CN103671899B - A kind of buncher hydraulic control system, buncher and vehicle - Google Patents
A kind of buncher hydraulic control system, buncher and vehicle Download PDFInfo
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- CN103671899B CN103671899B CN201210330355.8A CN201210330355A CN103671899B CN 103671899 B CN103671899 B CN 103671899B CN 201210330355 A CN201210330355 A CN 201210330355A CN 103671899 B CN103671899 B CN 103671899B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/14—Control of torque converter lock-up clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/4008—Control of circuit pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H2061/6604—Special control features generally applicable to continuously variable gearings
- F16H2061/6607—Controls concerning lubrication or cooling
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H2061/66204—Control for modifying the ratio control characteristic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H61/66272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
- F16H2061/66277—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing by optimising the clamping force exerted on the endless flexible member
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
Abstract
The invention provides a kind of buncher hydraulic control system, buncher and vehicle, by arranging basis hydraulic pressure supplying module, belt wheel hydraulic control module, auxiliary hydraulic pressure controls module, fluid torque-converter hydraulic control module and clutch hydraulic pressure control the functional modules such as module, and by the special annexation of respective devices, thus when only arranging a simple fail safe valve, buncher lubrication pressure is utilized to control the change of speed ratio, improve buncher efficiency under fail-safe mode, simplify the structure of hydraulic system, advantageously reduce cost.
Description
Technical field
The present invention relates to transmission for vehicles technical field, specifically can relate to a kind of buncher hydraulic control system, buncher and vehicle.
Background technology
Buncher set in vehicle, generally can be made up of electronic control unit, fluid torque-converter, clutch, driving pulley, driven pulley and hydraulic control system etc..
Wherein, hydraulic control system set in buncher, for the signal sent according to buncher electronic control unit, regulate the pressure of each oil circuit, control the flow direction and the flow of hydraulic oil, thus realizing the control to belt wheel clamping force and speed ratio, the control to clutch switching, to hydraulic torque converter lockout and the control opened, the control etc. to cooling and lubricating oil mass.
In hydraulic control system, also include some electromagnetic valves, for the signal of telecommunication of electronic control unit is converted into output pressure.
If vehicle is in running, electromagnetic valve and coupled joint, wire harness are short-circuited or the failure conditions such as open circuit, and the signal of telecommunication that electromagnetic valve obtains is 0, and electromagnetic valve is output as the pressure under no current state, no longer controlled.
In this case, in order to ensure the safety of vehicle, buncher should enter fail-safe mode, maintains the handling of vehicle, it is ensured that the personal safety of driver, until stopping carry out breakdown maintenance.
Generally, the fail-safe mode of buncher has following several:
One, clutch is opened, and cuts off power and connects.Such vehicle can reduce speed, until stopping.Vehicle runs out of steam suddenly, abnormally dangerous when vehicle travels；
Two, in buncher, opening frequently with fluid torque-converter, clutch combines with maximum pressure, and master and slave belt wheel pressure keeps maximum pressure.Under this fail-safe condition, transmission gear ratio can only rely on the moment of torsion of transmission to be adjusted, and moment of torsion reduces speed ratio and uprises, and moment of torsion raises speed ratio to be reduced.Although this control method ensure that the travelling of vehicle, but when vehicle stops, moment of torsion reduces, and speed ratio raises, and when being again started up, variator is still within high ratio, and vehicle launch acceleration is poor.And belt wheel is always maintained at maximum pressure and oil liquid leakage amount can be caused to increase, efficiency reduces, belt wheel and the steel band abrasion situation such as aggravation.
Three, in order to overcome the shortcoming of the second fail-safe mode, working connection arranges throttle orifice.Driving pump speed to raise when engine speed rises, when flow system flow is bigger, the pressure reduction relying on throttle orifice both sides bigger makes driving pulley pressure raise, and allows driving pulley pressure as feedback, makes working connection pressure reduce, and driven pulley pressure reduces, and speed ratio raises.Otherwise, engine speed declines, and pump speed reduces, and when flow system flow reduces, the less pressure reduction in throttle orifice both sides makes driving pulley pressure reduce, allows driving pulley pressure as feedback, makes working connection pressure increase, the increase of driven pulley pressure, speed ratio reduction.When the method ensures vehicle high-speed, speed ratio raises；During vehicle low speed, speed ratio reduces.But, this system working connection is provided with throttle orifice, causes loss in efficiency, and needs to arrange eduction valve, adds cost.
