CN103982652B - Power transfer confluxes variable speed drive - Google Patents

Power transfer confluxes variable speed drive Download PDF

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Publication number
CN103982652B
CN103982652B CN201410248722.9A CN201410248722A CN103982652B CN 103982652 B CN103982652 B CN 103982652B CN 201410248722 A CN201410248722 A CN 201410248722A CN 103982652 B CN103982652 B CN 103982652B
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China
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gear
hydraulic
oil
output shaft
valve
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CN103982652A (en
Inventor
孙保群
汪韶杰
常佳男
陆军
彭建刚
夏光
曲凯宁
李磊
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Hefei University of Technology
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Hefei University of Technology
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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
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4078—Fluid exchange between hydrostatic circuits and external sources or consumers
    • F16H61/4096—Fluid exchange between hydrostatic circuits and external sources or consumers with pressure accumulators
    • 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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • 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
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F16H61/431—Pump capacity control by electro-hydraulic control means, e.g. using solenoid valves

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The present invention relates to a kind of power transfer conflux variable speed drive and hydraulic control system thereof.This system is made up of machinery transfer case transmission mechanism and hydraulic drive governor motion；Described machinery transfer case transmission mechanism is made up of transfer gear TD and variable transmission mechanism, and wherein, transfer gear TD is planetary wheeling mechanism；Described hydraulic drive governor motion is made up of than governor motion RC hydraulic pressure drive control system mechanism and hydraulic drive.Machinery transfer case transmission mechanism has the power that two outfans are automatically shunted by the size according to working resistance suffered by two outfans and is adjusted assignment characteristic, input power in transmission process can be realized and with output power, there is the function carrying out stepless speed regulation within the specific limits, effectively promote the overall efficiency of vehicle drive system；When vehicle start and anxious acceleration, by strengthening the power of hydraulic drive shunting transmission and transmitting with big speed ratio, vehicle smooth-going can be made to start to walk and quickly improve speed.

Description

Power transfer confluxes variable speed drive
Technical field
The invention belongs to vehicle drive system, being specifically related to a kind of by input power mechanically and hydraulically being shunted transmission After realize power speed changing actuating device and the hydraulic control system thereof that power confluxes again.
Background technology
Variable ratio drive system is the important component part that vehicle is indispensable.According to power delivery mode, modern vehicle is conventional The drive systems such as the predominantly organic tool gear of employing, hydraulic drive, electric transmission.
Machine driven system is the power train formed with speed change gear with electromotor as power, with all kinds mechanical mechanism System, is characterized in that technology maturation, manufacturing process are perfect, production cost is low, drive system efficiency is high, be widely used, but with send out The Optimized Matching of motivation is difficult to the most effectively be promoted.
Hydraulic Power Transmission System is also called hydrostatic transmission system, is with hydraulic pump, hydraulic motor, hydraulic servocontrol and execution The power drive system of the composition such as actuation element and fluid pressure line, is characterized in transmitting power by hydraulic way, and system mechanics passes Dynamic component is few, simple in construction, gear ratio excursion big and can easily be accommodated, operate steadily, vibration noise is little, control is relative Easily and electrodeless variable-speed can be realized, but should not fast row too high, middle and high to vehicle as the hydraulic motor working speed driving element Transmission when sailing operating mode requires that adaptability is relatively poor.
Electric drive system is the drive system formed with simple mechanical mechanism with electric power as the energy, with motor, its feature Be that drive system structure is relatively easy, vibration noise and disposal of pollutants little, but under current technical conditions, use electric drive system Vehicle course continuation mileage limited, be difficult to meet user's request.
Additionally, the mixing such as also oil electric mixed dynamic transmission, extended-range electricity oil hybrid transmission, fuel-electro double mode formula transmission Or compound power drive system, wherein, oil electric mixed dynamic drive system energy-saving effect substantially but control to require high, system is multiple Miscellaneous, involve great expense, extended-range electricity oil hybrid drive system and fuel-electro double mode formula drive system the most all exist and electric powertrain The problem that identical course continuation mileage of uniting is limited.
Summary of the invention
The present invention provides a kind of power transfer to conflux variable speed drive and hydraulic control system thereof, its purpose is to more Effectively utilize the power of electromotor output, make full use of and play mechanical speed change transmission efficiency height, the change of hydraulic drive gear ratio Scope is big and is easy to the feature of regulation, makes that vehicle drive system is relatively easy, speed change is easy and more efficient, energy-conservation and environmental protection.
Power transfer confluxes variable speed drive and hydraulic control system thereof by machinery transfer case transmission mechanism and hydraulic drive regulation Mechanism forms；Described machinery transfer case transmission mechanism is made up of transfer gear TD and variable transmission mechanism, and described hydraulic drive regulates Mechanism is made up of than governor motion RC hydraulic pressure drive control system mechanism and hydraulic drive；
The size of working resistance suffered by two outfans of described transfer gear TD is automatically adjusted distribution to the power shunted, Drive system is made to have the function carrying out stepless speed regulation within the specific limits, it is achieved input power and output power in transmission process Optimal coupling, effectively promotes the overall efficiency of vehicle drive system；
Described hydraulic pressure drive control system mechanism includes hydraulic pump HB, hydraulic motor HM, and two outfans of transfer gear TD are respectively Hydraulic pump HB, the input of hydraulic motor HM；
Described hydraulic drive uses independent, totally enclosed internal hydraulic pressure oil circulation than governor motion RC, can be prevented effectively from hydraulic pressure When transmission controlling mechanism shares hydraulic oil liquid, easily affect because of oil contamination the hydraulic drive reliability than governor motion RC and Control accuracy；
When vehicle start and anxious acceleration, hydraulic drive is utilized to be capable of the feature of big speed ratio than governor motion RC, by strengthening Hydraulic drive shunts the power of transmission and transmits with big speed ratio, can make vehicle smooth-going starting and quickly improve speed；
When vehicle travel at a relatively high speed and car speed and running resistance change little time, utilize machinery transfer case transmission mechanism work Make characteristic and the work characteristics of hydraulic pressure drive control system mechanism, make system individually work in mechanically operated mode, be effectively improved system Overall transmission efficiency.
In described machinery transfer case transmission mechanism:
Transfer gear TD is planetary wheeling mechanism, including power input shaft 1, planet carrier 2, sun gear 3, plural planetary gear 4, ring gear the 5, first output shaft 6 and the second output shaft 7；Wherein the second output shaft 7 is pipe axle, described first output shaft 6 Coaxially it is plugged in the second output shaft 7, and two ends are overhanging；Described first output shaft 6 and the second output shaft 7 are respectively as speed change The power shaft of drive mechanism；
Variable transmission mechanism includes first output shaft the 6, second output shaft 7, reverse gear shaft 10, jackshaft 15 and unidirectional locking device 20；
On described second output shaft 7, empty set is provided with reverse gear driving gear 8, gear driving gear 12 and two gear driving gears 14 successively；
Described reversing gear is provided with reverse gear synchronizer 11 between driving gear 8 and a described gear driving gear 12；Described reverse gear synchronizer 11 Companion the second output shaft 7 synchronous axial system also can move axially to R position or N position along the second output shaft 7, when reverse gear synchronizer 11 Mobile to reversing gear driving gear 8 during R position and the second output shaft 7 driving gear 8 that locks and make to reverse gear exports in company with second Axle 7 synchronous rotary, the driving gear 8 that will reverse gear when reverse gear synchronizer 11 moves to N position unlocks with the second output shaft 7；
It is provided with forward gear lock unit 13 between a described gear driving gear 12 and two gear driving gears 14；Described forward gear lock unit 13 In company with the second output shaft 7 synchronous axial system and along the second output shaft 7, I or N position or II can be moved axially to；Work as forward gear Lock unit 13 move to when I can by one gear driving gear 12 and the second output shaft 7 lock and make a gear driving gear 12 with With the second output shaft 7 synchronous rotary；Can be by defeated with second for two gear driving gears 14 when forward gear lock unit 13 moves to II Shaft 7 locks and makes two gear driving gears 14 in company with the second output shaft 7 synchronous rotary；When forward gear lock unit 13 moves to N During position, one gear driving gear 12 and two gear driving gears 14 are unlocked with the second output shaft 7 simultaneously；
The driven gear 9 that reverses gear is fixed on reverse gear shaft 10；The two ends of described reverse gear shaft 10 are rotatably supported on system casing KT, Described reverse gear driven gear 9 simultaneously with reverse gear driving gear 8 and a gear driving gear 12 often engages；
Main deceleration driving gear 16, gear driven gear 17 and two gear driven gears 18 it are sequentially provided with on described jackshaft 15；
Described main deceleration driving gear 16 often engages with main reduction driven gear 22, described gear driven gear 17 and a gear driving tooth Wheel 12 often engages, and described two gear driven gears 18 often engage with two gear driving gears 14；Described main reduction driven gear 22 is solid It is located on the housing of differential assembly 23；Described unidirectional locking device 20 includes input and outfan, unidirectional locking device 20 Outfan is fixedly arranged on one end of the jackshaft 15 with the two gear adjacent sides of driven gear 18, and the input of unidirectional locking device 20 is solid It is located at one end of hydraulic motor axle 21, is provided with, between described two gear driven gears 18 and described unidirectional locking device 20, locking of reversing gear Lock unit 19；The described locking synchronization device 19 that reverses gear with jackshaft 15 synchronous axial system and can move axially to R position along jackshaft 15 Or N position, when the locking synchronization device 19 that reverses gear moves to R position, the input of unidirectional locking device 20 is locked on jackshaft 15 And make jackshaft 15 in company with the input synchronous axial system of unidirectional locking device 20, when the locking synchronization device 19 that reverses gear moves to N position The input of unidirectional locking device 20 is unlocked with jackshaft 15.
