CN203439027U - Hydraulic auxiliary drive and brake system - Google Patents
Hydraulic auxiliary drive and brake system Download PDFInfo
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- CN203439027U CN203439027U CN201320519796.2U CN201320519796U CN203439027U CN 203439027 U CN203439027 U CN 203439027U CN 201320519796 U CN201320519796 U CN 201320519796U CN 203439027 U CN203439027 U CN 203439027U
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Abstract
The utility model discloses a hydraulic auxiliary drive and brake system, and aims to solve the problems that an existing commercial truck difficultly passes a bad road surface, and brake is instable when a driver brakes after long-time driving. The hydraulic auxiliary drive and brake system comprises an engine, a clutch, a gearbox, a rear drive axle, two front wheels, an accelerator pedal, a brake pedal, a frame, a power take-off unit, an axial wobble plate type high-pressure variable pump, a three-position four-way electromagnetic directional valve, an electric-hydraulic proportional overflow valve, a heat exchanger, a safety valve set, two hydraulic constant displacement motors same in structure, an oil tank and an electronic control unit. The axial wobble plate type high-pressure variable pump is in pipe connection with the three-position four-way electromagnetic directional valve, the three-position four-way electromagnetic directional valve is in pipe connection with the safety valve set, the electric-hydraulic proportional overflow valve and the oil tank, and the two hydraulic constant displacement motors same in structure are in pipe connection with the axial wobble plate type high-pressure variable pump.
Description
Technical field
The utility model relates to a kind of driving and brake equipment that belongs to automobile hydraulic application technology field, and more particularly, the utility model relates to a kind of hydraulic pressure assistive drive and brake system.
Background technology
In recent years, along with the fast development of 21 century automobile industry, the application of secondary adjusting hydrostatic drive technology in conventional truck obtains important breakthrough, and this technology causes domestic and international research institution and automaker's great attention gradually.To hydraulic technique, the applied research on automobile mainly concentrates on colleges and universities at home, relevant hydraulic-driven technology application is many aspect the fluid dynamic coupling system of energy-conserving and environment-protective, comprise parallel connection, series-parallel connection liquid-driving mixed power system etc., the research of hydraulic pressure execution architecture aspect when the application of hydraulic braking technology is also confined to brake more.Abroad, U.S. Eaton company is applied to hydraulic-driven technology on various types of vehicles such as car and urban bus; MIT and German M.A.N company by hydraulic energy-accumulating system applies on urban bus, and in Europe and a plurality of cities, North America use.
Traditional commercial truck, large truck, the operating mode of tractor truck and engineering truck mostly is bad road surface of country or road surface, mine, Chang Po road surface, these roads roughness are larger, adhesion value is generally less, the phenomenon that vehicle often there will be drive wheel to skid while travelling on this road surface, affect dynamic property and the crossing ability of car load, vehicle often runs into the long-time service brake situation of descending simultaneously, need to use continuously or frequently running brake, cause brake wheel and brake plate severe wear, make the easy get out of hand of brake system, not only reduced the service life of running brake, also have a strong impact on travel safety.
Although hydraulic hybrid coupled system part has been improved dynamic property and the braking ability of conventional truck, but it is energy-conservation that main function is, and changing of design is larger, and control algorithm is complicated, cost is high, is not adapted at applying on the vehicles such as traditional load-carrying vehicle, heavy duty truck and tractor truck; The hydraulic resistance retarder that the mechanisms such as University Of Xiangtan propose can improve vehicle braking performances, but does not improve dynamic property and the crossing ability of vehicle when bad road traveling.
Summary of the invention
Technical problem to be solved in the utility model is that to overcome commercial truck crossing ability on bad road surface poor and brake unsettled problem when long-time service brake, proposes a kind of a set of hydraulic pressure assistive drive and the brake system that can simultaneously improve trafficability and insensitivity of installing on the architecture basics of existing vehicle.
For solving the problems of the technologies described above, the utility model adopts following technical proposals to realize, by reference to the accompanying drawings:
The utility model provides a kind of hydraulic pressure assistive drive and brake system, it comprises driving engine 1, power-transfer clutch 2, change speed gear box 4, rear driving axle 5, two trailing wheels 6, two front-wheels 7, acceleration pedal 18, brake pedal 19 and vehicle frames, the crank shaft output shaft 16 of driving engine 1 adopts spline pair to be connected with the input shaft of power-transfer clutch 2, the output shaft of power-transfer clutch 2 adopts spline pair to be connected with the input shaft of change speed gear box 4, and the output shaft of change speed gear box 4 adopts spline pair to be connected with the input shaft of rear driving axle 5; Also comprise power takeoff 3, axial inclined disc type high pressure controllable capacity pump 9,3-position 4-way solenoid directional control valve 10, electricity liquid ratio relief valve 11, H Exch 12, hydraulic pressure fixed displacement motor 15, oil tank 13 and electronic control unit 8 that 14,2 structures of safety valve group are identical, wherein, the input shaft of power takeoff 3 drives the output shaft 17 of annex to adopt spline pair to be connected with driving engine 1, and the output shaft of power takeoff 3 is connected by flange with the rotor shaft of axial inclined disc type high pressure controllable capacity pump 9; Axial inclined disc type high pressure controllable capacity pump 9 is connected with 3-position 4-way solenoid directional control valve 10 pipelines, and 3-position 4-way solenoid directional control valve 10 is connected with safety valve group 14, electricity liquid ratio relief valve 11, oil tank 13 pipelines respectively; The oil inlet pipeline of the hydraulic pressure fixed displacement motor 15 that the oil outlet of safety valve group 14 is identical with 2 structures connects, and 2 the identical oil outlet of hydraulic pressure fixed displacement motor 15 and oil inlet pipelines of axial inclined disc type high pressure controllable capacity pump 9 of structure are connected; The oil outlet of described electricity liquid ratio relief valve 11 is connected with the oil inlet pipeline of H Exch 12, and the oil outlet of H Exch 12 is connected with oil tank 13 pipelines; Electronic control unit 8 is connected with driving engine 1, axial inclined disc type high pressure controllable capacity pump 9,3-position 4-way solenoid directional control valve 10, electricity liquid ratio relief valve 11, acceleration pedal 18 and brake pedal 19 respectively by signal wire (SW).
