CN204942503U - The endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type - Google Patents
The endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type Download PDFInfo
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- CN204942503U CN204942503U CN201520716982.4U CN201520716982U CN204942503U CN 204942503 U CN204942503 U CN 204942503U CN 201520716982 U CN201520716982 U CN 201520716982U CN 204942503 U CN204942503 U CN 204942503U
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Abstract
The utility model relates to the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type, comprise casing, casing is provided with power input mechanism, double dynamical input mechanism, intermediate transmission and arrestment mechanism, differential speed type driving mechanism, left track driving mechanism, right side track driving mechanism, power take-off mechanism, intermediate transmission and arrestment mechanism are connected by differential speed type driving mechanism and drive left track driving mechanism and right side track driving mechanism.The utility model adopts machinery and the double dynamical input device of hydraulic parallel formula, oil hydraulic motor to control the differential speed type the steering gear of the gear ring clockwise and anticlockwise of driving wheel both sides planetary gears and built-in braking device, effectively can improve endless-track vehicle drive efficiency, manipulation convenience, improve and turn to precision, improve driving safety, overcome existing endless-track vehicle transmission efficiency low, travel that cornering drag is large, manipulation difficulty, the edge of a field turn to and stop up the problems such as serious, the efficient output difference of mud, braking device be complicated.
Description
Technical field
The utility model relates to the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type.
Background technique
Track-laying vehicle for agricultural operation mainly contains cat, crawler-type harvester and crawler farmland transfer vehicle etc.The variable ratio drive system of these endless-track vehicles adopts two types usually, one adopts Purely mechanical power transmission system transferring power, it has, and structure is simple, efficiency advantages of higher, but Purely mechanical power-transmitting unit, gear shift operation is complicated, drive a car or the technical ability of tractor because agricultural machinery operator does not possess usually simultaneously, be difficult to control to the cooperation of clutch, throttle, gearshift, and then limit the development of tractor.Another kind is the endless-track vehicle electrodeless variable-speed drive system adopting oil hydraulic pump-motor integrated device, the endless-track vehicle of electrodeless variable-speed drive system is driven convenience and is improved, agricultural machinery operator need not participate in the technical training of specialty, simple exercise is only needed to grasp driving efficiency, thus like by users, but after adding hydraulic system, drive system efficiency reduces, and heat load increases.Cat particularly in daily production and application process will mount agricultural machinery and implement usually, and agricultural machinery and implement are when farm work, motor is generally in large throttle state, close to constant engine operating mode, travelling speed change is little, power exports larger with moment of torsion, causes that system energy consumption is high, heating value is large, poor high temperature stability, seriously limits the application area of track-laying vehicle.
Simultaneously because the working principle of endless-track vehicle driving system and the travel operation principle of two-wheeled farm machinery are similar, speed changer be usually integrated with turn to, differential, main deceleration, one or more functions such as braking, and at least will integrated turning function.In integrated steering device: what track-laying vehicle in the market adopted steering linkages to operate jaw clutch and multi-disc brake usually turns to scheme, its implementation procedure is: when cat vehicle turn left to time, left side jaw clutch is separated driver's operation left steering pull bar and left side output shaft is braked, because crawler tractor vehicle left side transfer motion power interrupts and brake stopping the rotation, now under the driving of tractor right side power, facility realize turning to the left; In like manner can realize right hand steering, but this steering equipment adopts separation and realizes in conjunction with jaw clutch and break, it turns to precision low, and steering manipulation is poor.In integrated braking, the endless-track vehicle of part farmland operation as cat, crawler-type harvester due to travelling speed slow, after cutting off power, machinery stops fast, does not usually install break.But in order to improve the travel safety of endless-track vehicle, braking device installed by some endless-track vehicles, these braking device are arranged near driving wheel usually, owing to being arranged on transmission system end, braking device often adopts dry type friction disk type break, and brake structure is large, and left and right wheels is arranged symmetrically with, quantity is many, and braking conformity is poor.
Model utility content
The technical problem that the utility model solves is the endless-track vehicle speed changer providing the built-in braking device of a kind of double dynamical input type, to solve the shortcoming in above-mentioned background technology.
The technical problem that the utility model solves realizes by the following technical solutions:
The utility model provides the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type, comprise casing, casing is provided with power input mechanism, double dynamical input mechanism, intermediate transmission and arrestment mechanism, differential speed type driving mechanism, left track driving mechanism, right side track driving mechanism, power take-off mechanism, power is connected with power take-off mechanism through a power input mechanism part, another part is connected with double dynamical input mechanism, power take-off mechanism by transmission of power to external procedure part, double dynamical input mechanism is connected with intermediate transmission and arrestment mechanism, intermediate transmission and arrestment mechanism are connected by differential speed type driving mechanism and drive left track driving mechanism and right side track driving mechanism, wherein:
Described intermediate transmission and arrestment mechanism comprise jack shaft, be arranged on the jack shaft driving gear on jack shaft, reversing shaft, be arranged on the tumbler gear engaged on reversing shaft and with jack shaft driving gear, be arranged on the break of jack shaft one end, described jack shaft one end is installed on casing by the left deep groove ball bearing of jack shaft, and undertaken spacing by jack shaft left end cap, the other end is installed in jack shaft right end cap by the right deep groove ball bearing of jack shaft, the mounting structure at reversing shaft two ends is the same, its one end is installed on casing by reversing shaft deep groove ball bearing, and undertaken spacing by reversing shaft end cap, described break comprises platen, declutch shift shaft, multiple braking steel disc, multiple brake strip, described multiple braking steel disc is arranged on by spline on the inwall of described jack shaft right end cap, parallel to each other and spaced apart, described multiple brake strip is installed on jack shaft by spline, parallel to each other and spaced apart, and each brake strip is all engaged between adjacent two described braking steel discs, described platen is installed on the other end relative with jack shaft right end cap of described multiple braking steel disc, for compress or pine from brake strip, platen is provided with declutch shift shaft,
Described differential speed type driving mechanism comprises differential steering one axle, differential steering jack shaft, differential gear axle, differential steering one axle one end extend out to the outer connecting fluid pressure motor of casing, and be installed on casing by the left deep groove ball bearing of differential one axle, the left deep groove ball bearing of differential one axle is undertaken spacing by differential one axle left end cap, the differential steering one axle the other end is installed on casing by the right deep groove ball bearing of differential one axle, and undertaken spacing by differential one axle right end cap, differential steering one axle is provided with differential steering left side gear and differential steering right side gear; The mounting structure at differential steering jack shaft two ends is the same, and its one end is installed on casing by differential jack shaft deep groove ball bearing, and is undertaken spacing by differential jack shaft end cap; Differential steering jack shaft is provided with differential steering intermediate gear, differential steering intermediate gear side is provided with differential breast wheel sleeve; The mounting structure at differential gear axle two ends is the same, its one end is installed on casing by differential gear axle deep groove ball bearing, and being undertaken spacing by differential gear hubcap, differential gear axle is provided with and is positioned at final gear in the middle of differential gear axle and left side planetary gears, right side planetary gears that structure identical symmetrical with about final gear;
Left side planetary gears comprises the left lateral carrier be sleeved on successively on differential gear axle, left sun gear and left gear ring, left planetary pinion is installed in left lateral carrier by left planetary pinion supporting component circumference is uniform, and engage with the internal gear of left gear ring and left sun gear simultaneously, left lateral carrier is installed on differential gear axle by needle bearing, and left gear ring is installed on differential gear axle by right sliding bearing sleeve two;
Right side planetary gears comprises the right lateral carrier be sleeved on successively on differential gear axle, right sun gear and right gear ring, right planetary pinion is installed in right lateral carrier by right planetary pinion supporting component circumference is uniform, and engage with the internal gear of right gear ring and right sun gear simultaneously, right lateral carrier is installed on differential gear axle by needle bearing, and right gear ring is installed on differential gear axle by right sliding bearing sleeve two;
Left planetary pinion supporting component comprises left planetary pinion back shaft, be sleeved on left sliding bearing sleeve one on left planetary pinion back shaft and left planetary pinion fixing frame; Right planetary pinion supporting component comprises right planetary pinion back shaft, be sleeved on right sliding bearing sleeve one on right planetary pinion back shaft and right planetary pinion fixing frame;
The external toothing of right gear ring engages with differential steering intermediate gear, and differential steering intermediate gear engages with differential steering right side gear, and the external toothing of left gear ring engages with differential steering left side gear, and final gear engages with tumbler gear.
