CN104141750B - Double-clutch directly controlled stepless speed regulator for tracked vehicle - Google Patents
Double-clutch directly controlled stepless speed regulator for tracked vehicle Download PDFInfo
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- CN104141750B CN104141750B CN201410360000.2A CN201410360000A CN104141750B CN 104141750 B CN104141750 B CN 104141750B CN 201410360000 A CN201410360000 A CN 201410360000A CN 104141750 B CN104141750 B CN 104141750B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
Abstract
Disclosed is a double-clutch directly controlled stepless speed regulator for a tracked vehicle. Double clutches are connected with a double-clutch power input part. One part of power of the double-clutch power input part is output through a power output shaft speed reduction part, the other part of the power of the double-clutch power input part is transmitted to a stepless speed regulation part, the power output shaft speed reduction part transmits the power to an external operating part through a power output shaft part, the stepless speed regulation part transmits the power to a differential planetary transmission part, then the differential planetary transmission part transmits the power to drive a left track drive part and a right track drive part, a power output shaft gear shifting part is used for controlling switching of gear output of the double-clutch power input part for the power output shaft speed reduction part, and an external control connection part is used for achieving directly controlled steering. A double-clutch self-locking type hydraulic motor is adopted to control a planet carrier of a planetary gear transmission mechanism so as to achieve mechanical direct control and hydraulic stepless speed regulation, the switchover efficiency is high, integrated control is easy to implement, transmission efficiency is high, operation is easy and convenient, and steering precision is high.
Description
Technical field
The present invention relates to farm machinery transmission technology field, particularly relate to a kind of double clutch directly controlled type endless-track vehicle stepless speed variator.
Background technique
System of Tracked Vehicle Transmission System comprises clutch and the large main structure of speed changer two usually, and wheeled vehicle transmission system mainly comprises the five large main structures such as clutch, speed changer, Universal drive, main reducing gear and differential mechanism.Because endless-track vehicle and wheeled vehicle structure difference are large, working principle also has very large difference, and the transmission system of endless-track vehicle has the function of wheeled vehicle steering system usually; Current endless-track vehicle is mainly based on cat, usually Purely mechanical power transmission system transferring power is adopted with cat, it has, and structure is simple, efficiency advantages of higher, but Purely mechanical power-transmitting unit, gear shift operation is complicated, drive a car or the technical ability of tractor because agricultural machinery operator does not possess usually simultaneously, be difficult to control to the cooperation of clutch, throttle, gearshift, and then limit the development of tractor.At present, many crawler tractor manufacturers adopt oil hydraulic pump-motor integrated system to achieve the stepless drive system of crawler tractor, be improved owing to adopting the crawler tractor driving operation of stepless drive system, agricultural machinery operator need not participate in the technical training of specialty, only need simple exercise to grasp driving efficiency, thus accept by users, and achieve extraordinary effect, but after adding hydraulic system, improve complexity and the manufacture cost of operation system.In daily production and application process, cat will mount agricultural machinery and implement usually, and agricultural machinery and implement are when farm work, motor is generally in large throttle state, close to constant engine operating mode, speed of a motor vehicle change is little, the power of machinery is all larger with moment of torsion, and then adds cat energy ezpenditure.
Simultaneously, what cat vehicle in the market adopted steering linkages to operate jaw clutch and multi-disc brake usually turns to scheme, its implementation procedure is: when cat vehicle turn left to time, left side jaw clutch is separated driver's operation left steering pull bar and left side output shaft is braked, because crawler tractor vehicle left side transfer motion power interrupts and brake stopping the rotation, now under the driving of tractor right side power, facility realize turning to the left; In like manner reverse operating can realize right hand steering, but this steering equipment adopts separation and realizes in conjunction with jaw clutch and break, and it turns to precision low, and steering manipulation is poor.
Summary of the invention
Technical problem solved by the invention is to provide a kind of double clutch directly controlled type endless-track vehicle stepless speed variator, to solve the shortcoming in above-mentioned background technology.
Technical problem solved by the invention realizes by the following technical solutions:
Double clutch directly controlled type endless-track vehicle stepless speed variator, comprises double clutch, double-clutch power input part, pto＝power take-off deceleration part, Power output shaft portion, casing, stepless change part, pto＝power take-off gearshift part, external control attachment portion, differential planetary drive part, left track drive part and right side track drive part, wherein, double-clutch power input part, pto＝power take-off deceleration part, Power output shaft portion, stepless change part, pto＝power take-off gearshift part, differential control part, differential planetary drive part, left track drive part and right side track drive part are installed on casing, casing is arranged on engine power outgoing position place, and double clutch is connected with double-clutch power input part, double-clutch power input part respectively with pto＝power take-off deceleration part, stepless change part connects, power inputs through double-clutch power input part, a part exports through pto＝power take-off deceleration part, another part flows to stepless change part, pto＝power take-off deceleration part is connected with Power output shaft portion, for by transmission of power to external procedure part, stepless change part is connected with differential planetary drive part, and differential planetary drive part is connected with left track drive part, right side track drive part respectively, pto＝power take-off gearshift part is connected with double-clutch power input part, export for controlling low three gears in the high-altitude of switch dual clutch power input part to pto＝power take-off deceleration part, external control attachment portion is connected with differential planetary drive part, turns to for realizing straight control.
