CN201561118U - Dual-clutch gearbox gear shifting hydraulic control loop - Google Patents
Dual-clutch gearbox gear shifting hydraulic control loop Download PDFInfo
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- CN201561118U CN201561118U CN 200920276142 CN200920276142U CN201561118U CN 201561118 U CN201561118 U CN 201561118U CN 200920276142 CN200920276142 CN 200920276142 CN 200920276142 U CN200920276142 U CN 200920276142U CN 201561118 U CN201561118 U CN 201561118U
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Abstract
A dual-clutch gearbox gear shifting hydraulic control loop comprises two gear shifting two-position three-way electromagnetic valves and a gear shifting hydraulic loop which is formed by a gear shifting multi-way valve and controls actions of a gear shifting cylinder, and actions of the gear shifting multi-way valve are controlled via a pressure control device. Compared with the gear shifting hydraulic loop in the prior art, oil circuits of the gear shifting electromagnetic valves are selective, and usage of the electromagnetic valves is halved, thereby obviously reducing complexity of a hydraulic system. Through combination of the clutch hydraulic loop, the two gear shifting two-position three-way electromagnetic valves, the gear shifting multi-way valve and the pressure control device, the dual-clutch gearbox gear shifting hydraulic control loop greatly simplifies a dual-clutch gearbox gear shifting hydraulic control system, optimizes the hydraulic loop, leads design and manufacture of valve blocks to be easier, reduces cost of the system, is provided with the valve blocks with small volume, and meets using requirements of small-sized cars.
Description
Technical field
The utility model relates to a kind of hydraulic control circuit, relates in particular to a kind of shift hydraulic control circuit of dual-clutch gearbox.
Background technique
The clutch of double-clutch automatic gearbox and gear shift control are control sections most crucial in the double clutch, because the multi-disc wet clutch control performance is stable, thermal capacity is big, hydraulic control is ripe convenient, and control performance is good, has obtained using widely in the double clutch automatic speed changing system.The scheme of double clutch clutch shifting control, directly influence the performance of system, cost and enforcement degree, in the gearshift hydraulic control system of existing double-clutch automatic gearbox, be by two independently solenoid valve control the action of odd number clutch and even number clutch respectively, but the gear shift control scheme is all more numerous and diverse, as at patent US2006005647, among the US20060009326A1, in the gearshift pressure control circuit, adopted the two-stage hydraulic control, at first obtained (1 grade of odd cycle by two pressure controlled valves, 3 grades, 5 grades, the N shelves) and (2 grades in even loop, 4 grades, 6 grades, the R shelves) two-way, by 4 ON/OFF switch valves two-way pressure oil circuit is divided into 4 oil circuits again, gear shift control valve by electromagnetic valve passes to the corresponding piston pressure control cavity with pressure again, many and the complex structure of system's solenoid valve, system cost is quite high.Numerous and diverse system also causes the valve piece to manufacture and design difficulty, and volume is bigger, can not be adapted to use on the pony car.Therefore be necessary to study and propose novel gearshift loop.
The model utility content
The technical problems to be solved in the utility model provide a kind of simple in structure, valve block of making long-pending little, cost is low, be applicable to the shift hydraulic control circuit of dual-clutch gearbox that pony car uses.
For solving the problems of the technologies described above, the utility model adopts following technological scheme:
A kind of shift hydraulic control circuit of dual-clutch gearbox, the clutch pressure control loop that comprises the action of control double clutch, wherein also comprise by of the collaborative work of two gearshift two-bit triplet solenoid valves with the gearshift multi-way valve, a plurality of gearshift cylinder action controls have been realized, handle corresponding shift fork and realize the gearshift oil hydraulic circuit of gearshift, described gear shift multi-way valve makes its action by pressure control device control.
Shift hydraulic control circuit of dual-clutch gearbox of the present utility model, in the wherein said gearshift oil hydraulic circuit, the gearshift oil cylinder is first oil cylinder and second oil cylinder, and first oil cylinder and second oil cylinder are the two-way ram oil cylinder, and first oil cylinder and second oil cylinder are controlled odd number shelves and even number shelves respectively; The oil-feed port P of the oil-feed port P of the first gearshift two-bit triplet solenoid valve and the second gearshift two-bit triplet solenoid valve links to each other with main oil sources by main gearshift oil duct respectively, the oil return inlet T of the first gearshift two-bit triplet solenoid valve communicates with fuel tank by pipeline, the actuator port A of the first gearshift two-bit triplet solenoid valve links to each other with the actuator port E of gear shift multi-way valve by the first gearshift oil duct, the oil return inlet T 1 of gear shift multi-way valve, T2, T3 communicates with fuel tank by pipeline respectively, the actuator port A of gear shift multi-way valve communicates with the left active chamber of first oil cylinder by oil duct, the actuator port B of gear shift multi-way valve communicates with the left active chamber of second oil cylinder by oil duct, the actuator port C of gear shift multi-way valve communicates with the right active chamber of first oil cylinder by oil duct, and the actuator port D of gear shift multi-way valve communicates with the right active chamber of second oil cylinder by oil duct; The oil return inlet T of the second gearshift two-bit triplet solenoid valve communicates with fuel tank by pipeline, and the actuator port A of the second gearshift two-bit triplet solenoid valve links to each other with the actuator port F of gear shift multi-way valve by the second gearshift oil duct.First oil cylinder and second oil cylinder are controlled odd number shelves and even number shelves respectively, the first gearshift two-bit triplet solenoid valve is set and the second gearshift two-bit triplet solenoid valve carries out pressure control to the range piston left end or the right-hand member of correspondence respectively, the oil circuit of gearshift solenoid valve has selectivity, has significantly reduced the complexity of hydraulic system; Reduced the cost of system.
