CN106321805A - A hydraulic control system of a wet-type double-clutch gearbox, a gearbox, a TCU and an automobile - Google Patents
A hydraulic control system of a wet-type double-clutch gearbox, a gearbox, a TCU and an automobile Download PDFInfo
- Publication number
- CN106321805A CN106321805A CN201510362821.4A CN201510362821A CN106321805A CN 106321805 A CN106321805 A CN 106321805A CN 201510362821 A CN201510362821 A CN 201510362821A CN 106321805 A CN106321805 A CN 106321805A
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- Prior art keywords
- valve
- clutch
- loop
- direct action
- oil
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Classifications
-
- 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
- F16H61/02—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 characterised by the signals used
- F16H61/0202—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 characterised by the signals used the signals being electric
- F16H61/0204—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 characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
- F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves
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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
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated 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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/36—Inputs being a function of speed
- F16H59/38—Inputs being a function of speed of gearing elements
- F16H59/42—Input shaft speed
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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
- F16H61/02—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 characterised by the signals used
- F16H61/0202—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 characterised by the signals used the signals being electric
- F16H61/0251—Elements specially adapted for electric control units, e.g. valves for converting electrical signals to fluid signals
Abstract
The invention provides a hydraulic control system of a wet-type double-clutch gearbox, a gearbox, a TCU and an automobile. The hydraulic control system of a wet-type double-clutch gearbox comprises an oil tank used for storing hydraulic oil, a first oil pump and a second oil pump, wherein the first oil pump sucks oil from the oil tank, is driven by an engine and provides hydraulic oil of first displacement, and the second oil pump sucks oil from the oil tank, is driven by a motor and provides hydraulic oil of a second displacement. When the rotating speed of the engine is higher than a rotating speed set value, the engine drives the first oil pump to extract hydraulic oil required by a lubricating oil cooling loop, a clutch control loop and a shifting fork control loop from the oil tank; when the rotating speed of the engine is less than the rotating speed set value, the motor drives the second oil pump to extract hydraulic oil required by the lubricating oil cooling loop, the clutch control loop and the shifting fork control loop from the oil tank.
Description
Technical field
The present invention relates to change speed gear box technical field, be specifically related to the hydraulic pressure of a kind of wet-type dual-clutch change speed gear box
Control system, change speed gear box, TCU and automobile.
Background technology
Existing wet-type double-clutch automatic speed-change device technical scheme all uses hydraulic control system handle from
Clutch separating and combining and shelves gear switch.With reference to Fig. 1, this hydraulic control system typically by fuel tank, oil pump,
The part composition such as electromotor, lubricating oil cooling circuit, fork controls loop and Clutch Control loop.
Particularly, electromotor drives oil pump draw oil from fuel tank, after hydraulic oil flows out from fuel tank
Three loops can be flowed to: lubricating oil cooling circuit, for providing cooling and the hydraulic pressure of lubrication for clutch
Oil；Clutch Control loop, is used for separating or engaging clutch；Fork controls loop, is used for controlling to become
Speed gear box lifting.
With reference to Fig. 1, wherein, Clutch Control loop includes: odd number shelves Clutch Control loop and even gear
Clutch Control loop；On odd number shelves Clutch Control loop, hydraulic oil after fuel tank is extracted out by oil pump,
Flow to proportional pressure valve from pilot valve and flow to odd number shelves Clutch Control loop again, for odd number shelves clutch control
Hydraulic oil required for the offer of loop processed；Equally, on even gear Clutch Control loop, hydraulic oil from
After fuel tank is extracted out by oil pump, flow to proportional pressure valve from pilot valve and flow to even gear Clutch Control loop again,
Hydraulic oil required for providing for even gear Clutch Control loop.
For fork controls loop, hydraulic oil also can flow to ratio pressure from pilot valve after fuel tank is extracted out by oil pump
Power valve flows to fork controls loop again, for the hydraulic oil required for the offer of fork controls loop.Wherein, dial
Fork controls loop and includes: odd number shelves fork controls loop and even gear fork controls loop；No matter odd number shelves
Fork controls loop or even gear fork controls loop, each loop all can be provided with shift fork executor,
And shift fork executor is the double acting homalographic piston cylinder of band sealing function, the most described shift fork executor has
The function of way moving shift fork, then the way moving of piston cylinder, is required to necessarily in the both sides of piston cylinder
The hydraulic oil of pressure promotes shift fork to move.
Therefore, with reference to Fig. 1, on odd number shelves fork controls loop or even gear fork controls loop: guide
One group of pilot valve connected the most in parallel and proportional pressure valve after valve and proportional pressure valve series connection；That is, at odd number
Shelves fork controls loop on, hydraulic oil can distinguish from which one group series connection pilot valve and proportional pressure valve and
Pilot valve and pressure valve that another group is in series flow to odd number shelves fork controls loop；Equally, at even gear
On fork controls loop, hydraulic oil can distinguish the pilot valve of one group of series connection from which and proportional pressure valve with another
One group of pilot valve being in series and pressure valve flow to even gear fork controls loop.
Visible, in prior art, hydraulic control system has a following features:
1) oil pump of extract force feed is driven by the engine；
2) hydraulic oil all can flow to proportional pressure valve from pilot valve and flow to Clutch Control loop or shift fork again
Control loop.
But, vehicle is in idling or when running at a low speed, and engine speed is relatively low, the hydraulic pressure that mechanical oil pump is provided
Shortage of oil is to meet the liquid required for lubricating oil cooling circuit, Clutch Control loop or fork controls loop
Force feed, shift fork gear shift can be the most smooth.
Additionally, at electromotor from turning not to starting to rotate this process, oil pump can not extract clutch from fuel tank
Device controls the hydraulic oil required for loop or fork controls loop；To carry out shift fork gear shift, the most pending
Motivation start after, electromotor could drive oil pump extract lubricating oil cooling circuit, Clutch Control loop or
Hydraulic oil required for fork controls loop, carries out shift fork gear shift so that shift fork gear shift can not quickly be carried out.
Further, hydraulic oil, after fuel tank is extracted, all flows to proportional pressure valve from pilot valve and flows to clutch again
Device controls loop or fork controls loop；First, pilot valve oil leakage quantity is relatively big, brings the waste of oil；
Additionally, use pilot valve and proportional pressure valve to control to enter Clutch Control loop or fork controls loop
Hydraulic oil, such secondary valve control mode efficiency is low, it is impossible to be quickly Clutch Control loop or group
Fork controls the hydraulic oil needed for loop provides；Simultaneously for fork controls loop, hydraulic oil can respectively from
Pilot valve and pressure valve that the pilot valve of one of which series connection and proportional pressure valve are in series with another group flow to
Fork controls loop；For Clutch Control loop, hydraulic oil flows to proportional pressure valve again by pilot valve
Flow to Clutch Control loop；This causes the valve used on fork controls loop and Clutch Control loop
Quantity more.
Summary of the invention
The first problem that the present invention solves is: the hydraulic pressure control of wet-type dual-clutch change speed gear box in prior art
System processed needs by engine-driven oil pump, when vehicle is in idling or when running at a low speed, and electromotor
Rotating speed is relatively low, and the hydraulic oil that mechanical oil pump is provided is insufficient for lubricating oil cooling circuit, clutch control
Hydraulic oil required for loop processed or fork controls loop, shift fork gear shift can be the most smooth.
In addition the Second Problem that the present invention solves is: at electromotor from turning not to starting to rotate this process,
Shift fork gear shift can not quickly be carried out.
