CN204004227U - Machinery directly drives endless-track vehicle hydraulic control buncher - Google Patents
Machinery directly drives endless-track vehicle hydraulic control buncher Download PDFInfo
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- CN204004227U CN204004227U CN201420413611.4U CN201420413611U CN204004227U CN 204004227 U CN204004227 U CN 204004227U CN 201420413611 U CN201420413611 U CN 201420413611U CN 204004227 U CN204004227 U CN 204004227U
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Abstract
Machinery directly drives endless-track vehicle hydraulic control buncher, wherein, a power part for power input part is passed to pto＝power take-off part for external procedure through the output of pto＝power take-off deceleration part, another part is carried advance and retreat gear electrodeless variable-speed part, advance and retreat gear electrodeless variable-speed part reaches differential planetary drive part through intermediate power transmitting portions by power, drive left track drive part and right side track drive part by the output of differential planetary drive part, pto＝power take-off gearshift part is controlled and is switched the output of power input part to pto＝power take-off deceleration part; The gear switch of advance and retreat gear control section control advance and retreat gear electrodeless variable-speed part, differential control part is for controlling the differential of differential planetary drive part.The utility model adopts the planet carrier of self-locking type hydraulic motor control planetary gear mechanism directly to drive and hydraulic pressure stepless time adjustment to realize machinery, has effectively improved transmission efficiency high, and electrodeless variable-speed is in the middle variation of advancing, easy and simple to handle, is easy to drive, and turns to efficiency high.
Description
Technical field
The utility model relates to farm machinery transmission technology field, relates in particular to a kind of machinery and directly drives endless-track vehicle hydraulic control buncher.
Background technique
Endless-track vehicle is conventionally taking cat as main, cat vehicle adopts Purely mechanical power transmission system transferring power conventionally, it has simple in structure, efficiency advantages of higher, but Purely mechanical power-transmitting unit, gear shift operation complexity, drive a car or the technical ability of tractor because agricultural machinery operator does not possess conventionally simultaneously, the cooperation of clutch, throttle, gearshift is difficult to control, and then has limited the development of tractor.At present, much crawler tractor manufacturer adopts oil hydraulic pump-motor integrated system to realize the electrodeless drive system of crawler tractor, because the crawler tractor driving operation that adopts electrodeless drive system is improved, agricultural machinery operator need not participate in professional technical training, only need simple exercise can grasp driving efficiency, thereby accepted by users, and obtained extraordinary effect, but add after hydraulic system, improved complexity and the manufacture cost of operation system.In daily production and application process, cat will articulate agricultural machinery and implement conventionally, and agricultural machinery and implement are in the time of farm work, motor is generally in large throttle state, close to constant engine operating mode, the speed of a motor vehicle changes little, and power and the moment of torsion of machinery are all larger, so easily cause hydraulic system to have the problems such as energy consumption is high, heating value large, poor high temperature stability, even can not realize mouldboard plow farming industry, seriously limit the application area of cat, also increase energy consumption.
Cat vehicle in the market adopts the scheme that turns to of steering linkages operation jaw clutch and multi-disc brake conventionally, its implementation procedure is: when cat vehicle turn left to time, driver's operation left steering pull bar separates and the braking of left side output shaft left side jaw clutch, because crawler tractor vehicle left side transfer motion power interrupts and brakes and stop the rotation, now, under the driving of tractor right side power, facility are realized and being turned to the left; In like manner can realize right hand steering, but this steering equipment adopts separation and in conjunction with jaw clutch and break realization, it turns to precision low, steering manipulation is poor.
Model utility content
The technical problem that the utility model solves is to provide a kind of machinery directly to drive endless-track vehicle hydraulic control buncher, to solve the shortcoming in above-mentioned background technology.
The technical problem that the utility model solves realizes by the following technical solutions:
Machinery directly drives endless-track vehicle hydraulic control buncher, comprises power input part, pto＝power take-off deceleration part, pto＝power take-off part, casing, advance and retreat gear electrodeless variable-speed part, advance and retreat gear control section, pto＝power take-off gearshift part, intermediate power transmitting portions, differential control part, differential planetary drive part, left track drive part and right side track drive part, wherein, power input part, pto＝power take-off deceleration part, pto＝power take-off part, advance and retreat gear electrodeless variable-speed part, advance and retreat gear control section, pto＝power take-off gearshift part, intermediate power transmitting portions, differential control part, differential planetary drive part, left track drive part and right side track drive part are installed on casing, and power input part respectively with pto＝power take-off deceleration part, advance and retreat gear electrodeless variable-speed part connects, a power part for power input part input is exported through pto＝power take-off deceleration part, another part is delivered to advance and retreat gear electrodeless variable-speed part, pto＝power take-off deceleration part is connected with pto＝power take-off part, for by transmission of power to external procedure part, advance and retreat gear electrodeless variable-speed part is connected with differential planetary drive part by intermediate power transmitting portions, 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 power input part, for controlling the output of switching the high-altitude low third gear of power input part to pto＝power take-off deceleration part, advance and retreat gears control section is connected with advance and retreat gear electrodeless variable-speed part, keeps off electrodeless variable-speed part forward gears, reverses gear and the switching of neutral gear for advancing and retreat, differential control part is connected with differential planetary drive part, for the differential of differential planetary drive part is controlled.
