CN204061764U - Double-clutch type endless-track vehicle hydraulic stepless speed variator - Google Patents
Double-clutch type endless-track vehicle hydraulic stepless speed variator Download PDFInfo
- Publication number
- CN204061764U CN204061764U CN201420415298.8U CN201420415298U CN204061764U CN 204061764 U CN204061764 U CN 204061764U CN 201420415298 U CN201420415298 U CN 201420415298U CN 204061764 U CN204061764 U CN 204061764U
- Authority
- CN
- China
- Prior art keywords
- gear
- shaft
- ring
- double
- clutch
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn - After Issue
Links
Landscapes
- Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
- Retarders (AREA)
Abstract
Double-clutch type endless-track vehicle hydraulic stepless speed variator, wherein, double clutch is connected with double-clutch power input part, power is delivered to first order kinetics transmitting portions by double-clutch power input part, first order kinetics transmitting portions through second motive force transmitting portions by transmission of power to differential planetary drive stepless speed changing part, by differential planetary drive stepless speed changing part, power is exported driving transition gearing down part respectively again, finally pass to left track drive part and right side track drive part; And differential planetary drive stepless speed changing part adopts two self-locking type hydraulic motor control planetary gear mechanism, switching efficiency is high, be easy to realize computer integrating control, be conducive to track-laying vehicle and realize wireless remote integrating control and remote driving, and the velocity ratio of epicyclic transmission mechanism is large, control endless-track vehicle by oil hydraulic motor to advance, move backward or turn to, reduce component number; Be convenient to realize efficient small radius steering, steering operation mechanism is easy simultaneously.
Description
Technical field
The utility model relates to farm machinery transmission technology field, particularly relates to a kind of double-clutch type endless-track vehicle hydraulic stepless speed variator.
Background technique
Track-laying vehicle transmission system comprises clutch, 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, cat adopts Purely mechanical power transmission system transferring power usually, 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 can realize right hand steering, but this steering equipment adopts separation and realizes in conjunction with jaw clutch and break, it turns to precision low, and steering manipulation is poor, is unfavorable for that endless-track vehicle realizes wireless remote integrating control and remote driving; And in use because differential planetary drive part adopts indirection type to control, although reduce the structural manufacturing process difficulty of differential planetary drive part, also reduce the response characteristic of control accuracy and system.
Model utility content
The technical problem that the utility model solves is to provide a kind of double-clutch type endless-track vehicle hydraulic stepless speed variator, to solve the shortcoming in above-mentioned background technology.
The technical problem that the utility model solves realizes by the following technical solutions:
Double-clutch type endless-track vehicle hydraulic stepless speed variator, comprises double clutch, double-clutch power input part, casing, first order kinetics transmitting portions, second motive force transmitting portions, differential planetary drive stepless speed changing part, transition gearing down part, left track drive part and right side track drive part, wherein, double-clutch power input part, first order kinetics transmitting portions, second motive force transmitting portions, differential planetary drive stepless speed changing part, transition gearing down 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 first order kinetics transmitting portions, first order kinetics transmitting portions is connected with differential planetary drive stepless speed changing part by second motive force transmitting portions, differential planetary drive stepless speed changing part is connected with transition gearing down part, transition gearing down part is connected with left track drive part and right side track drive part respectively, power is delivered to first order kinetics transmitting portions through power input portion, first order kinetics transmitting portions through second motive force transmitting portions by transmission of power to differential planetary drive stepless speed changing part, outputed power by differential planetary drive stepless speed changing part again and drive transition gearing down part, finally pass to left track drive part and right side track drive part.
The concrete linkage structure of each part mentioned above is as follows:
In double-clutch power input part, forward gear power input shaft is arranged in casing, its one end is provided with forward gear drive bevel gear, and the other end is provided with forward gear clutch, and forward gear power input shaft drives forward gear drive bevel gear to rotate transferring power by spline; Power input shaft one end of reversing gear is installed in forward gear power input shaft by needle bearing one, the other end is installed in casing, and the back-up ring one 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, power input shaft one end of reversing gear is set with sleeve one and reverses gear drive bevel gear, sleeve one 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 first order kinetics transmitting portions, one-level driving shaft is installed in casing, and in the outer cover of one-level driving shaft one end, driven wheel of differential is housed, and driven wheel of differential drives one-level driving shaft to rotate by spline, and one-level driving gear is sleeved on one-level driving shaft; One-level driven shaft is installed in casing, and one-level driven gear is installed on one-level driven shaft, and one-level driven gear engages transferring power to follow-up relevant device with one-level driving gear simultaneously;
In second motive force transmitting portions, secondary drive shaft is installed in casing, secondary driven gear and secondary driving gear are set in secondary drive shaft, secondary driving gear side is provided with the snap ring one for axial limiting, and secondary driven gear engages with one-level driven gear, for driving secondary drive shaft to rotate by spline the power of one-level driven gear, secondary drive shaft drives secondary driving gear to rotate by spline, and gives follow-up relevant apparatus by transmission of power;