According to a kind of hydraulic pressure assistive drive provided by the utility model and brake system, the oil outlet of axial inclined disc type high pressure controllable capacity pump 9 is connected by high-voltage oil liquid seal for pipe joints with the P mouth of 3-position 4-way solenoid directional control valve 10, the A mouth of 3-position 4-way solenoid directional control valve 10 is connected by high-voltage oil liquid seal for pipe joints with the oil inlet of safety valve group 14, the B mouth of 3-position 4-way solenoid directional control valve 10 is connected by high-voltage oil liquid seal for pipe joints with the oil inlet of electricity liquid ratio relief valve 11, and the T mouth of 3-position 4-way solenoid directional control valve 10 is connected by the seal for pipe joints of low pressure fluid with oil tank 13; By regulating the position of 3-position 4-way solenoid directional control valve 10 spools, realize the different control position of P mouth and A mouth, B mouth, T mouth, actuating spindle is connected different hydraulic circuits to the oil outlet of inclined disc type high pressure controllable capacity pump 9.
According to a kind of hydraulic pressure assistive drive provided by the utility model and brake system, 2 identical hydraulic pressure fixed displacement motors 15 of structure are arranged on the wheel hub of two front-wheels 7 successively, and axial inclined disc type high pressure controllable capacity pump 9 is fixed on vehicle frame, the oil inlet of the hydraulic pressure fixed displacement motor 15 that the oil outlet of safety valve group 14 is identical with 2 structures connects by high-voltage oil liquid seal for pipe joints, 2 the identical oil outlet of hydraulic pressure fixed displacement motor 15 and oil inlets of axial inclined disc type high pressure controllable capacity pump 9 of structure are connected by high-voltage oil liquid seal for pipe joints, form a hydraulic circuit, 2 the identical output rotor axle of hydraulic pressure fixed displacement motor 15 and semiaxis of two front-wheels 7 of structure adopt gear to be connected with a joggle, by driving the output rotor axle of hydraulic pressure fixed displacement motor 15 to rotate, the hydraulic energy transfer that axial inclined disc type high pressure controllable capacity pump 9 is pumped is mechanical energy, drive front-wheel 7.
According to a kind of hydraulic pressure assistive drive provided by the utility model and brake system, the oil outlet of electricity liquid ratio relief valve 11 is connected by the seal for pipe joints of low pressure fluid with the oil inlet of H Exch 12, the oil outlet of H Exch 12 is connected by the seal for pipe joints of low pressure fluid with oil tank 13, electricity liquid ratio relief valve 11, H Exch 12 and oil tank 13 serial settings.
According to a kind of hydraulic pressure assistive drive provided by the utility model and brake system, the rated pressure of the hydraulic pressure fixed displacement motor 15 that 2 structures are identical is 40MPa, and discharge capacity is 1043ml/r; Axial inclined disc type high pressure controllable capacity pump 9 is discharge capacity 75ml/r, high pressure P 90 pumps of maximum speed of revolution 3600rpm; The Median Function of 3-position 4-way solenoid directional control valve 10 is H shape, and four-hole is connected entirely, pump off-load, and maneuverability pattern is that electromagnet is handled, spring reset, its spool position can left and right adjusting; The high-voltage ratio by pass valve that electricity liquid ratio relief valve 11 is 0-40MPa for range of regulation; H Exch 12 employing operating temperatures are the water-cooled cooler of 40-60 ℃; Safety valve group 14 is comprised of two identical safety valves of structure model of pressure limiting 40MPa, and the installation site of two safety valves is contrary.
According to the control method of a kind of hydraulic pressure assistive drive provided by the utility model and brake system, be: electronic control unit 8 gathers vehicle speed signal, the tach signal of driving engine 1, the position signal of acceleration pedal 18 and brake pedal 19 and hydraulic efficiency pressure system switch key signal judge intention and the vehicle running state of chaufeur, thereby actuating spindle is to inclined disc type high pressure controllable capacity pump 9, 3-position 4-way solenoid directional control valve 10 spool positions, electricity liquid ratio relief valve 11 and driving engine 1 accelerator open degree, realize the switch of hydraulic pressure assistive drive and brake system and the conversion between mode of operation, specifically comprise the following steps:
Step 1, gathers vehicle speed signal, acceleration pedal 18 position signals, brake pedal 19 position signals and hydraulic efficiency pressure system on-off signal;
Step 2, judges that whether the speed of a motor vehicle is greater than 0, if so, enters step 3; Otherwise, illustrate that vehicle, at parking state, enters step 10;
Step 4, vehicle is in braking mode, hydraulic efficiency pressure system is opened and is entered slow braking mode of operation: the spool that electronic control unit 8 sends instruction adjusting 3-position 4-way solenoid directional control valve 10 moves to right position, P mouth and B mouth, T mouth, A mouth are connected, adjusting shaft is maximum to the inclination angle of the swash plate of inclined disc type high pressure controllable capacity pump 9, electronic control unit 8 goes out the anti-driving torque size of hydraulic efficiency pressure system according to vehicle speed signal and braking requirement torque calculation simultaneously, to electricity liquid ratio relief valve 11, send instruction, the oil outlet pressure of regulated variable pump 9, returns to step 2;
Step 8, the speed of a motor vehicle is greater than the speed of a motor vehicle and sets limit value, hydraulic closure system, car load is in the independent drive pattern of driving engine, electronic control unit 8 sends instruction and regulates the spool of 3-position 4-way solenoid directional control valve 10 to move to meta, A mouth, B mouth, P mouth, T mouth are connected mutually, and axial inclined disc type high pressure controllable capacity pump 9 and hydraulic pressure fixed displacement motor 15, all in idling conditions, return to step 2;
Step 9, the speed of a motor vehicle is less than the speed of a motor vehicle and sets limit value, and hydraulic efficiency pressure system is automatically opened and is entered assistive drive mode of operation, enters step 6;
Compared with prior art, the beneficial effects of the utility model are:
1. the hydraulic pressure fixed displacement motor adopting in hydraulic booster system of the present utility model is compared with hydraulic variable flow Pump and Electromotor, and specific power is large, and volume is little simultaneously, quality is light, accounts for car load space little, arranges that mounting structure is simple.For example the specific power of motor is about 1.6kw/kg, and the specific power of HM Hydraulic Motor can reach 3.6kw/kg.
