CN104141747A - Double-clutch-type hydraulic control stepless speed regulator for tracked vehicle - Google Patents
Double-clutch-type hydraulic control stepless speed regulator for tracked vehicle Download PDFInfo
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- CN104141747A CN104141747A CN201410357507.2A CN201410357507A CN104141747A CN 104141747 A CN104141747 A CN 104141747A CN 201410357507 A CN201410357507 A CN 201410357507A CN 104141747 A CN104141747 A CN 104141747A
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- gear
- drive
- shaft
- hydraulic motor
- clutch
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
- F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H2061/6604—Special control features generally applicable to continuously variable gearings
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
- Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
- Motor Power Transmission Devices (AREA)
Abstract
Disclosed is a double-clutch-type hydraulic control stepless speed regulator for a tracked vehicle. Double clutches are connected with a double-clutch power input part. The double-clutch power input part transmits power to a first-level power transmission part, the first-level power transmission part transmits the power to a differential planetary transmission stepless speed regulation part through a second-level power transmission part, then the differential planetary transmission stepless speed regulation part outputs the power to drive a transition speed reduction transmission part, and the power is transmitted to a left track drive part and a right track drive part finally. The differential planetary transmission stepless speed regulation part is provided with double self-locking-type hydraulic motors to control planetary gear transmission mechanisms, switching efficiency is high, computer integrated control is achieved easily, and the tracked vehicle can achieve wireless remote integrated control and remote driving; the transmission ratio of the planetary gear transmission mechanisms is large, the hydraulic motors control the tracked vehicle to run forwards or back up or steer, and the number of parts is decreased; meanwhile, efficient small-radius steering is achieved conveniently, and a steering operating mechanism is easy and convenient to operate.
Description
Technical field
The present invention relates to farm machinery transmission technology field, relate in particular 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 conventionally, 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.Due to endless-track vehicle and wheeled vehicle structure difference large, working principle also has very large difference, and the transmission system of endless-track vehicle has the function of wheeled vehicle steering system conventionally; Endless-track vehicle is mainly taking cat as main at present, cat 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 stepless drive system of crawler tractor, because the crawler tractor driving operation that adopts stepless 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, power and the moment of torsion of machinery are all larger, and then have increased the consumption of cat energy.
Simultaneously, 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 and separate and in conjunction with the realization of jaw clutch and break, it turns to precision low, steering manipulation is poor, is unfavorable for that endless-track vehicle realizes the integrated control of wireless remote and remote driving; And in use because differential planetary drive part adopts indirection type control, although reduced the structural manufacturing process difficulty of differential planetary drive part, also reduced the response characteristic of control accuracy and system.
Summary of the invention
Technical problem solved by the invention 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.
Technical problem solved by the invention 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, one-level power transfer part, 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, one-level power transfer part, 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 one-level power transfer part, one-level power transfer part 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 one-level power transfer part through power input part, one-level power transfering part lease making second motive force transmitting portions by transmission of power to differential planetary drive stepless speed changing part, output power and drive transition gearing down part by differential planetary drive stepless speed changing part again, 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 rotation transferring power by spline; The power input shaft one end of reversing gear is installed in forward gear power input shaft by needle bearing (), the other end is installed in casing, and the back-up ring () for axial limiting is installed on the power input shaft that reverses gear, the clutch that reverses gear is installed on and reverses gear on power input shaft, and by the spline transferring power of reversing gear on power input shaft; In addition, reversing gear, power input shaft one end is set with sleeve () and the drive bevel gear of reversing gear, sleeve (one) is for axial clearance adjustment and spacing, and give by transmission of power the drive bevel gear of reversing gear by the spline that reverses gear on power input shaft, drive its rotation and by transmission of power to follow-up relevant device;
In one-level power transfer part, 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 the rotation of one-level driving shaft 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 one side is provided with the snap ring () for axial limiting, and secondary driven gear engages with one-level driven gear, for the power of one-level driven gear is driven to secondary drive shaft rotation by spline, secondary drive shaft drives the rotation of secondary driving gear by spline, and gives follow-up relevant apparatus by transmission of power;