The 3rd problem that the present invention solves is: hydraulic oil, after fuel tank is extracted, all flows to from pilot valve
Proportional pressure valve flows to Clutch Control loop or fork controls loop again；Pilot valve oil leakage quantity is relatively big,
Bring the waste of oil；Meanwhile, the secondary valve using pilot valve and proportional pressure valve controls to enter clutch control
The hydraulic pressure oil mass in loop processed or fork controls loop: can not be quickly Clutch Control loop or shift fork control
Hydraulic oil needed for the offer of loop processed；And, the quantity of the valve that fork controls loop is used is more.
For solving the problems referred to above, the present invention provides the hydraulic control system of a kind of wet-type dual-clutch change speed gear box,
Including:
For storing the fuel tank of hydraulic oil；
The first oil pump of oil suction from described fuel tank, described first oil pump is driven by electromotor, it is provided that the
The hydraulic oil of one discharge capacity；
The second oil pump of oil suction from described fuel tank, described second oil pump is driven by motor, it is provided that second
The hydraulic oil of discharge capacity；
Described first discharge capacity is more than described second discharge capacity；
Lubricating oil cooling circuit, for providing cooling and the hydraulic oil of lubrication for clutch；
Clutch Control loop, is used for separating or engaging clutch；
Fork controls loop, is used for controlling gearbox-gear lifting；
When described engine speed higher than speed setting value time, described electromotor drive described first oil pump from
Described fuel tank extracts described lubricating oil cooling circuit, described Clutch Control loop, described fork controls
Hydraulic oil needed for loop；
When described engine speed less than speed setting value time, by described motor drive described second oil pump from
Described fuel tank extracts described lubricating oil cooling circuit, described Clutch Control loop, described fork controls
Hydraulic oil needed for loop.
Optionally, the hydraulic oil flowed out from described fuel tank passes through the first direct action type proportional pressure valve being in series
With flow to described fork controls loop after direct action type proportional flow valve.
Optionally, described hydraulic oil commutates through at least one after described direct action type proportional flow valve flows out
Valve flows to described fork controls loop；
Also include: for controlling the switch electromagnetic valve that described reversal valve is turned on and off.
Optionally, the hydraulic oil flowed out from described fuel tank flows to described clutch through direct action type proportional pressure valve
Device controls loop.
Optionally, described fork controls loop includes: odd number shelves fork controls loop and even gear shift fork control
Loop processed；
Described odd number shelves fork controls loop, including:
Odd number shelves shift fork executor；
Described hydraulic oil flows to after the 4th direct action type proportional pressure valve and the second direct action type proportional flow valve
Described odd number shelves shift fork executor；
Described even gear fork controls loop, including:
Even gear shift fork executor；
Described hydraulic oil flows to after the 5th direct action type proportional pressure valve and the 3rd direct action type proportional flow valve
Described even gear shift fork executor.
Optionally, described fork controls loop includes: odd number shelves fork controls loop and even gear shift fork control
Loop processed；
Described odd number shelves fork controls loop, including: odd number shelves shift fork executor；Described even gear shift fork
Control loop, including: even gear shift fork executor；
Described hydraulic oil flows to institute through at least one reversal valve after described direct action type proportional flow valve flows out
State odd number shelves shift fork executor or described even gear shift fork executor.
Optionally, described reversal valve includes the first reversal valve and the second reversal valve being serially connected；Described open
Pass electromagnetic valve includes: control the first switch electromagnetic valve that described first reversal valve is turned on and off；Control institute
State the second switch electromagnetic valve that the second reversal valve is turned on and off.
Optionally, described wet-type dual-clutch change speed gear box is 7 speed wet-type dual-clutch change speed gear boxes；Described
One Direct Action Type proportional pressure valve is two-position three way direct action type proportional pressure valve；Described direct action type proportional flow valve
For 3-position 4-way direct action type proportional flow valve；Described first reversal valve is two ten six-way transfer valves；Described
Second reversal valve is two eight and leads to reversal valve.
Optionally, described fork controls loop includes: odd number shelves fork controls loop and even gear shift fork control
Loop processed；
Described odd number shelves fork controls loop, including: odd number shelves shift fork executor；
Described hydraulic oil flows to described odd number shelves through reversal valve after described direct action type proportional flow valve flows out
Shift fork executor；
Described even gear fork controls loop, including: even gear shift fork executor；
Described hydraulic oil flows to described even gear through reversal valve after described direct action type proportional flow valve flows out
Shift fork executor.
Optionally, described Clutch Control loop includes:
For separating or engage the odd number shelves clutch actuator of odd number shelves clutch；
For separating or engage the even gear clutch actuator of even gear clutch；
Described direct action type proportional pressure valve includes: the second direct action type proportional pressure valve being in parallel and the 3rd straight
Dynamic formula proportional pressure valve；
Described hydraulic oil flows to described odd number shelves clutch from described second direct action type proportional pressure valve and performs
Device；
Described hydraulic oil flows to described even gear clutch from described 3rd direct action type proportional pressure valve and performs
Device.
Optionally, described electromotor is configured for communicating with TCU with described motor；
When described TCU receives rotating speed corresponding to the tach signal of described electromotor less than speed setting value
Time, send open command to described motor；
When described TCU receives rotating speed corresponding to the tach signal of described electromotor higher than speed setting value
Time, send out code to described motor.
The present invention also provides for a kind of for joining with the hydraulic control system of described wet-type dual-clutch change speed gear box
The TCU closed, for receiving the tach signal of described electromotor, according to the tach signal received to described
Motor sends instruction；
When described TCU receives rotating speed corresponding to the tach signal of described electromotor less than speed setting value
Time, send open command to described motor；
When described TCU receives rotating speed corresponding to the tach signal of described electromotor higher than speed setting value
Time, send out code to described motor.
Optionally, including:
Memory element, for storing the speed setting value of electromotor；
Comparing unit, is used for receiving described tach signal, by rotating speed corresponding for described tach signal with described
Speed setting value relatively and sends comparative result；
Indicating member, is used for receiving described comparative result, sends to described motor according to described comparative result
Instruction；When comparative result be rotating speed that described tach signal is corresponding less than described speed setting value time, described
Rotating speed is low speed or 0, and described instruction is described open command；When comparative result is that described tach signal is corresponding
Tachometer value higher than described speed setting value time, described rotating speed be high speed, described instruction is that described closedown refers to
Order.
The present invention also provides for a kind of change speed gear box, including: the wet-type dual-clutch speed change described in any of the above-described item
The hydraulic control system of case.
The present invention also provides for a kind of automobile, including described change speed gear box.
Optionally, the TCU described in any of the above-described item is also included.
Compared with prior art, technical scheme has the advantage that
The hydraulic control system of wet-type dual-clutch change speed gear box of the present invention includes the first oil pump and the second oil
Pump, the first oil pump drives oil suction from fuel tank by electromotor, for lubricating oil cooling circuit, clutch control
Loop processed, fork controls loop provide the hydraulic oil of the first discharge capacity；Second oil pump is driven from oil by motor
Oil suction in case, provides second row for lubricating oil cooling circuit, Clutch Control loop, fork controls loop
The hydraulic oil of amount, wherein the first discharge capacity is more than the second discharge capacity.And in prior art, extract hydraulic pressure from fuel tank
The oil pump only one of which of oil, and be to be driven by electromotor.Use the hydraulic control system of the present invention, when
Vehicle is in normal driving process, and engine speed is higher than speed setting value, and described rotating speed is at a high speed, logical
Crossing electromotor and drive the first oil pump, electromotor drives described first oil pump to extract described profit from described fuel tank
Hydraulic oil needed for lubricating oil cooling circuit, described Clutch Control loop, described fork controls loop；When
Vehicle is in idling or when running at a low speed, and engine speed is less than speed setting value, and described rotating speed is low speed,
Now, by described motor drive described second oil pump extract from described fuel tank described lubricating oil cooling circuit,
Hydraulic oil needed for described Clutch Control loop, described fork controls loop.The present invention by arrange by
Engine-driven first oil pump and by motor-driven second oil pump, solves first skill of the present invention
Art problem.