Shift hydraulic control circuit of dual-clutch gearbox of the present utility model, wherein said pressure control device comprises the two-bit triplet electromagnetic pressure control valve and is arranged on the Returnning spring of gear shift multi-way valve left end, the oil-feed port P of two-bit triplet electromagnetic pressure control valve links to each other with main oil sources, actuator port A links to each other with the right control port of gear shift multi-way valve, and oil return inlet T communicates with fuel tank by pipeline.
Shift hydraulic control circuit of dual-clutch gearbox of the present utility model, in the wherein said clutch pressure control loop, double clutch is odd number clutch and even number clutch, the oil-feed port P of odd number clutch two-bit triplet solenoid valve links to each other with main oil sources respectively with the oil-feed port P of even number clutch two-bit triplet solenoid valve, the oil return inlet T of odd number clutch two-bit triplet solenoid valve communicates with fuel tank by pipeline, and the actuator port A of odd number clutch two-bit triplet solenoid valve links to each other with the odd number clutch by odd number Clutch Control oil duct; The oil return inlet T of even number clutch two-bit triplet solenoid valve communicates with fuel tank by pipeline, and the actuator port A of even number clutch two-bit triplet solenoid valve links to each other with the even number clutch by even number Clutch Control oil duct.
Shift hydraulic control circuit of dual-clutch gearbox of the present utility model, wherein said pressure control device comprises first selector valve control oil duct, second selector valve control oil duct and is arranged on the Returnning spring of gear shift multi-way valve left end, described odd number Clutch Control oil duct links to each other with the right control port of gear shift multi-way valve spool by first selector valve control oil duct, and even number Clutch Control oil duct links to each other with the left control port of gear shift multi-way valve spool by second selector valve control oil duct.Realize the switching of gear shift multi-way valve by the pressure difference of odd number Clutch Control oil duct and even number Clutch Control oil duct, realized the Collaborative Control of clutch and gearshift, and further reduced the solenoid valve usage quantity, and simplified oil hydraulic circuit, reduced the cost of system.
Shift hydraulic control circuit of dual-clutch gearbox of the present utility model, the wherein said first gearshift two-bit triplet solenoid valve and the second gearshift two-bit triplet solenoid valve are PWM solenoid valve or proportional electromagnetic valve.
Shift hydraulic control circuit of dual-clutch gearbox of the present utility model, the wherein said first gearshift two-bit triplet solenoid valve and the second gearshift two-bit triplet solenoid valve are the regular tap solenoid valve, on the described main gearshift oil duct combined type proportional dump valve is housed also, the combined type proportional dump valve can comprise gearshift buffering two-bit triplet pressure regulator valve, the 7th filter, gearshift buffering solenoid valve and the 3rd accumulator; Gearshift buffering two-bit triplet pressure regulator valve is installed on the main gearshift oil duct, also be parallel with the buffering oil duct on the main gearshift oil duct in gearshift buffering two-bit triplet pressure regulator valve the place ahead, described the 7th filter and described gearshift buffering solenoid valve are housed on the buffering oil duct successively, and the other end of buffering oil duct communicates with fuel tank; Be parallel with described the 3rd accumulator on the buffering oil duct between the 7th filter and the gearshift buffering solenoid valve, first restrictor is equipped with in the place ahead of the 3rd accumulator, the pipeline between first restrictor and the 3rd accumulator by being in series with second restrictor pipeline and the right control port of gearshift buffering two-bit triplet pressure regulator valve link to each other.
Shift hydraulic control circuit of dual-clutch gearbox of the present utility model, wherein said odd number clutch two-bit triplet solenoid valve and even number clutch two-bit triplet solenoid valve are PWM solenoid valve or proportional electromagnetic valve; Be in series with the 3rd fine filter on the odd number Clutch Control oil duct; Be in series with the 4th fine filter on the described even number Clutch Control oil duct.
Shift hydraulic control circuit of dual-clutch gearbox of the present utility model is parallel with accumulator respectively on wherein said odd number Clutch Control oil duct and the even number Clutch Control oil duct.
Shift hydraulic control circuit of dual-clutch gearbox of the present utility model, be parallel with pressure transducer respectively on wherein said odd number Clutch Control oil duct and the even number Clutch Control oil duct, be parallel with pressure transducer respectively on the described first gearshift oil duct and the second gearshift oil duct.
Shift hydraulic control circuit of dual-clutch gearbox of the present utility model is realized gearshift by two gearshift two-bit triplet solenoid valves and a gear shift multi-way valve control gearshift cylinder action, and the gear shift multi-way valve is controlled its action by pressure control device.Compare with gearshift oil hydraulic circuit of the prior art, the oil circuit of the utility model gearshift solenoid valve has selectivity, can reduce the solenoid valve use amount of half, significantly reduces the complexity of hydraulic system; Double clutch gearbox gearshift hydraulic control system has greatly been simplified in combination by clutch pressure control loop, two gearshift two-bit triplet solenoid valves, gear shift multi-way valve and pressure control device, optimized oil hydraulic circuit, it is more easy that the valve piece is manufactured and designed, the valve block that makes is long-pending small and exquisite, be adapted to pony car and use, greatly reduced the cost of system.