Summary of the invention
The embodiment of the present invention provides a kind of buncher hydraulic control system, buncher and vehicle; it is thus possible to ensure when buncher is in fail-safe mode; buncher can either realize vehicle when high speed to high ratio speed change; speed change is compared to low speed during vehicle low speed; ensure vehicle handling and be again started up acceleration there is again simple in construction, feature that cost is low.
The present invention provides scheme as follows:
Embodiments provide a kind of buncher hydraulic control system, control module including basis hydraulic pressure supplying module, belt wheel hydraulic control module, auxiliary hydraulic pressure；Wherein:
Described basis hydraulic pressure supplying module includes oil pump, working connection pressure-control valve, described working connection pressure-control valve the first end is connected to described oil pump by working connection, and the second end of described working connection pressure-control valve feeds back oil circuit by the first working connection and is connected to described working connection；
Described belt wheel hydraulic control module includes driving pulley pressure-control valve, driven pressure-control valve of leading the way, the 3rd end of described driving pulley pressure-control valve and the three-terminal link of described driven pressure-control valve of leading the way extremely described working connection；
Described auxiliary hydraulic pressure controls module and includes auxiliary oil way pressure-control valve, fail safe valve; described auxiliary oil way pressure-control valve the first end is connected to the 3rd end of described working connection pressure-control valve by auxiliary oil way; 3rd end of described auxiliary oil way pressure-control valve is connected to described fail safe valve the 3rd end by lubrication oil circuit, and the first end of described fail safe valve is connected to the second end of described working connection pressure-control valve and the second end of described driving pulley pressure-control valve by fail safe oil circuit.
Preferably, described basis hydraulic pressure supplying module also includes: oil sump and the first electromagnetic valve；
Described oil sump, for storing hydraulic oil required in buncher；
Described oil pump is under the driving of electromotor, from oil sump draw oil, provides pressure oil for hydraulic system；
Described first electromagnetic valve is connected to working connection pressure-control valve the 4th end by the first electromagnetic valve oil circuit；
Described first electromagnetic valve is normal high type electromagnetic valve.
Preferably, described belt wheel hydraulic control module also includes: driving pulley, driving pulley piston cylinder, the second electromagnetic valve, and driven pulley, driven pulley piston cylinder, the 3rd electromagnetic valve；Wherein:
Described driving pulley is connected to described driving pulley piston cylinder；
Described driving pulley piston cylinder is connected to the first end of described driving pulley pressure-control valve by driving pulley oil circuit；
Described second electromagnetic valve is connected to the second end of described driving pulley pressure-control valve by the second electromagnetic valve oil circuit；
4th end of described driving pulley pressure-control valve feeds back oil circuit by driving pulley and is connected to described driving pulley oil circuit；
Described driven pulley is connected to described driven pulley piston cylinder；
Described driven pulley piston cylinder is connected to the first end of described driven pulley pressure-control valve by driven pulley oil circuit；
Described 3rd electromagnetic valve is connected to the second end of described driven pulley pressure-control valve by the 3rd electromagnetic valve oil circuit；
Second end of described driven pulley pressure-control valve feeds back oil circuit by driven pulley and is connected to described driven pulley oil circuit；
4th end of described driven pulley pressure-control valve feeds back oil circuit by driven pulley the second working connection and is connected to described working connection；
Described second electromagnetic valve and the 3rd electromagnetic valve are normally low-type electromagnetic valve.
Preferably, described auxiliary hydraulic pressure control module also includes: the 4th electromagnetic valve；
Described 4th electromagnetic valve is connected to the second end of described fail safe valve by oil duct；
Described 4th electromagnetic valve is normal high type electromagnetic valve.
Preferably, described buncher hydraulic control system also includes fluid torque-converter hydraulic control module, and described fluid torque-converter hydraulic control module is connected to described auxiliary hydraulic pressure by described lubrication oil circuit and controls module.
Preferably, described buncher hydraulic control system also includes clutch hydraulic pressure and controls module, and described clutch hydraulic pressure controls module and is connected to described auxiliary hydraulic pressure control module by oil duct.
The embodiment of the present invention additionally provides a kind of buncher, and described buncher includes the buncher hydraulic control system that the invention described above embodiment provides.