Further, at electromotor from turning not to starting to rotate this process, in prior art, need to wait
Shift fork gear shift just can be carried out after engine start；The present invention, when carrying out shift fork gear shift, engine speed
It is 0, now can be extracted lubricating oil cooling circuit, clutch control from fuel tank by motor-driven second oil pump
Hydraulic oil required for loop processed or fork controls loop, and without waiting for engine start, solve this
Second technical problem of invention.
Further, in the present invention, the hydraulic oil flowed out from described fuel tank passes through the first Direct Action Type being in series
Described fork controls loop is flowed to after proportional pressure valve and direct action type proportional flow valve；Flow out from described fuel tank
Hydraulic oil flow to described Clutch Control loop through direct action type proportional pressure valve；That is, in fork controls
The first direct action type proportional pressure valve and direct action type proportional flow valve is have employed on loop；Return in Clutch Control
Road have employed direct action type proportional pressure valve；The present invention does not use pilot valve, uses direct action type proportional pressure
Power valve and direct action type proportional flow valve, oil leakage quantity is few.
And, on Clutch Control loop, it being provided only with a direct action type proportional pressure valve, the quantity of valve subtracts
Few, meanwhile, use direct action type proportional pressure valve, quickly can provide required for Clutch Control loop
Hydraulic oil；Equally, on fork controls loop, by arranging direct action type proportional pressure valve and Direct Action Type
Proportional flow control valve, compared to prior art, uses one group of pilot valve connected and proportional pressure valve the most in parallel
Pilot valve that another group is in series and pressure valve, the quantity of valve decreases, meanwhile, only by one group of string
First direct action type proportional pressure valve of connection and direct action type proportional flow valve, it is possible to make hydraulic oil flow to dialling
Fork controls loop, hydraulic oil without the pilot valve of respectively one group of series connection the most from which again and proportional pressure valve with another
One group of pilot valve being in series and pressure valve flow to fork controls loop；Can quickly cool down for lubricating oil
Hydraulic oil needed for loop, Clutch Control loop or the offer of fork controls loop；Solve the present invention's
3rd technical problem.
Additionally, in fork controls loop, hydraulic oil after direct action type proportional flow valve flows out through at least
One reversal valve flows to fork controls loop；Reversal valve can be set according to the gear of automobile, such as when for 7
During the double clutch gearbox of speed wet type, two reversal valves can be set；Being set to of each valve: the first Direct Action Type
Proportional pressure valve is two-position three way direct action type proportional pressure valve；Direct action type proportional flow valve is that 3-position 4-way is straight
Dynamic formula proportional flow control valve；First reversal valve is two ten six-way transfer valves；Second reversal valve is two eight and leads to
Reversal valve.
So, hydraulic oil flows successively through two-position three way direct action type proportional pressure valve, 3-position 4-way Direct Action Type ratio
Example flow valve, two eight lead to reversal valve, two ten six-way transfer valves after flow to odd number shelves fork controls loop
Or even gear fork controls loop；That is, owing to being provided with the first reversal valve and the second reversal valve, odd number shelves
Fork controls loop and even gear fork controls loop can share one group of direct action type proportional pressure valve being in series
With direct action type proportional flow valve, further reduce the quantity of valve.
Accompanying drawing explanation
Fig. 1 is the module frame chart of the hydraulic control system of the double clutch gearbox of prior art wet type；
Fig. 2 is the module frame chart one of the hydraulic control system of the double clutch gearbox of embodiment of the present invention wet type；
Fig. 3 is the module frame chart two of the hydraulic control system of the double clutch gearbox of embodiment of the present invention wet type；
Fig. 4 is the structural representation of the hydraulic control system of embodiment of the present invention wet-type dual-clutch change speed gear box.
Detailed description of the invention
Owing to, in prior art, the oil pump of extract force feed is driven by the engine, works as automobile engine
Rotating speed is relatively low, even when rotating speed is 0, oil pump just can not extract from fuel tank lubricating oil cooling circuit,
Hydraulic oil needed for Clutch Control loop, fork controls loop.
To this end, the present invention arranges two oil pumps in hydraulic control system, wherein, the first oil pump is by sending out
Motivation drives oil suction from fuel tank, returns for lubricating oil cooling circuit, Clutch Control loop, fork controls
Road provides the hydraulic oil of the first discharge capacity；Second oil pump drives oil suction from fuel tank by motor, for lubricating oil
Cooling circuit, Clutch Control loop, fork controls loop provide the hydraulic oil of the second discharge capacity, Qi Zhong
One discharge capacity is more than the second discharge capacity, the hydraulic oil of the i.e. first oil pump extraction huge discharge, the second oil pump extraction float
The hydraulic oil of amount.When vehicle is in normal driving process, engine speed is at a high speed, and engine speed is high
In speed setting value, driving the first oil pump by electromotor, electromotor drives described first oil pump from described
Fuel tank extracts described lubricating oil cooling circuit, described Clutch Control loop, described fork controls loop
Required hydraulic oil；When vehicle is in idling or when running at a low speed, and engine speed is less than speed setting value,
Described rotating speed is low speed even 0, now, described motor drives described second oil pump from described fuel tank
Needed for extracting described lubricating oil cooling circuit, described Clutch Control loop, described fork controls loop
Hydraulic oil.
Additionally, in prior art, hydraulic oil, after fuel tank is extracted, all flows to ratio pressure from pilot valve
Valve flows to Clutch Control loop or fork controls loop again；First, pilot valve oil leakage quantity is relatively big, band
Carry out oily waste；Meanwhile, pilot valve and proportional pressure valve is used to control enter Clutch Control loop or dial
Fork controls the hydraulic oil in loop, and such secondary valve control mode efficiency is low, it is impossible to be quickly clutch
Hydraulic oil needed for loop or the offer of fork controls loop is provided；Additionally, fork controls loop and clutch
The quantity of the valve used on control loop is more.
To this end, the present invention have employed direct action type proportional pressure valve and direct action type proportional on fork controls loop
Flow valve；Direct action type proportional pressure valve is have employed in Clutch Control loop；The present invention does not use elder generation
Pilot valve, uses direct action type proportional pressure valve and direct action type proportional flow valve, and oil leakage quantity is few.It addition,
On Clutch Control loop, being provided only with a direct action type proportional pressure valve, the quantity of valve decreases, meanwhile,
Use direct action type proportional pressure valve, the hydraulic oil needed for can quickly providing for Clutch Control loop；With
Sample, on fork controls loop, only by the first direct action type proportional pressure valve and Direct Action Type of one group of series connection
Proportional flow control valve, it is possible to making hydraulic oil flow to fork controls loop, hydraulic oil is without the most respectively from it
In the pilot valve of one group of series connection and the pilot valve that is in series with another group of proportional pressure valve and pressure valve flow to group
Fork controls loop, it is possible to quickly return for lubricating oil cooling circuit, Clutch Control loop or fork controls
Road provide needed for hydraulic oil, and the quantity of valve decreases.
