JP3772343B2 - Vehicle running interlock device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
  The present inventionVehicle running interlockThe present invention relates to a device, and in particular, can be used for a transmission device of various vehicles, for example.
[0002]
[Prior art and problems to be solved by the invention]
  Conventionally, this kindVehicle running interlockThe equipment is a hydrostatic type consisting of a hydraulic pump and a hydraulic motor.Driving interlockThe device is known. However, the cost is high and a large installation space is required.
[0003]
  Therefore, low cost and small installation space.Driving interlockThe technical problem which should be solved in order to provide an apparatus arises, and this invention aims at solving this problem.
[0004]
[Means for Solving the Problems]
  In view of the above problems, the present invention is configured as follows.
  That is, the left and right axle cases 47, 47 provided in the vehicle bodyDriving interlockDevice, each of the left and rightDriving interlockThe apparatus has a two-stage planetary gear having planetary gears 82 and 83 and a counter planetary gear 85 interposed between an input side sun gear 79 integral with the input shaft 72 and an output side sun gear 80 integral with the output shaft 74. A two-stage planetary gear mechanism 75, a carrier 76 connecting the planetary gears, and a normal rotation clutch 77 that fixes the input side sun gear 79 to rotate integrally with the input-side sun gear 79 by a normal spring 91, and the forward rotation clutch. A reverse clutch 78 in the form of a wet multi-plate, which is disposed on the inner side of the vehicle body than 77 and integrally fixes the carrier 76 to the axle case 47 in conjunction with the turning operation of the forward rotation clutch 77 by hydraulic operation. VehicleDriving interlockapparatusThe two-stage planetary gear mechanism 75, the forward rotation clutch 77, and the reverse rotation clutch 78 are arranged in parallel on the same axis from the outside of the vehicle body in the left and right axle cases 47, 47, respectively. Vehicle running interlock deviceIt was.
[0006]
[0007]
[0008]
[0009]
[0010]
[Effects of the Invention]
  The rotation of the input shaft 72 is transmitted to the output shaft sun gear 80 and the output shaft 74 via the input side sun gear 79 and the two-stage planetary gear mechanism 75. At this time, forward rotationClutch77, when the carrier of the two-stage planetary gear mechanism 75 is fixed integrally with the input-side sun gear 79, the rotation of the input shaft 72 is transmitted in the normal rotation, and the fixing is gradually released, whereby the input side The planetary gears 82, 83, 85 rotate relative to the sun gear 79, and the speed of the forward rotation is reduced. Further, the rotation stops when the fixing is completely released.
[0011]
  On the other hand, reverseClutch78, the carrier 76 of the two-stage planetary gear mechanism 75 isIntegrated with the axle case 47When fixed, the rotation of the input shaft 72 is transmitted in the reverse direction. By gradually strengthening the fixing, the planetary gears 82, 83, 85 do not rotate relative to the input-side sun gear 79. The rotation of the input shaft 72 is transmitted to the output shaft 74 in the reverse direction to increase the speed.
[0012]
【The invention's effect】
  In the present invention configured as described above, the two-stage planetary gear mechanism is interposed between the input shaft and the output shaft, and the forward rotation clutch 77 and the reverse rotation clutch 78 are provided. No. 91 is always on, and only the reverse clutch 78 is hydraulically operated, and both clutches are selectively engaged so that it is inexpensive and continuously from forward output to reverse output.It can be linked to runningit can.
[0013]
[0014]
  Since the reverse rotation clutch 78 is provided on the inner side of the vehicle body than the forward rotation clutch 77, the configuration relating to the hydraulic operation in particular is provided.Can be compactCost can be reduced.
[0015]
  Also,BookThe invention includes a two-stage planetary gear mechanism 75, a forward rotation clutch 77, a reverse rotation clutch 78 and a reverse rotation clutch 78 in the axle case 47 in order from the outside of the vehicle body.NextSo that they are arranged side by side on the same axis.the aboveIn addition to the effects, the conduction structure itself can be made compact.So space can be saved.