2. hydraulic booster system of the present utility model is compared with conventional truck, multi-state is adaptable, can significantly improve dynamic property, crossing ability and the hill climbing ability of vehicle, on the road surface between coefficient of road adhesion 0.34-0.57, improve tractive force ratio and be about 10%-23%, climbable gradient raising ratio is about 13%-25%.
3. hydraulic booster system of the present utility model is compared with conventional truck, when car brakeing, can enlarge markedly braking torque, when long-time service brake, can significantly reduce the heating of brake disc simultaneously, the stability of brake efficiency when raising vehicle is braked for a long time.
4. hydraulic booster system of the present utility model is that addition portion divides Hydraulic Elements to form on the architecture basics of existing vehicle, does not substantially change the structure of former vehicle, compares with liquid-driving mixed power system, and complete vehicle structure changes less, and cost increases less.
5. the driven by power that high potential control is compared in the quiet liquid transmission that hydraulic booster system of the present utility model adopts has more safety.
Accompanying drawing explanation
Below in conjunction with accompanying drawing, the utility model is described further:
Fig. 1 is the structural principle schematic diagram of the utility model hydraulic pressure assistive drive and brake system.
Fig. 2 is the utility model hydraulic pressure assistive drive and brake system power transmission line figure under the independent drive pattern of driving engine.
Fig. 3 is the utility model hydraulic pressure assistive drive and brake system power transmission line figure under hydraulic pressure assistive drive pattern.
Fig. 4 is the utility model hydraulic pressure assistive drive and brake system power transmission line figure under hydraulic retarding braking mode.
Fig. 5 is the control method diagram of circuit that the utility model hydraulic pressure assistive drive and brake system mode of operation switch.
Fig. 6 is the diagram of curves that the vehicle tractive force of the utility model hydraulic pressure assistive drive and brake system increases ratio.
Fig. 7 is the diagram of curves that the vehicle climbable gradient of the utility model hydraulic pressure assistive drive and brake system increases ratio.
In figure: 1-driving engine, 2-power-transfer clutch, 3-power takeoff, 4-change speed gear box, 5-rear driving axle, 6-trailing wheel, 7-front-wheel, 8-electronic control unit, 9-axial inclined disc type high pressure controllable capacity pump, 10-3-position 4-way solenoid directional control valve, 11-electricity liquid ratio relief valve, 12-H Exch, 13-oil tank, 14-safety valve group, 15-hydraulic pressure fixed displacement motor, 16-engine crankshaft output shaft, the output shaft of 17-engine drive annex, 18-acceleration pedal, 19-brake pedal.
The specific embodiment
Below in conjunction with accompanying drawing, the utility model is explained in detail:
The purpose of this utility model is that a set of hydraulic efficiency pressure system is installed on the architecture basics of existing commercial truck, with overcome its on bad road surface dynamic property, crossing ability is poor and the unsettled shortcoming of long-time service brake during lower long slope, improves the in-use performance of automobile.
With reference to figure 1, hydraulic pressure assistive drive and the brake system that the utility model provides comprises output shaft 17, acceleration pedal 18 and the brake pedal 19 of driving engine 1, power-transfer clutch 2, power takeoff 3, change speed gear box 4, rear driving axle 5, two trailing wheels 6, two front-wheels 7, vehicle frame, electronic control unit 8, axial inclined disc type high pressure controllable capacity pump 9,3-position 4-way solenoid directional control valve 10, electricity liquid ratio relief valve 11, H Exch 12, oil tank 13, safety valve group 14, two hydraulic pressure fixed displacement motors 15 that structure is identical, engine crankshaft output shaft 16, engine drive annex.
Driving engine 1 in system described in the utility model, power-transfer clutch 2, change speed gear box 4, rear driving axle 5, two trailing wheels 6, two front-wheels 7 and vehicle frame are propulsion source and the power-transmitting part of existing conventional truck, power takeoff 3, axial inclined disc type high pressure controllable capacity pump 9,3-position 4-way solenoid directional control valve 10, electricity liquid ratio relief valve 11, H Exch 12, safety valve group 14, two the hydraulic pressure fixed displacement motors 15 that structure is identical, oil tank 13 and electronic control units 8 are the parts that add on the drive mechanism basis of existing conventional truck not changing, and form new power transmission line.
The hydraulic pressure assistive drive that the utility model provides and brake system are not changing addition portion subelement formation on existing conventional truck architecture basics.