Understandable, below in conjunction with the accompanying drawings for enabling the above-mentioned purpose of the present invention, feature and advantage to become apparent from
The specific embodiment of the present invention is described in detail.
With reference to Fig. 2, the hydraulic control system of a kind of wet-type dual-clutch change speed gear box of the embodiment of the present invention, bag
Including the first oil pump 15 and the second oil pump 13, wherein, the first oil pump 15 is driven from fuel tank by electromotor 16
Oil suction in 10, for lubricating oil cooling circuit 2, Clutch Control loop (includes odd number shelves Clutch Control
Loop 31 and even gear Clutch Control loop 32), fork controls loop (include odd number shelves fork controls
Loop 33 and even gear fork controls loop 34) hydraulic oil of the first discharge capacity is provided；Second oil pump 13 leads to
Cross motor 14 and drive oil suction from fuel tank 10, for lubricating oil cooling circuit 2, Clutch Control loop (bag
Include odd number shelves Clutch Control loop 31 and even gear Clutch Control loop 32), fork controls loop (bag
Include odd number shelves fork controls loop 33 and even gear fork controls loop 34) hydraulic oil of the second discharge capacity is provided.
And in prior art, from the oil pump only one of which of fuel tank extract force feed, and be to be driven by electromotor
Dynamic.Use the hydraulic control system of the present invention, when vehicle is in normal driving process, electromotor 16 rotating speed
During higher than speed setting value, described rotating speed is that electromotor 16 drives the first oil pump 15 from described oil at a high speed
In case 10, the hydraulic oil of extraction disclosure satisfy that lubricating oil cooling circuit 2, Clutch Control loop (include strange
Several grades of Clutch Control loops 31 and even gear Clutch Control loop 32), fork controls loop (includes
Odd number shelves fork controls loop 33 and even gear fork controls loop 34) needed for hydraulic oil；But, work as car
In idling or when running at a low speed, electromotor 16 rotating speed is less than speed setting value, and described rotating speed is low speed,
Now, the hydraulic oil that electromotor 16 drives the first oil pump 15 to be extracted from fuel tank 10 can not meet lubrication
Oil cooling loop 2, Clutch Control loop (include odd number shelves Clutch Control loop 31 and even gear from
Clutch control loop 32), fork controls loop (include that odd number shelves fork controls loop 33 and even gear are dialled
Fork control loop 34) needed for hydraulic oil；So, motor 14 just drives the second oil pump 13 from fuel tank 10
Middle extraction lubricating oil cooling circuit 2, described Clutch Control loop (include odd number shelves Clutch Control loop
31 and even gear Clutch Control loop 32), fork controls loop (include odd number shelves fork controls loop
33 and even gear fork controls loop 34) needed for hydraulic oil.The embodiment of the present invention is by arranging by starting
The first oil pump 15 that machine 16 drives and the second oil pump 13 of being driven by motor 14, solve the of the present invention
One technical problem.
With continued reference to Fig. 2, vehicle can stop when running into red light, and now electromotor can stop operating；Hot
When lamp becomes green light, electromotor can restart to rotate, and electromotor is from turning not to starting to rotate this process
It is referred to as automobile start and stop；In prior art, after needing to wait engine start, just can carry out shift fork gear shift；This
Invention, when carrying out shift fork gear shift, motor 14 the second oil pump 13 driven can extract from fuel tank 10
Lubricating oil cooling circuit 2, Clutch Control loop (include odd number shelves Clutch Control loop 31 and even number
Shelves Clutch Control loop 32) or fork controls loop (include odd number shelves fork controls loop 33 and even number
Shelves fork controls loop 34) required for hydraulic oil, and without waiting engine start again, the second oil pump
13 quickly (can include odd number shelves clutch control for lubricating oil cooling circuit 2, Clutch Control loop
Loop 31 processed and even gear Clutch Control loop 32) or fork controls loop (include odd number shelves shift fork control
Loop 33 processed and even gear fork controls loop 34) extraction required for hydraulic oil, shift fork gear shift can be fast
Speed is carried out, and solves second technical problem of the present invention.
The hydraulic oil extracted from fuel tank 10 with continued reference to Fig. 2, the first oil pump 15 or the second oil pump 13 is successively
Pass through again after the first direct action type proportional pressure valve 320 being in series and direct action type proportional flow valve 321
Reversal valve 400 flows to fork controls loop and (includes odd number shelves fork controls loop 33 and even gear shift fork control
Loop 34 processed)；The hydraulic oil flowed out from fuel tank 10 flows to very through the second direct action type proportional pressure valve 310
Several grades of Clutch Control loops 31, flow to even gear clutch through the 3rd direct action type proportional pressure valve 314
Control loop 32；That is, (include that odd number shelves fork controls loop 33 and even gear are dialled in fork controls loop
Fork control loop 34) on have employed the first direct action type proportional pressure valve 320, the direct action type proportional being in series
Flow valve 321 and reversal valve 400；(odd number shelves Clutch Control loop is included in Clutch Control loop
31 and even gear Clutch Control loop 32) in have employed the second direct action type proportional pressure valve 310 and the 3rd
Direct action type proportional pressure valve 314；The embodiment of the present invention does not use pilot valve, then oil leakage quantity reduces.
Meanwhile, on odd number shelves Clutch Control loop 31, it is provided only with a second direct action type proportional pressure
Valve 310；On even gear Clutch Control loop 32, also it is provided only with a 3rd direct action type proportional pressure
Valve 314；Without as prior art: hydraulic oil flows through proportional pressure valve from pilot valve and flows to clutch again
Controlling loop, it is to avoid secondary valve controls, directly using direct action type proportional pressure valve can be quickly clutch
Control circuit supplies hydraulic oil；Equally, on fork controls loop, make owing to being provided with reversal valve 400
Obtain odd number shelves fork controls loop 33 and even gear fork controls loop 34 shares one group of first be in series
Direct action type proportional pressure valve 320 and direct action type proportional flow valve 321.
Compared to prior art, use one group of pilot valve connected and proportional pressure valve another group phase in parallel again
The pilot valve of series connection and pressure valve, the quantity of valve decreases, meanwhile, only by the first of one group of series connection
Direct action type proportional pressure valve and direct action type proportional flow valve, it is possible to hydraulic oil flow is returned to fork controls
Road, hydraulic oil is gone here and there with another group with proportional pressure valve mutually without the pilot valve of the most from which one group of series connection
Pilot valve and the pressure valve of connection flow to fork controls loop；Can be quickly lubricating oil cooling circuit, from
Clutch controls the hydraulic oil needed for loop or the offer of fork controls loop；Solve the 3rd skill of the present invention
Art problem.The number of the reversal valve 400 in the present embodiment does not limits, and sets commutation according to automobile gears
The number of valve 400.
In the present embodiment, with reference to Fig. 2, owing to being provided with reversal valve, reversal valve has multiple oil-out, can
So that odd number shelves fork controls loop 33 and even gear fork controls loop 34 share one group of first direct acting
Formula proportional pressure valve 320, direct action type proportional flow valve 321；In other embodiments, can not use and change
To valve, with reference to Fig. 3, odd number shelves fork controls loop 33 arranges the 4th Direct Action Type ratio of one group of series connection
Example pressure valve 320a and the second direct action type proportional flow valve 321a；On even gear fork controls loop 34
It is also provided with the 5th direct action type proportional pressure valve 320b and the 3rd direct action type proportional flow valve of one group of series connection
321b, does not uses pilot valve yet in the present embodiment, hydraulic oil passes through direct action type proportional pressure valve and Direct Action Type
Proportional flow control valve also is able to quickly flow to fork controls loop.