[0016]
[0017]
[0018]
DETAILED DESCRIPTION OF THE INVENTION
  Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings. 1 and 2 show a crawler type tractor 10 as an example of a work vehicle. A drive sprocket 12 is attached to a rear axle 11, and a follower sprocket 14 and a wheel 15 are pivotally attached to a track frame 13 that rotatably supports the drive sprocket 12. A crawler 16 is provided between the drive sprocket 12, the driven sprocket 14, and the wheel 15, and the front end of the track frame 13 is fixed to the vehicle body frame 17 to constitute a crawler type traveling device C. Reference numeral 23 denotes a mission case. The crawler type traveling device C is supported on the left and right sides of the mission case 23 and protrudes rearward from the mission case 23. The crawler 16 of the crawler type traveling device C is It is located behind the rear end of the vehicle body. As will be described later, the rotational power of the engine 46 is input to the mission case 23, and is transmitted to the rear axle 11 after being shifted by the transmission in the transmission case 23, and the drive sprocket 12 rotates to drive the crawler 16. The
[0019]
  In the vicinity of the driver's seat 18, a position lever 40 for setting the lifting position of the ground work machine 26, a plowing depth adjustment dial 41 for setting the plowing depth of the ground work machine 26, and a horizontal inclination of the ground work machine 26 are set. A level adjustment dial 42 and the like are provided, and a slope sensor 43 that detects a rolling angle in the left-right direction of the vehicle body is installed below the driver's seat 18. Further, a rotationally operated steering handle 19 which is a steering operation portion is provided in front of the driver's seat 18, and a steering handle shaft 20 is inserted into a steering handle column 21, and a steering operation device 22 is provided at a base end portion thereof. Is installed. Further, a brake pedal 44 is provided on the right side of the steering handle column 21, and a clutch pedal 45 is provided on the left side of the steering handle column 21. A controller 100 as a control unit is provided below the driver's seat 18.
[0020]
  A ground working machine 26 such as a rotary is connected to the rear portion of the vehicle body via a link mechanism 25. The link mechanism 25 includes a top link 27 and left and right lower links 28, 28. , 29 and the lower links 28, 28 are connected by lift rods 30, 30, and the lift arms 29 are rotated by driving the lift cylinder 32, whereby the lower links 28, 28 are moved via the lift rods 30, 30. Move up and down. Thus, the ground work machine 26 moves up and down with the tip ends of the lower links 28, 28 as the center of rotation.
[0021]
  A lift arm angle sensor 33 is provided at the rotation base of the lift arm 29 as a sensor for detecting the raising / lowering position of the ground work machine 26, and the lift arm angle sensor 33 detects the rotation angle of the lift arm 29, The elevation height of the ground work machine 26 is calculated. Further, a rear cover 35 is rotatably attached to the rear end portion of the main cover 34 of the ground work machine 26, and the rotation angle of the rear cover 35 is detected by the rear cover sensor 36 so that the working depth control of the ground work machine 26 can be performed. Is formed.
[0022]
  On the other hand, as an actuator for changing the horizontal inclination of the ground work machine 26 with respect to the vehicle body, a rolling cylinder 37 is provided in the middle of either the left or right lift rod 30, and the rolling cylinder 37 is expanded and contracted to increase the lift amount of the lower link 28. The rolling angle of the ground work machine 26 can be changed by changing the angle at. A stroke sensor 38 is provided adjacent to the rolling cylinder 37. The stroke sensor 38 detects the expansion / contraction length of the rolling cylinder 37 to measure the rolling angle of the ground work machine 26 with respect to the vehicle body, and the horizontal adjustment dial. The rolling cylinder 37 is expanded and contracted in accordance with the set value 42 so that the rolling control of the ground work machine 26 can be performed.
[0023]
  The configuration of the power transmission system will be described with reference to FIGS. The mission case 23 is composed of a front mission case 23a, a mid mission case 23b, and a rear mission case 23c. A power input shaft 48 projects from the front of the front mission case 23a at the top thereof. An engine rotation output shaft 49 and a power input shaft 48 surrounded by 17 are coaxially connected.
