 28. It is a figure which shows the 1st action state of FIG. It is a figure which shows the 2nd action state of FIG. It is a functional block diagram of a steering controller. It is a flowchart of the alignment control.
- a combine which is an example of a traveling vehicle includes a traveling machine body 1 supported by a pair of left and right traveling crawlers 2 as a traveling unit.
- a reaping device 3 that takes in a planted cereal culm (uncut cereal culm) in the field is harvested by a single-acting hydraulic cylinder 4 so as to be adjustable up and down.
- the traveling machine body 1 is equipped with a threshing device 5 with a feed chain 6 and a Glen tank 7 for storing grains after threshing in a side-by-side manner.
- the threshing device 5 is disposed on the left side in the traveling direction of the traveling machine body 1
- the Glen tank 7 is disposed on the right side in the traveling direction of the traveling machine body 1.
- a discharge auger 8 is provided at the rear of the traveling machine body 1 so as to be able to turn.
- the grain in the Glen tank 7 is carried out from the tip culling port of the discharge auger 8 to, for example, a truck bed or a container.
- a steering handle (manual operation tool for turning) as a turning manual operation tool for changing the turning direction and the turning speed of the traveling machine body 1 is provided.
- a control seat 11 on which an operator is seated.
- a side column 12 disposed on one side of the control seat 11 includes a main transmission lever 13 (straight forward manual operation tool) as a straight forward manual operation tool for performing a speed change operation of the traveling machine body 1, and a hydraulic continuously variable transmission described later.
- the main speed change lever 13 (straight forward manual operation tool) is used to move the traveling machine body 1 forward, stop, reverse and change its vehicle speed steplessly.
- the sub-shift lever 14 operates to change a sub-transmission mechanism 51 in the mission case 18 to be described later according to the working state, and the output and rotation speed of the straight-travel HST mechanism 53 to be described later are referred to as low speed, medium speed, high speed and neutral. This is for setting and maintaining the four speeds.
- the mowing clutch lever 15 is for power transmission operation to the mowing device 3
- the threshing clutch lever 16 is for power transmission operation to the threshing device 5.
- An engine 17 as a power source is disposed below the control unit 9.
- a transmission case 18 is disposed in front of the engine 17 for appropriately shifting the power from the engine 17 and transmitting it to the left and right traveling crawlers 2.
- the engine 17 is a diesel engine.
- the reaping device 3 includes a clipper-type cutting blade device 19, a culm pulling device 20 for four strips, a culm conveying device 21, and a weeding body 22.
- the cutting blade device 19 is disposed below a cutting frame 41 (see FIG. 1) constituting the framework of the cutting device 3.
- the grain raising device 20 is disposed above the cutting frame 41.
- the corn straw transporting device 21 is disposed between the corn straw pulling device 20 and the feed start end of the feed chain 6.
- the weed body 22 protrudes from the lower part of the grain raising device 20.
- the traveling machine body 1 continuously cuts unharmed cereals in the field by driving the reaping device 3 while driving the left and right traveling crawlers 2 by the engine 17 and moving in the field.
- the threshing device 5 includes a handling cylinder 23 for threshing the harvested cereal, a swing sorting mechanism 24 and a wind sorting mechanism 25 disposed below the handling cylinder 23, and a threshing that is taken out from the rear part of the handling cylinder 23.
- a dust-feeding port processing cylinder 26 for reprocessing an object is provided.
- the handling cylinder 23 is arranged in a handling chamber of the threshing device 5.
- the swing sorting mechanism 24 is for swinging and sorting the cereals threshed by the handling cylinder 23, and the wind sorting mechanism 25 is for wind sorting the threshed grains.
- the stocker side of the harvested cereals sent from the harvesting device 3 is inherited by the feed chain 6. Then, the tip side of the harvested cereal meal is carried into the threshing device 5 and threshed by the handling cylinder 23.
- the rotating shaft 95 (refer FIG. 3) of the handling cylinder 23 is extended along the feed direction (the advancing direction of the traveling body 1) of the harvested cereal meal by the feed chain 6.
- the first receiving bowl 27 where the most important grains such as fine grains are collected among the grains selected by the two sorting mechanisms 24, 25, the grain with a branch branch, the grain of ears, etc.
- a second receiving bowl 28 where the second item is collected.
- the two receiving rods 27 and 28 are horizontally provided above the rear portion of the traveling crawler 2 in a side view in order of the first receiving rod 27 and the second receiving rod 28 from the front side in the traveling direction of the traveling machine body 1.
- the first thing such as the fine grains collected in the first receiving bowl 27 through the sorting by the two sorting mechanisms 24 and 25 is the first conveyor 29 in the first receiving bowl 27 and the lifting in the milling cylinder 31. It is sent to the grain tank 7 via the grain conveyor 32 (see FIG. 3).
- Second items such as grain with branch stems are collected in the second receiving rod 28 behind the first receiving rod 27, and from here, the second conveyor 30 in the second receiving rod 28 and the reduction in the reducing cylinder 33 are collected. It is sent to the second processing cylinder 35 via the conveyor 34 (see FIG. 3). And after the second thing is rethreshed in the second treatment cylinder 35, it is returned to the threshing apparatus 5 and reselected. The sawdust is sucked into the dust exhaust fan 36 and discharged out of the machine from a discharge port (not shown) provided in the rear part of the threshing device 5.
- An exhaust chain 37 is disposed on the rear side (feed end side) of the feed chain 6.
- the waste (granulated soot) inherited from the rear end of the feed chain 6 to the waste chain 37 is discharged to the rear of the traveling machine body 1 in a long state, or the waste cutter 38 at the rear of the threshing device 5. After being cut to a short length as appropriate at, it is discharged to the rear of the traveling machine body 1.
- One of the motive power from the engine 17 is branched and transmitted in two directions of the reaping device 3 and the threshing device 5. Other power from the engine 17 is transmitted to the discharge auger 8.
- the branching power from the engine 17 toward the reaping device 3 is once transmitted to the hydraulic continuously variable transmission 50 of the transmission case 18 via the pulley / belt transmission system and the traveling clutch 89.
- the branch power from the engine 17 is appropriately shifted by the hydraulic continuously variable transmission 50 or the like of the mission case 18 and the left and right drive wheels 90 via the drive output shaft 77 projecting left and right outward from the mission case 18. It is configured to output to.
- the transmission case 18 includes the hydraulic continuously variable transmission 50 described above, a subtransmission mechanism 51 having a plurality of shift stages, and a differential mechanism 52 having a pair of left and right planetary gear mechanisms 68 (FIG. 4). reference).
- the hydraulic continuously variable transmission 50 includes a linear HST mechanism 53 (transmission for straight travel) composed of a first hydraulic pump 55 and a first hydraulic motor 56, and a swing composed of a second hydraulic pump 57 and a second hydraulic motor 58.
- the HST mechanism 54 (swivel transmission) is used.
- the power directed from the output shaft 49 of the engine 17 to the hydraulic continuously variable transmission 50 via the traveling clutch 89 is transmitted to the common pump shaft 59 that penetrates the first hydraulic pump 55 and the second hydraulic pump 57.
- a charge pump for supplying hydraulic oil to the hydraulic pumps 55 and 57 and the hydraulic motors 56 and 58 is attached to the common pump shaft 59.
- the charge pump can be interlocked with the common pump shaft 59 and is driven by the power of the engine 17.
- the straight-travel HST mechanism (straight-transmission transmission) 53 is in accordance with the amount of operation of the main transmission lever (straight-forward manual operation tool) 13 and the steering handle (turning manual operation tool) 10 disposed in the control unit 9.
- the linear motor that protrudes from the first hydraulic motor 56 The rotation direction and the number of rotations of the shaft 60 are arbitrarily adjusted.
- the rotational power of the linear motor shaft 60 is transmitted from the linear transmission gear mechanism 62 to the sub-transmission mechanism 51, which is a conventionally known gear mechanism, while the transmission is transmitted through the linear transmission gear mechanism 62 and the one-way clutch 63 described above. It is also transmitted to the cutting PTO shaft 64 projecting from the case 18.
- the power transmitted to the cutting PTO shaft 64 is transmitted to each device of the cutting device 3 via a cutting input shaft 43 in a horizontally long cutting input pipe 42 (see FIG. 1) constituting the framework of the cutting device 3. 19 to 21 are transmitted. Therefore, each of the devices 19 to 21 of the reaping device 3 is driven at a vehicle speed synchronization speed.