In the utility model, described jack shaft driving gear side is provided with jack shaft drive wheel snap ring and carries out spacing, tumbler gear side is provided with reverse wheel snap ring and carries out spacing, jack shaft right deep groove ball bearing side is provided with midship shaft bearing snap ring and carries out spacing, braking steel disc one end is provided with steel disc snap ring and carries out spacing, the platen the other end is provided with platen snap ring, and jack shaft left end cap, jack shaft right end cap, reversing shaft end cap are fastened by bolts on casing.
In the utility model, in described differential speed type driving mechanism: in differential one axle left end cap, corresponding differential steering one axle place is provided with differential one axle lip-shaped sealed ring and seals; Differential steering left side gear side is provided with differential left gear snap ring and carries out spacing; Differential steering right side gear side is provided with differential right gear snap ring and carries out spacing; Described differential one axle left end cap, differential one axle right end cap, differential jack shaft end cap, differential gear hubcap are all fastened by bolts on casing.
In the utility model, described power input mechanism comprises power and inputs the first axle, PTO power transmission shaft, described power take-off mechanism comprises pto＝power take-off, it is power intake that power inputs first axle one end, and be installed in the first hubcap by the first axle thrust bearing, first hubcap is anchored on casing, the other end is installed on casing by the first axle deep groove ball bearing, first axle deep groove ball bearing side is provided with power input bevel gear, power input wheel sleeve is provided with between power input bevel gear and the first axle deep groove ball bearing, PTO duplex slippage power shift gear is set with between first axle thrust bearing and the first axle deep groove ball bearing, PTO power transmission shaft one end is installed in casing by deep groove ball bearing in deep groove ball bearing before transmission shaft and transmission shaft, and undertaken spacing by transmission shaft outer end cap, and between deep groove ball bearing, PTO duplex power shift gear is installed in deep groove ball bearing and transmission shaft before transmission shaft, the other end is provided with the main deceleration driving gear of PTO, and being installed in casing by deep groove ball bearing after transmission shaft, after transmission shaft, deep groove ball bearing is undertaken spacing by transmission shaft inner end cap, pto＝power take-off one end is installed on casing by the outer deep groove ball bearing of output shaft, and undertaken spacing by output shaft outer end cap, the other end is clutch end, and be installed on casing by deep groove ball bearing in output shaft, in output shaft, deep groove ball bearing side is provided with output shaft inner end cap and carries out spacing, be provided with the main reduction driven gear of PTO between deep groove ball bearing in the outer deep groove ball bearing of output shaft and output shaft, and be provided with main reduction driven wheel sleeve between the main reduction driven gear of PTO and the outer deep groove ball bearing of output shaft.
In the utility model, described double dynamical input mechanism comprises hydrostatic stepless speed variator, the power of being located at casing side and inputs the second axle, power input the 3rd axle, hydrostatic stepless speed variator is provided with hydrostatic stepless speed variator power input shaft and hydrostatic stepless speed variator pto＝power take-off, the end of hydrostatic stepless speed variator power input shaft and hydrostatic stepless speed variator pto＝power take-off stretches in casing, and the end of hydrostatic stepless speed variator pto＝power take-off is provided with hydrostatic stepless speed variator power output gear, power inputs second axle one end and is fixedly connected with hydrostatic stepless speed variator power input shaft, and be installed on casing by the second axle deep groove ball bearing, its the other end is installed on casing by the second axle thrust bearing, power inputs on the second axle and is provided with driven wheel of differential and mechanical shelves driving gear, driven wheel of differential side is provided with driven wheel of differential sleeve, and driven wheel of differential and power input bevel gear and engages, the mounting structure at power input the 3rd axle two ends is the same, its one end is installed on casing by the 3rd axle deep groove ball bearing, and be provided with the 3rd hubcap and carry out spacing, power input the 3rd axle is provided with the stepless shelves gear of the 3rd axle, 3rd shaft mechanical shelves gear and the 3rd axle input gear, 3rd axle stepless gear gear inputs on the 3rd axle by stepless gear wheel sliding bearing sleeve empty set at power, 3rd shaft mechanical gear gear inputs on the 3rd axle by mechanical gear wheel sliding bearing sleeve empty set at power, 3rd axle stepless gear gear one end is provided with tight sleeve, the 3rd axle stepless gear gear the other end is provided with stepless gear wheel sleeve, 3rd axle stepless shelves gear engages with hydrostatic stepless speed variator power output gear, 3rd shaft mechanical shelves gear engages with mechanical shelves driving gear, and between the 3rd axle stepless shelves gear and the 3rd shaft mechanical shelves gear, double dynamical input splined hub is installed, double dynamical input splined hub is provided with combined cover, combined cover is provided with selector fork.
In the utility model, described left track driving mechanism is identical with right side track driving mechanism structure, and it is symmetrical about final gear, left track driving mechanism comprises track drive axle, track drive axle one end is installed on casing by live axle deep groove ball bearing, and actuation gear is installed, live axle deep groove ball bearing is undertaken spacing by live axle end cap, cover and supporting protheca in support are installed outside live axle end cap successively, supporting protheca is arranged on track drive axle by supporting sleeve deep groove ball bearing, the two ends overlapped in support are connected with supporting protheca and live axle end cap respectively, track drive axle the other end connecting band track traveling gear, the left outside gears meshing of the left lateral carrier outer end of actuation gear and differential speed type driving mechanism.