In differential planetary drive stepless speed changing part, on differential main shaft, be provided with left differential planetary drive part and right differential planetary drive part that structure is identical, and these two planetary reduction gear control sections are about differential driving gear symmetry, 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 the upper idle running of sliding of sliding bearing (three), right gear formula gear ring is sleeved on the upper idle running of sliding of 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 the upper idle running of sliding of sliding bearing (four), right gear formula planet carrier is set in the upper idle running of sliding of 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 and slide and rotate 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 and slide and rotate 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 circumferentially uniform along left gear formula planet carrier, engage with the internal gear of left gear formula gear ring and the external gear of left sun gear simultaneously, right planetary pinion is circumferentially uniform along right gear formula planet carrier, engages with the internal gear of right gear formula gear ring and the external gear of right sun gear simultaneously, in addition, on left gear formula gear ring, be provided with oil duct (), on left gear formula planet carrier, be provided with oil duct (two), on right gear formula gear ring, be provided with oil duct (three), on right gear formula planet carrier, be provided with oil duct (four), be respectively used to lubricant oil and enter corresponding sliding bearing, lubricate ensureing, differential main shaft is arranged in casing, symmetrical fastening being installed on casing of left oil hydraulic motor and right oil hydraulic motor, 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 rotation 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 rotation by spline spindle, and right hydraulic motor gear engages with the outer gear of right gear formula gear ring,
In transition gearing down part, on transition transmission shaft, be provided with left transition gearing down part and right transition gearing down part that structure is identical, and these two transition gearing down parts are about middle back-up ring symmetry, 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 left planetary outer gear, 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 right planetary outer gear, and right planetary power passes to follow-up relevant apparatus by the right side gear of right duplicate gear;
In left track drive part, end cap (ten) be 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 drive left driving shaft rotation by spline, to drive the outside wheel that travels, back-up ring (ten) be set on left driving shaft, for adjusting axial clearance;
In the track drive part of right side, 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 drive right driving axle rotation by spline, to drive the outside wheel that travels, 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 present invention, on casing, be also provided with box sealing lid (), box sealing lid (two) and oilhole plug screw, for realizing the sealing to casing.
In the present invention, back-up ring (two) and sleeve (two) are also installed, for adjusting one-level driving shaft axial clearance on one-level driving shaft.
In the present invention, on transition transmission shaft, transition is provided with sliding bearing (seven) and sliding bearing (eight), left duplicate gear is set on transition transmission shaft and is dallied by sliding bearing (seven), and right duplicate gear is set on transition transmission shaft and is dallied by sliding bearing (eight).
In the present invention, outside framework oil seal () is installed in end cap (ten), and outside framework oil seal () is set on left driving shaft, for the dynamic rotary sealing of left actuation gear.
In the present invention, outside framework oil seal (two) is installed in end cap (11), and outside framework oil seal (two) is set on right driving axle, for the dynamic rotary sealing of right actuation gear.
In the present invention, needle bearing (three) is installed in right driving axle one end, left driving shaft docks with right driving axle by needle bearing (three).
In the present invention, forward gear clutch engages, disconnects with the clutch that reverses gear is staggered, and in the time that forward gear clutch engages, the clutch that reverses gear disconnects, and in the time reversing gear clutch engagement, forward gear clutch disconnects, when endless-track vehicle advances, shift handle is placed in forward gears neutral gear position, the clutch that reverses gear disconnects, the engagement of forward gear clutch, the power of forward gear clutch drives the rotation of forward gear drive bevel gear through forward gear power input shaft, and the driven wheel of differential that warp engages with forward gear drive bevel gear transmits driven rotary, driven wheel of differential drives the rotation of one-level driving gear by one-level driving shaft, one-level driving gear drives the rotation of one-level driven gear, 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 under the control of outside hydraulic power in the non-self-locking state of non-resistance, output that transmission system is unpowered, and shift handle is while being placed in forward gears road location, left oil hydraulic motor and right oil hydraulic motor are rotated by external hydraulic dynamic Control, and differential main shaft drives left gear formula planet carrier and right gear formula planet carrier rotating Vortex, advances to realize endless-track vehicle stepless change, in the time that shift handle is placed in reverse gear neutral gear position, forward gear clutch disconnects, the clutch that reverses gear engagement, the power of clutch of reversing gear directly drives through the power input shaft that reverses gear the drive bevel gear rotation of reversing gear, and by transmission of power to one-level power transfer part, driving principle mode is identical when advancing, just opposite direction, when reversing, shift handle is placed in to car backing position.