In described hydraulic drive governor motion:
Hydraulic pressure drive control system mechanism include hydraulic pump HB, hydraulic motor HM, the first check valve SV1, the first accumulator AC1, One electromagnetic valve EV1, hand control valve HV and hydraulic pressure oil groove TA；Described hydraulic pump HB is unidirectional change displacement volume formula hydraulic pressure Pump, described hydraulic motor HM is two-way change displacement volume formula hydraulic motor；
The oil drain out O of described hydraulic pump HB connects the oil inlet P of the first check valve SV1, the oil of the first accumulator AC1 simultaneously Mouth A, the oil inlet P of the first electromagnetic valve EV1 and the oil-in a of lubricating oil flow controlling unit LC；
The oil inlet P of described hydraulic pump HB, the drain tap T of the first check valve SV1, the drain tap T of hand control valve HV all connect Hydraulic pressure oil groove TA；
The oil-out A of described first electromagnetic valve EV1 connects the oil inlet P of hand control valve HV, the first hydraulic fluid port A of hand control valve HV Connecting the first hydraulic fluid port A of described hydraulic motor HM, the second hydraulic fluid port B of hand control valve HV connects hydraulic motor HM's Second hydraulic fluid port B；
Described hydraulic drive is a totally enclosed hydraulic servocontrol and actuator than governor motion RC, including motor EM, electricity Dynamic oil pump DB, the second check valve SV2, the 3rd check valve SV3, the second accumulator AC2, the second electromagnetic valve EV2, the 3rd Electromagnetic valve EV3, the 4th electromagnetic valve EV4, the first oil cylinder HC1, the second oil cylinder HC2 and hydraulic control fuel tank TC；
The output shaft of described motor EM is connected to the rotor of electric oil pump DB；
The oil drain out O of described electric oil pump DB connects oil inlet P and the 3rd check valve of described second check valve SV2 simultaneously The oil inlet P of SV3；The oil-out A of described 3rd check valve SV3 connects first hydraulic fluid port of the second electromagnetic valve EV2 simultaneously A, the oil inlet P of the 3rd electromagnetic valve EV3 and the oil inlet P of the 4th electromagnetic valve EV4；The of described second electromagnetic valve EV2 Two hydraulic fluid port B connect the hydraulic fluid port A of described second accumulator AC2；The hydraulic fluid port A of described 3rd electromagnetic valve EV3 connects second The hydraulic fluid port A of oil cylinder HC2 rodless cavity；The hydraulic fluid port A of described 4th electromagnetic valve EV4 connects the first oil cylinder HC1 rodless cavity Hydraulic fluid port A；
The oil inlet P of described electric oil pump DB, the drain tap T of described second check valve SV2, the draining of the 3rd electromagnetic valve EV3 Mouth T, the drain tap T of the 4th electromagnetic valve EV4 all connect hydraulic control fuel tank TC；
When to the second oil cylinder HC2 fuel feeding, its oil cylinder can be made oil-filled, make the discharge capacity that singly turns of hydraulic motor HM strengthen simultaneously；When During two oil cylinder HC2 drainings, the discharge capacity that singly turns of hydraulic motor HM can be made to reduce；When oil pressure in the cylinder maintaining the second oil cylinder HC2 Time constant, can maintain hydraulic motor HM singly to turn discharge capacity constant；
When to the first oil cylinder HC1 fuel feeding, can make its oil cylinder oil-filled, simultaneously make hydraulic pump HB singly turn discharge capacity strengthen；When first During oil cylinder HC1 draining, the discharge capacity that singly turns of hydraulic pump HB can be made to reduce；When in the cylinder maintaining the first oil cylinder HC1, oil pressure is constant Time, can maintain hydraulic pump HB singly to turn discharge capacity constant；
One end of first output shaft 6 corresponding with hydraulic pressure drive control system mechanism connects the rotor of hydraulic pump HB；With hydraulic motor HM pair The one end of the jackshaft 15 answered is connected to hydraulic motor axle 21 by outfan and the input of unidirectional locking device 20；Advancing Under gear operating mode, when the rotating speed of hydraulic motor axle 21 is more than the rotating speed of jackshaft 15, the input of unidirectional locking device 20 is with defeated Go out to hold locking, make hydraulic motor axle 21 and jackshaft 15 locking synchronous axial system；In the rotating speed of hydraulic motor axle 21 is less than During the rotating speed of countershaft 15, the input of unidirectional locking device 20 unlocks with outfan, makes hydraulic motor axle 21 and jackshaft simultaneously 15 unlock；
Described first electromagnetic valve EV1 and the second electromagnetic valve EV2 is 22 and leads to electromagnetic switch valve；Described hand control valve HV is to pass through 34 of Non-follow control lead to reversal valve；Described 3rd electromagnetic valve EV3 and the 4th electromagnetic valve EV4 is 33 logical linear pressures Force rate example solenoid valve, or 33 lead to pulse width modulated pressure ratio solenoid valve.
Transfer gear TD has three kinds of structures to design:
Transfer gear TD: the power input shaft 1 of the first structure is connected to planet carrier 2；Be installed with on described planet carrier 2 two with On planet wheel spindle, each planet wheel spindle upper sliding sleeve is provided with planetary gear 4, and plural planetary gear 4 is respectively positioned on sun gear 3 He Between ring gear 5, and often engage with sun gear 3 and ring gear 5 simultaneously；The wheel shaft of sun gear 3 is connected to as transfer gear One end of first output shaft 6 of first outfan of TD；It is defeated that described ring gear 5 is connected to as transfer gear TD second Go out one end of the second output shaft 7 of end.
Transfer gear TD: the power input shaft 1 of the second structure is connected to ring gear 5；The wheel shaft of described sun gear 3 is even Then as one end of the first output shaft 6 of the first outfan of transfer gear TD；Described planet carrier 2 is connected to as transfer One end of second output shaft 7 of second outfan of mechanism TD；It is installed with plural planetary gear on described planet carrier 2 Axle, each planet wheel spindle upper sliding sleeve is provided with planetary gear 4, plural planetary gear 4 be respectively positioned on sun gear 3 and ring gear 5 it Between, and often engage with sun gear 3 and ring gear 5 simultaneously.
Transfer gear TD: the power input shaft 1 of the third structure is connected to the wheel shaft of sun gear 3；Described planet carrier 2 is even Then as one end of the first output shaft 6 of the first outfan of transfer gear TD；Be installed with on described planet carrier 2 two with On planet wheel spindle, each planet wheel spindle upper sliding sleeve is provided with planetary gear 4, and plural planetary gear 4 is respectively positioned on sun gear 3 He Between ring gear 5, and often engage with sun gear 3 and ring gear 5 simultaneously；Described ring gear 5 is connected to as transfer gear One end of second output shaft 7 of second outfan of TD.
