CN107044540B - Gear box hydraulic control system - Google Patents
Gear box hydraulic control system Download PDFInfo
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- CN107044540B CN107044540B CN201710373562.4A CN201710373562A CN107044540B CN 107044540 B CN107044540 B CN 107044540B CN 201710373562 A CN201710373562 A CN 201710373562A CN 107044540 B CN107044540 B CN 107044540B
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- valve
- oil
- control valve
- clutch
- pressure
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Classifications
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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
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
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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
- F16H61/04—Smoothing ratio shift
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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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/34—Locking or disabling mechanisms
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0203—Control by fluid pressure with an accumulator; Details thereof
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Transmission Device (AREA)
Abstract
Present invention is disclosed a kind of gear box hydraulic control systems, including fuel tank, oil supply subsystem, main oil pressure control valve, and the gearshift control subsystem, clutch control subsystem, lubrication control subsystem for passing through working connection connection, it is additionally provided with a branch on the working connection, is additionally provided with guide's oil pressure cntrol guiding valve with rear end feedback self-balancing thereon, the openings of sizes of the main oil pressure control valve controls the size of current of a solenoid valve to control by TCU.The beneficial effects are mainly as follows：Guide's oil pressure cntrol guiding valve can provide stable pilot pressure for entire gear change system, the size of pilot pressure will not be fluctuated because of the fluctuation of main oil pressure, the movement of gear shift guiding valve can be smoothly pushed under the action of solenoid valve, control hydraulic oil smoothly pushes selector fork to move, and has good gear shift ride comfort.
Description
Technical field
The present invention relates to automobile gearbox technical fields, are specifically applied to the hydraulic control system of the double clutch gearboxes of wet type
System.
Background technology
Wet-type dual-clutch refers to that double clutch is small one and large one two groups of multidisc clutches being co-axially mounted together, it
Be all installed in a closed oil pocket full of hydraulic oil.Therefore wet clutch structure has better regulating power,
Bigger torque can be transmitted；Meanwhile and due to can be cooled down and be lubricated using hydraulic oil, abrasion is smaller and scattered
Heat is good.For these reasons, wet-type dual-clutch is suitable for automobile manufacturing field by extensive fortune.
Although prior art hydraulic system can realize that the work of the double clutch gearboxes of wet type, control mode are susceptible to
The problems such as main oil pressure fluctuation is larger and oil pressure cntrol is unstable, the gearbox of such HYDRAULIC CONTROL SYSTEM mode is mounted in vehicle
Afterwards, it may appear that shifting shock and pause and transition in rhythm or melody are unfavorable for driving the driving impression of people.The pilot control oil pressure of main oil pressure control system by
It is affected in by working connection pressure fluctuation, the stability that main oil pressure controls can be caused relatively low, be susceptible to bigger oil
Pressure fluctuation, causes bigger influence, other hydraulic subsystems can follow the wave of main oil pressure to the control of other hydraulic subsystems
It moves and fluctuates, cause entire HYDRAULIC CONTROL SYSTEM unstable.Such as Chinese patent CN201410588154.7 and
Shown in CN201510362821.4, in the prior art, the hydraulic control system of the double clutch gearboxes of wet type needs to pass through engine
Mechanical oil pump is driven, the hydraulic oil that storage is drawn from the fuel tank as oil sources provides oil pressure.Although the hydraulic control system energy
Enough realize the work of the double clutch gearboxes of wet type, but control mode is susceptible to that main oil pressure fluctuation is larger and oil pressure cntrol is unstable
The problems such as, main reason is that：The ride comfort for controlling selector fork movement is more difficult, this is because the fluctuation of main oil pressure can be brought
Pilot control oil circuit impacts in gearshift control subsystem, due to the impact and fluctuation of guide's oil circuit, makes solenoid valve control in system
Gear shift guiding valve play occurs with the fluctuation of oil pressure, make the pressure oil by gear shift guiding valve occur fluctuating and impacting.In addition,
There is no interlocking structure in existing gearshift control subsystem, there is the risk for being formed simultaneously two gears on same root output shaft.
As shown in Chinese patent CN201510362821.4, in the prior art, the hydraulic control of the double clutch gearboxes of wet type
System relates merely to the separation and combination of clutch, when working connection fuel feeding shakiness can cause pressure fluctuation, is combined in clutch
When, inevitable the problems such as generating shifting shock and gear shift shake.In addition, the cleaning of oil circuit is also very in hydraulic control system
It is important, the case where otherwise will produce spool clamping stagnation.
The effect of speed changing box lubricating system is that double clutch to the inside of speed changer and the position of bearing element or sliding carry
For lubricating oil, it is ensured that the fluid lubrication of rubbing surface reduces friction and wear, while being cooled down to lubricant housings.With society
Develop, science and technology progress, requirement of the people to driver comfort and fuel-economy type is higher and higher, the requirement to discharge standard
More stringent, this promotes double clutch gearbox technology to be rapidly developed.Double clutch gearbox have unique structure and
The rotating speed of operation principle, operating mode complexity, gear and bearing is higher；Double clutch gear shift switching needs to control accurate, friction plate
Need the sliding control that rubs when gear shift switches, rub with the cunning of clutch, double clutch generates a large amount of heat, so to lubrication with
Cooling system proposes higher requirement.
In terms of gearbox gear cooling and lubricating, in current double clutch gearbox, some are used or tradition is splashed
Formula lubricates, and due to being arranged gear train assembly, is limited to the principle of splash system lubrication, is carried to the design and performance of tooth shaft
Huge challenge is gone out；Some also use compulsory lubricating system, but oil circuit and hardware configuration are sufficiently complex, to part
Design and producing technique propose higher requirement, such as Chinese patent CN203516692U, CN104196991B.
Chinese patent CN106321805A discloses a kind of lubrication oil circuit, but the lubrication oil circuit only only carries
For the cooling and lubricating to clutch, and the flow of cutting oil and pressure are not passed through spool and are controlled, lubrication oil stream amount
It is uncontrollable, cause entire lubricating and cooling system efficiency low.If clutch lubrication pressure is excessive, can cause clutch separation and
In conjunction with occurring, control is difficult, in the case where clutch control circuit pressure is relatively low, since lubrication pressure is excessively high, can cause from
Clutch cannot in conjunction with the case where occur.
Invention content
The purpose of the present invention is overcoming the shortcomings of the prior art, provide a kind of stabilization, safety to be applied to wet type double
The hydraulic control system of clutch gearbox.