In the present invention, self-locking in the time that left oil hydraulic motor is subject to external hydraulic motivational drive, the left hydraulic motor gear being installed on its spline spindle locks thereupon, now left gear formula gear ring is also in the lock state, differential driving gear drives the rotation of differential main shaft by spline, differential main shaft drives left sun gear rotation by spline, and drive is along the uniform left planetary pinion rotation of left gear formula planet carrier, thereby drive the rotation of left gear formula planet carrier, left gear formula planet carrier is given follow-up relevant apparatus by outer gear by transmission of power, directly drives to realize mechanical type; When the left oil hydraulic motor of external hydraulic positive direction actuation drives left hydraulic motor gear rotation, and then drive left gear formula gear ring to be rotated in the forward, accelerate the rotating speed of left gear formula planet carrier, otherwise reduce the rotating speed of left gear formula planet carrier, realize the stepless change to left oil hydraulic motor by the control to outside Hydrauservo System, and then realize the stepless change output to left gear formula planet carrier; Drive control left gear formula gear ring to realize acceleration or deceleration by left hydraulic motor gear; The mode that right fluid motor-driven control right gear formula gear ring is realized acceleration or deceleration is consistent with left oil hydraulic motor; In the time that 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 move backward to realize endless-track vehicle; In the time that 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, turn to slow-speed of revolution side crawler belt to realize, and in steering procedure by two self-locking type hydraulic motor controls, can realize both sides crawler belt clockwise and anticlockwise control, be convenient to efficient small radius steering, steering operation mechanism is easy, is conducive to the integrated control of computer.
Beneficial effect: the present invention adopts double clutch self-locking type hydraulic motor control planetary gear mechanism, switching efficiency is high, be easy to realize the integrated control of computer, be conducive to track-laying vehicle and realize the integrated control of wireless remote 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, in the situation that resultant gear ratio is constant, can reduce transmission progression, reduce component number; Adopt the planetary gear mechanism of the two self-locking type hydraulic motor controls that are arranged symmetrically with simultaneously, when two cover oil hydraulic motor working staties are when identical, drive left track drive part identical with the rotating speed of right side track drive part, advance or reverse travel to realize, in the time that 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, turn to slow-speed of revolution side crawler belt to realize, in steering procedure by oil hydraulic motor control, be convenient to realize efficient small radius steering, steering operation mechanism is easy.
Brief description of the drawings
Fig. 1 is the structural representation of preferred embodiment of the present invention.
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 invention.
Fig. 4 is one-level power transfer part structural representation in preferred embodiment of the present invention.
Fig. 5 is second motive force transmitting portions structural representation in preferred embodiment of the present invention.
Fig. 6 is differential planetary drive stepless speed changing part-structure schematic diagram in preferred embodiment of the present invention.
Fig. 7 is left differential planetary drive part structural representation in preferred embodiment of the present invention.
Fig. 8 is right differential planetary drive part structural representation in preferred embodiment of the present invention.
Fig. 9 is transition gearing down part-structure schematic diagram in preferred embodiment of the present invention.
Figure 10 is left track drive part and right side track drive part-structure schematic diagram in preferred embodiment of the present invention.
Embodiment
For technological means, creation characteristic that the present invention is realized, reach object and effect is easy to understand, below in conjunction with concrete diagram, further set forth the present invention.