Description of drawings
Fig. 1 is the schematic diagram of first kind of mode of execution of the utility model shift hydraulic control circuit of dual-clutch gearbox;
Fig. 2 is the schematic diagram of second kind of mode of execution of the utility model shift hydraulic control circuit of dual-clutch gearbox;
Fig. 3 is the schematic diagram of the third mode of execution of the utility model shift hydraulic control circuit of dual-clutch gearbox.
Embodiment
As shown in Figure 1, first kind of mode of execution of the utility model shift hydraulic control circuit of dual-clutch gearbox, comprise the clutch pressure control loop of control double clutch action, by the gearshift oil hydraulic circuit of 16, the 22 and controls that gear shift multi-way valve 25 constitutes gearshifts of two gearshift two-bit triplet solenoid valves cylinder actions, gear shift multi-way valve 25 makes its action by pressure control device control.
In the clutch pressure control loop, double clutch is odd number clutch 13 and even number clutch 31, one end of clutch main oil gallery 2 communicates with main oil sources 1, the other end links to each other with second filter 8 with first filter 3 respectively, the outlet of first filter 3 links to each other by the oil-feed port P of pipeline with odd number clutch two-bit triplet solenoid valve 4, the oil return inlet T of odd number clutch two-bit triplet solenoid valve 4 communicates with fuel tank 50 by pipeline, the actuator port A of odd number clutch two-bit triplet solenoid valve 4 links to each other with odd number clutch 13 by the odd number Clutch Control oil duct 7 that is in series with the 3rd fine filter 6, is parallel with first accumulator 5 on the odd number Clutch Control oil duct 7 between odd number clutch two-bit triplet solenoid valve 4 and the 3rd fine filter 6.The outlet of second filter 8 links to each other by the oil-feed port P of pipeline with even number clutch two-bit triplet solenoid valve 9, the oil return inlet T of even number clutch two-bit triplet solenoid valve 9 communicates with fuel tank 50 by pipeline, the actuator port A of even number clutch two-bit triplet solenoid valve 9 links to each other with even number clutch 31 by the even number Clutch Control oil duct 12 that is in series with the 4th fine filter 11, is parallel with second accumulator 10 on the even number Clutch Control oil duct 12 between even number clutch two-bit triplet solenoid valve 9 and the 4th fine filter 11.Odd number clutch two-bit triplet solenoid valve 4 and even number clutch two-bit triplet solenoid valve 9 are the two-bit triplet solenoid valve of band damper.First accumulator 5 respectively odd number clutch 13, even number clutch 31 are separated with second accumulator 10 or cohesive process in the compression shock that produces absorbed, make clutch separation with combine more steady.Be parallel with pressure transducer 71,72 respectively on odd number Clutch Control oil duct 7 and the even number Clutch Control oil duct 12,, improve pressure controling precision by the pressure control closed loop.
In the gearshift oil hydraulic circuit, the gearshift oil cylinder is that first oil cylinder 20 and second oil cylinder, 28, the first oil cylinders 20 and second oil cylinder 28 are the two-way ram oil cylinder.Gearshift main oil gallery 14 1 ends communicate with main oil sources 1, the other end links to each other with the 6th filter 21 with the 5th filter 15 respectively, the outlet of the 5th filter 15 links to each other by the oil-feed port P of pipeline with the first gearshift two-bit triplet solenoid valve 16, the oil return inlet T of the first gearshift two-bit triplet solenoid valve 16 communicates with fuel tank 50 by pipeline, the actuator port A of the first gearshift two-bit triplet solenoid valve 16 links to each other with the actuator port E of gear shift multi-way valve 25 by the first gearshift oil duct 17, the oil return inlet T 1 of gear shift multi-way valve 25, T2, T3 communicates with fuel tank 50 by pipeline respectively, the actuator port A of gear shift multi-way valve 25 communicates by the left active chamber of the 3rd gear shift oil duct 19 with first oil cylinder 20, the actuator port B of gear shift multi-way valve 25 communicates with the left active chamber of second oil cylinder 28 by the 4th gearshift oil duct 26, the actuator port C of gear shift multi-way valve 25 communicates by the right active chamber of the 5th gear shift oil duct 24 with first oil cylinder 20, and the actuator port D of gear shift multi-way valve 25 communicates by the right active chamber of the 6th gear shift oil duct 27 with second oil cylinder 28.The outlet of the 6th filter 21 links to each other by the oil-feed port P of pipeline with the second gearshift two-bit triplet solenoid valve 22, the oil return inlet T of the second gearshift two-bit triplet solenoid valve 22 communicates with fuel tank 50 by pipeline, and the actuator port A of the second gearshift two-bit triplet solenoid valve 22 links to each other with the actuator port F of gear shift multi-way valve 25 by the second gearshift oil duct 23.Be parallel with pressure transducer 73,74 respectively on the first gearshift oil duct 17 and the second gearshift oil duct 23,, improve pressure controling precision by the pressure control closed loop.