The concrete linkage structure of each part mentioned above is as follows:
In double-clutch power input part, forward gear power input shaft is installed in casing, end cap one is anchored on casing, forward gear drive bevel gear transition fit is installed on forward gear power input shaft, for giving follow-up relevant apparatus by the transmission of power of forward gear power input shaft, duplex power shift gear Spielpassung is set on forward gear power input shaft spline, forward gear power input shaft drives duplex power shift gear to rotate transferring power by spline, power sliding bearing interference fit is installed on forward gear power input shaft, duplex reduction gear gap is installed on power sliding bearing, gyration center around forward gear power input shaft rotates, forward gear clutch is installed on forward gear power input shaft, and by the spline transferring power on forward gear power input shaft, power input shaft one end of reversing gear is installed in forward gear power input shaft by needle bearing, the other end is installed in casing, and the back-up ring three power input shaft that reverses gear is provided with for axial limiting, the clutch that reverses gear is installed on and reverses gear on power input shaft, and the spline transferring power by reversing gear on power input shaft, in addition, sleeve two and drive bevel gear of reversing gear is set with in the one end of the power input shaft that reverses gear, sleeve two for axial clearance adjustment and spacing, and by the spline that reverses gear on power input shaft by transmission of power to drive bevel gear of reversing gear, drive it to rotate and by transmission of power to follow-up relevant device,
In pto＝power take-off deceleration part, power bearing shaft one end is installed in casing, and the other end docks with pto＝power take-off, and is provided with spline on power bearing shaft, and triple gear is set on power bearing shaft spline;
In Power output shaft portion, pto＝power take-off two ends are installed in casing, and at the dynamic output shaft spline of the outer installment of its one end, power output gear is sleeved on pto＝power take-off spline, and power output gear engages with the left side gear of duplex reduction gear, the right side gear of duplex reduction gear engages with the left side gear of triple gear;
In stepless change part, bevel gear back shaft two ends are installed in casing, and be set with driven wheel of differential in its one end, driven wheel of differential is rotated by the spline band dynamic bevel gear back shaft that bevel gear back shaft is arranged, back shaft sliding bearing and planet carrier sliding bearing respectively transition fit are installed on bevel gear back shaft, stepless speed-changing gear formula gear ring is set on back shaft sliding bearing and dallies, stepless speed-changing gear formula planet carrier is set on planet carrier sliding bearing and dallies, stepless change sun gear is set in bevel gear back shaft, and between stepless speed-changing gear formula gear ring and stepless speed-changing gear formula planet carrier, and stepless change planetary pinion is installed on stepless speed-changing gear formula planet carrier by Supporting Planetary Gears assembly circumference is uniform, the inner ring gear of stepless change planetary pinion and stepless speed-changing gear formula gear ring simultaneously, the outer ring gears meshing of stepless change sun gear, back shaft shield ring sleeve is loaded on bevel gear back shaft, and between back shaft sliding bearing and spring bearing, for adjusting the axial clearance of bevel gear back shaft, oil hydraulic motor is fastening to be installed on casing, and on the driving shaft of hydraulic motor gear suit oil hydraulic motor, the outer gear of stepless speed-changing gear formula planet carrier engages with hydraulic motor gear, jack shaft two ends are installed in casing, intermediate gear is set on jack shaft, and with the outer ring gears meshing of stepless speed-changing gear formula gear ring, jack shaft shield ring sleeve is loaded on jack shaft, simultaneously between intermediate bearing and intermediate gear, for adjusting the axial clearance of jack shaft, driven wheel of differential engages with forward gear drive bevel gear,
In pto＝power take-off gearshift part, declutch shift shaft is installed in casing, declutch shift shaft is provided with shift fork neutral gear lock ring, high-grade lock ring and low-grade lock ring, be provided with shift fork steel ball and shifting fork spring in shift fork and be sleeved on declutch shift shaft, its shift fork steel ball and shifting fork spring are for locking the position of shift fork, shift fork rotating shaft is installed in shift fork end cap, and its one end is inserted in fork slot, slide on declutch shift shaft for stirring shift fork, thus obtaining high-empty-low third gear switching, the other end is provided with the rotating shaft keyway for installing external control bar;
In external control attachment portion, connect end cap symmetrical and be arranged in casing about middle snap ring, hub splines is turned to be contained in steering bearing one and steering bearing two, steering bearing one and steering bearing two are arranged on about middle snap ring symmetry and are connected in end cap, turn to bevel gear to be set in and turn to splined shaft, and engage with the outside bevel gear of left sun gear and right sun gear simultaneously;
In differential planetary drive part, steering shaft is provided with the identical left planetary reduction gear control section of structure and right planetary reduction gear control section, and these two planetary reduction gear control sections are symmetrical about middle snap ring, steering shaft two ends are arranged in casing, middle snap ring is installed in steering shaft, and in the steering shaft of middle snap ring both sides respectively transition fit left sliding bearing one is installed, left sliding bearing two, right sliding bearing one and right sliding bearing two, left gear formula planet carrier is set on left sliding bearing two, right gear formula planet carrier is set on right sliding bearing two, left gear formula gear ring is set on left sliding bearing one and dallies, right gear formula gear ring is set on right sliding bearing one and dallies, steering shaft is set with roll left needle bearing two and right needle bearing two, the needle bearing three that rolls left is set in steering shaft, and between left gear formula gear ring and left sun gear, right needle bearing three is set in steering shaft, it is between right gear formula gear ring and right sun gear, in addition, left planetary pinion is distributed on left gear formula planet carrier by left planetary pinion supporting component circumference, left planetary pinion and the inner ring gear of left gear formula gear ring, the outer ring gears meshing of left sun gear simultaneously, right planetary pinion is distributed on right gear formula planet carrier by right planetary pinion supporting component circumference, simultaneously right planetary pinion and the inner ring gear of right gear formula gear ring, the outer ring gears meshing of right sun gear, diversion driving-gear is provided with on the right side of left bearing, diversion driving-gear by spline package in steering shaft, right back-up ring is provided with on the left of right bearing, right shield ring sleeve is loaded in steering shaft, the needle bearing one that rolls left is arranged between diversion driving-gear and left gear formula planet carrier, and right needle bearing one is arranged between right bearing and right gear formula planet carrier, left bearing and right bearing are set with in steering shaft, and are arranged in the end cap that is anchored on casing,
In left track drive part, left side end cap is installed on casing, and connecting sleeve one end, left side and Left hand bearing block overlap affixed, the other end and left side end cap affixed; Left driving output shaft one end is installed in casing, the other end is installed in Left hand bearing block cover, left side output shaft actuation gear is set in outside left driving output shaft one end, and it is spacing by left-hand axis snap ring, left side output shaft actuation gear by spline by transmission of power to left driving output shaft, also be provided with left hand sleeves at left driving output shaft, left hand sleeves is used for the axial limiting of left side output shaft actuation gear and the axial clearance adjustment of left driving output shaft simultaneously;
In right side track drive part, right side end cap is installed on casing, connecting sleeve one end, right side and right side bearing sleeve affixed, the other end and right side end cap affixed; Right side travels output shaft one end and is installed in casing, the other end is installed in the bearing sleeve of right side, right side output shaft actuation gear is set in right side and travels outside output shaft one end, and spacing by right-hand axis snap ring, transmission of power is travelled output shaft to right side by spline by right side output shaft actuation gear.
In the present invention, oil sealing one is installed in end cap one, for sealing the dynamic rotary of forward gear power input shaft.
In the present invention, Supporting Planetary Gears assembly comprises assembly line shaft, assembly back-up ring, component slippage bearing; Component slippage bearing transition fit is installed in stepless change planetary pinion, stepless change planetary pinion is loaded on assembly line shaft by component slippage bearing housing, assembly line shaft one end interference fit is installed in stepless speed-changing gear formula planet carrier, the other end interference fit is provided with assembly back-up ring, is used for limiting the planetary axial float of stepless change.
In the present invention, left planetary pinion supporting component comprises left assembly line shaft, left component slippage bearing, left assembly back-up ring, left component slippage bearing transition fit is installed in left planetary pinion, left planetary pinion is loaded on left assembly line shaft by left component slippage bearing housing, left assembly line shaft one end interference fit is installed in left sliding bearing two, the other end interference fit is provided with left assembly back-up ring, is used for limiting left planetary axial float; Right planetary pinion supporting component structure is consistent therewith.
In the present invention, the duplex reduction gear two ends be arranged on forward gear power input shaft are separately installed with the back-up ring one and back-up ring two that adjust for axial limiting and gap.
In the present invention, declutch shift shaft two ends are respectively arranged with seal ring one and seal ring two.
In the present invention, declutch shift shaft one end is provided with for entering line-locked snap ring two to declutch shift shaft.
In the present invention, be provided with shift fork seal ring in shift fork end cap, the dynamic rotary for shift fork rotating shaft seals.
In the present invention, be provided with Power output needle bearing in pto＝power take-off, one end of power bearing shaft is docked with pto＝power take-off by Power output needle bearing.