Referring to 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 () A, box sealing lid (two) B, oilhole plug screw C, the clutch P that reverses gear, forward gear clutch Q, one-level power transfer part 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, one-level power transfer part 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 are installed on casing W, casing W is arranged on engine power outgoing position place, clutch P reverses gear, forward gear clutch Q is connected with double-clutch power input part X, power is delivered to one-level power transfer part L through double-clutch power input part X, one-level power transfer part 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 respectively and driven transition gearing down part S 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 () X1, sleeve () X2, clamping bolt () X3, end cap () X4, back-up ring () X5, needle bearing () 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, the drive bevel gear of reversing gear X12.
Forward gear power input shaft X7 is installed in end cap () X4 by bearing (two) X9, end cap (one) X4 is anchored on casing W by clamping bolt () X3, oil sealing X8 is installed in end cap () X4, for the dynamic rotary sealing of forward gear power input shaft X7, 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 rotation transferring power by spline, and forward gear clutch Q is installed on one end of forward gear power input shaft X7, the power input shaft X11 one end of reversing gear is installed in forward gear power input shaft X7 by needle bearing () X6, the other end is installed in casing W by bearing () X1, and back-up ring () X5 is installed for axial limiting on the power input shaft X11 that reverses gear, the clutch P that reverses gear is installed on and reverses gear on power input shaft X11, and by the spline transferring power of reversing gear on power input shaft X11, reversing gear, one end of power input shaft X11 is set with sleeve () X2 and the drive bevel gear X12 that reverses gear, sleeve (one) X2 is for axial clearance adjustment and spacing, give by transmission of power the drive bevel gear X12 that reverses gear by the spline that reverses gear on power input shaft X11, drive its rotation and by transmission of power give follow-up relevant device.
Shown in Figure 4, one-level power transfer part 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 by bearing (four) L5 and needle bearing (two) L12 respectively, and bearing (four) L5 holds by be fastened on end cap (three) the 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 rotation by spline, back-up ring (two) L8 and sleeve (two) L9 are installed on respectively on one-level driving shaft L11, for axial clearance adjustment, 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 by bearing (three) L3 and needle bearing (two) L13 respectively, and bearing (three) L3 holds by be fastened on end cap (two) the 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, for axial clearance adjustment.
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 () 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, the other end is installed in casing W by bearing (six) M9, it is upper that 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 are set on secondary drive shaft M8, snap ring (one) M7 is for the axial limiting of secondary driving gear M6, snap ring (two) M12 and back-up ring (four) M4 are for the axial limiting of secondary driven gear M5, secondary driven gear M5 engages with one-level driven gear L15, the power of one-level driven gear L15 is driven to secondary drive shaft M8 rotation by spline, secondary drive shaft M8 drives secondary driving gear M6 rotation 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 are symmetrical arranged about differential driving gear T3, and it is upper that differential driving gear T3 is set in differential main shaft T4, and by being installed on snap ring (three) T1-8 and snap ring (five) the T2-8 axial limiting on differential main shaft T4.