The purpose of the present invention is achieved through the following technical solutions：
A kind of gear box hydraulic control system, including：
Fuel tank for providing hydraulic oil,
For being exported hydraulic oil to the oil supply subsystem of working connection from fuel tank,
Main oil pressure control valve for controlling working connection oil pressure,
And gearshift control subsystem, clutch control subsystem, the lubrication being connected to by working connection control subsystem
System,
The main oil pressure control valve is three-position four-way valve, has the guide end that be connected to the working connection, lead to it is oily after gram
Its spool is set to move to right after taking the spring force of the main oil pressure control valve spring of the main oil pressure control valve,
It is additionally provided with a branch on the working connection, is additionally provided with guide's oil pressure cntrol with rear end feedback self-balancing thereon
Guiding valve, forms the hydraulic oil of steady pressure by the hydraulic coupling at its guide end and the spring dynamic balance of spring terminal, and the hydraulic oil is logical
The spring terminal that guide's oil circuit leads to the main oil pressure control valve is crossed, the openings of sizes of the main oil pressure control valve controls one by TCU
The size of current of solenoid valve controls.
Preferably, the oil supply subsystem includes the mechanical pump and electronic pump for being respectively communicated with the fuel tank, the mechanical pump
Selectively hydraulic oil is exported from fuel tank with electronic pump to working connection, the hydraulic oil output end of the mechanical pump and electronic pump
On be equipped with check valve, be equipped with strainer on input terminal.
Preferably, the working connection is equipped with a safety relief valve, between the fuel tank and main oil pressure control valve
On oil circuit.
Preferably, the gearshift control subsystem includes：
The one group of selector fork driven by the hydraulic oil, the selector fork by synchronizer for selectively with
Shifting gear synchronizes to form gear, and the shifting gear includes seven forward gears and a reversing shelves gear, odd number shelves
Gear is arranged on same root odd number shelves output shaft, and even number shelves gear and reversing shelves gear are arranged in another even gear output
On axis,
The gear shift guiding valve equal with the selector fork quantity and the solenoid valve for controlling each gear shift guiding valve, it is same
Root output shaft is equipped with gear hydraulic interlock structure；
The main oil of the first gear shift hydraulic oil in working connection being selectively input to respectively in the plunger shaft of selector fork
Road and the second gear shift working connection；
Oil circuit change-over pilot valve for switching the first gear shift working connection and the second gear shift working connection.
Preferably, the gearshift control subsystem includes four gear shift cunning there are four selector fork and corresponding thereto
Valve, every two pairs of gear shift guiding valves and selector fork act on same root output shaft, and each gear shift guiding valve all has a control
The solenoid valve of its spool movement is made, and there is a guide end and spring terminal, the guide end passes through solenoid valve and the fuel tank
Connection, the hydraulic interlock structure is that the hydraulic interlock acted at two between the gear shift guiding valve on same root output shaft is arranged
Oil circuit, one end of the hydraulic interlock oil circuit are connected to the guide end of a gear shift guiding valve wherein, and the other end is connected at another
The spring terminal of gear shift guiding valve.
Preferably, by being formed by the hydraulic oil with steady pressure after guide's oil pressure cntrol guiding valve, pass through institute
The guide end for stating each gear shift guiding valve of guide's oil circuit connection, is equipped between the guide's oil circuit and the guide end of gear shift guiding valve
Strainer and throttle orifice.
Preferably, the guide's oil circuit of the oil circuit change-over pilot valve passes through a solenoid valve control；The oil circuit change-over pilot valve connects
It is connected to a counterbalance valve.
Preferably, the clutch hydraulic pressure control subsystem includes：
First clutch control valve and second clutch control valve are separately positioned on and lead to described first by the working connection
On the fluid pressure line of clutch and second clutch,
The accumulator of output end in the first clutch control valve and second clutch control valve is accordingly set respectively.
Preferably, the first clutch control valve has guide end and spring terminal, the first clutch control valve
The oil circuit of output end sets backfeed loop, and the backfeed loop is communicated between the guide end and spring terminal, and the guide end is anti-
The opening diameter for presenting the throttle orifice of oil circuit is less than the opening diameter that the spring terminal feeds back the throttle orifice of oil circuit；Second clutch
The oil channel structures of device control valve are identical as the oil channel structures of first clutch control valve.
Preferably, the input terminal and output end of the first clutch control valve and second clutch control valve respectively connect
There is strainer.
Preferably, the working connection leads to the first clutch respectively and the fluid pressure line of second clutch is equipped with pressure
The output end in the first clutch control valve and second clutch control valve is arranged in force snesor, the pressure sensor,
And at the plunger shaft of the first clutch and second clutch.
Preferably, the lubrication control subsystem, including：
The lubricant passage way exported from the main oil pressure control valve,
It is connected to the oil cooler and pressure filter of the lubricant passage way, and the lubrication exported from the oil cooler and pressure filter
Cooling oil path, the lubrication oil circuit are divided into two-way, are respectively used to clutch lubrication and gearbox inner bearing lubrication；
The lubrication oil circuit for gearbox inner bearing lubrication is divided into two-way, respectively axis lubrication oil circuit and
Bearing lubrication cooling oil path,
The lubrication oil circuit for clutch lubrication after a lubrication flow control valve by forming clutch lubrication
Cooling oil path, the lubrication flow control valve control the big of signal control valve electromagnetic part electric current by gear box control unit TCU
It is small come regulating valve openings of sizes, the output end of the lubrication flow control valve passes through one residual stress control valve of oil circuit connection, institute
It includes a guide end and a spring terminal with residual stress control valve spring to state residual stress control valve, is located at described residual
The both sides of residue stress control valve, the guide end of the residual stress control valve are connected to the lubrication oil circuit, the lubrication
For cooling oil path also by the residual stress control valve and a draining oil communication, the draining oil circuit output end leads to the oil
Case, the output end of the lubrication flow control valve are connected to the spring terminal of the residual stress control valve.
Preferably, the front and rear sides of the lubrication flow control valve are equipped with a strainer, are front side strainer and rear side respectively
Strainer, oil circuit connection point between the output end of the lubrication flow control valve and the residual stress control valve be located at it is described after
Between side screen and clutch.
Preferably, the oil circuit between the output end of the lubrication flow control valve and residual stress control valve spring end
It is equipped with throttle orifice, throttle orifice is equipped between the guide end of the residual stress control valve and the lubrication oil circuit.
Preferably, the lubricant passage way is equipped with flow control valve, and the hydraulic oil of the lubricant passage way output passes through institute
It is divided into two-way after stating flow control valve, wherein hydraulic oil overcomes flow control valve bullet through the dynamic flow control valve of throttle orifice pusher all the way
Spool is set to move to left after the spring force of spring, the second road hydraulic oil is divided into after throttle orifice as two-way, and the first via is after throttle orifice
The spring terminal for reaching the flow control valve, working with spring one makes the spool of the flow control valve move to right, thus with the right side
The pilot pressure of side forms a dynamic equilibrium, hydraulic oil of the second tunnel output with steady pressure and flow, into measured lubrication
The hydraulic oil of oil circuit, the measured lubrication oil circuit enters the oil cooler.
Preferably, a check valve in parallel on the inlet and outlet of fuel channel of the pressure filter.
Preferably, there is the measured lubrication oil circuit branch, the branch road to be equipped with one under case of by-pass valve effect
The by-passing valve of normal off, the branch is in parallel with by the oil circuit of the oil cooler, and the by-passing valve has a guide end, the elder generation
Lead end and the measured lubrication oil communication.