The concrete linkage structure of each part mentioned above is as follows:
Power input part comprises two bearings, be respectively bearing one and bearing two, power input shaft is installed on casing by bearing one and bearing two, and its one end is power intake, the other end is provided with drive bevel gear by spline, for the transmission of power of power input shaft; Duplex power shift gear Spielpassung is set on power input shaft spline, is convenient to duplex power shift gear and moves from left to right, switches from high-empty-low third gear to realize gear; Power input shaft drives duplex power shift gear rotation transferring power by power input shaft spline, power sliding bearing transition fit is arranged on power input shaft, duplex reduction gear gap is arranged on power sliding bearing, around the gyration center rotation of power input shaft;
Pto＝power take-off deceleration part comprises bearing three, power bearing shaft one end is installed on casing by bearing three, the other end is set in pto＝power take-off by needle bearing, and is provided with spline on power bearing shaft, and triple gear is set on power bearing shaft spline;
In pto＝power take-off part, pto＝power take-off two ends are arranged in casing, and the dynamic output shaft spline of outer installment in 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 pto＝power take-off gearshift part, declutch shift shaft is installed in casing, on declutch shift shaft, be provided with shift fork neutral gear lock ring, high-grade lock ring and low-grade lock ring, in shift fork, be provided with shift fork steel ball and shifting fork spring 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 insert in fork slot its one end, be used for stirring shift fork slides on declutch shift shaft, switch thereby obtain high-empty-low third gear, the other end is provided with the rotating shaft keyway for external control bar is installed;
In advance and retreat gear electrodeless variable-speed part, left side driven wheel of differential and right side driven wheel of differential empty set are slip idling conditions on bevel gear back shaft, splined hub is between left side driven wheel of differential and right side driven wheel of differential, and by spline package on bevel gear back shaft, combined cover is arranged in splined hub, drive bevel gear engages with left side driven wheel of differential and right side driven wheel of differential simultaneously, power input shaft by drive bevel gear by transmission of power to left side driven wheel of differential and right side driven wheel of differential; Left side thrust metal is integrated on bevel gear back shaft, right side thrust metal is positioned at a side of right side driven wheel of differential by snap ring, bevel gear back shaft two ends are arranged in casing by bearing, sun gear is sleeved on bevel gear back shaft spline, gear type gear ring is set on bevel gear back shaft and slides and dally, and planetary pinion is arranged between gear type gear ring and sun gear, and circumferentially uniform along gear type planet carrier by Supporting Planetary Gears assembly, planetary pinion engages with the internal gear of gear type gear ring, the external gear of sun gear simultaneously; Oil hydraulic motor is arranged on casing, and hydraulic motor gear is sleeved on the spline spindle of oil hydraulic motor, and the outer gear of gear type planet carrier engages with hydraulic motor gear;
In advance and retreat gear control section, sleeve interference is set in casing, spring seat is arranged on sleeve pipe one side, and gearshift spring and gearshift steel ball are installed in spring seat, shift shaft one end is arranged in sleeve pipe, and the other end is provided with the gearshift keyway for external control bar is installed, and selector fork is sleeved on shift shaft, during Intercalation overlaps simultaneously, and there are neutral gear lock ring, forward gears lock ring and the lock ring that reverses gear in the shift shaft outer installment of inserting sleeve end;
Intermediate power transmitting portions comprises two bearings, respectively bearing eight and bearing nine, jack shaft is arranged in casing by bearing eight and bearing nine, jackshaft drive pinion and counter shaft driven gear are set on jack shaft, and carry out transmission of power by the spline being arranged on jack shaft, snap ring in the middle of jackshaft drive pinion one side is provided with, for carrying out spacing to jackshaft drive pinion, sleeve is nested on jack shaft, and be positioned at counter shaft driven gear one side, for adjusting the axial clearance of jack shaft and carrying out spacing to counter shaft driven gear; Counter shaft driven gear engages with the external gear of gear type gear ring, and transmission of power is rotated with drive jackshaft drive pinion to the spline arranging on jack shaft;
In differential planetary drive part, in steering shaft, be provided with left planetary reduction gear control section and right planetary reduction gear control section that structure is identical, and these two planetary reduction gear control sections are about steering shaft driving gear symmetry, and in steering shaft driving gear both sides respectively spacer shell left sliding bearing and right sliding bearing are housed, left gear formula gear ring is sleeved on left sliding bearing and slides and dally, right gear formula gear ring is sleeved on right sliding bearing and slides and dally, left sun gear and right sun gear are set on the spline of steering shaft outer installment, and left planetary pinion is arranged between left gear formula gear ring and left sun gear, right planetary pinion is arranged between right gear formula gear ring and right sun gear, in addition, left planetary pinion is circumferentially uniform along left gear formula planet carrier by left planetary pinion supporting component, and left planetary pinion engages with the internal gear of left gear formula gear ring, the external gear of left sun gear simultaneously, right planetary pinion is circumferentially uniform along right gear formula planet carrier by right planetary pinion supporting component, and right planetary pinion engages with the internal gear of right gear formula gear ring, the external gear of right sun gear simultaneously,
Differential control part comprises bearing 12, differential end cap is symmetrical and be arranged in casing about steering shaft driving gear, turn to hub splines to be contained in bearing 12, bearing 12 is arranged in differential end cap about steering shaft driving gear symmetry, turn to bevel gear to be set in and turn to splined shaft, it carries out transferring power by spline, left side turns to duplicate gear and right hand steering duplicate gear turning on control jack shaft about turning to bevel gear to be symmetrical arranged also empty set, and left side turns to the bevel gear on duplicate gear and right hand steering duplicate gear to engage with turning to bevel gear simultaneously, left side turns to the cylindrical gears on duplicate gear to engage with the exterior cylindrical gear of left gear formula gear ring, cylindrical gears on right hand steering duplicate gear engages with the exterior cylindrical gear of right gear formula gear ring,
Left track drive part is identical with right side track drive part-structure, and about steering shaft driving gear symmetry, wherein, left track drive part comprises two bearings, respectively bearing 15 and bearing 16, exercising output shaft one end is arranged in bearing sleeve by bearing 16, the other end is arranged in casing by bearing 15, output shaft actuation gear is sleeved on exercises output shaft one end, left gear formula planet carrier engages with output shaft actuation gear, and output shaft actuation gear is given transmission of power to exercise output shaft by enforcement output shaft spline.
In the utility model, the duplex reduction gear two ends that are arranged on power input shaft are respectively arranged with back-up ring one and the back-up ring two for axial limiting and gap adjustment.
In the utility model, jack shaft one end is provided with end cap seven, and is anchored on casing by bolt six; The other end is provided with end cap eight, and is anchored on casing by bolt seven.
In the utility model, declutch shift shaft two ends are respectively arranged with seal ring one and seal ring two.
In the utility model, declutch shift shaft one end is provided with for declutch shift shaft is carried out to spacing snap ring two.
In the utility model, on shift shaft, be provided with for selector fork is carried out to spacing snap ring seven.
In the utility model, in shift fork end cap, be provided with shift fork seal ring, for the dynamic rotary sealing of shift fork rotating shaft.
In the utility model, power output needle bearing is installed in pto＝power take-off, one end of power bearing shaft is exported needle bearing by power and is docked with pto＝power take-off.
