CN208149301U - A kind of drive axle of integrated hydraulic auxiliary Pneumatic braking device - Google Patents
A kind of drive axle of integrated hydraulic auxiliary Pneumatic braking device Download PDFInfo
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- CN208149301U CN208149301U CN201721870313.8U CN201721870313U CN208149301U CN 208149301 U CN208149301 U CN 208149301U CN 201721870313 U CN201721870313 U CN 201721870313U CN 208149301 U CN208149301 U CN 208149301U
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Abstract
The utility model discloses a kind of drive axles of integrated hydraulic auxiliary Pneumatic braking device, including, former vehicle transmission system has the functions such as grade variable delivery hydraulic auxiliary braking system sum aggregate distribution power, differential and driving wheel in the drive axle of one.The deficiencies of installation space that integrated drive axle can make up transmission system in conventional hybrid scheme is big, automobile chassis weight is big, and power transmission line is long；There is grade variable system to replace conventional hybrid variable system using based on working in double modes characteristic, solves that conventional hybrid core element is at high price, the deficiency of poor reliability etc.；The working condition of system is judged according to the signal of the sensor of controller acquisition, and then the discharge capacity of required hydraulic pump/motor is calculated by program, immediate discharge capacity assembled scheme is chosen through a series of control algolithm, control of the commutation valve group realization to hydraulic pump motor working condition is controlled by controller.
Description
Technical field
The utility model relates to technical field of new energy, and in particular to the driving of integrated hydraulic auxiliary Pneumatic braking device
Bridge.
Background technique
With being becoming tight the day of world energy sources, the power saving of automobile more and more attention has been paid to compel by energy and environmental problem
Energy conservation and environmental protection of highly necessary seeking development vehicle, it has also become the common recognition in the world can delay energy consumption and reduce the mixing of disposal of pollutants
Power car becomes the primary research emphasis in countries in the world.In recent years, the research of Hydrostatic drive hybrid vehicle achieves very
Big progress, gradually causes the great attention of national governments, research institution and major automobile vendor.The technology utilizes hydraulic pump/horse
Up to the characteristic for being operable with four-quadrant, the kinetic energy that conventional truck is wasted in braking is recycled, and is stored in hydraulic accumulator, institute
The energy of recycling can provide auxiliary power in vehicle launch or acceleration, to reduce engine installed power or improve vehicle
Driving capability in short-term makes engine more work in economic zone, reduces oil consumption, reduces harmful tailpipe emissions.Hydraulic system
The characteristics of high power density, makes the technology be particularly suitable for having in frequent start-stop operating condition, in heavy duty vehicle.Hydrostatic passes
Driven mixed power vehicle is classified as one of the big crucial research contents of energy conservation and environmental protection vehicle three (electricity by Environmental Protection Agency (EPA)
Driven mixed power vehicle, Hydrostatic drive hybrid vehicle and cleaning diesel technology).
Current hybrid power scheme still uses the axle structure in conventional hybrid vehicle power train, vehicle bridge, transfer
Two independent components of case are connected by transmission shaft, and this structure is primarily present following defect：(1) installation space of transmission system
Greatly, big (2) power transmission line of automobile chassis weight is long, transmission efficiency reduces, poor (3) components of transmission performance are more, manufacture and
Installation cost is high.
The key element in hydraulic hybrid power system --- secondary component --- is all made of plunger variable element at present,
Extremely sensitive to oil contamination, reliability is poor；The problems such as in control there are variable low-response, null offset, vulnerable to interference.
Not only secondary component is in this way, there is the above problem in plunger type variable capacity pump, motor, and its high cost also becomes hydraulic pressure system
The factor that system user must be taken into consideration.Analog control variable mode traditional simultaneously, especially with the SERVO CONTROL of feedback
Middle needs carry out multiple A/D, D/A conversion, are also easy to produce commutation error and sluggishness.These disadvantages hinder hydraulic to a certain extent
Technology of Hybrid Electric Vehicle development and use.With becoming increasingly popular for digital control technology, using can be directly right with digital control form
The discrete type variable mode connect can be good at overcoming the above problem.
Chinese patent publication No. is CN102141040B, and date of publication is on December 14th, 2016, and utility model is entitled " more
Gear pump has a grade variable system ", apply for artificial Jilin University.The patent has a grade variable system using multiple constant displacement pumps/motor composition
System, it is real by common switch valve logic control using the pump/motor of lowest displacement in composite sequence as variable minimal gradient
Existing pump/motor displacement has grade adjusting.Its element is restructured using series connection gear pump/motor, has suction capacity strong, domestic
Change technology maturation, it is cheap the advantages that, but have steps transition of grade variable in multivariable process due to discharge capacity that can cause
On the one hand phenomena such as buffeting of impact and system in fluid pressure line, easily causes the reduction of system reliability, on the other hand can also
The comfort of operator can be deteriorated, this defect be limit one in this technology development and application to hybrid vehicle is great
Problem.
Hydraulic pump/motor is a kind of Hydraulic Elements that operating mode is reversible.In having grade variable number hydraulic pump/motor,
Assembled unit therein can be made to work in pump or motor both of which using the change of oil circuit.When it works in pump mode,
Absorb mechanical energy, output hydraulic pressure energy；When it works in motoring mode, hydraulic energy, output mechanical energy are absorbed.Based on above-mentioned original
Reason, if mechanical-hydraulic can be allocated and convert inside multi-stage variable digital hydraulic pump/motor, so that it may increase greatly
Add the combination of discharge capacity.