The beneficial effects are mainly as follows：
1, guide's oil pressure cntrol guiding valve of the present invention can provide stable pilot pressure, pilot pressure for entire gear change system
Size will not be fluctuated because of the fluctuation of main oil pressure, the movement of gear shift guiding valve can be smoothly pushed under the action of solenoid valve,
Control hydraulic oil smoothly pushes selector fork to move, and has good gear shift ride comfort；
2, gearshift control subsystem of the present invention has the function of the hydraulic interlock of same root output shaft gear, is exported in same root
Only there are one gears to combine on axis, avoids caused by solenoid valve malfunction causes to form two gears on same root output shaft
Gearbox damage；
3, lubrication control subsystem of the present invention is equipped with flow control valve, reflexive by the guide end of flow control valve
Feedback, spring terminal feedback and spring force ensure lubricating and cooling system of the present invention in the dynamic equilibrium of the axial direction of flow control valve
With stable pressure and flow；Equipped with residual pressure control valve, the highest oil pressure of lubricating and cooling system of the present invention is limited, is protected
The safety of lubricating and cooling system is demonstrate,proved；
4, lubrication control subsystem of the present invention is equipped with check valve in the oil circuit in parallel of pressure filter, ensures to lose in pressure filter
Enough lubricating cooling oils are provided for whole system when effect or blocking, ensure that gearbox can continue to work normally；In oil
Oil circuit after cooler and pressure filter series connection is equipped with by-passing valve, ensures when oil cooler occurs to block or this oil circuit is completely plugged,
Still enough hydraulic oil provides enough lubricating cooling oils for the bearing and clutch of gearbox；
5, the oil circuit of the nearly clutch vessel of clutch control subsystem of the present invention is equipped with accumulator, avoids because of working connection
Oil caused by fluctuation shakes and hydraulic shock；Clutch control guiding valve is equipped with feedback oil circuit at guide end and spring terminal, is formed certain
Pressure difference, so that the movement of guiding valve is more smoothed out, smoothed curve control may be implemented to the control of clutch pressure；
6, fuel feeding system of the present invention system uses mechanical pump and electronic pump double pump fuel feeding, can reduce the volume of mechanical pump, increases
Add the flexibility of arrangement, while improving the efficiency of entire hydraulic system；
7, present invention setting safety relief valve, can limit whole system maximum pressure, protect entire hydraulic system
Safe main oil pressure control subsystem.
Description of the drawings
Technical scheme of the present invention is further explained below in conjunction with the accompanying drawings：
Fig. 1：The hydraulic diagram of gear box hydraulic control system of the present invention；
Fig. 2：The hydraulic diagram of gearshift control subsystem of the present invention；
Fig. 3：The hydraulic diagram of clutch control subsystem of the present invention；
Fig. 4：The hydraulic diagram of main oil pressure control subsystem of the present invention；
Fig. 5：The hydraulic diagram of lubrication control subsystem of the present invention；
Fig. 6：The hydraulic diagram of oil supply subsystem of the present invention.
Specific implementation mode
Below with reference to specific implementation mode shown in the drawings, the present invention will be described in detail.But these embodiments are simultaneously
It is not limited to the present invention, structure that those skilled in the art are made according to these embodiments, method or functionally
Transformation is included within the scope of protection of the present invention.
As shown in Figure 1, present invention is disclosed a kind of gear box hydraulic control system, including 5 subsystems：Oil supply subsystem
5, main oil pressure control subsystem 3, gearshift control subsystem 1, clutch control subsystem 2 and lubrication control subsystem 4.
1, oil supply subsystem：Double pump fuel feeding, mechanical pump and electronic pump combine fuel feeding；
2, main oil pressure control subsystem：Safety relief valve and working connection control valve co- controlling；
3, clutch control subsystem：Control subsystem to carrying out double filtration by the hydraulic oil of clutch control valve,
Accumulator is added in the rear end oil circuit of control valve, accumulator can absorb the oil caused by main oil pressure fluctuates and shake, to realize
Clutch combines and the ride comfort of separation；
4, gearshift control subsystem：Gearshift control subsystem is by four groups of gear shift guiding valves and solenoid valve, reducer unit at subsystem
System hydraulic interlock, ensure that the safety of entire gear change system；
5, lubrication control subsystem：Mainly moistened by flow control guiding valve, by-passing valve, oil cooler, oil screen, clutch
Sliding control valve, residual pressure spool control valve composition can realize the sufficient lubrication of gearbox bearing and the double clutches of wet type, make entire
The parts of gearbox work within the scope of a reasonable temperature.
The structure and the course of work of subsystems are described in detail below in conjunction with the accompanying drawings.
In conjunction with shown in Fig. 1 and Fig. 6, present invention is disclosed a kind of oil supply subsystems 5.The oil supply subsystem 5 includes being used for
The fuel tank 500 of hydraulic oil is provided, and for the electronic pump 501 and mechanical pump 502 to subsystems pump oil.Double pump of the present invention
It is equipped with strainer 503 between fuel feeding, with the fuel tank 500, keeps the cleaning of the oil product of output.The liquid of the mechanical pump and electronic pump
Check valve 504 is equipped on pressure oil output end, the oil pressure for keeping subsystems.
In conjunction with shown in Fig. 1 and Fig. 4, present invention is disclosed a kind of main oil pressure control subsystems 3, including from the fuel feeding subsystem
The working connection a exported in system 5, the main oil pressure control valve 301 for controlling working connection oil pressure, the main oil pressure control valve 301 are
Three-position four-way valve has the guide end 302 being connected to the working connection a, the master of the main oil pressure control valve is overcome after logical oil
Move to right its spool after the spring force of oil pressure cntrol valve spring 303.
It is additionally provided with a branch on the working connection a, it is voltage-controlled to be additionally provided with a guide oil with rear end feedback self-balancing thereon
Guiding valve 304 processed forms the hydraulic oil of steady pressure by the hydraulic coupling at its guide end and the spring dynamic balance of spring terminal, specifically
's：Pressure oil of the pressure oil of working connection a after guide's oil pressure cntrol guiding valve 304 decompression provides pressure for the guide end of the valve
Power oil, since its spool has certain cross-sectional area, forms certain pressure with the pressure oil at the guide end for acting on the valve, pushes away
Movable valve plug overcomes the spring force of the other end, the power interaction at both ends to reach the relationship of a stable dynamic equilibrium.When main oil
When the pressure rise of road a, the hydraulic fluid flow rate for flowing through guide's oil pressure cntrol guiding valve 304 increases, through guide's oil pressure cntrol guiding valve 304
Pressure afterwards also can be with raising, at this point, the guide's oil pressure for acting on guide's oil pressure cntrol guiding valve 304 equally increases, formerly
Under the action of Oil Guide, guide's oil pressure cntrol guiding valve 304 will push spool to be moved to spring terminal under the action of hydraulic coupling, this
When, the hydraulic oil opening area into guide's oil pressure cntrol guiding valve 304 reduces, and the hydraulic fluid flow rate for flowing through the valve is reduced, and is passed through
Hydraulic fluid pressure after the valve reduces, and the guide's oil pressure for acting on the valve reduces, and under spring force, spool is to opposite
Direction is moved, and the hydraulic oil area for flowing through the spool increases, and is flowed through the pressure oil pressure all-the-time stable after the valve and is moved at one
State balances.When working connection pressure reduction, working method is similar to when increasing.