In the present invention, forward gear clutch and the clutch that reverses gear be staggered engage, disconnects, when forward gear clutch engage, and the clutch that reverses gear disconnection, when the clutch that reverses gear engages, the disconnection of forward gear clutch, when endless-track vehicle advances, shift handle is placed in forward gears neutral gear position, the clutch that reverses gear disconnects, forward gear clutch engages, a power part for forward gear clutch drives forward gears drive bevel gear to rotate through forward gears power input shaft, and the driven wheel of differential through engaging with forward gears drive bevel gear transmits driven rotary, another part passes to pto＝power take-off deceleration part through duplex power shift gear, pto＝power take-off deceleration part through Power output shaft portion by transmission of power to external procedure part, to drive external equipment work, bevel gear back shaft drives suit stepless change sun gear thereon to rotate by spline, stepless change sun gear drives stepless change planetary pinion to rotate, now stepless speed-changing gear formula gear ring is subject to the effect of external motion resistance, and oil hydraulic motor is in non-resistance non-self-lock-ing state under the control of external system, the planetary stepless speed-changing gear formula planet carrier that rotarily drives of now stepless change rotates, and drive hydraulic motor gear to dally around the driving shaft of oil hydraulic motor, transmission system no-output, and shift handle is when being placed in forward gears road location, the self-locking of external system hydraulic control motor, the stepless change planetary pinion rotated drives stepless speed-changing gear formula gear ring to rotate, and power is exported the follow-up relevant device of driving through intermediate gear, when the output speed of external system hydraulic control motor and when turning to, stepless speed-changing gear formula planet carrier is driven to rotate by hydraulic motor gear, stepless speed-changing gear formula planet carrier rotates forward the output speed that can increase stepless speed-changing gear formula gear ring, the counterrotating of stepless speed-changing gear formula planet carrier can reduce the output speed of stepless speed-changing gear formula gear ring, the rotational speed changing oil hydraulic motor can obtain the different output speed of stepless speed-changing gear formula gear ring, thus realize endless-track vehicle stepless change advance, when shift handle is placed in reverse gear neutral gear position, forward gear clutch disconnects, the clutch that reverses gear engages, power directly drives drive bevel gear of reversing gear to rotate through reverse gear power input shaft, and by transmission of power to stepless change part, identical when driving principle mode and advance, just direction is contrary, and now external procedure equipment quits work, during reversing, shift handle is placed in car backing position.In use, operator only needs controlled clutch can realize the change of gear, simple and convenient, and it is high that double clutch controls switching efficiency, is easy to realize computer integrating control, is conducive to endless-track vehicle and realizes wireless remote integrating control and remote driving.
In the present invention, power is passed to steering shaft through spline and drives it to rotate by diversion driving-gear, steering shaft drives left sun gear and right sun gear to rotate by spline respectively simultaneously, and then drive left planetary pinion and right planetary pinion to rotate, external control device locks left gear formula gear ring and right gear formula gear ring by turning to bevel gear simultaneously, now left gear formula planet carrier exports with identical rotating speed with right gear formula planet carrier, transmission of power is driven left track drive part by left gear formula planet carrier, transmission of power is driven right side track drive part by right gear formula planet carrier, when external driver device turns to bevel gear to rotate by turning to splined shaft to drive, left gear formula gear ring and right gear formula gear ring is driven to do the rotation of different direction, like this while slow down to Gear Planet Transmission part, another side accelerates Gear Planet Transmission part, speed is produced poor between left gear formula gear ring and right gear formula gear ring, thus realize turning to, turn to the clockwise and anticlockwise of bevel gear to realize the left and right turn of endless-track vehicle.
Beneficial effect: the present invention adopts the planet carrier of double clutch self-locking type hydraulic motor control planetary gear mechanism directly to drive and hydraulic stepless speed regulating to realize machinery, efficiently solve mechanical type and directly drive the problem that transmission is combined with hydraulic stepless formula, it is high that double clutch controls switching efficiency, be easy to realize computer integrating control, be conducive to endless-track vehicle and realize wireless remote integrating control and remote driving, differential drives and adopts bevel gear directly to control gear ring type structure simultaneously, effectively improve control accuracy and the response characteristic of control system, power failure-free in steering procedure, transmission efficiency is high, and stepless change is used for middle change of advancing, easy and simple to handle, be easy to drive, be convenient to cat and realize wheel steering, turn to precision high.
Accompanying drawing explanation
Fig. 1 is the structural representation of preferred embodiment of the present invention.
Fig. 2 is B-B place sectional view in Fig. 1.
Fig. 3 is D-D place sectional view in Fig. 1.
Fig. 4 is E-E place sectional view in Fig. 2.
Fig. 5 is double-clutch power input part and reverse gear clutch, forward gear clutch configuration schematic diagram in preferred embodiment of the present invention.
Fig. 6 is preferred embodiment medium power output shaft deceleration part of the present invention and double-clutch power input part, pto＝power take-off part-structure schematic diagram.
Fig. 7 is preferred embodiment medium power output shaft separation structure schematic diagram of the present invention.
Fig. 8 is stepless change part-structure schematic diagram in preferred embodiment of the present invention.
Fig. 9 is Supporting Planetary Gears modular construction schematic diagram in preferred embodiment of the present invention.
Figure 10 is differential planetary drive part structural representation in preferred embodiment of the present invention.
Figure 11 is left planetary pinion supporting component structural representation in preferred embodiment of the present invention.
Figure 12 is C-C place sectional view in Fig. 1.
Figure 13 is left track drive part structural representation in preferred embodiment of the present invention.
Figure 14 is right side track drive part structural representation in preferred embodiment of the present invention.
Embodiment
The technological means realized to make the present invention, creation characteristic, reaching object and effect is easy to understand, below in conjunction with concrete diagram, setting forth the present invention further.
See the double clutch directly controlled type endless-track vehicle stepless speed variator of Fig. 1 ~ Fig. 2, comprise double-clutch power input part X, pto＝power take-off deceleration part Y, Power output shaft portion Z, casing W, the clutch P that reverses gear, forward gear clutch Q, stepless change part L, pto＝power take-off gearshift part U, external control attachment portion R, differential planetary drive part S, left track drive part N1 and right side track drive part N2, wherein, double-clutch power input part X, pto＝power take-off deceleration part Y, Power output shaft portion Z, stepless change part L, pto＝power take-off gearshift part U, differential control part R, differential planetary drive part S, left track drive part N1 and right side track drive part N2 is installed on casing W, and casing W is arranged on engine power outgoing position place, reverse gear clutch P, forward gear clutch Q is connected with double-clutch power input part X, power inputs through double-clutch power input part X, a part exports through pto＝power take-off deceleration part Y, another part flows to stepless change part L, pto＝power take-off deceleration part Y through Power output shaft portion Z by transmission of power to external procedure part, stepless change part L by transmission of power to differential planetary drive part S, by differential planetary drive part S, power is exported driving left track drive part N1 and right side track drive part N2 respectively again, pto＝power take-off gearshift part U exports for controlling low three gears in the high-altitude of switch dual clutch power input part X to pto＝power take-off deceleration part Y, external control attachment portion R turns to for realizing straight control.