Differential planetary drive stepless speed changing part comprises four sliding bearings, sliding bearing three respectively, sliding bearing four, sliding bearing five and sliding bearing six, differential main shaft is provided with the identical left differential planetary drive part of structure and right differential planetary drive part, and these two planetary reduction gear control sections are symmetrical about differential driving gear, differential driving gear is set in differential main shaft, its both sides spacer shell is equipped with sliding bearing three and sliding bearing five, left gear formula gear ring is sleeved on slip idle running on sliding bearing three, right gear formula gear ring is sleeved on slip idle running on sliding bearing five, left sun gear and right sun gear are set on the spline of differential main shaft outer installment, and sliding bearing four and sliding bearing six respectively spacer shell be loaded on differential main shaft, left gear formula planet carrier is set in slip idle running on sliding bearing four, right gear formula planet carrier is set in slip idle running on sliding bearing six, left lateral star-wheel sliding bearing interference is in left planetary pinion, left planetary pinion is arranged between left gear formula gear ring and left sun gear, and be set in slip rotation on left lateral star-wheel line shaft by left lateral star-wheel sliding bearing, right lateral star-wheel sliding bearing interference is in right planetary pinion, right planetary pinion is arranged between right gear formula gear ring and right sun gear, and be set in slip rotation on right lateral star-wheel line shaft by right lateral star-wheel sliding bearing, one end interference of left lateral star-wheel line shaft is installed in left gear formula planet carrier, and the other end interference has left lateral star-wheel back-up ring, and one end interference of right lateral star-wheel line shaft is installed in right gear formula planet carrier, and the other end interference has right lateral star-wheel back-up ring, left planetary pinion is uniform along left gear formula planet carrier circumference, engage with the internal gear of left gear formula gear ring and the external gear of left sun gear simultaneously, right planetary pinion is uniform along right gear formula planet carrier circumference, engages with the internal gear of right gear formula gear ring and the external gear of right sun gear simultaneously, in addition, left gear formula gear ring is provided with oil duct one, left gear formula planet carrier is provided with oil duct two, right gear formula gear ring is provided with oil duct three, right gear formula planet carrier is provided with oil duct four, is respectively used to lubricant oil and enters corresponding sliding bearing, to ensure lubrication, differential main shaft is arranged in casing, left oil hydraulic motor and right oil hydraulic motor are symmetrical fastening to be installed on casing, left hydraulic motor gear is set on the spline spindle of left oil hydraulic motor, spline spindle one end of left oil hydraulic motor is spacing by snap ring four, left oil hydraulic motor drives left hydraulic motor gear to rotate by spline spindle, and left hydraulic motor gear engages with the outer gear of left gear formula gear ring, right hydraulic motor gear is set on the spline spindle of right oil hydraulic motor, spline spindle one end of right oil hydraulic motor is spacing by snap ring six, right oil hydraulic motor drives right hydraulic motor gear to rotate by spline spindle, and right hydraulic motor gear engages with the outer gear of right gear formula gear ring,
In transition gearing down part, transition transmission shaft is provided with the identical left transition gearing down part of structure and right transition gearing down part, and these two transition gearing down parts are symmetrical about middle back-up ring, and transition transmission shaft is arranged in casing, left duplicate gear is set in transition transmission shaft, and right duplicate gear is set in transition transmission shaft; In addition, the right side gear of left duplicate gear engages with the planetary outer gear in a left side, left planetary power passes to follow-up relevant apparatus by the left side gear of left duplicate gear, the left side gear of right duplicate gear engages with the planetary outer gear in the right side, and right planetary power passes to follow-up relevant apparatus by the right side gear of right duplicate gear;
Left track drive part comprises an end cap, a bearing and a back-up ring, that end cap ten is installed on casing respectively, left driving shaft is installed in end cap ten by bearing 11, left actuation gear is installed on left driving shaft, and drive left driving shaft to rotate by spline, to drive outside traveling to take turns, back-up ring ten is set on left driving shaft, for adjusting axial clearance;
Right side track drive part comprises an end cap, a bearing and a back-up ring, end cap 11, bearing 12 and back-up ring 11 respectively, end cap 11 is installed on casing, right driving axle is installed in end cap 11 by bearing 12, right actuation gear is installed on right driving axle, and drives right driving axle to rotate by spline, takes turns to drive outside traveling, back-up ring 11 is set on right driving axle, for adjusting axial clearance; And left driving shaft docks with right driving axle.
In the utility model, casing is also provided with box sealing lid one, box sealing lid two and oilhole plug screw, for realizing the sealing to casing.
In the utility model, one-level driving shaft is also provided with back-up ring two and sleeve two, for adjusting one-level driving shaft axial clearance.
In the utility model, on transition transmission shaft, transition is provided with two sliding bearings, be sliding bearing seven and sliding bearing eight respectively, left duplicate gear is set on transition transmission shaft by sliding bearing seven and dallies, and right duplicate gear is set on transition transmission shaft by sliding bearing eight and dallies.
In the utility model, be provided with outside framework oil seal one in end cap ten, and outside framework oil seal one is set on left driving shaft, the dynamic rotary for left actuation gear seals.
In the utility model, be provided with outside framework oil seal two in end cap 11, and outside framework oil seal two is set on right driving axle, the dynamic rotary for right actuation gear seals.
In the utility model, be provided with needle bearing three in right driving axle one end, left driving shaft is docked with right driving axle by needle bearing three.
In the utility model, 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, the power of forward gear clutch drives forward gear drive bevel gear to rotate through forward gear power input shaft, and the driven wheel of differential through engaging with forward gear drive bevel gear transmits driven rotary, driven wheel of differential drives one-level driving gear to rotate by one-level driving shaft, one-level driving gear drives one-level driven gear to rotate, and through second motive force transmitting portions by transmission of power to differential planetary drive stepless speed changing part, now left oil hydraulic motor and right oil hydraulic motor are in non-resistance non-self-lock-ing state under the control of outside hydraulic power, output that transmission system is unpowered, and shift handle is when being placed in forward gears road location, left oil hydraulic motor and right oil hydraulic motor rotate by external hydraulic dynamic Control, and differential main shaft drives left gear formula planet carrier and right gear formula planet carrier rotating Vortex, to 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, reverse gear clutch power directly through reverse gear power input shaft drive reverse gear drive bevel gear rotate, and by transmission of power to first order kinetics transmitting portions, identical when driving principle mode and advance, just direction is contrary, during reversing, shift handle is placed in car backing position.