Utility model content
The technical issues of the utility model is solved is the installation space for making up transmission system in conventional hybrid scheme
Greatly, automobile chassis weight is big, and power transmission line is long, and transmission efficiency is low, transmission performance is poor, and components are more, manufacture and be mounted to
This height and core secondary component are at high price, poor reliability sensitive to oil contamination, variable low-response, zero point drift in control
It moves, vulnerable to interference, tradition proposes a kind of integrated with the presence of the deficiency of grade variable control system torque shock, system chatter etc.
The drive axle of hydraulic auxiliary Pneumatic braking device.
In order to solve the above technical problems, the utility model adopts the following technical scheme that realization：
A kind of drive axle of integrated hydraulic auxiliary Pneumatic braking device, including former vehicle transmission system:Engine, turns gearbox
Angular-rate sensor at fast sensor, brake pedal, brake pedal, gas pedal, angular-rate sensor at gas pedal, it is main from
Clutch, right side wheels, right side friction brake, left side wheel, left side friction brake, hydraulic auxiliary brake system：Hydraulic pump/
Groups of motors, clutch, commutation valve group, pressure sensor, accumulator, shut-off valve open in usual, normally closed type shut-off valve, overflow valve, oil
Case, filter, thermometer integrate the drive axle of the functions such as distribution power, differential and driving wheel:Transfer gear, drive axle
Shell, differential mechanism, differential carrier, differential spider pinion shaft, differential side gear one, differential pinion gear, differential mechanism half
Shaft gear two, main reducing gear, main reducing gear driven wheel of differential, main reducing gear drive bevel gear, controller, flange.
Preferably, the differential mechanism includes differential carrier, differential spider pinion shaft, differential side gear one, differential
Device planetary gear, differential side gear two, the main reducing gear include main reducing gear driven wheel of differential, main reducing gear initiative taper
Gear.The driven wheel of differential of main reducing gear is fixed on the flange of differential carrier with bolt or rivet, the axle journal of planetary gear shaft
Corresponding groove is formed by hole on differential carrier end face, on two side shaft journals equal empty boasting a differential spider tooth
Wheel, they are engaged with differential side gear one and differential side gear two respectively, and the axle journal of axle shaft gear is respectively in differential
In the corresponding bore of device shell, and it is connected by spline with semiaxis, the transfer gear is engaged with the driven wheel of differential of main deceleration.
The original vehicle transmission system is by engine, gearbox, speed probe, brake pedal angular-rate sensor, system
Dynamic pedal, gas pedal, angular-rate sensor, main clutch, right side wheels, right side friction brake, left side at gas pedal
The composition such as wheel, left side friction brake, engine, main clutch, gearbox, speed probe are sequentially coaxially connected, revolving speed
Sensor output shaft is coaxially connected with the main reducing gear drive bevel gear in driving axle housing, angle speed at brake pedal, brake pedal
Degree sensor, gas pedal, angular-rate sensor is mounted in driver's cabin at gas pedal, and left side wheel semiaxis is rubbed by left side
It wipes brake to be connected with left side wheel, right side wheels semiaxis is connected by right side friction brake with right side wheels.
Preferably, the clutch uses electromagnetic clutch.
The output shaft of the transfer gear and the input hole of clutch are coupled, the delivery outlet of clutch and hydraulic pump/horse
Axis up to group is coupled, and hydraulic pump/motor group is fixed on axle housing by flange.
The reversal valve used in the utility model commutation valve group is the three-position four-way electromagnetic directional valve with p-type Median Function
Or electro-hydraulic reversing valve, or identical function can be reached with the three-position four-way electromagnetic directional valve or electro-hydraulic reversing valve of p-type Median Function
The combination of other valves of effect.
Preferably, the hydraulic pump/motor used in the hydraulic pump/motor group is gear pump motor.
It include the hydraulic pump/motor of at least two different displacements in the hydraulic pump/motor group, each hydraulic pump/motor is adopted
It is connected with axis.The hydraulic pump/motor respectively correspond one described in reversal valve, the P mouth of each hydraulic pump/motor
The P mouth of reversal valve is connected, the T mouth of each reversal valve is separately connected the T mouth of corresponding hydraulic pump/motor, and hydraulic pump/motor is by changing
It is followed by fuel tank through filter to the B mouth of valve, the A mouth of each reversal valve is connected with total hydraulic fluid port, and total hydraulic fluid port divides two-way, all the way often
Open type shut-off valve connects accumulator, takes back fuel tank through normally closed type shut-off valve all the way.Fuel tank attachment has thermometer.
The digital output end of controller connects the controlled end of reversal valve and the controlled end of clutch, the simulation of controller respectively
Amount output end connects the controlled end of Pneumatic braking system (not shown) and the controlled end of engine, analog input termination braking respectively
The output end of angular-rate sensor at pedal, the output end of angular-rate sensor at gas pedal, speed probe output end and
The output end of pressure sensor.