In the utility model, in described power input mechanism: first axle thrust bearing one end is provided with for carrying out the first spacing axle thrust bearing snap ring to the first hubcap, first axle thrust bearing snap ring is hole snap ring, in transmission shaft, deep groove ball bearing one end is provided with deep groove ball bearing snap ring in transmission shaft, and the first hubcap, transmission shaft outer end cap are fastened by bolts on casing; In described power take-off mechanism: be provided with the first Simmer ring sealed for inputting the first axle to power in the first hubcap, be provided with the output shaft seal ring for sealing pto＝power take-off in described output shaft outer end cap, transmission shaft inner end cap, output shaft outer end cap, output shaft inner end cap are fastened by bolts on casing.
In the utility model, in described double dynamical input mechanism: machinery gear driving gear side is provided with machinery gear driving wheel snap ring, hydrostatic stepless speed variator power output gear side is provided with stepless output wheel snap ring, and the 3rd axle input gear one end is provided with the 3rd axle wheel for inputting snap ring; Second hubcap, the 3rd hubcap are fastened by bolts on casing.
In the utility model, in described left track driving mechanism: actuation gear one end is provided with driving wheel snap ring and carries out spacing, be provided with supporting sleeve lip-shaped sealed ring in support protheca and seal, supporting sleeve deep groove ball bearing side is provided with supporting sleeve bearing snap ring; Live axle end cap is fastened by bolts on casing.
Advantage and beneficial effect:
(1) the utility model adopts double dynamical input mechanism, namely mechanical direct-drive and hydraulic stepless transmission are connected in parallel, solve mechanical direct-drive and the problem that the electrodeless formula of hydraulic pressure is combined by Change-over knot trap, effectively improve transmission efficiency high, improve the handling of endless-track vehicle;
(2) the utility model is provided with intermediate transmission and braking system, by brake, when stepping on brake petal, platen compresses braking steel disc and brake strip, jack shaft is made to produce braking, because power between jack shaft and track drive axle is without interruption, therefore intermediate shaft brake, is equal to the braking of track drive axle, be equal to endless-track vehicle braking, because this braking system is arranged on the high speed end of speed changer, therefore structure is little, operates light.
(3) oil hydraulic motor connecting differential steering one axle is provided with in the utility model differential speed type driving mechanism, when oil hydraulic motor is to differential steering one axle input power, power transmission is to gear ring, another strand of power inputs from sun gear simultaneously, due to planetary gears transmission principle, fixing sun gear input forms compound motion with the gear ring of counterturn, makes planet carrier export difference and turns to, thus realize turning to, make the utility model steering manipulation strong.
In a word, the utility model adopts machinery and the double dynamical input device of hydraulic parallel formula, oil hydraulic motor to control the differential speed type the steering gear of the gear ring clockwise and anticlockwise of driving wheel both sides planetary gears and built-in braking device, effectively can improve endless-track vehicle drive efficiency, manipulation convenience, improve and turn to precision, improve driving safety, overcome existing endless-track vehicle transmission efficiency low, travel that cornering drag is large, manipulation difficulty, the edge of a field turn to and stop up the problems such as serious, the efficient output difference of mud, braking device be complicated.
Accompanying drawing explanation
Fig. 1 is the structural representation of preferred embodiment of the present utility model.
Fig. 2 is B-B sectional view in Fig. 1.
Fig. 3 is the structural representation of Fig. 1 medium power input mechanism and power take-off mechanism.
Fig. 4 is the D-D sectional view of Fig. 3.
Fig. 5 is the structural representation of double dynamical input mechanism in Fig. 1.
Fig. 6 is K-K sectional view in Fig. 5.
Fig. 7 is H-H sectional view in Fig. 5.
Fig. 8 is I-I sectional view in Fig. 5.
Fig. 9 is J-J sectional view in Fig. 5.
Figure 10 is the structural representation of intermediate transmission and arrestment mechanism in Fig. 1.
Figure 11 is the A enlarged view in Figure 10.
Figure 12 is the structural representation of differential speed type driving mechanism in Fig. 1.
Figure 13 is E-E sectional view in Figure 11.
Figure 14 is F-F sectional view in Figure 11.
Figure 15 is the structural representation of left track driving mechanism in Fig. 1.
Embodiment
The technological means realized to make the utility model, creation characteristic, reaching object and effect is easy to understand, below in conjunction with concrete diagram, setting forth the utility model further.
See the endless-track vehicle speed changer of the built-in braking device of double dynamical input type of Fig. 1 ~ Fig. 2, it comprises casing X, casing X is provided with power input mechanism P, double dynamical input mechanism S, intermediate transmission and arrestment mechanism M, differential speed type driving mechanism D, left track driving mechanism Q(L), right side track driving mechanism Q(R), power take-off mechanism T, power input mechanism P is connected with double dynamical input mechanism S and power take-off mechanism T, double dynamical input mechanism S is connected with differential speed type driving mechanism D by intermediate transmission and arrestment mechanism M, differential speed type driving mechanism D and left track driving mechanism Q(L), right side track driving mechanism Q(R) connect.Power inputs through power input mechanism P, a part exports through power take-off mechanism T, another part flows to double dynamical input mechanism S, power take-off mechanism T by transmission of power to external procedure part, double dynamical input mechanism S by intermediate transmission and arrestment mechanism M by transmission of power to differential speed type driving mechanism D, then by differential speed type driving mechanism D power exported respectively drive left track driving mechanism Q(L) and right side track driving mechanism Q(R).
Shown in Fig. 3 ~ Fig. 4, power input mechanism P comprises power input bevel gear P1, PTO duplex slippage power shift gear P2, power inputs the first axle P3, power input selector fork P4, PTO duplex power shift gear P5, PTO power transmission shaft P6, also comprise the first axle thrust bearing P7, first hubcap P8, first Simmer ring P9, first axle thrust bearing snap ring P10, first axle deep groove ball bearing P11, power input wheel sleeve P12, deep groove ball bearing P13 before transmission shaft, deep groove ball bearing P14 in transmission shaft, transmission shaft outer end cap P15, deep groove ball bearing snap ring P16 in transmission shaft, power take-off mechanism T comprises the main deceleration driving gear T3 of pto＝power take-off T1, PTO main reduction driven gear T2, PTO, also comprises deep groove ball bearing T8, output shaft inner end cap T9, output shaft seal ring T10, main reduction driven wheel sleeve T11 in deep groove ball bearing T4, transmission shaft inner end cap T5 after transmission shaft, output shaft outer deep groove ball bearing T6, output shaft outer end cap T7, output shaft.
Power inputs the first axle P3 side and is installed in the first hubcap P8 by the first axle thrust bearing P7, first Simmer ring P9 is installed in the first hubcap P8, seal for inputting the first axle P3 to power, first axle thrust bearing snap ring P10 is hole snap ring, it to be installed in the first hubcap P8 and to be positioned at the side of the first axle thrust bearing P7, for carrying out hole to location to the first axle thrust bearing P7.Power inputs the first axle P3 opposite side and is installed on casing X by the first axle deep groove ball bearing P11, the end that this power inputs the first axle P3 opposite side place is provided with power input bevel gear P1, is provided with power input wheel sleeve P12 between power input bevel gear P1 and the first axle deep groove ball bearing P11; PTO duplex slippage power shift gear P2 is installed between the first axle thrust bearing P7 and the first axle deep groove ball bearing P11, PTO duplex slippage power shift gear P2 is fitted with power input selector fork P4.
