JP2013193469A - Traveling vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a traveling vehicle capable of reducing a manufacturing cost and improving maintainability.SOLUTION: A traveling vehicle includes: a traveling machine body having left and right traveling parts 2; a hydraulic transmission 53 for direct advance, which drives the traveling parts 2 in the same direction; a hydraulic transmission 54 for turning, which drives the traveling parts 2 in an opposite direction; a differential mechanism 61 which combines the output of the hydraulic transmission 53 for the direct advance with the output of the hydraulic transmission 54 for turning and transmits them to the traveling parts 2; a gear shifter 12; and a turning operator 10. In the traveling vehicle, a counter steering prevention means for making the steering direction of the turning operator 10 be matched with the turning direction of the traveling machine body is provided, the counter steering prevention means is disposed between a steering link mechanism connected to the turning operator 10 and a trunnion arm for turning, and the output of a hydraulic pump 57 for turning can be maintained at 0 regardless of the operation of the turning operator 10 by the neutral operation of the gear shifter 12.

Description

  The present invention relates to a combine vehicle for harvesting grains by harvesting cereals planted in a field, or a traveling vehicle such as an agricultural tractor for plowing the field, and more specifically, left and right traveling units (left and right traveling crawlers or , Etc.) for a traveling vehicle that forcibly makes a differential movement of the wheel and the like.

  Conventionally, in a combine as a traveling vehicle, an engine is mounted on a traveling machine body supported by a traveling unit such as a left and right crawler, and a straight traveling device that transmits the power of the engine to the left and right traveling units to move straight forward; A turning traveling device is provided that transmits the power of the engine to the left and right traveling units to turn. An example of a combine having such a configuration is disclosed in Patent Document 1 or 2.

JP 2000-177619 A JP 2001-26282 A

  In Patent Document 1 or 2, a turning operation tool that controls turning output of the turning traveling device with respect to the left and right traveling units is provided, and the output control unit of the turning traveling device is mechanically connected to the turning operation tool via an output control mechanism. It is connected. The output control mechanism for controlling the operation of the turning traveling device (or the straight traveling device) uses a rod, an arm, a pivot pin, and the like, and thus has a complicated structure. Further, since the link member connected to the turning travel device (or the straight traveling device) moves around the axis of the turning input shaft, the link member is elongated in the axial direction of the turning input shaft. Need to form. Therefore, when it is mounted on a traveling vehicle such as a combine, not only a large occupied space is required, but also the parts cost required for the output control mechanism increases, and the assembly man-hours and adjustment man-hours in the production line are also large. There are problems such as.

  Accordingly, the present invention seeks to provide a traveling vehicle that has been improved by examining these current conditions.

  In order to achieve the above object, a traveling vehicle according to a first aspect of the present invention includes a traveling machine body having left and right traveling units, a linear hydraulic pump for driving the left and right traveling units in the same direction in the same rotation, and a straight traveling A rectilinear hydraulic transmission having a hydraulic motor, a swing hydraulic pump having a swing hydraulic pump and a swing hydraulic motor for driving the left and right traveling units in the reverse direction in the same rotation, and the straight hydraulic A differential mechanism that combines the output of the transmission and the output of the turning hydraulic transmission and transmits the output to the left and right traveling units, a transmission operating tool that controls the output of the linear hydraulic transmission, and the turning hydraulic transmission In a traveling vehicle including a turning operation tool for controlling the output of the machine, a reverse handle that matches the steering direction of the turning operation tool with the turning direction of the traveling machine body in any of the forward operation and the reverse operation of the speed change operation tool. The reverse handle preventing means is disposed between the steering link mechanism connected to the turning operation tool and the trunnion arm of the turning hydraulic pump, and the neutralization mechanism of the speed change operation tool. According to the operation, the output of the turning hydraulic pump can be maintained at 0 regardless of the operation of the turning operation tool.

  According to a second aspect of the present invention, in the traveling vehicle according to the first aspect, a forward locking portion, a neutral locking portion, and a reverse locking portion are formed on the trunnion arm of the turning hydraulic pump, and the forward locking mechanism is formed. The trunnion arm is configured to be connectable to the steering link mechanism via a stop portion, the neutral locking portion, or the reverse locking portion.

  According to a third aspect of the present invention, in the traveling vehicle according to the first aspect, a reverse handle switching connecting pin provided on the steering link mechanism side and an arcuate reverse side provided on the trunnion arm side of the turning hydraulic pump. The reverse handle preventing means is formed by a handle switching long groove, and the reverse handle switching connecting pin is engaged with the reverse handle switching long groove, and the shift operation tool is in a neutral position. A connecting pin for switching the reverse handle is supported at an intermediate portion of the long groove for switching the reverse handle, and the reverse is switched to both ends of the long groove for switching the reverse handle by a forward operation or a reverse operation of the speed change operation tool. The connecting pin for switching the handle is configured to be movable.