The utility model is controlled corresponding hydraulic by controlling the operating position of each reversal valve in commutation valve group
Pump/motor works in pump state, motor condition or idling conditions respectively, enable mechanical-hydraulic multi-stage variable digital hydraulic pump/
It is allocated and converts inside motor, realize that discharge capacity has grade variation.When the work of reversal valve left position, hydraulic pump correspondingly/
The T mouth of motor, from fuel tank oil suction, works in hydraulic pump state through reversal valve, when the right position work of reversal valve, coaxially in hydraulic
The high pressure oil of hydraulic pump/motor or the accumulator discharge of pump state enters corresponding hydraulic pump/horse through the A-T oil circuit of reversal valve
It reaches, drives corresponding hydraulic pump/motor, make its work in motor condition.When position in reversal valve, corresponding hydraulic pump/motor discharge
Oil liquid a part by reversal valve enter hydraulic pump/motor pump in circulation make its idle running, another part is through hydraulic pump/motor
After flow back to fuel tank, convenient for heat dissipation, corresponding hydraulic pump/motor is in unloading condition.
The expression formula of hydraulic booster system hydraulic pump/motor effective discharge described in the utility model is V=a1V1+a2V2+
a3V3+……+anVn, anValue be -1,0 or 1, n is the natural number more than or equal to 2.To keep discharge capacity gradient constant, hydraulic pump/
Motor displacement presses Vn=V13n-1Value, then the discharge capacity after combining can be 0, V1,V2-V1,V2,V1+V2,V3-V1-V2, V3-
V2... ..., V1+V2+……VnValue in range, discharge capacity is with minimum injection rate V1For step pitch stepped change, range of variables is 0~(3n-
1)/2, variable series is (3n+1)/2。
The control method of the drive axle of above-mentioned integrated hydraulic auxiliary Pneumatic braking device includes the following steps：
Signal detection:Four tunnel analog signals are acquired by sensor：Accelerator pedal angle αm, angle of brake pedal αp, transmission
Axis revolving speed v, energy storage pressure p carry out judgement and calculate with data；
Operating condition selection:According to the signal of the signal of gas pedal collected and brake pedal, the work of hydraulic system is judged
Make state；When gas pedal has signal output, i.e., vehicle is in driving process, when brake pedal has signal output, i.e. vehicle
Be in braking process；
Drive course control method for use：Turn if the driving torque that hydraulic hybrid power system provides can satisfy requirement drive
Then vehicle is operated alone by hydraulic hybrid power system in square, otherwise provides the driving moment of supplement by engine with meet demand
Torque；When rotating speed of transmission shaft v exceeds a certain range, vehicle is operated alone by former motor vehicle drive system in disconnection electromagnetic clutch, on the contrary
Continue to execute following control：Firstly, calculating target torque:T=Kmαm, wherein KmTo drive gain coefficient, secondly, calculated pump rate
Demand:V=2 π T/p, finally, according to different target discharge capacity V, from V1,V2-V1,V2,V1+V2,V3-V1-V2, V3-V2... ..., V1
+V2+……VnIt is middle to choose the combination closest to the hydraulic pump/motor group 14 of scheme, commutation valve group, realization pair are controlled by controller
The control of the discharge capacity combination of hydraulic pump/motor group, and then realize permanent torque starting；
Braking process control method：First, it is determined that hydraulic system pressure, if hydraulic system pressure is greater than system most senior engineer
Make pressure, then electromagnetic clutch disconnects, hydraulic pump/motor group discharge capacity is zero disconnection hydraulic system；Secondly, hydraulic system pressure is just
Chang Shi measures the real-time speed v of transmission shaft according to speed probe and substitutes into formulaCalculate severity of braking；Finally, sentencing
Disconnected severity of braking Z size, if severity of braking Z >=0.7, system enter emergency brake modes, if severity of braking Z < 0.7, system
Dynamic system is in service brake mode；
Emergency brake modes control flow：Electromagnetic clutch engagement, hydraulic pump/motor group discharge capacity keep maximum value, air pressure
Braking is calculated by corresponding braking percentage；
Service brake mode control flow：Firstly, judging whether vehicle is in forward travel state according to neutral gear and the state of reversing gear；
Secondly, determining whether hydraulic system participates in braking according to secondary component revolving speed：Have when hydraulic pump/motor revolving speed is greater than its minimum
When imitating revolving speed, braking preferentially uses hydraulic braking moment, and braking moment is according to formula T=KpαpIt calculates, wherein KpFor braking moment
Gain coefficient, hydraulic braking moment insufficient section are made up by air-pressure brake torque, and hydraulic pump/motor demand discharge capacity is according to public affairs
Formula V=2 π T/p are calculated, according to different target discharge capacity V, from V1,V2-V1,V2,V1+V2,V3-V1-V2,V 3-V2... ..., V1+V2
+……VnIt is middle to choose the combination closest to the hydraulic pump/motor group (14) of scheme, commutation valve group is controlled by controller (29)
(13), it realizes the control of the discharge capacity combination to hydraulic pump/motor group (14), and then realizes permanent torque control；Work as hydraulic pump/motor
When revolving speed is less than its minimum effective revolving speed, hydraulic system is completely cut through.
Compared with prior art, the utility model has the beneficial effects that：
The drive axle of integrated hydraulic auxiliary Pneumatic braking device described in the utility model, makes transfer case, differential mechanism, main deceleration
The transmission of being integrally formed of device, eliminates drive shaft, shortens drive path, improve the mechanical efficiency in transmission system, simultaneously
It completes to functions such as hydraulic auxiliary brake system distribution power, differential and driving wheels, keeps conventional system architecture compact, mitigate
Quality, is conducive to the lightweight of automobile chassis.