PTO power transmission shaft P6 one end is arranged on casing X by deep groove ball bearing P14 in deep groove ball bearing P13 before transmission shaft and transmission shaft, before transmission shaft, deep groove ball bearing P13 is installed on casing X, and undertaken spacing by transmission shaft outer end cap P15, in transmission shaft, deep groove ball bearing P14 side is positioned by the shaft shoulder, opposite side is positioned by deep groove ball bearing snap ring P16 in transmission shaft, in transmission shaft, deep groove ball bearing snap ring P16 is axle snap ring, is set with PTO duplex power shift gear P5 before transmission shaft in deep groove ball bearing P13 and transmission shaft between deep groove ball bearing P14; The PTO power transmission shaft P6 the other end is arranged on casing X by deep groove ball bearing T4 after transmission shaft, and is undertaken spacing by transmission shaft inner end cap T5, and the PTO power transmission shaft P6 the other end is also provided with the main deceleration driving gear T3 of PTO.
Pto＝power take-off T1 side is installed on casing X by the outer deep groove ball bearing T6 of output shaft, and is undertaken spacing by output shaft outer end cap T7, pto＝power take-off T1 opposite side is installed on casing X by deep groove ball bearing T8 in output shaft, and undertaken spacing by output shaft inner end cap T9, output shaft seal ring T10 is installed in output shaft outer end cap T7, for sealing pto＝power take-off T1, between deep groove ball bearing T8, the main reduction driven gear T2 of PTO is installed in the outer deep groove ball bearing T6 of output shaft and output shaft, between outer deep groove ball bearing T6 and the PTO main reduction driven gear T2 of output shaft, main reduction driven wheel sleeve T11 is installed, main reduction driven wheel sleeve T11 is used for the axial clearance of motivation of adjustment output shaft T1 and carries out spacing to PTO main reduction driven gear T2.
PTO duplex slippage power shift gear P2 engages with PTO duplex power shift gear P5, and the main reduction driven gear T2 of PTO main deceleration driving gear T3 and PTO engages.
PTO duplex slippage power shift gear P2 inputs on the first axle P3 at power and moves from left to right, high to realize gear, low-grade switching, as shown in Figure 3, for low grade, its drive path is described: the right side gear of PTO duplex slippage power shift gear P2 engages with the right side gear of PTO duplex power shift gear P5 → PTO duplex power shift gear P5 drive PTO power transmission shaft P6 rotate → PTO power transmission shaft P6 drives PTO main deceleration driving gear T3 to rotate transferring power → PTO main deceleration driving gear T3 and PTO main reduction driven gear T2 to engage → the main reduction driven gear T2 of PTO drives pto＝power take-off T1 to rotate, this transmission process entirety is gearing down.
Shown in Fig. 5 ~ Fig. 9, double dynamical input mechanism S comprises hydrostatic stepless speed variator S1, hydrostatic stepless speed variator power input shaft S2, machinery gear driving gear S3, power inputs the second axle S4, driven wheel of differential S5, hydrostatic stepless speed variator power output gear S6, hydrostatic stepless speed variator pto＝power take-off S7, selector fork S8, combined cover S9, double dynamical input splined hub S10, power input the 3rd axle S11, 3rd axle input gear S12, 3rd shaft mechanical gear gear S13, 3rd axle stepless gear gear S14, power inputs the first axle P3, power input bevel gear P1, also comprises the second axle deep groove ball bearing S15, second axle thrust bearing S16, second hubcap S17, second axle lip-shaped sealed ring S18, machinery gear driving wheel snap ring S19, driven wheel of differential sleeve S20, 3rd axle deep groove ball bearing S21, 3rd hubcap S22, machinery gear wheel sliding bearing sleeve S23, stepless gear wheel sliding bearing sleeve S24, tight sleeve S25, stepless gear wheel sleeve S26, 3rd axle wheel for inputting snap ring S27, stepless output wheel snap ring S28, Power output spline S29.
Power inputs bevel gear P1 by power and inputs, and is then passed to intermediate transmission and the arrestment mechanism M of speed changer by this device.
Hydrostatic stepless speed variator S1 is arranged on casing X side, hydrostatic stepless speed variator S1 comprises hydrostatic stepless speed variator power input shaft S2 and hydrostatic stepless speed variator pto＝power take-off S7, hydrostatic stepless speed variator pto＝power take-off S7 end is provided with hydrostatic stepless speed variator power output gear S6, and adopts stepless output wheel snap ring S28 to carry out spacing.Power inputs second axle S4 one end and is connected with hydrostatic stepless speed variator power input shaft S2, and is arranged on casing X by the second axle deep groove ball bearing S15; Power inputs the second axle S4 the other end and is provided with Power output spline S29, and be arranged on casing X by the second axle thrust bearing S16, Power output spline S29 can external oil hydraulic pump, water pump, endless-track vehicle self-saving device or other equipments, further expand the function of endless-track vehicle, second axle thrust bearing S16 is undertaken spacing by the second hubcap S17, is provided with the second axle lip-type packing S18 and seals in the second hubcap S17; Power inputs the second axle S4 and is provided with machinery gear driving gear S3 and driven wheel of differential S5, machinery gear driving gear S3 carries out axial limiting by machinery gear driving wheel snap ring S19, driven wheel of differential S5 be arranged on power input on the first axle P3 power input bevel gear P1 and engage, be provided with driven wheel of differential sleeve S20 between driven wheel of differential S5 and the second axle thrust bearing S16, driven wheel of differential sleeve S20 is used for carrying out spacing to driven wheel of differential S5.
The mounting structure at power input the 3rd axle S11 two ends is the same, and its one end is installed on casing X by the 3rd axle deep groove ball bearing S21, and is undertaken spacing by the 3rd hubcap S22, power input the 3rd axle S11 is also provided with the 3rd axle stepless gear gear S14 vertically successively, double dynamical input splined hub S10, 3rd shaft mechanical gear gear S13, 3rd axle input gear S12, 3rd axle stepless gear gear S14 inputs on the 3rd axle S11 by stepless gear wheel sliding bearing sleeve S24 empty set at power, 3rd shaft mechanical gear gear S13 inputs on the 3rd axle S11 by mechanical gear wheel sliding bearing sleeve S23 empty set at power, 3rd axle stepless gear gear S14 engages with hydrostatic stepless speed variator power output gear S6, 3rd shaft mechanical gear gear S13 keeps off driving gear S3 with machinery and engages, tight sleeve S25 is provided with between 3rd axle stepless gear gear S14 and double dynamical input splined hub S10,3rd axle stepless gear gear S14 opposite side is provided with stepless gear wheel sleeve S26, double dynamical input splined hub S10 is provided with combined cover S9, combined cover S9 is fitted with selector fork S8, 3rd axle input gear S12 is undertaken spacing by the 3rd axle wheel for inputting snap ring S27.
