JP2013193472A - Traveling vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a traveling vehicle capable of reducing components costs and assembling man-hours, control man-hours or the like in a manufacturing line therefor, while it can reduce a moving speed of a traveling machine body 1 by only a course changing operation, when a course of the traveling machine body 1 is changed.SOLUTION: A traveling vehicle includes: a traveling machine body 1 which is supported by right and left traveling sections 2; a linear hydraulic transmission 53 which comprises a linear hydraulic pumps 55 and a linear hydraulic motor 56; a turning hydraulic transmission 54 which comprises a turning hydraulic pump 57 and a turning hydraulic motor 58; and a forced differential mechanism 61 which performs output of the linear hydraulic transmission 53 and output of the turning hydraulic transmission 54 by synthesizing them together. The traveling vehicle has a structure which is configured to make output of the linear hydraulic motor 56 changeable. An output control mechanism 56b of the linear hydraulic motor 56 is connected to an output control mechanism 57b of the turning hydraulic pump 57, and output of the linear hydraulic motor 56 is changed in such a manner as to interlock with a change in output of the turning hydraulic pump 57.

Description

  The present invention relates to a traveling vehicle such as a combine that harvests cereal grains planted in a field and collects grains, or an agricultural tractor that cultivates the field, and more specifically, left and right traveling units (right and left traveling crawlers or left and right traveling crawlers). , 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. In addition, since the rod body connected to the turning traveling device (or the straight traveling device) moves around the axis of the turning input shaft, the rod body 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 supported by left and right traveling units, a rectilinear hydraulic transmission having a rectilinear hydraulic pump and a rectilinear hydraulic motor, and a swing hydraulic pump. And a turning hydraulic transmission having a turning hydraulic motor, and a forcible differential mechanism that combines and outputs the output of the straight hydraulic transmission and the output of the turning hydraulic transmission, the output of the straight hydraulic motor The output control mechanism of the rectilinear hydraulic motor is connected to the output control mechanism of the swing hydraulic pump, and the output of the rectilinear hydraulic motor is interlocked with the output change of the swing hydraulic pump. Is configured to change.

  According to a second aspect of the present invention, in the traveling vehicle according to the first aspect, the straight hydraulic transmission and the turning hydraulic transmission are arranged in a transmission case, the swivel pump trunnion and the straight motor The trunnions for use are connected via a link mechanism.

  According to a third aspect of the present invention, in the traveling vehicle according to the first aspect, the linear hydraulic transmission and the turning hydraulic transmission are arranged in a transmission case, and the speed reduction is interlocked with a turning pump trunnion. An operation shaft and a link mechanism that connects the trunnion for the straight motor to the trunnion for the swing pump via the deceleration operation shaft are provided.

  According to the first aspect of the present invention, a traveling machine body supported by the left and right traveling units, a straight traveling hydraulic transmission having a rectilinear hydraulic pump and a rectilinear hydraulic motor, and a swing having a swing hydraulic pump and a swing hydraulic motor. In a traveling vehicle comprising a hydraulic transmission and a forced differential mechanism that combines and outputs the output of the straight hydraulic transmission and the output of the turning hydraulic transmission, the output of the straight hydraulic motor can be changed. The output control mechanism of the rectilinear hydraulic motor is connected to the output control mechanism of the swing hydraulic pump, and the output of the rectilinear hydraulic motor changes in conjunction with the output change of the swing hydraulic pump. Therefore, the turning radius of the traveling unit (the turning operation) is changed by the turning operation (steering control of the turning hydraulic pump) of the operator that changes (changes direction) the course of the traveling machine body. Of the steering angle) to the in proportion, can slow down the moving speed of the traveling machine body (vehicle speed). When the route of the traveling machine body is changed (direction change) by operating the turning operation tool, the moving speed of the traveling machine body can be reduced without operating the traveling gear shifting operation tool. In addition, the manufacturing cost can be easily reduced as compared with a conventional steering link mechanism or transmission link mechanism. Maintenance work can be simplified. Parts costs, assembly man-hours or adjustment man-hours in the production line can be reduced.

  According to the second aspect of the present invention, the straight hydraulic transmission and the turning hydraulic transmission are arranged in a transmission case, and the turning pump trunnion and the straight motor trunnion are arranged via the deceleration link mechanism. Therefore, the straightening motor trunnion can be connected to the swivel pump trunnion by a simple speed reduction link mechanism, and the adjustment operation in the assembly work can be simplified.