Relevant content in technique scheme is explained as follows:
1., in technique scheme, described lubricating oil flow controlling unit LC is made up of flow control valve CV and choke valve TH, The oil-in a of lubricating oil flow controlling unit LC connects the oil drain out O of hydraulic pump HB, oil-out b connects and lubricates Flow-rate adjustment in parallel between the oil-in a and oil-out b of cooling oil path interface LUO, lubricating oil flow controlling unit LC Valve CV and choke valve TH, wherein: raised along with the oil pressure of its oil inlet P by the hydraulic fluid flow rate of flow control valve CV And being progressively smaller until is 0, is raised along with the oil pressure of its oil inlet P by the hydraulic fluid flow rate of choke valve TH and gradually increase Add, but after the oil pressure of its oil inlet P is increased to certain value, the speed increased by the hydraulic fluid flow rate of choke valve TH is slowed down And gradually one constant flow of convergence；
2. in technique scheme, described hydraulic drive than adjustment module be one by motor EM, electric oil pump DB, second unidirectional Valve SV2, the 3rd check valve SV3, the second accumulator AC2, the second electromagnetic valve EV2, the 3rd electromagnetic valve EV3, the 4th electricity Independent, the totally enclosed hydraulic pressure of magnet valve EV4, the first oil cylinder HC1, the second oil cylinder HC2 and hydraulic control fuel tank TC composition pass Dynamic ratio regulation system, compares the hydraulic oil liquid of regulation in hydraulic drive than adjustment module inner loop for hydraulic drive；
3., in technique scheme, the described first oil cylinder HC1 stator relative to hydraulic pump HB is fixedly installed, and can have two kinds of realities Existing mode:
(1) described first oil cylinder HC1 is fixedly arranged on the stator of described hydraulic pump HB；
(2) stator of described first oil cylinder HC1 and described hydraulic pump HB is fixedly arranged on described system casing KT simultaneously；
4., in technique scheme, the described second oil cylinder HC2 stator relative to hydraulic motor HM is fixedly installed, and can have two kinds Implementation:
(1) described second oil cylinder HC2 is fixedly arranged on the stator of described hydraulic motor HM；
(2) stator of described second oil cylinder HC2 and described hydraulic motor HM is fixedly arranged on described system casing KT simultaneously；
5., in technique scheme, described motor EM and described electric oil pump DB is fixedly installed can have relative to system casing KT Three kinds of implementations:
(1) stator of described motor EM is fixedly arranged on the stator of described electric oil pump DB, and described electric oil pump DB is fixedly arranged on and is On system housing KT；
(2) stator of described electric oil pump DB is fixedly arranged on the stator of described motor EM, and the stator of described motor EM is fixedly arranged on On system casing KT；
(3) stator of described electric oil pump DB and the stator of described motor EM are fixedly arranged on system casing KT simultaneously.
Owing to having used technique scheme, the present invention has following advantages and an effect:
A kind of power transfer the most involved in the present invention confluxes variable speed drive and hydraulic control system thereof, and the mechanical transfer used fills Put and there is the power that two outfans are automatically shunted by the size according to working resistance suffered by two outfans be adjusted distribution Operating characteristic, it is possible to achieve input power and optimal coupling of output power in transmission process, effectively promote vehicle drive system Overall efficiency；
A kind of power transfer the most involved in the present invention confluxes variable speed drive and hydraulic control system thereof, utilizes machinery transfer module There is the work being sized to automatically be adjusted the rotating speed of two outfans according to working resistance suffered by two outfan special Property, drive system can be made to have the function carrying out stepless speed regulation within the specific limits；
A kind of power transfer the most involved in the present invention confluxes variable speed drive and hydraulic control system thereof, when vehicle start with anxious accelerate Time, hydraulic drive can be made full use of and be capable of the feature of big speed ratio, by strengthen hydraulic drive shunting transmission power and Transmit with big speed ratio, vehicle smooth-going starting can be made and quickly improve speed；
A kind of power transfer the most involved in the present invention confluxes variable speed drive and hydraulic control system thereof, goes at a relatively high speed at vehicle Sail and car speed and running resistance change little time, the machinery operating characteristic of transfer device and hydraulic pump can be made full use of Work characteristics, makes system individually work in mechanically operated mode, the overall transmission efficiency of the system that is effectively improved；
A kind of power transfer the most involved in the present invention confluxes variable speed drive and hydraulic control system thereof, for hydraulic pump and hydraulic pressure horse The hydraulic drive of the discharge capacity regulation reached uses independent, totally enclosed internal hydraulic pressure oil circulation than adjustment module, can effectively keep away When exempting to share hydraulic oil liquid with hydraulic drive and control system, easily affect because of oil contamination hydraulic drive than adjustment module can By property and control accuracy；
A kind of power transfer the most involved in the present invention confluxes variable speed drive and hydraulic control system thereof, at hydraulic drive and control Module have employed flow control valve CV and choke valve TH, under flow control valve CV and choke valve TH regulates jointly, Fluid flow for system lubrication and cooling can be adjusted and there is maximum stream flow restriction effect, lubrication can be prevented effectively from System overall efficiency is caused and because of for system lubrication and cooling oil beyond being actually needed with the fluid flow of cooling The shunting action impact on Hydraulic Power Transmission System operating pressure.
Accompanying drawing explanation
Fig. 1 is that power transfer of the present invention confluxes variable speed drive and hydraulic control system theory of constitution figure thereof.
Fig. 2 is that power transfer of the present invention confluxes the transmission of machinery transfer module in variable speed drive and hydraulic control system thereof Connect the first replacement scheme schematic diagram.
Fig. 3 is that power transfer of the present invention confluxes the transmission of machinery transfer module in variable speed drive and hydraulic control system thereof Connect the second replacement scheme schematic diagram.
Code name in figure: power input shaft 1, planet carrier 2, sun gear 3, planetary gear 4, ring gear the 5, first output shaft 6, the second output shaft 7, the driving gear 8 that reverses gear, the driven gear 9 that reverses gear, reverse gear shaft 10, reverse gear synchronizer 11, gear master Moving gear 12, forward gear lock unit 13, two gear driving gear 14, jackshaft 15, main deceleration driving gear 16, a gear from Moving gear 17, two gear driven gear 18, the locking synchronization device 19 that reverses gear, unidirectional locking device 20, hydraulic motor axle 21, master subtract Speed driven gear 22, differential assembly 23, hydraulic pump HB, hydraulic motor HM, electric oil pump DB, the first check valve SV1, the second check valve SV2, the 3rd check valve SV3, the first accumulator AC1, the second accumulator AC2, flow control valve CV, choke valve TH, the first electromagnetic valve EV1, the second electromagnetic valve EV2, the 3rd electromagnetic valve EV3, the 4th electromagnetic valve EV4, hand control valve HV, the first oil cylinder HC1, the second oil cylinder HC2, motor EM, hydraulic pressure oil groove TA, hydraulic control fuel tank TC, system casing KT, transfer gear TD, hydraulic drive than adjustment module RC, lubricating oil flow controlling unit LC, Lubrication oil circuit interface LUO, input power PI, output power PO.
Detailed description of the invention
Below in conjunction with the accompanying drawings, by embodiment, the present invention is further described.
Embodiment 1:
Seeing Fig. 1, a kind of power transfer confluxes variable speed drive and hydraulic control system is passed by machinery transfer case transmission mechanism and hydraulic pressure Dynamic governor motion composition；Described machinery transfer case transmission mechanism is made up of transfer gear TD and variable transmission mechanism, and described hydraulic pressure passes Dynamic governor motion is made up of than governor motion RC hydraulic pressure drive control system mechanism and hydraulic drive.
In described machinery transfer case transmission mechanism:
Transfer gear TD is planetary wheeling mechanism, including power input shaft 1, planet carrier 2, sun gear 3, plural planetary gear 4, ring gear the 5, first output shaft 6 and the second output shaft 7.Power input shaft 1 is connected to planet carrier 2；On planet carrier 2 admittedly Being provided with plural planet wheel spindle, each planet wheel spindle upper sliding sleeve is provided with planetary gear 4, the plural equal position of planetary gear 4 Between sun gear 3 and ring gear 5, and often engage with sun gear 3 and ring gear 5 simultaneously；The wheel shaft of sun gear 3 is connected to One end of the first output shaft 6 as first outfan of transfer gear TD；Ring gear 5 is connected to as transfer gear TD One end of the second output shaft 7 of the second outfan.Second output shaft 7 is pipe axle, and described first output shaft 6 is coaxially plugged in In second output shaft 7, and two ends are overhanging；Described first output shaft 6 and the second output shaft 7 are respectively as variable transmission mechanism Power shaft；
Variable transmission mechanism includes first output shaft the 6, second output shaft 7, reverse gear shaft 10, jackshaft 15 and unidirectional locking device 20；
On described second output shaft 7, empty set is provided with reverse gear driving gear 8, gear driving gear 12 and two gear driving gears 14 successively；
It is provided with reverse gear synchronizer 11 between driving gear 8 and a described gear driving gear 12 reversing gear；Reverse gear synchronizer 11 is in company with Two output shaft 7 synchronous axial system also can move axially to R position or N position along the second output shaft 7, when reverse gear synchronizer 11 move to The driving gear 8 that the driving gear 8 that reverses gear can be locked with the second output shaft 7 and be made during R position to reverse gear is synchronize in company with the second output shaft 7 Rotating, the driving gear 8 that will reverse gear when reverse gear synchronizer 11 moves to N position unlocks with the second output shaft 7.
Between a gear driving gear 12 and two gear driving gears 14, forward gear lock unit 13 is installed；Forward gear lock unit 13 in company with the second output shaft 7 synchronous axial system and can move axially to I or N position or II along the second output shaft 7；Work as advance Gear lock unit 13 moves and can lock and make a gear driving gear 12 by a gear driving gear 12 and the second output shaft 7 to when I In company with the second output shaft 7 synchronous rotary；Can be by two gear driving gears 14 and second when forward gear lock unit 13 moves to II Output shaft 7 locks and makes two gear driving gears 14 in company with the second output shaft 7 synchronous rotary；When forward gear lock unit 13 move to During N position, one gear driving gear 12 and two gear driving gears 14 are unlocked with the second output shaft 7 simultaneously.