The embodiment of the present invention additionally provides a kind of vehicle, and described vehicle includes the buncher as the above-mentioned embodiment of the present invention provides.
Can be seen that from the above, buncher hydraulic control system provided by the invention, buncher and vehicle, by arranging basis hydraulic pressure supplying module, belt wheel hydraulic control module, auxiliary hydraulic pressure controls module, fluid torque-converter hydraulic control module and clutch hydraulic pressure control the functional modules such as module, and by the special annexation of respective devices, thus when only arranging a simple fail safe valve, buncher lubrication pressure is utilized to control the change of speed ratio, improve buncher efficiency under fail-safe mode, simplify the structure of hydraulic system, advantageously reduce cost.
Accompanying drawing explanation
The buncher hydraulic control system configuration schematic diagram one that Fig. 1 provides for the embodiment of the present invention；
The buncher hydraulic control system configuration schematic diagram two that Fig. 2 provides for the embodiment of the present invention.
Detailed description of the invention
Embodiments providing a kind of buncher hydraulic control system, as shown in Figure 1, this buncher hydraulic control system specifically can be made up of following functions module:
Basis hydraulic pressure supplying module 100, belt wheel hydraulic control module 200, auxiliary hydraulic pressure control the functional module compositions such as module 300, fluid torque-converter hydraulic control module 400, clutch hydraulic pressure control module 500.
Below, in conjunction with accompanying drawing 2, the concrete structure composition of the buncher hydraulic control system that the embodiment of the present invention provides is described in detail.
As shown in Figure 2, the basic hydraulic pressure supplying module 100 involved by the embodiment of the present invention specifically can be made up of following device:
Oil sump 1, for storing the hydraulic oil needed for buncher.
Oil pump 2, is driven by electromotor, is used for from oil sump oil suction, and is that hydraulic system provides pressure oil by working connection 21.
Working connection pressure-control valve 3, for regulating the pressure of working connection 21, supplies driving pulley pressure-control valve 5 and driven pulley pressure-control valve 9, and leak separatory force feed enters auxiliary oil way 31.
In the embodiment of the present invention, the first end of working connection pressure-control valve 3 is connected to working connection 21；Second end of working connection pressure-control valve 3 is connected to the second end of driving pulley pressure-control valve 5 set in belt wheel hydraulic control module 200 by fail safe oil circuit; and auxiliary hydraulic pressure controls the first end of fail safe valve 20 set in module 300, and the second end of working connection pressure-control valve 3 feeds back oil circuit 41 also by the first working connection and is connected to working connection 21；3rd end of working connection pressure-control valve 3 is connected to auxiliary hydraulic pressure by auxiliary oil way 31 and controls the first end of auxiliary oil way pressure-control valve 13 set in module 300；4th end of working connection pressure-control valve 3 is connected to electromagnetic valve 4 by electromagnetic valve oil circuit 22.
Electromagnetic valve 4, the signal of telecommunication for being sent by electronic control unit in buncher is converted into the output pressure of correspondence.
Electromagnetic valve 4 involved by the embodiment of the present invention is normal high type electromagnetic valve concretely, and namely when electric current is 0, output pressure is maximum；When electric current is maximum, output pressure is 0.
As shown in Figure 2, the belt wheel hydraulic control module 200 involved by the embodiment of the present invention specifically can be made up of following device:
Interconnective driving pulley 7 and driving pulley piston cylinder 8, and interconnective driven pulley 11 and driven pulley piston cylinder 12.
Driving pulley pressure-control valve 5, for controlling the pressure of driving pulley oil circuit 24.
Driven pulley pressure-control valve 9, for controlling the pressure of driven pulley oil circuit 27.
Electromagnetic valve 6 and electromagnetic valve 10, the signal of telecommunication for being sent by electronic control unit in buncher is converted into the output pressure of correspondence.
In the embodiment of the present invention, electromagnetic valve 6 and electromagnetic valve 10 concretely normally low-type electromagnetic valve, namely when electric current is 0, output pressure is 0；When electric current is maximum, output pressure is maximum.