  According to a third aspect of the present invention, the linear hydraulic transmission and the turning hydraulic transmission are arranged in a transmission case, the speed reducing operation shaft interlocking with the turning pump trunnion, and the turning pump trunnion A link mechanism for connecting a trunnion for a straight-advancing motor via the deceleration operation shaft, so that a trunnion for a straight-advancing motor can be connected to the trunnion for a rectilinear pump by a simple link mechanism. The adjustment operation in the assembly work can be simplified. The steering operation mechanism on the turning operation tool side to be connected to the turning pump trunnion, the link mechanism to be connected between the deceleration operating shaft and the straight motor trunnion, and the like can be arranged without causing interference with each other.

It is a right view of the combine for 2 line cutting. It is a top view of a combine. It is drive system diagrams, such as a mission case. It is a hydraulic circuit diagram of a combine. It is a right view of a mission case part. FIG. 6 is an enlarged explanatory view of FIG. 5.

  Hereinafter, an embodiment embodying the present invention will be described based on the drawings (FIGS. 1 to 6) 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 (granulated soot) 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 FIGS. 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 mission case 18, the steering input shaft 78, the reverse rotation 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 that is larger than the belief turning radius. Turn left or right. 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, with reference to FIGS. 4-6, the hydraulic circuit and speed change operation structure of the traveling drive part which transmits motive power to the traveling crawler 2 are demonstrated. As shown in FIG. 4, the first hydraulic pump 55 for straight travel and the first hydraulic motor 56 are connected by a closed loop straight forward oil passage 91. The second hydraulic pump 57 for turning and the second hydraulic motor 58 are connected by a closed loop turning oil passage 92. The first hydraulic pump 55 and the second hydraulic pump 57 and the charge pump 93 are driven by the engine 17, and the first hydraulic motor is controlled by the swash plate angle control of the first hydraulic pump 55 or the swash plate angle control of the second hydraulic pump 57. 56 or the second hydraulic motor 58 is configured to perform forward rotation or reverse rotation.

  Further, as shown in FIG. 4, the turning oil passage 92 includes an unload valve 94 that short-circuits the pressure oil discharge side and the suction side of the second hydraulic pump 57. A switching solenoid 95 is provided on the unload valve 94. Based on the detection result of a limit switch type neutral position sensor (not shown) that detects whether or not the main speed change lever 12 is supported at the neutral position (vehicle speed 0 position), the switching solenoid 95 is operated and the second hydraulic pump In a state where the pressure oil discharge side and the suction side of 57 are short-circuited (FIG. 4), or in a state where the second hydraulic motor 58 is hydraulically connected to the second hydraulic pump 57 (a swirling oil passage 92 closed loop state). Can be switched.

  For example, when the main transmission lever 12 is supported at the neutral position (vehicle speed 0 position), the pressure oil discharge side and the suction side of the second hydraulic pump 57 are short-circuited, and the control lever 10 turns left or right. Even when operated in the rotational direction, the rotational output of the second hydraulic motor 58 is maintained at zero. That is, when the main transmission lever 12 is in the neutral position, the traveling machine body 1 does not move even if the control lever 10 is turned. On the other hand, when the main transmission lever 12 is supported at a position other than the neutral position (vehicle speed 0 position), the second hydraulic motor 58 is hydraulically connected to the second hydraulic pump 57, and the control lever 10 is turned counterclockwise. When operated in the direction of turning or turning right, a turning driving force is output from the second hydraulic motor 58, and the course of the traveling machine body 1 is corrected with a turning radius proportional to the operation amount of the control lever 10. Instead of electrical connection such as a neutral position sensor (not shown), an unload valve 94 is mechanically connected to the main transmission lever 12 via a cam or a link mechanism, etc., so that the main transmission lever 12 can be operated. The unload valve 94 can also be switched in conjunction with it.

  As shown in FIGS. 5 and 6, the straight pump side trunnion 55 b and the straight pump side trunnion arm 55 c that change the swash plate 55 a angle of the first hydraulic pump 55, and the straight drive that changes the swash plate 56 a angle of the first hydraulic motor 56. A motor side trunnion 56b and a straight motor side trunnion arm 56c are provided. On the other hand, the swing pump side trunnion 57b and the swing pump side trunnion arm 57c for changing the swash plate 57a angle of the second hydraulic pump 57, and the swing motor side trunnion 58b and the swing motor for changing the swash plate 58a angle of the second hydraulic motor 58 are shown. A side trunnion arm 58c is provided. On the other hand, a linear pump side sensor shaft 55d and a linear pump side sensor arm 55e interlocked with the linear pump side trunnion 55b, and a rotary pump side sensor shaft 57d and a rotary pump side sensor arm 57e interlocked with the rotary pump side trunnion 57b are provided.