Sliding bearing (three) T1-5 spacer shell is loaded on differential main shaft T4, the spline that left sun gear T1-7 is set in differential main shaft T4 outer installment is uploaded the power of successive difference speed main shaft T4, left gear formula gear ring T1-1 is set in the upper slip idle running of sliding bearing (three) T1-5, sliding bearing (four) T1-21 spacer shell is loaded on differential main shaft T4, left gear formula planet carrier T1-10 is set in the upper slip idle running of sliding bearing (four) T1-21, 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 the upper rotation of sliding of left lateral star-wheel line shaft T1-3 by left lateral star-wheel sliding bearing T1-12, 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 circumferentially uniform along left gear formula planet carrier T1-10, 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, be installed on the axial clearance that bearing (seven) T1-9 between snap ring (three) T1-8 and sliding bearing (four) T1-21 is respectively used to adjust left differential planetary drive part T1, on left gear formula gear ring T1-1, be provided with oil duct () T1-4, on left gear formula planet carrier T1-10, be provided with oil duct (two) T1-11, be respectively used to lubricant oil and enter corresponding sliding bearing, ensure lubricated, bearing (seven) T1-19 is set on differential main shaft T4, and be installed on by clamping bolt (six) T1-18 and be fastened in end cap (six) T1-20 on casing W, left oil hydraulic motor T1-17 is installed on casing W by fastening screw trip bolt () 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 rotation 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 self-locking during without external hydraulic motivational drive, the left hydraulic motor gear T1-15 being 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 rotation by spline, differential main shaft T4 drives left sun gear T1-7 rotation by spline, and drive is along the uniform left planetary pinion T1-13 rotation of left gear formula planet carrier T1-10, thereby drive left gear formula planet carrier T1-10 rotation, left gear formula planet carrier T1-10 gives follow-up relevant apparatus by outer gear by transmission of power, realizing mechanical type directly drives, when the left oil hydraulic motor T1-17 of external hydraulic positive direction actuation drives left hydraulic motor gear T1-15 rotation, and then drive left gear formula gear ring T1-1 to be rotated in the forward, can accelerate the rotating speed of left gear formula planet carrier T1-10, otherwise can reduce the rotating speed of left gear formula planet carrier T1-10, by realizing the stepless change to left oil hydraulic motor T1-17 to the control of outside Hydrauservo System, and then realize the stepless change output to left gear formula planet carrier T1-10, drive control left gear formula gear ring T1-1 to realize acceleration or deceleration by left hydraulic motor gear T1-15.
Sliding bearing (five) T2-5 spacer shell is loaded on differential main shaft T4, the spline that right sun gear T2-7 is set in differential main shaft T4 outer installment is uploaded the power of successive difference speed main shaft T4, right gear formula gear ring T2-1 is set in the upper slip idle running of sliding bearing (five) T2-5, sliding bearing (six) T2-21 spacer shell is loaded on differential main shaft T4, right gear formula planet carrier T2-10 is set in the upper idle running of sliding of 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 the upper rotation of sliding of right lateral star-wheel line shaft T2-3 by right lateral star-wheel sliding bearing T2-12, right lateral star-wheel line shaft T2-3 the other end interference has right lateral star-wheel back-up ring T2-2, with the axial float of restriction right lateral star-wheel line shaft T2-13, and right planetary pinion T2-13 is circumferentially uniform along right gear formula planet carrier T2-10, 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, be installed on the axial clearance that back-up ring (seven) T2-9 between snap ring (five) T2-8 and sliding bearing (six) T2-21 is respectively used to adjust right differential planetary drive part T2, on right gear formula gear ring T2-1, be provided with oil duct (three) T2-4, on right gear formula planet carrier T2-10, be provided with oil duct (four) T2-11, be respectively used to lubricant oil and enter corresponding sliding bearing, ensure lubricated, bearing (eight) T2-19 is set on differential main shaft T4, and be installed on by clamping bolt (seven) T2-18 and be fastened in end cap (seven) T2-20 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 rotation 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 self-locking during without external hydraulic motivational drive, the right hydraulic motor gear T2-15 being 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 rotation by spline, differential main shaft T4 drives right sun gear T2-7 rotation by spline, and drive is along the uniform right planetary pinion T2-13 rotation of right gear formula planet carrier T2-10, thereby drive right gear formula planet carrier T2-10 rotation, right gear formula planet carrier T2-10 gives follow-up relevant apparatus by outer gear by transmission of power, realizing mechanical type directly drives, when the right oil hydraulic motor T2-17 of external hydraulic positive direction actuation drives right hydraulic motor gear T2-15 rotation, and then drive right gear formula gear ring T2-1 to be rotated in the forward, can accelerate the rotating speed of right gear formula planet carrier T2-10, otherwise can reduce the rotating speed of right gear formula planet carrier T2-10, by realizing the stepless change to right oil hydraulic motor T2-17 to the control of outside Hydrauservo System, and then realize the stepless change output to right gear formula planet carrier T2-10, drive control right gear formula gear ring T2-1 to realize acceleration or deceleration by right hydraulic motor gear T2-15.