It should be noted that, electromotor 16 and motor 14 in the present embodiment are configured for and TCU
(Transmission Control Unit, i.e. automatic gear-box control unit) communicates；When described TCU connects
When receiving rotating speed corresponding to the tach signal of electromotor 16 less than speed setting value, described rotating speed be low speed or
When 0, send open command to motor 14；When described TCU receives the tach signal pair of electromotor 16
When the rotating speed answered is higher than speed setting value, when described rotating speed is high speed, send out code to motor 14.
That is, motor 14 be turned on and off controlled according to the rotating speed of electromotor 16 by TCU, described rotating speed sets
Definite value does not limits.
In order to spirit and the essence of the present invention are expanded on further, below in association with Fig. 2 and Fig. 4, to this
Bright it is described in detail.
The present embodiment is as a example by the hydraulic control system of the 7 double clutch gearboxes of speed wet type, but is not limited to 7 speed
The hydraulic control system of the double clutch gearbox of wet type.7 speed wet-type dual-clutch change speed gear boxes include: odd number shelves (1,
3,5,7 grades), even gear (2,4,6 grades and R shelves).Odd number shelves Clutch Control loop 31 controls
The separation of odd number shelves clutch or joint in change speed gear box, even gear Clutch Control loop 32 controls change speed gear box
The separation of middle even gear clutch or joint；Odd number shelves fork controls loop 33 controls odd number shelves in change speed gear box
The lifting of gear, even gear fork controls loop 34 controls the lifting of even gear gear in change speed gear box.
Above-mentioned odd number shelves Clutch Control loop 31, even gear Clutch Control loop 32, odd number shelves shift fork
The operation controlling loop 33 and even gear fork controls loop 34 is required to certain hydraulic oil；With reference to Fig. 4,
Storing hydraulic oil in fuel tank 10, the temperature of hydraulic oil can not be too low, if temperature is too low, hydraulic oil is more viscous
Thick, it is impossible to ensure clutch and shift fork gear shift action smoothly；Therefore, in fuel tank 10, arrange temperature pass
Sensor 12, monitors the temperature of hydraulic oil in fuel tank 10 by temperature sensor 12, when temperature sensor 12
When monitoring that the temperature of hydraulic oil is too low in fuel tank 10, oil temperature signal can be sent to by temperature sensor 12
It is that fuel tank 10 heats, in preventing fuel tank 10 that gear box control unit TCU, TCU can control heating system
Oil temperature is too low.
With continued reference to Fig. 4, the oil-out of fuel tank 10 arranges oil absorption filter 11；First oil pump 15
The hydraulic oil extracted from fuel tank 10 with the second oil pump 13 is through oil absorption filter 11, oil absorption filter 11
The hydraulic oil extracted is carried out primary filter, the pollutant in trapped fluid force feed, makes hydraulic oil keep clear
Clean, it is to avoid hydraulic oil normally the working because of pollution effect hydraulic control system extracted out from fuel tank 10.
With continued reference to Fig. 4, when electromotor 16 drives the first oil pump 15 after extract force feed from fuel tank 10,
In order to prevent extracted hydraulic oil from refluxing, the hydraulic oil extracted can be flowed out by the first check valve 17；
When motor 14 drives the second oil pump 13 after drawing liquid force feed from fuel tank 10, equally, in order to prevent being extracted
Hydraulic oil backflow, the hydraulic oil extracted can be flowed out by the second check valve 18.
The hydraulic oil flowed out from the first check valve 17 or the second check valve 18 can be divided into two branches, wherein
One branch is: hydraulic oil by high pressure filter 30 enter Clutch Control loop (include odd number shelves from
Clutch controls loop 31 and even gear Clutch Control loop 32) and fork controls loop (include odd number shelves
Fork controls loop 33 and even gear fork controls loop 34)；Another one branch is: hydraulic oil flow to
Lubricating oil cooling circuit 2.
Wherein, hydraulic oil is after the first check valve 17 or the second check valve 18 flow out, described in entering
Having one section of oil circuit before two branches is the working connection of hydraulic control system, and accordingly, lubricating oil cools back
Road and Clutch Control loop and fork controls loop are the auxiliary oil circuit of hydraulic control system.Due to, clutch
Device controls loop and fork controls loop normal job demand high pressure, when not working, Clutch Control loop
High pressure is need not with fork controls loop；Therefore, can be able to be provided for regulating working connection oil in working connection
The pressure valve 21 of pressure value size, main oil way valve 21 can be the electromagnetic valve of Direct Action Type；Guide can also be used
Valve 23 controls the aperture size of pressure valve 21, thus regulates the oil pressure value size of working connection, at working connection
On be additionally provided with guarantee working connection pressure normal working connection relief valve 20.
With continued reference to Fig. 4, from the hydraulic oil of the first oil pump 15 or the extraction of the second oil pump 13 from relief valve 22
Flowing into lubricating oil cooling circuit 2, relief valve 22 ensure that the safe operation of lubricating oil cooling circuit.Liquid
Force feed is divided into two branches after described relief valve 22 flows out, and one of them branch is: by flow solenoid valve
The 26 clutch lubrication oil return lines controlled, hydraulic oil is through described flow solenoid valve 26, by fuel injector 27
Clutch is lubricated, to reduce clutch abrasion.
Wherein, the aperture size of flow solenoid valve 26 is controlled by pilot solenoid valve 28；Meanwhile, at stream
It is additionally provided with electromagnetic valve amortisseur 29, electromagnetic valve amortisseur 29 between amount electromagnetic valve 26 and pilot solenoid valve 28
For controlling and absorb the pressure fluctuation of described lubricating oil cooling circuit 2, prevent hydraulic vibration to described liquid
The impact of pressure control system.
From main safety valve 22 flow out hydraulic oil flow to another branch be to flow to oil cooler 24, oil cooler
Gear and bearing are carried out cooling down radiating treatment by the 24 clutch lubrication oil pipes 25 connecting gear synchronizer.
With continued reference to Fig. 4, the hydraulic oil flowed out from the first check valve 17 or the second check valve 18 passes through high pressure
Filter 30 enter Clutch Control loop (include odd number shelves Clutch Control loop 31 and even gear from
Clutch control loop 32) and fork controls loop (include that odd number shelves fork controls loop 33 and even gear are dialled
Fork controls loop 34).
Wherein, odd number shelves Clutch Control loop 31 includes: for separating or engage odd number shelves clutch
Odd number shelves clutch actuator 311；For regulating the of oil pressure for described odd number shelves clutch actuator 311
Two direct action type proportional pressure valve 310, hydraulic oil from the second direct action type proportional pressure valve 310 flow to odd number shelves from
Clutch executor 311, odd number shelves clutch actuator 311 and the second direct action type proportional pressure valve 310 it
Between connect have the first pressure transducer 312 and the first hydraulic damper 313；Described even gear Clutch Control
Loop 32 includes: for separating or engage the even gear clutch actuator 315 of even gear clutch；With
In regulating the 3rd direct action type proportional pressure valve 314 of oil pressure for described even gear clutch actuator 315, liquid
Force feed flows to even gear clutch actuator 315 from the 3rd direct action type proportional pressure valve 314, even gear from
Connect between clutch executor 315 and the 3rd direct action type proportional pressure valve 314 and have the second pressure transducer 317
With the second hydraulic damper 316.