  Further, the straight transmission pump side trunnion arm 55c is connected to the main transmission lever 12 via the main transmission operation rod 111, and the angle of the swash plate 55a of the first hydraulic pump 55 is changed by tilting the main transmission lever 12 in the front-rear direction. Then, the hydraulic output of the first hydraulic pump 55 is controlled, the rotational direction and the rotational speed of the first hydraulic motor 56 are changed, the traveling direction is switched to the forward side or the backward side, and the moving speed (straight vehicle speed) is changed. It is configured to shift. The auxiliary transmission shaft 113 of the transmission case 18 is connected to the auxiliary transmission lever 13 via the auxiliary transmission operation rod 112, and the operation of the auxiliary transmission lever 13 switches the output of the first hydraulic motor 56 to low speed or high speed.

  Further, the swivel pump side trunnion arm 57c is connected to the control lever 10 via the steering rod 114, and the angle of the swash plate 57a of the second hydraulic pump 57 is changed by tilting the control lever 10 in the left-right direction. 2 The hydraulic output of the hydraulic pump 57 is controlled, and the rotational speed of the second hydraulic motor 58 is changed to change the course (turning radius) of the traveling machine body 1. In addition, a shift neutral mechanism 116 having a neutral spring 115 is provided in the straight pump side trunnion 55b installation portion so as to support the straight pump side trunnion arm 55c in a shift neutral state.

  Next, as shown in FIG. 6, there is provided a forward / reverse switching mechanism 221 for connecting the turning motor side trunnion arm 58c to the linear pump side sensor arm 55e. The switching relay shaft 223 is pivotally supported via the bearing body 222 on the case (transmission case 18) of the straight hydraulic transmission 53. The first relay link 224 and the second relay link 225 are fixed to the switching relay shaft 223. A second relay link 225 is connected to the linear pump side sensor arm 55e. The first relay link 224 is connected to the turning motor side trunnion arm 58c via a forward / reverse switching rod 226 with a turnbuckle for adjusting the length.

  That is, when the main transmission lever 12 is shifted forward, the forward / reverse switching mechanism 221 switches the swash plate 58a angle of the second hydraulic motor 58 to the normal rotation angle. On the other hand, when the main transmission lever 12 is operated to shift backward, the forward / reverse switching mechanism 221 switches the swash plate 58a angle of the second hydraulic motor 58 to the reverse rotation angle. Accordingly, in either the forward side operation of the main speed change lever 12 or the reverse side operation of the main speed change lever 12, the traveling body 1 can be turned to the right by the tilting operation of the control lever 10 in the right direction. By the tilting operation of the lever 10 in the left direction, the traveling machine body 1 can be turned in the left direction.

  The swing motor side trunnion arm 58c is provided with a switching spring (not shown) such as a fulcrum spring that is elastically supported at the forward rotation position or the reverse rotation position, and the angle of the swash plate 58a of the second hydraulic motor is the forward rotation angle or reverse rotation. It is configured to be maintained at either one of the angles.

  Further, a turning speed reduction mechanism 231 is provided for connecting the straight motor side trunnion arm 56c to the turning pump side sensor arm 57e. A transmission relay shaft 233 is pivotally supported on the transmission case 18 via a bearing body 232. The first linkage link 234 and the second linkage link 235 are fixed to the deceleration relay shaft 233. The first linkage link 224 is connected to the sensor arm 75e via a turning deceleration rod 236 with a length-adjusting turnbuckle. Further, the second linkage link 235 is connected to the trunnion arm 56c.

  That is, when the control lever 10 is tilted to the left turning side (or right turning side), the turning deceleration mechanism 231 returns the angle of the swash plate 56a of the first hydraulic motor 56 to the deceleration side. Therefore, in either the left turning operation or the right turning operation of the control lever 10, the output of the first hydraulic motor 56 is controlled to be decelerated in proportion to the operation amount of the control lever 10. With the main transmission lever 12 fixed at a fixed operation position on the forward side or the reverse side, the vehicle speed is reduced by the turning operation of the control lever 10 as the turning radius of the traveling machine body 1 decreases, while the control lever 10 moves straight. By returning to the position, the vehicle speed of the traveling machine body 1 returns to the original speed (the vehicle speed set by the main transmission lever 12).