Shown in Fig. 3 ~ Fig. 7, double-clutch power input part X comprises the clutch P that reverses gear, forward gear clutch Q, oil sealing one X1, forward gear power input shaft X2, end cap one X3, bearing one X4, bolt one X5, the power input shaft X6 that reverses gear, duplex power shift gear X7, back-up ring one X8, duplex reduction gear X9, back-up ring two X10, bearing two X11, forward gear drive bevel gear X12, power sliding bearing X13, sleeve one X14, needle bearing X15, back-up ring three X16, bearing three X17, sleeve two X18, reverse gear drive bevel gear X19; Pto＝power take-off deceleration part Y comprises triple gear Y1, bearing four Y2, power bearing shaft Y3, end cap two Y4, bolt two Y5; Power output shaft portion Z comprises bolt three Z1, pto＝power take-off Z2, back-up ring four Z3, bearing five Z4, Power output needle bearing Z5, bearing six Z6, end cap three Z7, oil sealing two Z8, power output gear Z9; Pto＝power take-off gearshift part U comprises seal ring one U1, declutch shift shaft U2, shift fork U3, shift fork neutral gear lock ring U4, snap ring two U5, seal ring two U6, high-grade lock ring U7, shift fork steel ball U8, shifting fork spring U9, low gear lock ring U10, shift fork rotating shaft U11, shift fork end cap U12, snap ring three U13, rotating shaft keyway U14, shift fork seal ring U15, hexagon socket head cap screw one U16.
Forward gear power input shaft X2 is installed in casing W by bearing one X4 at two ends and bearing two X11, end cap one X3 is anchored on casing W by bolt one X5, oil sealing one X1 is installed in end cap one X3, dynamic rotary for forward gear power input shaft X2 seals, bearing two X11 and casing W is interference fit, forward gear drive bevel gear X12 transition fit is installed on forward gear power input shaft X2, for giving follow-up relevant apparatus by the transmission of power of forward gear power input shaft X2, duplex power shift gear X7 Spielpassung is set on forward gear power input shaft X2 spline, forward gear power input shaft X2 drives duplex power shift gear X7 to rotate transferring power by spline, power sliding bearing X13 interference fit is installed on forward gear power input shaft X2, duplex reduction gear X9 gap is installed on on power sliding bearing X13, gyration center around forward gear power input shaft X2 rotates, and the duplex reduction gear X9 two ends on forward gear power input shaft X2 are provided with back-up ring one X8 and back-up ring two X10 that adjust for axial limiting and gap, forward gear clutch Q is installed on forward gear power input shaft X2, and by the spline transferring power on forward gear power input shaft X2, power input shaft X6 one end of reversing gear is installed in forward gear power input shaft X2 by needle bearing X15, the other end is installed in W by bearing three X17, and the power input shaft X6 that reverses gear is provided with back-up ring three X16 for axial limiting, the clutch P that reverses gear is installed on and reverses gear on power input shaft X6, and the spline transferring power by reversing gear on power input shaft X6, in addition, reverse gear one end of power input shaft X6 is set with sleeve two X18 and the drive bevel gear X19 that reverses gear, sleeve two X18 be used for axial clearance adjustment and spacing, by the spline that reverses gear on power input shaft X6 by transmission of power to the drive bevel gear X19 that reverses gear, drive its rotate and by transmission of power give follow-up relevant device.
Bearing four Y2 is installed in casing W, and seal spacing by end cap two Y4, end cap two Y4 is anchored on casing W by bolt two Y5, pto＝power take-off Z2 one end is installed in casing W by bearing five Z4, and limits its axial float by back-up ring four Z3, and its other end is installed in casing W by bearing six Z6, and it is spacing by end cap three Z7, end cap three Z7 is anchored on casing W by bolt three Z1, and oil sealing two Z8 is installed in end cap three Z7, carries out dynamic rotary sealing to pto＝power take-off Z2.
Power output needle bearing Z5 is installed in pto＝power take-off Z2, power bearing shaft Y3 two ends are installed in Power output needle bearing Z5 and bearing four Y2 respectively, triple gear Y1 is set on the spline of power bearing shaft Y3, and at the dynamic output shaft spline of pto＝power take-off Z2 one end outer installment, power output gear Z9 is set on pto＝power take-off spline; Power output gear Z9 engages with the left side gear of duplex reduction gear X9, the right side gear of duplex reduction gear X9 engages with the left side gear of triple gear Y1, duplex power shift gear X7 moves from left to right on forward gear power input shaft X2, switches from high-empty-low third gear to realize gear; As shown in Figure 6, for low grade, its drive path being described: the right side gear of duplex power shift gear X7 engages with the right side gear of triple gear Y1 → left side gear of triple gear Y1 engages with the right side gear of duplex reduction gear X9 → and the left side gear of duplex reduction gear X9 engages with power output gear Z9, final power output gear Z9 by spline by transmission of power to pto＝power take-off Z2, drive it to rotate, this transmission process entirety is gearing down.
Declutch shift shaft U2 is installed in casing W, its two ends are sealed by seal ring one U1 and seal ring two U6, and locked by snap ring two U5, declutch shift shaft U2 is designed with shift fork neutral gear lock ring U4, high-grade lock ring U7 and low gear lock ring U10, shift fork U3 is set on declutch shift shaft U2, shift fork steel ball U8 and shifting fork spring U9 is designed with in shift fork U3, for locking the position of shift fork U3, shift fork rotating shaft U11 one end is inserted in fork slot, slide on declutch shift shaft U2 for stirring shift fork U3, thus obtain high-empty-low third gear switching, the other end of shift fork rotating shaft U11 is provided with rotating shaft keyway U14, for the installation of external control bar, shift fork rotating shaft U11 is installed in shift fork end cap U12, and lock spacing by snap ring three U13, shift fork end cap U12 is anchored on casing W by hexagon socket head cap screw one U16, shift fork seal ring U15 is provided with in shift fork end cap U12, dynamic rotary for shift fork rotating shaft U11 seals.
Shown in Fig. 8 ~ Fig. 9, stepless change part L comprises back shaft sliding bearing L1, back shaft back-up ring L2, spring bearing L3, clamping bolt one L4, stepless change planetary pinion L5, stepless speed-changing gear formula gear ring L6, intermediate bearing L7, clamping bolt two L8, jack shaft back-up ring L9, intermediate gear L10, jack shaft needle bearing L11, jack shaft L12, stepless speed-changing gear formula planet carrier L13, back shaft needle bearing L14, planet carrier sliding bearing L15, bevel gear back shaft L16, stepless change sun gear L17, Supporting Planetary Gears assembly L18, driven wheel of differential L19, motor snap ring L20, hydraulic motor gear L21, motor fastening screw trip bolt L22, oil hydraulic motor L23, back shaft end cap L24, jack shaft end cap L25, assembly line shaft L18-1, assembly back-up ring L18-2, component slippage bearing L18-3.