The driven gear 9 that reverses gear is fixedly installed on reverse gear shaft 10；The two ends of reverse gear shaft 10 are rotatably supported at system casing KT On, reverse gear driven gear 9 simultaneously with reverse gear driving gear 8 and a gear driving gear 12 often engages.
It is installed with main deceleration driving gear 16, gear driven gear 17 on described jackshaft 15 successively and two gears are driven Gear 18.
Described main deceleration driving gear 16 often engages with main reduction driven gear 22, described gear driven gear 17 and a gear Driving gear 12 often engages, and described two gear driven gears 18 often engage with two gear driving gears 14；Described main reduction driven tooth Wheel 22 is fixedly arranged on the housing of differential assembly 23；Described unidirectional locking device 20 includes input and outfan, unidirectional locking The outfan of device 20 is fixedly arranged on and one end of jackshafts 15 of the two gear adjacent sides of driven gear 18, unidirectional locking device 20 defeated Enter end and be fixedly arranged on one end of hydraulic motor axle 21.It is provided with between two gear driven gears 18 and described unidirectional locking device 20 and reverses gear Locking synchronization device 19；The locking synchronization device 19 that reverses gear with jackshaft 15 synchronous axial system and can move axially to R position along jackshaft 15 Or N position, when the locking synchronization device 19 that reverses gear moves to R position, the input of unidirectional locking device 20 is locked on jackshaft 15 And make jackshaft 15 in company with the input synchronous axial system of unidirectional locking device 20, when the locking synchronization device 19 that reverses gear moves to N position The input of unidirectional locking device 20 is unlocked with jackshaft 15.
In hydraulic drive governor motion:
Seeing Fig. 1, hydraulic pressure drive control system mechanism includes hydraulic pump HB, hydraulic motor HM, the first check valve SV1, the first accumulation of energy Device AC1, the first electromagnetic valve EV1, hand control valve HV and hydraulic pressure oil groove TA；Hydraulic pump HB is unidirectional change displacement volume formula Hydraulic pump, it singly turns discharge capacity can be 0 to carry out step-less adjustment between maximum pump discharge in discharge capacity.Hydraulic motor HM is two-way change Displacement volume formula hydraulic motor, it singly turns discharge capacity can be 0 to carry out step-less adjustment between maximum pump discharge in discharge capacity.
The oil drain out O of described hydraulic pump HB connects the oil inlet P of the first check valve SV1, the first accumulator simultaneously The hydraulic fluid port A of AC1, the oil inlet P of the first electromagnetic valve EV1 and the oil-in a of lubricating oil flow controlling unit LC；Hydraulic pressure The oil inlet P of pump HB, the drain tap T of the first check valve SV1, the drain tap T of hand control valve HV all connect hydraulic pressure oil groove TA。
The oil-out A of described first electromagnetic valve EV1 connects the oil inlet P of hand control valve HV, the first of hand control valve HV Hydraulic fluid port A connects the first hydraulic fluid port A of described hydraulic motor HM, and the second hydraulic fluid port B of hand control valve HV connects hydraulic motor The second hydraulic fluid port B of HM.
Hydraulic pressure drive control system mechanism also includes lubricating oil flow controlling unit LC, including flow control valve CV and choke valve TH；Flow control valve CV is that internal control leaks formula flow control valve, and choke valve TH is the single hole throttle valve of big L/D ratio.Lubrication The oil-in a of fluid flow controlling unit LC connects the oil inlet P of flow control valve CV and entering of choke valve TH simultaneously The oil-out A of the oil-out A and choke valve TH of hydraulic fluid port P, described flow control valve CV connects lubricating oil flow simultaneously The oil-out b of control unit LC；Described oil-out b connects lubrication oil circuit interface LUO.
Described hydraulic drive is a totally enclosed hydraulic servocontrol and actuator than governor motion RC, including motor EM, electric oil pump DB, the second check valve SV2, the 3rd check valve SV3, the second accumulator AC2, the second electromagnetic valve EV2, the 3rd electromagnetic valve EV3, the 4th electromagnetic valve EV4, the first oil cylinder HC1, the second oil cylinder HC2 and hydraulic control fuel tank TC.
The output shaft of motor EM is connected to the rotor of electric oil pump DB；The oil drain out O of electric oil pump DB connects simultaneously Oil inlet P and the oil inlet P of the 3rd check valve SV3 of described second check valve SV2；Described 3rd check valve SV3's Oil-out A connects the first hydraulic fluid port A of the second electromagnetic valve EV2, the oil inlet P of the 3rd electromagnetic valve EV3 and the 4th electricity simultaneously The oil inlet P of magnet valve EV4；The second hydraulic fluid port B of described second electromagnetic valve EV2 connects the oil of described second accumulator AC2 Mouth A；The hydraulic fluid port A of described 3rd electromagnetic valve EV3 connects the hydraulic fluid port A of the second oil cylinder HC2 rodless cavity；Described 4th electromagnetism The hydraulic fluid port A of valve EV4 connects the hydraulic fluid port A of the first oil cylinder HC1 rodless cavity.The oil inlet P of electric oil pump DB, the second list All connect to the drain tap T of valve SV2, the drain tap T of the 3rd electromagnetic valve EV3, the drain tap T of the 4th electromagnetic valve EV4 Hydraulic control fuel tank TC.
When to the second oil cylinder HC2 fuel feeding, its oil cylinder can be made oil-filled, make the discharge capacity that singly turns of hydraulic motor HM add simultaneously Greatly；When the second oil cylinder HC2 draining, the discharge capacity that singly turns of hydraulic motor HM can be made to reduce；When maintaining the second oil cylinder HC2's When in cylinder, oil pressure is constant, can maintain hydraulic motor HM singly to turn discharge capacity constant.
When to the first oil cylinder HC1 fuel feeding, can make its oil cylinder oil-filled, simultaneously make hydraulic pump HB singly turn discharge capacity strengthen； When the first oil cylinder HC1 draining, the discharge capacity that singly turns of hydraulic pump HB can be made to reduce；When oil in the cylinder maintaining the first oil cylinder HC1 When pressing constant, can maintain hydraulic pump HB singly to turn discharge capacity constant.
One end of first output shaft 6 corresponding with hydraulic pressure drive control system mechanism connects the rotor of hydraulic pump HB；With hydraulic motor One end of jackshaft 15 corresponding for HM is connected to hydraulic motor axle 21 by outfan and the input of unidirectional locking device 20；? Under forward gear operating mode, when the rotating speed of hydraulic motor axle 21 is more than the rotating speed of jackshaft 15, the input of unidirectional locking device 20 With outfan locking, make hydraulic motor axle 21 and jackshaft 15 locking synchronous axial system；When the rotating speed of hydraulic motor axle 21 is little When the rotating speed of jackshaft 15, the input of unidirectional locking device 20 and outfan unlock, make simultaneously hydraulic motor axle 21 with in Countershaft 15 unlocks.
First electromagnetic valve EV1 and the second electromagnetic valve EV2 is 22 and leads to electromagnetic switch valve；Hand control valve HV is to pass through hands Dynamic 34 controlled lead to reversal valve；3rd electromagnetic valve EV3 and the 4th electromagnetic valve EV4 is 33 and leads to line pressure ratio Solenoid valve, or 33 lead to pulse width modulated pressure ratio solenoid valve.
The operation principle of the present embodiment is as follows:
Vehicle neutral:
During vehicle neutral, reverse gear synchronizer 11 is in N position, and forward gear lock unit 13 is in N position, at the locking synchronization device 19 that reverses gear In N position, the discharge capacity that singly turns of hydraulic pump HB is 0, and the discharge capacity that singly turns of hydraulic motor HM is 0, and the first electromagnetic valve EV1 is in 1st valve position makes its oil inlet P connection oil-out A, hand control valve HV be in the 2nd valve position and make its oil inlet P, the first hydraulic fluid port A, the second hydraulic fluid port B and drain tap T all interconnect, and flow control valve CV is in fully on state and makes its oil inlet P Connecting completely with between oil-out A, motor EM no power, electric oil pump DB does not works, and the second electromagnetic valve EV2 is in 1st valve position makes its first hydraulic fluid port A and the second hydraulic fluid port B end simultaneously, and the 3rd electromagnetic valve EV3 is in the 1st valve position and makes its oil-feed Mouthful P cut-off, hydraulic fluid port A connect drain tap T, the 4th electromagnetic valve EV4 be in the 1st valve position make its oil inlet P end, hydraulic fluid port A connects drain tap T, the first oil cylinder HC1 and is in cylinder without oil condition, and it is interior without oil condition that the second oil cylinder HC2 is in cylinder；Dynamic Power power shaft 1 input power, owing to now machinery two outfan sun gears 3 of transfer module TD and ring gear are neither by about Bundle, machinery transfer module TD does not forms transfer effect, and therefore vehicle maintains resting state.