- the sub-transmission mechanism 51 has a two-stage adjustment range of the rotational power (rotation direction and number of rotations) from the linear motor shaft 60 by operating the sub-transmission lever 14 disposed in the control unit 9. This is for switching to a gear position. Note that a neutral position (a position where the output of the sub-shift is 0 (zero)) exists between the low speed and the high speed of the sub-shift.
- a parking brake shaft 65 that is a component of the auxiliary transmission mechanism 51 is provided with a parking brake 66 such as a wet multi-disc.
- Rotational power from the auxiliary transmission mechanism 51 is transmitted to the differential mechanism 52 from an auxiliary transmission output gear 67 fixed to the parking brake shaft 65.
- the differential mechanism 52 includes a pair of planetary gear mechanisms 68 arranged in a symmetrical manner and a relay shaft 69 positioned between the planetary gear mechanism 68 and the parking brake shaft 65.
- the auxiliary transmission output gear 67 of the parking brake shaft 65 meshes with an intermediate gear 70 attached to the relay shaft 69, and the intermediate gear 70 meshes with a center gear 76 (details will be described later) fixed to the sun gear shaft 75. ing.
- Each planetary gear mechanism 68 includes a pair of sun gears 71, a plurality of planetary gears 72 that mesh with the outer periphery of the sun gear 71, a ring gear 73 that meshes with the outer periphery of the planetary gear 72, and a plurality of planetary gears 72. And a carrier 74 rotatably supported on the shaft.
- the carriers 74 of the planetary gear mechanisms 68 are arranged so as to oppose each other at an appropriate interval on the same axis.
- a center gear 76 that meshes with the intermediate gear 70 is fixed to the center of the sun gear shaft 75 located between the planetary gear mechanisms 68.
- Sun gears 71 are fixed to both sides of the sun gear shaft 75 with the center gear 76 interposed therebetween.
- Each ring gear 73 having inner teeth on the inner peripheral surface and outer teeth on the outer peripheral surface is arranged concentrically on the sun gear shaft 75 with the inner teeth meshing with a plurality of planetary gears 72.
- Each ring gear 73 is rotatably supported by the drive output shaft 77 that protrudes left and right outward from the outer surface of the carrier 74.
- a driving wheel 90 is attached to the tip of the driving output shaft 77. Accordingly, the rotational power transmitted from the auxiliary transmission mechanism 51 to the left and right planetary gear mechanisms 68 is transmitted to the drive output shaft 77 of each carrier 74 and thus to the left and right drive wheels 90 at the same rotational speed in the same direction, so The crawler 2 is driven.
- the inclination angle of the rotary swash plate in the second hydraulic pump 57 is changed and adjusted in accordance with the amount of turning operation of the steering handle 10, and the second By changing the discharge direction and discharge amount of the hydraulic oil to the hydraulic motor 58, the rotation direction and the rotation speed of the turning motor shaft 61 protruding from the second hydraulic motor 58 are arbitrarily adjusted.
- the rotational power of the turning motor shaft 61 is transmitted from the turning transmission gear mechanism 85 to the steering clutch shaft 80 via the steering brake shaft 78 and the steering clutch 81.
- a pair of left and right transmission gears 86 and 87 are fixed to the steering clutch shaft 80, and the rotational power transmitted to the steering clutch shaft 80 is input from the left and right transmission gears 86 and 87 to the corresponding left and right input gears. It is transmitted to the gear mechanisms 82 and 83.
- the shift output from each of the motor shafts 60 and 61 is transmitted to the drive wheels 90 of the left and right traveling crawlers 2 via the auxiliary transmission mechanism 51 and the differential mechanism 52.
- the vehicle speed (traveling speed) and traveling direction of the traveling machine body 1 are determined.
- the rotation output from the linear motor shaft 60 is the same from the center gear 76 to the left and right sun gears 71.
- the left and right traveling crawlers 2 are driven at the same rotational speed in the same direction via the planetary gear 72 and the carrier 74 of both planetary gear mechanisms 68, and the traveling machine body 1 travels straight.
- the left planetary gear mechanism 68 is driven by the rotational power from the turning motor shaft 61.
- the right planetary gear mechanism 68 rotates in the reverse or forward direction.
- one of the drive wheels 90 of the left and right traveling crawlers 2 rotates forward and the other rotates backward, so that the traveling machine body 1 spin-turns on the spot.
- the traveling machine body 1 moves forward or backward while turning larger than the spin turn turning radius. Will turn left or right.
- the turning radius at this time is determined according to the speed difference between the left and right traveling crawlers 2.
- the branching power toward the threshing device 5 among the power from the engine 17 is transmitted to the threshing input shaft 92 via the threshing clutch 91.
- a part of the power transmitted to the threshing input shaft 92 is transmitted to the rotating shaft 94 of the dust feeding port processing cylinder 26, the rotating shaft 95 of the handling cylinder 23, and the waste chain 37 via the threshing drive mechanism 93.
- the Kara fan shaft 96 of the wind sorting mechanism 25 is also transmitted to the barrel 35, the swing shaft 97 of the swing selection mechanism 24, the dust discharge shaft 98 of the dust exhaust fan 36, and the waste cutter 38.
- the branching power via the dust removal shaft 98 is transmitted to the feed chain 6 via the feed chain clutch 99 and the feed chain shaft 100.
- the power from the engine 17 is directly transmitted to the reaping device 3 without passing through the mission case 18, thereby forcibly driving the reaping device 3 at a constant high speed regardless of whether the vehicle speed is fast or slow. It is the composition which can be made to do.
- the power from the engine 17 toward the discharge auger 8 is transferred to the bottom conveyor 104 in the Glen tank 7 and the vertical auger cylinder in the discharge auger 8 via the Glen input gear mechanism 102 and the auger clutch 103 for power transmission.
- the power is transmitted to the vertical conveyor 105, and then the power is transmitted to the discharge conveyor 107 in the horizontal auger cylinder of the discharge auger 8 via the transfer screw 106.
- a vertically long box-like steering column 112 is erected in front of the control seat 11 on the step floor member 111 constituting the bottom surface of the control unit 9. From the upper surface of the steering column 112, an upper handle shaft 113 that extends in the vertical direction and is rotatably supported at a substantially center inside the steering column 112 protrudes upward.
- a steering handle 10 is attached to the upper end of the upper handle shaft 113 as a turning manual operation tool.
- the lower end of the upper handle shaft 113 is connected to the lower handle shaft 115 protruding upward from the steering box 120 on the lower surface side of the step floor member 111 via a universal joint 114 (see FIG. 9).
- the steering box 120 is detachably attached to the support frame 118 that supports the step floor member 111 of the control unit 9 and has a sealed structure.
- the steering box 120 incorporates a mechanical interlocking mechanism 121 for the main speed change lever (manual operation tool for straight travel) 13 and the steering handle (manual operation tool for turning) 10.
- This mechanical interlocking mechanism 121 is 1.
- the traveling machine body 1 moves to the left or right with a smaller turning radius as the amount of rotation operation increases.
- the vehicle speed of the traveling machine body 1 (the forward and backward turn speeds) decreases as the turning radius decreases. 2.
- the turning operation direction of the steering handle 10 matches the turning direction of the traveling machine body 1 (the steering handle 10 is turned to the left). If it is turned, the traveling machine body 1 turns left, and if the steering handle 10 is turned to the right, the traveling machine body 1 turns right) 3.
- the main shift lever 13 If the main shift lever 13 is in the neutral position, it does not function even if the steering handle 10 is operated. In order to execute the various operations, the operation force from the main transmission lever 13 and the steering handle 10 is appropriately converted, and the transmission output shaft 136 and the turning output shaft 164 projecting outward from the side surface of the steering box 120 (details) Is configured to be transmitted to a later described).
- the mechanical interlocking mechanism 121 includes a vertical turning input shaft 122 pivotally supported at both ends in the steering box 120.
- the gear 123 fixed to the upper end portion of the turning input shaft 122 and the gear 116 fixed to the lower end portion of the lower handle shaft 115 protruding into the steering box 120 are engaged with each other, thereby turning the lower handle shaft 115 and the lower handle shaft 115.