Working principle:
1) upward sliding selector fork S8, combined cover S9 moves, combined cover S9 is separately fixed on double dynamical input splined hub S10 and the 3rd axle stepless gear gear S14, power is passed to the 3rd axle stepless gear gear S14 by hydrostatic stepless speed variator power output gear S6, be passed to double dynamical input splined hub S10 again, be then passed to the 3rd axle input gear S12.Now speed changer is hydrostatic stepless gear, the exportable infinite variable speed forward gear of speed changer and reverse gear shift.
2) slide downward selector fork S8, combined cover S9 moves down, combined cover S9 is separately fixed at double dynamical input splined hub S10 and the 3rd shaft mechanical keeps off on gear S13, power keeps off driving gear S3 by machinery and is passed to the 3rd shaft mechanical gear gear S13, be passed to double dynamical input splined hub S10 again, be then passed to the 3rd axle input gear S12.Now speed changer is machinery gear, and the forward gear exporting a certain speed fixed by speed changer, can not export reverse gear shift, and this gear is mainly used in track-laying vehicle field high-efficient homework.
The utility model adopts double dynamical input, comprise machinery gear and hydrostatic electrodeless gear two keep off power transmission route.
The drive path of machinery gear power is: power input on the first axle P3 power input bevel gear P1 and driven wheel of differential S5 → driven wheel of differential S5 drive power to input the second axle S4 to rotate transferring power → machinery and keep off driving gear S3 and rotate → tool keeps off driving gear S3 to be kept off gear S13 with the 3rd shaft mechanical and engages → the 3rd shaft mechanical keeps off gear S13 and drive power to input the 3rd axle S11 to rotate → power inputs the 3rd axle S11 and drive the 3rd axle input gear S12 to rotate the → the three axle input gear S12 by transmission of power to intermediate transmission and arrestment mechanism M.
The drive path of hydrostatic electrodeless gear power is: power input on the first axle P3 power input bevel gear P1 and driven wheel of differential S5 → driven wheel of differential S5 drive power to input the second axle S4 to rotate transferring power → power and transmit into hydrostatic stepless speed variator S1 stepless change from hydrostatic stepless speed variator power input shaft S2, then from hydrostatic stepless speed variator pto＝power take-off S7 output → hydrostatic stepless speed variator pto＝power take-off S7 drive hydrostatic stepless speed variator power output gear S6 rotation → hydrostatic stepless speed variator power output gear S6 engage with the 3rd axle stepless gear gear S14 → the 3rd axle stepless gear gear S14 drives power to input the 3rd axle S11 to rotate → power inputs the 3rd axle S11 and drive the 3rd axle input gear S12 to rotate the → the three axle input gear S12 by transmission of power to intermediate transmission and arrestment mechanism M.
Shown in Figure 10 ~ Figure 11, intermediate transmission and arrestment mechanism M comprise jack shaft M1, jack shaft driving gear M2, break M3, reversing shaft M4, tumbler gear M5, also comprise the left deep groove ball bearing M6 of jack shaft, jack shaft left end cap M7, the right deep groove ball bearing M8 of jack shaft, jack shaft right end cap M9, reversing shaft deep groove ball bearing M10, reversing shaft end cap M11, jack shaft drive wheel snap ring M12, reverse wheel snap ring M13, steel disc snap ring M14, platen snap ring M15, midship shaft bearing snap ring M16, platen M31, declutch shift shaft M32, braking steel disc M33, brake strip M34.
Jack shaft M1 one end is installed on casing by the left deep groove ball bearing M6 of jack shaft, and undertaken spacing by jack shaft left end cap M7, the other end is installed in jack shaft right end cap M9 by the right deep groove ball bearing M8 of jack shaft, and break M3 is installed in jack shaft right end cap M9; The mounting structure at reversing shaft M4 two ends is the same, and its one end is installed on casing by reversing shaft deep groove ball bearing M10, and is undertaken spacing by reversing shaft end cap M11.Jack shaft driving gear M2 is installed on jack shaft M1, and tumbler gear M5 is installed on reversing shaft M4, and intermediate drive gear M2 engages with tumbler gear M5.Jack shaft driving gear side is provided with jack shaft drive wheel snap ring M12 and carries out spacing, and tumbler gear M5 side is provided with reverse wheel snap ring M13 and carries out spacing, and jack shaft right deep groove ball bearing M8 side is provided with midship shaft bearing snap ring M16 and carries out spacing.
Break M3 comprises platen M31, declutch shift shaft M32, six braking steel disc M33, five brake strip M34, six braking steel disc M33 are arranged on the inwall of described jack shaft right end cap M9, these six braking steel disc M33 are parallel to each other and spaced apart, five brake strip M34 are installed on jack shaft M1, parallel to each other and spaced apart, and each brake strip M34 is all engaged between adjacent two braking steel disc M33; Braking steel disc M33 one end is provided with steel disc snap ring M14 and carries out spacing, also be provided with the platen M31 be arranged on jack shaft M1, platen M31 is provided with declutch shift shaft M32, declutch shift shaft M32 for control platen M31 and compress or pine from braking steel disc M33, the platen M31 the other end is provided with platen snap ring M15.
Brake strip M34 is arranged on the external splines of jack shaft M1 by internal spline, five brake strip M34 can move in the axial direction on jack shaft M1, can not freely rotate, mobile ultimate range limits by the location end face of platen snap ring M15, braking steel disc M33 and jack shaft right end cap M9.Braking steel disc M33 is arranged on by external splines on the internal spline of jack shaft right end cap M9, braking steel disc M33 can move in the axial direction on jack shaft right end cap M9, can not freely rotate, mobile ultimate range limits by the location end face on steel disc snap ring M14 and jack shaft right end cap M9.
The working principle of break M3:
Produce braking: step on brake petal, declutch shift shaft M32 rotates counterclockwise, and declutch shift shaft M32 makes platen M31 move down, platen M31 compresses braking steel disc M33 and brake strip M34.Because brake strip M34 freely can not rotate, brake steel disc M33 and freely can not rotate in jack shaft right end cap M9 circumference in jack shaft M1 circumference.When the frictional force that platen M31 compresses braking steel disc M33 and brake strip M34 is greater than jack shaft driving force, jack shaft M1 produces braking.Because power between jack shaft M1 and track drive axle Q1 is without interruption, therefore jack shaft M1 brakes, and is equal to track drive axle Q1 and brakes, and is equal to endless-track vehicle braking.Because this braking system is arranged on the high speed end of speed changer, therefore structure is little, operates light.
Brake off: loosen the brake, declutch shift shaft M32 return, braking steel disc M33 and brake strip M34 produces gap, zerofriction force between braking steel disc M33 and brake strip M34, brake release.
Shown in Figure 12 ~ Figure 14, differential speed type driving mechanism D comprises differential steering one axle D1, differential steering left side gear D2, differential steering right side gear D3, differential steering intermediate gear D4, differential steering jack shaft D5, final gear D6, differential gear axle D7, right side planetary gears D8, left side planetary gears D9, also comprise the left deep groove ball bearing D10 of differential one axle, differential one axle left end cap D11, differential one axle lip-shaped sealed ring D12, the right deep groove ball bearing D13 of differential one axle, differential one axle right end cap D14, differential left gear snap ring D15, differential right gear snap ring D16, differential jack shaft deep groove ball bearing D17, differential jack shaft end cap D18, differential breast wheel sleeve D19, differential gear axle deep groove ball bearing D20, differential gear hubcap D21, right sliding bearing sleeve one D22, needle bearing D23, right sliding bearing sleeve two D24, left sliding bearing sleeve one D25, needle bearing D26, left sliding bearing sleeve two D27.