  According to the first aspect of the present invention, a traveling airframe having a left and right traveling unit, a straight traveling hydraulic pump and a straight traveling hydraulic motor for driving the left and right traveling units in the same direction with the same rotation. A transmission, a turning hydraulic transmission having a turning hydraulic pump and a turning hydraulic motor for driving the left and right traveling units in the same direction and in the reverse direction, an output of the straight hydraulic transmission and the turning A differential mechanism that synthesizes the output of the hydraulic transmission and transmits it to the left and right traveling units, a shift operation tool that controls the output of the linear hydraulic transmission, and a turning control tool that controls the output of the turning hydraulic transmission In the traveling vehicle comprising: a reverse handle preventing means for matching the steering direction of the turning operation tool and the turning direction of the traveling machine body in any of the forward operation and the reverse operation of the shift operation tool. The reverse handle preventing means is disposed between the steering link mechanism connected to the turning operation tool and the trunnion arm of the turning hydraulic pump, and the operation of the turning operation tool is performed by a neutral operation of the speed change operation tool. Regardless of whether the output of the turning hydraulic pump can be maintained at 0, the steering direction of the turning operation tool and the turning direction of the traveling machine body can always coincide with each other. When the shift operation tool is operated in a neutral (output 0) state, the traveling machine body can be prevented from moving due to an erroneous operation of the turning operation tool. Further, the manufacturing cost can be easily reduced as compared with the conventional steering operation structure. Maintenance work can be simplified. Parts costs, assembly man-hours or adjustment man-hours in the production line can be reduced.

  According to the invention which concerns on Claim 2, the forward locking part, the neutral locking part, and the backward locking part are formed in the trunnion arm of the hydraulic pump for turning, and the forward locking part or the neutral locking part or Since the trunnion arm is configured to be connectable to the steering link mechanism via the reverse locking portion, the manufacturing cost can be easily reduced compared to the conventional steering operation structure. The neutral locking portion can be installed on a straight line connecting the steering link mechanism and the trunnion arm connecting portion and the trunnion of the turning hydraulic pump, and with the neutral locking portion as a center, the forward locking portion and The reverse lock portion can be disposed at a symmetrical position, and can be compactly assembled to the output control portion of the turning hydraulic transmission.

  According to the third aspect of the present invention, the reverse handle is provided by the reverse handle switching connecting pin provided on the steering link mechanism side and the arc-shaped reverse handle switching long groove provided on the trunnion arm side of the turning hydraulic pump. A preventive means is formed, and the reverse handle switching connecting pin is engaged with the reverse handle switching long groove, and the middle of the reverse handle switching long groove when the speed change operation tool is in the neutral position. The connecting pin for switching the reverse handle is supported on the portion, and the connecting pin for switching the reverse handle can be moved to both ends of the long groove for switching the reverse handle by forward operation or reverse operation of the shift operation tool. Therefore, the manufacturing cost can be easily reduced as compared with the conventional steering operation structure, but the neutralization (output 0) operation of the speed change operation tool can be achieved. Locating the arcuate middle of the reverse handle switching long groove and the connecting pin for switching the reverse handle on a straight line connecting the steering link mechanism and the trunnion arm connecting portion and the trunnion of the turning hydraulic pump. And a reverse handle switching connecting pin can be positioned on both arcuate ends of the reverse handle switching long groove by forward operation or reverse operation of the speed change operation tool. It can be assembled compactly in the output control unit.

It is a right view of the combine for 2 line cutting. It is a top view of a combine. It is a drive system diagram of a combine. It is explanatory drawing of the forward / reverse switching mechanism. FIG. 5 is an enlarged plan view of a forward / reverse switching mechanism when a main transmission lever is moving forward. FIG. 6 is an enlarged plan view of a forward / reverse switching mechanism when a main transmission lever is neutral. FIG. 6 is an enlarged plan view of a forward / reverse switching mechanism when a main transmission lever is reverse.

  Hereinafter, an embodiment embodying the present invention will be described with reference to the drawings (FIGS. 1 to 7) when applied to a combine as a traveling vehicle. In the following description, the left side in the forward direction of the traveling machine body 1 is simply referred to as the left side, and the right side in the forward direction is also simply referred to as the right side.

  As shown in FIGS. 1 and 2, the combine includes a traveling machine body 1 supported by a pair of left and right traveling crawlers 2 as traveling portions. At the front part of the traveling machine body 1, a two-row mowing device 3 that takes in while harvesting cereals is provided around a mowing input case 16 that is a horizontal axis by a single-acting lifting hydraulic cylinder 4 as a lifting actuator. It is attached to be adjustable up and down. A threshing device 5 having a feed chain 6 and a grain tank 7 for storing the grains taken out from the threshing device 5 are mounted on the traveling machine body 1 side by side. The threshing device 5 is disposed on the left side in the forward direction of the traveling machine body 1, and the grain tank 7 is disposed on the right side in the forward 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 configured to be discharged from the spear opening of the discharge auger 8 to a truck bed or a container. . A driving control unit 9 is provided on the right side of the reaping device 3 and on the front side of the grain tank 7.