In conventional truck structure, the crank shaft output shaft 16 of driving engine 1 is connected with power-transfer clutch 2 input spline pairs, and the output shaft of power-transfer clutch 2 adopts spline pair to be connected with the input shaft of change speed gear box 4, and the output shaft of change speed gear box 4 adopts spline pair to be connected with the input shaft of rear driving axle 5; The input shaft of the output shaft of power-transfer clutch 2 and change speed gear box 4 is arranged on separately on housing and in same level by antifriction-bearing box respectively, keeps rotation axis to be parallel to each other; The input shaft gear of change speed gear box 4 is sleeved on its input shaft and becomes to be fixedly connected with on output shaft with output shaft gear, and its input shaft gear and output shaft gear are connected with a joggle; The input shaft of the output shaft of change speed gear box 4 and rear driving axle 5 is arranged on separately on housing and in same level by antifriction-bearing box respectively, and keeps rotation axis to be parallel to each other.Driving engine 1, as propulsion source outputting power, passes to rear driving axle 5 through power-transfer clutch 2, change speed gear box 4, drives trailing wheel 6.
In new structure of adding, the input shaft of power takeoff 3 adopts spline pair to be connected with the output shaft 17 of engine drive annex, the input shaft driving gear of power takeoff 3 and the engaged transmission of output shaft driven gear, output shaft by the transmission of power of driving engine 1 to power takeoff 3, between the rotor shaft of the output shaft of power takeoff 3 and axial inclined disc type high pressure controllable capacity pump 9, adopt flange to be connected, thereby make the rotation of driving engine 1 drive the rotor shaft of axial inclined disc type high pressure controllable capacity pump 9 synchronously to rotate by power takeoff 3, pump fluid.
The oil outlet of axial inclined disc type high pressure controllable capacity pump 9 is connected by high-voltage oil liquid seal for pipe joints with the P mouth of 3-position 4-way solenoid directional control valve 10, and the A mouth of 3-position 4-way solenoid directional control valve 10 and the oil inlet of safety valve group 14 are connected by high-voltage oil liquid seal for pipe joints, the B mouth of 3-position 4-way solenoid directional control valve 10 is connected by high-voltage oil liquid seal for pipe joints with the oil inlet of electricity liquid ratio relief valve 11, and the T mouth of 3-position 4-way solenoid directional control valve 10 is connected by the seal for pipe joints of low pressure fluid with oil tank 13; 3-position 4-way solenoid directional control valve 10 is by the position of regulating spool, realizes the different control position of P mouth and A mouth, B mouth, T mouth, and actuating spindle is connected different hydraulic circuits to the oil outlet of inclined disc type high pressure controllable capacity pump 9.
The oil inlet of the hydraulic pressure fixed displacement motor 15 that the oil outlet of safety valve group 14 is identical with being arranged on two structures on two front-wheel 7 wheel hubs connects by high-voltage oil liquid seal for pipe joints, the oil outlet of the hydraulic pressure fixed displacement motor 15 that two structures are identical is connected by high-voltage oil liquid seal for pipe joints with the oil inlet that is fixed on the axial inclined disc type high pressure controllable capacity pump 9 on vehicle frame, form a hydraulic circuit, and the output rotor axle of the identical hydraulic pressure fixed displacement motor 15 of two structures adopts gear to be connected with a joggle with the semiaxis of two front-wheels 7 respectively, the hydraulic energy that axial inclined disc type high pressure controllable capacity pump 9 is pumped is by driving the output rotor axle of hydraulic pressure fixed displacement motor 15 to rotate, be converted into mechanical energy, pass to and drive front-wheel 7.
The oil outlet of electricity liquid ratio relief valve 11 is connected by the seal for pipe joints of low pressure fluid with the oil inlet of H Exch 12, and the oil outlet of H Exch 12 is connected by the seal for pipe joints of low pressure fluid with oil tank 13, and three's serial arranges.
Electronic control unit 8 is connected with brake pedal 19 with driving engine 1, axial inclined disc type high pressure controllable capacity pump 9,3-position 4-way solenoid directional control valve 10, electricity liquid ratio relief valve 11, acceleration pedal 18 respectively by signal wire (SW), receive the position signal of acceleration pedal 18 and brake pedal 19, send instruction to regulate the accelerator open degree of driving engine 1, the inclination angle of the swash plate of axial inclined disc type high pressure controllable capacity pump 9, the oil pressure relief of the spool position of 3-position 4-way solenoid directional control valve 10 and electricity liquid ratio relief valve 11.
When vehicle travels in good road surface, trailing wheel 6 can utilize the outputting power of driving engine 1 completely, now, power-transfer clutch 2 engages, electronic control unit 8 is according to now the intention of chaufeur and the motoring condition of vehicle send instruction to 3-position 4-way solenoid directional control valve 10, regulate its spool position, P mouth and T mouth are connected, the oil outlet of axial inclined disc type high pressure controllable capacity pump 9 directly and oil tank 13 connections, the now load of axial inclined disc type high pressure controllable capacity pump 9 is zero, thereby the load that axial inclined disc type high pressure controllable capacity pump 9 imposes on driving engine 1 through power takeoff 3 is also zero; The resistance to motion of the vehicle that the now load of driving engine 1 just passes over through trailing wheel 6, rear driving axle 5, change speed gear box 4, power-transfer clutch 2, so the power of driving engine 1 output all passes to rear driving axle 5 by power-transfer clutch 2, change speed gear box 4, drives trailing wheel 6; Axial inclined disc type high pressure controllable capacity pump 9 is in idling conditions.