- the input shaft 122 is connected to be able to transmit power. Accordingly, the turning operation force of the steering handle 10 is transmitted to the turning input shaft 122 via the lower handle shaft 115.
- a slider 125 is slidably fitted to the upper part of the turning input shaft 122, and a holder member 126 is fitted to the lower part so as not to rotate and slide.
- the slider 125 rotates around the vertical axis P together with the swivel input shaft 122 in a state in which the slider 125 can freely slide along the vertical axis P direction of the swivel input shaft 122 with a ball key 127 or the like. It is configured.
- a winding spring 128 is fitted on a part of the turning input shaft 122 below the holder member 126.
- the start end 128 a and the end end 128 b of the winding spring 128 sandwich both the upward convex pin 129 fixed to the steering box 120 and the downward convex pin 130 fixed to the holder member 126.
- the steering handle 10 is configured to always urge the steering handle 10 back to the neutral position (straight running position) from the position rotated left and right. That is, the turning operation of the steering handle 10 in the left-right direction is performed against the elasticity of the winding spring 128. Then, the turning operation to the original neutral position (straight running position) uses the elastic restoring force of the winding spring 128.
- a control body 131 configured in a ring shape surrounding the periphery of the turning input shaft 122 in a plan view when viewed from the direction of the longitudinal axis P of the turning input shaft 122 is disposed.
- a pair of left and right inward boss portions 132 are provided on a portion of the inner surface of the control body 131 on the horizontal axis S that passes through the rotation center of the turning input shaft 122 in a plan view and is orthogonal to the longitudinal axis P of the turning input shaft 122. Is formed.
- the control body 131 is configured to be rotatable about the horizontal axis S by pivotally attaching the both inward boss portions 132 to the holder member 126 by the screw shaft 133.
- control body 131 is rotatable around two axes P and S orthogonal to each other.
- the vertical axis P corresponds to the first axis described in the claims
- the horizontal axis S corresponds to the second axis described in the claims.
- a circular cam 134 extending in the circumferential direction is formed on the outer periphery of the control body 131.
- the circular cam 134 is provided with a cam groove 134a extending over the entire circumference.
- a main transmission lever input shaft 135 is disposed horizontally on one of the left and right sides of the turning input shaft 122, and on the other side, the lateral transmission output shaft 136 is disposed. Are placed sideways.
- the main transmission lever input shaft 135 and the transmission output shaft 136 extend in parallel with each other in plan view and are pivotally supported by the steering box 120.
- One end portions of the main transmission lever input shaft 135 and the transmission output shaft 136 protrude outward from the side surfaces of the steering box 120.
- the main transmission lever input shaft 135 protrudes from the steering box 120 toward the left and right center side of the traveling machine body 1 and is fixed to the protruding end of the main transmission lever input shaft 135.
- a main transmission lever (straight forward manual operation tool) 13 on the side column 12 is connected to the transmission arm 137 via interlocking connecting means 138 such as a rod so that the main transmission lever input shaft 135 is rotated by its forward / backward tilting operation. Are connected.
- the shift output shaft 136 protrudes from the steering box 120 toward the rear side of the traveling machine body 1, and the shift output arm 139 fixed to the protruding end of the shift output shaft 136 moves straight on the transmission case 18.
- the HST mechanism (linear transmission) 53 is connected to a linear control shaft 149 (see FIG. 4) via a linear link mechanism 140 so as to perform a shift operation by rotation of the transmission output shaft 136. Yes.
- the rectilinear control shaft 149 is for adjusting the inclination angle (swash plate angle) of the rotary swash plate of the first hydraulic pump 55 in the rectilinear HST mechanism (straight transmission) 53, and the rectilinear HST mechanism 53. It functions as an adjustment unit that adjusts the shift output of the. That is, by adjusting the swash plate angle of the first hydraulic pump 55 by forward / reverse rotation of the rectilinear control shaft 149, the rotational speed control and forward / reverse switching of the first hydraulic motor 56 are executed, and the traveling speed (vehicle speed) is adjusted. Stepless change and forward / reverse switching are performed.
- the straight link mechanism 140 includes a lateral support shaft 144 pivotally supported by a bracket 143 fixed to the upper surface of the transmission case 18 and a shift output arm 139 and a lateral support.
- a speed change rod 147 is provided to connect the fixed straight operation arm 148.
- One end of the relay rod 142 is connected to the speed change output arm 139 via a ball joint joint, and the other end of the relay rod 142 is connected to the first swing arm 145 via a ball joint joint.
- One end of the speed change rod 147 is connected to the second swing arm 146 via a ball joint, and the other end of the speed change rod 147 is directed laterally to the straight operation arm 148 on the straight control shaft 149 side. It is pivotally attached via a pivot pin.
- a pair of main transmission fork arms 151 is fixed to a portion of the main transmission lever input shaft 135 in the steering box 120, and a ball bearing 152 provided at the tip of the main transmission fork arms 151 is a slider 125.
- the slider 125 is configured to slide up and down along the turning input shaft 122 by the rotation of the main transmission lever input shaft 135 and the turning operation of the main transmission lever 13. That is, the slider 125 is located at a position indicated by a solid line in FIG. 12 when the main transmission lever 13 is in the neutral position, but is moved up and down by a rotation operation from the neutral position of the main transmission lever 13 back and forth. Become.
- the slider 125 and the control body 131 are connected to each other by a swing link 153 having pins 154 at both ends.
- the main speed change lever (straight forward manual operation tool) 13 When the main speed change lever (straight forward manual operation tool) 13 is in the neutral position, the slider 125 does not move up and down, and the control body 131 remains in the horizontal position at the neutral position and does not tilt and rotate.
- the main speed change lever 13 When the main speed change lever 13 is rotated back and forth from the neutral position, the slider 125 moves up and down, and the control body 131 appropriately moves in the vertical direction around the horizontal axis S around the screw shaft 133 with the horizontal posture interposed therebetween.
- the angle ⁇ 1 and ⁇ 2 are tilted and rotated (see FIG. 16).
- An intermediate shaft 155 serving as a straight traveling shaft extending in parallel with the transmission output shaft 136 is pivotally supported in a portion of the steering box 120 directly below the transmission output shaft 136 so as to protrude into the steering box 120. .
- the intermediate shaft 155 is for converting the rotation amount of the control body 131 around the horizontal axis S into the control amount of the straight-travel HST mechanism 53.
- a straight link 156 is provided at the inner end of the intermediate shaft 155 so as to freely rotate in the vertical direction.
- a portion of the straight link 156 on the orthogonal axis W extending perpendicularly to the horizontal axis S through the rotation center of the turning input shaft 122 in a plan view is formed in the cam groove 134a of the circular cam 134 of the control body 131 in the portion.
- a shifting slider member 157 that is slidably engaged in the circumferential direction is provided so as to freely rotate around the orthogonal axis W.
- the shifting slider member 157 includes a shaft portion 157a that is rotatably supported by a linear link 156 by a ball bearing 157b, and a spherical body 157c that is integrally provided at the tip of the shaft portion 157a. It is comprised by.
- the spherical body 157c of the speed change slider member 157 is slidably and rotatably inserted into the cam groove 134a of the circular cam 134 in the control body 131.
- the front end side of the speed change output link 158 that is rotatably connected to the speed change output shaft 136 is connected to the straight link 156 via a connection link 159. For this reason, in conjunction with the tilt rotation of the control body 131 about the horizontal axis S, the straight link 156 and thus the transmission output link 158 rotate up and down.
- the base end of the non-decelerating arm 160 is rotatably fitted to the speed change output shaft 136.
- the non-decelerating arm 160 is interlocked with the vertical movement of the main transmission fork arm 151 by fitting and engaging a pin 161 provided at the front end of the main transmission fork arm 151 in a long hole 160a formed at the front end. It is comprised so that it may rotate (refer FIG. 17).
- the transmission output link 158 or the non-deceleration arm 160 is selected at a portion of the transmission output shaft 136 between the transmission output link 158 and the non-deceleration arm 160 so as to rotate integrally with the transmission output shaft 136.
- a switching member 162 for connection is provided so as to be slidable in the axial direction of the speed change output shaft 136.
- the difference in speed between the left and right crawlers during turning should not be too great (insensitive turning feeling), or turning on the road or in dry fields, or on wetlands and mud
- the turning performance can be improved (the turning feeling can be agile).