  The driving control unit 9 includes a control lever 10 as a turning operation tool, a driving seat 11, a main transmission lever 12 as a straight operation tool, an auxiliary transmission lever 13, a threshing clutch lever 14 for turning on and off the threshing clutch, A cutting clutch lever 15 for turning the cutting clutch on and off is disposed. The driving control unit 9 is provided with a handle column provided with a control lever 10 and a lever column provided with the levers 13, 14 and the like. An engine 17 as a power source is disposed below the driver seat 11 in the traveling machine body 1. 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.

  As shown in FIG. 1, left and right track frames 21 are arranged on the lower surface side of the traveling machine body 1. The track frame 21 includes a driving sprocket 22 that transmits the power of the engine 17 to the traveling crawler 2, a tension roller 23 that maintains the tension of the traveling crawler 2, and a plurality of track rollers that hold the ground side of the traveling crawler 2 in a grounded state. 24 and an intermediate roller 25 that holds the non-grounded side of the traveling crawler 2 are provided. The driving sprocket 22 supports the front side of the traveling crawler 2, the tension roller 23 supports the rear side of the traveling crawler 2, the track roller 24 supports the grounding side of the traveling crawler 2, and the intermediate roller 25 supports the non-traveling crawler 2. Support the ground side.

  The reaping device 3 includes a hair clipper-type cutting blade device 31, a chopstick pulling device 32 for two strips, a pestle transporting device 33, and a weed body 34. The cutting blade device 31 is disposed on a cutting frame 35 that forms a machine frame of the cutting device 3. The grain raising apparatus 32 is disposed above the cutting frame 35. A corn straw transporting device 33 is arranged between the corn straw pulling device 32 and the feed start end of the feed chain 6. A weeding body 34 is projected in front of the lower part of the grain raising device 32. The traveling machine body 1 continuously cuts uncut cereal grains in the field by driving the reaping device 3 while driving the left and right traveling crawler 2 by the engine 17 and moving in the field.

  The threshing device 5 includes a handling cylinder 41 for threshing the harvested cereal, a swing sorting mechanism 42 and a wind sorting mechanism 43 disposed below the handling cylinder 41, and a threshing that is taken out from the rear part of the handling cylinder 41. A dust feed processing cylinder 44 for reprocessing an object is provided. The handling cylinder 41 is arranged in a handling chamber of the threshing device 5. The stock source side of the harvested cereal meal sent from the harvesting device 3 is inherited by the feed chain 6. Then, the tip side of the harvested cereal culm is carried into the threshing device 5 and threshed by the handling cylinder 41.

  In the lower part of the threshing device 5, the first receiving bowl 45 and the first conveyor 46 in which the most refined grains are collected among the grains sorted by the sorting mechanisms 42 and 43, A second receiving rod 47 and a second conveyor 48 for collecting second items such as spiked grains are provided. The first thing such as fine grains collected in the first receiving bowl 45 is sent to the grain tank 7 via the first conveyor 46 in the first receiving bowl 45 and the cereal conveyor in the cereal tube 49. .

  The second item such as the grain with branches is gathered in the second receiving rod 47 behind the first receiving rod 45, and passes through the second conveyor 48 in the second receiving rod 47 and the reducing conveyor in the reducing cylinder 50. And returned to the swing sorting mechanism 42. Then, the second item is re-sorted by the swing sorting mechanism 42. The sawdust is sucked into a dust exhaust fan (not shown) and discharged from the rear portion of the threshing device 5 to the outside of the machine.

  A waste chain 51 is disposed on the rear side (feed end side) of the feed chain 6. The waste (the grain that has been shattered) inherited from the rear end of the feed chain 6 to the waste chain 51 is discharged to the rear of the traveling machine body 1 in a long state, or the waste cutter located behind the threshing device 5. After being cut to a suitable length at 52, it is discharged to the rear of the traveling machine body 1.

  Next, a traveling drive structure for transmitting power from the engine 17 to the traveling crawler 2 will be described with reference to FIG. A transmission case 18 having a straight traveling hydraulic transmission 53 and a turning hydraulic transmission 54 as a hydraulic continuously variable transmission is provided. The power from the engine 17 toward the traveling crawler 2 is transmitted to the straight traveling hydraulic transmission 53 and the turning hydraulic transmission 54 via the belt transmission mechanism. The output of the engine 17 is shifted by a straight traveling hydraulic transmission 53 or a turning hydraulic transmission 54 and output to the left and right drive sprockets 22 via left and right axles 75 projecting left and right outward from the mission case 18. It is configured as follows.