In the embodiment of the present invention, driving pulley 7 and driven pulley 11, each belt wheel all have a fixed cone dish and one can movable cone dish in axial sliding, hold steel band between two cone dishes.In speed change work process, utilization is applied on movable cone dish hydraulic pressure and steps up steel band, regulate the pressure dependence of driving pulley 7 and driven pulley 11, it is possible to make steel band radius of clean-up on two belt wheels change, thus reaching the function of infinitely variable speeds and transmitting power.Speed ratio changes from low to high, and driving pulley piston cylinder 8 is oil-filled, and movable cone dish moves inward, and the steel band radius of clean-up on driving pulley 7 becomes big；Meanwhile, driven pulley piston cylinder 12 draining, movable cone dish is displaced outwardly, and the steel band radius of clean-up on driven pulley 11 diminishes.Speed ratio changes from high to low, driving pulley piston cylinder 8 draining, and movable cone dish is displaced outwardly, and the steel band radius of clean-up on driving pulley 7 diminishes；Meanwhile, driven pulley piston cylinder 12 is oil-filled, and movable cone dish moves inward, and the steel band radius of clean-up on driven pulley 11 becomes big.
In the embodiment of the present invention, the first end of driving pulley pressure-control valve 5 is connected to driving pulley piston cylinder 8 by driving pulley oil circuit 24；Second end of driving pulley pressure-control valve 5 is connected to electromagnetic valve 6 by electromagnetic valve oil circuit 25, and the second end of driving pulley pressure-control valve 5 is connected to the second end of working connection pressure-control valve 3 also by fail safe oil circuit 23 and auxiliary hydraulic pressure controls the first end of fail safe valve 20 set in module 300；3rd end of driving pulley pressure-control valve 5 is connected to working connection pressure-control valve 3 and oil pump 2 by working connection 21；4th end of driving pulley pressure-control valve 5 is connected to driving pulley oil circuit 24 by driving pulley feedback oil circuit 26.
In the embodiment of the present invention, the first end of driven pulley pressure-control valve 9 is connected to driven pulley piston cylinder 12 by driven pulley oil circuit 27；Second end of driven pulley pressure-control valve 9 is connected to driven pulley oil circuit 27 by driven pulley feedback oil circuit 30, and the second end of driven pulley pressure-control valve 9 is connected to electromagnetic valve 10 by electromagnetic valve oil circuit 29；3rd end of driven pulley pressure-control valve 9 is connected to working connection pressure-control valve 3 and oil pump 2 by working connection 21；4th end of driven pulley pressure-control valve 9 is connected to working connection 21 by the second working connection feedback oil circuit 28.
As shown in Figure 2, the auxiliary hydraulic pressure control module 300 involved by the embodiment of the present invention specifically can be made up of following device:
Auxiliary oil way pressure-control valve 13, for regulating the pressure of auxiliary oil way 31, and leak separatory force feed oil enters lubrication oil circuit 35.
Auxiliary oil way pressure-control valve 13 is connected to working connection pressure-control valve 3 by auxiliary oil way 31
Fail safe valve 20, for when buncher is in fail-safe mode, by coordinating with other devices in hydraulic control system, regulates the pressure of driving pulley oil circuit 24 and working connection 21.
Electromagnetic valve 15, the signal of telecommunication for being sent by electronic control unit in buncher is converted into the output pressure of correspondence.
In the embodiment of the present invention, electromagnetic valve 15 is normal high type electromagnetic valve concretely, and namely when electric current is 0, output pressure is maximum；When electric current is maximum, output pressure is 0.
In the embodiment of the present invention, the first end of fail safe valve 20 is connected to the second end of working connection pressure-control valve 3 and the second end of driving pulley pressure-control valve 5 by fail safe oil circuit 23；Second end of fail safe valve 20 is connected to electromagnetic valve 15 by oil circuit 33 and clutch hydraulic pressure controls the clutch pressure control valve 14 of setting in module 500；The hydraulic torque converter lockout that 3rd end of fail safe valve 20 is connected in the 3rd end of auxiliary oil way pressure-control valve 13 and fluid torque-converter hydraulic control module 400 by lubricating oil cooling oil path 35 arrange controls valve 17.
As shown in Figure 2, the fluid torque-converter hydraulic control module 400 involved by the embodiment of the present invention specifically can be made up of following device:
Fluid torque-converter 19, for passing to variator by the moment of torsion of electromotor.