In the utility model, between splined hub and left side driven wheel of differential, be provided with back-up ring four, between splined hub and right side driven wheel of differential, be provided with back-up ring five, back-up ring four and back-up ring five are for splined hub axially locating on bevel gear back shaft.
In the utility model, in the time that outside operating handle promotes shift shaft, gearshift steel ball correspondence under the effect of gearshift spring falls into neutral gear lock ring, forward gears lock ring and reverses gear in lock ring, in the time that gearshift steel ball correspondence falls into neutral gear lock ring, the center position of combined cover in splined hub, now left side driven wheel of differential and right side driven wheel of differential are all in idling conditions, and vehicle stop travels; In the time that external control bar drives shift shaft left lateral, the selector fork being installed on shift shaft moves to left thereupon and drives combined cover to slide left, now the spline of combined cover inside engages with the external splines of splined hub and the external splines of left side driven wheel of differential simultaneously, left side driven wheel of differential passes to splined hub by power by combined cover, splined hub is rotated in the forward by spline band dynamic bevel gear back shaft, and vehicle advances and travels; In like manner, in the time that external control bar drives combined cover to move to right, right side driven wheel of differential passes to splined hub by power by combined cover, and splined hub is by the counterrotating of spline band dynamic bevel gear back shaft, and vehicle falls back and travels.In use, operator only needs to handle external control bar and promotes shift shaft and can realize the change of gear, simple and convenient.
In the utility model, oil hydraulic motor drives hydraulic motor gear rotation by spline spindle, hydraulic motor gear engages with the outer gear of gear type planet carrier, when oil hydraulic motor self-locking during without external hydraulic motivational drive, the hydraulic motor gear being installed on its spline spindle locks thereupon, now gear type planet carrier is also in the lock state, bevel gear back shaft drives sun gear rotation by spline, and drive uniform planetary pinion to rotate, thereby driven gear formula gear ring rotation, gear type gear ring by outer gear by transmission of power to follow up device, directly drive to realize mechanical type, when external hydraulic positive direction actuation oil hydraulic motor drives hydraulic motor gear rotation, and then the wheeled gear ring of driving gear is rotated in the forward, rotating speed that can accelerating gear formula gear ring, otherwise can reduce the rotating speed of gear type gear ring, by to the control of outside Hydrauservo System to realize electrodeless variable-speed to oil hydraulic motor, and then realize the electrodeless variable-speed output to gear type gear ring.
In the utility model, steering shaft driving gear passes to power steering shaft and drives its rotation through spline, steering shaft drives respectively left sun gear and the rotation of right sun gear by spline simultaneously, and then drive left planetary pinion and right planetary pinion to rotate, external control device is by turn to bevel gear to turn to duplicate gear and right hand steering duplicate gear to lock to left side simultaneously, now left gear formula planet carrier and right gear formula planet carrier are with identical rotating speed output, left gear formula planet carrier by transmission of power to left track drive part, right gear formula planet carrier by transmission of power to right side track drive part, in the time that external driver device turns to bevel gear rotation by turning to splined shaft to drive, drive left side to turn to duplicate gear and right hand steering duplicate gear to rotate along different direction, thereby drive left gear formula planet carrier and right gear formula planet carrier to do the rotation of different direction, now on one side Gear Planet Transmission part is slowed down, another side accelerates Gear Planet Transmission part, between left gear formula planet carrier and right gear formula planet carrier, produce speed poor, turn to thereby realize, turn to the clockwise and anticlockwise of bevel gear to realize the left and right turn of endless-track vehicle.
Beneficial effect: the utility model adopts the planet carrier of self-locking type hydraulic motor control planetary gear mechanism directly to drive and hydraulic pressure stepless time adjustment to realize machinery, solve mechanical type and directly driven the problem that transmission is combined with the electrodeless formula of hydraulic pressure, effectively improved mechanical transmission efficiency high; And electrodeless variable-speed is used for the variation of advancing, easy and simple to handle, be easy to drive, be convenient to cat and realize wheel steering, turn to precision high, steering manipulation is strong, cornering ability is good, be conducive to realize mouldboard plow farming industry, expanded the application area of cat simultaneously, also reduced energy consumption.
Brief description of the drawings
Fig. 1 is the structural representation of preferred embodiment of the present utility model.
Fig. 2 is B-B place sectional view in Fig. 1.
Fig. 3 is C-C place sectional view in Fig. 1.
Fig. 4 is D-D place sectional view in Fig. 1.
Fig. 5 is preferred embodiment medium power output shaft part-structure schematic diagram of the present utility model.
Fig. 6 is preferred embodiment medium power output shaft deceleration part of the present utility model and power input part, pto＝power take-off part-structure schematic diagram.
Fig. 7 is advance and retreat gear electrodeless variable-speed part-structure schematic diagram in preferred embodiment of the present utility model.
Fig. 8 is F-F place sectional view in Fig. 1.
Fig. 9 is advance and retreat gear electrodeless variable-speed part and power input part structural representation in preferred embodiment of the present utility model.
Figure 10 is intermediate power transmitting portions structural representation in preferred embodiment of the present utility model.
Figure 11 is differential planetary drive part structural representation in preferred embodiment of the present utility model.
Figure 12 is E-E place sectional view in Fig. 1.
Figure 13 is left track drive part structural representation in preferred embodiment of the present utility model.
Figure 14 is schematic diagram of the present utility model.
Embodiment
For technological means, creation characteristic that the utility model is realized, reach object and effect is easy to understand, below in conjunction with concrete diagram, further set forth the utility model.