The drive axle of integrated hydraulic auxiliary Pneumatic braking device described in the utility model, which uses, is based on digital hydraulic pump/horse
The digitalization control method for having grade variable system up to working in double modes characteristic solves compared with conventional hybrid system
Traditional core secondary component is at high price, extremely sensitive to oil contamination, and reliability is poor, in control there are variable low-response,
Null offset, vulnerable to interference the problems such as, using solenoid directional control valve or electro-hydraulic reversing valve carry out control solve traditional analog quantity
Variable mode is controlled, is converted especially with needing to carry out multiple A/D, D/A in the SERVO CONTROL of feedback, is also easy to produce commutation error
With sluggish problem.
The drive axle of integrated hydraulic auxiliary Pneumatic braking device described in the utility model, which uses, is based on digital hydraulic pump/horse
Up to the digitalization control method for having grade variable system of working in double modes characteristic, based on number compared with tradition has grade variable system
Hydraulic pump/motor working in double modes characteristic has grade variable system that can realize smaller variable ladder with identical assembled unit number
Degree, or realize identical discharge capacity adjustable range using less assembled unit number, effectively reduce discharge capacity gradient or expand variable grade
Number, to variable pressure impact is reduced, improving system chatter has good effect, has largely improved a grade variable system
Movement regularity and stability so that the comfort in the service life of mechanical organ, the reliability of system and operator all obtains very
It is big to improve.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of the drive axle of integrated hydraulic auxiliary Pneumatic braking device described in the utility model.
In figure：1. angular-rate sensor at brake pedal, 2. brake pedals, 3. gas pedals, angle speed at 4. gas pedals
Degree sensor, 5. pressure sensors, 6. accumulators, 7, shut-off valve open in usual, 8. normally closed type shut-off valves, 9. overflow valves, 10. oil
Case, 11. filters, 12. thermometers, 13. commutation valve groups, 14. hydraulic pump/motor groups, 15. flanges, 16. clutches, 17. transfers
Device, 18. left side wheels, 19. left side friction brakes, 20. driving axle housings, 21. differential mechanisms, 21-1. differential carrier, 21-2. are poor
Fast device planetary gear shaft, 21-3. differential side gear one, 21-4. differential side gear two, 21-5. differential spider tooth
Wheel, 22. main reducing gears, 22-1. main reducing gear driven gear, 22-2. main reducing gear driving gear, 23. main clutch, 24. hairs
Motivation, 25. gearboxes, 26. speed probes, 27. right side friction brakes, 28. right side wheels, 29. controllers.
Specific implementation method
The utility model is explained in detail with reference to the accompanying drawing：
Refering to fig. 1, the drive axle of integrated hydraulic auxiliary Pneumatic braking device, including former vehicle transmission system:Engine 24, speed change
Case 25, speed probe 26, brake pedal 2, angular-rate sensor 1 at brake pedal, gas pedal 3, angle speed at gas pedal
Sensor 4, main clutch 23, right side wheels 28, right side friction brake 27, left side wheel 18, left side friction brake 19 are spent,
Hydraulic auxiliary brake system：It is hydraulic pump/motor group 14, clutch 16, commutation valve group 13, pressure sensor 5, accumulator 6, normally opened
Formula shut-off valve 7, normally closed type shut-off valve 8, overflow valve 9, fuel tank 10, filter 11, thermometer 12, collection distribution power, differential and drive
The functions such as motor car wheel are in the drive axle of one：Transfer gear 17, driving axle housing 20, differential mechanism 21, differential carrier 21-1, differential mechanism row
Star gear shaft 21-2, one 21-3 of differential side gear, two 21-4 of differential side gear, differential pinion gear 21-5, master
Retarder 22, main reducing gear driven wheel of differential 22-1, main reducing gear drive bevel gear 22-2, controller 29, flange 15.
In the present embodiment, the differential mechanism 21 includes differential carrier 21-1, differential spider pinion shaft 21-2, differential mechanism half
One 21-3 of shaft gear, two 21-4 of differential side gear, differential pinion gear 21-5, the main reducing gear 22 include main deceleration
Device driven wheel of differential 22-1, main reducing gear drive bevel gear 22-2.The driven wheel of differential 22-1 bolt or rivet of main reducing gear
(not shown) is fixed on the flange of differential carrier 21-1, and the axle journal of planetary gear shaft 21-2 is on the end face differential carrier 21-1
Corresponding groove is formed by hole, on two side shaft journals equal empty boasting a differential pinion gear 21-5, they respectively with difference
Fast one 21-3 of device axle shaft gear and two 21-4 of differential side gear engagement, the axle journal of axle shaft gear is respectively in differential carrier 21-1
In corresponding bore, and it is connected by spline with semiaxis, the transfer gear 17 is engaged with the driven wheel of differential 22-1 of main deceleration.