  As shown in FIGS. 1 and 4 to 6, a traveling machine body 1 supported by a traveling crawler 2 as a left and right traveling unit, a first hydraulic pump 55 as a linear hydraulic pump, and a first hydraulic pressure as a linear hydraulic motor. A straight hydraulic transmission 53 having a motor 56, a second hydraulic pump 57 as a swing hydraulic pump, and a swing hydraulic transmission 54 having a second hydraulic motor 58 as a swing hydraulic motor, and a straight hydraulic shift 53 In the traveling vehicle including the differential mechanism 61 as a forced differential mechanism that combines the output and the output of the turning hydraulic transmission 54, the output of the second hydraulic motor 58 is configured to be changeable. A swivel motor side trunnion 58b as an output control mechanism of the second hydraulic motor 58 is connected to a straight pump side trunnion 55b as an output control mechanism of the first hydraulic pump 55, and the first oil In conjunction with the output changing of the pump 55, it is configured such that the output of the second hydraulic motor 58 is changed. Therefore, when the travel shift position is the neutral position (the output of the first hydraulic pump 55 is 0), the swash plate angle of the second hydraulic motor 58 can be set to 0 and the output of the second hydraulic pump 57 can be disabled. Movement of the traveling machine body 1 due to an erroneous operation of the control lever 10 (turning operation tool) can be prevented. Further, the output (turning speed) of the turning hydraulic transmission 54 is changed based on the control of the straight-traveling hydraulic transmission 53 (change in vehicle speed) without providing a steering link mechanism or a speed change link mechanism as in the prior art. it can. In addition, the manufacturing cost can be easily reduced while maintaining the same turning control performance as that of the conventional steering link mechanism or transmission link mechanism. 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 6, the straight traveling hydraulic transmission 53 and the turning hydraulic transmission 54 are arranged in the transmission case 18, and the straight traveling pump side trunnion 55 b for the first hydraulic pump 55 travels straight. There is provided a forward / reverse switching mechanism 221 as a link mechanism for connecting the turning motor side trunnion 58b for the second hydraulic motor 58 via a linear pump side sensor shaft 55d as a turning operation shaft interlocked with the pump side trunnion 55b. . Therefore, while the swivel motor side trunnion 58b can be connected to the straight pump side trunnion 55b by a simple forward / reverse switching mechanism 221, adjustment operations and the like in the assembly work can be simplified. A main speed change rod 111 as a speed change operation mechanism on the speed change lever 12 side to be connected to the straight pump side trunnion 55b, a forward / reverse switching mechanism 221 to be connected between the straight pump side sensor shaft 55d and the turning motor side trunnion 58b, etc. They can be placed without interfering with each other.

  As shown in FIG. 4, an unload valve 94 is provided in the hydraulic circuit (closed loop turning oil passage 92) of the turning hydraulic transmission 54, so that even when there is an output from the second hydraulic pump 57 when the speed change is neutral. The unloading operation of the unloading valve 94 is configured such that the output of the second hydraulic motor 58 becomes zero. Therefore, the output from the second hydraulic pump 57 can be disabled by the unload valve 94 when the shift is neutral. While the assembly man-hours or adjustment man-hours in the production line can be reduced, the minute output of the second hydraulic motor 58 can be easily prohibited. For example, the turning output of the turning hydraulic transmission 54 even when the control lever 10 (turning operation tool) is operated when the main speed change lever 12 (travel shifting operation tool) is in the neutral position (straight-running output is 0). Can be maintained at zero, and the stop state of the traveling machine body 1 can be continued.

  Further, as shown in FIGS. 1 and 4 to 6, a traveling machine body 1 supported by the left and right traveling units 2, a first hydraulic pump 55 as a linear hydraulic pump, and a first hydraulic motor 56 as a linear hydraulic motor. , A turning hydraulic transmission 54 having a second hydraulic pump 57 as a turning hydraulic pump and a second hydraulic motor 58 as a turning hydraulic motor, and an output of the straight hydraulic transmission 53. In a traveling vehicle including a differential mechanism 61 as a forced differential mechanism that synthesizes and outputs the output of the turning hydraulic transmission 54, the output of the first hydraulic motor 56 can be changed, and the second hydraulic pressure can be changed. Output control mechanism of the pump 57 The trunnion 57b of the first hydraulic motor 56 is connected to the trunnion 57b of the swing pump side trunnion 57b, and interlocked with the output change of the second hydraulic pump 57. Te constitute such that the output of the first hydraulic motor 56 is changed.