The hydraulic oil of the steady pressure leads to the spring terminal of the main oil pressure control valve, the main oil by guide's oil circuit d
The openings of sizes of pressure control valve 301 controls the size of current of a solenoid valve 305 to control by TCU.
The working connection is equipped with a safety relief valve 306, the oil circuit between the fuel tank and main oil pressure control valve
On.The safety relief valve 306 can limit whole system maximum pressure, make entire hydraulic work system in a rational pressure
In range, protect entire hydraulic system and its related work parts, safety relief valve way of realization in engineer application more
Sample, implementation method are flexible.When the pressure of system is greater than the set value, the pressure at the guide end of safety relief valve 306 overcomes spring
Power, so that spool is moved to left, draining decompression.
The shape that main oil pressure control subsystem 3 is combined using one main oil pressure control valve of safety relief valve and solenoid valve control
Formula.303 working methods of main oil pressure control valve are：By controlling the size of the electric current of solenoid valve 305, and then controls and enter guiding valve
Control of the how much realizations of spring terminal flow to pressure size controls the control of pressure size main oil by solenoid valve 305
The position of pressure control valve controls the size of the mobile control port of valve position by main oil pressure to realize the control to main oil pressure.
Guide's oil pressure cntrol guiding valve 304 is fed back by rear end, using the equilibrium relation of hydraulic coupling and spring force, is provided surely for whole system
Fixed guide's oil pressure.
In conjunction with shown in Fig. 1 and Fig. 2, present invention is disclosed a kind of gearshift control subsystems 1, including：First gear shift working connection b
With the second gear shift working connection c.There is an oil circuit change-over pilot valve 105 controlled by solenoid valve S5, the oil circuit change-over pilot valve 105 can
With selectively by working connection a switching connections the first gear shift working connection b or the second gear shift working connection c.The solenoid valve S5 TCU
The size of its electric current of Linear Control.The oil circuit change-over pilot valve 105 is connected with a counterbalance valve 108, after ensure that working connection switching,
In the oil duct that no fluid is supplied always with the presence of hydraulic oil, oil pressure is quickly established conducive to entire hydraulic shift control system.
The first gear shift working connection b and the second gear shift working connection c make hydraulic pressure by being selectively communicated with gear shift guiding valve
Oil be selectively input in the plunger shaft of selector fork, each selector fork can selectively with shifting gear synchronize form shelves
Position, the shifting gear include seven forward gears and a reversing shelves gear, and it is strange that odd number shelves gear is arranged in same root
On several grades of output shafts, even number shelves gear and reversing shelves gear are arranged on another even gear output shaft.
Specifically, there are four selector forks, respectively the first selector fork F1, the second gear shift for preferred embodiments thereof
Shift fork F2, third selector fork F3, the 4th selector fork F4.Wherein, the first selector fork F1 is for controlling corresponding synchronizer and 1
Shelves gear or 5 shelves gears synchronize to form gear, and the second selector fork F2 is for controlling corresponding synchronizer and 3 shelves gears or 7 grades of teeth
Wheel synchronizes to form gear, third selector fork F3 for control corresponding synchronizer and R shelves gears or 4 shelves gears synchronize form shelves
Position, the 4th selector fork F4 for control corresponding synchronizer and 2 shelves gears or 6 shelves gears synchronize form gear.
Each selector fork is controlled by a gear shift guiding valve, respectively the first gear shift guiding valve 101, the second gear shift guiding valve
102, third gear shift guiding valve 103, the 4th gear shift guiding valve 104.For example, the hydraulic oil in working connection passes through the second gear shift guiding valve
102 when entering in the plunger shaft of 3 shelves gear gears of control, pushes the second corresponding synchronizer of selector fork F2 control and 3 grades of teeth
Wheel synchronized shifting synchronizes to form gear.
Each gear shift guiding valve all has a guide end and spring terminal, and the guide end is by controlling guide's oil circuit
Solenoid valve is connected to the fuel tank.Preferably, each gear shift guiding valve all has the movement of its spool of a control and determines it and open
Solenoid valve S1, S2, S3, S4 of mouth size, and the guide's oil circuit at its guide end is connected to guide's oil pressure cntrol guiding valve 304.Make
For being equipped with gear between the gear shift guiding valve of two selector forks on the odd number shelves output shaft or even gear output shaft
Hydraulic interlock structure；The hydraulic interlock structure is hydraulic interlock oil circuit, and one end connection of the hydraulic interlock oil circuit is wherein
The guide end of one gear shift guiding valve, the other end are connected to the spring terminal in another gear shift guiding valve.Such as：With odd number shelves output shaft phase
Cooperation is the first gear shift guiding valve 101 and the second gear shift guiding valve 102, has hydraulic interlock structure between the two, is that a hydraulic pressure is mutual
Oil circuit 107 is locked, at the guide end of the first gear shift guiding valve 101, other end connection exists for one end connection of the hydraulic interlock oil circuit 107
The spring terminal of second gear shift guiding valve 102.Equally there is hydraulic interlock knot between the gear shift guiding valve of mating on even gear output shaft
Structure.
The guide end of each gear shift guiding valve of guide's oil circuit d connections in this subsystem.The guide's oil circuit with
Strainer and throttle orifice are equipped between guide end.
The course of work of gearshift control subsystem of the present invention is briefly described below.
For fuel tank by working connection a fuel feeding, the position through the 5th solenoid valve S5 control oil circuits change-over pilot valve 105 gives first respectively
Gear shift working connection b and the second gear shift working connection c fuel feeding, when the solenoid valve for controlling oil passage change-over valve does not have electric current, at this time the
One gear shift working connection b can be 4 grades, 5 grades, 6 grades, 7 grades of this four gear fuel feeding, when the electromagnetism of control oil circuit change-over pilot valve 105
When valve S5 reaches a constant current, oil circuit change-over pilot valve 105 switches oil circuit at this time, the second gear shift working connection c at this time to R grades, 1
Shelves, 2 grades, 3 grades of this four gear fuel feeding.
The hydraulic oil of working connection a after guide's oil pressure cntrol guiding valve 304 be respectively：First gear shift guiding valve 101, second changes
Shelves guiding valve 102, third gear shift guiding valve 103, the 4th gear shift guiding valve 104, oil circuit change-over pilot valve 105 provide stable guide oil, are
The oil circuit smooth-going switching of oil circuit change-over pilot valve 105 provides guarantee, makes the guide oil of control gear shift guiding valve not acceptor's pressure fluctuation
Influence.