[0024]
  The rotational power of the engine 46 is inputted into the front mission case 23a from the engine rotational output shaft 49 and the power input shaft 48, first transmitted to the lower part of the case by the reduction gear 50, and then transmitted to the rear main clutch 51. Then, it is transmitted to the hydraulic pump 52 provided in the front part of the front mission case 23a. The power that is turned on and off by the main clutch 51 is appropriately decelerated by the main transmission 53 and the sub-transmission 54 in the mid-transmission case 23b, and the rear mission is transmitted through the pinion shaft 55 that serves as the sub-transmission output shaft. It is transmitted into the case 23c. A support shaft 68 is provided between the left and right side walls of the rear mission case 23c, and a bevel gear 69 that meshes with the pinion shaft 55 is spline-fitted at a position slightly deviated from the center of the support shaft 68.
[0025]
  The main transmission 53 is provided with a gear set 58 having a first to third forward speed and a first reverse speed between the main transmission drive shaft 56 and the main transmission driven shaft 57, and the main transmission driven shaft 57. By operating the slide key 59 provided in the back and forth, a so-called key shift type transmission mechanism that transmits power through any one of the gear sets 58 is provided.
[0026]
  The sub-transmission device 54 has a sub-transmission drive shaft 60 pivoted on the extension of the main transmission drive shaft 56, and the high-speed and low-speed two-stage gears 61, 62 are attached to the sub-transmission drive shaft 60. The auxiliary transmission driven shaft, that is, the pinion shaft 55 is provided on the extension of the main transmission driven shaft 57. A transmission device using a so-called constant mesh gear, in which a slidable two-stage gear 63 is provided on the pinion shaft 55, and the slidable two-stage gear 63 is slid and meshed with one of the two-stage gears 61 and 62, It has become. Reference numeral 64 denotes a PTO transmission shaft, which transmits power to a rear PTO shaft 66 protruding from a rear portion of the rear mission case 23c via a PTO transmission 65 provided in the rear mission case 23c.
[0027]
  Reference numeral 47 denotes a rear axle case 47 provided on the left and right sides of the rear mission case 23c. The rear axle case 47 is a substantially cylindrical casting case, and the crawler type traveling device C is supported by the rear axle case 47. Yes. As described above, a support shaft 68 is pivotally mounted between the left and right side walls of the rear mission case 23c, and a bevel gear 69 that engages with the pinion shaft 55 is spline-fitted at a position slightly deviated to the left of the center of the support shaft 68. In addition, a brake disc 70 is provided at a position substantially opposite to the left and right of the bevel gear 69.
[0028]
  Then, the brake pedal 44 and the brake disc 70 are connected by a link mechanism (not shown), and the brake disc 70 is crimped by depressing the brake pedal 44, thereby rotating the support shaft 68, that is, the left and right crawlers 16. , 16 is braked. A reduction gear set 71 is provided at both left and right ends of the support shaft 68, and the rotation of the bevel gear 69 is transmitted to the input shaft 72 in the rear axle case 47 via the reduction gear set 71.
[0029]
  A forward / reverse switching device 73 is disposed inside the rear axle case 47, and the forward / reverse switching device 73 is pivotally mounted coaxially with the input shaft 72 on one end side of the input shaft 72 and the input shaft 72. Output shaft 74, a two-stage planetary gear mechanism 75 interposed between the input shaft 72 and the output shaft 73, and a wet multi-plate type forward rotation provided on a carrier 76 of the two-stage planetary gear mechanism 75. A clutch 77 (outside the vehicle body) and a reverse clutch 78 (inside the vehicle body) are included. The carrier 76 includes a first carrier 76a constituting a two-stage planetary gear mechanism 75 between two opposing surfaces, and a second carrier 76b provided with a forward rotation clutch 77 and a reverse rotation clutch 78. And are integrally formed by bolting.
[0030]
  In the configuration of the two-stage planetary gear mechanism 75, an input side sun gear 79 is fixed to one end portion of the input shaft 72, and an output side sun gear 80 is fixed to one end portion of the output shaft 74. In addition, the first carrier 76a is mounted so as to be freely rotatable around the input shaft 72 and the output shaft 74, and a plurality of the first carriers 76a are arranged on the same circumference centering on the input shaft 72. Are provided with first carrier pins 81, 81. In the present embodiment, three first carrier pins 81, 81, 81 are provided at equal intervals on the same circumference.