Bevel gear back shaft L16 two ends are installed in casing W respectively by spring bearing L3 and back shaft needle bearing L14, and spring bearing L3 holds by being fastened on the jack shaft end cap L25 position limiting sealed on casing W by clamping bolt one L4, bevel gear back shaft L16 one end is set with driven wheel of differential L19, driven wheel of differential L19 is rotated by spline band dynamic bevel gear back shaft L16, back shaft sliding bearing L1 and planet carrier sliding bearing L15 respectively transition fit is installed on bevel gear back shaft L16, stepless speed-changing gear formula gear ring L6 is set on back shaft sliding bearing L1 and dallies, stepless speed-changing gear formula planet carrier L13 is set on planet carrier sliding bearing L15 and dallies, bevel gear back shaft L16 is set with stepless change sun gear L17, stepless change sun gear L17 is between stepless speed-changing gear formula gear ring L6 and stepless speed-changing gear formula planet carrier L13, stepless change planetary pinion L5 is installed on stepless speed-changing gear formula planet carrier L13 by Supporting Planetary Gears assembly L18 circumference is uniform, and stepless change planetary pinion L5 engages with the inner ring gear of stepless speed-changing gear formula gear ring L6 and the outer ring gear of stepless change sun gear L17 simultaneously, bevel gear back shaft L16 is set with back shaft back-up ring L2, it is located between spring bearing L3 and back shaft sliding bearing L1, for adjusting the axial clearance of bevel gear back shaft L16, oil hydraulic motor L23 is installed on casing W by motor fastening screw trip bolt L22 is fastening, and hydraulic motor gear L21 is installed on the driving shaft of oil hydraulic motor L23, and spacing by motor snap ring L20, hydraulic motor gear L21 engages with the outer gear of stepless speed-changing gear formula planet carrier L13, jack shaft L12 two ends are installed in casing W respectively by intermediate bearing L7 and jack shaft needle bearing L11, and this end of intermediate bearing L7 is by being fastened on the back shaft end cap L24 position limiting sealed on casing W by clamping bolt two L8, intermediate gear L10 is set on jack shaft L12, and engage with the outer gear of stepless speed-changing gear formula gear ring L6, between intermediate bearing L7 and intermediate gear L10, jack shaft L12 is set with jack shaft back-up ring L9, jack shaft back-up ring L9 is for adjusting the axial clearance of jack shaft L12.
In Supporting Planetary Gears assembly L18, component slippage bearing L18-3 transition fit is installed in stepless change planetary pinion L5, stepless change planetary pinion L5 is set on assembly line shaft L18-1 by component slippage bearing L18-3, assembly line shaft L18-1 one end interference fit is installed in stepless speed-changing gear formula planet carrier L13, the other end interference fit is provided with assembly back-up ring L18-2, is used for limiting the axial float of stepless change planetary pinion L5.
In the present embodiment, when forward gear clutch Q engages, the clutch P that reverses gear disconnects, when the clutch P that reverses gear engages, forward gear clutch Q disconnects, be explained for forward gear clutch Q engagement below: when endless-track vehicle advances, shift handle is placed in forward gears neutral gear position, reverse clutch P disconnects, forward gear clutch Q engages, the power of motor inputs through forward gear clutch Q, and a power part of forward gear clutch Q drives forward gear drive bevel gear X12 to rotate through forward gear power input shaft X2, and the driven wheel of differential L19 through engaging with forward gear drive bevel gear X12 transmits driven rotary, another part passes to pto＝power take-off deceleration part Y and Power output shaft portion Z through duplex power shift gear X7 and exports, drive external equipment works, bevel gear back shaft L16 drives suit stepless change sun gear L17 thereon to rotate by spline, stepless change sun gear L17 drives stepless change planetary pinion L5 to rotate, now stepless speed-changing gear formula gear ring L6 is subject to the effect of external motion resistance, and L23 is in non-resistance non-self-lock-ing state under the control of external system, now the stepless speed-changing gear formula that the rotarily drives planet carrier L13 of stepless change planetary pinion L5 rotates, and drive hydraulic motor gear L21 to dally around the driving shaft of oil hydraulic motor L23, transmission system no-output, when shift handle is placed in forward gears road location, during the L23 self-locking of external system hydraulic control motor, the stepless change planetary pinion L5 rotated drives stepless speed-changing gear formula gear ring L6 to rotate, and power is exported the follow-up relevant device of driving through intermediate gear L10, when the output speed of external system hydraulic control motor L23 and when turning to, stepless speed-changing gear formula planet carrier L13 is driven to rotate by hydraulic motor gear L21, stepless speed-changing gear formula planet carrier L13 rotates forward the output speed that can increase stepless speed-changing gear formula gear ring L6, stepless speed-changing gear formula planet carrier L13 counterrotating can reduce the output speed of stepless speed-changing gear formula gear ring L6, the rotational speed changing oil hydraulic motor L23 can obtain the different output speed of stepless speed-changing gear formula gear ring L6, thus realize endless-track vehicle stepless change advance, when shift handle is placed in reverse gear neutral gear position, forward gear clutch Q disconnects, the clutch P that reverses gear engages, the power of motor directly drives the drive bevel gear X19 that reverses gear to rotate through the power input shaft X6 that reverses gear, and by transmission of power to stepless change part L, identical when driving principle mode and advance, just direction is contrary, now external procedure equipment quits work, and hydraulic system is locking not, transmission system no-output, during reversing, shift handle is placed in car backing position, now hydraulic system locking, realizes endless-track vehicle reversing, the facility drawn because of all cats are moveed backward all without the need to work, therefore reverse gear and pto＝power take-off have nothing to do.
Shown in Figure 10 ~ Figure 12, differential planetary drive part S comprises left lateral star transmission control part and divides S1 and right lateral star transmission control part to divide S2, specific as follows: left lateral star transmission control part divides S1 to comprise left planetary pinion supporting component S1-1, left sliding bearing one S1-2, left gear formula planet carrier S1-3, left sliding bearing two S1-4, needle bearing one S1-5 that rolls left, needle bearing two S1-7 that rolls left, left sun gear S1-8, left planetary pinion S1-9, the needle bearing Three S's 1-10 that rolls left, left gear formula gear ring S1-11; Right lateral star transmission control part divides S2 to comprise right planetary pinion supporting component S2-1, right sliding bearing one S2-2, right gear formula planet carrier S2-3, right sliding bearing two S2-4, right needle bearing one S2-5, right needle bearing two S2-7, right sun gear S2-8, right planetary pinion S2-9, right needle bearing Three S's 2-10, right gear formula gear ring S2-11; Steering shaft S3, middle snap ring S4, diversion driving-gear S5, right end cap S6, right clamping bolt S7, right bearing S8, right back-up ring S9, left end cap S10, left clamping bolt S11, left bearing S12; Left planetary pinion supporting component S1-1 comprises left assembly line shaft S1-1-1, left component slippage bearing S1-1-2, left assembly back-up ring S1-1-3; And right planetary pinion supporting component S2-1 is consistent with left planetary pinion supporting component S1-1 structure; External control attachment portion R comprises and connects end cap R1, turn to splined shaft R2, steering bearing one R3, turn to bevel gear R4, steering bearing two R5, end cap clamping bolt R6.
Steering shaft S3 two ends are installed in casing W respectively by left bearing S12 and right bearing S8, and pass through by the fastening left end cap S10 of left clamping bolt S11 and seal spacing by the right end cap S6 that right clamping bolt S7 is fastening, middle snap ring S4 is installed on steering shaft S3, and left lateral star transmission control part divides S1 and right lateral star transmission control part to divide S2 to be installed on steering shaft S3 about middle snap ring S4 symmetry.