Odd number clutch two-bit triplet solenoid valve 4, even number clutch two-bit triplet solenoid valve 9, the first gearshift two-bit triplet solenoid valve 16 and the second gearshift two-bit triplet solenoid valve 22 can be the high-speed switch electromagnetic valve or the proportional electromagnetic valve of PWM (pulse duration modulation) control.Make-and-break time by the PWM continuous control first gearshift two-bit triplet solenoid valve 16 or the second gearshift two-bit triplet solenoid valve 22 is progressively regulated the hydraulic fluid flow rate that enters first oil cylinder 20 or second oil cylinder 28, slowly increase thereby reach the hydraulic fluid pressure that makes in first oil cylinder 20 or second oil cylinder 28, avoid the unexpected high pressure oil that increases to cause the generation of shift impact phenomenon.
In the present embodiment, pressure control device comprises first selector valve control oil duct 29, second selector valve control oil duct 30, is arranged on the Returnning spring 18 of gear shift multi-way valve 25 left ends, odd number Clutch Control oil duct 7 links to each other with the right control port 51 of gear shift multi-way valve 25 spools by first selector valve control oil duct 29, and even number Clutch Control oil duct 12 links to each other with the left control port 52 of gear shift multi-way valve 25 spools by second selector valve control oil duct 30.
In the present embodiment, promptly 1 grade and 3 grades of first oil cylinder, 20 control odd number shelves, promptly 2 grades and 4 grades of second oil cylinder, 28 control even number shelves.When hydraulic oil entered in the left active chamber of first oil cylinder 20 by the 3rd gearshift oil duct 19, piston shaft moved right and drives 1 grade of selector fork and move, and 1 grade of selector fork is connected with synchronizer gear sleeve, thereby hangs up 1 grade.When hydraulic oil enters the right active chamber of first oil cylinder 20 by the 5th gearshift oil duct 24, piston shaft is moved to the left and drives 3 grades of selector forks and move, and 3 grades of selector forks are connected with synchronizer gear sleeve, thereby hang up 3 grades.When hydraulic oil entered in the left active chamber of second oil cylinder 28 by the 4th gearshift oil duct 26, piston shaft moved right and drives 2 grades of selector forks and move, and 2 grades of selector forks are connected with synchronizer gear sleeve, thereby hang up 2 grades.When hydraulic oil enters the right active chamber of second oil cylinder 28 by the 6th gearshift oil duct 27, piston shaft is moved to the left and drives 4 grades of selector forks and move, and 4 grades of selector forks are connected with synchronizer gear sleeve, thereby hang up 4 grades.
In the present embodiment, 1,3 gears and the collaborative work of odd number clutch, 2,4 gears and 31 collaborative works of even number clutch.In when gearshift, when current gear is 1,3 grades of odd number shelves, 13 combinations of odd number clutch, right control port 51 pressure of gear shift multi-way valve spool raise, and the gear shift multi-way valve is in right valve position, and the gearshift oil hydraulic circuit is that the even number gearshift of carrying out is subsequently got ready; When current gear is the even number shelves, 31 combinations of even number clutch, gear shift multi-way valve spool left side control port 52 pressure raise, and multi-way valve is in left valve position, and the gearshift oil hydraulic circuit is that the odd number gearshift of carrying out is subsequently got ready.
As shown in Figure 2, the second kind of mode of execution of the utility model shift hydraulic control circuit of dual-clutch gearbox and the difference of first kind of mode of execution are: the first gearshift two-bit triplet solenoid valve 16 and the second gearshift two-bit triplet solenoid valve 22 are the regular tap solenoid valve, but on main gearshift oil duct 14 combined type proportional dump valve 145 is housed also, it comprises gearshift buffering two-bit triplet pressure regulator valve 32, the 7th filter 33, gearshift buffering solenoid valve 34 and the 3rd accumulator 35.Gearshift buffering two-bit triplet pressure regulator valve 32 is installed on the main gearshift oil duct 14, also be parallel with buffering oil duct 141 on the main gearshift oil duct 14 in gearshift buffering two-bit triplet pressure regulator valve 32 the place aheads, the 7th filter 3 and gearshift buffering solenoid valve 34 are housed on the buffering oil duct 141 successively, and the other end of buffering oil duct 141 communicates with fuel tank 50.Be parallel with the 3rd accumulator 35 on the buffering oil duct 141 between the 7th filter 3 and the gearshift buffering solenoid valve 34, the place ahead of the 3rd accumulator 35 be equipped with pipeline between first restrictor, 142, the first restrictors 142 and the 3rd accumulator 35 by being in series with second restrictor 143 pipeline and the right control port 144 of gearshift buffering two-bit triplet pressure regulator valve 32 link to each other.
When hydraulic oil flows into through leading gearshift oil duct 14, part hydraulic oil cushions the flow control pressure of solenoid valve 34 control flows oil sump tanks 50 earlier through the 7th filter 33, gearshift, hydraulic oil enters the 3rd accumulator 35 through first restrictor 142 simultaneously, and flow to the right control port 144 of gearshift buffering two-bit triplet pressure regulator valves 32 through second restrictor 143, make gear shift buffering two-bit triplet pressure regulator valve 32 move to corresponding pressure adjusted position, hydraulic oil flows to the 5th filter 15 or the 6th filter 22 through gearshift buffering two-bit triplet pressure regulator valve 32.The pressure oil that enters in first oil cylinder 20 and second oil cylinder 28 by 145 pairs of combined type proportional dump valves carries out the pressure adjusting, the pressure oil that enters in first oil cylinder 20 and second oil cylinder 28 is raise gradually by the goal pressure of controlling, avoid excess pressure directly to impact oil cylinder, cause shift impact.