Directly drive endless-track vehicle hydraulic control buncher referring to the machinery of Fig. 1～Fig. 2, comprise power input part X, pto＝power take-off deceleration part Y, pto＝power take-off part Z, casing W, advance and retreat gear electrodeless variable-speed part L, advance and retreat gear control section T, pto＝power take-off gearshift part U, intermediate power transmitting portions M, differential control part R, differential planetary drive part S, left track drive part N1 and right side track drive part N2, wherein, power input part X, pto＝power take-off deceleration part Y, pto＝power take-off part Z, advance and retreat gear electrodeless variable-speed part L, advance and retreat gear control section T, pto＝power take-off gearshift part U, intermediate power transmitting portions M, differential control part R, differential planetary drive part S, left track drive part N1 and right side track drive part N2 are installed on casing W, casing W is arranged on engine power outgoing position place, power is inputted through power input part X, a part is exported through pto＝power take-off deceleration part Y, another part flows to advance and retreat gear electrodeless variable-speed part L, pto＝power take-off deceleration part Y through pto＝power take-off part Z by transmission of power to external procedure part, advance and retreat gears electrodeless variable-speed part L through intermediate power transmitting portions M by transmission of power to differential planetary drive part S, divide power is exported respectively and driven left track drive part N1 and right side track drive part N2 by differential planetary drive part S again, pto＝power take-off gearshift part U switches power input part X to the low three gear outputs in the high-altitude of pto＝power take-off deceleration part Y for controlling, advance and retreat gear control section T is for the forward gear of the gear electrodeless variable-speed part L that advances and retreat, reverse gear and the switching of neutral, differential control part R is for the differential control to differential planetary drive part S.
Shown in Fig. 3～Fig. 6, power input part X comprises oil sealing one X1, power input shaft X2, end cap one X3, bearing one X4, bolt one X5, snap ring one X6, duplex power shift gear X7, back-up ring one X8, duplex reduction gear X9, back-up ring two X10, bearing two X11, drive bevel gear X12, power sliding bearing X13; Pto＝power take-off deceleration part Y comprises triple gear Y1, bearing three Y2, power bearing shaft Y3, end cap two Y4, bolt two Y5; Pto＝power take-off part Z comprises bolt three Z1, pto＝power take-off Z2, back-up ring three Z3, bearing four Z4, power output needle bearing Z5, bearing five 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.
Pto＝power take-off X2 is installed in casing W by bearing one X4 and bearing two X11 at two ends, end cap one X3 is anchored on casing W by bolt one X5, oil sealing one X1 is installed in end cap one X3, for the dynamic rotary sealing of power input shaft X2, snap ring one X6 is installed for limiting the axial float of bearing one X4 in end cap one X3, and bearing two X11 and casing W are interference fit, drive bevel gear X12 transition fit is installed on power input shaft X2, for giving follow-up relevant apparatus by the transmission of power of power input shaft X2, duplex power shift gear X7 Spielpassung is set on power input shaft X2 spline, power input shaft X2 drives duplex power shift gear X7 rotation transferring power by spline, power sliding bearing X13 interference fit is installed on power input shaft X2, duplex reduction gear X9 gap be installed on power sliding bearing X13 on, around the gyration center rotation of power input shaft X2, and the two ends of duplex reduction gear X9 are provided with back-up ring one X8 and back-up ring two X10 for axial limiting and gap adjustment on power input shaft X2, bearing three Y2 are installed in casing W, and spacing by end cap two Y4 sealings, end cap two Y4 are anchored on casing W by bolt two Y5, pto＝power take-off Z2 one end is installed in casing W by bearing four Z4, and limits its axial float by back-up ring three Z3, and its other end is installed in casing W by bearing five Z6, and spacing by end cap three Z7, it is upper that end cap three Z7 are anchored on casing W by bolt three Z1, and oil sealing two Z8 are installed in end cap three Z7, and pto＝power take-off Z2 is carried out to dynamic rotary sealing.
Power output needle bearing Z5 is installed in pto＝power take-off Z2, power bearing shaft Y3 two ends are installed on respectively in power output needle bearing Z5 and bearing three Y2, triple gear Y1 is set on the spline of power bearing shaft Y3, 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 power input shaft X2, switches from high-empty-low third gear to realize gear; As shown in Figure 6, its drive path is described as an example of low grade example: the right side gear of duplex power shift gear X7 engages with power output gear Z9 with the left side gear of the left side gear of engage → triple gear of the right side gear of triple gear Y1 Y1 and engage → duplex of the right side gear reduction gear X9 of duplex reduction gear X9, final power output gear Z9 by spline by transmission of power to pto＝power take-off Z2, drive its rotation, this transmission process entirety is gearing down.
Declutch shift shaft U2 is installed in casing W, its two ends are by seal ring one U1 and seal ring two U6 sealings, and by snap ring two U5 lockings, on declutch shift shaft U2, be 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, in shift fork U3, be designed with shift fork steel ball U8 and shifting fork spring U9, for locking the position of shift fork U3, insert in fork slot shift fork rotating shaft U11 one end, be used for stirring shift fork U3 slides on declutch shift shaft U2, thereby obtaining high-empty-low third gear switches, 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 spacing by snap ring three U13 lockings, shift fork end cap U12 is anchored on casing W by hexagon socket head cap screw one U16, in shift fork end cap U12, be provided with shift fork seal ring U15, for the dynamic rotary sealing of shift fork rotating shaft U11.
Shown in Fig. 7～Fig. 9, advance and retreat gear electrodeless variable-speed part L comprises left side driven wheel of differential L1-1, back-up ring four L1-2, needle bearing L1-3, combined cover L3, splined hub L4, right side driven wheel of differential L2-1, back-up ring five L2-2, needle bearing L2-3, right side thrust metal L5, snap ring four L6, bevel gear back shaft L7, bearing six L8, snap ring five L9, end cap five L10, bolt four L11, Supporting Planetary Gears assembly L12, gear type gear ring L13, planetary pinion L14, snap ring six L15, hydraulic motor gear L16, hexagon socket head cap screw two L17, oil hydraulic motor L18, bolt five L19, back-up ring six L20, bearing seven L21, end cap six L22, back-up ring seven L23, gear type planet carrier L24, sun gear L25, left side thrust metal L26, advance and retreat gear control section T comprises neutral gear lock ring T1, sleeve pipe T2, forward gears lock ring T3, gearshift spring T4, gearshift steel ball T5, reverse gear lock stop ring T6, shifting shaft T7, selector fork T8, snap ring seven T9, seal ring four T10, gearshift keyway T11, spring seat T12.