The original vehicle transmission system is sensed by engine 24, gearbox 25, speed probe 26, brake pedal angular speed
Device 1, brake pedal 2, gas pedal 3, angular-rate sensor 4, main clutch 23, right side wheels 28, right side are rubbed at gas pedal
The composition such as brake 27, left side wheel 18, left side friction brake 19 is wiped, engine 24, gearbox 25, turns main clutch 23
Fast sensor 26 is sequentially coaxially connected, the main reducing gear drive bevel gear in 26 output shaft of speed probe and driving axle housing 20
22-2 is coaxially connected, angular-rate sensor 1 at brake pedal 2, brake pedal, gas pedal 3, angular speed sensing at gas pedal
Device 4 is mounted in driver's cabin, and left side wheel semiaxis is connected by left side friction brake 19 with left side wheel 18, right side wheels half
Axis is connected by right side friction brake 27 with right side wheels 28.
In the present embodiment, the clutch 16 uses electromagnetic clutch.
The input hole of the output shaft and clutch 16 of the transfer gear 17 is coupled, the delivery outlet of clutch 16 with it is hydraulic
The axis of pump/motor group 14 is coupled, and hydraulic pump/motor group 14 is fixed on driving axle housing 20 by flange 15.
In the present embodiment, the reversal valve used in the commutation valve group 13 is the 3-position 4-way electricity with p-type Median Function
Magnetic reversal valve, the hydraulic pump/motor used in the hydraulic pump/motor group 14 is gear pump motor.
It include the hydraulic pump/motor of at least two different displacements, each hydraulic pump/motor in the hydraulic pump/motor group 14
It is connected using axis.The hydraulic pump/motor respectively correspond one described in reversal valve, the P of each hydraulic pump/motor
The P mouth of mouth connection reversal valve, the T mouth of each reversal valve are separately connected the T mouth of corresponding hydraulic pump/motor, and hydraulic pump/motor passes through
The B mouth of reversal valve connected tank 10 after filter 11, the A mouth of each reversal valve are connected with total hydraulic fluid port, and total hydraulic fluid port divides two-way, and one
Road connects accumulator 6 through shut-off valve 7 open in usual, takes back fuel tank 10 through normally closed type shut-off valve 8 all the way.10 attachment of fuel tank has thermometer
12。
The digital output end of controller 29 connects the controlled end of reversal valve and the controlled end of clutch 16, controller 29 respectively
Analog output end connect the controlled end of Pneumatic braking system (not shown) and the controlled end of engine 24, analog input respectively
Terminate the output end of angular-rate sensor 1 at brake pedal, at gas pedal angular-rate sensor 4 output end, revolution speed sensing
The output end of device 26 output end and pressure sensor 5.
The utility model controls corresponding liquid by controlling the operating position of each reversal valve in commutation valve group 13
Pressure pump/motor works in pump state, motor condition or idling conditions respectively, enables mechanical-hydraulic in multi-stage variable digital hydraulic
It is allocated and converts inside pump/motor, realize that discharge capacity has grade variation.When the work of reversal valve left position, correspondingly hydraulic
The T mouth of pump/motor, from 10 oil suction of fuel tank, works in hydraulic pump state through reversal valve, when the right position work of reversal valve, is coaxially in
The high pressure oil of hydraulic pump/motor or accumulator 6 discharge of hydraulic pump state enters corresponding hydraulic through the A-T oil circuit of reversal valve
Pump/motor drives corresponding hydraulic pump/motor, makes its work in motor condition.When position in reversal valve, corresponding hydraulic pump/motor
Oil liquid a part of discharge, which enters hydraulic pump/motor circulation in pump by reversal valve, makes its idle running, another part through hydraulic pump/
Fuel tank 10 is flowed back to after motor, convenient for heat dissipation, corresponding hydraulic pump/motor is in unloading condition.
The expression formula of 14 effective discharge of hydraulic booster system hydraulic pump/motor group described in the utility model is V=a1V1+
a2V2+a3V3+……+anVn, anValue be -1,0 or 1, n is the natural number more than or equal to 2.To keep discharge capacity gradient constant, liquid
Pump/motor displacement is pressed to press Vn=V13n-1Value, then the discharge capacity after combining can be 0, V1,V2-V1,V2,V1+V2,V3-V1-V2, V3-
V2... ..., V1+V2+……VnValue in range, discharge capacity is with minimum injection rate V1For step pitch stepped change, range of variables is 0~(3n-
1)/2, variable series is (3n+1)/2。
The working principle of hydraulic auxiliary brake system:
When hydraulic auxiliary brake system participates in auxiliary vehicle braking system, at this point, in pump in hydraulic pump/motor group 14
The discharge capacity of the hydraulic pump/motor of operating condition and greater than the hydraulic pump/motor in motor operating conditions discharge capacity and, i.e. hydraulic pump/motor
Group 14 can be equivalent to the hydraulic pump/motor for being in pump condition, coordinate common offer braking torque with former vehicle braking system,
By partial brake energy regenerating, the hydraulic pump/motor in pump condition is from fuel tank 10 through reversal valve from 10 oil suction of fuel tank and through changing
Liquid pressure energy is converted by the kinetic energy of vehicle to 6 filling liquid of accumulator to valve to be stored in accumulator 6；When vehicle launch, accelerate
When driving, accumulator 6, which discharges high pressure oil driving hydraulic pump/motor group 14, makes it work in motor operating conditions, by liquid in accumulator 6
Pressure be converted into kinetic energy, coordinate to provide vehicle launch or while giving it the gun required torque with former car engine.