- the switching operation mechanism 169 is configured as described below. That is, as shown in FIG. 16, a switching operation shaft 170 extending parallel to the speed change output shaft 136 is supported on the steering box 120 so as to be slidable and rotatable.
- the switching plate 171 fixed to the switching operation shaft 170 is fitted and engaged with an annular groove 172 formed in the switching member 162.
- One end of the switching operation shaft 170 protrudes outside the steering box 120, and a handle 173 is provided at the protruding end.
- the switching operation shaft 170 By switching the switching operation shaft 170 in the axial direction while holding the handle 173, the switching between the turning deceleration state and the turning non-deceleration state is performed from the outside of the steering box 120.
- the switching operation shaft 170 is held in a turning deceleration state in which the transmission output shaft 136 and the transmission output link 158 are coupled, and a turning non-deceleration state in which the transmission output shaft 136 and the non-deceleration arm 160 are coupled.
- a ball clutch 174 is provided.
- a turning output shaft 164 as a turning shaft extending in a direction orthogonal to the speed change output shaft 136 is projected to the inside and outside of the steering box 120 at a portion of the side surface of the steering box 120 substantially directly below the speed change output shaft 136. It is pivotally supported. As will be described in detail later, the turning output shaft 164 is for converting the turning amount of the control body 131 around the vertical axis P into the control amount of the turning HST mechanism (turning transmission) 54.
- the base end of the turning link 165 is fixed to the end of the turning output shaft 164 in the steering box 120.
- a part of the turning link 165 on the horizontal axis S in a plan view has a turning slider member 166 that engages with a cam groove 134a of the circular cam 134 of the control body 131 slidably in the circumferential direction. Is provided.
- the turning slider member 166 includes a shaft portion 166a attached to the turning link 165, a sphere 166b integrally provided at the tip of the shaft portion 166a, and a sphere 166b that is rotatable. It is comprised by the ring body 166c fitted so that it could incline freely in arbitrary directions with respect to the axis line of the axial part 166a.
- the ring body 166c of the turning slider member 166 is slidably and rotatably inserted into the cam groove 134a of the circular cam 134 in the control body 131.
- the axis AX1 of the intermediate shaft 155 and the axis AX2 of the turning output shaft 164 are located on substantially the same plane.
- the turning radius r1 of the straight link 156 (which can be said to be the length from the intermediate shaft 155 to the shifting slider member 157) and the turning radius r2 of the turning link 165 (turning)
- the turning output arm 167 fixed to the outer end of the turning output shaft 164 is provided with a turning interlock mechanism 180 on the turning control shaft 189 protruding from the turning HST mechanism (turning transmission) 54 of the transmission case 18. Via the rotation output shaft 164 so as to perform a speed change operation.
- the turning control shaft 189 is for adjusting the inclination angle (swash plate angle) of the rotary swash plate of the second hydraulic pump 57 in the turning HST mechanism 54, and adjusts the shift output of the turning HST mechanism 54. Functions as a control unit.
- the turning interlock mechanism 180 includes a relay support shaft 184 that is rotatably supported by a bracket 183 fixed to the upper surface of the mission case 18.
- One end of a relay rod 182 having a turnbuckle 181 is connected to the fixed first arm 185.
- the turning interlock mechanism 180 connects the second arm 186 fixed to the other end of the relay support shaft 184 and the turning operation arm 188 fixed to the turning control shaft 189.
- a swivel rod 187 is provided.
- a stroke absorbing mechanism 200 having a built-in spring 199 for absorbing a reciprocating stroke in the relay rod 182 is provided in the middle of the relay rod 182 in the turning interlock mechanism 180.
- the other end of the relay rod 182 is provided with a connecting mechanism 210 that connects a hydraulic cylinder 193 for alignment.
- the hydraulic cylinder 193 is attached to the side surface of the steering box 120.
- the coupling mechanism 210 is configured to transmit the operation of the hydraulic cylinder 193 to the turning HST mechanism (turning transmission) 54 via the turning interlocking mechanism 180.
- the connecting mechanism 210 includes a turning link 191 configured in a balance shape, and an intermediate portion of the turning link 191 is pivotally attached to the turning output arm 167 by a center pin 190.
- One end of the turning link 191 is connected to the other end of the relay rod 182 by an action pin 192.
- the other end of the turning link 191 is connected to the tip of the piston rod 194 in the hydraulic cylinder 193 by a fulcrum pin 195.
- the hydraulic cylinder 193 has a three-position cylinder configuration in which the piston rod 194 is operated in the front-rear direction across a neutral position.
- the piston rod 194 of the hydraulic cylinder 193 is neutral as shown in FIG.
- the fulcrum pin 195 coincides with the axis of the turning output shaft 164 when viewed from the axial direction of the turning output shaft 164.
- a three-position hydraulic switching valve 198 In the middle of the hydraulic circuit 197 from the hydraulic pump 196 driven to rotate by the engine 17 to the hydraulic cylinder 193, a three-position hydraulic switching valve 198 is provided.
- the three-position hydraulic switching valve 198 includes a right-turn solenoid 198a that moves the piston rod 194 backward, a spring 198c that returns the right-turn solenoid 198a to return the piston rod 194 to the neutral position, and a left-turn that moves the piston rod 194 in a protruding manner.
- a rotating solenoid 198b and a spring 198d for returning the left-turning solenoid 198b so as to return the piston rod 194 to the neutral position are provided.
- the steering handle (manual operation tool for turning) 10 is provided with a right turning switch 205 and a left turning switch 206.
- the right turn switch 205 When the right turn switch 205 is pressed, the right turn solenoid 198a is excited, the piston rod 194 of the hydraulic cylinder 193 is retracted from its neutral position, and when the left turn switch 206 is pressed, the left turn solenoid 198b is excited, The piston rod 194 is configured to project from its neutral position.
- Both the right turn switch 205 and the left turn switch 206 are manually operated. However, when the hand is released from the switch, the right turn solenoid 198a or the left turn solenoid 198b is demagnetized, and the corresponding springs 198c and 198d are respectively provided. To actuate the piston rod 194 back to its neutral position.
- the right turn switch 205 and the left turn switch 206 are composed of a single switch that can be operated in both the left and right directions. You may make it turn left.
- the minute turning to the left and right of the traveling machine body 1 by operating the right turning switch 205 or the left turning switch 206 is configured to function when the traveling machine body 1 is traveling straight.
- the steering column 112 is provided with a rectilinear sensor 208 (see FIG. 23) as means for detecting the rotation of the steering handle 10.
- the straight traveling sensor 208 detects whether or not the steering handle 10 is in a neutral region (including a neutral position and a so-called play region), that is, whether or not the traveling machine body 1 is in a straight traveling state.
- the straight steering sensor 208 detects that the steering handle 10 is not in the neutral region, in other words, when the traveling vehicle body 1 is swung to the left or right by the steering handle 10, the hydraulic pressure of the hydraulic circuit 197 The switching valve 198 is not switched, so that the operations by the right turn switch 205 and the left turn switch 206 do not function.
- the traveling machine body 1 When the traveling machine body 1 is largely turned left and right by the operation of the steering handle 10, it is usually not during cutting and threshing. If the right turn switch 205 and the left turn switch 206 are erroneously operated at times other than during the mowing and threshing operation, the traveling machine body 1 may face an unexpected direction against the operator's intention. Therefore, when the traveling machine body 1 is largely turned left and right by the steering handle 10, the turning operation by the right turning switch 205 and the left turning switch 206 is restricted so as not to function.
- a flow rate adjusting valve is provided in the hydraulic circuit 197 for the hydraulic cylinder 193 or the three-position hydraulic switching valve is provided. This can be accomplished by means such as increasing and decreasing the speed of the projecting and retracting operations from the neutral position at 198.
- the steering box 120 includes a die cast or cast upper box body 120a and a die cast or cast lower box body on a plane A (see FIG. 11) perpendicular to the longitudinal axis P of the turning input shaft 122.
- the structure is divided in two with 120b.
- Both box bodies 120a and 120b are detachably coupled with a plurality of bolts (not shown) with a sealing gasket (not shown) sandwiched therebetween.