Splined hub L4 is positioned at the centre of left side driven wheel of differential L1-1 and right side driven wheel of differential L2-1 and is set on the spline of bevel gear back shaft L7, drive bevel gear X12 engages with the bevel gear of left side driven wheel of differential L1-1, right side driven wheel of differential L2-1 simultaneously, power input shaft X2 by drive bevel gear X12 by transmission of power to left side driven wheel of differential L1-1, right side driven wheel of differential L2-1, left side driven wheel of differential L1-1 and right side driven wheel of differential L2-1 are set on bevel gear back shaft L7 and are slip idling conditions, sleeve pipe T2 interference is in casing W, shifting shaft T7 one end is loaded in sleeve pipe T2, seal ring four T10 are installed in casing W, to shifting shaft, T7 plays seal action, the shifting shaft T7 the other end is provided with gearshift keyway T11, for the installation of external control bar, sleeve pipe T2 mono-side is provided with spring seat T12, gearshift spring T4, gearshift steel ball T5 is arranged in spring seat T12, selector fork T8 is set on shifting shaft T7, and spacing by being installed on snap ring seven T9 on shifting shaft T7, simultaneously in the external slot of selector fork T8 Intercalation cover L3, and there is neutral gear lock ring T1 in the shifting shaft T7 outer installment of inserting sleeve pipe T2 end, forward gears lock ring T3 and reverse gear lock stop ring T6.
In the time that outside operating handle promotes shifting shaft T7, gearshift steel ball T5 correspondence under the effect of gearshift spring T4 falls in neutral gear lock ring T1, forward gears lock ring T3 and reverse gear lock stop ring T6, in the time that gearshift steel ball T5 correspondence falls into neutral gear lock ring T1, be set in combined cover L3 on the splined hub L4 center position in splined hub L4, now left side driven wheel of differential L1-1 and right side driven wheel of differential L2-1 are all in idling conditions; In the time that external control bar drives shift shaft T7 left lateral, the selector fork T8 being installed on shift shaft T7 moves to left thereupon and drives combined cover L3 to slide left, now left side driven wheel of differential L1-1 passes to splined hub L4 by power by combined cover L3, and splined hub L4 rotates by spline band dynamic bevel gear back shaft L7; In like manner, in the time that external control bar drives combined cover L3 to move to right, right side driven wheel of differential L2-1 passes to splined hub L4 by power by combined cover L3, and splined hub L4 is by spline band dynamic bevel gear back shaft L7 counterrotating.
Between splined hub L4 and left side driven wheel of differential L1-1, be provided with back-up ring four L1-2, between splined hub L4 and right side driven wheel of differential L2-1, be provided with back-up ring five L2-2, back-up ring four L1-2 and back-up ring five L2-2 are all for splined hub L4 axially locating on bevel gear back shaft L7, the side that left side driven wheel of differential L1-1 is set in bevel gear back shaft L7 is designed with needle bearing L1-3, axial thrust load while being used for accepting left side driven wheel of differential L1-1 dynamic rotary transferring power, equally, the side that L2-1 is set in bevel gear back shaft L7 is provided with needle bearing L2-3, axial thrust load while being used for accepting right side driven wheel of differential L2-1 dynamic rotary transferring power, left side thrust metal L26 is integrated on bevel gear back shaft L7, right side thrust metal L5 is positioned at a side of right side driven wheel of differential L2-1 by snap ring four L6, bevel gear back shaft L7 two ends are installed in casing W by bearing six L8 and bearing seven L21 respectively, its one end is spacing by snap ring five L9, and by the fastening end cap five L10 sealings of bolt four L11, and spacing to bearing six L8, the other end is spacing by back-up ring six L20, and by the fastening end cap six L22 sealings of bolt five L19, and spacing to bearing seven L21, sun gear L25 is set in the power that transmits bevel gear back shaft L7 on the outside spline designing of bevel gear back shaft L7, gear type gear ring L13 is set in the upper idle running of sliding of bevel gear back shaft L7, planetary pinion L14 is circumferentially uniform along gear type planet carrier L24 by Supporting Planetary Gears assembly L12, uniform planetary pinion L14 is installed between gear type gear ring L13 and sun gear L25, simultaneously with the internal gear of gear type gear ring L13, the external gear engagement of sun gear L25, be installed on back-up ring seven L23 between back-up ring six L20 and gear type planet carrier L24 for adjusting the axial clearance of planetary reduction gear part, oil hydraulic motor L18 is installed on casing W by hexagon socket head cap screw two L17 are fastening, hydraulic motor gear L16 is set on the spline spindle of oil hydraulic motor L18, spline spindle one end of oil hydraulic motor L18 is spacing by snap ring six L15, oil hydraulic motor L18 drives hydraulic motor gear L16 rotation by spline spindle, and hydraulic motor gear L16 engages with the outer gear of gear type planet carrier L24.
When oil hydraulic motor L18 self-locking during without external hydraulic motivational drive, the hydraulic motor gear L16 being installed on its spline spindle is locked thereupon, now gear type planet carrier L24 is also in the lock state, bevel gear back shaft L7 drives sun gear L25 rotation by spline, and drive uniform planetary pinion L14 to rotate, thereby driven gear formula gear ring L13 rotation, gear type gear ring L13 gives follow-up relevant apparatus by outer gear by transmission of power, realizes mechanical type and directly drives; When external hydraulic positive direction actuation L18 drives hydraulic motor gear L16 rotation, and then the wheeled planet carrier L24 of driving gear is rotated in the forward, rotating speed that can accelerating gear formula gear ring L13, otherwise can reduce the rotating speed of gear type gear ring L13, by realizing the electrodeless variable-speed to oil hydraulic motor L18 to the control of outside Hydrauservo System, and then realize the electrodeless variable-speed output to gear type gear ring L13; Drive control gear formula planet carrier L24 to realize acceleration or deceleration by hydraulic motor gear L16.
Shown in Figure 10, intermediate power transmitting portions M comprises bolt six M1, end cap seven M2, bearing eight M3, sleeve M4, counter shaft driven gear M5, jackshaft drive pinion M6, middle snap ring M7, jack shaft M8, bolt seven M9, end cap eight M10 and bearing nine M11, jack shaft M8 two ends are installed in casing W by bearing nine M11 and bearing eight M3 respectively, its one end is spacing and sealing by fastening end cap seven M2 of bolt six M1, the other end is spacing and sealing by fastening end cap eight M10 of bolt seven M9, counter shaft driven gear M5 and jackshaft drive pinion M6 are set with on jack shaft M8, jackshaft drive pinion M6 is spacing by middle snap ring M7, sleeve M4 is for adjusting the axial clearance of jack shaft M8 and carrying out spacing to counter shaft driven gear M5, counter shaft driven gear M5 engages with the external gear of gear type gear ring L13, transmission of power is driven to jackshaft drive pinion M6 rotation to jack shaft M8 and by spline, transmission of power is given follow-up relevant apparatus by jackshaft drive pinion M6.