The starting of vehicle forward gear and acceleration:
When vehicle is converted to forward gear starting by neutral position state, forward gear lock unit 13 moves I, makes the second output shaft 7 and gear Driving gear 12 locks, owing to now vehicle is in the resting state not yet started to walk, vehicle inertia power by driving wheel of vehicle through difference Speed device 23, main reduction driven gear 22, main deceleration driving gear 16, jackshaft 15, gear driven gear 17, gear are main Moving gear 12, forward gear lock unit the 13, second output shaft 7 form fixed constraint to ring gear 5, and power input shaft 1 is to too Sun wheel 3 formation definite proportion transmission, but because the discharge capacity that singly turns of hydraulic pump HB is 0, makes it to the first output shaft 6 and sun gear 3 It is formed without constraint, so that machinery transfer module TD does not produce shunting gearing；Afterwards, hand control valve HV is by the 2nd valve position Move to the 1st valve position, make its oil inlet P connect the first hydraulic fluid port A, the second hydraulic fluid port B connection drain tap T；Second electromagnetic valve EV2 energising makes its first hydraulic fluid port A connect the second hydraulic fluid port B, make the fluid stored in the second accumulator AC2 simultaneously to the 3rd The oil inlet P of electromagnetic valve EV3 and the oil inlet P fuel feeding of the 4th electromagnetic valve EV4, now, in the second accumulator AC2 The oil liquid pressure stored is not enough to drive the first oil cylinder HC1 and the second oil cylinder HC2 work, then to motor EM energising, driving Electric oil pump DB is sucked fluid from hydraulic control fuel tank TC by its oil inlet P and discharges, by electric oil pump DB through oil drain out O Oil drain out O discharge fluid after the oil inlet P and oil-out A of the 3rd check valve SV3, simultaneously to the second electromagnetic valve First hydraulic fluid port A, the oil inlet P of the 3rd electromagnetic valve EV3 and the oil inlet P fuel feeding of the 4th electromagnetic valve EV4 of EV2；Conveying The hydraulic fluid port A of the second accumulator AC2 is supplied by the fluid of the first hydraulic fluid port A to the second electromagnetic valve EV2 through its second hydraulic fluid port B Oil；Subsequently, the 3rd electromagnetic valve EV3 powered at full capacity, make it be converted to the 3rd valve position, oil inlet P even by the 1st valve position Logical hydraulic fluid port A, make the fluid being transported to its oil inlet P through hydraulic fluid port A to the second oil cylinder HC2 fuel feeding, make hydraulic motor HM's Singly turn discharge capacity and reach maximum；4th electromagnetic valve EV4 is powered and is gradually increased supply current, makes it by the 1st valve position gradually Be converted to the 2nd valve position, oil inlet P connects hydraulic fluid port A and drain tap T simultaneously, and makes the connection journey of oil inlet P and hydraulic fluid port A Degree strengthens with supply current increase, oil inlet P reduces with increasing with supply current with the connecting degree of drain tap T, defeated Deliver to the fluid of oil inlet P of the 4th electromagnetic valve EV4 through hydraulic fluid port A to the first oil cylinder HC1 fuel feeding and fuel feeding oil pressure along with The connecting degree of the oil inlet P of four electromagnetic valves and hydraulic fluid port A strengthens and raises so that hydraulic pump HB singly turn discharge capacity by Cumulative adduction strengthens with the connecting degree of hydraulic fluid port A along with the oil inlet P of the 4th electromagnetic valve and increases；Along with hydraulic pump HB's Singly turning discharge capacity to be gradually increased by 0, hydraulic pump HB begins through its oil inlet P and sucks fluid from hydraulic pressure oil groove TA and through it Flowed friction suffered by oil drain out O discharge, hydraulic pump HB suction and the fluid amount of discharge and rotor thereof singly turns discharge capacity with it Increase and increase, so that the first output shaft 6 and the rotation condition power suffered by sun gear 3 and the transmission of power output shaft 1 transfer Power to ring gear 5 is gradually increased；Transfer is delivered to the power of ring gear 5 through the second output shaft 7, forward gear lock unit 13, gear driving gear 12, gear driven gear 17 passes to jackshaft 15 with mechanical drive mode；Hydraulic pump HB discharges Fluid in, a part be transported to lubrication oil circuit interface LUO, another part warp through lubricating oil flow controlling unit LC The oil inlet P of the first electromagnetic valve EV1 and oil-out A, the oil inlet P of hand control valve and the first hydraulic fluid port A enter hydraulic motor The first hydraulic fluid port A of HM also drives its rotor rotate and externally export power, makes to be in transmission connection with the rotor of hydraulic motor HM Hydraulic motor axle 21 rotating speed higher than jackshaft 15 rotating speed, make unidirectional locking device 20 lock, so that being inputted by power The power that axle 1 transfer is delivered on sun gear 3 is delivered to jackshaft 15 with hydraulic transmission mode；Along with hydraulic motor HM's Rotor rotates, and enters the fluid of the first hydraulic fluid port A of hydraulic motor HM through its second hydraulic fluid port B, second oil of hand control valve HV Mouth B and drain tap T flow back into hydraulic control fuel tank TC；Above-mentioned it is delivered to centre with mechanical drive mode and hydraulic transmission mode respectively After power on axle 15 confluxes, pass to differential mechanism 23 and to car through main deceleration driving gear 16, main reduction driven gear 22 Wheel forms driving force, the vehicle start when the driving force formed is sufficiently large；When needing after the starting of vehicle forward gear to continue to accelerate, By increase power input shaft 1 input power and rotating speed or continue strengthen hydraulic pump HB singly turn discharge capacity and at its single turn Discharge capacity is gradually reduced the rotating speed that discharge capacity makes its rotor export that singly turns of hydraulic motor HM after reaching maximum increase or increase simultaneously The power and rotating speed, the continuation that add power input shaft 1 input strengthen singly turning discharge capacity and singly turning discharge capacity at it and reach of hydraulic pump HB Be gradually reduced hydraulic motor HM after big value singly turns discharge capacity, and vehicle can be made to continue to accelerate.
Vehicle forward gear at the uniform velocity travels.
When vehicle accelerate to certain speed need to enter at the uniform velocity transport condition time, maintain hydraulic pump HB singly to turn discharge capacity constant, Simultaneously progressively reduce the supply current to the 3rd electromagnetic valve EV3 until being 0, make the 3rd electromagnetic valve EV3 by its 2nd valve position by Step is converted to the 1st valve position, the fluid of the second hydraulic jack HC2 gradually empties, make hydraulic motor HM's singly to turn discharge capacity gradually Tend to 0；Subsequently, the first electromagnetic valve EV1 energising makes it be converted to the 2nd valve position, oil inlet P and hydraulic fluid port A by the 1st valve position Ending, the fluid that hydraulic pump HB discharges can only flow to lubrication oil circuit through lubricating oil flow controlling unit LC and connect simultaneously Mouth LUO, fluid flow hydraulic pump HB being discharged due to the metering function of lubricating oil flow controlling unit LC is limited System, so that the rotor of hydraulic pump maintains certain rotating speed, and then makes to be formed between power input shaft 1 and differential mechanism 12 to determine Ratio transmission, makes vehicle enter at the uniform velocity transport condition.
When vehicle at the uniform velocity travels, owing to the first electromagnetic valve EV1 is in the 2nd valve position, has interrupted the confession to hydraulic motor HM Oil oil circuit, makes the rotor speed of hydraulic motor HM and the rotating speed of hydraulic motor axle 21 rotating speed less than jackshaft 15, so that Unidirectional locking device 20 unlocks.
When vehicle travels with a gear, vehicle can be realized necessarily by the power and rotating speed controlling power input shaft 1 input Acceleration, deceleration in velocity interval and at the uniform velocity travel.
Vehicle forward gear is shifted gears.
When vehicle need by one gear change to two gears time, first electromagnetic valve EV1 energising be in the 2nd valve position make its oil inlet P and Oil-out A ends simultaneously, and the discharge capacity that singly turns of hydraulic pump HB is adjusted to 0, makes machinery transfer module TD lose transfer effect； Subsequently, after forward gear lock unit 13 is moved to II by I, makes the second output shaft 7 first unlock with a gear driving gear 12 Locking with two gear driving gears 14, afterwards, the discharge capacity that singly turns of hydraulic pump HB is recovered right by 0 being gradually increased, make its rotor again First output shaft 6 and the rotation condition of sun gear 3, make vehicle enter two gear transport conditions.
When vehicle travels with two gears, vehicle can be realized necessarily by the power and rotating speed controlling power input shaft 1 input Acceleration, deceleration in velocity interval and at the uniform velocity travel.
Contrary with above-mentioned shift process, vehicle can be made to be changed to a gear by two gears.
Vehicle reverse gear starting, accelerate and at the uniform velocity travel.