As shown in Figure 3, the third mode of execution of the utility model shift hydraulic control circuit of dual-clutch gearbox, be with the different of first kind of mode of execution: pressure control device comprises the 3rd selector valve control oil duct 63, two-bit triplet electromagnetic pressure control valve 60, be arranged on the Returnning spring 18 and the 8th filter 61 of gear shift multi-way valve 25 left ends, the 3rd selector valve control oil duct 63 1 ends are connected in parallel on the main gearshift oil duct 14, the other end links to each other with the right control port 51 of gear shift multi-way valve 25, the 8th filter 61 and two-bit triplet electromagnetic pressure control valve 60 are connected on the 3rd selector valve control oil duct 63 successively, the oil-feed port P of two-bit triplet electromagnetic pressure control valve 60 links to each other with the 3rd selector valve control oil duct 63 respectively with actuator port A, and oil return inlet T communicates with fuel tank 50 by pipeline.By the pressure of the right control port 51 of control gear shift multi-way valve 25 spools, control spool right-hand member pressure and left end Returnning spring equilibrium of forces can be realized the switching of gear shift multi-way valve 25 valve position.
Be the working procedure of example explanation the utility model shift hydraulic control circuit of dual-clutch gearbox below with first kind of mode of execution.
Odd number clutch two-bit triplet solenoid valve 4, even number clutch two-bit triplet solenoid valve 9, the first gearshift two-bit triplet solenoid valve 16 and the second gearshift two-bit triplet solenoid valve 22 provide instruction by TCU (transmission control unit) and control.On first oil cylinder and second oil cylinder displacement transducer (not shown) is installed, is used for the displacement of perception selector fork and current gear.And signal passed to TCU, by the feedback control of control signal, improve the gear shift control quality.
During original state, odd number clutch two-bit triplet solenoid valve 4, even number clutch two-bit triplet solenoid valve 9, the first gearshift two-bit triplet solenoid valve 16 and the second gearshift two-bit triplet solenoid valve 22 all are in position, a left side, and gear shift multi-way valve 25 is in position, a left side.
When hanging 1 grade, the first gearshift two-bit triplet solenoid valve 16 moves to right position, hydraulic oil from main oil sources 1 through the gearshift main oil gallery 14, the 5th filter 15, the oil-feed port P of the first gearshift two-bit triplet solenoid valve 16, the actuator port A of the first gearshift two-bit triplet solenoid valve 16, the actuator port E of gear shift multi-way valve 25, the actuator port A of gear shift multi-way valve, the 3rd gearshift oil duct 19 enters the left active chamber of first oil cylinder 20, piston shaft moves right and drives 1 grade of selector fork and move, thereby hang up 1 grade, this moment, displacement transducer was passed to TCU with signal, the first gearshift two-bit triplet solenoid valve 16 moves to position, a left side and cuts out, and the hydraulic oil in first oil cylinder, the 20 left active chambers is through the 3rd gearshift oil duct 19, the actuator port A of gear shift multi-way valve, the actuator port E of gear shift multi-way valve 25, the actuator port A of the first gearshift two-bit triplet solenoid valve 16, the oil return inlet T of the first gearshift two-bit triplet solenoid valve 16 flows back into fuel tank 50.Odd number clutch two-bit triplet solenoid valve 4 moves to right position and opens controlled boost then, hydraulic oil enters odd number clutch 13 from main oil sources 1 through oil-feed port P, the actuator port A of odd number clutch two-bit triplet solenoid valve 4, the 3rd fine filter 6, the odd number Clutch Control oil duct 7 of first filter 3, odd number clutch two-bit triplet solenoid valve 4,13 combinations of odd number clutch, hydraulic oil enters the right control port 51 of gear shift multi-way valve 25 simultaneously through first selector valve control oil duct 29, multi-way control valve 25 moves to right position, and can hang 2 grades or 4 grades this moment.
When hanging 2 grades, the first gearshift two-bit triplet solenoid valve 16 moves to right position, hydraulic oil from main oil sources 1 through the gearshift main oil gallery 14, the 5th filter 15, the oil-feed port P of the first gearshift two-bit triplet solenoid valve 16, the actuator port A of the first gearshift two-bit triplet solenoid valve 16, the actuator port E of gear shift multi-way valve 25, the actuator port B of gear shift multi-way valve, the 4th gearshift oil duct 26 enters the left active chamber of second oil cylinder 28, piston shaft moves right and drives 2 grades of selector forks and move, thereby hang up 2 grades, this moment, displacement transducer was passed to TCU with signal, the first gearshift two-bit triplet solenoid valve 16 moves to position, a left side and cuts out, and the hydraulic oil in second oil cylinder, the 28 left active chambers is through the 4th gearshift oil duct 26, the actuator port B of gear shift multi-way valve, the actuator port E of gear shift multi-way valve 25, the actuator port A of the first gearshift two-bit triplet solenoid valve 16, the oil return inlet T of the first gearshift two-bit triplet solenoid valve 16 flows back into fuel tank 50.Odd number clutch two-bit triplet solenoid valve 4 moves to position, a left side and cuts out controlled release then, and the hydraulic oil in the odd number clutch 13 flows back into fuel tank 50 through the actuator port A of odd number Clutch Control oil duct 7, odd number clutch two-bit triplet solenoid valve 4, the oil return inlet T of odd number clutch two-bit triplet solenoid valve 4.Even number clutch two-bit triplet solenoid valve 9 moves to right position and opens synchronous controlled boost simultaneously, hydraulic oil enters even number clutch 31 from main oil sources 1 through oil-feed port P, the actuator port A of even number clutch two-bit triplet solenoid valve 9, the 4th fine filter 11, the even number Clutch Control oil duct 12 of second filter 8, even number clutch two-bit triplet solenoid valve 9,31 combinations of even number clutch, hydraulic oil enters the left control port 52 of gear shift multi-way valve 25 simultaneously through second selector valve control oil duct 30, multi-way control valve 25 moves to position, a left side, and can hang 1 grade or 3 grades this moment.