When vehicle travels on bad road surface, skidding appears in trailing wheel 6, can not utilize the outputting power of driving engine 1 completely, now, power-transfer clutch 2 engages, electronic control unit 8 is according to now the intention of chaufeur and the motoring condition of vehicle regulate its spool position to the 10 transmission instructions of 3-position 4-way solenoid directional control valve, P mouth and A mouth are connected, the oil outlet of axial inclined disc type high pressure controllable capacity pump 9 is connected by safety valve group 14 and the oil inlet that is arranged on two hydraulic pressure fixed displacement motors 15 on front-wheel 7 wheel hubs, the load of front-wheel 7 is by hydraulic pressure fixed displacement motor 15, axial inclined disc type high pressure controllable capacity pump 9 and power takeoff 3 load to driving engine 1.A power part for driving engine 1 output passes to rear driving axle 5 by power-transfer clutch 2, change speed gear box 4, drives trailing wheel 6, another part power drives axial inclined disc type high pressure controllable capacity pump 9 input rotor shafts to rotate by power takeoff 3, electronic control unit 8 determines that according to engine output and trailing wheel slip rate driving engine 1 can offer the assistive drive power of two front-wheels 7, to axial inclined disc type high pressure controllable capacity pump 9, send instruction, regulate its displacement size, axial inclined disc type high pressure controllable capacity pump 9 transmits by driving engine 1 mechanical energy of coming and is converted into hydraulic energy, by two hydraulic pressure fixed displacement motors of safety valve group 14 pressure limiting rear drive 15, rotate, hydraulic pressure fixed displacement motor 15 is converted into mechanical energy by hydraulic energy again and drives front-wheel 7.
Work as car brakeing, especially when the long-time service brake of lower long slope, driving engine 1 is not as propulsion source outputting power, and car load kinetic energy during car brakeing is as propulsion source, and process trailing wheel 6 is to the transmission system outputting power of rear driving axle 5, change speed gear box 6, power-transfer clutch 2 formations.Now, power-transfer clutch 2 engages, electronic control unit 8 sends instruction according to vehicle running state to 3-position 4-way solenoid directional control valve 10 and regulates its spool position, its P mouth and B mouth are connected, make axial inclined disc type high pressure controllable capacity pump 9 oil outlets connect electricity liquid ratio relief valve 11, the return opening of electricity liquid ratio relief valve 11 is connected with H Exch 12 by hydraulic tubing, absorbs vehicle energy and hydraulic oil that temperature raises is back to oil tank 13 after cooling by H Exch 12.Power through rear driving axle 5, change speed gear box 4, power-transfer clutch 2, driving engine 1 and power takeoff 3, drives the rotor shaft of axial inclined disc type high pressure controllable capacity pump 9 synchronously to rotate from trailing wheel 6, pumps fluid.The pressure that pumps fluid is subject to the linear regulation of electricity liquid ratio relief valve 11.The driving torque of axial inclined disc type high pressure controllable capacity pump 9 equals the opposing torque of its driven wheel, and this opposing torque reacts on rear driving axle 5 by power takeoff 3, driving engine 1, power-transfer clutch 2, change speed gear box 4, and car load is produced to brake action.Electronic control unit 8 is according to the position of brake pedal 19, to electricity liquid ratio relief valve 11, send corresponding instruction, the outlet oil pressure of axial inclined disc type high pressure controllable capacity pump 9 is set up as certain value, the opposing torque occurring on the rotor shaft of axial inclined disc type high pressure controllable capacity pump 9 acts on driving engine 1 by power takeoff 3, now driving engine 1 is not as propulsion source, and as the deceleration loading on transmission shaft, add that axial inclined disc type high pressure controllable capacity pump 9 transmits the braking torque of coming, by the transmission of power-transfer clutch 2 and change speed gear box 4, this braking torque acts on trailing wheel 6 after rear driving axle 5 amplifies, consume car load kinetic energy, realize auxiliary braking.
The hydraulic pressure assistive drive that the utility model provides and the specific works pattern of brake system are as shown in the table:
Mode of operation:
1) the independent drive pattern of driving engine
With reference to figure 2, now vehicle travels on good normal road surface, trailing wheel 6(drive wheel) do not skid, the required torque of vehicle operating is all provided separately by driving engine 1, power-transfer clutch 2 combinations, 3-position 4-way solenoid directional control valve 10 spools are at midway location, A, B, P, tetra-mouth intercommunications of T, be fixedly mounted on axial inclined disc type high pressure controllable capacity pump 9 oil outlets on vehicle frame directly with oil tank 13 connections, load is zero, thereby the load that axial inclined disc type high pressure controllable capacity pump 9 imposes on driving engine 1 through power takeoff 3 is also zero; The resistance to motion of the vehicle that the now load of driving engine 1 just passes over through trailing wheel 6, rear driving axle 5, change speed gear box 4, power-transfer clutch 2; The identical hydraulic pressure fixed displacement motor 15 of two structures being arranged on front-wheel 7 wheel hubs is not worked, and load is also zero, keeps idling conditions.Now driving engine 1 power is all passed to rear driving axle 5 through power-transfer clutch 2 and change speed gear box 4, directly drives trailing wheel 6.Power transmission line as shown in Figure 2.
2) hydraulic pressure assistive drive pattern
With reference to figure 3, when vehicle travels on bad road surface, trailing wheel 6(drive wheel) occur skidding, the power that has only utilized part driving engine 1 to transmit.Now power-transfer clutch 2 engages, electronic control unit 8 regulates the spool of 3-position 4-way solenoid directional control valve 10 to move to left position by driver intention or vehicle running state, P mouth and A mouth, T mouth and B mouth are connected, hydraulic auxiliary driving system is opened, and axial inclined disc type high pressure controllable capacity pump 9 oil outlets are arranged on HM Hydraulic Motor 15 oil inlets that two structures on front-wheel 7 wheel hubs are identical and connect with two by safety valve group 14.Axial inclined disc type high pressure controllable capacity pump 9 obtains a part of power of driving engine 1 by power takeoff 3, mechanical energy is converted into hydraulic energy, through safety valve group 14, high pressure oil is provided to two identical HM Hydraulic Motor 15 of two structures that are arranged on front-wheel 7 wheel hubs, it is that mechanical energy drives two front-wheels 7 by hydraulic energy transfer that high pressure oil drives 15 work of two HM Hydraulic Motor; Other a part of power of driving engine 1 passes to rear driving axle 5 by power-transfer clutch 2, change speed gear box 4 and drives two trailing wheels 6, thereby realization becomes four wheels from two rear wheel drive vehicles, jointly drives vehicle.Electronic control unit 8 is according to the power of different slip rates and driving engine now 1 simultaneously, determine that driving engine 1 can offer the assistive drive watt level of two front-wheels 7, electronic control unit 8 is according to the transformation relation between parts power, the driving power size that calculates controllable capacity pump 9, the inclination angle size of the swash plate of control variable pump 9 is to offer two propulsive efforts that hydraulic pressure fixed displacement motor 15 is suitable that are contained on two front-wheel 7 wheel hubs.Power transmission line as shown in Figure 3.