  Therefore, by the turning operation (steering control of the second hydraulic pump 57) of the operator who changes (changes direction) the traveling path of the traveling machine body 1, it is proportional to the turning radius of the traveling crawler 2 (the steering angle of the turning operation tool 10). The moving speed (vehicle speed) of the traveling machine body 1 can be reduced. When changing the course of the traveling machine body 1 by operating the turning operation tool 10, the moving speed of the traveling machine body 1 can be reduced without operating the main speed change lever 12 (traveling gear operation tool). In addition, the manufacturing cost can be easily reduced as compared with a conventional steering link mechanism or transmission link mechanism. 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 6, the straight hydraulic transmission 53 and the turning hydraulic transmission 54 are arranged in the transmission case 18, and the turning pump trunnion 57b and the straight motor trunnion 56b are arranged. These are connected via a turning speed reduction mechanism 231 as a speed reduction link mechanism. Therefore, the straightening motor trunnion 56b can be connected to the swivel pump trunnion 57b by a simple speed reduction link mechanism (swing speed reduction mechanism 231), and adjustment operations and the like in the assembly work can be simplified.

  As shown in FIGS. 4 to 6, the straight hydraulic transmission 53 and the turning hydraulic transmission 54 are arranged in the transmission case 18 and turn as a deceleration operation shaft that is linked to the turning pump trunnion 57b. A pump side sensor shaft 57d and a turning speed reduction mechanism 231 for connecting the straight motor trunnion 56b to the turning pump trunnion 57b via the turning pump side sensor shaft 57d are provided. Accordingly, the straightening motor trunnion 56b can be connected to the swivel pump trunnion 57b by the simple swivel speed reduction mechanism 231, and the adjustment operation in the assembly work can be simplified. A steering operation mechanism (steering rod 114) on the control lever 10 (turning operation tool) side to be connected to the turning pump trunnion 57b, and a turning speed reduction mechanism to be connected between the turning pump side sensor shaft 57d and the straight motor trunnion 56b. 231 and the like can be arranged without interfering with each other.

1 traveling machine body 2 traveling crawler (traveling section)
18 Mission case 53 Hydraulic transmission for rectilinear movement 54 Hydraulic transmission for turning 55 First hydraulic pump (linear hydraulic pump)
56 1st hydraulic motor (straight forward hydraulic motor)
56b Trunion 57 on straight motor side Second hydraulic pump (swivel hydraulic pump)
57d Rotary pump side sensor shaft (deceleration operation shaft)
58 Second hydraulic motor (Swivel hydraulic motor)
61 Differential mechanism (forced differential mechanism)
231 Turning deceleration mechanism (link mechanism)

Claims (3)

A traveling machine body supported by the left and right traveling units, a rectilinear hydraulic transmission having a rectilinear hydraulic pump and a rectilinear hydraulic motor, a slewing hydraulic transmission having a slewing hydraulic pump and a slewing hydraulic motor, and the rectilinear hydraulic shift In a traveling vehicle having a forced differential mechanism that combines and outputs the output of the aircraft and the output of the turning hydraulic transmission,
The output of the rectilinear hydraulic motor is configured to be changeable, the output control mechanism of the rectilinear hydraulic motor is connected to the output control mechanism of the swing hydraulic pump, and in conjunction with the output change of the swing hydraulic pump, A traveling vehicle characterized in that the output of the straight hydraulic motor changes.   2. The straight hydraulic transmission and the turning hydraulic transmission are arranged in a transmission case, wherein the turning pump trunnion and the straight motor trunnion are connected via a link mechanism. The traveling vehicle described in 1.   The linear hydraulic transmission and the turning hydraulic transmission are arranged in a transmission case, the speed reducing operation shaft interlocking with the turning pump trunnion, and the straight driving motor via the speed reducing operation shaft to the turning pump trunnion The traveling vehicle according to claim 1, further comprising a link mechanism that connects the trunnions for use.

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