Before not forming gear, the first gear shift guiding valve 101, the second gear shift guiding valve 102, third gear shift guiding valve 103, the 4th
Under the effect of spring force, gear shift guiding valve is in left position to gear shift guiding valve 104.First gear shift guiding valve 101, the second gear shift guiding valve
102, third gear shift guiding valve 103, the 4th gear shift guiding valve 104, oil circuit change-over pilot valve 105 position movement respectively by solenoid valve S1,
S2, S3, S4, S5 are controlled, the switching of the mobile corresponding oil circuit of carry out by controlling gear shift spool position, and then complete shelves
The switching of position.
Synchronize to form shifting gear on same axis due to forming 1 grade, 3 grades, 5 grades, 7 grades, formed R grades, 2 grades, 4
Shelves, 6 grades synchronize to form shifting gear on same axis, in order to avoid being exported in same root caused by the malfunction of solenoid valve
It is formed simultaneously two gears on axis, the damage or vehicle in turn resulting in gearbox are unable to normally travel, therefore, utilize hydraulic pressure
Interlocking mode respectively to 1 grade, 3 grades, 5 grades, 7 grades progress hydraulic protectings, while in the same way to R grades, 2 grades, 4 grades, 6
Shelves carry out hydraulic interlock protection.
Specific gear switch is as follows：For 1 grade, hydraulic oil enters working connection a, and solenoid valve S5 is powered at this time, oil circuit
105 guide end of change-over pilot valve forms closed vessel, establishes pilot pressure, and the spool of oil circuit change-over pilot valve 105 is pushed to overcome bullet
Spring force moves to left, and the valve is made to work in right position, by the second gear oil circuit c unicom, at this time the first gear oil circuit b cut-offs.Solenoid valve S1
Work, 101 guide end of the first gear shift guiding valve form closed vessel, establish guide's oil pressure, and the first gear shift guiding valve 101 is pushed to overcome
Spring force is moved to the left, and by the plunger shaft unicom of 1 grade of the second gear shift working connection c and control, piston pushes selector fork movement,
Under the control of solenoid valve, quick flat consequent relief is at 1 grade.Meanwhile guide's oil pressure at 101 guide end of the first gear shift guiding valve acts on
The spring terminal and spring of two gear shift guiding valves 102 ensure that the second gear shift guiding valve 102 is in left position together, at this point, even if solenoid valve S2
Malfunction, there is oil pressure at 102 guide end of the second gear shift guiding valve, due to gear shift guiding valve spring terminal hydraulic coupling than guide end first pilot
Power is big or equally big, plays the role of spring force simultaneously in spring terminal, therefore the plunger shaft for leading to 3,7 gears there will not be hydraulic pressure
Oil enters, and avoiding has two pairs of gears in the gear for forming gear on same axis while synchronizing the case where forming gear.
Similarly, when forming 3 grades, 1 grade of control, 5 grades, 7 grades of oil circuit be in cut-off state, such control mode is formed liquid
Pressure interlocking, guarantee is provided for the normal work of gearbox.
Before 1 grade rises 2 grades, 2 grades of pre- gear selecting work has been completed, and operation principle is identical as 1 grade of operation principle, i.e.,
1 grade rises 2 grades, and solenoid valve S5 is powered, and pilot pressure is established at 105 guide end of oil circuit change-over pilot valve, pushes 105 grams of oil circuit change-over pilot valve
It takes spring force to move to left, makes the right position work of the valve, by the second gear oil circuit c unicom, at this time the first gear oil circuit b cut-offs.At this point, with
It is 0A by the current control of the solenoid valve S1 of the first gear shift guiding valve 101, the oil circuit of the first gear shift guiding valve 101 control is in cut-off
State.The solenoid valve for controlling the 4th gear shift guiding valve 104 uses the size of TCU Linear Control electric currents at this time, progressivelyes reach maximum value, liquid
Pressure oil acts on the plunger shaft of 2 grades of control, and piston movement pushes shift fork smoothly to move, and quick flat consequent relief is at 2 grades.4th changes
Oil pressure is established at the guide end of shelves guiding valve 104, and the 4th gear shift guiding valve 104 is pushed to be moved to the left, meanwhile, act on the 4th gear shift guiding valve
104 guide oil acts on the spring terminal of shift valve C, and the oil circuit of R grades and 4 grades of control is made to be in cut-off state.Similarly, work as formation
At 4 grades, R grades, 2 grades, 6 grades are in cut-off state.Its hydraulic interlock protected mode with it is aforementioned similarly, avoided in this way same
Malfunction on root axis because of solenoid valve is formed simultaneously the generation of two gear stages, avoids the risk of gearbox damage.
Show in conjunction with Fig. 1 and Fig. 3, present invention is disclosed a kind of clutch control subsystems 2, for controlling the first clutch respectively
The combination and separation of device 201 and second clutch 202, including the first clutch 201 is led to by the working connection 30 respectively
The corresponding first clutch control valve 203 and second clutch control valve being equipped with the fluid pressure line of second clutch 202
204.Specifically, the first clutch control valve 203 and second clutch control valve 204 are VFS solenoid valves.VFS electromagnetism
The characteristics of valve is can be to pressure and precise control of flew.The first clutch control valve 203 has guide end 2031 and bullet
The oil circuit at spring end 2032, the output end of the first clutch control valve 203 sets backfeed loop, and the backfeed loop is communicated in institute
It states between guide end 2031 and spring terminal 2032, the opening diameter that the throttle orifice 2033 of oil circuit is fed back at the guide end 2031 is less than
The spring terminal 2032 feeds back the opening diameter of the throttle orifice 2034 of oil circuit；The oil circuit knot of the second clutch control valve 204
Structure is identical as the oil channel structures of the first clutch control valve 203.
The control accuracy of clutch of the present invention is embodied in：By the oil circuit of output end on rear side of VFS clutch control valves
If backfeed loop, i.e., it is equipped with feedback oil circuit at guide end 2031 and spring terminal 2032, the throttle orifice of oil circuit is fed back at guide end 2031
The size that 2033 size ratio spring terminal 2032 feeds back the throttle orifice 2034 of oil circuit is small, certain pressure difference can be formed, in electricity
When magnet valve controls, the accuracy that control clutch is combined and detached can be improved.Meanwhile the first clutch control valve 203
It is respectively connected with an accumulator 205 with the output end of second clutch control valve 204.The accumulator 205 can be absorbed because of main oil
Oil caused by the fluctuation on road shakes and hydraulic shock, keeps the combination of clutch and both states of separation more steady.
The input terminal of the first clutch control valve 203 and second clutch control valve 204 is respectively connected with strainer
206.The output end of the first clutch control valve 203 and second clutch control valve 204 is respectively connected with strainer 207.It is main
Hydraulic oil in oil circuit a reaches VFS clutch control valves after the filtering of strainer 206, and hydraulic oil passes through VFS clutch control valves
Afterwards, the filtering again through filter screen 207 reaches clutch.The main function that the strainer 207 is set be when the clutch is disengaged, from
When hydraulic oil draining inside clutch plunger shaft can after the strainer 207 again by clutch control valve draining, which ensure that
When draining, clutch control valve will not due to fluid takes back the impurity inside clutch clamping stagnation.