Shown in Figure 11～Figure 12, differential planetary drive part S comprises end cap nine S1-1, bearing ten S1-2, needle bearing S1-3, left gear formula planet carrier S1-4, left sun gear S1-5, back-up ring eight S1-6, left sliding bearing S1-7, left gear formula gear ring S1-8, left planetary pinion S1-9, left planetary pinion supporting component S1-10, end cap ten S2-1, bearing 11 S2-2, needle bearing S2-3, right gear formula planet carrier S2-4, right sun gear S2-5, back-up ring nine S2-6, right sliding bearing S2-7, right gear formula gear ring S2-8, right planetary pinion S2-9, right planetary pinion supporting component S2-10, steering shaft S3 and steering shaft driving gear S4, differential control part R comprises end cap 11 R1, turns to splined shaft R2, bearing 12 R3, turn to bevel gear R4, end cap 12 R5, bearing 13 R6, right hand steering duplicate gear R7, turn to control jack shaft R8, left side turns to duplicate gear R9, bearing 14 R10 and end cap 13 R11.
Left sliding bearing S1-7 spacer shell is loaded on steering shaft S3, left sun gear S1-5 is set in the power that transmits steering shaft S3 on the spline of steering shaft S3 outer installment, left gear formula gear ring S1-8 is set in the upper idle running of sliding of left sliding bearing S1-7, left planetary pinion supporting component S1-10 is installed on left planetary pinion S1-9 on left gear formula planet carrier S1-4, and S1-4 is circumferentially uniform along left gear formula planet carrier, uniform left planetary pinion S1-9 is installed between left gear formula gear ring S1-8 and left sun gear S1-5, simultaneously with the internal gear of left gear formula gear ring S1-8, the external gear engagement of left sun gear S1-5, be installed on back-up ring eight S1-6 between left sliding bearing S1-7 and left sun gear S1-5 for adjusting the axial clearance of planetary reduction gear part, in end cap nine S1-1, be designed with needle bearing S1-3, and be set on steering shaft S3, bearing ten S1-2 are set on steering shaft S3, and be installed in end cap nine S1-1 that are fastened on casing W,
Right sliding bearing S2-7 spacer shell is loaded on steering shaft S3, right sun gear S2-5 is set in the power that transmits steering shaft S3 on the outside spline designing of steering shaft S3, right gear formula gear ring S2-8 is set in the upper idle running of sliding of right sliding bearing S2-7, right planetary pinion supporting component S2-10 is installed on right planetary pinion S2-9 on right gear formula planet carrier S2-4, and S2-4 is circumferentially uniform along right gear formula planet carrier, uniform right planetary pinion S2-9 is installed between right gear formula gear ring S2-8 and right sun gear S2-5, simultaneously with the internal gear of right gear formula gear ring S2-8, the external gear engagement of right sun gear S2-5, be installed on back-up ring nine S2-6 between right sliding bearing S2-7 and right sun gear S2-5 for adjusting the axial clearance of planetary reduction gear part, in end cap ten S2-1, be provided with needle bearing S2-3, and be set on steering shaft S3, bearing 11 S2-2 are set on steering shaft S3, and be installed in end cap ten S2-1 that are fastened on casing W.
End cap 11 R1 are about symmetrical fastening being installed on casing W of steering shaft driving gear S4, turn to splined shaft R2 to be set in bearing 12 R3, bearing 12 R3 are installed in end cap 11 R1 about steering shaft driving gear S4 symmetry, turn to bevel gear R4 to be set in and turn on splined shaft R2, and by spline transferring power, bearing 13 R6 and bearing 14 R10 are installed on respectively and turn to the two ends of controlling jack shaft R8, and be installed in casing W, and two ends by fastening be installed on end cap 13 R11 on casing W and end cap 12 R5 are spacing and sealing, right hand steering duplicate gear R7 and left side turn to duplicate gear R9 to control on jack shaft R8 about turning to bevel gear R4 to be symmetrical arranged to be set in to turn to, side turns to duplicate gear R7 and left side to turn to the bevel gear on duplicate gear R9 to engage with turning to bevel gear R4 simultaneously, left side turns to the cylindrical gears on duplicate gear R9 to engage with the exterior cylindrical gear of left gear formula gear ring S1-8, cylindrical gears on right hand steering duplicate gear R7 engages with the exterior cylindrical gear of right gear formula gear ring S2-8.
Steering shaft driving gear S4 passes to power steering shaft S3 and drives its rotation through spline, steering shaft S3 drives respectively left sun gear S1-5 and right sun gear S2-5 rotation by spline simultaneously, and then left sun gear S1-5 drives left planetary pinion S1-9 rotation, right sun S2-5 drives right planetary pinion S2-9 rotation, external control device is subject to the active force of right planetary pinion S2-9 by the active force that turns to bevel gear R4 and right hand steering duplicate gear R7 and left side are turned to duplicate gear R9 to lock to be subject to left planetary pinion S1-9 as left gear formula gear ring S1-8 and right gear formula gear ring S2-8 simultaneously and has auto-lock function when identical, now left gear formula planet carrier S1-4 and right gear formula planet carrier S2-4 are with identical rotating speed output, left gear formula planet carrier S1-4 is by transmission of power driving N 1 part, right gear formula planet carrier S2-4 is by transmission of power driving N 2 parts,
In the time that external driver device turns to bevel gear R4 rotation by turning to splined shaft R2 to drive, drive left side to turn to duplicate gear R9 and right hand steering duplicate gear R7 to do the rotation of different direction, thereby drive left gear formula gear ring S1-8 and right gear formula gear ring S2-8 to do the rotation of different direction, so on one side Gear Planet Transmission part is slowed down, another side accelerates Gear Planet Transmission part, between left gear formula planet carrier S1-4 and right gear formula planet carrier S2-4, produce speed poor, turn to thereby realize, turn to the clockwise and anticlockwise of bevel gear R4 to realize the left and right turn of vehicle.