Left sliding bearing two S1-4 and left sliding bearing one S1-2 respectively transition fit is installed on steering shaft S3, left gear formula planet carrier S1-3 is set on left sliding bearing two S1-4 and dallies, left gear formula gear ring S1-11 is set on left sliding bearing one S1-2 and dallies, left sun gear S1-8 by spline package on steering shaft S3, between left gear formula planet carrier S1-3 and left sun gear S1-8, steering shaft S3 is set with needle bearing two S1-7 that rolls left, between left gear formula gear ring S1-11 and left sun gear S1-8, steering shaft S3 is set with the needle bearing Three S's 1-10 that rolls left, left planetary pinion S1-9 is installed on left gear formula planet carrier S1-3 by left planetary pinion supporting component S1-1 circumference is uniform, and left planetary pinion S1-9 engages with the inner ring gear of left gear formula gear ring S1-11, the outer ring gear of left sun gear S1-8 simultaneously, diversion driving-gear S5 on steering shaft S3, is positioned on the right side of left bearing S12 by spline package, between diversion driving-gear S5 and left gear formula planet carrier S1-3, be provided with needle bearing one S1-5 that rolls left, in like manner, right sliding bearing two S2-4 and right sliding bearing one S2-2 respectively transition fit is installed on steering shaft S3, right gear formula planet carrier S2-3 is set on right sliding bearing two S2-4 and dallies, right gear formula gear ring S2-11 is set on right sliding bearing one S2-2 and dallies, right sun gear S2-8 by spline package on steering shaft S3, between right gear formula planet carrier S2-3 and right sun gear S2-8, steering shaft S3 is set with right needle bearing two S2-7, between right gear formula gear ring S2-11 and right sun gear S2-8, steering shaft S3 is set with right needle bearing Three S's 2-10, right planetary pinion S2-9 is installed on right gear formula planet carrier S2-3 by right planetary pinion supporting component S2-1 circumference is uniform, and the inner ring gear of right planetary pinion S2-9 and right gear formula gear ring S2-11, the outer ring gear of right sun gear S2-8 engages simultaneously, on the left of right bearing S8, right back-up ring S9 is set on steering shaft S3, right needle bearing one S2-5 is provided with between right bearing S8 and right gear formula planet carrier S2-3.
In left planetary pinion supporting component S1-1, left component slippage bearing S1-1-2 transition fit is installed in left planetary pinion S1-9, left planetary pinion S1-9 is set on left assembly line shaft S1-1-1 by left component slippage bearing S1-1-2, left assembly line shaft S1-1-1 one end interference fit is installed in left sliding bearing two S1-4, the other end interference fit is provided with left assembly back-up ring S1-1-3, is used for limiting the axial float of left planetary pinion S1-9.
Connecting end cap R1 is installed on casing W about middle snap ring S4 symmetry by end cap clamping bolt R6 is fastening, splined shaft R2 is turned to be set in steering bearing one R3 and steering bearing two R5, steering bearing one R3 and steering bearing two R5 are installed on about middle snap ring S4 symmetry and are connected in end cap R1, turn to bevel gear R4 to be set in and turn on splined shaft R2, and by spline transferring power, turn to bevel gear R4 to engage with the outside bevel gear of left sun gear S1-8 and right sun gear S2-8 simultaneously.
Power is passed to steering shaft S3 through spline and drives it to rotate by diversion driving-gear S5, steering shaft S3 drives left sun gear S1-8 and right sun gear S2-8 to rotate by spline respectively simultaneously, and then left sun gear S1-8 drives left planetary pinion S1-9 to rotate, right sun gear S2-8 drives right planetary pinion S2-9 to rotate, external control device has auto-lock function by turning to bevel gear R4 to carry out locking to left gear formula gear ring S1-11 and right gear formula gear ring S2-11 simultaneously when the active force that the active force that left gear formula gear ring S1-11 is subject to left planetary pinion S1-9 and right gear formula gear ring S2-11 are subject to right planetary pinion S2-9 is identical, now left gear formula planet carrier S1-3 exports with identical rotating speed with right gear formula planet carrier S2-3, transmission of power is driven left track drive part N1 by left gear formula planet carrier S1-3, transmission of power is driven right side track drive part N2 by right gear formula planet carrier S2-3, when external driver device turns to bevel gear R4 to rotate by turning to splined shaft R2 to drive, left gear formula gear ring S1-11 and right gear formula gear ring S2-11 is driven to do the rotation of different direction, like this while slow down to Gear Planet Transmission part, another side accelerates Gear Planet Transmission part, speed is produced poor between left gear formula planet carrier S1-3 and right gear formula planet carrier S2-3, thus realize turning to, turn to the clockwise and anticlockwise of bevel gear R4 to realize left and right turn.
Shown in Figure 13, left track drive part N1 comprises left side bearing one N1-1, left driving output shaft N1-2, left-hand axis snap ring N1-3, left side output shaft actuation gear N1-4, left side end cap N1-5, left side connecting sleeve N1-6, Left hand bearing block cover N1-7, left hole snap ring N1-8, left side bearing two N1-9, left side clamping bolt N1-10 and left hand sleeves N1-11, wherein, left side end cap N1-5 is installed on casing W by left side clamping bolt N1-10, connecting sleeve N1-6 two ends, left side overlap N1-7 with Left hand bearing block respectively and left side end cap N1-5 is affixed, left side bearing one N1-1 and left side bearing two N1-9 is set with in left driving output shaft N1-2 two ends, left side bearing one N1-1 is installed in casing W, left side bearing two N1-9 is installed in Left hand bearing block cover N1-7, and it is spacing by left hole snap ring N1-8, left side output shaft actuation gear N1-4 is set in left driving output shaft N1-2 one end, and it is spacing by left-hand axis snap ring N1-3, left side output shaft actuation gear N1-4 by spline by transmission of power to left driving output shaft N1-2, between left side bearing one N1-1 and left side output shaft actuation gear N1-4, left driving output shaft N1-2 is set with left hand sleeves N1-11, for the axial limiting of left side output shaft actuation gear N1-4 and the axial clearance adjustment of left driving output shaft N1-2.
Shown in Figure 14, right side track drive part N2 comprises right side bearing one N2-1, right side travels output shaft N2-2, right-hand axis snap ring N2-3, right side output shaft actuation gear N2-4, right side end cap N2-5, right side connecting sleeve N2-6, right side bearing sleeve N2-7, right ports snap ring N2-8, right side bearing two N2-9 and right side clamping bolt N2-10, wherein, right side end cap N2-5 is installed on casing W by right side clamping bolt N2-10, connecting sleeve N2-6 two ends, right side are affixed with right side bearing sleeve N2-7 and right side end cap N2-5 respectively, right side bearing one N2-1 and right side bearing two N2-9 is set with the two ends travelling output shaft N2-2 in right side, right side bearing one N2-1 is installed in casing W, right side bearing two N2-9 is installed in the bearing sleeve N2-7 of right side, and it is spacing by right ports snap ring N2-8, right side output shaft actuation gear N2-4 is set in right side and travels output shaft N2-2 one end, and it is spacing by right-hand axis snap ring N2-3, transmission of power is travelled output shaft N2-2 to right side by spline by right side output shaft actuation gear N2-4.