In the utility model, when left oil hydraulic motor is by self-locking during external hydraulic motivational drive, the left hydraulic motor gear be installed on its spline spindle locks thereupon, now left gear formula gear ring is also in the lock state, differential driving gear drives differential main shaft to rotate by spline, differential main shaft drives left sun gear to rotate by spline, and drive the left planetary pinion along left gear formula planet carrier is uniform to rotate, thus drive left gear formula planet carrier to rotate, transmission of power is given follow-up relevant apparatus, to realize mechanical type Direct driver by outer gear by left gear formula planet carrier; When the left oil hydraulic motor of external hydraulic positive direction actuation drives left hydraulic motor gear to rotate, and then drive left gear formula gear ring to rotate forward, then accelerate the rotating speed of left gear formula planet carrier, otherwise then reduce the rotating speed of left gear formula planet carrier, by to the control realization of outside Hydrauservo System to the stepless change of left oil hydraulic motor, and then realize exporting the stepless change of left gear formula planet carrier; Namely acceleration or deceleration is realized by left hydraulic motor gear drived control left gear formula gear ring; The mode that right fluid motor-driven control right gear formula gear ring realizes acceleration or deceleration is consistent with left oil hydraulic motor; When left oil hydraulic motor is identical with right oil hydraulic motor working state, drive left track drive part identical with the rotating speed of right side track drive part, advance or reversing to realize endless-track vehicle; When left oil hydraulic motor is different from right oil hydraulic motor working state, drive left track drive part different from the rotating speed of right side track drive part, to realize turning to slow-speed of revolution side crawler belt, and by two self-locking type hydraulic motor control in steering procedure, both sides crawler belt clockwise and anticlockwise can be realized control, be convenient to efficient small radius steering, steering operation mechanism is easy, is conducive to computer integrating control.
Beneficial effect: the utility model adopts double clutch self-locking type hydraulic motor control planetary gear mechanism, switching efficiency is high, be easy to realize computer integrating control, be conducive to track-laying vehicle and realize wireless remote integrating control and remote driving, efficiently solve mechanical type and directly drive the problem that transmission is combined with hydraulic stepless formula, and the velocity ratio of epicyclic transmission mechanism is large, can reduce transmission progression when resultant gear ratio is constant, reduce component number; Adopt the planetary gear mechanism of the two self-locking type hydraulic motor controls be arranged symmetrically with simultaneously, when two cover oil hydraulic motor working staties are identical, drive left track drive part identical with the rotating speed of right side track drive part, to realize advancing or reverse travel, when two cover oil hydraulic motor working staties are different, drive left track drive part different from the rotating speed of right side track drive part, to realize turning to slow-speed of revolution side crawler belt, controlled by oil hydraulic motor in steering procedure, be convenient to realize efficient small radius steering, steering operation mechanism is easy.
Accompanying drawing explanation
Fig. 1 is the structural representation of preferred embodiment of the present utility model.
Fig. 2 is A-A place sectional view in Fig. 1.
Fig. 3 is double-clutch power input part structural representation in preferred embodiment of the present utility model.
Fig. 4 is first order kinetics transmitting portions structural representation in preferred embodiment of the present utility model.
Fig. 5 is second motive force transmitting portions structural representation in preferred embodiment of the present utility model.
Fig. 6 is differential planetary drive stepless speed changing part-structure schematic diagram in preferred embodiment of the present utility model.
Fig. 7 is left differential planetary drive part structural representation in preferred embodiment of the present utility model.
Fig. 8 is right differential planetary drive part structural representation in preferred embodiment of the present utility model.
Fig. 9 is transition gearing down part-structure schematic diagram in preferred embodiment of the present utility model.
Figure 10 is left track drive part and right side track drive part structural representation in preferred embodiment of the present utility model.
Embodiment
The technological means realized to make the utility model, creation characteristic, reaching object and effect is easy to understand, below in conjunction with concrete diagram, setting forth the utility model further.
See the double-clutch type endless-track vehicle hydraulic stepless speed variator of Fig. 1 ~ Fig. 2, comprise double-clutch power input part X, casing W, box sealing lid one A, box sealing lid two B, oilhole plug screw C, the clutch P that reverses gear, forward gear clutch Q, first order kinetics transmitting portions L, second motive force transmitting portions M, differential planetary drive stepless speed changing part T, transition gearing down part S, left track drive part N1 and right side track drive part N2, wherein, double-clutch power input part X, box sealing lid one A, box sealing lid two B, oilhole plug screw C, first order kinetics transmitting portions L, second motive force transmitting portions M, differential planetary drive stepless speed changing part T, transition gearing down part S, left track drive part N1 and right side track drive part N2 is installed on casing W, 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 is delivered to first order kinetics transmitting portions L through double-clutch power input part X, first order kinetics transmitting portions L through second motive force transmitting portions M by transmission of power to differential planetary drive stepless speed changing part T, by differential planetary drive stepless speed changing part T, power is exported driving transition gearing down part S respectively again, finally pass to left track drive part N1 and right side track drive part N2.
Shown in Figure 3, double-clutch power input part X comprises bearing one X1, sleeve one X2, clamping bolt one X3, end cap one X4, back-up ring one X5, needle bearing one X6, forward gear power input shaft X7, oil sealing X8, bearing two X9, forward gear drive bevel gear X10, the power input shaft X11 that reverses gear, reverse gear drive bevel gear X12.