  The transmission case 18 includes a straight traveling hydraulic transmission 53 including a first hydraulic pump 55 and a first hydraulic motor 56, a turning hydraulic transmission 54 including a second hydraulic pump 57 and a second hydraulic motor 58, and a plurality of shifts. A sub-transmission mechanism 59 having a gear and a differential mechanism 61 (forced differential mechanism) having a pair of left and right planetary gear mechanisms 60 and the like are provided (see FIG. 3).

  Power from the output shaft of the engine 17 toward the traveling crawler 2 is transmitted to the transmission input shaft 62 that drives the first hydraulic pump 55 and the second hydraulic pump 57. In the straight traveling hydraulic transmission 53, the first hydraulic motor 56 is driven by the first hydraulic pump 55. Similarly, in the turning hydraulic transmission 54, the second hydraulic motor 58 is driven by the second hydraulic pump 57.

  The rectilinear hydraulic transmission 53 changes and adjusts the inclination angle of the output control swash plate in the first hydraulic pump 55 according to the operation amount of the main transmission lever 12 disposed in the control unit 9, and thereby adjusts the first hydraulic motor 56. By changing the discharge direction and the discharge amount of the hydraulic oil, the rotation direction and the rotation speed of the straight advance motor shaft 63 protruding from the first hydraulic motor 56 are arbitrarily adjusted.

  The rotational power of the linear motor shaft 63 is transmitted from the linear transmission gear mechanism 64 to the sub-transmission mechanism 59, while the cutting that projects from the transmission case 18 via the linear transmission gear mechanism 64 and the one-way clutch 65 described above. It is also transmitted to the PTO shaft 66. The power transmitted to the reaping PTO shaft 66 is transmitted to each part of the reaping device 3. For this reason, each part of the reaping device 3 is driven at a speed synchronized with the vehicle speed.

  The sub-transmission mechanism 59 is for switching the rotational output of the linear motor shaft 60 in two stages, low speed or high speed, by operating the sub transmission lever 13 disposed in the control unit 9. A parking brake 68 such as a wet multi-plate disk is provided on the parking brake shaft 67 which is a component of the auxiliary transmission mechanism 59.

  The rotational power from the auxiliary transmission mechanism 59 is transmitted to the differential mechanism 61 from an auxiliary transmission output gear 69 fixed to the parking brake shaft 67. The differential mechanism 61 includes a sun gear shaft 70 positioned between a pair of left and right planetary gear mechanisms 60. The auxiliary speed change output gear 69 of the parking brake shaft 67 meshes with a center gear 76 fixed in the middle of the sun gear shaft 70.

  The planetary gear mechanism 60 includes one sun gear 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 circumference of the planetary gear 72, and a carrier 74 that rotatably supports the plurality of planetary gears 72. Is provided. The carriers 74 of the left and right planetary gear mechanisms 68 are arranged on the axis line of the axle 75. The left and right sun gears 71 are fixed to both ends of the center gear 76.

  The ring gear 73 is concentrically arranged on the sun gear shaft 70 with its inner teeth meshed with the plurality of planetary gears 72 and is rotatably supported on an axle 75 projecting left and right outward from the outer surface of the carrier 74. Has been. Accordingly, the linear rotational force transmitted from the auxiliary transmission mechanism 59 to the left and right planetary gear mechanisms 60 is transmitted from the respective axles 75 to the left and right drive sprockets 22 at the same rotational speed in the same direction, and travels straight through the left and right traveling crawlers 2. To drive.

  In the turning hydraulic transmission 54, by changing and adjusting the inclination angle of the output control swash plate in the second hydraulic pump 57, the discharge direction and discharge amount of the hydraulic oil to the second hydraulic motor 58 are changed, so that the second The rotation direction and the number of rotations of the turning motor shaft 77 protruding from the hydraulic motor 58 are arbitrarily adjusted.

  As shown in FIG. 3, in the transmission case 18, the steering input shaft 78, the reverse input shaft 79, the left input gear 80 that always meshes with the external teeth of the left ring gear 73, and the external teeth of the right ring gear 73 are always meshed. A right input gear 81 and a reverse gear 82 for connecting the left input gear 80 to the steering input shaft 78 are provided. The rotational power of the turning motor shaft 61 is transmitted from the turning transmission gear mechanism 83 to the steering input shaft 78. The rotational power transmitted to the steering input shaft 78 is transmitted to the right ring gear 73 through the right input gear 81 in the normal rotation state, and at the same time, reversely transmitted to the left ring gear 73 through the left input gear 80 and the reverse gear 82. Transmitted in a rotating state.