Shown in Figure 13, left track drive part N1 and right side track drive part N2 are symmetrical arranged about steering shaft driving gear S4, now taking left track drive part N1 as example, left track drive part N1 comprises bearing 15 N1-1, the output shaft N1-2 that travels, snap ring nine N1-3, output shaft actuation gear N1-4, end cap 14 N1-5, connecting sleeve N1-6, bearing sleeve N1-7, snap ring nine N1-8, bearing 16 N1-9 and bolt eight N1-10, wherein, end cap 14 N1-5 are installed on casing W by bolt eight N1-10, connecting sleeve N1-6 two ends are affixed with bearing sleeve N1-7 and end cap 14 N1-5 respectively, bearing 15 N1-1 and bearing 16 N1-9 are set with in the two ends of the output shaft N1-2 that travels, bearing 15 N1-1 are installed in casing W, bearing 16 N1-9 are installed in bearing sleeve N1-7, and spacing by snap ring nine N1-8, output shaft actuation gear N1-4 is set in the output shaft N1-2 one end of travelling, and spacing by snap ring nine N1-3, output shaft actuation gear N1-4 gives by transmission of power the output shaft N1-2 that travels by spline.
More than show and described 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; that in above-described embodiment and specification, describes just illustrates principle of the present utility model; do not departing under the prerequisite of 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. machinery directly drives endless-track vehicle hydraulic control buncher, it is characterized in that, power input part, pto＝power take-off deceleration part, pto＝power take-off part, advance and retreat gear electrodeless variable-speed part, advance and retreat gear control section, pto＝power take-off gearshift part, intermediate power transmitting portions, differential control part, differential planetary drive part, left track drive part and right side track drive part are installed on casing, and power input part is connected with pto＝power take-off deceleration part, advance and retreat gear electrodeless variable-speed part respectively; Pto＝power take-off deceleration part is connected with pto＝power take-off part, advance and retreat gear electrodeless variable-speed part is connected with differential planetary drive part by intermediate power transmitting portions, 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 power input part, advance and retreat gear control section is connected with advance and retreat gear electrodeless variable-speed part, and differential control part is connected with differential planetary drive part.
2. machinery according to claim 1 directly drives endless-track vehicle hydraulic control buncher, it is characterized in that, the concrete linkage structure of each part mentioned above is as follows:
Power input part comprises two bearings, is respectively bearing one and bearing two, and power input shaft is installed on casing by bearing one and bearing two, and its one end is power intake, and the other end is provided with drive bevel gear by spline; Duplex power shift gear Spielpassung is set on power input shaft spline; Power sliding bearing transition fit is arranged on power input shaft, and duplex reduction gear gap is arranged on power sliding bearing;
Pto＝power take-off deceleration part comprises bearing three, power bearing shaft one end is installed on casing by bearing three, the other end is set in pto＝power take-off by needle bearing, and is provided with spline on power bearing shaft, and triple gear is set on power bearing shaft spline;
In pto＝power take-off part, pto＝power take-off two ends are arranged in casing, and the dynamic output shaft spline of outer installment in 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 pto＝power take-off gearshift part, declutch shift shaft is installed in casing, on declutch shift shaft, be provided with shift fork neutral gear lock ring, high-grade lock ring and low-grade lock ring, in shift fork, be provided with shift fork steel ball and shifting fork spring and be sleeved on declutch shift shaft, shift fork rotating shaft is installed in shift fork end cap, and insert in fork slot its one end, and the other end is provided with the rotating shaft keyway for external control bar is installed;
In advance and retreat gear electrodeless variable-speed part, left side driven wheel of differential and right side driven wheel of differential empty set are on bevel gear back shaft, splined hub is between left side driven wheel of differential and right side driven wheel of differential, and by spline package on bevel gear back shaft, combined cover is arranged in splined hub, and drive bevel gear engages with left side driven wheel of differential and right side driven wheel of differential simultaneously; Left side thrust metal is integrated on bevel gear back shaft, right side thrust metal is positioned at a side of right side driven wheel of differential by snap ring, bevel gear back shaft two ends are arranged in casing by bearing, sun gear is sleeved on bevel gear back shaft spline, gear type gear ring is set on bevel gear back shaft, and planetary pinion is arranged between gear type gear ring and sun gear, and circumferentially uniform along gear type planet carrier by Supporting Planetary Gears assembly, planetary pinion engages with the internal gear of gear type gear ring, the external gear of sun gear simultaneously; Oil hydraulic motor is arranged on casing, and hydraulic motor gear is sleeved on the spline spindle of oil hydraulic motor, and the outer gear of gear type planet carrier engages with hydraulic motor gear;
In advance and retreat gear control section, sleeve interference is set in casing, spring seat is arranged on sleeve pipe one side, and gearshift spring and gearshift steel ball are installed in spring seat, shift shaft one end is arranged in sleeve pipe, and the other end is provided with the gearshift keyway for external control bar is installed, and selector fork is sleeved on shift shaft, during Intercalation overlaps simultaneously, and there are neutral gear lock ring, forward gears lock ring and the lock ring that reverses gear in the shift shaft outer installment of inserting sleeve end;
Intermediate power transmitting portions comprises two bearings, respectively bearing eight and bearing nine, jack shaft is arranged in casing by bearing eight and bearing nine, jackshaft drive pinion and counter shaft driven gear are set on jack shaft, snap ring in the middle of jackshaft drive pinion one side is provided with, sleeve is nested on jack shaft, and counter shaft driven gear engages with the external gear of gear type gear ring;
In differential planetary drive part, in steering shaft, be provided with left planetary reduction gear control section and right planetary reduction gear control section that structure is identical, and these two planetary reduction gear control sections are about steering shaft driving gear symmetry, and in steering shaft driving gear both sides respectively spacer shell left sliding bearing and right sliding bearing are housed, left gear formula gear ring is sleeved on left sliding bearing, right gear formula gear ring is sleeved on right sliding bearing, left sun gear and right sun gear are set on the spline of steering shaft outer installment, and left planetary pinion is arranged between left gear formula gear ring and left sun gear, right planetary pinion is arranged between right gear formula gear ring and right sun gear, in addition, left planetary pinion is circumferentially uniform along left gear formula planet carrier by left planetary pinion supporting component, and left planetary pinion engages with the internal gear of left gear formula gear ring, the external gear of left sun gear simultaneously, right planetary pinion is circumferentially uniform along right gear formula planet carrier by right planetary pinion supporting component, and right planetary pinion engages with the internal gear of right gear formula gear ring, the external gear of right sun gear simultaneously,
Differential control part comprises bearing 12, differential end cap is symmetrical and be arranged in casing about steering shaft driving gear, turn to hub splines to be contained in bearing 12, bearing 12 is arranged in differential end cap about steering shaft driving gear symmetry, turn to bevel gear to be set in and turn to splined shaft, left side turns to duplicate gear and right hand steering duplicate gear turning on control jack shaft about turning to bevel gear to be symmetrical arranged also empty set, and left side turns to the bevel gear on duplicate gear and right hand steering duplicate gear to engage with turning to bevel gear simultaneously, left side turns to the cylindrical gears on duplicate gear to engage with the exterior cylindrical gear of left gear formula gear ring, cylindrical gears on right hand steering duplicate gear engages with the exterior cylindrical gear of right gear formula gear ring,
Left track drive part is identical with right side track drive part-structure, and about steering shaft driving gear symmetry, wherein, left track drive part comprises two bearings, be respectively bearing 15 and bearing 16, exercise output shaft one end and be arranged in bearing sleeve by bearing 16, the other end is arranged in casing by bearing 15, output shaft actuation gear is sleeved on exercises output shaft one end, and left gear formula planet carrier engages with output shaft actuation gear.