[0031]
  Then, the input-side planetary gear 82 and the output-side planetary gear 83 are coaxially and integrally pivotally attached to each first carrier pin 81. Further, the carrier 76 is provided with the same number of second carrier pins 84 as the first carrier pins 81 at equal intervals on the same circumference, and a counter gear 85 is pivotally attached to each second carrier pin 84, and the counter gear 85 is meshed with both the output-side planetary gear 83 and the output-side sun gear 80. That is, the first and second carrier pins 81 and 84 are provided between the two opposing surfaces of the first carrier 76a to form a two-stage six-axis planetary gear mechanism.
[0032]
  A carrier pin fixing plate 86 is bolted to the outer surface of the first carrier 76a. The carrier pin fixing plate 86 is larger than the outer shape of the first carrier 76a and is extended outward from the outer edge. At the same time, the tip of the carrier pin fixing plate 86 is bent to provide a notch 86a, which is read by a rotation sensor (not shown). Therefore, the fixed and rotating state of the first carrier 76a can be easily detected without using a dummy gear or the like. In addition, since the tip of the carrier pin fixing plate 86 is bent, the surrounding oil is stirred and the cooling performance can be improved.
[0033]
  On the other hand, the forward rotation clutch 77 and the reverse rotation clutch 78 are provided on opposite sides of the partition wall 76c of the second carrier 76b, and the drive disk 77a of the forward rotation clutch 77 is connected to the input side sun gear 79, that is, the input shaft 72. The driven disk 77b of the forward rotation clutch 77 is integrally engaged with the second carrier 76b. Further, the drive disk 77a and the driven disk 77b are alternately overlapped to provide a pressing plate 90 on the partition wall 76c side, and a spring 91 is interposed between the pressing plate 90 and the partition wall 72c. Thus, the pressing plate 90 is pushed to the outside of the vehicle body to be urged so as to press the drive disk 77a and the driven disk 77b.
[0034]
  On the other hand, the drive disk 78a of the reverse clutch 78 is integrally engaged with the rear axle case 47, and the driven disk 78b of the reverse clutch 78 is integrally engaged with the second carrier 76b. Further, the drive disk 78a and the driven disk 78b are alternately overlapped to provide a pressing plate 92 on the partition wall 72c side, and a hydraulic piston 93 is interposed between the pressing plate 92 and the partition wall 72c. The pressing plate 90 of the forward rotation clutch 77 and the pressing plate 92 of the reverse rotation clutch 78 are connected by a connecting rod 94 so that the both pressing plates 90 and 92 move together. Accordingly, when the pressure oil is supplied to the oil chamber 95, the hydraulic piston 93 pushes the pressing plate 92 to the inside of the vehicle body, and presses the drive disk 78a and the driven disk 78b.
[0035]
  The other end of the output shaft 74 is integrally assembled with a lid 96 that shields the outer open portion of the rear axle case 47. The lid 96 is made of the same casting as the rear axle case 47. An outer lid portion 96a having bolt holes 97 for connecting to the rear axle case 47, an inner lid portion 96b attached to the inner surface of the outer lid portion 96a with a bolt to cover the inner surface, and the outer lid portion The ring gear 98 is interposed between the inner cover 96b and the inner cover 96b. A pack-like space 99 is formed between the outer lid portion 96a and the inner lid portion 96b, and one end portion of the rear axle 11 is pivotally mounted coaxially with the output shaft 74 in the space portion 99. A planetary gear mechanism 101 for reducing the rotation of the output shaft 74 and transmitting it to the rear axle 11 is provided.