In the time that forward gear clutch Q engages, the clutch P that reverses gear disconnects, in the time reversing gear clutch P engagement, forward gear clutch Q disconnects, be explained as an example of forward gear clutch Q engagement example 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 rotation through forward gear power input shaft X7, and the driven wheel of differential L10 that warp engages with forward gear drive bevel gear X10 transmits driven rotary, driven wheel of differential L10 drives one-level driving gear L4 rotation by one-level driving shaft L11, one-level driving gear L4 drives one-level driven gear L15 rotation, now left oil hydraulic motor T1-17 and right oil hydraulic motor T2-17 under the control of outside hydraulic power in the non-self-locking state of non-resistance, output that transmission system is unpowered, and shift handle is while being placed in forward gears road location, left oil hydraulic motor T1-17 and right oil hydraulic motor T2-17 are rotated 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 rotation, advances to realize endless-track vehicle stepless change, in the time that shift handle is placed in reverse gear neutral gear position, forward gear clutch Q disconnects, the clutch P that reverses gear engagement, power directly drives through the power input shaft X11 that reverses gear the drive bevel gear X12 rotation of reversing gear, and by transmission of power to one-level power transfer part L, driving principle mode is identical when advancing, just opposite direction, when reversing, shift handle is placed in to car backing position.
In the time that 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 move backward to realize endless-track vehicle, in the time that left oil hydraulic motor T1-17 is different from right oil hydraulic motor T2-17 working state; Drive left track drive part N1 different from the rotating speed of right side track drive part N2, turn to slow-speed of revolution side crawler belt to realize, and in steering procedure by two self-locking type hydraulic motor controls, can realize both sides crawler belt clockwise and anticlockwise control, be convenient to efficient small radius steering, steering operation mechanism is easy, is conducive to the integrated control of computer.
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 are 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, it is upper that 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 are installed on transition transmission shaft S4, left duplicate gear S1-4 is set in the upper idle running of transition transmission shaft S4 by sliding bearing (seven) S1-6, right duplicate gear S2-4 is set in the upper idle running of transition transmission shaft S4 by sliding bearing (eight) S2-6, centre separates by the middle back-up ring S3 being set on transition transmission shaft S4, back-up ring (six) S1-5 is passed through respectively at two ends and back-up ring (seven) S2-5 is spacing and adjust axial clearance, 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 () 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, for the dynamic rotary sealing of left actuation gear N1-1, left actuation gear N1-1 is installed on left driving shaft N1-5, and drive left driving shaft N1-5 rotation by spline, wheel travels in driving outside, back-up ring (eight) N1-2 is set on left driving shaft N1-5, be used 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, for the dynamic rotary sealing of right actuation gear N2-1, right actuation gear N2-1 is installed on right driving axle N2-5, and drive right driving axle N2-5 rotation by spline, wheel travels in driving outside, back-up ring (nine) N2-2 is set on right driving axle N2-5, for the inside, one end of adjusting axial clearance right driving axle N2-5, needle bearing (three) N2-8 is installed, left driving shaft N1-5 docks with right driving axle N2-5 by needle bearing (three) N2-8.