3) hydraulic retarding braking mode
With reference to figure 4, work as car brakeing, especially during the long-time service brake when lower long slope, traditional drg there will be braking heat fade phenomenon, and lock torque is unstable.Now electronic control unit 8 moves to right position according to the spool of brake pedal 19 Signal Regulation 3-position 4-way solenoid directional control valves 10, P mouth and B mouth, T mouth and A mouth are connected, the oil outlet of axial inclined disc type high pressure controllable capacity pump 9 is connected electro-hydraulic proportional valve 11 loops, adjusting shaft is maximum to the inclination angle of the swash plate of inclined disc type high pressure controllable capacity pump 9 simultaneously, and hydraulic retarding braking mode is opened.
Under this pattern, as shown in Figure 4, now propulsion source is the car load kinetic energy from trailing wheel 6 to front transfer to power transmission line, and the parts of participation mainly contain axial inclined disc type high pressure controllable capacity pump 9, electricity liquid ratio relief valve 11, H Exch 12 and oil tank 13.The power transmitting from trailing wheel 6, through change speed gear box 4, power-transfer clutch 2, driving engine 1 and power takeoff 3, drives the rotor shaft of axial inclined disc type high pressure controllable capacity pump 9 synchronously to rotate, and pumps fluid.What the oil outlet of axial inclined disc type high pressure controllable capacity pump 9 connect is electricity liquid ratio relief valve 11, the pressure that pumps fluid is subject to the linear regulation of this electricity liquid ratio relief valve 11, the return opening of electricity liquid ratio relief valve 11 is connected with H Exch 12 by hydraulic tubing, absorbs vehicle energy and hydraulic oil that temperature raises is back to oil tank 13 after cooling by H Exch 12.The driving torque of axial inclined disc type high pressure controllable capacity pump 9 equals the opposing torque of its driven wheel, and this opposing torque reacts on driving engine 1 by power takeoff 3, and now driving engine 1 is as propulsion source, but as the load of transmission shaft.The deceleration loading of driving engine 1, adds and the opposing torque of axial inclined disc type high pressure controllable capacity pump 9 reacts on rear driving axle 5 by power-transfer clutch 2, change speed gear box 4, and car load is produced to brake action.Obviously, when the delivery pressure of axial inclined disc type high pressure controllable capacity pump 9 is low, its driving torque needing is just little, and the anti-driving torque that car load is produced is just little; By regulating the pressure of electricity liquid ratio relief valve 11 to get final product adjusting shaft to the delivery pressure of inclined disc type high pressure controllable capacity pump 9, and then regulate anti-driving torque.When needs are braked, electronic control unit 8 is according to the position of brake pedal, to electricity liquid ratio relief valve 11, send corresponding instruction, the outlet oil pressure of axial inclined disc type high pressure controllable capacity pump 9 is set up as certain value, now on axial inclined disc type high pressure controllable capacity pump 9 driven wheels, there is opposing torque, add the deceleration loading of driving engine 1, after change speed gear box 4 and rear driving axle 5 amplifications, act on trailing wheel 6, reach the object to the slow braking of vehicle.
When vehicle is at fully loaded 100t, change speed gear box one gear speed ratio is 12.1 o'clock, can calculate tractive force ratio and climbable gradient ratio that hydraulic booster system described in the utility model can improve, as shown in Figure 6 and Figure 7.Simultaneously when described hydraulic efficiency pressure system is during in slow braking mode, the transmitting ratio that adopts power takeoff 3 in system described in the utility model is 1:2, the maximum speed of revolution of Hydraulic Pump 9 is 3600rpm, max.cap. is 75ml/r, the pressure of the highest output hydraulic pressure oil is 40MPa, one gear speed ratio of vehicle is 12.1, base ratio is 5.73, as calculated, in the utility model, maximum braking torque can be additionally provided is 477.7Nm to Hydraulic Pump, through transmission device, amplify, the lock torque that acts on trailing wheel can reach 66240.7Nm.
In the hydraulic pressure assistive drive that the utility model provides and the structure of brake system:
Driving engine 1 is the common propulsion source of conventional truck and hydraulic pressure assistive drive and brake system, and it chooses the dynamic property requirement according to car load, selects existing product, the WP12_375NW h type engine h that for example maximum output power is 295KW.
Power-transfer clutch 2 is selected existing product, and structure is the common normally closed diaphragm spring friction clutch that is usually used in commercial truck, the DS430 type power-transfer clutch that for example friction lining diameter is 430mm.
Change speed gear box 4 requires to select existing product, the mechanical transmission that for example model is 12JSD180TA according to the gear of vehicle.
The power taking mode of power takeoff 3, can be chosen from driving engine 1 end power taking for directly in existing product; The structure of power takeoff 3 comprises two intermeshing driving and driven gears, driving gear is set in input shaft and becomes to be fixedly connected with on output shaft with driven gear, power, from input shaft transmission input, through the engaged transmission of driving and driven gear, is exported from output shaft transmission.