More than show and describe basic principle of the present invention and major character and advantage of the present invention.The technician of the industry should understand; the present invention is not restricted to the described embodiments; what describe in above-described embodiment and specification just illustrates principle of the present invention; without departing from the spirit and scope of the present invention; the present invention also has various changes and modifications, and these changes and improvements all fall in the claimed scope of the invention.Application claims protection domain is defined by appending claims and equivalent thereof.
Claims (10)
1. double clutch directly controlled type endless-track vehicle stepless speed variator, comprises double clutch, double-clutch power input part, pto＝power take-off deceleration part, Power output shaft portion, casing, stepless change part, pto＝power take-off gearshift part, external control attachment portion, differential planetary drive part, left track drive part and right side track drive part; It is characterized in that, double-clutch power input part, pto＝power take-off deceleration part, Power output shaft portion, stepless change part, pto＝power take-off gearshift part, differential control part, differential planetary drive part, left track drive part and right side track drive part are installed on casing, casing is arranged on engine power outgoing position place, and double clutch is connected with double-clutch power input part, double-clutch power input part is connected with pto＝power take-off deceleration part, stepless change part respectively; Pto＝power take-off deceleration part is connected with Power output shaft portion, stepless change part is connected with differential planetary drive part, and differential planetary drive part is connected with left track drive part, right side track drive part respectively, pto＝power take-off gearshift part is connected with double-clutch power input part, and external control attachment portion is connected with differential planetary drive part.
2. double clutch directly controlled type endless-track vehicle stepless speed variator according to claim 1, it is characterized in that, the concrete linkage structure of each part mentioned above is as follows:
In double-clutch power input part, forward gear power input shaft is installed in casing, end cap one is anchored on casing, forward gear drive bevel gear transition fit is installed on forward gear power input shaft, duplex power shift gear Spielpassung is set on forward gear power input shaft spline, power sliding bearing interference fit is installed on forward gear power input shaft, duplex reduction gear gap is installed on power sliding bearing, gyration center around forward gear power input shaft rotates, and forward gear clutch is installed on forward gear power input shaft; Power input shaft one end of reversing gear is installed in forward gear power input shaft by needle bearing, and the other end is installed in casing, and the power input shaft that reverses gear is provided with the back-up ring for axial limiting, and the clutch that reverses gear is installed on and reverses gear on power input shaft; In addition, sleeve is set with in the one end of the power input shaft that reverses gear and drive bevel gear of reversing gear;
In pto＝power take-off deceleration part, power bearing shaft one end is installed in casing, and the other end docks with pto＝power take-off, and is provided with spline on power bearing shaft, and triple gear is set on power bearing shaft spline;
In Power output shaft portion, pto＝power take-off two ends are installed in casing, and at the dynamic output shaft spline of the outer installment of its one end, power output gear is sleeved on pto＝power take-off spline, and power output gear engages with the left side gear of duplex reduction gear, the right side gear of duplex reduction gear engages with the left side gear of triple gear;
In stepless change part, bevel gear back shaft two ends are installed in casing, and be set with driven wheel of differential in its one end, back shaft sliding bearing and planet carrier sliding bearing respectively transition fit are installed on bevel gear back shaft, stepless speed-changing gear formula gear ring is set on back shaft sliding bearing and dallies, stepless speed-changing gear formula planet carrier is set on planet carrier sliding bearing and dallies, stepless change sun gear is set in bevel gear back shaft, and between stepless speed-changing gear formula gear ring and stepless speed-changing gear formula planet carrier, and stepless change planetary pinion is installed on stepless speed-changing gear formula planet carrier by Supporting Planetary Gears assembly circumference is uniform, the inner ring gear of stepless change planetary pinion and stepless speed-changing gear formula gear ring simultaneously, the outer ring gears meshing of stepless change sun gear, back shaft shield ring sleeve is loaded on bevel gear back shaft, oil hydraulic motor is fastening to be installed on casing, and on the driving shaft of hydraulic motor gear suit oil hydraulic motor, the outer gear of stepless speed-changing gear formula planet carrier engages with hydraulic motor gear, jack shaft two ends are installed in casing, and intermediate gear is set on jack shaft, and with the outer ring gears meshing of stepless speed-changing gear formula gear ring, jack shaft shield ring sleeve is loaded on jack shaft, and driven wheel of differential engages with forward gear drive bevel gear,
In pto＝power take-off gearshift part, declutch shift shaft is installed in casing, declutch shift shaft is provided with shift fork neutral gear lock ring, high-grade lock ring and low-grade lock ring, be provided with shift fork steel ball and shifting fork spring in shift fork and be sleeved on declutch shift shaft, shift fork rotating shaft is installed in shift fork end cap, and its one end is inserted in fork slot, the other end is provided with the rotating shaft keyway for installing external control bar;
In external control attachment portion, connect end cap symmetrical and be arranged in casing about middle snap ring, hub splines is turned to be contained in steering bearing one and steering bearing two, steering bearing one and steering bearing two are arranged on about middle snap ring symmetry and are connected in end cap, turn to bevel gear to be set in and turn to splined shaft, and engage with the outside bevel gear of left sun gear and right sun gear simultaneously;
In differential planetary drive part, steering shaft is provided with the identical left planetary reduction gear control section of structure and right planetary reduction gear control section, and these two planetary reduction gear control sections are symmetrical about middle snap ring, steering shaft two ends are arranged in casing, middle snap ring is installed in steering shaft, and in the steering shaft of middle snap ring both sides respectively transition fit left sliding bearing one is installed, left sliding bearing two, right sliding bearing one and right sliding bearing two, left gear formula planet carrier is set on left sliding bearing two, right gear formula planet carrier is set on right sliding bearing two, left gear formula gear ring is set on left sliding bearing one and dallies, right gear formula gear ring is set on right sliding bearing one and dallies, steering shaft is set with roll left needle bearing two and right needle bearing two, the needle bearing three that rolls left is set in steering shaft, and between left gear formula gear ring and left sun gear, right needle bearing three is set in steering shaft, it is between right gear formula gear ring and right sun gear, in addition, left planetary pinion is distributed on left gear formula planet carrier by left planetary pinion supporting component circumference, left planetary pinion and the inner ring gear of left gear formula gear ring, the outer ring gears meshing of left sun gear simultaneously, right planetary pinion is distributed on right gear formula planet carrier by right planetary pinion supporting component circumference, simultaneously right planetary pinion and the inner ring gear of right gear formula gear ring, the outer ring gears meshing of right sun gear, diversion driving-gear is provided with on the right side of left bearing, diversion driving-gear by spline package in steering shaft, right back-up ring is provided with on the left of right bearing, right shield ring sleeve is loaded in steering shaft, the needle bearing one that rolls left is arranged between diversion driving-gear and left gear formula planet carrier, and right needle bearing one is arranged between right bearing and right gear formula planet carrier, left bearing and right bearing are set with in steering shaft, and are arranged in the end cap that is anchored on casing,
In left track drive part, left side end cap is installed on casing, and connecting sleeve one end, left side and Left hand bearing block overlap affixed, the other end and left side end cap affixed; Left driving output shaft one end is installed in casing, the other end is installed in Left hand bearing block cover, left side output shaft actuation gear is set in outside left driving output shaft one end, and spacing by left-hand axis snap ring, is also provided with left hand sleeves at left driving output shaft simultaneously;
In right side track drive part, right side end cap is installed on casing, connecting sleeve one end, right side and right side bearing sleeve affixed, the other end and right side end cap affixed; Right side travels output shaft one end and is installed in casing, and the other end is installed in the bearing sleeve of right side, and right side output shaft actuation gear is set in right side and travels outside output shaft one end, and spacing by right-hand axis snap ring.