Vehicle by neutral position state be converted to reverse gear starting time, reverse gear synchronizer 11 move to R position, make the second output shaft 7 with The driving gear 8 that reverses gear locks, and the locking synchronization device 19 that reverses gear moves to R position, makes jackshaft 15 lock with hydraulic motor axle 21 Fixed, owing to now vehicle is in the resting state not yet started to walk, vehicle inertia power is subtracted through differential mechanism 23, master by driving wheel of vehicle Speed driven gear 22, main deceleration driving gear 16, jackshaft 15, keep off driven gear 17, the driven gear 9 that reverses gear, reverse gear Driving gear 8, reverse gear synchronizer 11 and the second output shaft 7 form fixed constraint to ring gear 5, and power input shaft 1 is to too Sun wheel 3 formation definite proportion transmission, but because the discharge capacity that singly turns of hydraulic pump HB is 0, makes it to the first output shaft 6 and sun gear 3 It is formed without constraint, so that machinery transfer module TD does not produce shunting gearing；Afterwards, hand control valve HV is by the 2nd valve position Move to the 3rd valve position, make its oil inlet P connect the second hydraulic fluid port B, the first hydraulic fluid port A connection drain tap T；Second electromagnetic valve EV2 energising makes its first hydraulic fluid port A connect the second hydraulic fluid port B, make the fluid stored in the second accumulator AC2 simultaneously to the 3rd The oil inlet P of electromagnetic valve EV3 and the oil inlet P fuel feeding of the 4th electromagnetic valve EV4, now, in the second accumulator AC2 The fluid stored is not enough to drive the first oil cylinder HC1 and the second oil cylinder HC2 work, then to motor EM energising, drive electronic Oil pump DB is sucked fluid from hydraulic control fuel tank TC by its oil inlet P and discharges, by the row of electric oil pump DB through oil drain out O The fluid that hydraulic fluid port O discharges is after the oil inlet P and oil-out A of the 3rd check valve SV3, simultaneously to the second electromagnetic valve EV2's First hydraulic fluid port A, the oil inlet P of the 3rd electromagnetic valve EV3 and the oil inlet P fuel feeding of the 4th electromagnetic valve EV4；It is transported to second The fluid of the first hydraulic fluid port A of electromagnetic valve EV2 is through its second hydraulic fluid port B hydraulic fluid port A fuel feeding to the second accumulator AC2；With After, subsequently, the 3rd electromagnetic valve EV3 powered at full capacity, make it be converted to the 3rd valve position, oil inlet P even by the 1st valve position Logical hydraulic fluid port A, make the fluid being transported to its oil inlet P through hydraulic fluid port A to the second oil cylinder HC2 fuel feeding, make hydraulic motor HM's Singly turn discharge capacity and reach maximum；4th electromagnetic valve EV4 is powered and is gradually increased supply current, makes it by the 1st valve position gradually Be converted to the 2nd valve position, oil inlet P connects hydraulic fluid port A and drain tap T simultaneously, and makes the connection journey of oil inlet P and hydraulic fluid port A Degree strengthens with supply current increase, oil inlet P reduces with increasing with supply current with the connecting degree of drain tap T, defeated Deliver to the fluid of oil inlet P of the 4th electromagnetic valve EV4 through hydraulic fluid port A to the first oil cylinder HC1 fuel feeding and fuel feeding oil pressure along with The connecting degree of the oil inlet P of four electromagnetic valves and hydraulic fluid port A strengthens and raises so that hydraulic pump HB singly turn discharge capacity by Cumulative adduction strengthens with the connecting degree of hydraulic fluid port A along with the oil inlet P of the 4th electromagnetic valve and increases；Along with hydraulic pump HB's Singly turning discharge capacity to be gradually increased by 0, hydraulic pump HB begins through its oil inlet P and sucks fluid from hydraulic pressure oil groove TA and through it Flowed friction suffered by oil drain out O discharge, hydraulic pump HB suction and the fluid amount of discharge and rotor thereof singly turns discharge capacity with it Increase and increase, so that the first output shaft 6 and the rotation condition power suffered by sun gear 3 and the transmission of power output shaft 1 transfer Power to ring gear 5 is gradually increased；Transfer be delivered to the power of ring gear 5 through the second output shaft 7, reverse gear synchronizer 11, One reverse gear driving gear 8, reverse gear driven gear 9 and a gear driven gear 17 passes to jackshaft 15 also with mechanical drive mode Jackshaft 15 is driven to rotate backward；In the fluid that hydraulic pump HB discharges, a part is through lubricating oil flow controlling unit LC It is transported to lubrication oil circuit interface LUO, another part through the oil inlet P of the first electromagnetic valve EV1 and oil-out A, manual control The oil inlet P of valve and the second hydraulic fluid port B enter the second hydraulic fluid port B of hydraulic motor HM and drive its rotor to reversely rotate and through list To the input of lock device 20, the locking synchronization device 19 that reverses gear, jackshaft 15 is exported power, so that by power input shaft 1 The power that transfer is delivered on sun gear 3 is delivered to jackshaft 15 with hydraulic transmission mode and drives jackshaft 15 to rotate backward； Along with hydraulic motor HM rotor rotate, enter hydraulic motor HM the second hydraulic fluid port B fluid through its first hydraulic fluid port A, The first hydraulic fluid port A of hand control valve HV and drain tap T flow back into hydraulic control fuel tank TC；Above-mentioned respectively with mechanical drive mode and hydraulic pressure After the power that the kind of drive is delivered on jackshaft 15 confluxes, pass through main deceleration driving gear 16, main reduction driven gear 22 Passing differential mechanism 23 and wheel is formed reverse actuating force, when the driving force formed is sufficiently large, vehicle reverses gear starting.
Vehicle reverse gear starting after need continue accelerate time, by increase power input shaft 1 input power and rotating speed or Continue to strengthen singly turning discharge capacity and singly turning at it and be gradually reduced the list of hydraulic motor HM after discharge capacity reaches maximum and turn of hydraulic pump HB The rotating speed that discharge capacity makes its rotor export increases or increases simultaneously power and rotating speed, the continuation increasing liquid of power input shaft 1 input Press pump HB singly turn discharge capacity and its singly turn be gradually reduced hydraulic motor HM after discharge capacity reaches maximum singly turn discharge capacity, all may be used So that vehicle continues acceleration of reversing gear.
When vehicle accelerate to certain speed need enter at the uniform velocity transport condition time, maintain hydraulic pump HB singly turn discharge capacity not Become, progressively reducing the supply current to the 3rd electromagnetic valve EV3 until being 0 simultaneously, making the 3rd electromagnetic valve EV3 by its 2nd valve Position is progressively converted to the 1st valve position, the fluid of the second hydraulic jack HC2 gradually empties, make hydraulic motor HM's singly to turn discharge capacity Gradually tend to 0；Subsequently, the first electromagnetic valve EV1 energising makes it be converted to the 2nd valve position, oil inlet P and hydraulic fluid port by the 1st valve position A ends simultaneously, and the fluid that hydraulic pump HB discharges can only flow to lubrication oil circuit through lubricating oil flow controlling unit LC Interface LUO, fluid flow hydraulic pump HB being discharged due to the metering function of lubricating oil flow controlling unit LC is subject to Limit, so that the rotor of hydraulic pump maintains certain rotating speed, and then make to be formed between power input shaft 1 and differential mechanism 12 Definite proportion transmission, makes vehicle enter the at the uniform velocity transport condition that reverses gear.
Vehicle with reverse gear traveling time, by control power input shaft 1 input power and rotating speed can realize vehicle reverse gear time Acceleration, deceleration in certain speed range and at the uniform velocity travel.
In above example 1, give specific embodiment as shown in Figure 1 about machinery transfer module TD. But understood planet carrier 2 in mechanical transfer module TD that one skilled in the art will appreciate that in the present invention after present invention, Sun gear 3 and first replacement scheme that can also use as shown in Figure 2 that is in transmission connection of ring gear 5, be i.e. by defeated for described power Enter that axle 1 is in transmission connection with ring gear 5, described sun gear 3 is as machinery the first outfan of transfer module, described planet carrier 2 As the second outfan of machinery transfer module, or use the second replacement scheme as shown in Figure 3, be i.e. by defeated for described power Enter that axle 1 is in transmission connection with sun gear 3, described planet carrier 2 is as machinery the first outfan of transfer module, described ring gear 5 As the second outfan of machinery transfer module, its essence is that the power realized between power intake and two clutch ends divides Stream and differential gearing, and an accompanying drawing 1 simply typical embodiment.
Above-described embodiment only for technology design and the feature of the present invention are described, its object is to allow and is familiar with art of the present invention The personage of technology will appreciate that present disclosure and implements according to this, can not limit the scope of the invention with this.All bases The equivalence that spirit of the invention is made changes or modifies, and all should contain within protection scope of the present invention.