Differential steering one axle D1 one end extend out to outside casing X, be connected with oil hydraulic motor, and be installed on casing X by the left deep groove ball bearing D10 of differential one axle, differential one axle left deep groove ball bearing D10 is undertaken spacing by differential one axle left end cap D11, and in differential one axle left end cap D11, corresponding differential steering one axle D1 place is provided with differential one axle lip-shaped sealed ring D12 and seals; The differential steering one axle D1 the other end is installed on casing X by the right deep groove ball bearing D13 of differential one axle, and is undertaken spacing by differential one axle right end cap D14; Differential steering one axle D1 is provided with differential steering left side gear D2 and differential steering right side gear D3, differential steering left side gear D2 side is provided with differential left gear snap ring D15 and carries out spacing, and differential steering right side gear D3 side is provided with differential right gear snap ring D16 and carries out spacing.
The mounting structure at differential steering jack shaft D5 two ends is the same, and its one end is installed on casing X by differential jack shaft deep groove ball bearing D17, and is undertaken spacing by differential jack shaft end cap D18; Differential steering jack shaft D5 is provided with differential steering intermediate gear D4, differential steering intermediate gear D4 side is provided with differential breast wheel sleeve D19.Differential steering intermediate gear D4 engages with differential steering right side gear D3.
The mounting structure at differential gear axle D7 two ends is the same, and its one end is installed on casing X by differential gear axle deep groove ball bearing D20, and is undertaken spacing by differential gear hubcap D21; Position, differential gear axle D7 middle is provided with final gear D6, and final gear D6 engages with the tumbler gear M5 of intermediate transmission and arrestment mechanism M; Planetary gears D9 is identical with the structure of right side planetary gears D8 in left side, and symmetrical about final gear D6.
Left side planetary gears D9 comprises left sun gear D91, left lateral carrier D92, left lateral star gear D 93, left planetary pinion back shaft D94, left gear ring D95, left planetary pinion fixing frame D96, also comprises left sliding bearing sleeve one D25, needle bearing D26, left sliding bearing sleeve two D27.
Right side planetary gears D8 comprises right sun gear D81, right lateral carrier D82, right lateral star gear D 83, right planetary pinion back shaft D84, right gear ring D85, right planetary pinion fixing frame D86, also comprises right sliding bearing sleeve one D22, needle bearing D23, right sliding bearing sleeve two D24.
Left gear ring D95, left sun gear D91 and left lateral carrier D92 are arranged on differential gear axle D7 successively, left lateral star gear D 93 is installed on left lateral carrier D92 by left planetary pinion supporting component circumference is uniform, engages with the internal gear of left gear ring D95 and left sun gear D91 simultaneously; Left planetary pinion supporting component comprises left planetary pinion back shaft D94, be sleeved on left sliding bearing sleeve one D25 on left planetary pinion back shaft D94 and left planetary pinion fixing frame D96, left lateral carrier D92 is installed on differential gear axle D7 by needle bearing D26, and left gear ring D95 is installed on differential gear axle D7 by right sliding bearing sleeve two D27.The external gear of left gear ring D95 engages with differential steering left side gear D2.
Right gear ring D85, right sun gear D81 and right lateral carrier D82 are sleeved on differential gear axle D7 successively, right lateral star gear D 83 is installed on right lateral carrier D82 by right planetary pinion supporting component circumference is uniform, and engages with the internal gear of right gear ring D85 and right sun gear D81 simultaneously; Right planetary pinion supporting component comprises right planetary pinion back shaft D84, be sleeved on right sliding bearing sleeve one D22 on right planetary pinion back shaft D84 and right planetary pinion fixing frame D86, right lateral carrier D82 is installed on differential gear axle D7 by needle bearing D23, and right gear ring D85 is installed on differential gear axle D7 by right sliding bearing sleeve two D24.The external gear of right gear ring D85 engages with differential steering intermediate gear D4.
The working principle of differential speed type driving mechanism D:
Power is imported into by the differential gear axle D7 at final gear D6 and final gear D6 place, is then passed to the left sun gear D91 of both sides, right sun gear D81.Left sun gear D91 is by left lateral star gear D 93 by transmission of power extremely left gear ring D95, and left planetary pinion back shaft D94 is by transmission of power to left lateral carrier D92, and left lateral carrier D92 outer end is provided with left outside gear, the outer outputting power of left outside gear mesh.Right sun gear D81 is by right lateral star gear D 83 by transmission of power extremely right gear ring D85, and right planetary pinion back shaft D84 is by transmission of power to right lateral carrier D82, and right lateral carrier D82 outer end is provided with right outside gear, the outer outputting power of right outside gear mesh.Right gear ring D85 outer ring is provided with external toothing and engages with differential steering intermediate gear D4, and left gear ring D95 outer ring is provided with external toothing and engages with differential steering left side gear D2, constitutes planetary gears and drives the differential steering system turned to hydraulic driving.
Constant speed locking exports: the differential steering left side gear D2 of differential steering one axle D1 engages with the left gear ring D95 on the D9 of left side planetary gears.The differential steering right side gear D3 of differential steering one axle D1 engages with differential steering intermediate gear D4, then engages with the right gear ring D85 on the planetary gears D8 of right side.When oil hydraulic motor input unpowered to differential steering one axle D1, now from the power of sun gear input, this power divides two-way to export from external toothing and planet carrier respectively, because left and right side planetary carrier gear ring is fixed by rightabout steering gear, now differential steering device locking, left and right side planetary pinion equispeed output.
Differential steering exports: when oil hydraulic motor input dynamic to differential steering one axle D1, the left gear ring D95 on the D9 of left side planetary gears turns to contrary with the right gear ring D85 on the planetary gears D8 of right side.According to planetary gears transmission principle, fixing sun gear input forms compound motion with the gear ring of counterturn, makes planet carrier export difference and turns to, thus realize turning to.
Shown in Figure 15, left track driving mechanism Q(L) comprise in track drive axle Q1, support protheca Q2, support and overlap Q3, actuation gear Q4, also comprise live axle deep groove ball bearing Q5, driving wheel snap ring Q6, live axle end cap Q7, supporting sleeve deep groove ball bearing Q8, supporting sleeve lip-shaped sealed ring Q9, supporting sleeve bearing snap ring Q10.