  That is, the rotational power of the turning motor shaft 77 (second hydraulic motor 58) is input to the right planetary gear mechanism 60 in the normal direction and is input to the left planetary gear mechanism 60 in the reverse direction. Accordingly, the left and right traveling crawlers 2 are configured to be driven in different rotational directions by the second hydraulic motor 58. The steering input shaft 78 is provided with a steering brake 84 such as a wet multi-plate disk.

  For example, when the vehicle travels straight in the forward direction with the output of the first hydraulic motor 56, when the right traveling crawler 2 is rotated forward with the forward rotation output of the second hydraulic motor 58, the left traveling crawler 2 is The vehicle rotates backward and the traveling machine body 1 turns in the left direction. On the other hand, when the vehicle travels straight in the forward direction with the output of the first hydraulic motor 56, when the left traveling crawler 2 is rotated forward with the reverse rotation output of the second hydraulic motor 58, the right traveling crawler 2 moves backward. It rotates and the traveling body 1 is comprised so that turning movement may be carried out rightward.

  As can be seen from the above configuration, the shift output from the motor shafts 63 and 77 is transmitted to the drive sprockets 22 of the left and right traveling crawlers 2 via the auxiliary transmission mechanism 59 and the differential mechanism 61, respectively. As a result, the vehicle speed (traveling speed) and traveling direction of the traveling machine body 1 are determined.

  That is, when the first hydraulic motor 56 is driven in a state where the second hydraulic motor 58 is stopped and the left and right ring gears 73 are stationary and fixed by braking of the steering brake 84, the rotation from the linear motor shaft 63 is performed. The output is transmitted from the center gear 76 to the left and right sun gears 71 at the same rotational speed in the same direction, and the left and right traveling crawlers 2 have the same rotational speed in the same direction via the planetary gears 72 and the carriers 74 of the left and right planetary gear mechanisms 60. The traveling machine body 1 travels straight.

  On the other hand, when the second hydraulic motor 58 is driven forward (or reverse) while the first hydraulic motor 56 is stopped and the left and right sun gears 71 are stationary and fixed by the braking of the parking brake 68, The left planetary gear mechanism 60 is rotated forward (or reversely rotated) by the normal rotation (or reverse rotation) power from the motor shaft 77, and the right planetary gear mechanism 60 is reversely rotated (or forwardly rotated). That is, one of the drive sprockets 22 of the left and right traveling crawlers 2 rotates forward, the other rotates backward, and the traveling machine body 1 performs a pivoting operation in which a spin turn is performed on the spot. Further, when the second hydraulic motor 58 is driven while the first hydraulic motor 56 is driven, a difference occurs between the speeds of the left and right traveling crawlers 2, and the traveling machine body 1 moves forward or backward and has a turning radius larger than the belief turning radius. Turn left or right at. The turning radius of the traveling machine body 1 at this time is determined according to the speed difference between the left and right traveling crawlers 2 (the rotational speed of the first hydraulic motor 56 and the rotational speed of the second hydraulic motor 58).

  Next, the output control structure of the turning hydraulic transmission 54 by the control lever 10 and the output control structure of the straight hydraulic transmission 53 by the main transmission lever 12 will be described with reference to FIGS. As shown in FIG. 4, one end side of the straight traveling speed change rod 86 is connected to the main speed change lever 12 via the straight traveling speed change link mechanism 86 a. Further, the straight travel trunnion arm 55 c is fixed to the straight travel trunnion 55 b of the first hydraulic pump 55, and the straight travel trunnion arm 55 c is connected to the other end of the straight travel speed change rod 86. When the main transmission lever 12 is supported at the neutral position, the hydraulic output of the first hydraulic pump 55 is maintained at zero. When the main transmission lever 12 is tilted forward (or reverse), the straight trunnion 55b rotates via the straight shift rod 86, and the output of the straight hydraulic transmission 53 rotates forward (or reverse). The traveling machine body 1 is configured to move forward (or reverse).

  Further, as shown in FIG. 4, one end side of the turning speed change rod 87 is connected to the control lever 10 via the turning speed change link mechanism 87a. A fulcrum pin 95 for switching the reverse handle is provided on one end of the turning speed change rod 87. A connecting pin 88 for switching the reverse handle is provided on the other end side of the turning rod 87 for turning. On the other hand, the turning trunnion arm 57 c is fixed to the turning trunnion 57 b of the second hydraulic pump 57. A long groove 89 for switching the reverse handle is formed in the turning trunnion arm 57c. A long groove 89 for switching the reverse handle is provided in an arc shape on the circumference centering on the fulcrum pin 95 for switching the reverse handle. A connecting pin 88 for switching the reverse handle is loosely supported in the long groove 89. In the case where the turning speed change rod 87 is linear, a long groove 89 for switching the reverse handle is formed in an arc shape with the rod length of the turning speed change rod 87 as a radius.