3. machinery according to claim 2 directly drives endless-track vehicle hydraulic control buncher, it is characterized in that, the duplex reduction gear two ends that are arranged on power input shaft are respectively arranged with back-up ring one and the back-up ring two for axial limiting and gap adjustment.
4. machinery according to claim 2 directly drives endless-track vehicle hydraulic control buncher, it is characterized in that, is provided with for selector fork is carried out to spacing snap ring on shift shaft.
5. machinery according to claim 2 directly drives endless-track vehicle hydraulic control buncher, it is characterized in that, declutch shift shaft one end is provided with for declutch shift shaft is carried out to spacing snap ring.
6. machinery according to claim 2 directly drives endless-track vehicle hydraulic control buncher, it is characterized in that, is provided with shift fork seal ring in shift fork end cap.
7. machinery according to claim 2 directly drives endless-track vehicle hydraulic control buncher, it is characterized in that, power output needle bearing is installed in pto＝power take-off, and one end of power bearing shaft is exported needle bearing by power and docked with pto＝power take-off.
8. machinery according to claim 2 directly drives endless-track vehicle hydraulic control buncher, it is characterized in that, between splined hub and left side driven wheel of differential, is provided with back-up ring.
9. machinery according to claim 2 directly drives endless-track vehicle hydraulic control buncher, it is characterized in that, between splined hub and right side driven wheel of differential, is provided with back-up ring.
10. machinery according to claim 2 directly drives endless-track vehicle hydraulic control buncher, it is characterized in that, sleeve is positioned at counter shaft driven gear one side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420413611.4U CN204004227U (en) | 2014-07-25 | 2014-07-25 | Machinery directly drives endless-track vehicle hydraulic control buncher |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420413611.4U CN204004227U (en) | 2014-07-25 | 2014-07-25 | Machinery directly drives endless-track vehicle hydraulic control buncher |
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| Publication Number | Publication Date |
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| CN204004227U true CN204004227U (en) | 2014-12-10 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201420413611.4U Withdrawn - After Issue CN204004227U (en) | 2014-07-25 | 2014-07-25 | Machinery directly drives endless-track vehicle hydraulic control buncher |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104141749A (en) * | 2014-07-25 | 2014-11-12 | 湖南农业大学 | Hydraulic control continuously variable transmission for mechanical direct-drive tracked vehicle |
| CN105065619A (en) * | 2015-09-16 | 2015-11-18 | 湖南省农友机械集团有限公司 | Dual-power input type multi-gear and differential-type steering track vehicle transmission |
| CN109030223A (en) * | 2018-08-22 | 2018-12-18 | 黄志敏 | Engine shift fork spring dynamometer |
| CN110104062A (en) * | 2019-04-25 | 2019-08-09 | 长沙桑铼特农业机械设备有限公司 | A kind of endless-track vehicle separated type ratio differential steering speed changer |
| CN111271427A (en) * | 2020-04-01 | 2020-06-12 | 浙江四方集团公司 | Integral double HST planetary differential steering gearbox |
| CN114233834A (en) * | 2021-12-09 | 2022-03-25 | 江苏沃得农业机械配件制造有限公司 | Dual-drive forward and reverse gearbox |
-
2014
- 2014-07-25 CN CN201420413611.4U patent/CN204004227U/en not_active Withdrawn - After Issue
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104141749A (en) * | 2014-07-25 | 2014-11-12 | 湖南农业大学 | Hydraulic control continuously variable transmission for mechanical direct-drive tracked vehicle |
| CN105065619A (en) * | 2015-09-16 | 2015-11-18 | 湖南省农友机械集团有限公司 | Dual-power input type multi-gear and differential-type steering track vehicle transmission |
| CN109030223A (en) * | 2018-08-22 | 2018-12-18 | 黄志敏 | Engine shift fork spring dynamometer |
| CN109030223B (en) * | 2018-08-22 | 2021-03-26 | 佛山市星学金属制品有限公司 | Starter fork spring dynamometer |
| CN110104062A (en) * | 2019-04-25 | 2019-08-09 | 长沙桑铼特农业机械设备有限公司 | A kind of endless-track vehicle separated type ratio differential steering speed changer |
| CN110104062B (en) * | 2019-04-25 | 2024-04-26 | 长沙桑铼特农业机械设备有限公司 | Split type proportion differential steering transmission of tracked vehicle |
| CN111271427A (en) * | 2020-04-01 | 2020-06-12 | 浙江四方集团公司 | Integral double HST planetary differential steering gearbox |
| CN111271427B (en) * | 2020-04-01 | 2023-08-01 | 浙江四方集团有限公司 | Integrated double HST planetary differential steering gearbox |
| CN114233834A (en) * | 2021-12-09 | 2022-03-25 | 江苏沃得农业机械配件制造有限公司 | Dual-drive forward and reverse gearbox |
| CN114233834B (en) * | 2021-12-09 | 2024-03-22 | 江苏沃得农业机械配件制造有限公司 | Dual-drive positive and negative speed gearbox |
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Legal Events
| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20141210 Effective date of abandoning: 20150429 |