Described odd number shelves Clutch Control loop 31 is identical with the structure in even gear Clutch Control loop 32,
Therefore, illustrate as example below by way of odd number shelves Clutch Control loop 31.
In described odd number shelves Clutch Control loop 31, with reference to Fig. 4, from the first oil pump 15 or the second oil
The hydraulic oil flow that pump 13 flows out is to the second direct action type proportional pressure valve 310；Second direct action type proportional pressure valve
310 is principle based on switch electromagnetic valve, and pressure and the input current size of electric magnet in valve are proportional,
The pressure of the big then valve of electric current is big, and the pressure of the little then valve of electric current is little；Monitored in real time by pressure transducer 312
The operating pressure of clutch actuator 311, thus the second direct action type proportional pressure valve 310 can be to odd number shelves
Position clutch actuator 311 carries out control and the regulation of pressure, makes described clutch actuator 311 keep
Correct duty, thus odd number shelves clutch actuator 311 controls the unlatching of odd number shelves clutch again
Or close.
Can produce during clutch actuator 311 action certain pressure fluctuation (pressure fluctuation refers to:
Pressure acts on clutch actuator 311 and uneven, at certain position of clutch actuator 311
There is that relatively concentrate or bigger pressure, and this pressure single duration is the longest, it is possible to present one
Fixed periodicity).Controlled and absorb the pressure arteries and veins in described Clutch Control loop by hydraulic buffer 313
Dynamic, prevent the hydraulic vibration impact on described hydraulic control system.
In embodiments of the present invention, as a example by the hydraulic control system of the 7 double clutch gearboxes of speed wet type, institute
State fork controls loop 32 to include: odd number shelves (1,3,5,7 grades) fork controls loop 33 and even number
Shelves (2,4,6 grades and R shelves) fork controls loop.
With continued reference to Fig. 4, odd number shelves (1,3,5,7 grades) fork controls loop 33 includes: 1/3 grade
324,5/7 grade of shift fork executor 325 of shift fork executor；Even gear (2,4,6 grades and R shelves) shift fork
Control loop 34 to include: 2/4 grade of shift fork executor 326,6/R shelves shift fork executor 327.
In the present embodiment, odd number shelves fork controls loop 33 and even gear fork controls loop 34 share one
First direct action type proportional pressure valve 320 of group series connection and direct action type proportional flow valve 321, the first Direct Action Type ratio
Example pressure valve 320 is two-position three way direct action type proportional pressure valve, and direct action type proportional flow valve 321 is three
Four-way direct action type proportional flow valve；Meanwhile, in order to reduce the quantity of valve, between shift fork executor and valve
Also being in series with reversal valve 400 (with reference to Fig. 2), the present embodiment wet-type dual-clutch gear box hydraulic controls system
System is 7 speed wet-type dual-clutch gear box hydraulic control systems, then reversal valve 400 includes the first reversal valve
323 and second reversal valve 322, the first reversal valve 323 is two ten six-way transfer valves, the second reversal valve 322
It is two eight and leads to reversal valve.
With reference to Fig. 4, the hydraulic oil that the first oil pump 15 or the second oil pump 13 are extracted out from fuel tank 10 successively from
First direct action type proportional pressure valve 320, direct action type proportional flow valve the 321, second reversal valve 322, first
Reversal valve 323 flows to shift fork executor, and in the present embodiment, shift fork executor is 1/3 grade of shift fork executor
324,325,2/4 grade of shift fork executor 326 and 6/R shelves shift fork executor 327 of 5/7 grade of shift fork executor；
Four shift fork executors are connected in parallel on the first reversal valve 323.
Being turned on and off of reversal valve 400 is controlled by switch electromagnetic valve 500, and switch electromagnetic valve 500 includes
First switch electromagnetic valve 329 and second switch electromagnetic valve 328；First reversal valve 323 connects the first switch electricity
Magnet valve 329, hydraulic oil flow to the first switch electromagnetic valve 329 thus control the first reversal valve 323 unlatching or
Guan Bi；Equally, the second reversal valve 322 is connected with second switch electromagnetic valve 328, and hydraulic oil flow is to second
Switch electromagnetic valve 328 thus control the closure or openness of the second reversal valve 322.
In prior art, each shift fork executor uses an independent control valve, and this adds undoubtedly
The quantity of control valve.In embodiment of the present invention fork controls loop, use the first direct action type proportional pressure valve
320, the control that direct action type proportional flow valve 321 is connected with the first reversal valve 323 and the second reversal valve 322
Structure control shift fork executor；Ensureing fork controls accuracy, decreasing in fork controls loop and control
The number of applications of valve, has saved system cost.
Due in the present embodiment, the first direct action type proportional pressure valve 320 and direct action type proportional flow valve 321
Connect again with the first reversal valve 323 and the second reversal valve 322 after series connection；And the first reversal valve 323 is two
Position ten six-way transfer valves, the second reversal valve 322 is two eight and leads to reversal valve；It is achieved thereby that the present embodiment
Middle fork controls loop: strange (1,3,5,7 grades), even (2,4,6 grades and R shelves) amount to 8 shelves
The action of position, in other embodiments, can connect and have the reversal valve of more multi-path, it is achieved have more
The action in the fork controls loop of many gears.
Simultaneously as use the first direct action type proportional pressure valve 320, direct action type proportional flow valve 321 and the
One reversal valve 323 and the second reversal valve 322 are connected, and 324,5/7 grade of shift fork of 1/3 grade of shift fork executor performs
325,2/4 grade of shift fork executor 326 of device, 6/R shelves shift fork executor 327 all can be with the first reversal valves 323
Connecting, the action of the shift fork executor of each gear is all held to corresponding shift fork by the first reversal valve 323
Row device provides hydraulic oil；So, four shift fork executors are independently controlled, do not interfere with each other, therefore
Ensure the independence of fork controls and safety, it is to avoid the risk of multiple shift fork of same time action simultaneously,
Improve the safety of system.
In being embodied as, 324,5/7 grade of shift fork executor 325,2/4 of described 1/3 grade of shift fork executor
Shelves shift fork executor 326,6/R shelves shift fork executor 327 can be the double acting homalographics of band sealing function
Piston cylinder, the most described shift fork executor has function and the piston-rodless of way moving shift fork.Additionally, institute
The size structure stating 4 shift fork executors in fork controls loop 32 is identical, to reach to save into
This purpose.
Hereafter by the work of the hydraulic control system of the 7 speed wet-type dual-clutch change speed gear boxes to the embodiment of the present invention
Illustrate as mode.
As a example by 1 grade of working condition:
With reference to Fig. 4, electromotor 16 first oil pump 15 oil suction in fuel tank 10 driven, hydraulic oil warp
Crossing high pressure filter 30 and flow to fork controls loop and Clutch Control loop, now, odd number clutch is held
Row device 311 is in opening, then odd number shelves clutch is off (clutch during shift fork gear shift
Need to disconnect)；Wherein, the hydraulic oil flowed out from high pressure filter 30 is partly into the first switch electromagnetic valve
329, the first switching control pilot 329 controls the first reversal valve 323 and opens；It is partly into second switch electricity
Magnet valve 328, second switch electromagnetic valve 328 controls the second reversal valve 322 and opens；Treat the first reversal valve 323
After opening with the second reversal valve 322；Hydraulic oil flows into Direct Action Type from the first direct action type proportional pressure valve 320
Proportional flow control valve 321, then flow into shift fork executor from the second reversal valve 322 and the first reversal valve 323.