- hydraulic oil used in various hydraulic devices in the combine for example, a hydraulic cylinder that moves the reaping device 3 up and down
- the mechanical interlocking mechanism 121 is lubricated by the incoming and outgoing hydraulic oil. It has become.
- the steering box 120 is provided with an inlet and an outlet through which hydraulic oil enters and exits.
- both the HST mechanisms 53, 54 does not drive and the traveling body 1 can be reliably maintained in a stop state. Therefore, for example, when performing maintenance work, it is possible to reliably avoid the possibility that the traveling machine body 1 behaves unexpectedly against the operator's intention by simply setting the main transmission lever 13 to the neutral position. Can be secured sufficiently.
- the shift slider member 157 moves up and down via the straight link 156, the connection link 159, the shift output link 158, the switching member 162, the shift output shaft 136, the shift output arm 139, and the straight link mechanism 140. , And is transmitted to the rectilinear control shaft 149 of the rectilinear HST mechanism 53.
- the straight traveling HST mechanism 53 performs a speed change operation from the neutral position by the tilt rotation around the horizontal axis S in the control body 131.
- the turning slider member 166 that engages with the portion on the horizontal axis S of the circular cam 134 in the control body 131 is the steering handle 10.
- the turning HST mechanism 54 does not shift from the neutral position. Accordingly, the same rotational speed is simultaneously transmitted from the straight traveling HST mechanism 53 to the left and right traveling crawlers 2, and the traveling machine body 1 travels straight in the forward or backward direction.
- the travel speed (vehicle speed) during straight travel is determined by the amount of rotation of the straight travel control shaft 149 in the straight travel HST mechanism 53, and the amount of travel is the vertical travel distances L 1 and L 2 of the speed change slider member 157. Since the tilt rotation angles ⁇ 1 and ⁇ 2 from the neutral position in the control body 131 and the amount of tilting operation of the main transmission lever 13 are increased or decreased, the traveling speed during straight traveling in the traveling machine body 1 is determined by the main transmission lever 13. It can be adjusted in proportion to the operation amount from the neutral position.
- the steering handle 10 is rotated left or right from the neutral position to rotate the turning input shaft 122.
- the control body 131 rotates together with the turning input shaft 122 while being tilted and rotated about the horizontal axis S.
- the turning slider member 166 engaged with the portion on the horizontal axis S of the circular cam 134 moves up and down by the rotation of the turning input shaft 122, and the up and down movement corresponds to the turning link 165 and the turning output.
- the pivot link 191 is transmitted to the pivot link 191 via the shaft 164 and the pivot output arm 167, and the pivot link 191 is centered on the fulcrum pin 195 and the pivot output shaft 164 located on the same axis as shown in FIGS. It rotates clockwise or counterclockwise, and this rotation is transmitted to the turning control shaft 189 of the turning HST mechanism 54. As a result, the turning HST mechanism 54 shifts from the neutral position.
- the shift operation amount from the neutral position in the turning HST mechanism 54 that is, the turning amount of the turning control shaft 189 is rotated by the turning input shaft 122 in a state where the control body 131 is rotated forward and backward around the horizontal axis S.
- This is proportional to the amount of movement of the turning slider member 166 in the vertical direction and the turning operation angle (turning operation amount) of the steering handle 10 from the neutral position.
- the speed difference between the left and right traveling crawlers 2 increases in proportion to the rotation operation angle (rotation operation amount) from the neutral position of the steering handle 10, and the turning radius of the traveling machine body 1 decreases.
- the shifting slider member 157 that engages with the circular cam 134 of the control body 131 is moved up and down by tilt rotation around the horizontal axis S, so that linear control is performed in proportion to the amount of rotation of the steering handle 10.
- the shaft 149 can be rotated in the opposite direction, and the turning speed of the traveling machine body 1 can be reduced according to the turning radius at that time.
- the control body 131 is rotated by the turning input shaft 122 while being tilted and rotated about the horizontal axis S, and is engaged with the circular cam 134 of the control body 131.
- the shifting slider member 157 that moves moves from the portion on the orthogonal axis W of the circular cam 134 to the portion on the horizontal axis S as the control body 131 rotates.
- the vertical movement distances L1 and L2 of the shifting slider member 157 are smaller than those in the position on the orthogonal axis W of the circular cam 134, and as a result, the rotation amount of the linear control shaft 149 (linear advance)
- the transmission speed of the HST mechanism 53 for use in the vehicle is reduced, the number of rotations transmitted to the left and right traveling crawlers 2 is controlled in the deceleration direction, and the traveling speed when the traveling machine body 1 turns is decreased.
- the speed difference between the left and right traveling crawlers 2 increases, the turning radius decreases, and the speed in the straight traveling direction decreases, so that the traveling machine body 1 as a whole travels. Since the speed (vehicle speed) is slowed down, the centrifugal force acting on the traveling machine body 1 outwardly from the turning can be reduced during turning. Further, since the tilting and turning direction around the horizontal axis S of the control body 131 is reversed with respect to the turning operation of the steering handle 10 at the time of forward movement and reverse movement, the steering handle at any time of forward and backward movement. The 10 rotation operation directions and the turning direction of the traveling machine body 1 coincide with each other.
- the operation of the switching member 162 by the switching operation mechanism 169 switches the state in which the speed change output link 158 is coupled to the speed change output shaft 136 to the state in which the non-deceleration arm 160 is coupled to the speed change output shaft 136.
- the operation of the main transmission lever 13 is performed as it is regardless of the turning operation of the steering handle 10 as it is.
- the transmission output shaft 136, the transmission output arm 139, and the straight travel link mechanism 140 are transmitted to the straight travel control shaft 149 of the straight travel HST mechanism 53.
- the turning operation of the steering handle 10 and the tilting operation of the main speed change lever 13 are not directly related to each other, and the control body 131 is released from the deceleration state by the circular cam 134, and the main speed change lever 13 is tilted.
- a traveling speed (vehicle speed) proportional to the operation amount is maintained. Therefore, it is possible to make the combine a wet field specification so as to suppress the sinking into the soft ground.
- a steering controller 209 such as a microcomputer as a control means is a central processing unit (CPU) for executing various arithmetic processes and controls, and a read-only for storing data in a control program Memory (ROM), read / write memory (RAM) for storing data temporarily with a control program, clock as a timer function, input / output interface to exchange data with each input system device (sensor, actuator, etc.) Etc.
- CPU central processing unit
- ROM control program Memory
- RAM read / write memory
- a straight advance sensor 208 that is a rotation detection means of the steering handle 10, a right turn switch 205 provided on the steering handle 10, a left turn switch 206, and a side column 12 are provided.
- the alignment switch 207 and the like are connected.
- a right turning solenoid 198a and a left turning solenoid 198b for switching the hydraulic pressure switching valve 198 are connected.
- the straight traveling sensor 208 determines that the traveling machine body 1 is not in the straight traveling state (No in S1), it is determined whether or not the alignment switch 207 is in the on state (S8).
- the alignment switch 207 is in the off state (No in S8), the process returns.
- the alignment switch 207 is in the on state (Yes in S8), it is determined whether or not the left turn switch 206 is in the on state (S9).
- the left turn switch 206 When the left turn switch 206 is in the off state (No in S9), it is determined whether or not the right turn switch 205 is in the on state (S12). If the right turn switch 205 is not in the on state (No in S12), even if the alignment switch 207 is in the on state, the right turn switch 205 and the left turn switch 206 are in a state of being not operated, and the process returns. To do.
- the control body 131 that can rotate around the two axes P and S orthogonal to each other is provided, and the control body 131 rotates in the forward and reverse directions around the vertical line P as the steering handle 10 is operated.
- the turning HST mechanism 54 is actuated by movement, and the rectilinear HST mechanism 53 is actuated by forward / reverse rotation about the horizontal axis S associated with the operation of the main speed change lever 13.
- the traveling body 1 turns left or right with a smaller turning radius as the turning operation amount increases.
- the operation of “doing” can be executed by both the forward / reverse rotation around the vertical axis P and the forward / reverse rotation around the horizontal axis S in the control body 131.
- control body 131 operates the turning HST mechanism 54 in conjunction with the turning operation of the steering handle 10, and the function in which the straight traveling HST mechanism 53 is operated in conjunction with the tilting operation of the main transmission lever 13. Both will be combined.