The working connection a leads to the first clutch 201 respectively and the fluid pressure line of second clutch 202 is equipped with pressure
Force snesor 208.The pressure sensor 208 is arranged in the first clutch control valve 203 and second clutch control valve
204 output end, and at the plunger shaft of the first clutch 201 and second clutch 202.I.e. the present invention is in the control
Oil circuit sets pressure sensor at clutch piston cavity, the pressure value measured closer to clutch control pressure it is true
Value, reliable guarantee is provided for the self-learning function of whole system.
The control mode of clutch control subsystem of the present invention is the size control of the electric current by controlling clutch control valve
Spool processed and valve body cooperation opening size control into clutch piston cavity hydraulic oil number, clutch plunger is adjusted
The size of hydraulic fluid pressure in chamber, and then adjust the size of clutch transmission torque.
In the present invention in clutch control subsystem, the control loop of clutch is provided on rear side of clutch control valve
Accumulator can absorb the pressure fluctuation caused by fuel feeding is unstable, when clutch combines, to avoid shifting shock and can change
The problems such as shelves shake；It is provided with pressure sensor in clutch control circuit, can in real time be transmitted clutch pressure signals
To TCU, guarantee is provided for the closed-loop control of clutch, data supporting is provided for the self-learning function of gearbox, it is entire to become
The control of fast case is more accurate；It is provided with front and back strainer in clutch control oil, ensure that the cleannes of control oil circuit, valve
There is the case where clamping stagnation and seldom occurs in core.
Referring to figure 1 and figure 5, present invention further teaches a kind of lubrication control subsystems.The lubrication control
Subsystem includes by hydraulic oil from the working connection a exported in fuel tank and the lubrication exported from the main oil pressure control valve 301
Oil circuit m.The main oil pressure control valve 301 has the guide end being connected to the working connection a.When gearbox works, hydraulic oil is logical
The left side guide end 302 that throttle orifice acts on the main oil pressure control valve 301 is crossed, hydraulic oil plays guide at this time, pushes
The main oil pressure control valve 301 moves to the right, and the main oil pressure control valve 301 works in middle position at this time, by working connection a and profit
Lubricating oil road m is connected to, and lubricating oil is provided for entire lubricating and cooling system.
The lubricant passage way m is equipped with flow control valve 403, and what the lubricant passage way m was exported has certain pressure
Hydraulic oil is divided into two-way after the flow control valve 403, wherein hydraulic oil pushes flow control after throttle orifice H5 all the way
Valve 403 makes spool move to left after overcoming the spring force of flow control valve spring S6, and the second road hydraulic oil is divided into after throttle orifice H6
For two-way, the first via reaches the spring terminal of the flow control valve 403 after throttle orifice H7, and working with spring one, it is described to make
The spool of flow control valve 403 moves to right, and to form a dynamic equilibrium with the pilot pressure on right side, the output of the second tunnel, which has, stablizes
The hydraulic oil of pressure and flow enters measured lubrication oil circuit n, the hydraulic oil of the measured lubrication oil circuit n after throttle orifice H6
Pressure filter 410 is reached after oil cooler 408, forms lubrication oil circuit e.Wherein, the pressure filter 410 is equipped with parallel connection
Check valve 409, when pressure filter 410 blocks, check valve 409 is opened, and ensure that the lubrication of gearbox bearing and clutch
It is cooling.Meanwhile it being equipped on side in oil cooler 408 with oil circuit in parallel, parallel oil road is equipped on 410 concatenated oil circuit of pressure filter
The by-passing valve 404 of the lower normal off of port valve spring S7 effects.The by-passing valve 404 has a guide end, and the guide end passes through throttling
Hole H8 is connected to the measured lubrication oil circuit n.When the oil cooler 408 connect with pressure filter 410 oil circuit block when, it is described
By-passing valve 404 is opened, and ensure that gearbox has enough lubricating oil, vehicle is allow to continue to travel.
Lubrication oil circuit e after pressure filter is divided into two-way, is respectively used to clutch lubrication and gearbox inner bearing profit
It is sliding.Wherein, the lubrication oil circuit e for gearbox inner bearing lubrication is divided into two-way, respectively axis lubrication oil circuit h and axis
Lubrication oil circuit j is held, every branch road is equipped with throttle orifice.Purpose equipped with throttle orifice be for entire lubricating and cooling system into
Row pressurize, this is the common knowledge of throttle orifice, is hereafter repeated no more.
The lubrication oil circuit e for clutch cooling and lubricating by formed after a lubrication flow control valve 406 from
Clutch lubrication oil circuit g.Specifically, the lubricating cooling oil for clutch cooling and lubricating passes through lubrication flow control valve 406
After accurately controlling, the filtering of small strainer is again passed by, enough lubricating cooling oils are provided for clutch.The lubrication flow control
Valve 406 controls signal by gear box control unit TCU and controls the size of electromagnetic part electric current come regulating valve openings of sizes.
The output end of the lubrication flow control valve 406 passes through one residual stress control valve 405 of oil circuit connection, the remnants
Stress Control valve 405 includes a guide end and a spring terminal, is located at the both sides of the residual stress control valve 405, described
The guide end of residual stress control valve 405 is connected to the lubrication oil circuit e, and the lubrication oil circuit e also passes through described
Residual stress control valve 405 is connected to a draining oil circuit f, and the draining oil circuit f output ends lead to the fuel tank.
The output end of the lubrication flow control valve 406 is connected to the spring terminal of the residual stress control valve 405.It is described
Oil circuit connection point between the output end of lubrication flow control valve 406 and the residual stress control valve 405 is located at the rear side
Between small strainer and clutch.
The reason of being arranged in this way is：When being worked normally due to clutch, the lubricating cooling oil needed is less, in sliding rub
The lubrication Chuck Steak needed, in order to ensure that the pressure of lubricating and cooling system is unlikely excessive, lubrication control of the present invention
System is equipped with the residual stress control valve 405.The main function of the residual stress control valve 405 is when clutch needs greatly
When the lubricating cooling oil of flow, lubrication flow control valve 406 is opened, and is had enough in the spring terminal of residual stress control valve 405
Hydraulic oil, the hydraulic oil of 405 spring terminal of residual stress control valve and spring collective effect make the residual stress control
Valve 405 is in cut-off state, lubricating oil will not draining to fuel tank；It is cold due to lubricating when the lubricating oil that clutch needs is less
But the lubricating oil of system is stable flow, in order to ensure that the pressure of entire lubricating and cooling system is unlikely excessive, residual stress control
The guide end of valve 405 processed is moved to the left under the action of hydraulic oil, and lubrication oil circuit e and draining oil circuit f unicom are let out to fuel tank
Oil；When the lubrication oil circuit e pressure is smaller, under the action of residual pressure control valve spring S5, residual stress control
Valve 405 moves right, and closes draining.The setting of residual stress control valve 405 not only ensure that system had enough flows, but also energy
Ensure that the pressure of lubrication is unlikely excessive.