  The reverse handle preventing means is formed by a reverse handle switching connecting pin 88 provided on the steering link mechanism side and an arcuate reverse handle switching long groove 89 provided on the trunnion arm 57c side of the second hydraulic pump 57, The reverse handle switching connecting groove 88 is engaged with the reverse handle switching long groove 89, and the intermediate portion of the reverse handle switching long groove 89 (neutral) when the main transmission lever 12 is in the neutral position. The connecting pin 88 for switching the reverse handle is supported by the locking portion), and the both ends of the long groove 89 for switching the reverse handle (forward locking portion or reverse shift) by the forward operation or reverse operation of the main speed change lever 12. The connecting pin 88 for switching the reverse handle is moved to the stop portion to prevent the reverse handle operation. That is, the forward locking portion, the neutral locking portion, and the reverse locking portion are formed in the long groove 89 provided in the trunnion arm 57c of the second hydraulic pump 57, and the forward locking portion, the neutral locking portion, or the reverse drive is formed. The trunnion arm 57c is coupled to the turning speed change rod 87 via a locking portion.

  A straight movement maintaining arm 91 (neutral support body) that holds the connecting pin 88 is provided at an intermediate portion (neutral locking portion) of the long groove 89. The straight movement maintaining arm 91 is rotatably supported on the neutral maintaining arm shaft 93. A fulcrum overspring 92 having a tensile force in a linear direction connecting the connecting pin 88, the neutral maintaining arm shaft 93 and the fulcrum pin 95 is provided. A fulcrum spring 92 is connected to the straight movement maintaining arm 91, and the connecting pin 88 is supported at the straight movement position by the bias of the fulcrum spring 92, and the control lever 10 is supported at the straight movement position. . That is, when the connecting pin 88 is supported at the straight movement position, the tilting operation of the control lever 10 is blocked by the connecting pin 88, and the steering (left turn or right turn) operation of the control lever 10 is prohibited.

  Further, as shown in FIG. 4, the turning speed change rod 87 is connected to the straight traveling trunnion arm 55 c via the sensor link member 90. When the speed change operation of the main speed change lever 12 is made forward or backward, the connecting pin 88 moves toward both ends (forward lock part or reverse lock part) of the long groove 89 via the sensor link member 90. Due to the fulcrum overloading action (tensile force) of the fulcrum spring 92, the straight movement maintaining arm 91 is tilted to the posture toward both ends (the forward locking portion or the backward locking portion) of the long groove 89. The steering lever 10 is configured to be released from the steering prohibition state (left turn or right turn). The straight travel trunnion arm 55c does not operate due to the operation of the turning speed change rod 87 based on the operation of the control lever 10, but the turning speed change rod 87 due to the operation of the straight travel trunnion arm 55c based on the operation of the main speed change lever 12. It is configured in a link structure that operates.

  When the main shift lever 12 is operated to shift forward or backward and the steering lever 10 steering (left turn or right turn) prohibition state is released, the control lever 10 is turned to the left turn side (or right turn side). ) Can be operated. By the left turning side (or right turning side) operation of the control lever 10, the turning trunnion arm 57c is turned in the left turning side (or right turning side) direction via the connecting pin 88, and the second hydraulic pump. The second hydraulic motor 58 is driven forward or reverse by 57. The left and right traveling crawlers 2 are driven to turn left (or turn right) to change the course of the traveling machine body 1.

  As shown in FIG. 5, when the main transmission lever 12 is supported at the neutral (output 0) position, the connecting pin 88 is positioned at the midpoint of the long groove 89 formed in the turning trunnion 57b. At this time, the turning trunnion 57 b, the connecting pin 88, and the fulcrum pin 95 are positioned in a straight line in the axial direction of the turning speed change rod 87. The straight movement maintaining arm 91 is maintained at the neutral (straight forward) position by the pulling force of the fulcrum spring 92. In other words, since the connecting pin 88 is maintained at the neutral position of the long groove 89 by the straight movement maintaining arm 91, the turning trunnion 57 b does not rotate even if the axial pulling force is transmitted to the turning speed change rod 87. That is, when the main transmission lever 12 is supported at the neutral position, the control lever 10 cannot be tilted to the left turn side or the right turn side. Therefore, in the neutral state of the main speed change lever 12 where the traveling machine body 1 is stopped, the traveling machine body 1 does not move due to an erroneous operation of the control lever 10.

  As shown in FIG. 6, when the main transmission lever 12 is operated to the forward side, the connecting pin 88 moves in the long groove 89 formed in the turning trunnion 57b. The straight movement maintaining arm 91 is rotated to a forward posture around the neutral maintaining arm shaft 93 by the tensile force of the fulcrum spring 92. At this time, the straight movement maintaining arm 91 pushes the connecting pin 88 and moves the connecting pin 88 to the advanced position of the long groove 89.