Fluid torque-converter 19 involved by the embodiment of the present invention, specifically may be mounted at buncher front end.Fluid torque-converter power shaft is connected with engine output shaft, and output shaft and clutch 16 are connected.Fluid torque-converter relies on liquid to transmit moment of torsion with the change that blade interaction produces the moment of momentum, it is possible to the moment of torsion of electromotor is smoothly passed to variator, it is prevented that system overload, is conducive to vehicle gentle start；It addition, when vehicle suddenly accelerates, play the effect increasing moment of torsion.When vehicle travels under the plateau that speed is higher, fluid torque-converter can be locked out, and loses its function, makes electromotor and transmission clutch power shaft be directly connected to.The purpose of locking fluid torque-converter is to improve efficiency, reduces hydraulic losses.
Hydraulic torque converter lockout controls valve 17, for controlling unblock or the locking of fluid torque-converter 19, and detent pressure.
Hydraulic torque converter lockout controls the first end of valve 17 and is connected to lubricating oil cooling oil path 35 and lubricant passage way 40；Hydraulic torque converter lockout controls the second end of valve 17 and is connected to its 3rd end by feeding back oil circuit 39；Hydraulic torque converter lockout controls the 3rd end of valve 17 and is connected to fluid torque-converter 19 by fluid torque-converter unblock oil circuit 37 and oil circuit 38；Hydraulic torque converter lockout control valve 17 the 4th end by electromagnetic valve oil circuit 36 be connected in fluid torque-converter hydraulic control module 400 arrange electromagnetic valve 18.
Electromagnetic valve 18, the signal of telecommunication for being sent by electronic control unit in buncher is converted into the output pressure of correspondence.
In the embodiment of the present invention, electromagnetic valve 18 concretely normally low-type electromagnetic valve, namely when electric current is 0, output pressure is 0；When electric current is maximum, output pressure is maximum.
As shown in Figure 2, the clutch hydraulic pressure control module 500 involved by the embodiment of the present invention specifically can be made up of following device:
Clutch 16, including forward clutch and reverse clutch, the power shaft of clutch 16 and fluid torque-converter 19 output shaft are connected, and the output shaft of clutch 16 connects buncher belt wheel mechanism.The moment of torsion of electromotor, through fluid torque-converter, passes to clutch, by the combination of different clutches with open, it is achieved the advance of vehicle, falls back and neutral gear function.Clutch 16 is mainly made up of friction plate and piston.When the piston cylinder not having pressure oil to enter clutch, friction plate will not be in conjunction with, and engine torque interrupts transmission at clutch place, and vehicle is in neutral position state.When pressure oil enters clutch plunger cylinder, promoting piston, pressing friction sheet, engine torque can transmit.
Clutch pressure control valve 14, for regulating the pressure of clutch oil circuit 32, controls opening or combining of clutch 16.
First end of clutch pressure control valve 14 is connected to the 3rd end of working connection pressure-control valve 3 and the first end of auxiliary oil way pressure-control valve by auxiliary oil way 31；Second end of clutch pressure control valve 14 is connected to clutch oil circuit 32 by clutch feedback oil circuit 34；3rd end of clutch pressure control valve 14 is connected to clutch 16 by clutch oil circuit 32；4th end of clutch pressure control valve 14 is connected to the second end and the electromagnetic valve 15 of fail safe valve 20 by oil circuit 33.
Below, based on the annexation of each device in the buncher hydraulic control system that the invention described above embodiment provides, this hydraulic control system work process in a specific embodiment is described in detail.
When the electric parts of buncher is short-circuited or the fault such as open circuit, the input current of all electromagnetic valves is 0, and buncher enters fail-safe mode.
So now, as shown in Figure 2, the output pressure of normally low-type electromagnetic valve 18 (6,10) is 0, normal high type electromagnetic valve 15 (4) output high pressure, and hydraulic torque converter lockout controls to be in the position shown in accompanying drawing 2 under the effect of the spring force that valve 17 is arranged at himself right-hand member.Lubrication oil circuit 35 controls valve 17 by hydraulic torque converter lockout and communicates with fluid torque-converter unblock oil circuit 37, and hydraulic oil flows out from oil circuit 38 after entering fluid torque-converter 19, again passes by hydraulic torque converter lockout and controls valve 17, enters lubricant passage way 40.Fluid torque-converter is in released state.