In the present invention, when the pressure of main oil pressure is excessive, the working position of main oil pressure control valve 301 can be in left position, at this point,
For a part of hydraulic oil draining in working connection a to fuel tank, another part hydraulic oil flows to lubricant passage way m.In order to ensure main oil pressure
Control valve 301 in high pressure not because draining excessively leads to lubricating system hydraulic pressure shortage of oil, in the right end of main oil pressure control valve 301,
I.e. the spring terminal of main oil pressure control valve 301 is equipped with guide's oil circuit d, and the big of spring terminal hydraulic fluid pressure is controlled by solenoid valve 305
It is small to carry out the location of control main oil pressure control valve 301.
The entire lubrication control subsystem of the present invention has always by the control of series of valves, entire lubricating and cooling system
There is sufficient lubricating cooling oil, so that the parts of transmission internal is fully cooled lubrication, ensure that gearbox can be stablized just
Often work.System is equipped with flow control valve, is being flowed by the guide end self feed back of flow control valve, spring terminal feedback and spring force
The dynamic equilibrium of the axial direction of control valve ensures that lubricating and cooling system of the present invention has stable pressure and flow；This hair
The bright oil circuit in parallel in pressure filter is equipped with check valve, ensures to provide for whole system when pressure filter fails or blocks enough
Lubricating cooling oil ensure that gearbox can continue to work normally；Oil circuit of the present invention after oil cooler and pressure filter series connection is set
There is by-passing valve, ensures that, when oil cooler occurs to block or this oil circuit is completely plugged, it is gearbox still to have enough hydraulic oil
Bearing and clutch enough lubricating cooling oils are provided；The present invention is equipped with residual pressure control valve, limits lubrication of the present invention
The highest oil pressure of cooling system ensure that the safety of lubricating and cooling system；Lubrication flow control in clutch lubrication oil circuit of the present invention
Valve processed is controlled using VFS solenoid valves, than using VBS solenoid valve controls more accurate, ensure that clutch has in sliding rub
Enough lubrication flows, make the service life of clutch be significantly improved；The present invention is equipped with guide's oil pressure cntrol guiding valve, is
Main oil pressure control valve provides stable guide's oil pressure.
It should be appreciated that although this specification is described in terms of embodiments, but not each embodiment only includes one
A independent technical solution, this description of the specification is merely for the sake of clarity, and those skilled in the art should will say
As a whole, the technical solution in each embodiment may also be suitably combined to form those skilled in the art can for bright book
With the other embodiment of understanding.
The series of detailed descriptions listed above only for the present invention feasible embodiment specifically
Bright, they are all without departing from equivalent implementations made by technical spirit of the present invention not to limit the scope of the invention
Or change should all be included in the protection scope of the present invention.
Claims (16)
1. gear box hydraulic control system, it is characterised in that：Including
Fuel tank for providing hydraulic oil,
For being exported hydraulic oil to the oil supply subsystem of working connection from fuel tank,
Main oil pressure control valve for controlling working connection oil pressure,
And gearshift control subsystem, clutch control subsystem, lubrication control subsystem by working connection connection,
The main oil pressure control valve is three-position four-way valve, has the guide end being connected to the working connection, overcomes institute after logical oil
Its spool is set to move to right after stating the spring force of the main oil pressure control valve spring of main oil pressure control valve,
It is additionally provided with a branch on the working connection, is additionally provided with guide's oil pressure cntrol with rear end feedback self-balancing thereon and slides
Valve, forms the hydraulic oil of steady pressure by the hydraulic coupling at its guide end and the spring dynamic balance of spring terminal, which passes through
Guide's oil circuit leads to the spring terminal of the main oil pressure control valve, and the openings of sizes of the main oil pressure control valve controls list by gearbox
Member controls the size of current of a solenoid valve to control；
The gearshift control subsystem includes four gear shift guiding valves there are four selector fork and corresponding thereto, described in every two pairs
Gear shift guiding valve and selector fork act on same root output shaft, and each gear shift guiding valve all has a control its spool movement
Solenoid valve, and there is a guide end and spring terminal, the guide end is connected to by solenoid valve with the fuel tank, and the hydraulic pressure is mutual
Lock construction is that the hydraulic interlock oil circuit acted at two between the gear shift guiding valve on same root output shaft is arranged, and the hydraulic pressure is mutual
The one end for locking oil circuit is connected to the guide end of a gear shift guiding valve wherein, and the other end is connected to the spring in another gear shift guiding valve
End.
2. gear box hydraulic control system according to claim 1, it is characterised in that：The oil supply subsystem includes difference
Be connected to the mechanical pump and electronic pump of the fuel tank, the mechanical pump and electronic pump selectively hydraulic oil is exported from fuel tank to
It is equipped with check valve on the hydraulic oil output end of working connection, the mechanical pump and electronic pump, strainer is equipped on input terminal.
3. gear box hydraulic control system according to claim 2, it is characterised in that：The working connection is equipped with a safety
Pressure reducing valve, on the oil circuit between the fuel tank and main oil pressure control valve.
4. gear box hydraulic control system according to any one of claims 1 to 3, it is characterised in that：Gearshift control
System includes
The one group of selector fork driven by the hydraulic oil, the selector fork by synchronizer for selectively with gear
Gear synchronous forms gear, and the shifting gear includes seven forward gears and a reversing shelves gear, odd number shelves gear
It is arranged on same root odd number shelves output shaft, even number shelves gear and reversing shelves gear are arranged in another even gear output shaft
On,
The gear shift guiding valve equal with the selector fork quantity and the solenoid valve for controlling each gear shift guiding valve, same root are defeated
Shaft is equipped with gear hydraulic interlock structure；
Respectively by the hydraulic oil in working connection be selectively input to the first gear shift working connection in the plunger shaft of selector fork and
Second gear shift working connection；
Oil circuit change-over pilot valve for switching the first gear shift working connection and the second gear shift working connection.
5. gear box hydraulic control system according to claim 1, it is characterised in that：It is slided by guide's oil pressure cntrol
It is formed by the hydraulic oil with steady pressure after valve, the guide of each gear shift guiding valve is connected to by the guide's oil circuit
End is equipped with strainer and throttle orifice between the guide's oil circuit and the guide end of gear shift guiding valve.
6. gear box hydraulic control system according to claim 5, it is characterised in that：The guide of the oil circuit change-over pilot valve
Oil circuit passes through a solenoid valve control；The oil circuit change-over pilot valve is connected with a counterbalance valve.
7. gear box hydraulic control system according to any one of claims 1 to 3, it is characterised in that：The clutch control
Subsystem includes,
First clutch control valve and second clutch control valve, be separately positioned on by the working connection lead to first clutch and
On the fluid pressure line of second clutch,
The accumulator of output end in the first clutch control valve and second clutch control valve is accordingly set respectively.