  When the control lever 10 is tilted toward the left side (left turning side) of the traveling machine body 1 with the connecting pin 88 moved to the forward movement position of the long groove 89, the turning lever 10 is turned via the turning speed change rod 87. The trunnion 57b rotates in the left turning direction. The left and right traveling crawlers 2 are driven by the left turning output of the turning hydraulic transmission 54, and the traveling machine body 1 turns left. Further, when the control lever 10 is tilted toward the right side (right turning side) of the traveling machine body 1 with the connecting pin 88 moved to the forward movement position of the long groove 89, the turning rod 87 is turned through. The turning trunnion 57b rotates in the right turning direction. Then, the right and left traveling crawlers 2 are driven by the right turning output of the turning hydraulic transmission 54, and the traveling machine body 1 turns right.

  As shown in FIG. 7, when the main transmission lever 12 is operated to the reverse side, the connecting pin 88 moves in the long groove 89 formed in the turning trunnion 57b. The rectilinear maintaining arm 91 is rotated to the reverse posture around the neutral maintaining arm shaft 93 by the pulling force of the fulcrum spring 92. At this time, the straight movement maintaining arm 91 pushes the connecting pin 88 and moves the connecting pin 88 to the backward movement position of the long groove 89.

  When the control lever 10 is tilted toward the left side (left turning side) of the traveling machine body 1 with the connecting pin 88 moved to the reverse position of the long groove 89, the turning lever 10 is turned via the turning speed change rod 87. The trunnion 57b rotates in the left turning direction. The left and right traveling crawlers 2 are driven by the left turning output of the turning hydraulic transmission 54, and the traveling machine body 1 turns left. Further, when the control lever 10 is tilted toward the right side (right turn side) of the traveling machine body 1 with the connecting pin 88 moved to the backward movement position of the long groove 89, the turning rod 87 is turned through the turning speed change rod 87. The turning trunnion 57b rotates in the right turning direction. Then, the right and left traveling crawlers 2 are driven by the right turning output of the turning hydraulic transmission 54, and the traveling machine body 1 turns right.

  As shown in FIGS. 1 and 4 to 7, the traveling machine body 1 having left and right traveling crawlers 2 (traveling portions) and the straight traveling hydraulic pump for driving the left and right traveling crawlers 2 in the same direction with the same rotation. A linear hydraulic transmission 53 having a first hydraulic pump 55 and a first hydraulic motor 56 as a linear hydraulic motor, and a rotary hydraulic pump as a turning hydraulic pump for driving the left and right traveling crawlers 2 in the reverse direction in the same rotation. Two hydraulic pumps 57 and a turning hydraulic transmission 54 having a second hydraulic motor 58 as a turning hydraulic motor, and the output of the straight hydraulic transmission 53 and the output of the turning hydraulic transmission 54 are combined to run left and right. A differential mechanism 61 for transmitting to the crawler 2, a main transmission lever 12 as a transmission operating tool for controlling the output of the straight traveling hydraulic transmission 53, and an operation as a turning operating tool for controlling the output of the turning hydraulic transmission 54. In a traveling vehicle equipped with the lever 10, the reverse handle switching means as a reverse handle preventing means for making the steering direction of the control lever 10 coincide with the turning direction of the traveling machine body 1 in either the forward operation or the reverse operation of the main transmission lever 12. A structure including a connecting pin 88 and a long groove 89 for switching a reverse handle, between a turning speed change rod 87 as a steering link mechanism connected to the control lever 10 and a trunnion arm 57c of the turning hydraulic pump 57. Are provided with a connecting pin 88 for switching the reverse handle and a long groove 89 for switching the reverse handle, and the output of the second hydraulic pump 57 is set to 0 by the neutral operation of the main transmission lever 12 regardless of the operation of the control lever 10. It is configured to be sustainable. Therefore, when the main transmission lever 12 is operated neutrally (output 0) while the steering direction of the control lever 10 and the turning direction of the traveling machine body 1 can always coincide with each other, an erroneous operation of the control lever 10 is performed. Can prevent the traveling machine body 1 from moving. Further, the manufacturing cost can be easily reduced as compared with the conventional steering operation structure. Maintenance work can be simplified. Parts costs, assembly man-hours or adjustment man-hours in the production line can be reduced.

  As shown in FIGS. 4 to 7, the trunnion arm 57c of the second hydraulic pump 57 is provided with one end 89a (advance locking portion) of the long groove, an intermediate portion 89b (neutral locking portion) of the long groove, and the other end 89c of the long groove. (Reverse locking portion) is formed, and the trunnion arm 57c can be connected to the turning speed change rod 87 via one end 89a of the long groove, middle portion 89b of the long groove, or other end 89c of the long groove. Therefore, the manufacturing cost can be easily reduced as compared with the conventional steering operation structure, but on the straight line connecting the connecting portion of the turning rod 87 and the trunnion arm 57c and the trunnion 57b of the second hydraulic pump 57. The middle part 89b of the long groove can be installed, and one end part 89a of the long groove and the other end part 89c of the long groove can be arranged symmetrically with the middle part 89b of the long groove as the center, and the output control part of the turning hydraulic transmission 54 can be made compact. Can be assembled.