Embodiment 2:
The power input shaft 1 seeing Fig. 2, transfer gear TD is connected to ring gear 5；The wheel shaft of described sun gear 3 is connected to conduct One end of first output shaft 6 of first outfan of transfer gear TD；Described planet carrier 2 is connected to as transfer gear TD One end of the second output shaft 7 of the second outfan；It is installed with plural planet wheel spindle, Mei Gehang on described planet carrier 2 Spider gear shaft upper sliding sleeve is provided with planetary gear 4, and plural planetary gear 4 is respectively positioned between sun gear 3 and ring gear 5, and simultaneously Often engage with sun gear 3 and ring gear 5.
Other structure is with embodiment 1.
Operation principle is with embodiment 1.
Embodiment 3:
Seeing Fig. 3, the power input shaft 1 of transfer gear TD is connected to the wheel shaft of sun gear 3；Described planet carrier 2 is connected to conduct One end of first output shaft 6 of first outfan of transfer gear TD；It is installed with plural planet on described planet carrier 2 Wheel shaft, each planet wheel spindle is provided with planetary gear 4, plural planetary gear 4 be respectively positioned on sun gear 3 and ring gear 5 it Between, and often engage with sun gear 3 and ring gear 5 simultaneously；It is defeated that described ring gear 5 is connected to as transfer gear TD second Go out one end of the second output shaft 7 of end.
Other structure is with embodiment 1.
Operation principle is with embodiment 1.

Claims (9)

1. power transfer confluxes variable speed drive, it is characterised in that: by machinery transfer case transmission mechanism and hydraulic drive governor motion group Become；Described machinery transfer case transmission mechanism is made up of transfer gear TD and variable transmission mechanism, and described transfer gear TD has one Individual input and two outfans；Described hydraulic drive governor motion is compared governor motion by hydraulic pressure drive control system mechanism and hydraulic drive RC forms；Suffered by two outfans of described transfer gear TD, the power shunted automatically is carried out by the size of working resistance Regulation distribution, make drive system have the function carrying out stepless speed regulation within the specific limits, it is achieved in transmission process input power with The optimal coupling of output power, effectively promotes the overall efficiency of vehicle drive system；Described hydraulic pressure drive control system mechanism includes hydraulic pressure Pump HB, hydraulic motor HM, two outfans of transfer gear TD are respectively hydraulic pump HB, the input of hydraulic motor HM End；Described hydraulic drive uses independent, totally enclosed internal hydraulic pressure oil circulation than governor motion RC, can be prevented effectively from When sharing hydraulic oil liquid with hydraulic pressure drive control system mechanism, easily affect because of oil contamination hydraulic drive than governor motion RC can By property and control accuracy；
When vehicle start and anxious acceleration, hydraulic drive is utilized to be capable of the feature of big speed ratio than governor motion RC, by strengthening Hydraulic drive shunts the power of transmission and transmits with big speed ratio, can make vehicle smooth-going starting and quickly improve speed；
When vehicle travel at a relatively high speed and car speed and running resistance change little time, utilize machinery transfer case transmission mechanism work Make characteristic and the work characteristics of hydraulic pressure drive control system mechanism, make system individually work in mechanically operated mode, be effectively improved system Overall transmission efficiency；
In described machinery transfer case transmission mechanism: transfer gear TD is planetary wheeling mechanism, including power input shaft (1), planet carrier (2), sun gear (3), plural planetary gear (4), ring gear (5), the first output shaft (6) and the second output shaft (7)；Wherein the second output shaft (7) is pipe axle, and described first output shaft (6) is coaxially plugged in the second output shaft (7) In, and two ends are overhanging；Described first output shaft (6) and the second output shaft (7) are respectively as the input of variable transmission mechanism Axle；
Variable transmission mechanism includes the first output shaft (6), the second output shaft (7), reverse gear shaft (10), jackshaft (15) and unidirectional Lock device (20)；
On described second output shaft (7), empty set is provided with the driving gear that reverses gear (8), gear driving gear (12) and two gears actively successively Gear (14)；It is provided with reverse gear synchronizer between the described driving gear that reverses gear (8) and described gear driving gear (12) (11)；Described reverse gear synchronizer (11) companion the second output shaft (7) synchronous axial system also can be axial along the second output shaft (7) Move to R position or N position, can be by the driving gear that reverses gear (8) and the second output when reverse gear synchronizer (11) moves to R position Axle (7) locks and makes driving gear (8) companion the second output shaft (7) synchronous rotary that reverses gear, when reverse gear synchronizer (11) The driving gear (8) that will reverse gear when moving to N position unlocks with the second output shaft (7)；
It is provided with forward gear lock unit (13) between described gear driving gear (12) and two gears driving gear (14)；Described forward gear Lock unit (13) is in company with the second output shaft (7) synchronous axial system and can move axially to I or N along the second output shaft (7) Position or II；Can be by gear driving gear (12) and the second output shaft when forward gear lock unit (13) moves to I (7) lock and make a gear driving gear (12) in company with the second output shaft (7) synchronous rotary；When forward gear lock unit (13) Mobile to two gears driving gear (14) and the second output shaft (7) can be locked and make when II two gear driving gears (14) with With the second output shaft (7) synchronous rotary；When forward gear lock unit (13) moves to N position by gear driving gear (12) Unlock with the second output shaft (7) with two gears driving gear (14) simultaneously；The driven gear (9) that reverses gear is fixed at reverse gear shaft (10) on；The two ends of described reverse gear shaft (10) are rotatably supported on system casing KT, described in reverse gear driven gear (9) Often engage with the driving gear that reverses gear (8) and gear driving gear (12) simultaneously；Described jackshaft is sequentially provided with master on (15) Deceleration driving gear (16), gear driven gear (17) and two gears driven gear (18)；
Described main deceleration driving gear (16) is often engaged with main reduction driven gear (22), and described gear driven gear (17) is with one Gear driving gear (12) often engages, and described two gears driven gear (18) often engage with two gears driving gear (14)；Described master Reduction driven gear (22) is fixedly arranged on the housing of differential assembly (23)；Described unidirectional locking device (20) includes input And outfan, the outfan of unidirectional locking device (20) is fixedly arranged on and the jackshaft of two gear driven gear (18) adjacent sides (15) one end, the input of unidirectional locking device (20) is fixedly arranged on one end of hydraulic motor axle (21), and described two gears are driven The locking synchronization device (19) that reverses gear it is provided with between gear (18) and described unidirectional locking device (20)；The described locking synchronization device that reverses gear (19) with jackshaft (15) synchronous axial system and along jackshaft (15), R position or N position can be moved axially to, when locking of reversing gear Lock unit (19) movement above and makes centre to the input of unidirectional locking device (20) is locked in during R position jackshaft (15) Axle (15) is in company with the input synchronous axial system of unidirectional locking device (20), when the locking synchronization device (19) that reverses gear is mobile to N position Time the input of unidirectional locking device (20) and jackshaft (15) are unlocked；
In described hydraulic drive governor motion:
Hydraulic pressure drive control system mechanism include hydraulic pump HB, hydraulic motor HM, the first check valve SV1, the first accumulator AC1, One electromagnetic valve EV1, hand control valve HV and hydraulic pressure oil groove TA；Described hydraulic pump HB is unidirectional change displacement volume formula hydraulic pressure Pump, described hydraulic motor HM is two-way change displacement volume formula hydraulic motor；
The oil drain out O of described hydraulic pump HB connects the oil inlet P of the first check valve SV1, the oil of the first accumulator AC1 simultaneously Mouth A, the oil inlet P of the first electromagnetic valve EV1 and the oil-in a of lubricating oil flow controlling unit LC；
The oil inlet P of described hydraulic pump HB, the drain tap T of the first check valve SV1, the drain tap T of hand control valve HV all connect Hydraulic pressure oil groove TA；
The oil-out A of described first electromagnetic valve EV1 connects the oil inlet P of hand control valve HV, the first hydraulic fluid port A of hand control valve HV Connecting the first hydraulic fluid port A of described hydraulic motor HM, the second hydraulic fluid port B of hand control valve HV connects hydraulic motor HM's Second hydraulic fluid port B；
Described hydraulic drive is a totally enclosed hydraulic servocontrol and actuator than governor motion RC, including motor EM, electricity Dynamic oil pump DB, the second check valve SV2, the 3rd check valve SV3, the second accumulator AC2, the second electromagnetic valve EV2, the 3rd Electromagnetic valve EV3, the 4th electromagnetic valve EV4, the first oil cylinder HC1, the second oil cylinder HC2 and hydraulic control fuel tank TC；
The output shaft of described motor EM is connected to the rotor of electric oil pump DB；
The oil drain out O of described electric oil pump DB connects oil inlet P and the 3rd check valve of described second check valve SV2 simultaneously The oil inlet P of SV3；The oil-out A of described 3rd check valve SV3 connects first hydraulic fluid port of the second electromagnetic valve EV2 simultaneously A, the oil inlet P of the 3rd electromagnetic valve EV3 and the oil inlet P of the 4th electromagnetic valve EV4；The of described second electromagnetic valve EV2 Two hydraulic fluid port B connect the hydraulic fluid port A of described second accumulator AC2；The hydraulic fluid port A of described 3rd electromagnetic valve EV3 connects second The hydraulic fluid port A of oil cylinder HC2 rodless cavity；The hydraulic fluid port A of described 4th electromagnetic valve EV4 connects the first oil cylinder HC1 rodless cavity Hydraulic fluid port A；The oil inlet P of described electric oil pump DB, drain tap T, the 3rd electromagnetic valve EV3 of described second check valve SV2 Drain tap T, the drain tap T of the 4th electromagnetic valve EV4 all connect hydraulic control fuel tank TC；
When to the second oil cylinder HC2 fuel feeding, its oil cylinder can be made oil-filled, make the discharge capacity that singly turns of hydraulic motor HM strengthen simultaneously；When During two oil cylinder HC2 drainings, the discharge capacity that singly turns of hydraulic motor HM can be made to reduce；When oil pressure in the cylinder maintaining the second oil cylinder HC2 Time constant, can maintain hydraulic motor HM singly to turn discharge capacity constant；
When to the first oil cylinder HC1 fuel feeding, can make its oil cylinder oil-filled, simultaneously make hydraulic pump HB singly turn discharge capacity strengthen；When first During oil cylinder HC1 draining, the discharge capacity that singly turns of hydraulic pump HB can be made to reduce；When in the cylinder maintaining the first oil cylinder HC1, oil pressure is constant Time, can maintain hydraulic pump HB singly to turn discharge capacity constant；The one of first output shaft (6) corresponding with hydraulic pressure drive control system mechanism End connects the rotor of hydraulic pump HB；Unidirectional locking device is passed through in one end of the jackshaft (15) corresponding with hydraulic motor HM (20) outfan and input are connected to hydraulic motor axle (21)；Under forward gear operating mode, when hydraulic motor axle (21) Rotating speed more than the rotating speed of jackshaft (15) time, the input of unidirectional locking device (20) and outfan locking, make hydraulic motor Axle (21) and jackshaft (15) locking synchronous axial system；When the rotating speed of hydraulic motor axle (21) is less than jackshaft (15) During rotating speed, the input of unidirectional locking device (20) unlocks with outfan, makes hydraulic motor axle (21) and jackshaft simultaneously (15) unlock；
Described first electromagnetic valve EV1 and the second electromagnetic valve EV2 is 22 and leads to electromagnetic switch valve；Described hand control valve HV is to pass through 34 of Non-follow control lead to reversal valve；Described 3rd electromagnetic valve EV3 and the 4th electromagnetic valve EV4 is 33 logical linear pressures Force rate example solenoid valve, or 33 lead to pulse width modulated pressure ratio solenoid valve.