Axial inclined disc type high pressure controllable capacity pump 9 and selecting according to the power of vehicle of hydraulic pressure fixed displacement motor 15 require to choose existing product, for example discharge capacity is 75ml/r, maximum speed of revolution is high pressure P 90 pumps of 3600rpm, and rated pressure is 40MPa, the radial plunger piston motor MFE08-0 that discharge capacity is 1043ml/r.
3-position 4-way solenoid directional control valve 10 is selected existing product, and its Median Function is H shape, and four-hole is connected entirely, pump off-load, and maneuverability pattern is that electromagnet is handled, spring reset; According to input electrical signal instruction, its spool position can left and right adjusting to realize commutation function.
Electricity liquid ratio relief valve 11 is that range of regulation is the high-voltage ratio by pass valve of 0-40MPa, selects existing product.
The control method that the hydraulic pressure assistive drive that the utility model provides and the mode of operation of brake system switch specifically describes as follows:
With reference to figure 5, electronic control unit 8 is by gathering vehicle speed signal, tach signal, acceleration pedal 18 and brake pedal 19 position signals of driving engine 1 and intention and the vehicle running state that hydraulic efficiency pressure system switch key signal judges chaufeur, thereby actuating spindle is to inclined disc type high pressure controllable capacity pump 9,3-position 4-way solenoid directional control valve 10 spool positions, electricity liquid ratio relief valve 11 and driving engine 1 accelerator open degree, realize the switch of hydraulic pressure assistive drive and brake system and the conversion between mode of operation, specifically comprise the following steps:
Step 1, gathers vehicle speed signal, acceleration pedal position signal, brake pedal position signal and hydraulic efficiency pressure system on-off signal;
Step 2, judges that whether the speed of a motor vehicle is greater than 0, if so, enters step 3; Otherwise illustrate that vehicle enters the end step of step 10 at parking state;
Step 4, vehicle is in braking mode, and hydraulic efficiency pressure system is opened and is entered slow braking mode of operation:
The spool that electronic control unit 8 sends instruction adjusting 3-position 4-way solenoid directional control valve 10 moves to right position, P mouth and B mouth, T mouth and A mouth are connected, adjusting shaft is maximum to the inclination angle of the swash plate of inclined disc type high pressure controllable capacity pump 9, electronic control unit 8 goes out the anti-driving torque size of hydraulic efficiency pressure system according to vehicle speed signal and braking requirement torque calculation simultaneously, to electricity liquid ratio relief valve 11, send instruction, adjusting shaft, to the oil outlet pressure of inclined disc type high pressure controllable capacity pump 9, returns to step 2;
The spool that electronic control unit 8 sends instruction adjusting 3-position 4-way solenoid directional control valve 10 moves to left position, P mouth and A mouth, T mouth and B mouth are connected, axial inclined disc type high pressure controllable capacity pump 9 is connected with two hydraulic pressure fixed displacement motors 15 that are arranged on two front-wheel 7 wheel hubs through safety valve group 14, according to the tach signal of driving engine 1 and vehicle speed signal, calculate the required power of hydraulic pressure fixed displacement motor 15 of front-wheel, electronic control unit 8 sends instruction to controllable capacity pump 9, regulate the inclination angle size of its swash plate to offer two propulsive efforts that hydraulic pressure fixed displacement motor 15 is suitable that are contained on two front-wheel 7 wheel hubs, return to step 2,
Step 8, the speed of a motor vehicle is greater than the speed of a motor vehicle and sets limit value, illustrates that vehicle travels in good road surface, hydraulic closure system, car load is in the independent drive pattern of driving engine.Now electronic control unit 8 transmission instructions regulate the spool of 3-position 4-way solenoid directional control valve 10 to move to meta, and A mouth, B mouth, P mouth, T mouth are connected mutually), axial inclined disc type high pressure controllable capacity pump 9 and HM Hydraulic Motor 15, all in idling conditions, are returned to step 2;
Step 9, the speed of a motor vehicle is less than the speed of a motor vehicle and sets limit value, illustrates that vehicle travels on bad road surface, and hydraulic efficiency pressure system is automatically opened and is entered assistive drive mode of operation, enters step 6;
Claims (5)
1. a hydraulic pressure assistive drive and brake system, comprise driving engine (1), power-transfer clutch (2), change speed gear box (4), rear driving axle (5), two trailing wheels (6), two front-wheels (7), acceleration pedal (18), brake pedal (19) and vehicle frame, the crank shaft output shaft (16) of described driving engine (1) adopts spline pair to be connected with the input shaft of power-transfer clutch (2), the output shaft of power-transfer clutch (2) adopts spline pair to be connected with the input shaft of change speed gear box (4), and the output shaft of change speed gear box (4) adopts spline pair to be connected with the input shaft of rear driving axle (5); It is characterized in that, also comprise power takeoff (3), axial inclined disc type high pressure controllable capacity pump (9), 3-position 4-way solenoid directional control valve (10), electricity liquid ratio relief valve (11), H Exch (12), safety valve group (14), 2 hydraulic pressure fixed displacement motor (15), oil tank (13) and electronic control units (8) that structure is identical, wherein, the input shaft of described power takeoff (3) adopts spline pair to be connected with the output shaft (17) of engine drive annex, and the output shaft of power takeoff (3) is connected by flange with the rotor shaft of axial inclined disc type high pressure controllable capacity pump (9); Axial inclined disc type high pressure controllable capacity pump (9) is connected with 3-position 4-way solenoid directional control valve (10) pipeline, and 3-position 4-way solenoid directional control valve (10) is connected with safety valve group (14), electricity liquid ratio relief valve (11), oil tank (13) pipeline respectively; The oil inlet pipeline of the hydraulic pressure fixed displacement motor (15) that the oil outlet of safety valve group (14) is identical with 2 structures connects, and the oil outlet of the hydraulic pressure fixed displacement motor (15) that 2 structures are identical is connected with the oil inlet pipeline of axial inclined disc type high pressure controllable capacity pump (9); The oil outlet of described electricity liquid ratio relief valve (11) is connected with the oil inlet pipeline of H Exch (12), and the oil outlet of H Exch (12) is connected with oil tank (13) pipeline; Electronic control unit (8) is connected with driving engine (1), axial inclined disc type high pressure controllable capacity pump (9), 3-position 4-way solenoid directional control valve (10), electricity liquid ratio relief valve (11), acceleration pedal (18) and brake pedal (19) respectively by signal wire (SW).