  As shown in FIGS. 4 to 7, a reverse handle switching connecting pin 88 provided on the turning speed change rod 87 side and an arcuate reverse handle switching long groove 89 provided on the trunnion arm 57c side of the second hydraulic pump 57 are provided. The reverse handle preventing means is formed, and the reverse handle switching connecting pin 88 is engaged with the reverse handle switching long groove 89, and when the main transmission lever 12 is in the neutral position, A reverse handle switching connecting pin 88 is supported at an intermediate portion of the long groove 89, and a reverse handle switching connecting pin is provided at both ends of the reverse handle switching long groove 89 by forward or reverse operation of the main transmission lever 12. 88 is configured to be movable. Therefore, compared to the conventional steering operation structure, the manufacturing cost can be easily reduced, but by the neutral (output 0) operation of the main transmission lever 12, the connecting portion of the turning speed change rod 87 and the trunnion arm 57c, On the straight line connecting the trunnion 57b of the second hydraulic pump 57, the arcuate middle of the long groove 89 for switching the reverse handle and the connecting pin 88 for switching the reverse handle can be positioned, and the main transmission lever 12 can be moved forward or backward. By operation, the reverse handle switching connecting pins 88 can be positioned on both ends of the arcuate end of the reverse handle switching long groove 89, and can be compactly assembled to the output control unit of the turning hydraulic transmission 54.

1 traveling machine body 2 traveling crawler (traveling section)
10 Control lever (turning tool)
12 Main gear shift lever (shift gear)
18 Mission case 53 Hydraulic transmission for rectilinear movement 54 Hydraulic transmission for turning 55 First hydraulic pump (linear hydraulic pump)
55b Straight running trunnion 55c Straight running trunnion arm 56 First hydraulic motor (straight running hydraulic motor)
57 Second hydraulic pump (swivel hydraulic pump)
57b Trunnion for turning 57c Trunnion arm for turning 58 Second hydraulic motor (turning hydraulic motor)
86 Linear rod for straight travel 87 Variable rod for turning (steering link mechanism)
88 Connecting pin for reverse handle switching (reverse handle prevention means)
89 Long groove for reverse handle switching (reverse handle prevention means)
89a One end of the long groove (advance locking part)
89b Middle part of long groove (neutral locking part)
89c The other end of the long groove (reverse locking part)

Claims (3)

A traveling machine body having left and right traveling units, a straight traveling hydraulic pump having a straight traveling hydraulic pump and a straight traveling hydraulic motor for driving the left and right traveling units in the same direction in the same rotation, and the left and right traveling units. A turning hydraulic transmission having a turning hydraulic pump and a turning hydraulic motor for driving in the reverse direction in the same rotation, and combining the output of the straight hydraulic transmission and the output of the turning hydraulic transmission, In a traveling vehicle comprising: a differential mechanism that transmits to left and right traveling units; a shift operation tool that performs output control on the straight hydraulic transmission; and a turning operation tool that performs output control on the turning hydraulic transmission.
In either the forward operation or the reverse operation of the speed change operation tool, the structure is provided with reverse handle prevention means for matching the steering direction of the turning operation tool with the turning direction of the traveling machine body, and is connected to the turning operation tool. The reverse handle preventing means is disposed between the steering link mechanism and the trunnion arm of the turning hydraulic pump, and the turning operation tool is neutrally operated by the neutral operation of the shifting operation tool regardless of the operation of the turning operation tool. A traveling vehicle characterized in that the output of the hydraulic pump can be maintained at zero.   A forward locking portion, a neutral locking portion, and a reverse locking portion are formed on the trunnion arm of the turning hydraulic pump, and the forward locking portion, the neutral locking portion, or the reverse locking portion, The traveling vehicle according to claim 1, wherein the trunnion arm is connectable to a steering link mechanism.   The reverse handle preventing means is formed by a reverse handle switching connecting pin provided on the steering link mechanism side and an arcuate reverse handle switching long groove provided on the trunnion arm side of the turning hydraulic pump, and the reverse handle switching is formed. The reverse handle switching connecting pin is engaged with the long handle groove, and the reverse handle switching connecting pin is provided in the middle of the reverse handle switching long groove when the speed change operation tool is in the neutral position. The reverse handle switching connecting pin is configured to be movable to both ends of the reverse handle switching long groove by forward operation or reverse operation of the speed change operation tool. The traveling vehicle according to 1.

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