Forward gear power input shaft X7 is installed in end cap one X4 by bearing two X9, end cap one X4 is anchored on casing W by clamping bolt one X3, oil sealing X8 is installed in end cap one X4, dynamic rotary for forward gear power input shaft X7 seals, forward gear drive bevel gear X10 is installed on one end of forward gear power input shaft X7, forward gear power input shaft X7 drives forward gear drive bevel gear X10 to rotate transferring power by spline, and forward gear clutch Q is installed on one end of forward gear power input shaft X7, power input shaft X11 one end of reversing gear is installed in forward gear power input shaft X7 by needle bearing one X6, the other end is installed in casing W by bearing one X1, and the power input shaft X11 that reverses gear is provided with back-up ring one X5 for axial limiting, the clutch P that reverses gear is installed on and reverses gear on power input shaft X11, and the spline transferring power by reversing gear on power input shaft X11, reverse gear one end of power input shaft X11 is set with sleeve one X2 and the drive bevel gear X12 that reverses gear, sleeve one X2 be used for axial clearance adjustment and spacing, by the spline that reverses gear on power input shaft X11 by transmission of power to the drive bevel gear X12 that reverses gear, drive its rotate and by transmission of power give follow-up relevant device.
Shown in Figure 4, first order kinetics transmitting portions L comprises clamping bolt two L1, end cap two L2, bearing three L3, one-level driving gear L4, bearing four L5, end cap three L6, clamping bolt three L7, back-up ring two L8, sleeve two L9, driven wheel of differential L10, one-level driving shaft L11, needle bearing two L12, needle bearing two L13, one-level driven shaft L14, one-level driven gear L15, back-up ring three L16.
One-level driving shaft L11 two ends are installed in casing W respectively by bearing four L5 and needle bearing two L12, and bearing four L5 holds by being fastened on the end cap three L6 position limiting sealed on casing W by clamping bolt three L7, and in one-level driving shaft L11 one end outer cover, driven wheel of differential L10 is housed, driven wheel of differential L10 drives one-level driving shaft L11 to rotate by spline, back-up ring two L8 and sleeve two L9 is installed on one-level driving shaft L11 respectively, adjust for axial clearance, one-level driving gear L4 is set on one-level driving shaft L11, by spline transferring power; One-level driven shaft L14 two ends are installed in casing W respectively by bearing three L3 and needle bearing two L13, and bearing three L3 holds by being fastened on the end cap two L2 position limiting sealed on casing W by clamping bolt two L1, one-level driven gear L15 is installed on one-level driven shaft L14, one-level driven gear L15 engages with one-level driving gear L4 with transferring power to follow-up relevant device, back-up ring three L16 is installed between bearing three L3 and one-level driven gear L15, adjusts for axial clearance.
Shown in Figure 5, second motive force transmitting portions M comprises bearing five M1, end cap four M2, clamping bolt four M3, back-up ring four M4, secondary driven gear M5, secondary driving gear M6, snap ring one M7, secondary drive shaft M8, bearing six M9, end cap five M10, clamping bolt five M11, snap ring two M12; Wherein, secondary drive shaft M8 one end is installed in casing W by bearing five M1, and the other end is installed in casing W by bearing six M9, and end cap four M2 is installed on casing W by clamping bolt four M3, and end cap five M10 is installed on casing W by clamping bolt five M11; Secondary driven gear M5 and secondary driving gear M6 is set on secondary drive shaft M8, snap ring one M7 is used for the axial limiting of secondary driving gear M6, snap ring two M12 and back-up ring four M4 is used for the axial limiting of secondary driven gear M5, secondary driven gear M5 engages with one-level driven gear L15, secondary drive shaft M8 is driven to rotate by spline the power of one-level driven gear L15, secondary drive shaft M8 drives secondary driving gear M6 to rotate by spline, and gives follow-up relevant apparatus by transmission of power.
Shown in Fig. 6 ~ Fig. 8, differential planetary drive stepless speed changing part T comprises left differential planetary drive part T1, right differential planetary drive part T2, differential driving gear T3, differential main shaft T4, and left differential planetary drive part T1 comprises left gear formula gear ring T1-1, left lateral star-wheel back-up ring T1-2, left lateral star-wheel line shaft T1-3, oil duct one T1-4, sliding bearing three T1-5, back-up ring four T1-6, left sun gear T1-7, snap ring three T1-8, back-up ring five T1-9, left gear formula planet carrier T1-10, oil duct two T1-11, left lateral star-wheel sliding bearing T1-12, left planetary pinion T1-13, snap ring four T1-14, left hydraulic motor gear T1-15, fastening screw trip bolt one T1-16, left oil hydraulic motor T1-17, clamping bolt six T1-18, bearing seven T1-19, end cap six T1-20, sliding bearing four T1-21,
Right differential planetary drive part T2 comprises right gear formula gear ring T2-1, right lateral star-wheel back-up ring T2-2, right lateral star-wheel line shaft T2-3, oil duct three T2-4, sliding bearing five T2-5, back-up ring six T2-6, right sun gear T2-7, snap ring five T2-8, back-up ring seven T2-9, right gear formula planet carrier T2-10, oil duct four T2-11, right lateral star-wheel sliding bearing T2-12, right planetary pinion T2-13, snap ring six T2-14, right hydraulic motor gear T2-15, fastening screw trip bolt two T2-16, right oil hydraulic motor T2-17, clamping bolt seven T2-18, bearing eight T2-19, end cap seven T2-20, sliding bearing six T2-21.
Left differential planetary drive part T1 and right differential planetary drive part T2 is symmetrical arranged about differential driving gear T3, and differential driving gear T3 is set on differential main shaft T4, and by being installed on snap ring three T1-8 on differential main shaft T4 and snap ring five T2-8 axial limiting.