2. a kind of hydraulic pressure assistive drive as claimed in claim 1 and brake system, it is characterized in that, described axial inclined disc type high pressure controllable capacity pump (9) is connected with 3-position 4-way solenoid directional control valve (10) pipeline, 3-position 4-way solenoid directional control valve (10) respectively with safety valve group (14), the connection of electricity liquid ratio relief valve (11) pipeline refers to: the oil outlet of axial inclined disc type high pressure controllable capacity pump (9) is connected by high-voltage oil liquid seal for pipe joints with the P mouth of 3-position 4-way solenoid directional control valve (10), the A mouth of 3-position 4-way solenoid directional control valve (10) is connected by high-voltage oil liquid seal for pipe joints with the oil inlet of safety valve group (14), the B mouth of 3-position 4-way solenoid directional control valve (10) is connected by high-voltage oil liquid seal for pipe joints with the oil inlet of electricity liquid ratio relief valve (11), the T mouth of 3-position 4-way solenoid directional control valve (10) is connected by the seal for pipe joints of low pressure fluid with oil tank (13).
3. a kind of hydraulic pressure assistive drive as claimed in claim 1 and brake system, it is characterized in that, the hydraulic pressure fixed displacement motor (15) that described 2 structures are identical is arranged on the wheel hub of two front-wheels (7) successively, and axial inclined disc type high pressure controllable capacity pump (9) is fixed on vehicle frame; The oil inlet of the hydraulic pressure fixed displacement motor (15) that the oil outlet of described safety valve group (14) is identical with 2 structures connects by high-voltage oil liquid seal for pipe joints, the oil outlet of the hydraulic pressure fixed displacement motor (15) that 2 structures are identical is connected by high-voltage oil liquid seal for pipe joints with the oil inlet of axial inclined disc type high pressure controllable capacity pump (9), and 2 the identical output rotor axle of hydraulic pressure fixed displacement motor (15) and semiaxis of two front-wheels (7) of structure adopt gears to be connected with a joggle.
4. a kind of hydraulic pressure assistive drive as claimed in claim 1 and brake system, it is characterized in that, the oil outlet of described electricity liquid ratio relief valve (11) is connected by the seal for pipe joints of low pressure fluid with the oil inlet of H Exch (12), the oil outlet of H Exch (12) is connected by the seal for pipe joints of low pressure fluid with oil tank (13), electricity liquid ratio relief valve (11), H Exch (12) and oil tank (13) serial setting.
5. a kind of hydraulic pressure assistive drive as claimed in claim 1 and brake system, is characterized in that, the rated pressure of the hydraulic pressure fixed displacement motor (15) that described 2 structures are identical is 40MPa, and discharge capacity is 1043ml/r; Described axial inclined disc type high pressure controllable capacity pump (9) is discharge capacity 75ml/r, high pressure P 90 pumps of maximum speed of revolution 3600rpm; The Median Function of described 3-position 4-way solenoid directional control valve (10) is H shape, and four-hole is connected entirely; The high-voltage ratio by pass valve that described electricity liquid ratio relief valve (11) is 0-40MPa for range of regulation; Described H Exch (12) employing operating temperature is the water-cooled cooler of 40-60 ℃; Described safety valve group (14) is comprised of two identical safety valves of structure model of pressure limiting 40MPa, and the installation site of two safety valves is contrary.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320519796.2U CN203439027U (en) | 2013-08-23 | 2013-08-23 | Hydraulic auxiliary drive and brake system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320519796.2U CN203439027U (en) | 2013-08-23 | 2013-08-23 | Hydraulic auxiliary drive and brake system |
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| Publication Number | Publication Date |
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| CN203439027U true CN203439027U (en) | 2014-02-19 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201320519796.2U Withdrawn - After Issue CN203439027U (en) | 2013-08-23 | 2013-08-23 | Hydraulic auxiliary drive and brake system |
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| CN (1) | CN203439027U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103407449A (en) * | 2013-08-23 | 2013-11-27 | 吉林大学 | Hydraulic auxiliary driving and braking system and control method thereof |
| WO2019119496A1 (en) * | 2017-12-20 | 2019-06-27 | 中车长春轨道客车股份有限公司 | Train axle speed control device and train |
| CN110056758A (en) * | 2019-04-24 | 2019-07-26 | 吉林大学 | A kind of displacement-variable oil pump control device and its method under damped condition |
| CN110920383A (en) * | 2018-09-20 | 2020-03-27 | 中冶宝钢技术服务有限公司 | Molten iron car differential control system, method and computer readable storage medium |
-
2013
- 2013-08-23 CN CN201320519796.2U patent/CN203439027U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103407449A (en) * | 2013-08-23 | 2013-11-27 | 吉林大学 | Hydraulic auxiliary driving and braking system and control method thereof |
| WO2019119496A1 (en) * | 2017-12-20 | 2019-06-27 | 中车长春轨道客车股份有限公司 | Train axle speed control device and train |
| CN110920383A (en) * | 2018-09-20 | 2020-03-27 | 中冶宝钢技术服务有限公司 | Molten iron car differential control system, method and computer readable storage medium |
| CN110056758A (en) * | 2019-04-24 | 2019-07-26 | 吉林大学 | A kind of displacement-variable oil pump control device and its method under damped condition |
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