3. double clutch directly controlled type endless-track vehicle stepless speed variator according to claim 2, it is characterized in that, Supporting Planetary Gears assembly comprises assembly line shaft, assembly back-up ring, component slippage bearing; Component slippage bearing transition fit is installed in stepless change planetary pinion, stepless change planetary pinion is loaded on assembly line shaft by component slippage bearing housing, assembly line shaft one end interference fit is installed in stepless speed-changing gear formula planet carrier, and the other end interference fit is provided with assembly back-up ring.
4. double clutch directly controlled type endless-track vehicle stepless speed variator according to claim 2, it is characterized in that, left planetary pinion supporting component comprises left assembly line shaft, left component slippage bearing, left assembly back-up ring, left component slippage bearing transition fit is installed in left planetary pinion, left planetary pinion is loaded on left assembly line shaft by left component slippage bearing housing, left assembly line shaft one end interference fit is installed in left sliding bearing two, and the other end interference fit is provided with left assembly back-up ring.
5. double clutch directly controlled type endless-track vehicle stepless speed variator according to claim 2, is characterized in that, the duplex reduction gear two ends be arranged on forward gear power input shaft are separately installed with the back-up ring one and back-up ring two that adjust for axial limiting and gap.
6. double clutch directly controlled type endless-track vehicle stepless speed variator according to claim 2, it is characterized in that, declutch shift shaft one end is provided with for entering line-locked snap ring to declutch shift shaft.
7. double clutch directly controlled type endless-track vehicle stepless speed variator according to claim 2, it is characterized in that, declutch shift shaft two ends are respectively arranged with seal ring one and seal ring two.
8. double clutch directly controlled type endless-track vehicle stepless speed variator according to claim 2, is characterized in that, be provided with Power output needle bearing in pto＝power take-off, and one end of power bearing shaft is docked with pto＝power take-off by Power output needle bearing.
9. the double clutch directly controlled type endless-track vehicle stepless speed variator according to any one of claim 1 ~ 8, it is characterized in that, when endless-track vehicle advances, shift handle is placed in forward gears neutral gear position, the clutch that reverses gear disconnects, forward gear clutch engages, a power part for forward gear clutch drives forward gears drive bevel gear to rotate through forward gears power input shaft, and the driven wheel of differential through engaging with forward gears drive bevel gear transmits driven rotary, another part passes to pto＝power take-off deceleration part through duplex power shift gear, pto＝power take-off deceleration part through Power output shaft portion by transmission of power to external procedure some work, bevel gear back shaft drives suit stepless change sun gear thereon to rotate by spline, stepless change sun gear drives stepless change planetary pinion to rotate, now stepless speed-changing gear formula gear ring is subject to the effect of external motion resistance, and oil hydraulic motor is in non-resistance non-self-lock-ing state under the control of external system, the planetary stepless speed-changing gear formula planet carrier that rotarily drives of now stepless change rotates, and drive hydraulic motor gear to dally around the driving shaft of oil hydraulic motor, transmission system no-output, and shift handle is when being placed in forward gears road location, the self-locking of external system hydraulic control motor, the stepless change planetary pinion rotated drives stepless speed-changing gear formula gear ring to rotate, and power is exported driving through intermediate gear, when the output speed of external system hydraulic control motor and when turning to, stepless speed-changing gear formula planet carrier is driven to rotate by hydraulic motor gear, stepless speed-changing gear formula planet carrier rotates forward the output speed increasing stepless speed-changing gear formula gear ring, the counterrotating of stepless speed-changing gear formula planet carrier reduces the output speed of stepless speed-changing gear formula gear ring, change the rotational speed of oil hydraulic motor to obtain the different output speed of stepless speed-changing gear formula gear ring, thus realize endless-track vehicle stepless change advance, when shift handle is placed in reverse gear neutral gear position, forward gear clutch disconnects, the clutch that reverses gear engages, power directly drives drive bevel gear of reversing gear to rotate through reverse gear power input shaft, and by transmission of power to stepless change part, identical when driving principle mode and advance, just direction is contrary, and now external procedure equipment quits work, during reversing, shift handle is placed in car backing position.
10. the double clutch directly controlled type endless-track vehicle stepless speed variator according to any one of claim 1 ~ 8, it is characterized in that, power is passed to steering shaft through spline and drives it to rotate by diversion driving-gear, steering shaft drives left sun gear and right sun gear to rotate by spline respectively simultaneously, and then drive left planetary pinion and right planetary pinion to rotate, external control device locks left gear formula gear ring and right gear formula gear ring by turning to bevel gear simultaneously, now left gear formula planet carrier exports with identical rotating speed with right gear formula planet carrier, transmission of power is driven left track drive part by left gear formula planet carrier, transmission of power is driven right side track drive part by right gear formula planet carrier, when external driver device turning to bevel gear to rotate by turning to splined shaft to drive, driving left gear formula gear ring and right gear formula gear ring to do the rotation of different direction, between left gear formula gear ring and right gear formula gear ring, producing speed poor, thus realizing turning to.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410360000.2A CN104141750B (en) | 2014-07-25 | 2014-07-25 | Double-clutch directly controlled stepless speed regulator for tracked vehicle |
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| CN201410360000.2A CN104141750B (en) | 2014-07-25 | 2014-07-25 | Double-clutch directly controlled stepless speed regulator for tracked vehicle |
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| CN106641240B (en) * | 2017-02-15 | 2017-11-28 | 湖南农业大学 | A kind of gearshift and control method of integrated clutch manipulation function |
| CN106763750B (en) * | 2017-02-15 | 2017-11-28 | 湖南农业大学 | A kind of device and its control method with remote control gearshift function |
| CN109340274A (en) * | 2018-11-29 | 2019-02-15 | 株洲齿轮有限责任公司 | Vehicle drive system and its clutch box assembly |
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| CN204025567U (en) * | 2014-07-25 | 2014-12-17 | 湖南农业大学 | Double clutch directly controlled type endless-track vehicle buncher |
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| CN2039369U (en) * | 1988-08-24 | 1989-06-14 | 魏景丰 | Hydraulically-controlled differential planet gear |
| JP3363325B2 (en) * | 1996-10-18 | 2003-01-08 | ヤンマー農機株式会社 | Steering device for traveling work equipment |
| KR100569136B1 (en) * | 2003-11-27 | 2006-04-07 | 현대자동차주식회사 | Double clutch transmission |
| JP4746279B2 (en) * | 2004-03-16 | 2011-08-10 | ヤンマー株式会社 | Work vehicle transmission |
| CN100516589C (en) * | 2007-08-16 | 2009-07-22 | 中国一拖集团有限公司 | Vertically arranged transmission device of minitype wheeled tractor |
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| CN204025567U (en) * | 2014-07-25 | 2014-12-17 | 湖南农业大学 | Double clutch directly controlled type endless-track vehicle buncher |
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