First reversal valve 323 is relevant with the gear of change speed gear box with choosing of the second reversal valve 322, this enforcement
In example, owing to gearbox-gear includes: strange (1,3,5,7 grades), even (2,4,6 grades and R shelves)
Amount to 8 gears, then, the first reversal valve 323 is two ten six-way transfer valves, the second reversal valve 322
It is two eight and leads to reversal valve；In the oil-in of each grade of each shift fork executor and the first reversal valve 323
An oil-out be connected, the most all shift fork executors amount to 8 oil-ins, the most corresponding first reversal valve
8 oil-outs in 323；And in the first reversal valve 323 in each two oil-in and the second reversal valve 322
An oil-out be connected, two oil-ins being connected with 1/3 grade respectively in the i.e. first reversal valve 323 and
2/4 grade of connected two oil-in, two oil-ins being connected with 5/7 grade, be connected with 6/R shelves two
Oil-in is connected with an oil-out in the second reversal valve 322 respectively, that is, the second reversal valve 322
In four oil-outs provide hydraulic oil to four shift fork executors respectively.
Particularly, hydraulic oil flows to the second reversal valve 322 from direct action type proportional flow valve 321, and
From the second reversal valve 322, flow to the first reversal valve 323, then flow in 1/3 grade of shift fork executor 324
Third gear end, thus the hydraulic pressure of third gear end is more than the hydraulic pressure of one grade of end, the pressure of hydraulic oil promotes shift fork to one
Gear moves, thus one grade of work in the shift fork executor 324 of 1/3 grade；Now, hydraulic oil flow is to
Two direct action type proportional pressure valve 310 also enter odd number shelves clutch actuator 311 so that odd number shelves clutch
It is in bonding state, thus one grade is started working.
When needs are in time being changed to third gear for one grade, and odd number clutch actuator 311 is in opening, the most very
Several grades of clutches are off, and the first reversal valve 323 and the second reversal valve 322 need to be in unlatching
State；Hydraulic oil flows into direct action type proportional flow valve 321 from the first direct action type proportional pressure valve 320, then from
Second reversal valve 322 and the first reversal valve 323 flow into shift fork executor；Hydraulic oil is from direct action type proportional stream
Amount valve 321 flows in the second reversal valve 322, and flows to the first reversal valve 323 from the second reversal valve 322,
Flow to one grade of end in 1/3 grade of shift fork executor 324 again, thus the hydraulic pressure of one grade of end is more than the liquid of third gear end
Pressure, the pressure of hydraulic oil promotes shift fork to move to third gear displacement, the third gear in the shift fork executor 324 of 1/3 grade
Work；Complete the gear shift from a grade to third gear.1/3 grade of phase in the operation principle of remaining gear and the present embodiment
With, do not repeat at this.
The present invention also provides for a kind of TCU, TCU and includes: memory element, for storing the rotating speed of electromotor
Setting value；Comparing unit, is used for receiving described tach signal, by rotating speed corresponding for described tach signal with
Described speed setting value relatively and sends comparative result；Indicating member, is used for receiving described comparative result,
Instruction is sent to described motor according to described comparative result；When comparative result is that described tach signal is corresponding
When rotating speed is less than described speed setting value, described rotating speed is low speed or 0, and described instruction is described open command；
When comparative result be tachometer value that described tach signal is corresponding higher than described speed setting value time, described rotating speed
For at a high speed, described instruction is described out code.
Specifically apply to embodiment is:
It is low speed or when 0 when described TCU receives rotating speed corresponding to the tach signal of described electromotor 16,
Sending open command to described motor 14, now, the first oil pump 15 does not works, by the second oil pump 13 from
Extract force feed in fuel tank, meets Clutch Control loop, fork controls loop and lubricating oil cooling circuit
Required hydraulic oil；
When described TCU receive rotating speed corresponding to the tach signal of described electromotor 16 be high speed time, to
Described motor 14 sends out code, now, it is not necessary to the second oil pump 13 works.
Additionally, TCU detects (such as climbing, large throttle starting) when vehicle low speed high load works, now
Clutch is not completely combined and carries out skidding and will generate heat in a large number, and now, not only the first oil pump 15 is in work, the
The demand of lubrication flow also will be started in real time by two oil pumps 13 according to clutch, to maximize clutch
Lubrication flow, improves clutch heat absorption ability.
It should be noted that, in the present embodiment, with reference to Fig. 4, owing to being provided with reversal valve 400, shift fork performs
Device (1/3 grade of shift fork executor 324,5/7 grade of shift fork executor 325,2/4 grade of shift fork executor 326,6/R
Shelves shift fork executor 327) one group of first direct action type proportional pressure valve 320 and direct acting being in series can be shared
Formula proportional flow control valve 321, in other embodiments, can be not provided with reversal valve 400, and each shift fork performs
Device is individually connected direct action type proportional pressure valve and direct action type proportional flow valve, in Fig. 3, odd number shelves shift fork
Control to connect on loop 33 the 4th direct action type proportional pressure valve 320a and the second direct action type proportional flow valve
321a；The 5th direct action type proportional pressure valve 320b of connecting on even gear fork controls loop 34 and the 3rd straight
Dynamic formula proportional flow control valve 321a；Or, two shift fork executors share a reversal valve, then direct acting of connecting
Formula proportional pressure valve and direct action type proportional flow valve；Or, each shift fork executor is all used alone one
Individual reversal valve, i.e. on odd number shelves fork controls loop, described hydraulic oil is from direct action type proportional pressure valve
Flow to direct action type proportional flow valve and flow to odd number shelves shift fork executor through a reversal valve again；At even gear
On fork controls loop, described hydraulic oil flows to direct action type proportional flow valve again from direct action type proportional pressure valve
Even gear shift fork executor is flowed to through a reversal valve；The present embodiment amounts to four shift fork executors,
Corresponding reversal valve is four.
The present invention also provides for a kind of change speed gear box, including the hydraulic control of above-mentioned wet-type dual-clutch change speed gear box
System.
The present invention also provides for a kind of automobile, including above-mentioned change speed gear box and above-mentioned TCU.
Although present disclosure is as above, but the present invention is not limited to this.Any those skilled in the art,
Without departing from the spirit and scope of the present invention, all can make various changes or modifications, therefore the guarantor of the present invention
The scope of protecting should be as the criterion with claim limited range.
Claims (16)
1. the hydraulic control system of a wet-type dual-clutch change speed gear box, it is characterised in that including:
For storing the fuel tank of hydraulic oil；
The first oil pump of oil suction from described fuel tank, described first oil pump is driven by electromotor, it is provided that the
The hydraulic oil of one discharge capacity；
The second oil pump of oil suction from described fuel tank, described second oil pump is driven by motor, it is provided that second
The hydraulic oil of discharge capacity；
Described first discharge capacity is more than described second discharge capacity；
Lubricating oil cooling circuit, for providing cooling and the hydraulic oil of lubrication for clutch；
Clutch Control loop, is used for separating or engaging clutch；
Fork controls loop, is used for controlling gearbox-gear lifting；
When described engine speed higher than speed setting value time, described electromotor drive described first oil pump from
Described fuel tank extracts described lubricating oil cooling circuit, described Clutch Control loop, described fork controls
Hydraulic oil needed for loop；
When described engine speed less than speed setting value time, by described motor drive described second oil pump from
Described fuel tank extracts described lubricating oil cooling circuit, described Clutch Control loop, described fork controls
Hydraulic oil needed for loop.