- the axis AX2 of the turning output shaft 164 that rotates in conjunction with the turning operation of the steering handle 10 and the axis AX1 of the intermediate shaft 155 that rotates in conjunction with the tilting operation of the main transmission lever 13 are substantially provided. Therefore, the operation range of the control body 131 (particularly the vertical tilt rotation range around the horizontal axis S) is limited. Compared with the structure of the operation system using many arms, pivot pins, etc., the dimension along the vertical axis P can be greatly shortened in the mechanical interlocking mechanism 121. Therefore, the structure of the mechanical interlocking mechanism 121 can be remarkably simplified and reduced in size compared with the case of Patent Document 1, and the entire operation system can be made compact.
- the swing link 191 can rotate the swing output regardless of the rotation of the swing output shaft 164 and the swing output arm 167. Since the center pin 190 with respect to the arm 167 is rotated clockwise or counterclockwise and this rotation is transmitted to the turning control shaft 189 of the turning HST mechanism 54, the traveling machine body 1 turns slightly. Will be.
- the minute turning operation by the alignment hydraulic cylinder 193 can be performed separately from the turning operation of the steering handle (turning manual operation tool) 10, and the steering handle (turning manual operation tool). ) It can be performed even during the 10 turning operation.
- the alignment switch 207 is operated to selectively switch between turning and not turning by the hydraulic cylinder 193. You can also.
- the turning by the alignment hydraulic cylinder 193 is restricted so as not to exceed the clockwise turning angle ⁇ 1 and the counterclockwise turning angle ⁇ 2 of the turning link 191. It is possible to reliably avoid erroneous excessive turning by the hydraulic cylinder 193 and to ensure safety.
- the alignment hydraulic cylinder 193 is connected to the turning interlock mechanism 180 that connects the control body 131 and the turning HST mechanism 54 via the connecting mechanism 210, and the connecting mechanism 210 is connected to the steering box 120. Is assembled. That is, by using the turning interlock mechanism 180, the structure for turning the turning HST mechanism 54 by the hydraulic cylinder 193 can be simplified, and the structure can be made compact and assembled to the steering box 120. In addition, since the hydraulic cylinder 193 and the steering box 120 can be unitized, assembly and replacement are easy, and maintenance can be easily performed.
- the configuration around the transmission case 18 can be simplified.
- the installation space can be reduced.
- FIG. 1 The swivel interlocking mechanism 180 having a modified structure basically exhibits the same function as the swivel interlocking mechanism 180 described above. However, in the modified structure, the connecting mechanism 210 for connecting the forward / reverse rotating electric motor 293 for alignment is provided at the other end of the relay rod 182 in the turning interlock mechanism 180 first. This is different from the structure of the swivel interlocking mechanism 180 described.
- the electric motor 293 is attached to the side surface of the steering box 120.
- the coupling mechanism 210 is configured to transmit the operation of the electric motor 293 to the turning HST mechanism (turning transmission) 54 via the turning interlocking mechanism 180.
- a cam disk 295 is fixed to the output shaft 294 of the electric motor 293.
- One end of a rod 296 is pivotally attached by a pin 298 to a portion of the cam disk 295 that is eccentric from the output shaft 294 by an appropriate distance.
- the connecting mechanism 210 includes a turning link 191 configured in a balance shape, and an intermediate portion of the turning link 191 is pivotally attached to the turning output arm 167 by a center pin 190.
- One end of the turning link 191 is connected to the other end of the relay rod 182 by an action pin 192.
- the other end of the rod 296 attached to the cam disk 295 of the electric motor 293 is connected to the other end of the turning link 191 by a fulcrum pin 195.
- the fulcrum pin 195 at the other end of the swing link 191 is aligned with the axis of the swing output shaft 164 when viewed from the axial direction of the swing output shaft 164. They are in a neutral position where they match.
- the turning link 191 has a small angle ⁇ 1 counterclockwise around the center pin 190.
- the electric motor 293 rotates the cam disk 295 counterclockwise by an angle ⁇ 2 from the neutral position
- the turning link 191 is turned.
- the ball clutch 201 provided in the electric motor 293 or the steering box 120 is fitted and engaged with the outer peripheral surface of the cam disk 295.
- the ball clutch 201 is engaged and engaged when the cam disk 295 is rotated by ⁇ 1 in the clockwise direction.
- the ball clutch 201 is engaged and engaged when the cam disk 295 is rotated counterclockwise by ⁇ 1.
- a third recess 295c is provided to hold the position.
- notch grooves 295d, 295e, and 295f are provided along the circumferential direction.
- three contactless type three are provided on the outer side of the cam disk 295.
- Limit switches 202, 203, and 204 are disposed along the circumferential direction, and among the three limit switches 202, 203, and 204, the first limit switch 202 has the cam disk 295 in the neutral position described above.
- the electric motor 293 stops rotating, and the second limit switch 203 is operated when the cam disk 295 rotates clockwise by the angle ⁇ 1.
- the electric motor 293 stops rotating clockwise, and the third limit switch 204 is connected to the cam disk.
- the third cutout groove 295F it is configured so as to stop the counterclockwise rotation of the electric motor 293.
- the electric motor 293 rotates the cam disk 295 in the clockwise direction when the right turn switch 205 provided on the steering handle 10 is turned on.
- the cam disk 295 is configured to rotate counterclockwise when the provided left turn switch 206 is turned on.
- Both the right turn switch 205 and the left turn switch 206 are manually operated, but when the hand is released from the switch, the electric motor 293 rotates in a direction to return the turn link 191 to the neutral position.
- the right turn switch 205 and the left turn switch 206 are composed of a single switch that can be operated in both the left and right directions. You may make it turn left.
- the minute turning to the left and right of the traveling machine body 1 by operating the right turning switch 205 or the left turning switch 206 is configured to function when the traveling machine body 1 is traveling straight.
- the steering column 112 is provided with a rectilinear sensor 208 (see FIG. 32) as means for detecting rotation of the steering handle 10.
- the straight traveling sensor 208 detects whether or not the steering handle 10 is in a neutral region (including a neutral position and a so-called play region), that is, whether or not the traveling machine body 1 is in a straight traveling state.
- the straight steering sensor 208 detects that the steering handle 10 is not in the neutral region, in other words, when the traveling vehicle body 1 is largely turning left or right by the steering handle 10, the electric motor 293 is rotated. The operation by the right turn switch 205 and the left turn switch 206 is prevented from functioning.
- the traveling machine body 1 When the traveling machine body 1 is largely turned left and right by the operation of the steering handle 10, it is usually not during cutting and threshing. If the right turn switch 205 and the left turn switch 206 are erroneously operated at times other than during the mowing and threshing operation, the traveling machine body 1 may face an unexpected direction against the operator's intention. Therefore, when the traveling machine body 1 is largely turned left and right by the steering handle 10, the turning operation by the right turning switch 205 and the left turning switch 206 is restricted so as not to function.
- the alignment switch 207 when the alignment switch 207 is in the on state (when the right turning switch 205 or the left turning switch 206 is operated with the steering handle 10 turned largely), It is configured to turn at a slower speed than when the alignment switch 207 is in the off state (when the right turn switch 205 or the left turn switch 206 is operated with the steering handle 10 in the neutral region).
- the small turn is performed slowly to improve the operability during the turn. Yes.
- a delay circuit is provided in an electric circuit that connects the electric motor 293 and the left and right turning switches 205 and 206. Can be achieved.
- a steering controller 209 such as a microcomputer as a control means is a central processing unit (CPU) for executing various arithmetic processes and controls, and a read-only for storing data in a control program Memory (ROM), read / write memory (RAM) for storing data temporarily with a control program, clock as a timer function, input / output interface to exchange data with each input system device (sensor, actuator, etc.) Etc.
- CPU central processing unit
- ROM control program Memory
- RAM read / write memory
- a straight advance sensor 208 that is a rotation detection means of the steering handle 10, a right turn switch 205 provided on the steering handle 10, a left turn switch 206, and a side column 12 are provided.
- the alignment switch 207, the first limit switch 202 for detecting the rotation direction of the electric motor 293, the second limit switch 203, the third limit switch 204, and the like are connected.
- An electric motor 293 and the like are connected to the output interface of the steering controller 209.
- the straight traveling sensor 208 determines that the traveling machine body 1 is not in the straight traveling state (No in SA1), it is determined whether or not the alignment switch 207 is in the on state (SA8).