[0036]
  The planetary gear mechanism 101 includes a sun gear 102 fixed to the other end portion of the output shaft 74, a carrier 103 fixed to one end portion of the rear axle 11, a carrier pin 104 provided on the carrier 103, A planetary gear 105 is pivotally attached to the carrier pin 104 and meshes with both the sun gear 102 and the ring gear 99. Further, the planetary gear mechanism 101 can arbitrarily change the reduction ratio according to the specification change of the tractor 10 such as when the wheel specification and the crawler specification are mutually changed or when the wheel diameter of the wheel specification is changed. It may be a simple mechanism. Reference numeral 106 denotes a rotation speed detection gear, and a non-contact type rotation sensor 107 is disposed close to the rotation speed detection gear 106 so that the output rotation speed to the left and right crawlers 16 and 16 can be detected. It is configured.
[0037]
  Next, the operation of the forward / reverse switching device 73 will be described. Normally, the spring 91 presses the disks 77a and 77b of the forward rotation clutch 77 through the pressing plate 90. In this state, the input side sun gear 79 that engages with the drive side disk 77a of the forward rotation clutch 77; Since the carrier 76 engaged with the driven disk 77b rotates integrally with the driven disk 77b, the rotation of the input shaft 72 is transmitted from the input side sun gear 79 to the output side sun gear 80 at a one-to-one rotation ratio. The shaft 74 rotates in the same direction at the same rotation speed.
[0038]
  On the other hand, when pressure oil is fed into the oil chamber 95 of the reverse clutch 78, the hydraulic piston 93 presses the pressing plate 92 to press the disks 78a and 78b of the reverse clutch 78. In this state, the rear axle case 47 that engages with the drive side disk 78a of the reverse rotation clutch 78 and the carrier 76 that engages with the driven disk 78b are integrated, so the carrier 76 does not rotate. Therefore, the rotation of the input shaft 72 is transmitted by being decelerated from the input-side sun gear 79 to the input-side planetary gear 82, and further transmitted from the output-side planetary gear 83 through the counter gear 85 to the output-side sun gear 80 by decelerating and reversely rotating. The input shaft 72 and the output shaft 74 rotate in opposite directions, and the rotation speed is reduced to a predetermined rotation speed according to each gear ratio of the two-stage planetary gear mechanism 75.
[0039]
  Here, when the forward rotation clutch 77 is engaged and the input shaft 72 and the output shaft 74 are rotating in the same direction and at the same rotation speed, the pressure plate 92 of the reverse rotation clutch 78 is driven by the hydraulic piston 93. When is pressed, since the pressing plate 92 and the pressing plate 90 of the forward rotation clutch 77 are connected by the connecting rod 94, both the pressing plates 90, 92 move together in the vehicle body inner direction. Accordingly, as the disks 78 a and 78 b of the reverse rotation clutch 78 are pressure-bonded, the pressure of the disks 77 a and 77 b of the forward rotation clutch 77 is gradually released against the bias of the spring 91. That is, as the hydraulic pressure supplied to the oil chamber 95 increases, the forward rotation clutch 77 slips and the reverse rotation clutch 78 is connected in a half-clutch state, and the rotational speed of the output shaft 74 decreases.
[0040]
  Thus, the rotational speed of the rear axle 11 on one side decreases, and the driving speed of the crawler 16 is reduced. When pressure oil is continuously fed to the oil chamber 95 and the amount of movement of the hydraulic piston 93 is increased to the inside of the vehicle body in the figure, the pressure-bonding of the driving disk 77a and the driven disk 77b of the forward clutch 77 is completely released. Thus, the rotation of the output side sun gear 80 becomes zero, the rotation of the crawler 16 on one side stops, and the forward / reverse switching device 73 is switched from the forward rotation state to the cut state. If pressure oil continues to be fed to the oil chamber 95 through this cut-off state, the drive side disk 78a and the driven side disk 78b of the reverse rotation clutch 78 are gradually pressed and the output side sun gear 80 is rotated in the reverse direction. The crawler 16 is driven in the reverse direction, and the forward / reverse switching device 73 is in the reverse rotation state.