More than show and described basic principle of the present invention and major character and advantage of the present invention.The technician of the industry should understand; the present invention is not restricted to the described embodiments; that in above-described embodiment and specification, describes just illustrates principle of the present invention; without departing from the spirit and scope of the present invention; the present invention also has various changes and modifications, and these changes and improvements all fall in the claimed scope of the invention.The claimed scope of the present invention 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, one-level power transfer part, 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, one-level power transfer part, 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 one-level power transfer part, one-level power transfer part 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; The power input shaft one end of reversing gear is installed in forward gear power input shaft by needle bearing (), the other end is installed in casing, and the back-up ring () for axial limiting is installed on the power input shaft that reverses gear, and the clutch that reverses gear is installed on and reverses gear on power input shaft; In addition, the power input shaft one end of reversing gear is set with sleeve () and the drive bevel gear of reversing gear;
In one-level power transfer part, 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 the rotation of one-level driving shaft 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 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 one side is provided with the snap ring () for axial limiting, and secondary driven gear engages with one-level driven gear, for the power of one-level driven gear is driven to secondary drive shaft rotation by spline, secondary drive shaft drives the rotation of secondary driving gear to carry out transmission of power by spline;
In differential planetary drive stepless speed changing part, on differential main shaft, be provided with left differential planetary drive part and right differential planetary drive part that structure is identical, and these two planetary reduction gear control sections are about differential driving gear symmetry, 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 the upper idle running of sliding of sliding bearing (three), right gear formula gear ring is sleeved on the upper idle running of sliding of 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 the upper idle running of sliding of sliding bearing (four), right gear formula planet carrier is set in the upper idle running of sliding of 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 and slide and rotate 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 and slide and rotate 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 circumferentially uniform along left gear formula planet carrier, engage with the internal gear of left gear formula gear ring and the external gear of left sun gear simultaneously, right planetary pinion is circumferentially uniform along right gear formula planet carrier, engages with the internal gear of right gear formula gear ring and the external gear of right sun gear simultaneously, in addition, on left gear formula gear ring, be provided with oil duct (), on left gear formula planet carrier, be provided with oil duct (two), on right gear formula gear ring, be provided with oil duct (three), on right gear formula planet carrier, be provided with oil duct (four), differential main shaft is arranged in casing, symmetrical fastening being installed on casing of left oil hydraulic motor and right oil hydraulic motor, left hydraulic motor gear is set on the spline spindle of left oil hydraulic motor, left oil hydraulic motor drives left hydraulic motor gear rotation 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, right oil hydraulic motor drives right hydraulic motor gear rotation by spline spindle, and right hydraulic motor gear engages with the outer gear of right gear formula gear ring,
In transition gearing down part, on transition transmission shaft, be provided with left transition gearing down part and right transition gearing down part that structure is identical, and these two transition gearing down parts are about middle back-up ring symmetry, 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 left planetary outer gear, left planetary power is by the left side gear transmission of left duplicate gear, the left side gear of right duplicate gear engages with right planetary outer gear, and right planetary power is by the right side gear transmission of right duplicate gear;
In left track drive part, end cap (ten) be 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 drive left driving shaft rotation by spline, to drive the outside wheel that travels, back-up ring (ten) be set on left driving shaft;
In the track drive part of right side, 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 drive right driving axle rotation by spline, to drive the outside wheel that travels, 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, is also provided with box sealing lid (), box sealing lid (two) and oilhole plug screw on casing.
4. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, is characterized in that, back-up ring (two) and sleeve (two) are also installed on one-level driving shaft.
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 sliding bearing (seven) and sliding bearing (eight), left duplicate gear is set on transition transmission shaft and is dallied by sliding bearing (seven), and right duplicate gear is set on transition transmission shaft and is dallied by sliding bearing (eight).
6. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, is characterized in that, outside framework oil seal () is installed in end cap (ten), and outside framework oil seal () is set on left driving shaft.
7. double-clutch type endless-track vehicle hydraulic stepless speed variator according to claim 2, is characterized in that, outside framework oil seal (two) is installed 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, needle bearing (three) is installed in right driving axle one end, and left driving shaft docks with right driving axle by needle bearing (three).