Track drive axle Q1 one end is installed on casing X by live axle deep groove ball bearing Q5, and actuation gear Q4 is installed, actuation gear Q4 end is provided with driving wheel snap ring Q6 and carries out spacing, live axle deep groove ball bearing Q5 is undertaken spacing by live axle end cap Q7, be provided with successively in support outside live axle end cap Q7 and overlap Q3 and supporting protheca Q2, supporting protheca Q2 is arranged on track drive axle Q1 by supporting sleeve deep groove ball bearing Q8, and be provided with supporting sleeve lip-shaped sealed ring Q9 and seal, supporting sleeve deep groove ball bearing Q8 side is provided with supporting sleeve bearing snap ring Q10, the two ends overlapping Q3 in support are connected with supporting protheca Q2 and live axle end cap Q7 respectively, track drive axle Q1 the other end connecting band track traveling gear.The left outside gears meshing of the left lateral carrier D92 outer end of actuation gear Q4 and differential speed type driving mechanism D.
Right side track driving mechanism Q(R) with left track driving mechanism Q(L) structure communicates, and is symmetrical arranged about final gear D6.Differential speed type driving mechanism D connects and drives left track driving mechanism Q(L) and right side track driving mechanism Q(R).
More than show and describe basic principle of the present utility model and major character and advantage of the present utility model.The technician of the industry should understand; the utility model is not restricted to the described embodiments; what describe in above-described embodiment and specification just illustrates principle of the present utility model; under the prerequisite not departing from the utility model spirit and scope; the utility model also has various changes and modifications, and these changes and improvements all fall within the scope of claimed the utility model.The claimed scope of the utility model is defined by appending claims and equivalent thereof.
Claims (9)
1. the endless-track vehicle speed changer of the built-in braking device of double dynamical input type, comprise casing, it is characterized in that, casing is provided with power input mechanism, double dynamical input mechanism, intermediate transmission and arrestment mechanism, differential speed type driving mechanism, left track driving mechanism, right side track driving mechanism, power take-off mechanism, power is connected with power take-off mechanism through a power input mechanism part, another part is connected with double dynamical input mechanism, power take-off mechanism by transmission of power to external procedure part, double dynamical input mechanism is connected with intermediate transmission and arrestment mechanism, intermediate transmission and arrestment mechanism are connected by differential speed type driving mechanism and drive left track driving mechanism and right side track driving mechanism, wherein:
Described intermediate transmission and arrestment mechanism comprise jack shaft, be arranged on the jack shaft driving gear on jack shaft, reversing shaft, be arranged on the tumbler gear engaged on reversing shaft and with jack shaft driving gear, be arranged on the break of jack shaft one end, described jack shaft one end is installed on casing by the left deep groove ball bearing of jack shaft, and undertaken spacing by jack shaft left end cap, the other end is installed in jack shaft right end cap by the right deep groove ball bearing of jack shaft, the mounting structure at reversing shaft two ends is the same, its one end is installed on casing by reversing shaft deep groove ball bearing, and undertaken spacing by reversing shaft end cap, described break comprises platen, declutch shift shaft, multiple braking steel disc, multiple brake strip, described multiple braking steel disc is arranged on by spline on the inwall of described jack shaft right end cap, parallel to each other and spaced apart, described multiple brake strip is installed on jack shaft by spline, parallel to each other and spaced apart, and each brake strip is all engaged between adjacent two described braking steel discs, described platen is installed on the other end relative with jack shaft right end cap of described multiple braking steel disc, for compress or pine from brake strip, platen is provided with declutch shift shaft,
Described differential speed type driving mechanism comprises differential steering one axle, differential steering jack shaft, differential gear axle, differential steering one axle one end extend out to the outer connecting fluid pressure motor of casing, and be installed on casing by the left deep groove ball bearing of differential one axle, the left deep groove ball bearing of differential one axle is undertaken spacing by differential one axle left end cap, the differential steering one axle the other end is installed on casing by the right deep groove ball bearing of differential one axle, and undertaken spacing by differential one axle right end cap, differential steering one axle is provided with differential steering left side gear and differential steering right side gear; The mounting structure at differential steering jack shaft two ends is the same, and its one end is installed on casing by differential jack shaft deep groove ball bearing, and is undertaken spacing by differential jack shaft end cap; Differential steering jack shaft is provided with differential steering intermediate gear, differential steering intermediate gear side is provided with differential breast wheel sleeve; The mounting structure at differential gear axle two ends is the same, its one end is installed on casing by differential gear axle deep groove ball bearing, and being undertaken spacing by differential gear hubcap, differential gear axle is provided with and is positioned at final gear in the middle of differential gear axle and left side planetary gears, right side planetary gears that structure identical symmetrical with about final gear;
Left side planetary gears comprises the left lateral carrier be sleeved on successively on differential gear axle, left sun gear and left gear ring, left planetary pinion is installed in left lateral carrier by left planetary pinion supporting component circumference is uniform, and engage with the internal gear of left gear ring and left sun gear simultaneously, left lateral carrier is installed on differential gear axle by needle bearing, and left gear ring is installed on differential gear axle by right sliding bearing sleeve two;
Right side planetary gears comprises the right lateral carrier be sleeved on successively on differential gear axle, right sun gear and right gear ring, right planetary pinion is installed in right lateral carrier by right planetary pinion supporting component circumference is uniform, and engage with the internal gear of right gear ring and right sun gear simultaneously, right lateral carrier is installed on differential gear axle by needle bearing, and right gear ring is installed on differential gear axle by right sliding bearing sleeve two;
Left planetary pinion supporting component comprises left planetary pinion back shaft, be sleeved on left sliding bearing sleeve one on left planetary pinion back shaft and left planetary pinion fixing frame; Right planetary pinion supporting component comprises right planetary pinion back shaft, be sleeved on right sliding bearing sleeve one on right planetary pinion back shaft and right planetary pinion fixing frame;
The external toothing of right gear ring engages with differential steering intermediate gear, and differential steering intermediate gear engages with differential steering right side gear, and the external toothing of left gear ring engages with differential steering left side gear, and final gear engages with tumbler gear.
2. the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type according to claim 1, it is characterized in that, described jack shaft driving gear side is provided with jack shaft drive wheel snap ring and carries out spacing, tumbler gear side is provided with reverse wheel snap ring and carries out spacing, jack shaft right deep groove ball bearing side is provided with midship shaft bearing snap ring and carries out spacing, braking steel disc one end is provided with steel disc snap ring and carries out spacing, the platen the other end is provided with platen snap ring, and jack shaft left end cap, jack shaft right end cap, reversing shaft end cap are fastened by bolts on casing.
3. the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type according to claim 1, it is characterized in that, in described differential speed type driving mechanism: in differential one axle left end cap, corresponding differential steering one axle place is provided with differential one axle lip-shaped sealed ring and seals; Differential steering left side gear side is provided with differential left gear snap ring and carries out spacing; Differential steering right side gear side is provided with differential right gear snap ring and carries out spacing; Described differential one axle left end cap, differential one axle right end cap, differential jack shaft end cap, differential gear hubcap are all fastened by bolts on casing.