2. the hydraulic control system of wet-type dual-clutch change speed gear box as claimed in claim 1, it is characterised in that
The hydraulic oil flowed out from described fuel tank passes through the first direct action type proportional pressure valve and Direct Action Type ratio being in series
Described fork controls loop is flowed to after example flow valve.
3. the hydraulic control system of wet-type dual-clutch change speed gear box as claimed in claim 2, it is characterised in that
Described hydraulic oil flows to institute through at least one reversal valve after described direct action type proportional flow valve flows out
State fork controls loop；
Also include: for controlling the switch electromagnetic valve that described reversal valve is turned on and off.
4. the hydraulic control system of wet-type dual-clutch change speed gear box as claimed in claim 1, it is characterised in that
The hydraulic oil flowed out from described fuel tank flows to described Clutch Control through direct action type proportional pressure valve and returns
Road.
5. the hydraulic control system of wet-type dual-clutch change speed gear box as claimed in claim 2, it is characterised in that
Described fork controls loop includes: odd number shelves fork controls loop and even gear fork controls loop；
Described odd number shelves fork controls loop, including:
Odd number shelves shift fork executor；
Described hydraulic oil flows to after the 4th direct action type proportional pressure valve and the second direct action type proportional flow valve
Described odd number shelves shift fork executor；
Described even gear fork controls loop, including:
Even gear shift fork executor；
Described hydraulic oil flows to after the 5th direct action type proportional pressure valve and the 3rd direct action type proportional flow valve
Described even gear shift fork executor.
6. the hydraulic control system of wet-type dual-clutch change speed gear box as claimed in claim 3, it is characterised in that
Described fork controls loop includes: odd number shelves fork controls loop and even gear fork controls loop；
Described odd number shelves fork controls loop, including: odd number shelves shift fork executor；Described even gear shift fork
Control loop, including: even gear shift fork executor；
Described hydraulic oil flows to institute through at least one reversal valve after described direct action type proportional flow valve flows out
State odd number shelves shift fork executor or described even gear shift fork executor.
7. the hydraulic control system of wet-type dual-clutch change speed gear box as claimed in claim 6, it is characterised in that
Described reversal valve includes the first reversal valve and the second reversal valve being serially connected；
Described switch electromagnetic valve includes: control the first switch electromagnetism that described first reversal valve is turned on and off
Valve；Control the second switch electromagnetic valve that described second reversal valve is turned on and off.
8. the hydraulic control system of wet-type dual-clutch change speed gear box as claimed in claim 7, it is characterised in that
Described wet-type dual-clutch change speed gear box is 7 speed wet-type dual-clutch change speed gear boxes；
Described first direct action type proportional pressure valve is two-position three way direct action type proportional pressure valve；
Described direct action type proportional flow valve is 3-position 4-way direct action type proportional flow valve；
Described first reversal valve is two ten six-way transfer valves；
Described second reversal valve is two eight and leads to reversal valve.
9. the hydraulic control system of wet-type dual-clutch change speed gear box as claimed in claim 3, it is characterised in that
Described fork controls loop includes: odd number shelves fork controls loop and even gear fork controls loop；
Described odd number shelves fork controls loop, including: odd number shelves shift fork executor；
Described hydraulic oil flows to described odd number shelves through reversal valve after described direct action type proportional flow valve flows out
Shift fork executor；
Described even gear fork controls loop, including: even gear shift fork executor；
Described hydraulic oil flows to described even gear through reversal valve after described direct action type proportional flow valve flows out
Shift fork executor.
10. the hydraulic control system of wet-type dual-clutch change speed gear box as claimed in claim 4, it is characterised in that
Described Clutch Control loop includes:
For separating or engage the odd number shelves clutch actuator of odd number shelves clutch；
For separating or engage the even gear clutch actuator of even gear clutch；
Described direct action type proportional pressure valve includes: the second direct action type proportional pressure valve being in parallel and the 3rd straight
Dynamic formula proportional pressure valve；
Described hydraulic oil flows to described odd number shelves clutch from described second direct action type proportional pressure valve and performs
Device；
Described hydraulic oil flows to described even gear clutch from described 3rd direct action type proportional pressure valve and performs
Device.
The hydraulic control system of 11. wet-type dual-clutch change speed gear boxes as claimed in claim 1, it is characterised in that
Described electromotor is configured for communicating with TCU with described motor；
When described TCU receives rotating speed corresponding to the tach signal of described electromotor less than speed setting value
Time, send open command to described motor；
When described TCU receives rotating speed corresponding to the tach signal of described electromotor higher than speed setting value
Time, send out code to described motor.
12. 1 kinds for coordinating with the hydraulic control system of the wet-type dual-clutch change speed gear box described in claim 1
TCU, it is characterised in that
For receiving the tach signal of described electromotor, send out to described motor according to the tach signal received
Send instruction；
When described TCU receives rotating speed corresponding to the tach signal of described electromotor less than speed setting value
Time, send open command to described motor；
When described TCU receives rotating speed corresponding to the tach signal of described electromotor higher than speed setting value
Time, send out code to described motor.
13. TCU as claimed in claim 12, it is characterised in that including:
Memory element, for storing the speed setting value of electromotor；
Comparing unit, is used for receiving described tach signal, by rotating speed corresponding for described tach signal with described
Speed setting value relatively and sends comparative result；
Indicating member, is used for receiving described comparative result, sends to described motor according to described comparative result
Instruction；When comparative result be rotating speed that described tach signal is corresponding less than described speed setting value time, described
Rotating speed is low speed or 0, and described instruction is described open command；When comparative result is that described tach signal is corresponding
Tachometer value higher than described speed setting value time, described rotating speed be high speed, described instruction is that described closedown refers to
Order.
14. 1 kinds of change speed gear boxes, it is characterised in that include the wet-type dual-clutch described in any one of claim 1-11
The hydraulic control system of change speed gear box.
15. 1 kinds of automobiles, it is characterised in that include the change speed gear box described in claim 14.
16. automobiles as claimed in claim 15, it is characterised in that also include any one of claim 12-13 institute
The TCU stated.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510362821.4A CN106321805A (en) | 2015-06-26 | 2015-06-26 | A hydraulic control system of a wet-type double-clutch gearbox, a gearbox, a TCU and an automobile |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510362821.4A CN106321805A (en) | 2015-06-26 | 2015-06-26 | A hydraulic control system of a wet-type double-clutch gearbox, a gearbox, a TCU and an automobile |
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| CN107044540A (en) * | 2017-05-24 | 2017-08-15 | 捷孚传动科技有限公司 | gear box hydraulic control system |
| CN107061547A (en) * | 2017-05-24 | 2017-08-18 | 捷孚传动科技有限公司 | hybrid vehicle and its gear box hydraulic control system |
| CN108730509A (en) * | 2018-08-22 | 2018-11-02 | 北京航空航天大学 | A kind of new-energy automobile automatic speed variator hydraulic system |
| CN109027216A (en) * | 2018-08-22 | 2018-12-18 | 北京航空航天大学 | A kind of hydraulic system suitable for new-energy automobile automatic transmission |
| CN109958763A (en) * | 2017-12-26 | 2019-07-02 | 长城汽车股份有限公司 | A kind of hydraulic control system and speed changer, vehicle of double-clutch automatic gearbox |
| CN112664584A (en) * | 2019-10-16 | 2021-04-16 | 上海汽车集团股份有限公司 | Lubrication control method and device of wet clutch and vehicle |
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