The control method of the drive axle of the integrated hydraulic auxiliary Pneumatic braking device, it is characterised in that, including following step
Suddenly：
Signal detection:Four tunnel analog signals are acquired by sensor：3 angle [alpha] of gas pedalm, 2 angle [alpha] of brake pedalp, pass
Moving axis revolving speed v, 6 pressure p of accumulator carry out judgement and calculate with data.
Operating condition selection:According to the signal of the signal of gas pedal 3 collected and brake pedal 2, hydraulic system is judged
Working condition.
When gas pedal 3 has signal output, i.e., vehicle is in driving process, when brake pedal 2 has signal output, i.e.,
Vehicle is in braking process.
Drive course control method for use：
If the driving torque that hydraulic hybrid power system provides can satisfy requirement drive torque, by hydraulic hybrid
Vehicle is operated alone in system, otherwise provides the driving moment of supplement by engine 24 with meet demand torque.
When rotating speed of transmission shaft v exceeds a certain range, vehicle is operated alone by former motor vehicle drive system in disconnection electromagnetic clutch 16
, otherwise continue to execute following control：
Calculate target torque:
T=Kmαm(1), wherein KmTo drive gain coefficient；
Calculated pump rate demand:V=2 π T/p (2)；
According to different target discharge capacity V, from V1,V2-V1,V2,V1+V2,V3-V1-V2, V3-V2... ..., V1+V2+……VnIn
Choose closest to scheme hydraulic pump/motor group 14 combination, by controller 29 control commutation valve group 13, realize to hydraulic pump/
The control of the discharge capacity combination of groups of motors 14, and then realize permanent torque starting.
Braking process control method：
It is divided into emergency braking and service brake both of which at this time.Severity of braking calculation formula is：
In formula：G-acceleration of gravity
As Z >=0.7, system thinks that vehicle is in emergency brake modes, and as severity of braking Z < 0.7, system thinks vehicle
Be in service brake mode.
Control flow：First, it is determined that hydraulic system pressure, if hydraulic system pressure is greater than system maximum working pressure,
Then electromagnetic clutch 16 disconnects, 14 discharge capacity of hydraulic pump/motor group is zero disconnection hydraulic system；Secondly, hydraulic system pressure is normal
When, real-time speed v substitution formula (3) of transmission shaft is measured according to speed probe 26 and calculates severity of braking；Finally, judgement braking
Intensity Z size, if severity of braking Z >=0.7, system enter emergency brake modes, if severity of braking Z < 0.7, braking system
In service brake mode.
Emergency brake modes control flow：Electromagnetic clutch 16 engages, and 14 discharge capacity of hydraulic pump/motor group keeps maximum value,
Air-pressure brake is calculated by corresponding braking percentage；
Service brake mode control flow：Firstly, judging whether vehicle is in forward travel state according to neutral gear and the state of reversing gear；
Secondly, determining whether hydraulic system participates in braking according to secondary component revolving speed：Have when hydraulic pump/motor revolving speed is greater than its minimum
When imitating revolving speed, braking preferentially uses hydraulic braking moment, and braking moment is according to formula T=Kpαp(4), wherein KpFor braking moment
Gain coefficient, hydraulic braking moment insufficient section are made up by air-pressure brake torque, and hydraulic pump/motor demand discharge capacity is according to public affairs
Formula (2) calculates, according to different target discharge capacity V, from V1,V2-V1,V2,V1+V2,V3-V1-V2, V3-V2... ..., V1+V2+……Vn
It is middle to choose the combination closest to the hydraulic pump/motor group 14 of scheme, commutation valve group 13 is controlled by controller 29, is realized to hydraulic
The control of the discharge capacity combination of pump/motor group 14, and then realize permanent torque control；Have when hydraulic pump/motor revolving speed is less than its minimum
When imitating revolving speed, hydraulic system is completely cut through.
14 discharge capacity combined method concrete application example of hydraulic pump/motor group：
Below with n=3, V1=10mL/r (No. I), V2=30mL/r (No. II), V3To this reality for=90mL/r (No. III)
It is illustrated with novel middle 14 discharge capacity combined method of hydraulic pump/motor group.
N=3, V1=10mL/r (No. I), V2=30mL/r (No. II), V3=90mL/r (No. III) is then producible to be equivalent to
The discharge capacity of pump combines and corresponding reversal valve state is as shown in table 1, the producible discharge capacity combination for being equivalent to motor and corresponding
("+" indicates that reversal valve corresponds to electromagnet energization to reversal valve state, and it is obstructed that "-" indicates that reversal valve corresponds to electromagnet as shown in table 2
Electricity).