When hanging 3 grades, the second gearshift two-bit triplet solenoid valve 22 moves to right position, hydraulic oil from main oil sources 1 through the gearshift main oil gallery 14, the 6th filter 21, the oil-feed port P of the second gearshift two-bit triplet solenoid valve 22, the actuator port A of the second gearshift two-bit triplet solenoid valve 22, the actuator port F of gear shift multi-way valve 25, the actuator port C of gear shift multi-way valve, the 5th gearshift oil duct 24 enters the right active chamber of first oil cylinder 20, piston shaft is moved to the left 3 grades of selector forks of drive and moves, thereby hang up 3 grades, this moment, displacement transducer was passed to TCU with signal, the second gearshift two-bit triplet solenoid valve 22 moves to position, a left side and cuts out, and the hydraulic oil in first oil cylinder, the 20 right active chambers is through the 5th gearshift oil duct 24, the actuator port C of gear shift multi-way valve, the actuator port F of gear shift multi-way valve 25, the actuator port A of the second gearshift two-bit triplet solenoid valve 22, the oil return inlet T of the second gearshift two-bit triplet solenoid valve 22 flows back into fuel tank 50.Even number clutch two-bit triplet solenoid valve 9 moves to position, a left side and cuts out controlled release then, and the hydraulic oil in the even number clutch 31 flows back into fuel tank 50 through actuator port A, even number clutch two-bit triplet solenoid valve 9 oil return inlet T of even number Clutch Control oil duct 12, even number clutch two-bit triplet solenoid valve 9.Odd number clutch two-bit triplet solenoid valve 4 moves to right position and opens synchronous controlled boost simultaneously, hydraulic oil enters odd number clutch 13 from main oil sources 1 through oil-feed port P, the actuator port A of odd number clutch two-bit triplet solenoid valve 4, the 3rd fine filter 6, the odd number Clutch Control oil duct 7 of first filter 3, odd number clutch two-bit triplet solenoid valve 4,13 combinations of odd number clutch, hydraulic oil enters the right control port 51 of gear shift multi-way valve 25 simultaneously through first selector valve control oil duct 29, multi-way control valve 25 moves to right position, and can hang 2 grades or 4 grades this moment.
When hanging 4 grades, the second gearshift two-bit triplet solenoid valve 22 moves to right position, hydraulic oil from main oil sources 1 through the gearshift main oil gallery 14, the 6th filter 21, the oil-feed port P of the second gearshift two-bit triplet solenoid valve 22, the actuator port A of the second gearshift two-bit triplet solenoid valve 22, the actuator port F of gear shift multi-way valve 25, the actuator port D of gear shift multi-way valve, the 6th gearshift oil duct 27 enters the right active chamber of second oil cylinder 28, piston shaft is moved to the left 4 grades of selector forks of drive and moves, thereby hang up 4 grades, this moment, displacement transducer was passed to TCU with signal, the second gearshift two-bit triplet solenoid valve 22 moves to position, a left side and cuts out, and the hydraulic oil in second oil cylinder, the 28 right active chambers is through the 6th gearshift oil duct 27, the actuator port D of gear shift multi-way valve, the actuator port F of gear shift multi-way valve 25, the actuator port A of the second gearshift two-bit triplet solenoid valve 22, the oil return inlet T of the second gearshift two-bit triplet solenoid valve 22 flows back into fuel tank 50.Odd number clutch two-bit triplet solenoid valve 4 moves to position, a left side and cuts out controlled release then, and the hydraulic oil in the odd number clutch 13 flows back into fuel tank 50 through actuator port A, odd number clutch two-bit triplet solenoid valve 4 oil return inlet T of odd number Clutch Control oil duct 7, odd number clutch two-bit triplet solenoid valve 4.Even number clutch two-bit triplet solenoid valve 9 moves to right position and opens synchronous controlled boost simultaneously, hydraulic oil enters even number clutch 31 from main oil sources 1 through oil-feed port P, the actuator port A of even number clutch two-bit triplet solenoid valve 9, the 4th fine filter 11, the even number Clutch Control oil duct 12 of second filter 8, even number clutch two-bit triplet solenoid valve 9,31 combinations of even number clutch, hydraulic oil enters the left control port 52 of gear shift multi-way valve 25 simultaneously through second selector valve control oil duct 30, multi-way control valve 25 moves to position, a left side, and can hang 1 grade or 3 grades this moment.