- the alignment switch 207 is in the off state (No in SA8), the process returns.
- the alignment switch 207 is in the on state (Yes in SA8), it is determined whether or not the left turn switch 206 is in the on state (SA9).
- the turning link 191 is turned into the turning output shaft 164 and the turning by rotating the disc cam 295 clockwise or counterclockwise from the neutral position by the electric motor 293 for alignment. Regardless of the rotation of the output arm 167, it rotates counterclockwise or clockwise around the center pin 190 with respect to the turning output arm 167, and this turning is applied to the turning control shaft 189 of the turning HST mechanism 54. Since it is transmitted, the traveling machine body 1 is turned slightly.
- the minute turning operation by the alignment electric motor 293 can be performed separately from the turning operation of the steering handle (turning manual operation tool) 10, and the steering handle (turning manual operation tool). ) It can be performed even during the 10 turning operation.
- the turning by the electric motor 293 for alignment is restricted so as not to exceed the clockwise rotation angle ⁇ 1 and the counterclockwise rotation angle ⁇ 2 of the turning link 191. It is possible to reliably avoid erroneous excessive turning by the electric motor 293 and to ensure safety.
- the alignment switch 207 is operated to selectively switch between the case where the electric motor 293 is turned and the case where the turning is not performed. You can also.
- the turning operation can be further improved by making the turning by the electric motor 293 performed during the turning operation of the steering handle (the turning manual operation tool) 10 at a slower speed than usual.
- the delay circuit is provided in the electric motor 293 and the electric circuit connecting the electric motor 293 and the left and right turning switches 205 and 206. Can be achieved.
- restricting the rotation angle of the swivel link 191 within the range of ⁇ 1 to ⁇ 2 can be achieved by configuring the electric motor 293 to rotate in the forward and reverse directions for an appropriate time.
- the left and right turning switches 205 and 206 can be provided on the main speed change lever (straight forward manual operation tool) 13 instead of being provided on the steering handle (turning manual operation tool) 10.
- the alignment electric motor 293 is connected to the turning interlock mechanism 180 that connects the control body 131 and the turning HST mechanism 54 via the connecting mechanism 210, and the connecting mechanism 210 is connected to the steering box 120.
- the turning interlock mechanism 180 is used for the turning operation of the turning HST mechanism 54 by the electric motor 293, the number of parts of the structure can be reduced, and the electric motor 293, the coupling mechanism 210, etc.
- the electric motor 293 and the steering box 120 can be unitized, assembly and replacement are easy, and maintenance can be easily performed.
- the configuration around the transmission case 18 can be simplified and the arrangement space can be reduced. it can.
- the shifting slider member 157 may have the configuration shown in FIG. 19 instead of the configuration shown in FIG.
- the turning slider member 166 may have a configuration shown in FIG. 18 instead of the configuration shown in FIG.
- the circular cam 134 of the control body 131 may be configured to have a circular or square cross-sectional member in a circular shape.
Abstract
Description
「走行機体に搭載されたエンジンの動力を、左右の走行部に伝達する直進用変速機及び前記左右の走行部に逆回転して伝達する旋回用変速機と、前記直進用変速機に対する直進手動操作具と、前記旋回用変速機に対する旋回用手動操作具とを備えているコンバインであって、互いに直交する2つの軸線回りに回動可能な制御体を備え、この制御体は、前記旋回用手動操作具の旋回操作に伴う当該制御体における前記第1軸線回りの正逆回動により旋回連動機構を介して前記旋回用変速機を旋回作動させる一方、前記直進用手動操作具の変速操作に伴う当該制御体における前記第2軸線回りの正逆回動により前記直進用変速機を変速作動させるように構成されており、更に、前記制御体を配置するステアリングボックスと、前記旋回用変速機を旋回作動するように構成したアクチュエータとを備え、前記アクチュエータが前記ステアリングボックスに組付けられている。」
ことを特徴としている。
「前記請求項1の記載において、前記アクチュエータとして油圧シリンダを備え、前記油圧シリンダが、前記旋回用変速機を旋回作動させない中立位置を備えた3ポジションシリンダの構成である。」
ことを特徴としている。
「前記請求項2の記載において、前記油圧シリンダによる前記旋回用変速機の旋回作動は、所定の旋回切れ角を越えることがないように規制されている。」
ことを特徴としている。
「前記請求項2または3の記載において、前記旋回連動機構に前記油圧シリンダを連結する連結機構を設け、前記連結機構は前記ステアリングボックスに組み付けられ、前記油圧シリンダが前記連結機構及び前記旋回連動機構を介して前記旋回用変速機を旋回作動させるように構成している。」
ことを特徴としている。
「前記請求項4の記載において、前記連結機構は旋回リンクを備え、前記旋回リンクの中間部を前記制御体における前記第1軸線回りの正逆回動に連動して回動する旋回出力アームに枢着し、この旋回リンクの一端を前記旋回用変速機に、この旋回リンクの他端を前記油圧シリンダに各々連結している。」
ことを特徴としている。
まず、図1及び図2を参照しながら、コンバインの概略構造について説明する。
次に、図3及び図4を参照しながら、コンバインの動力伝達系について説明する。
次に、図1、図2、図5~図22を参照しながら、走行機体1の車速及び進行方向を調節する変速操向制御のための構造について説明する。
1.主変速レバー13を中立以外の位置に傾動操作した状態で、操向ハンドル10を中立以外の位置に回動操作すると、その回動操作量が大きいほど小さな旋回半径で走行機体1が左又は右に旋回し、且つ旋回半径が小さいほど走行機体1の車速(前進及び後退峙の旋回速度)が減速する、
2.主変速レバー13を前進及び後退のいずれの方向に傾動操作した場合であっても、操向ハンドル10の回動操作方向と走行機体1の旋回方向とが一致する(操向ハンドル10を左に回せば走行機体1が左旋回し、操向ハンドル10を右に回せば走行機体1は右旋回する)、
3.主変速レバー13が中立位置にあると操向ハンドル10を操作しても機能しない、
という各種動作を実行するために、主変速レバー13や操向ハンドル10からの操作力を適宜変換して、ステアリングボックス120の側面から外向きに突出する変速出力軸136及び旋回出力軸164(詳細は後述する)に伝達するように構成されている。
次に、図9~図22を参照しながら、主変速レバー(直進用手動操作具)13や操向ハンドル(旋回用手動操作具)10を操作したときの機械式連動機構121の作動について説明する。
次に、図23を参照しながら、走行機体1の条合わせ制御(作動)を実行するための構成について説明する。
左旋回スイッチ206が切り状態のときには(S9でNo)、右旋回スイッチ205が入り状態であるか否かを判別する(S12)。右旋回スイッチ205が入り状態でないときには(S12でNo)、条合わせスイッチ207が入り状態であっても、右旋回スイッチ205及び左旋回スイッチ206がいずれも操作されていない状態であるからリターンする。
次に、図25~図33を参照しながら、旋回連動機構180の変形構造(参考例)について説明する。変形構造の旋回連動機構180は基本的に、先に説明した旋回連動機構180と同じ機能を発揮するものである。ただし、変形構造においては、旋回連動機構180における前記中継ロッド182の他端には、条合わせ用の正逆回転式の電動モータ293を連結する連結機構210が設けられているという点が先に説明した旋回連動機構180の構造と異なっている。