Power transfer the most according to claim 1 confluxes variable speed drive, it is characterised in that: described transfer gear TD's Power input shaft (1) is connected to planet carrier (2)；Plural planet wheel spindle it is installed with on described planet carrier (2), each Planet wheel spindle upper sliding sleeve is provided with planetary gear (4), and plural planetary gear (4) is respectively positioned on sun gear (3) and ring gear (5) between, and often engage with sun gear (3) and ring gear (5) simultaneously；The wheel shaft of sun gear (3) is connected to as dividing One end of first output shaft (6) of first outfan of motivation structure TD；Described ring gear (5) is connected to as transfer gear One end of second output shaft (7) of second outfan of TD.
Power transfer the most according to claim 1 confluxes variable speed drive, it is characterised in that: described transfer gear TD's Power input shaft (1) is connected to ring gear (5)；The wheel shaft of described sun gear (3) is connected to as transfer gear TD One end of first output shaft (6) of one outfan；Described planet carrier (2) is connected to the second output as transfer gear TD One end of second output shaft (7) of end；Plural planet wheel spindle, each planetary gear it is installed with on described planet carrier (2) Axle upper sliding sleeve is provided with planetary gear (4), plural planetary gear (4) be respectively positioned on sun gear (3) and ring gear (5) it Between, and often engage with sun gear (3) and ring gear (5) simultaneously.
Power transfer the most according to claim 1 confluxes variable speed drive, it is characterised in that: described transfer gear TD's Power input shaft (1) is connected to the wheel shaft of sun gear (3)；Described planet carrier (2) is connected to as transfer gear TD's One end of first output shaft (6) of the first outfan；Plural planet wheel spindle it is installed with, often on described planet carrier (2) Individual planet wheel spindle upper sliding sleeve is provided with planetary gear (4), and plural planetary gear (4) is respectively positioned on sun gear (3) and ring gear (5) between, and often engage with sun gear (3) and ring gear (5) simultaneously；Described ring gear (5) is connected to as transfer One end of second output shaft (7) of second outfan of mechanism TD.
Power transfer the most according to claim 1 confluxes variable speed drive, it is characterised in that: described hydraulic pressure drive control system machine Structure also includes that lubricating oil flow controlling unit LC, described lubricating oil flow controlling unit LC include flow control valve CV With choke valve TH；The oil-in a of lubricating oil flow controlling unit LC connects the oil inlet P of flow control valve CV simultaneously With the oil inlet P of choke valve TH, the oil-out A of the oil-out A and choke valve TH of described flow control valve CV connects simultaneously Lead to the oil-out b of lubricating oil flow controlling unit LC；Described oil-out b connects lubrication oil circuit interface LUO.
Power transfer the most according to claim 1 confluxes variable speed drive, it is characterised in that: described unidirectional locking device (20) it is roller oblique slot type one-way clutch, or free wheeling sprag clutch.
Power transfer the most according to claim 1 confluxes variable speed drive, it is characterised in that: described hydraulic pump HB is single To variable displacement vane pump, or unidirectional change displacement axial piston pump, it singly turns discharge capacity can be 0 between maximum pump discharge in discharge capacity Carry out step-less adjustment.
Power transfer the most according to claim 1 confluxes variable speed drive, it is characterised in that: described hydraulic motor HM is Two-way change discharge capacity sliding-vane motor, or two-way change displacement axial piston motor, its singly turn discharge capacity can discharge capacity be 0 to maximum row Step-less adjustment is carried out between amount.
Power transfer the most according to claim 1 confluxes variable speed drive, it is characterised in that: described motor EM is miniature Constant speed motor, or miniature variable-speed motor.
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109927547A (en) * 2019-03-08 2019-06-25 合肥工业大学 A kind of electromechanical combined formula transmission device
CN110778677A (en) * 2019-10-08 2020-02-11 长沙桑铼特农业机械设备有限公司 Integrated pump motor with mechanical gear and application method thereof

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104728385B (en) * 2015-03-23 2017-02-22 合肥工业大学 Parallel type double-flow variable-speed drive device
DE102016200755A1 (en) * 2016-01-20 2017-07-20 Avl Commercial Driveline & Tractor Engineering Gmbh Stepless, hydrostatic-mechanical power split transmission and commercial vehicle with such a power split transmission
CN108006188B (en) * 2017-12-27 2020-06-26 北京理工大学 Double-speed hydraulic hybrid power driving system
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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102374269A (en) * 2010-08-11 2012-03-14 马里控股公司 Method used for operating continuous changeable transmission device possessing static hydraulic/mechanical torque distribution and transmission device for realizing the method
CN103660910A (en) * 2013-12-06 2014-03-26 合肥工业大学 Gasoline and electricity hydrostatic composite hybrid power transmission system

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3703108B2 (en) * 1995-06-09 2005-10-05 株式会社小松製作所 Hydraulic mechanical transmission
JP2000081004A (en) * 1998-08-20 2000-03-21 Caterpillar Inc Under speed control system for hydromechanical drive system and operation method therefor
US6260440B1 (en) * 1999-12-17 2001-07-17 Caterpillar Inc. Method and apparatus for shifting ranges in a continuously variable transmission
JP2004353685A (en) * 2003-05-27 2004-12-16 Komatsu Ltd Hydraulic mechanical transmission
JP4789507B2 (en) * 2005-05-24 2011-10-12 株式会社小松製作所 Transmission

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102374269A (en) * 2010-08-11 2012-03-14 马里控股公司 Method used for operating continuous changeable transmission device possessing static hydraulic/mechanical torque distribution and transmission device for realizing the method
CN103660910A (en) * 2013-12-06 2014-03-26 合肥工业大学 Gasoline and electricity hydrostatic composite hybrid power transmission system

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109927547A (en) * 2019-03-08 2019-06-25 合肥工业大学 A kind of electromechanical combined formula transmission device
CN109927547B (en) * 2019-03-08 2020-07-03 合肥工业大学 Electromechanical composite transmission device
CN110778677A (en) * 2019-10-08 2020-02-11 长沙桑铼特农业机械设备有限公司 Integrated pump motor with mechanical gear and application method thereof
CN110778677B (en) * 2019-10-08 2020-08-11 长沙桑铼特农业机械设备有限公司 Integrated pump motor with mechanical gear and application method thereof

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