Table 1
| 1DT | 1YA | 2DT | 2YA | 3DT | 3YA | Discharge capacity (mL/r) |
| + | ─ | ─ | ─ | ─ | ─ | 10 |
| ─ | + | + | ─ | ─ | ─ | 20 |
| ─ | ─ | + | ─ | ─ | ─ | 30 |
| + | ─ | + | ─ | ─ | ─ | 40 |
| ─ | + | ─ | + | + | ─ | 50 |
| ─ | ─ | ─ | + | + | ─ | 60 |
| + | ─ | ─ | + | + | ─ | 70 |
| ─ | + | ─ | ─ | + | ─ | 80 |
| ─ | ─ | ─ | ─ | + | ─ | 90 |
| + | ─ | ─ | ─ | + | ─ | 100 |
| + | ─ | + | ─ | + | ─ | 110 |
| ─ | ─ | + | ─ | + | ─ | 120 |
| + | ─ | + | ─ | + | ─ | 130 |
Table 2
When auxiliary braking, controller selects practical pump motor discharge capacity according to pump motor demand discharge capacity is calculated, and selects
Program is referring to the principle that rounds up.Referring to table 1, when calculating pump motor discharge capacity is 5-14.9mL/r, control pump motor discharge capacity is meter
When to calculate pump motor discharge capacity be 10mL/r, control pump motor discharge capacity is to calculate pump motor discharge capacity when being 15-24.9mL/r, control pump horse
It is 20mL/r up to discharge capacity, when calculating pump motor discharge capacity is 25-34.9mL/r, control pump motor discharge capacity is 30mL/r, calculates pump horse
Up to discharge capacity be 35-44.9mL/r when, control pump motor discharge capacity be 40mL/r, calculate pump motor discharge capacity be 45-54.9mL/r when, control
Pump motor discharge capacity processed is 50mL/r, and when calculating pump motor discharge capacity is 55-64.9mL/r, control pump motor discharge capacity is 60mL/r, meter
When calculation pump motor discharge capacity is 65-74.9mL/r, control pump motor discharge capacity is 70mL/r, and calculating pump motor discharge capacity is 75-84.9mL/
When r, control pump motor discharge capacity is 80mL/r, and when calculating pump motor discharge capacity is 85-94.9mL/r, control pump motor discharge capacity is
90mL/r, when calculating pump motor discharge capacity is 95-104.9mL/r, control pump motor discharge capacity is 100mL/r, calculates pump motor discharge capacity
When for 105-114.9mL/r, control pump motor discharge capacity is 110mL/r, when to calculate pump motor discharge capacity be 115-124.9mL/r, control
Pump motor discharge capacity processed is 120mL/r, and when calculating pump motor discharge capacity is 125-134.9mL/r, control pump motor discharge capacity is 130mL/
r。
It is identical when discharge capacity combined method is with auxiliary braking when auxiliary drive, referring to table 2.
It is only preferred embodiments of the present invention described in upper, the protection scope of the utility model is not limited merely to
Embodiment is stated, technical solution belonging to the idea of the present invention belongs to the protection scope of the utility model.It should be pointed out that
For those skilled in the art, several improvement without departing from the principle of the utility model and profit
Decorations, are regarded as the protection scope of the utility model.
Claims (4)
1. a kind of drive axle of integrated hydraulic auxiliary Pneumatic braking device, which is characterized in that including former vehicle transmission system:Engine
(24), gearbox (25), speed probe (26), brake pedal (2), angular-rate sensor (1), gas pedal at brake pedal
(3), angular-rate sensor (4), main clutch (23), right side wheels (28), right side friction brake (27), a left side at gas pedal
Side wheel (18), left side friction brake (19), hydraulic auxiliary brake system：Hydraulic pump/motor group (14), clutch (16),
Commutation valve group (13), pressure sensor (5), accumulator (6), shut-off valve open in usual (7), normally closed type shut-off valve (8), overflow valve
(9), fuel tank (10), filter (11), thermometer (12) integrate the drive of the functions such as distribution power, differential and driving wheel
Dynamic bridge：Transfer gear (17), driving axle housing (20), differential mechanism (21), differential carrier (21-1), differential spider pinion shaft (21-
2), differential side gear one (21-3), differential side gear two (21-4), differential pinion gear (21-5), main deceleration
Device (22), main reducing gear driven wheel of differential (22-1), main reducing gear drive bevel gear (22-2), controller (29), flange (15)；
The differential mechanism (21) includes differential carrier (21-1), differential spider pinion shaft (21-2), differential side gear one
(21-3), differential side gear two (21-4), differential pinion gear (21-5), the main reducing gear (22) includes main deceleration
Device driven wheel of differential (22-1), main reducing gear drive bevel gear (22-2)；The driven wheel of differential (22-1) of main reducing gear uses bolt
Or rivet is fixed on the flange of differential carrier (21-1), the axle journal of planetary gear shaft (21-2) is held embedded in differential carrier (21-1)
Corresponding groove is formed by hole on face, on two side shaft journals equal empty boasting a differential pinion gear (21-5), they point
It is not engaged with differential side gear one (21-3) and differential side gear two (21-4), the axle journal of axle shaft gear is respectively in difference
In the corresponding bore of fast device shell (21-1), and it is connected by spline with semiaxis, the transfer gear (17) is driven with main reducing gear
Bevel gear (22-1) engagement；The input hole of the output shaft and clutch (16) of the transfer gear (17) is coupled, clutch
(16) delivery outlet and the axis of hydraulic pump/motor group (14) are coupled, and hydraulic pump/motor group (14) is fixed by flange (15)
On driving axle housing (20)；
It include the hydraulic pump/motor of at least two different displacements in the hydraulic pump/motor group (14), each hydraulic pump/motor is adopted
It is connected with axis；The hydraulic pump/motor respectively correspond one described in a reversal valve in commutation valve group (13),