Sliding bearing three T1-5 spacer shell is loaded on differential main shaft T4, the power of successive difference speed main shaft T4 uploaded by the spline that left sun gear T1-7 is set in differential main shaft T4 outer installment, left gear formula gear ring T1-1 is set in idle running that sliding bearing three T1-5 slides, sliding bearing four T1-21 spacer shell is loaded on differential main shaft T4, left gear formula planet carrier T1-10 is set in idle running that sliding bearing four T1-21 slides, left lateral star-wheel line shaft T1-3 one end interference is installed in left gear formula planet carrier T1-10, left lateral star-wheel sliding bearing T1-12 interference is in left planetary pinion T1-13, left planetary pinion T1-13 is set in by left lateral star-wheel sliding bearing T1-12 rotation that left lateral star-wheel line shaft T1-3 slides, left lateral star-wheel line shaft T1-3 the other end interference has left lateral star-wheel back-up ring T1-2, to limit the axial float of left planetary pinion T1-13, and left planetary pinion T1-13 is uniform along left gear formula planet carrier T1-10 circumference, uniform left planetary pinion T1-13 is installed between left gear formula gear ring T1-1 and left sun gear T1-7, engage with the internal gear of left gear formula gear ring T1-1 and the external gear of left sun gear T1-7 simultaneously, be installed on back-up ring four T1-6 between sliding bearing three T1-5 and left sun gear T1-7, bearing seven T1-9 be installed between snap ring three T1-8 and sliding bearing four T1-21 is respectively used to the axial clearance adjusting left differential planetary drive part T1, left gear formula gear ring T1-1 is provided with oil duct one T1-4, left gear formula planet carrier T1-10 is provided with oil duct two T1-11, be respectively used to lubricant oil and enter corresponding sliding bearing, ensure lubrication, bearing seven T1-19 is set on differential main shaft T4, and be installed in end cap six T1-20 that to be fastened on by clamping bolt six T1-18 on casing W, left oil hydraulic motor T1-17 is installed on casing W by fastening screw trip bolt one T1-16 is fastening, left hydraulic motor gear T1-15 is set on the spline spindle of left oil hydraulic motor T1-17, spline spindle one end of left oil hydraulic motor T1-17 is spacing by snap ring four T1-14, left oil hydraulic motor T1-17 drives left hydraulic motor gear T1-15 to rotate by spline spindle, left hydraulic motor gear T1-15 engages with the outer gear of left gear formula gear ring T1-1.
When left oil hydraulic motor T1-17 is without self-locking during external hydraulic motivational drive, the left hydraulic motor gear T1-15 be installed on its spline spindle locks thereupon, now left gear formula gear ring T1-1 is also in the lock state, differential driving gear T3 drives differential main shaft T4 to rotate by spline, differential main shaft T4 drives left sun gear T1-7 to rotate by spline, and drive rotates along the left planetary pinion T1-13 that left gear formula planet carrier T1-10 is uniform, thus drive left gear formula planet carrier T1-10 to rotate, transmission of power is given follow-up relevant apparatus by outer gear by left gear formula planet carrier T1-10, realize mechanical type Direct driver, when external hydraulic positive direction actuation left oil hydraulic motor T1-17 drives left hydraulic motor gear T1-15 to rotate, and then drive left gear formula gear ring T1-1 to rotate forward, then can accelerate the rotating speed of left gear formula planet carrier T1-10, otherwise then can reduce the rotating speed of left gear formula planet carrier T1-10, by can realize the stepless change to left oil hydraulic motor T1-17 to the control of outside Hydrauservo System, and then realize exporting the stepless change of left gear formula planet carrier T1-10, namely acceleration or deceleration is realized by left hydraulic motor gear T1-15 drived control left gear formula gear ring T1-1.
Sliding bearing five T2-5 spacer shell is loaded on differential main shaft T4, the power of successive difference speed main shaft T4 uploaded by the spline that right sun gear T2-7 is set in differential main shaft T4 outer installment, right gear formula gear ring T2-1 is set in idle running that sliding bearing five T2-5 slides, sliding bearing six T2-21 spacer shell is loaded on differential main shaft T4, right gear formula planet carrier T2-10 is set in slip idle running on T2-21 sliding bearing six, right lateral star-wheel line shaft T2-3 one end interference is installed in right gear formula planet carrier T2-10, right lateral star-wheel sliding bearing T2-12 interference is in right planetary pinion T2-13, right planetary pinion T2-13 is set in by right lateral star-wheel sliding bearing T2-12 rotation that right lateral star-wheel line shaft T2-3 slides, right lateral star-wheel line shaft T2-3 the other end interference has right lateral star-wheel back-up ring T2-2, to limit the axial float of right lateral star-wheel line shaft T2-13, and right planetary pinion T2-13 is uniform along right gear formula planet carrier T2-10 circumference, uniform right planetary pinion T2-13 is installed between right gear formula gear ring T2-1 and right sun gear T2-7, engage with the internal gear of right gear formula gear ring T2-1 and the external gear of right sun gear T2-7 simultaneously, be installed on back-up ring six T2-6 between sliding bearing five T2-5 and right sun gear T2-7, back-up ring seven T2-9 be installed between snap ring five T2-8 and sliding bearing six T2-21 is respectively used to the axial clearance adjusting right differential planetary drive part T2, right gear formula gear ring T2-1 is provided with oil duct three T2-4, right gear formula planet carrier T2-10 is provided with oil duct four T2-11, be respectively used to lubricant oil and enter corresponding sliding bearing, ensure lubrication, bearing eight T2-19 is set on differential main shaft T4, and be installed in end cap seven T2-20 that to be fastened on by clamping bolt seven T2-18 on casing W, right oil hydraulic motor T2-17 is installed on casing W by fastening screw trip bolt two T2-16 is fastening, right hydraulic motor gear T2-15 is set on the spline spindle of right oil hydraulic motor T2-17, spline spindle one end of right oil hydraulic motor T2-17 is spacing by snap ring six T2-14, right oil hydraulic motor T2-17 drives right hydraulic motor gear T2-15 to rotate by spline spindle, right hydraulic motor gear T2-15 engages with the outer gear of right gear formula gear ring T2-1.