[0041]
  FIG. 7 is a block diagram of the control system. Inside the controller 100 which is a control unit, a CPU for calculating and processing various information, a RAM for storing various sensor values and setting values, and a ROM for storing control programs and the like The controller 100 has an input unit for setting signals such as a position lever 40, a tilling depth adjustment dial 41, a horizontal adjustment dial 42, a lift arm angle sensor 33, a slope sensor 43, and crawler rotations on the left and right sides. Detection signals from the sensors 107 and 107, the steering angle sensor 110, the throttle position sensor 111, the engine speed sensor 112, and the like are input.
[0042]
  Further, based on these input signals, from the output part of the controller 100, a lift solenoid or a lower solenoid of the control valve for the lift cylinder 32, an extension solenoid or a contract solenoid of the control valve for the rolling cylinder 37, and a brake solenoid of the control valve for the brake disk 70. The control signals are output to the clutch solenoids of the control valves for the left and right forward / reverse switching devices 73, the governor adjusting actuators, and the like.
[0043]
  FIG. 8 shows the relationship between the magnitude of the clutch current (clutch cylinder pressure) output from the controller 100 and the rotation state of the crawler 16. For example, when the clutch current is 0 A in the forward running state, the clutch cylinder pressure is 0 kg / cm.²As described above, the forward rotation clutch 77 is connected at full pressure by the urging of the spring 91, the rotation of the input shaft 72 is transmitted to the output shaft 74 as it is, and the crawler 16 is rotationally driven in the forward direction. The If the clutch current output from the controller 100 to the clutch solenoid of the forward / reverse switching device 73 is gradually increased to increase the clutch cylinder pressure, the forward rotation clutch 77 slips when the clutch current is around 0.2 A, and the crawler 16 The rotational speed in the forward direction decreases. When the clutch current increases to around 0.4A, the clutch cylinder pressure is 10kg / cm.²Thus, both the forward rotation clutch 77 and the reverse rotation clutch 78 hold the disengaged state. For this reason, the rotation of the input shaft 72 is not transmitted to the output shaft 74 and the rear axle 11, and the crawler 16 is not driven to rotate.
[0044]
  From this state, when the clutch current is further increased to around 0.6 A, the reverse rotation clutch 78 is connected while slipping, the rotation of the input shaft 72 is reversed and transmitted to the output shaft, and the half clutch In this state, the crawler 16 starts to rotate in the backward direction. When the clutch current is increased to about 0.8 A, the clutch cylinder pressure is 20 kg / cm.²Thus, the reverse rotation clutch 78 is connected at full pressure. Accordingly, the crawler 16 is driven at a high speed in the backward direction.
[0045]
  In this way, by changing the clutch current output from the controller 100, the clutch cylinder pressure of the forward / reverse switching device 73 is increased or decreased, and the connected state of the forward rotation clutch 77 and the reverse rotation clutch 78 is continuously changed. The forward / reverse switching device 73 can continuously and arbitrarily adjust the rotational direction and rotational speed of the crawler 16 while continuously having driving torque between forward rotation and reverse rotation.
[0046]
  Thus, the steering operation (rotation operation) of the steering handle 19 is detected by the steering angle sensor 110, and the clutch of one of the forward / reverse switching devices 73 is controlled according to the steering operation amount (change in the turning angle). Then, by decelerating the rotation of the crawler 16 inside the turning, the vehicle body can be turned by giving a rotation difference to the left and right crawlers 16 and 16. On relatively hard ground, the crawler 16 inside the turn may be stopped or reversed to turn the vehicle body suddenly. However, if the rotation of the crawler 16 is locked during turning, the ground is likely to be rough. By slipping the clutch of the switching device 73 and decelerating the rotation of the crawler 16 inside the turn, the vehicle body is turned slowly.
[0047]
  For example, in the forward running state, the clutch current is 0 A, that is, the clutch cylinder pressure is 0 kg / cm.²In this case, the left and right forward clutches 77 and 77 are connected at full pressure, and the left and right crawlers 16 and 16 are both driven to rotate forward. When the steering handle 19 is turned, the clutch current to the clutch solenoid of the forward / reverse switching device 73 on one side (turning inside) is gradually increased to increase the clutch cylinder pressure. In the vicinity of 0.2 A, the forward rotation clutch 77 slips and the rotation of one of the crawlers 16 in the forward direction decreases, so that a rotation difference occurs between the left and right crawlers 16 and 16 and the vehicle body turns. By maintaining this clutch slip state, the vehicle body can be turned slowly (brake turn) without roughening the ground.