Owing to normal high type electromagnetic valve 15 exports high pressure, pressure acts on the left end of clutch pressure control valve 14 by oil duct 33, clutch pressure control valve 14 is applied pressure to the right, this pressure overcomes the spring force in clutch pressure control valve 14, clutch pressure control valve 14 is moved to the position shown in accompanying drawing 2, auxiliary oil way 31 and clutch oil circuit 32 are connected, electromagnetic valve pressure to the right balances each other with spring force to the left and clutch feedback oil circuit 34 pressure, spring force change is less, electromagnetic valve pressure reaches maximum, clutch feedback pressure also reaches maximum, clutch feedback oil circuit 34 is connected with clutch oil circuit 32, pressure is identical, therefore clutch pressure also reaches maximum, clutch 16 is in bonding state.Normal high type electromagnetic valve 15 exports the other branch road of oil duct 33 and acts on the right-hand member of fail safe valve 20; fail safe valve 20 is applied power to the left; this is made every effort to overcome and takes the initial tension of spring that fail safe valve 20 left end is arranged; fail safe valve 20 is moved to the position shown in Fig. 2; lubricant passage way 35 communicates with fail safe oil circuit 23, and pressure is identical.
Owing to normal high type electromagnetic valve 4 exports maximum pressure, working connection pressure-control valve 3 left end is subject to initial tension of spring and electromagnetic valve oil circuit 22 pressure to the right, and right-hand member is subject to the pressure of working connection feedback oil circuit 41 and the pressure of fail safe oil circuit 23.Working connection pressure-control valve 3 keeps balance under these power effects.Working connection pressure-control valve 3 left end electromagnetic valve oil circuit 22 exports maximum pressure, makes right-hand member working connection feedback pressure be also at higher-pressure level for balance with it, thus ensureing to provide enough clamping pressure to driving pulley 7 and driven pulley 11.
Owing to normally low-type electromagnetic valve 6 output pressure is 0; driving pulley pressure-control valve 5 left end is subject to initial tension of spring and driving pulley feedback oil circuit 26 power to the right; right side is subject to fail safe oil circuit 23 pressure to the left, and driving pulley pressure-control valve 5 keeps balance under these three power effect.Driving pulley oil circuit 24 passes into driving pulley piston cylinder 8, provides clamping force for driving pulley 7.
Owing to normally low-type electromagnetic valve 10 output pressure is 0, driven pulley pressure-control valve 9 left end is subject to initial tension of spring and the pressure of working connection feedback oil circuit 28, and direction is to the right；Being subject to driven pulley oil circuit 30 feedback pressure on the right side of driven pulley pressure-control valve 9, direction is to the left.Because driven pulley pressure is all the time not over working connection pressure, therefore driven pulley pressure-control valve 9 is under being subject to the effect made a concerted effort to the right, it is in the position shown in Fig. 2, working connection 21 directly connects with driven pulley oil circuit 27, working connection pressure acts directly in driven pulley piston cylinder 12, provides clamping force for driven pulley 11.Driven pulley pressure-control valve 9 does not recur and regulates the effect of pressure, and the pressure of driven pulley 11 directly relies on working connection pressure-control valve 3 to regulate.
In accordance with the above, under fail-safe mode, fluid torque-converter is in released state, and clutch combines with maximum pressure, and driven pulley oil circuit 27 pressure is directly controlled by working connection pressure-control valve 3, and driven pulley pressure-control valve 9 is ineffective.Fail safe valve 20 moves, and makes fail safe oil circuit 23 communicate with lubricant passage way 35, and lubricant passage way pressure acts on working connection pressure-control valve 3 and driving pulley pressure-control valve 5 right-hand member.
Under fail-safe mode, driver still wants can regulation speed, it is ensured that vehicle can drive to safe place or maintenace point.
Concrete, when the vehicle accelerates, along with the rising of engine speed, buncher oil pump 2 rotating speed raises simultaneously, and in hydraulic control system, oil flow increases, and excessive oil enters lubricant passage way 35, causes lubrication pressure to increase.Lubrication pressure acts on working connection pressure-control valve 3 right-hand member by fail safe oil circuit 23; owing to electromagnetic valve oil circuit 22 pressure of left end remains unchanged; spring pressure excursion is less; working connection pressure-control valve about 3 stress keeps balance; when the fail safe pressure of right-hand member increases; namely working connection feedback oil circuit 41 pressure reduce, and reduces thus acting on working connection 21 pressure on driven pulley 11.And for driving pulley pressure-control valve 5; fail safe oil circuit 23 pressure of right-hand member increases; electromagnetic valve oil circuit 25 pressure is 0; the spring force excursion that right-hand member balances with it is less; therefore driving pulley feedback oil circuit 26 pressure raises, and namely acts on driving pulley oil circuit 24 pressure on driving pulley 7 and raises.Driving pulley 7 pressure raises, and driven pulley 11 pressure reduces, and speed ratio switches to high ratio, it is possible to reduce engine speed when high vehicle speeds；Particularly under high vehicle speeds state, when abruptly entering fail-safe mode, maintain high ratio, be not result in engine speed and the unexpected acute variation of speed, the safety of vehicle is had very important effect.