When right oil hydraulic motor T2-17 is without self-locking during external hydraulic motivational drive, the right hydraulic motor gear T2-15 be installed on its spline spindle locks thereupon, now right gear formula gear ring T2-1 is also in the lock state, differential driving gear T3 drives differential main shaft T4 to rotate by spline, differential main shaft T4 drives right sun gear T2-7 to rotate by spline, and drive rotates along the right planetary pinion T2-13 that right gear formula planet carrier T2-10 is uniform, thus drive right gear formula planet carrier T2-10 to rotate, transmission of power is given follow-up relevant apparatus by outer gear by right gear formula planet carrier T2-10, realize mechanical type Direct driver, when external hydraulic positive direction actuation right oil hydraulic motor T2-17 drives right hydraulic motor gear T2-15 to rotate, and then drive right gear formula gear ring T2-1 to rotate forward, then can accelerate the rotating speed of right gear formula planet carrier T2-10, otherwise then can reduce the rotating speed of right gear formula planet carrier T2-10, by can realize the stepless change to right oil hydraulic motor T2-17 to the control of outside Hydrauservo System, and then realize exporting the stepless change of right gear formula planet carrier T2-10, namely acceleration or deceleration is realized by right hydraulic motor gear T2-15 drived control right gear formula gear ring T2-1.
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, the clutch P that reverses gear disconnects, forward gear clutch engagement Q, the power of forward gear clutch Q drives forward gear drive bevel gear X10 to rotate through forward gear power input shaft X7, and the driven wheel of differential L10 through engaging with forward gear drive bevel gear X10 transmits driven rotary, driven wheel of differential L10 drives one-level driving gear L4 to rotate by one-level driving shaft L11, one-level driving gear L4 drives one-level driven gear L15 to rotate, now left oil hydraulic motor T1-17 and right oil hydraulic motor T2-17 is in non-resistance non-self-lock-ing state under the control of outside hydraulic power, output that transmission system is unpowered, and shift handle is when being placed in forward gears road location, left oil hydraulic motor T1-17 and right oil hydraulic motor T2-17 rotates by external hydraulic dynamic Control, differential main shaft T4 drives left gear formula planet carrier T1-10 and right gear formula planet carrier T2-10 to rotate, and advances to realize endless-track vehicle stepless change, when shift handle is placed in reverse gear neutral gear position, forward gear clutch Q disconnects, the clutch P that reverses gear engages, power directly drives the drive bevel gear X12 that reverses gear to rotate through the power input shaft X11 that reverses gear, and by transmission of power to first order kinetics transmitting portions L, identical when driving principle mode and advance, just direction is contrary, during reversing, shift handle is placed in car backing position.
When left oil hydraulic motor T1-17 is identical with right oil hydraulic motor T2-17 working state, drive left track drive part N1 identical with the rotating speed of right side track drive part N2, advance or reversing, when left oil hydraulic motor T1-17 is different from right oil hydraulic motor T2-17 working state to realize endless-track vehicle; Drive left track drive part N1 different from the rotating speed of right side track drive part N2, to realize turning to slow-speed of revolution side crawler belt, and by two self-locking type hydraulic motor control in steering procedure, both sides crawler belt clockwise and anticlockwise can be realized control, be convenient to efficient small radius steering, steering operation mechanism is easy, is conducive to computer integrating control.
Shown in Figure 9, transition gearing down part S comprises left transition gearing down part S1, right transition gearing down part S2, middle back-up ring S3 and transition transmission shaft S4, wherein, left transition gearing down part S1 comprises end cap eight S1-1, bearing eight S1-2, clamping bolt eight S1-3, left duplicate gear S1-4, back-up ring six S1-5, sliding bearing seven S1-6; Right transition gearing down part S2 comprises end cap nine S2-1, bearing nine S2-2, clamping bolt nine S2-3, right duplicate gear S2-4, back-up ring seven S2-5, sliding bearing eight S2-6.
Left transition gearing down part S1 and right transition gearing down part S2 is symmetrical set about middle back-up ring S3, transition transmission shaft S4 one end is installed in end cap eight S1-1 by bearing eight S1-2, the other end is installed in end cap nine S2-1 by bearing nine S2-2, end cap eight S1-1 is installed on casing W by clamping bolt eight S1-3, and end cap nine S2-1 is installed on casing W by clamping bolt nine S2-3, sliding bearing seven S1-6 and sliding bearing eight S2-6 respectively transition is installed on transition transmission shaft S4, left duplicate gear S1-4 is set on transition transmission shaft S4 by sliding bearing seven S1-6 and dallies, right duplicate gear S2-4 is set on transition transmission shaft S4 by sliding bearing eight S2-6 and dallies, centre is separated by the middle back-up ring S3 be set on transition transmission shaft S4, two ends are spacing and adjustment axial clearance respectively by back-up ring six S1-5 and back-up ring seven S2-5, the right side gear of left duplicate gear S1-4 engages with the outer gear of left planetary pinion T1-13, and the power of left planetary pinion T1-13 is passed to follow-up relevant apparatus by the left side gear of left duplicate gear S1-4, the left side gear of right duplicate gear S2-4 engages with the outer gear of right planetary pinion T2-13, and the power of right planetary pinion T2-13 is passed to follow-up relevant apparatus by the right side gear of right duplicate gear S2-4.