[0048]
  Further, when the clutch current for the clutch solenoid of the forward / reverse switching device 73 on one side (turning inside) is increased to around 0.4 A, the clutch cylinder pressure is 10 kg / cm.²Thus, one of the forward rotation clutch 77 and the reverse rotation clutch 78 is in a disengaged state. For this reason, the rotation of the input shaft 72 is not transmitted to one of the rear axles 11, the rotation of the crawler 16 inside the turning stops, the turning radius becomes small, and the vehicle body can be pivoted (lock turn).
[0049]
  Further, when the clutch current for the clutch solenoid of one (turning inside) forward / reverse switching device 73 is increased to about 0.8 A, the clutch cylinder pressure is 20 kg / cm.²Thus, one reverse clutch 78 is connected at full pressure. For this reason, the rotation of the input shaft 72 is reversed and transmitted to the output shaft 74, one of the rear axles 11 is reversed and the crawler 16 on the inner side of the turning is driven to rotate backward. Accordingly, the left and right crawlers 16 and 16 rotate in opposite directions to minimize the turning radius, and the vehicle body can be turned in a super-confident manner (spin turn).
[0050]
  It should be noted that the present invention can be variously modified without departing from the spirit of the present invention, and the present invention naturally extends to the modified ones.
[Brief description of the drawings]
The figure shows an embodiment of the present invention.
FIG. 1 is a side view of a crawler tractor.
FIG. 2 is a rear view of the crawler tractor.
FIG. 3 is a cross-sectional view showing the inside of a mission case.
FIG. 4 is a sectional view showing the inside of a rear axle case.
5A is a cross-sectional view taken along line AA in FIG. 4, and FIG. 5B is a cross-sectional view taken along line BB in FIG.
FIG. 6 is an explanatory diagram showing a power transmission path.
FIG. 7 is a block diagram of a control system.
FIG. 8 is a graph showing the relationship between clutch cylinder pressure and the crawler rotation state.
[Explanation of symbols]
10 Tractor
16 Crawler
23 Mission Case
47 Rear axle case
72 Input shaft
73 Forward / reverse switching device
74 Output shaft
75 Two-stage planetary gear mechanism
76 Career
76c Bulkhead
77 Forward rotation clutch
77a Drive disk
77b Driven disk
78 Reverse clutch
78 Drive disk
78b Driven disk
79 Input side sun gear
80 Output sun gear
81 First carrier pin
82 Planetary gear on the input side
83 Output side planetary gear
84 Second carrier pin
90 pressure plate
91 Spring
92 Press plate
93 Hydraulic piston
94 Connecting rod
100 controller
C Crawler type traveling device

Claims (1)

It is a traveling interlock device for a work vehicle provided in each of the left and right axle cases 47, 47 provided in the vehicle body, and each of the left and right traveling interlocking devices is integrated with the input shaft 72 to input side sun gear 79. And a planetary gear mechanism 75 having a planetary gear 82, 83 and a counter planetary gear 85 interposed between the planetary gear 82 and the output-side sun gear 80, and the planetary gear. A normal rotation clutch 77 for fixing the carrier 76 to rotate integrally with the input-side sun gear 79 by a spring 91 at a normal time, and a forward rotation clutch 77 arranged on the vehicle body side of the forward rotation clutch 77, by hydraulic operation. The reverse of the wet multi-plate configuration in which the carrier 76 is integrally fixed to the axle case 47 in conjunction with the turning operation of the forward rotation clutch 77. The traveling interlock structure as the vehicle including the use clutch 78
In the left and right axle cases 47, 47, a two-stage planetary gear mechanism 75, a forward rotation clutch 77, a reverse rotation clutch 78, and a reverse rotation clutch 78 are sequentially arranged on the same axis from the outside of the vehicle body. Vehicle running interlock device.

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