The P mouth of the P mouth connection reversal valve of each hydraulic pump/motor, the T mouth of each reversal valve are separately connected the T of corresponding hydraulic pump/motor
Mouthful, hydraulic pump/motor connected tank (10), A mouth and total oil of each reversal valve after filter (11) by the B mouth of reversal valve
Mouth is connected, and total hydraulic fluid port divides two-way, connects accumulator (6) through shut-off valve open in usual (7) all the way, connects all the way through normally closed type shut-off valve (8)
Oil return box (10)；
The reversal valve used in commutation valve group (13) is the three-position four-way electromagnetic directional valve or electro-hydraulic with p-type Median Function
Reversal valve, or identical function effect can be reached with the three-position four-way electromagnetic directional valve or electro-hydraulic reversing valve of p-type Median Function
The combination of valve；
The original vehicle transmission system is passed by engine (24), gearbox (25), speed probe (26), brake pedal angular speed
Sensor (1), brake pedal (2), gas pedal (3), angular-rate sensor (4), main clutch (23), right side vehicle at gas pedal
Take turns the composition such as (28), right side friction brake (27), left side wheel (18), left side friction brake (19), engine (24), master
Clutch (23), gearbox (25), speed probe (26) are sequentially coaxially connected, speed probe (26) output shaft and drive axle
Main reducing gear drive bevel gear (22-2) in shell (20) is coaxially connected, angular-rate sensor at brake pedal (2), brake pedal
(1), gas pedal (3), angular-rate sensor (4) is mounted in driver's cabin at gas pedal, left side wheel semiaxis passes through left side
Friction brake (19) is connected with left side wheel (18), and right side wheels semiaxis passes through right side friction brake (27) and right side wheels
(28) it is connected；
The digital output end of controller (29) connects the controlled end and clutch (16) of reversal valve in commutation valve group (13) respectively
The analog output end of controlled end, controller (29) connects the controlled end of Pneumatic braking system and the controlled end of engine, mould respectively
The output end of angular-rate sensor (1) at analog quantity input termination brake pedal, at gas pedal angular-rate sensor (4) output
It holds, the output end of speed probe (26) output end and pressure sensor (5).
2. the drive axle of integrated hydraulic auxiliary Pneumatic braking device according to claim 1, it is characterised in that：Fuel tank (10) is attached
Part has thermometer (12).
3. the drive axle of integrated hydraulic auxiliary Pneumatic braking device according to claim 1, it is characterised in that：The clutch
(16) electromagnetic clutch is used.
4. the drive axle of integrated hydraulic auxiliary Pneumatic braking device according to claim 1, it is characterised in that：Described is hydraulic
The expression formula of auxiliary system hydraulic pump/motor effective discharge is V=a1V1+a2V2+a3V3+L L+anVn, anValue be -1,0 or
1, n is the natural number more than or equal to 2；To keep discharge capacity gradient constant, hydraulic pump/motor discharge capacity presses Vn=V13n-1Value then combines
Discharge capacity afterwards can be 0, V1,V2-V1,V2,V1+V2,V3-V1-V2, V3-V2... ..., V1+V2+……VnValue in range, discharge capacity with
Minimum injection rate V1For step pitch stepped change, range of variables is 0~(3n- 1)/2, variable series is (3n+1)/2。
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201721406543 | 2017-10-27 | ||
| CN2017214065439 | 2017-10-27 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN208149301U true CN208149301U (en) | 2018-11-27 |
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ID=64413167
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201721870313.8U Withdrawn - After Issue CN208149301U (en) | 2017-10-27 | 2017-12-28 | A kind of drive axle of integrated hydraulic auxiliary Pneumatic braking device |
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| Country | Link |
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| CN (1) | CN208149301U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107985290A (en) * | 2017-10-27 | 2018-05-04 | 吉林大学 | A kind of drive axle and its control method of integrated hydraulic auxiliary Pneumatic braking device |
| CN113280011A (en) * | 2021-05-11 | 2021-08-20 | 中冶宝钢技术服务有限公司 | Static pressure driving system of vehicle and control method thereof |
| CN115352419A (en) * | 2022-08-23 | 2022-11-18 | 中国人民解放军陆军装甲兵学院 | Hydraulic control system and method for snow pressing vehicle capable of recycling braking energy |
-
2017
- 2017-12-28 CN CN201721870313.8U patent/CN208149301U/en not_active Withdrawn - After Issue
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107985290A (en) * | 2017-10-27 | 2018-05-04 | 吉林大学 | A kind of drive axle and its control method of integrated hydraulic auxiliary Pneumatic braking device |
| CN107985290B (en) * | 2017-10-27 | 2023-04-28 | 吉林大学 | Driving axle integrated with hydraulic auxiliary pneumatic braking device and control method thereof |
| CN113280011A (en) * | 2021-05-11 | 2021-08-20 | 中冶宝钢技术服务有限公司 | Static pressure driving system of vehicle and control method thereof |
| CN113280011B (en) * | 2021-05-11 | 2022-10-21 | 中冶宝钢技术服务有限公司 | Hydrostatic drive system for vehicle and control method thereof |
| CN115352419A (en) * | 2022-08-23 | 2022-11-18 | 中国人民解放军陆军装甲兵学院 | Hydraulic control system and method for snow pressing vehicle capable of recycling braking energy |
| CN115352419B (en) * | 2022-08-23 | 2024-04-16 | 中国人民解放军陆军装甲兵学院 | Hydraulic control system and method for snow pressing vehicle capable of recycling braking energy |
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