9. according to the double-clutch type endless-track vehicle hydraulic stepless speed variator described in claim 1～8, it is characterized in that, when endless-track vehicle advances, shift handle is placed in forward gears neutral gear position, the clutch that reverses gear disconnects, the engagement of forward gear clutch, the power of forward gear clutch drives the rotation of forward gear drive bevel gear through forward gear power input shaft, and the driven wheel of differential that warp engages with forward gear drive bevel gear transmits driven rotary, driven wheel of differential drives the rotation of one-level driving gear by one-level driving shaft, one-level driving gear drives the rotation of one-level driven gear, 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 under the control of outside hydraulic power in the non-self-locking state of non-resistance, output that transmission system is unpowered, and shift handle is while being placed in forward gears road location, left oil hydraulic motor and right oil hydraulic motor are rotated by external hydraulic dynamic Control, and differential main shaft drives left gear formula planet carrier and right gear formula planet carrier rotating Vortex, advances to realize endless-track vehicle stepless change, in the time that shift handle is placed in reverse gear neutral gear position, forward gear clutch disconnects, the clutch that reverses gear engagement, the power of clutch of reversing gear directly drives through the power input shaft that reverses gear the drive bevel gear rotation of reversing gear, and by transmission of power to one-level power transfer part, driving principle mode is identical when advancing, just opposite direction, when reversing, shift handle is placed in to car backing position.
10. according to the double-clutch type endless-track vehicle hydraulic stepless speed variator described in claim 1～9, it is characterized in that, when the self-locking during without external hydraulic motivational drive of left oil hydraulic motor, the left hydraulic motor gear being installed on its spline spindle locks thereupon, now left gear formula gear ring is also in the lock state, differential driving gear drives the rotation of differential main shaft by spline, differential main shaft drives left sun gear rotation by spline, and drive is along the uniform left planetary pinion rotation of left gear formula planet carrier, thereby drive the rotation of left gear formula planet carrier, left gear formula planet carrier by outer gear by transmission of power, directly drive to realize mechanical type, when the left oil hydraulic motor of external hydraulic positive direction actuation drives left hydraulic motor gear rotation, and then drive left gear formula gear ring to be rotated in the forward, accelerate the rotating speed of left gear formula planet carrier, otherwise reduce the rotating speed of left gear formula planet carrier, realize the stepless change to left oil hydraulic motor by the control to outside Hydrauservo System, and then realize the stepless change output to left gear formula planet carrier, drive control left gear formula gear ring to realize acceleration or deceleration by left hydraulic motor gear, the mode that right fluid motor-driven control right gear formula gear ring is realized acceleration or deceleration is consistent with left oil hydraulic motor, in the time that 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 move backward to realize endless-track vehicle, in the time that 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, turn to realize to slow-speed of revolution side crawler belt.
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| CN106741171A (en) * | 2017-02-15 | 2017-05-31 | 苏州萨伯工业设计有限公司 | Hydraulic control ratio differential gearing method |
| CN107461461A (en) * | 2017-07-28 | 2017-12-12 | 江苏沃得农业机械配件制造有限公司 | Running on wheels mechanical electro-hydraulic controls gearbox |
| CN113103862A (en) * | 2021-04-10 | 2021-07-13 | 重庆工程职业技术学院 | Crawler-type obstacle crossing vehicle |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105065614A (en) * | 2015-06-25 | 2015-11-18 | 南通黄海药械有限公司 | Hydraulic-drive stepless speed changing gearbox for crawler-type spraying machine |
| CN106741171A (en) * | 2017-02-15 | 2017-05-31 | 苏州萨伯工业设计有限公司 | Hydraulic control ratio differential gearing method |
| CN107461461A (en) * | 2017-07-28 | 2017-12-12 | 江苏沃得农业机械配件制造有限公司 | Running on wheels mechanical electro-hydraulic controls gearbox |
| CN107461461B (en) * | 2017-07-28 | 2023-06-06 | 江苏沃得农业机械配件制造有限公司 | Wheel type walking machinery electrohydraulic control gearbox |
| CN113103862A (en) * | 2021-04-10 | 2021-07-13 | 重庆工程职业技术学院 | Crawler-type obstacle crossing vehicle |
| CN113103862B (en) * | 2021-04-10 | 2022-08-05 | 重庆工程职业技术学院 | Crawler-type obstacle crossing vehicle |
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|---|---|
| CN104141747B (en) | 2015-05-27 |
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