And when the vehicle is decelerating, along with the reduction of engine speed, buncher oil pump 2 rotating speed also reduces, in hydraulic control system, oil flow reduces, and lubrication oil circuit 35 pressure reduces.Lubrication pressure acts on working connection pressure-control valve 3 right-hand member by fail safe oil circuit 23; owing to electromagnetic valve oil circuit 22 pressure of left end remains unchanged; spring pressure excursion is less; working connection pressure-control valve about 3 stress keeps balance; when the fail safe pressure of working connection pressure-control valve 3 right-hand member reduces; namely working connection feedback oil circuit 41 pressure increase, and increases thus acting on working connection 21 pressure on driven pulley 11.And for working connection pressure-control valve 5; fail safe oil circuit 23 pressure of right-hand member reduces; electromagnetic valve oil circuit 25 pressure is 0; the spring force excursion that right-hand member balances with it is less; therefore driving pulley feedback oil circuit 26 pressure reduces, and namely acts on driving pulley oil circuit 24 pressure on driving pulley 7 and reduces.Driving pulley 7 pressure reduces, and driven pulley 11 pressure increases, and speed ratio switches to low speed ratio, it is possible to ensure that when low vehicle speeds electromotor does not stop working；Particularly when vehicle stops, speed ratio is preferably minimized, and is conducive to vehicle again start to walk and accelerate.
Be can be seen that by foregoing description; the buncher hydraulic control system that the embodiment of the present invention provides; working connection throttle orifice need not be set; only a simple fail safe valve need to be set; variator lubrication pressure is utilized to control the change of speed ratio; improve buncher efficiency under fail-safe mode, simplify the structure of hydraulic system, advantageously reduce cost.
Based on the buncher hydraulic control system that the embodiment of the present invention provides, the embodiment of the present invention additionally provides a kind of buncher, is provided with the hydraulic control system as shown in accompanying drawing 1,2 that the embodiment of the present invention provides in this buncher.
Based on the buncher hydraulic control system that the embodiment of the present invention provides, the embodiment of the present invention additionally provides a kind of vehicle, is provided with the buncher that the embodiment of the present invention provides in this vehicle.
The above is only embodiments of the present invention; it should be pointed out that, for those skilled in the art, under the premise without departing from the principles of the invention; can also making some improvements and modifications, these improvements and modifications also should be regarded as protection scope of the present invention.
Claims (8)
1. a buncher hydraulic control system, it is characterised in that include basis hydraulic pressure supplying module, belt wheel hydraulic control module, auxiliary hydraulic pressure control module；Wherein:
Described basis hydraulic pressure supplying module includes oil pump, working connection pressure-control valve, described working connection pressure-control valve the first end is connected to described oil pump by working connection, and the second end of described working connection pressure-control valve feeds back oil circuit by the first working connection and is connected to described working connection；
Described belt wheel hydraulic control module includes driving pulley pressure-control valve, driven pulley pressure-control valve, the 3rd end of described driving pulley pressure-control valve and the three-terminal link of described driven pulley pressure-control valve extremely described working connection；
Described auxiliary hydraulic pressure controls module and includes auxiliary oil way pressure-control valve, fail safe valve; described auxiliary oil way pressure-control valve the first end is connected to the 3rd end of described working connection pressure-control valve by auxiliary oil way; 3rd end of described auxiliary oil way pressure-control valve is connected to described fail safe valve the 3rd end by lubrication oil circuit, and the first end of described fail safe valve is connected to the second end of described working connection pressure-control valve and the second end of described driving pulley pressure-control valve by fail safe oil circuit.