4. the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type according to claim 1, it is characterized in that, described power input mechanism comprises power and inputs the first axle, PTO power transmission shaft, described power take-off mechanism comprises pto＝power take-off, it is power intake that power inputs first axle one end, and be installed in the first hubcap by the first axle thrust bearing, first hubcap is anchored on casing, the other end is installed on casing by the first axle deep groove ball bearing, first axle deep groove ball bearing side is provided with power input bevel gear, power input wheel sleeve is provided with between power input bevel gear and the first axle deep groove ball bearing, PTO duplex slippage power shift gear is set with between first axle thrust bearing and the first axle deep groove ball bearing, PTO power transmission shaft one end is installed in casing by deep groove ball bearing in deep groove ball bearing before transmission shaft and transmission shaft, and undertaken spacing by transmission shaft outer end cap, and between deep groove ball bearing, PTO duplex power shift gear is installed in deep groove ball bearing and transmission shaft before transmission shaft, the other end is provided with the main deceleration driving gear of PTO, and being installed in casing by deep groove ball bearing after transmission shaft, after transmission shaft, deep groove ball bearing is undertaken spacing by transmission shaft inner end cap, pto＝power take-off one end is installed on casing by the outer deep groove ball bearing of output shaft, and undertaken spacing by output shaft outer end cap, the other end is clutch end, and be installed on casing by deep groove ball bearing in output shaft, in output shaft, deep groove ball bearing side is provided with output shaft inner end cap and carries out spacing, be provided with the main reduction driven gear of PTO between deep groove ball bearing in the outer deep groove ball bearing of output shaft and output shaft, and be provided with main reduction driven wheel sleeve between the main reduction driven gear of PTO and the outer deep groove ball bearing of output shaft.
5. the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type according to claim 4, it is characterized in that, in described power input mechanism: first axle thrust bearing one end is provided with for carrying out the first spacing axle thrust bearing snap ring to the first hubcap, first axle thrust bearing snap ring is hole snap ring, in transmission shaft, deep groove ball bearing one end is provided with deep groove ball bearing snap ring in transmission shaft, and the first hubcap, transmission shaft outer end cap are fastened by bolts on casing; In described power take-off mechanism: be provided with the first Simmer ring sealed for inputting the first axle to power in the first hubcap, be provided with the output shaft seal ring for sealing pto＝power take-off in described output shaft outer end cap, transmission shaft inner end cap, output shaft outer end cap, output shaft inner end cap are fastened by bolts on casing.
6. the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type according to claim 1, it is characterized in that, described double dynamical input mechanism comprises the hydrostatic stepless speed variator being located at casing side, power inputs the second axle, power input the 3rd axle, hydrostatic stepless speed variator is provided with hydrostatic stepless speed variator power input shaft and hydrostatic stepless speed variator pto＝power take-off, the end of hydrostatic stepless speed variator power input shaft and hydrostatic stepless speed variator pto＝power take-off stretches in casing, and the end of hydrostatic stepless speed variator pto＝power take-off is provided with hydrostatic stepless speed variator power output gear, power inputs second axle one end and is fixedly connected with hydrostatic stepless speed variator power input shaft, and be installed on casing by the second axle deep groove ball bearing, its the other end is installed on casing by the second axle thrust bearing, power inputs on the second axle and is provided with driven wheel of differential and mechanical shelves driving gear, driven wheel of differential side is provided with driven wheel of differential sleeve, and driven wheel of differential and power input bevel gear and engages, the mounting structure at power input the 3rd axle two ends is the same, its one end is installed on casing by the 3rd axle deep groove ball bearing, and be provided with the 3rd hubcap and carry out spacing, power input the 3rd axle is provided with the stepless shelves gear of the 3rd axle, 3rd shaft mechanical shelves gear and the 3rd axle input gear, 3rd axle stepless gear gear inputs on the 3rd axle by stepless gear wheel sliding bearing sleeve empty set at power, 3rd shaft mechanical gear gear inputs on the 3rd axle by mechanical gear wheel sliding bearing sleeve empty set at power, 3rd axle stepless gear gear one end is provided with tight sleeve, the 3rd axle stepless gear gear the other end is provided with stepless gear wheel sleeve, 3rd axle stepless shelves gear engages with hydrostatic stepless speed variator power output gear, 3rd shaft mechanical shelves gear engages with mechanical shelves driving gear, and between the 3rd axle stepless shelves gear and the 3rd shaft mechanical shelves gear, double dynamical input splined hub is installed, double dynamical input splined hub is provided with combined cover, combined cover is provided with selector fork.
7. the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type according to claim 6, it is characterized in that, in described double dynamical input mechanism: machinery gear driving gear side is provided with machinery gear driving wheel snap ring, hydrostatic stepless speed variator power output gear side is provided with stepless output wheel snap ring, and the 3rd axle input gear one end is provided with the 3rd axle wheel for inputting snap ring; Second hubcap, the 3rd hubcap are fastened by bolts on casing.
8. the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type according to claim 1, it is characterized in that, described left track driving mechanism is identical with right side track driving mechanism structure, and it is symmetrical about final gear, left track driving mechanism comprises track drive axle, track drive axle one end is installed on casing by live axle deep groove ball bearing, and actuation gear is installed, live axle deep groove ball bearing is undertaken spacing by live axle end cap, cover and supporting protheca in support are installed outside live axle end cap successively, supporting protheca is arranged on track drive axle by supporting sleeve deep groove ball bearing, the two ends overlapped in support are connected with supporting protheca and live axle end cap respectively, track drive axle the other end connecting band track traveling gear, the left outside gears meshing of the left lateral carrier outer end of actuation gear and differential speed type driving mechanism.
9. the endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type according to claim 8, it is characterized in that, in described left track driving mechanism: actuation gear one end is provided with driving wheel snap ring and carries out spacing, be provided with supporting sleeve lip-shaped sealed ring in support protheca to seal, supporting sleeve deep groove ball bearing side is provided with supporting sleeve bearing snap ring; Live axle end cap is fastened by bolts on casing.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520716982.4U CN204942503U (en) | 2015-09-16 | 2015-09-16 | The endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520716982.4U CN204942503U (en) | 2015-09-16 | 2015-09-16 | The endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type |
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| CN204942503U true CN204942503U (en) | 2016-01-06 |
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| CN201520716982.4U Expired - Fee Related CN204942503U (en) | 2015-09-16 | 2015-09-16 | The endless-track vehicle speed changer of the built-in braking device of a kind of double dynamical input type |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105042049A (en) * | 2015-09-16 | 2015-11-11 | 湖南农业大学 | Dual-power-input type crawler vehicle speed changer with built-in braking device |
| CN114396462A (en) * | 2022-01-21 | 2022-04-26 | 浙江云洲科技有限公司 | Novel mechanical flexible steering stepless gearbox |
-
2015
- 2015-09-16 CN CN201520716982.4U patent/CN204942503U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105042049A (en) * | 2015-09-16 | 2015-11-11 | 湖南农业大学 | Dual-power-input type crawler vehicle speed changer with built-in braking device |
| CN114396462A (en) * | 2022-01-21 | 2022-04-26 | 浙江云洲科技有限公司 | Novel mechanical flexible steering stepless gearbox |
| CN114396462B (en) * | 2022-01-21 | 2023-11-14 | 浙江云洲科技有限公司 | Novel mechanical flexible steering stepless gearbox |
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Granted publication date: 20160106 Termination date: 20160916 |