Shown in Figure 10, left track drive part N1 comprises left actuation gear N1-1, back-up ring eight N1-2, clamping bolt ten N1-3, bearing ten N1-4, left driving shaft N1-5, outside framework oil seal one N1-6, end cap ten N1-7, right side track drive part N2 comprises right actuation gear N2-1, back-up ring nine N2-2, clamping bolt 11 N2-3, bearing 11 N2-4, right driving axle N2-5, outside framework oil seal two N2-6, end cap 11 N2-7, needle bearing three N2-8, wherein, end cap ten N1-7 is installed on casing W by clamping bolt ten N1-3, left driving shaft N1-5 is installed in end cap ten N1-7 by bearing ten N1-4, outside framework oil seal one N1-6 is installed in end cap ten N1-7, and be set on left driving shaft N1-5, dynamic rotary for left actuation gear N1-1 seals, left actuation gear N1-1 is installed on left driving shaft N1-5, and drive left driving shaft N1-5 to rotate by spline, outside traveling is driven to take turns, back-up ring eight N1-2 is set on left driving shaft N1-5, for adjusting axial clearance, end cap 11 N2-7 is installed on casing W by clamping bolt 11 N2-3, right driving axle N2-5 is installed in end cap 11 N2-7 by bearing 11 N2-4, outside framework oil seal two N2-6 is installed in end cap 11 N2-7, and be set on right driving axle N2-5, dynamic rotary for right actuation gear N2-1 seals, right actuation gear N2-1 is installed on right driving axle N2-5, and drive right driving axle N2-5 to rotate by spline, outside traveling is driven to take turns, back-up ring nine N2-2 is set on right driving axle N2-5, inside, one end for adjusting axial clearance right driving axle N2-5 is provided with needle bearing three N2-8, left driving shaft N1-5 is docked with right driving axle N2-5 by needle bearing three N2-8.
More than show and describe basic principle of the present utility model and major character and advantage of the present utility model.The technician of the industry should understand; the utility model is not restricted to the described embodiments; what describe in above-described embodiment and specification just illustrates principle of the present utility model; under the prerequisite not departing from the utility model spirit and scope; the utility model also has various changes and modifications, and these changes and improvements all fall within the scope of claimed the utility model.The claimed scope of the utility model is defined by appending claims and equivalent thereof.
Claims (10)
1. double-clutch type endless-track vehicle hydraulic stepless speed variator, comprises double clutch, double-clutch power input part, casing, first order kinetics transmitting portions, second motive force transmitting portions, differential planetary drive stepless speed changing part, transition gearing down part, left track drive part and right side track drive part, it is characterized in that, double-clutch power input part, first order kinetics transmitting portions, second motive force transmitting portions, differential planetary drive stepless speed changing part, transition gearing down 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 first order kinetics transmitting portions, first order kinetics transmitting portions is connected with differential planetary drive stepless speed changing part by second motive force transmitting portions, differential planetary drive stepless speed changing part is connected with transition gearing down part, transition gearing down part is connected with left track drive part and right side track drive part respectively.
2. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 1, 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 arranged in casing, and its one end is provided with forward gear drive bevel gear, and the other end is provided with forward gear clutch; Power input shaft one end of reversing gear is installed in forward gear power input shaft by needle bearing one, and the other end is installed in casing, and the clutch that reverses gear is installed on and reverses gear on power input shaft; In addition, power input shaft one end of reversing gear is set with sleeve one and reverses gear drive bevel gear;
In first order kinetics transmitting portions, one-level driving shaft is installed in casing, and in the outer cover of one-level driving shaft one end, driven wheel of differential is housed, and driven wheel of differential drives one-level driving shaft to rotate by spline, and one-level driving gear is sleeved on one-level driving shaft; One-level driven shaft is installed in casing, and one-level driven gear is installed on one-level driven shaft, and one-level driven gear engages with one-level driving gear simultaneously;
In second motive force transmitting portions, secondary drive shaft is installed in casing, and secondary driven gear and secondary driving gear are set in secondary drive shaft, and secondary driven gear engages with one-level driven gear;
Differential planetary drive stepless speed changing part comprises four sliding bearings, sliding bearing three respectively, sliding bearing four, sliding bearing five and sliding bearing six, differential main shaft is provided with the identical left differential planetary drive part of structure and right differential planetary drive part, and these two planetary reduction gear control sections are symmetrical about differential driving gear, differential driving gear is set in differential main shaft, its both sides spacer shell is equipped with sliding bearing three and sliding bearing five, left gear formula gear ring is sleeved on sliding bearing three, right gear formula gear ring is sleeved on sliding bearing five, left sun gear and right sun gear are set on the spline of differential main shaft outer installment, and sliding bearing four and sliding bearing six respectively spacer shell be loaded on differential main shaft, left gear formula planet carrier is set on sliding bearing four, right gear formula planet carrier is set on sliding bearing six, left lateral star-wheel sliding bearing interference is in left planetary pinion, left planetary pinion is arranged between left gear formula gear ring and left sun gear, and be set on left lateral star-wheel line shaft by left lateral star-wheel sliding bearing, right lateral star-wheel sliding bearing interference is in right planetary pinion, right planetary pinion is arranged between right gear formula gear ring and right sun gear, and be set on right lateral star-wheel line shaft by right lateral star-wheel sliding bearing, one end interference of left lateral star-wheel line shaft is installed in left gear formula planet carrier, and the other end interference has left lateral star-wheel back-up ring, and one end interference of right lateral star-wheel line shaft is installed in right gear formula planet carrier, and the other end interference has right lateral star-wheel back-up ring, left planetary pinion is uniform along left gear formula planet carrier circumference, engage with the internal gear of left gear formula gear ring and the external gear of left sun gear simultaneously, right planetary pinion is uniform along right gear formula planet carrier circumference, engages with the internal gear of right gear formula gear ring and the external gear of right sun gear simultaneously, in addition, left gear formula gear ring is provided with oil duct one, left gear formula planet carrier is provided with oil duct two, right gear formula gear ring is provided with oil duct three, right gear formula planet carrier is provided with oil duct four, differential main shaft is arranged in casing, left oil hydraulic motor and right oil hydraulic motor are symmetrical fastening to be installed on casing, left hydraulic motor gear is set on the spline spindle of left oil hydraulic motor, and left hydraulic motor gear engages with the outer gear of left gear formula gear ring, right hydraulic motor gear is set on the spline spindle of right oil hydraulic motor, and right hydraulic motor gear engages with the outer gear of right gear formula gear ring,
In transition gearing down part, transition transmission shaft is provided with the identical left transition gearing down part of structure and right transition gearing down part, and these two transition gearing down parts are symmetrical about middle back-up ring, and transition transmission shaft is arranged in casing, left duplicate gear is set in transition transmission shaft, and right duplicate gear is set in transition transmission shaft; In addition, the right side gear of left duplicate gear engages with the planetary outer gear in a left side, and the left side gear of right duplicate gear engages with the planetary outer gear in the right side;
Left track drive part comprises an end cap, a bearing and a back-up ring, end cap ten, bearing 11 and back-up ring ten respectively, end cap ten is installed on casing, left driving shaft is installed in end cap ten by bearing 11, left actuation gear is installed on left driving shaft, and back-up ring ten is set on left driving shaft;
Right side track drive part comprises an end cap, a bearing and back-up ring end cap 11, bearing 12 and a back-up ring 11, end cap 11 is installed on casing, right driving axle is installed in end cap 11 by bearing 12, right actuation gear is installed on right driving axle, and back-up ring 11 is set on right driving axle; And left driving shaft docks with right driving axle.
3. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, is characterized in that, casing is also provided with box sealing lid one, box sealing lid two and oilhole plug screw.
4. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, is characterized in that, one-level driving shaft is also provided with back-up ring two and sleeve two.
5. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, it is characterized in that, on transition transmission shaft, transition is provided with two sliding bearings, sliding bearing seven and sliding bearing eight respectively, left duplicate gear is set on transition transmission shaft by sliding bearing seven, and right duplicate gear is set on transition transmission shaft by sliding bearing eight.
6. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, it is characterized in that, be provided with outside framework oil seal one in end cap ten, and outside framework oil seal one is set on left driving shaft.
7. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, it is characterized in that, be provided with outside framework oil seal two in end cap 11, and outside framework oil seal two is set on right driving axle.
8. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, is characterized in that, be provided with needle bearing three in right driving axle one end, and left driving shaft is docked with right driving axle by needle bearing three.
9. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, is characterized in that, the power input shaft that reverses gear is provided with the back-up ring one for axial limiting.
10. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, is characterized in that, secondary driving gear side is provided with the snap ring one for axial limiting.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420415298.8U CN204061764U (en) | 2014-07-25 | 2014-07-25 | Double-clutch type endless-track vehicle hydraulic stepless speed variator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420415298.8U CN204061764U (en) | 2014-07-25 | 2014-07-25 | Double-clutch type endless-track vehicle hydraulic stepless speed variator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204061764U true CN204061764U (en) | 2014-12-31 |
Family
ID=52203285
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420415298.8U Withdrawn - After Issue CN204061764U (en) | 2014-07-25 | 2014-07-25 | Double-clutch type endless-track vehicle hydraulic stepless speed variator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204061764U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104141747A (en) * | 2014-07-25 | 2014-11-12 | 湖南农业大学 | Double-clutch-type hydraulic control stepless speed regulator for tracked vehicle |
| CN111532340A (en) * | 2020-07-09 | 2020-08-14 | 山东科技职业学院 | Vehicle transmission speed difference steering device |
-
2014
- 2014-07-25 CN CN201420415298.8U patent/CN204061764U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104141747A (en) * | 2014-07-25 | 2014-11-12 | 湖南农业大学 | Double-clutch-type hydraulic control stepless speed regulator for tracked vehicle |
| CN111532340A (en) * | 2020-07-09 | 2020-08-14 | 山东科技职业学院 | Vehicle transmission speed difference steering device |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104088989B (en) | Continuously variable transmission for direct control mode crawler | |
| CN104141748B (en) | Continuously-variable transmission for mechanical direct-drive hydraulic double-control tracked vehicle | |
| CN104141749B (en) | Hydraulic control continuously variable transmission for mechanical direct-drive tracked vehicle | |
| CN204004227U (en) | Machinery directly drives endless-track vehicle hydraulic control buncher | |
| CN205089929U (en) | Machine liquid hybrid -driven formula gearbox | |
| CN104141747B (en) | Double-clutch-type hydraulic control stepless speed regulator for tracked vehicle | |
| CN105151120B (en) | A kind of double dynamical input type endless-track vehicle speed changer | |
| CN105042049A (en) | Dual-power-input type crawler vehicle speed changer with built-in braking device | |
| CN204004322U (en) | Directly controlled type endless-track vehicle buncher | |
| CN203557951U (en) | Special-purpose pure electric automobile driving system with automatic two-gear speed changing capability | |
| CN204061764U (en) | Double-clutch type endless-track vehicle hydraulic stepless speed variator | |
| CN202765086U (en) | Electric power steering system | |
| CN204004226U (en) | Machinery directly drives hydraulic pressure double controlled endless-track vehicle buncher | |
| WO2022143964A1 (en) | Gearbox for controlling steering of tracked vehicle | |
| CN101975262B (en) | Power difference-adjusting differential | |
| CN105090431A (en) | Integrated transmission for tracked vehicle | |
| CN104141750B (en) | Double-clutch directly controlled stepless speed regulator for tracked vehicle | |
| CN205588965U (en) | Box of tricks of bi -motor control | |
| CN204025567U (en) | Double clutch directly controlled type endless-track vehicle buncher | |
| CN204942503U (en) | The endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type | |
| CN104864057A (en) | Phase two-way stepless precise adjustable control mechanism | |
| CN205155044U (en) | Normal position turns to gearbox | |
| CN107448577A (en) | Differential drive mechanism | |
| CN206929305U (en) | Differential drive mechanism | |
| CN206694508U (en) | A kind of planet wheel decelerator rear axle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20141231 Effective date of abandoning: 20150527 |
|
| RGAV | Abandon patent right to avoid regrant |