The difference of the working procedure of the third mode of execution of the utility model shift hydraulic control circuit of dual-clutch gearbox and first kind of mode of execution is: control the switching of gear shift multi-way valve 25 by two-bit triplet electromagnetic pressure control valve 60, two-bit triplet electromagnetic pressure control valve 60 provides instruction by TCU (transmission control unit) and replaces.When needs were hung 1 grade or 3 grades, two-bit triplet electromagnetic pressure control valve 60 dead electricity were in position, a left side, and gear shift multi-way valve 25 is in position, a left side under Returnning spring 18 effects, and can hang 1 grade or 3 grades this moment.When needs are hung 2 grades or 4 grades, two-bit triplet electromagnetic pressure control valve 60 gets the electric right position that is in, hydraulic oil is through the 3rd selector valve control oil duct 63, the 8th filter 61, the oil-feed port P of two-bit triplet electromagnetic pressure control valve 60 and the right control port 51 that actuator port A enters gear shift multi-way valve 25, gear shift multi-way valve 25 moves to right position, and can hang 2 grades or 4 grades this moment.
Above-described embodiment is described preferred implementation of the present utility model; be not that scope of the present utility model is limited; under the prerequisite that does not break away from the utility model design spirit; various distortion and improvement that those of ordinary skills make the technical solution of the utility model all should fall in the definite protection domain of the utility model claims.
Claims (10)
1. shift hydraulic control circuit of dual-clutch gearbox, the clutch pressure control loop that comprises the action of control double clutch, it is characterized in that: also comprise by the collaborative work of two gearshift two-bit triplet solenoid valves (16,22) with gearshift multi-way valve (25), a plurality of gearshift cylinder action controls have been realized, handle corresponding shift fork and realize the gearshift oil hydraulic circuit of gearshift, described gear shift multi-way valve (25) makes its action by pressure control device control.
2. shift hydraulic control circuit of dual-clutch gearbox according to claim 1, it is characterized in that: in the described gearshift oil hydraulic circuit, the gearshift oil cylinder is first oil cylinder (20) and second oil cylinder (28), first oil cylinder (20) and second oil cylinder (28) are the two-way ram oil cylinder, and first oil cylinder (20) and second oil cylinder (28) are controlled odd number shelves and even number shelves respectively; The oil-feed port P of the oil-feed port P of the first gearshift two-bit triplet solenoid valve (16) and the second gearshift two-bit triplet solenoid valve (22) links to each other with main oil sources (1) by main gearshift oil duct (14) respectively, the oil return inlet T of the first gearshift two-bit triplet solenoid valve (16) communicates with fuel tank (50) by pipeline, the actuator port A of the first gearshift two-bit triplet solenoid valve (16) links to each other with the actuator port E of gear shift multi-way valve (25) by the first gearshift oil duct (17), the oil return inlet T 1 of gear shift multi-way valve (25), T2, T3 communicates with fuel tank (50) by pipeline respectively, the actuator port A of gear shift multi-way valve (25) communicates by the left active chamber of oil duct with first oil cylinder (20), the actuator port B of gear shift multi-way valve (25) communicates by the left active chamber of oil duct with second oil cylinder (28), the actuator port C of gear shift multi-way valve (25) communicates by the right active chamber of oil duct with first oil cylinder (20), and the actuator port D of gear shift multi-way valve (25) communicates by the right active chamber of oil duct with second oil cylinder (28); The oil return inlet T of the second gearshift two-bit triplet solenoid valve (22) communicates with fuel tank (50) by pipeline, and the actuator port A of the second gearshift two-bit triplet solenoid valve (22) links to each other with the actuator port F of gear shift multi-way valve (25) by the second gearshift oil duct (23).
3. shift hydraulic control circuit of dual-clutch gearbox according to claim 1 and 2, it is characterized in that: described pressure control device comprises two-bit triplet electromagnetic pressure control valve (60) and is arranged on the Returnning spring (18) of gear shift multi-way valve (25) left end, the oil-feed port P of two-bit triplet electromagnetic pressure control valve (60) links to each other with main oil sources (1), actuator port A links to each other with the right control port (51) of gear shift multi-way valve (25), and oil return inlet T communicates with fuel tank (50) by pipeline.
4. shift hydraulic control circuit of dual-clutch gearbox according to claim 1 and 2, it is characterized in that: in the described clutch pressure control loop, double clutch is odd number clutch (13) and even number clutch (31), the oil-feed port P of the oil-feed port P of odd number clutch two-bit triplet solenoid valve (4) and even number clutch two-bit triplet solenoid valve (9) links to each other with main oil sources (1) respectively, the oil return inlet T of odd number clutch two-bit triplet solenoid valve (4) communicates with fuel tank (50) by pipeline, and the actuator port A of odd number clutch two-bit triplet solenoid valve (4) links to each other with odd number clutch (13) by odd number Clutch Control oil duct (7); The oil return inlet T of even number clutch two-bit triplet solenoid valve (9) communicates with fuel tank (50) by pipeline, and the actuator port A of even number clutch two-bit triplet solenoid valve (9) links to each other with even number clutch (31) by even number Clutch Control oil duct (12).
5. shift hydraulic control circuit of dual-clutch gearbox according to claim 4, it is characterized in that: described pressure control device comprises first selector valve control oil duct (29), second selector valve is controlled oil duct (30) and is arranged on the Returnning spring (18) of gear shift multi-way valve (25) left end, described odd number Clutch Control oil duct (7) links to each other with the right control port (51) of gear shift multi-way valve (25) spool by first selector valve control oil duct (29), and even number Clutch Control oil duct (12) links to each other with the left control port (52) of gear shift multi-way valve (25) spool by second selector valve control oil duct (30).