本発明は、前述の実施形態に限らず、様々な態様に具体化できる。例えば、前記変速用滑り子部材157は、図18に示す構成に代えて、図19に示す構成にしてもよい。前記旋回用滑り子部材166は、図19に示す構成に代えて、図18に示す構成にしてもよい。更に、前記制御体131の円形カム134を、丸形又は角形断面の部材を円形にした形態にするという構成にしても良い。
9 操縦部
10 操向ハンドル(旋回用手動操作具)
13 主変速レバー(直進用手動操作具)
18 ミッションケース
50 油圧無段変速機
53 直進用HST機構(直進用変速機)
54 旋回用HST機構(旋回用変速機)
120 ステアリングボックス
121 機械式連動機構
122 旋回入力軸
125 スライダ
131 制御体
136 変速出力軸
140 直進用リンク機構
149 直進制御軸
157 変速用滑り子部材
158 変速出力リンク
164 旋回出力軸(旋回用軸)
166 旋回用滑り子部材
167 旋回出力アーム
180 旋回連動機構
189 旋回制御軸
191 旋回リンク
190 中心ピン
192 作用ピン
193 油圧シリンダ
194 ピストンロッド
195 支点ピン
196 油圧ポンプ
198 油圧切換弁
200 ストローク吸収機構
P 縦軸線(第1軸線)
S 横軸線(第2軸線)
Claims (5)
- 走行機体に搭載されたエンジンの動力を、左右の走行部に伝達する直進用変速機及び前記左右の走行部に逆回転して伝達する旋回用変速機と、前記直進用変速機に対する直進手動操作具と、前記旋回用変速機に対する旋回用手動操作具とを備えているコンバインであって、
互いに直交する2つの軸線回りに回動可能な制御体を備え、この制御体は、前記旋回用手動操作具の旋回操作に伴う当該制御体における前記第1軸線回りの正逆回動により旋回連動機構を介して前記旋回用変速機を旋回作動させる一方、前記直進用手動操作具の変速操作に伴う当該制御体における前記第2軸線回りの正逆回動により前記直進用変速機を変速作動させるように構成されており、
更に、前記制御体を配置するステアリングボックスと、前記旋回用変速機を旋回作動するように構成したアクチュエータとを備え、前記アクチュエータが前記ステアリングボックスに組付けられていることを特徴とするコンバイン。 - 前記請求項1の記載において、前記アクチュエータとして油圧シリンダを備え、前記油圧シリンダが、前記旋回用変速機を旋回作動させない中立位置を備えた3ポジションシリンダの構成であることを特徴とするコンバイン。
- 前記請求項2の記載において、前記油圧シリンダによる前記旋回用変速機の旋回作動は、所定の旋回切れ角を越えることがないように規制されていることを特徴とするコンバイン。
- 前記請求項2または3の記載において、前記旋回連動機構に前記油圧シリンダを連結する連結機構を設け、前記連結機構は前記ステアリングボックスに組み付けられ、前記油圧シリンダが前記連結機構及び前記旋回連動機構を介して前記旋回用変速機を旋回作動させるように構成していることを特徴とするコンバイン。
- 前記請求項4の記載において、前記連結機構は旋回リンクを備え、前記旋回リンクの中間部を前記制御体における前記第1軸線回りの正逆回動に連動して回動する旋回出力アームに枢着し、この旋回リンクの一端を前記旋回用変速機に、この旋回リンクの他端を前記油圧シリンダに各々連結していることを特徴とするコンバイン。
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN200980000337.XA CN101827515B (zh) | 2008-09-16 | 2009-03-16 | 联合收割机 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2008235912A JP5355005B2 (ja) | 2008-09-16 | 2008-09-16 | コンバイン |
JP2008-235912 | 2008-09-16 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010032505A1 true WO2010032505A1 (ja) | 2010-03-25 |
Family
ID=42039352
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2009/055056 WO2010032505A1 (ja) | 2008-09-16 | 2009-03-16 | コンバイン |
Country Status (4)
Country | Link |
---|---|
JP (1) | JP5355005B2 (ja) |
KR (1) | KR101643995B1 (ja) |
CN (1) | CN101827515B (ja) |
WO (1) | WO2010032505A1 (ja) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103477123B (zh) * | 2011-04-15 | 2016-10-12 | 洋马株式会社 | 联合收割机 |
JP5837760B2 (ja) * | 2011-04-28 | 2015-12-24 | ヤンマー株式会社 | コンバイン |
CN107396683B (zh) * | 2012-02-01 | 2021-07-06 | 株式会社久保田 | 割取收获机 |
US9565802B2 (en) * | 2014-05-20 | 2017-02-14 | Deere & Company | Crop sensing system and method with immediate gap detection |
JP2017073984A (ja) * | 2015-10-13 | 2017-04-20 | ヤンマー株式会社 | コンバイン |
KR101868504B1 (ko) * | 2017-01-09 | 2018-06-19 | 국제종합기계 주식회사 | 작업차의 hst 운전 조작력 전달 장치 |
KR101927900B1 (ko) * | 2017-01-09 | 2019-02-26 | 국제종합기계 주식회사 | 작업차의 운전 조작력 전달 장치 |
KR101955248B1 (ko) * | 2017-01-09 | 2019-03-08 | 국제종합기계 주식회사 | 작업차의 선회 운전 조작력 전달 장치 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1053153A (ja) * | 1996-08-09 | 1998-02-24 | Yanmar Agricult Equip Co Ltd | Hst式ミッション装置の操作機構 |
JPH1149018A (ja) * | 1997-07-30 | 1999-02-23 | Yanmar Agricult Equip Co Ltd | コンバイン |
JP2001120041A (ja) * | 1999-10-27 | 2001-05-08 | Yanmar Agricult Equip Co Ltd | コンバイン |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4248715B2 (ja) * | 1999-12-13 | 2009-04-02 | ヤンマー農機株式会社 | クローラ走行車 |
JP4474793B2 (ja) * | 2001-04-25 | 2010-06-09 | 井関農機株式会社 | 走行装置 |
JP2004262292A (ja) * | 2003-02-28 | 2004-09-24 | Yanmar Co Ltd | コンバイン |
JP2005104291A (ja) * | 2003-09-30 | 2005-04-21 | Kubota Corp | 作業車の旋回制御装置 |
-
2008
- 2008-09-16 JP JP2008235912A patent/JP5355005B2/ja active Active
-
2009
- 2009-03-16 KR KR1020097021303A patent/KR101643995B1/ko active IP Right Grant
- 2009-03-16 WO PCT/JP2009/055056 patent/WO2010032505A1/ja active Application Filing
- 2009-03-16 CN CN200980000337.XA patent/CN101827515B/zh not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1053153A (ja) * | 1996-08-09 | 1998-02-24 | Yanmar Agricult Equip Co Ltd | Hst式ミッション装置の操作機構 |
JPH1149018A (ja) * | 1997-07-30 | 1999-02-23 | Yanmar Agricult Equip Co Ltd | コンバイン |
JP2001120041A (ja) * | 1999-10-27 | 2001-05-08 | Yanmar Agricult Equip Co Ltd | コンバイン |
Also Published As
Publication number | Publication date |
---|---|
JP2010068713A (ja) | 2010-04-02 |
KR20110068733A (ko) | 2011-06-22 |
CN101827515A (zh) | 2010-09-08 |
JP5355005B2 (ja) | 2013-11-27 |
CN101827515B (zh) | 2014-01-01 |
KR101643995B1 (ko) | 2016-07-29 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2010032505A1 (ja) | コンバイン | |
JP2012085598A (ja) | コンバイン | |
JP5435881B2 (ja) | 走行車両 | |
JP5373454B2 (ja) | 走行車両 | |
JP5270933B2 (ja) | 走行車両 | |
KR101643994B1 (ko) | 주행 차량 | |
JP5340682B2 (ja) | コンバイン | |
JP2008141999A (ja) | 作業車両 | |
JP4886608B2 (ja) | 走行車両 | |
JP5285321B2 (ja) | 走行車両 | |
JP5324809B2 (ja) | 走行車両 | |
JP5340753B2 (ja) | 走行車両 | |
JP5313957B2 (ja) | 収穫機の走行伝動装置 | |
JP3988891B2 (ja) | 走行車両 | |
JP2009018620A (ja) | 走行車両 | |
JP2011177108A (ja) | 作業車両 | |
JP4886607B2 (ja) | 走行車両 | |
JP3590365B2 (ja) | 作業車 | |
JP2005218315A (ja) | モアー用トラクタ | |
JP2008239032A (ja) | 走行車両 | |
JP2011207448A (ja) | 収穫機の走行伝動装置 | |
JP2002372124A (ja) | 走行伝動装置 | |
JPH10250616A (ja) | コンバインの操向操作装置 | |
JP2017042132A (ja) | コンバイン | |
JP2013193469A (ja) | 走行車両 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 200980000337.X Country of ref document: CN |
|
ENP | Entry into the national phase |
Ref document number: 20097021303 Country of ref document: KR Kind code of ref document: A |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 09814350 Country of ref document: EP Kind code of ref document: A1 |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 09814350 Country of ref document: EP Kind code of ref document: A1 |