8. gear box hydraulic control system according to claim 7, it is characterised in that：The first clutch control valve tool
There are guide end and spring terminal, the oil circuit of the output end of the first clutch control valve to set backfeed loop, the backfeed loop connects
It passes through between the guide end and spring terminal, the opening diameter of the throttle orifice of the guide end feedback oil circuit is less than the spring terminal
Feed back the opening diameter of the throttle orifice of oil circuit；The oil channel structures of the second clutch control valve are controlled with the first clutch
The oil channel structures of valve are identical.
9. gear box hydraulic control system according to claim 8, it is characterised in that：The first clutch control valve and
The input terminal and output end of second clutch control valve are respectively connected with strainer.
10. gear box hydraulic control system according to claim 9, it is characterised in that：The working connection leads to institute respectively
The fluid pressure line for stating first clutch and second clutch is equipped with pressure sensor, and the pressure sensor setting is described the
The output end of one clutch control valve and second clutch control valve, and close to the work of the first clutch and second clutch
It fills at chamber.
11. gear box hydraulic control system according to any one of claims 1 to 3, it is characterised in that：The lubrication control
Subsystem, including
The lubricant passage way exported from the main oil pressure control valve,
It is connected to the oil cooler and pressure filter of the lubricant passage way, and the lubrication exported from the oil cooler and pressure filter
Oil circuit, the lubrication oil circuit are divided into two-way, are respectively used to clutch lubrication and gearbox inner bearing lubrication；
The lubrication oil circuit for gearbox inner bearing lubrication is divided into two-way, respectively axis lubrication oil circuit and bearing
Lubrication oil circuit,
The lubrication oil circuit for clutch lubrication is by forming clutch lubrication cooling after a lubrication flow control valve
Oil circuit, the lubrication flow control valve control the size of signal control valve electromagnetic part electric current to adjust by gear box control unit
Valve openings of sizes, by one residual stress control valve of oil circuit connection, the remnants are answered the output end of the lubrication flow control valve
Force control valve includes a guide end and a spring terminal with residual stress control valve spring, is located at the residual stress control
The both sides of valve processed, the guide end of the residual stress control valve are connected to the lubrication oil circuit, the lubrication oil circuit
Also by the residual stress control valve and a draining oil communication, the draining oil circuit output end leads to the fuel tank, described
The output end of lubrication flow control valve is connected to the spring terminal of the residual stress control valve.
12. gear box hydraulic control system according to claim 11, it is characterised in that：The lubrication flow control valve
Front and rear sides are equipped with a strainer, are front side strainer and rear side strainer, the output end of the lubrication flow control valve and institute respectively
The oil circuit connection point between residual stress control valve is stated between the rear side strainer and clutch.
13. gear box hydraulic control system according to claim 12, it is characterised in that：The lubrication flow control valve
Oil circuit between output end and residual stress control valve spring end is equipped with throttle orifice, the elder generation of the residual stress control valve
It leads and is equipped with throttle orifice between end and the lubrication oil circuit.
14. gear box hydraulic control system according to claim 13, it is characterised in that：The lubricant passage way is equipped with one
The hydraulic oil of flow control valve, the lubricant passage way output is divided into two-way after the flow control valve, wherein hydraulic pressure all the way
Oil makes spool move to left after the dynamic flow control valve of throttle orifice pusher overcomes the spring force of flow control valve spring, the second road hydraulic oil
It is divided into after throttle orifice as two-way, the first via reaches the spring terminal of the flow control valve after throttle orifice, with spring one
Working makes the spool of the flow control valve move to right, and to form a dynamic equilibrium with the pilot pressure on right side, the second road is defeated
The hydraulic oil for providing steady pressure and flow, into measured lubrication oil circuit, the hydraulic oil of the measured lubrication oil circuit enters institute
State oil cooler.
15. gear box hydraulic control system according to claim 14, it is characterised in that：The inlet and outlet of fuel channel of the pressure filter
A upper check valve in parallel.
16. gear box hydraulic control system according to claim 15, it is characterised in that：The measured lubrication oil circuit has
One branch, branch road be equipped with one under case of by-pass valve effect normal off by-passing valve, the branch with pass through the oil cooling
The oil circuit of device is in parallel, and the by-passing valve has a guide end, the guide end and the measured lubrication oil communication.
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| CN201710373562.4A CN107044540B (en) | 2017-05-24 | 2017-05-24 | Gear box hydraulic control system |
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| CN108050245B (en) * | 2017-12-29 | 2019-07-19 | 科力远混合动力技术有限公司 | Hybrid power gearbox hydraulic control system |
| CN110040083B (en) * | 2018-01-16 | 2021-03-26 | 宝沃汽车（中国）有限公司 | Clutch oil state detection method and device, cloud server and vehicle |
| CN110332257B (en) * | 2019-07-29 | 2020-07-03 | 北京航空航天大学 | Clutch pressure hysteresis control optimization method and device |
| CN111207207B (en) * | 2020-01-03 | 2021-05-04 | 博格华纳联合传动***有限公司 | Current control composite switch valve |
| CN112539230A (en) * | 2020-11-26 | 2021-03-23 | 江苏新能源汽车研究院有限公司 | Single-gear box hydraulic control method, system and device |
| CN112984005B (en) * | 2021-03-31 | 2022-03-29 | 安徽江淮汽车集团股份有限公司 | Wet clutch hydraulic control system and automatic gearbox |
| CN114017450B (en) * | 2021-10-29 | 2023-09-12 | 中国第一汽车股份有限公司 | Hydraulic control device of automatic transmission |
| CN114352659B (en) * | 2021-11-09 | 2023-07-21 | 苏州瑞赛精密工具有限公司 | Double-pump hydraulic system of 2AT transmission |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| DE102009005756A1 (en) * | 2009-01-23 | 2010-07-29 | Daimler Ag | Control device for an automated change-speed gearbox |
| CN201561118U (en) * | 2009-12-08 | 2010-08-25 | 重庆青山工业有限责任公司 | Dual-clutch gearbox gear shifting hydraulic control loop |
| EP3396213B1 (en) * | 2010-07-21 | 2019-10-30 | hofer mechatronik GmbH | Method for operating transmission hydraulics with a hydraulic control unit |
| CN102168754B (en) * | 2011-04-08 | 2013-10-30 | 浙江万里扬变速器股份有限公司 | Hydraulic control system for wet-type double-clutch automatic transmission |
| CN203743410U (en) * | 2013-11-29 | 2014-07-30 | 长城汽车股份有限公司 | Double-clutch automatic transmission hydraulic control system and corresponding transmission and automobile |
| CN106321805A (en) * | 2015-06-26 | 2017-01-11 | 上海汽车集团股份有限公司 | A hydraulic control system of a wet-type double-clutch gearbox, a gearbox, a TCU and an automobile |
| CN206874809U (en) * | 2017-05-24 | 2018-01-12 | 捷孚传动科技有限公司 | Gear box hydraulic control system |
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