2. buncher hydraulic control system as claimed in claim 1, it is characterised in that described basis hydraulic pressure supplying module also includes: oil sump and the first electromagnetic valve；
Described oil sump, for storing hydraulic oil required in buncher；
Described oil pump is under the driving of electromotor, from oil sump draw oil, provides pressure oil for hydraulic system；
Described first electromagnetic valve is connected to working connection pressure-control valve the 4th end by the first electromagnetic valve oil circuit；
Described first electromagnetic valve is normal high type electromagnetic valve.
3. buncher hydraulic control system as claimed in claim 1, it is characterised in that described belt wheel hydraulic control module also includes: driving pulley, driving pulley piston cylinder, the second electromagnetic valve, and driven pulley, driven pulley piston cylinder, the 3rd electromagnetic valve；
Described driving pulley is connected to described driving pulley piston cylinder；
Described driving pulley piston cylinder is connected to the first end of described driving pulley pressure-control valve by driving pulley oil circuit；
Described second electromagnetic valve is connected to the second end of described driving pulley pressure-control valve by the second electromagnetic valve oil circuit；
4th end of described driving pulley pressure-control valve feeds back oil circuit by driving pulley and is connected to described driving pulley oil circuit；
Described driven pulley is connected to described driven pulley piston cylinder；
Described driven pulley piston cylinder is connected to the first end of described driven pulley pressure-control valve by driven pulley oil circuit；
Described 3rd electromagnetic valve is connected to the second end of described driven pulley pressure-control valve by the 3rd electromagnetic valve oil circuit；
Second end of described driven pulley pressure-control valve feeds back oil circuit by driven pulley and is connected to described driven pulley oil circuit；
4th end of described driven pulley pressure-control valve feeds back oil circuit by the second working connection and is connected to described working connection；
Described second electromagnetic valve and the 3rd electromagnetic valve are normally low-type electromagnetic valve.
4. buncher hydraulic control system as claimed in claim 1, it is characterised in that described auxiliary hydraulic pressure controls module and also includes: the 4th electromagnetic valve；
Described 4th electromagnetic valve is connected to the second end of described fail safe valve by oil duct；
Described 4th electromagnetic valve is normal high type electromagnetic valve.
5. buncher hydraulic control system as claimed in claim 1, it is characterised in that also include fluid torque-converter hydraulic control module, described fluid torque-converter hydraulic control module is connected to described auxiliary hydraulic pressure by described lubrication oil circuit and controls module.
6. buncher hydraulic control system as claimed in claim 1, it is characterised in that also include clutch hydraulic pressure and control module, described clutch hydraulic pressure controls module and is connected to described auxiliary hydraulic pressure control module by oil duct.
7. a buncher, it is characterised in that described buncher includes the buncher hydraulic control system as described in any one of claim 1 to 6.
8. a vehicle, it is characterised in that described vehicle includes buncher as claimed in claim 7.
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| CN201210330355.8A CN103671899B (en) | 2012-09-07 | 2012-09-07 | A kind of buncher hydraulic control system, buncher and vehicle |
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| CN201210330355.8A CN103671899B (en) | 2012-09-07 | 2012-09-07 | A kind of buncher hydraulic control system, buncher and vehicle |
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| CN103671899B true CN103671899B (en) | 2016-06-29 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104482196B (en) * | 2014-12-19 | 2017-07-07 | 湖南江麓容大车辆传动股份有限公司 | For the direct drive type hydraulic device and vapour stepless speed variator of vehicle of buncher |
| CN106715967B (en) * | 2015-02-06 | 2019-03-19 | 深圳瀚飞科技开发有限公司 | Hydraulic continuously variable transmission |
| CN106195244B (en) * | 2015-04-29 | 2018-07-24 | 长城汽车股份有限公司 | A kind of fluid torque-converter stall protection method and system |
| CN107061671A (en) * | 2017-03-29 | 2017-08-18 | 湖南江麓容大车辆传动股份有限公司 | A kind of buncher hydraulic system |
| CN109595321A (en) * | 2018-12-30 | 2019-04-09 | 芜湖万里扬变速器有限公司 | Pure electric vehicle stepless speed variator system |
| JP6933698B2 (en) * | 2019-10-07 | 2021-09-08 | 本田技研工業株式会社 | Hydraulic control device and hydraulic control method for continuously variable transmission |
| CN112211970B (en) * | 2020-11-04 | 2021-09-21 | 湘潭大学 | Hydraulic self-locking type stepless transmission slippage control device and control method |
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