6. according to claim 2 or 5 described shift hydraulic control circuit of dual-clutch gearbox, it is characterized in that: the described first gearshift two-bit triplet solenoid valve (16) and the second gearshift two-bit triplet solenoid valve (22) are PWM solenoid valve or proportional electromagnetic valve.
7. according to claim 2 or 5 described shift hydraulic control circuit of dual-clutch gearbox, it is characterized in that: the described first gearshift two-bit triplet solenoid valve (16) and the second gearshift two-bit triplet solenoid valve (22) are the regular tap solenoid valve, on the described main gearshift oil duct (14) combined type proportional dump valve (145) is housed also, combined type proportional dump valve (145) comprises gearshift buffering two-bit triplet pressure regulator valve (32), the 7th filter (33), gearshift buffering solenoid valve (34) and the 3rd accumulator (35); Gearshift buffering two-bit triplet pressure regulator valve ((32)) is installed on the main gearshift oil duct (14), also be parallel with buffering oil duct (141) on the main gearshift oil duct (14) in gearshift buffering two-bit triplet pressure regulator valve (32) the place ahead, described the 7th filter (33) and described gearshift buffering solenoid valve (34) is housed on the buffering oil duct (141) successively, and the other end of buffering oil duct (141) communicates with fuel tank (50); Be parallel with described the 3rd accumulator (35) on the buffering oil duct (141) between the 7th filter (33) and the gearshift buffering solenoid valve (34), first restrictor (142) is equipped with in the place ahead of the 3rd accumulator (35), the pipeline between first restrictor (142) and the 3rd accumulator (35) by being in series with second restrictor (143) pipeline and the right control port (144) of gearshift buffering two-bit triplet pressure regulator valve (32) link to each other.
8. shift hydraulic control circuit of dual-clutch gearbox according to claim 4 is characterized in that: described odd number clutch two-bit triplet solenoid valve (4) and even number clutch two-bit triplet solenoid valve (9) are PWM solenoid valve or proportional electromagnetic valve; Be in series with the 3rd fine filter (6) on the odd number Clutch Control oil duct (7); Be in series with the 4th fine filter (11) on the described even number Clutch Control oil duct (12).
9. according to claim 5 or 8 described shift hydraulic control circuit of dual-clutch gearbox, it is characterized in that: be parallel with accumulator (5,10) on described odd number Clutch Control oil duct (7) and the even number Clutch Control oil duct (12) respectively.
10. shift hydraulic control circuit of dual-clutch gearbox according to claim 9, it is characterized in that: be parallel with pressure transducer (71,72) on described odd number Clutch Control oil duct (7) and the even number Clutch Control oil duct (12) respectively, be parallel with pressure transducer (73,74) respectively on the described first gearshift oil duct (17) and the second gearshift oil duct (23).
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| Application Number | Priority Date | Filing Date | Title |
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| CN 200920276142 CN201561118U (en) | 2009-12-08 | 2009-12-08 | Dual-clutch gearbox gear shifting hydraulic control loop |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200920276142 CN201561118U (en) | 2009-12-08 | 2009-12-08 | Dual-clutch gearbox gear shifting hydraulic control loop |
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| CN201561118U true CN201561118U (en) | 2010-08-25 |
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| CN 200920276142 Expired - Fee Related CN201561118U (en) | 2009-12-08 | 2009-12-08 | Dual-clutch gearbox gear shifting hydraulic control loop |
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Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101709777A (en) * | 2009-12-08 | 2010-05-19 | 重庆青山工业有限责任公司 | Shift hydraulic control circuit of dual-clutch gearbox |
| CN102062204A (en) * | 2010-11-16 | 2011-05-18 | 浙江吉利汽车研究院有限公司 | Clutch hydraulic control device of double-clutch automatic transmission |
| CN102230534A (en) * | 2011-04-22 | 2011-11-02 | 安徽江淮汽车股份有限公司 | Hydraulic control system for double-clutch automatic gearbox |
| CN102230533A (en) * | 2011-04-22 | 2011-11-02 | 安徽江淮汽车股份有限公司 | Hydraulic control system for dual-clutch automatic transmission |
| CN103403402A (en) * | 2011-03-30 | 2013-11-20 | 爱信艾达株式会社 | Hydraulic control device |
| CN103542019A (en) * | 2013-09-24 | 2014-01-29 | 浙江吉利控股集团有限公司 | Clutch hydraulic control device of double-clutch automatic transmission |
| CN105299213A (en) * | 2015-11-11 | 2016-02-03 | 安徽江淮汽车股份有限公司 | Oil pre-charging system of dual-clutch automatic transmission |
| CN105465355A (en) * | 2014-09-03 | 2016-04-06 | 上海汽车集团股份有限公司 | Dual-clutch transmission and hydraulic control system thereof |
| EP2735754A4 (en) * | 2011-07-20 | 2016-06-08 | Aisin Ai Co Ltd | Transmission |
| 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 |
| CN108006015A (en) * | 2017-11-24 | 2018-05-08 | 四川凌峰航空液压机械有限公司 | Dynamic test stand supplies oil return hydraulic system |
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| CN101709777B (en) * | 2009-12-08 | 2013-11-27 | 重庆青山工业有限责任公司 | Shift hydraulic control circuit of dual-clutch gearbox |
| CN101709777A (en) * | 2009-12-08 | 2010-05-19 | 重庆青山工业有限责任公司 | Shift hydraulic control circuit of dual-clutch gearbox |
| CN102062204B (en) * | 2010-11-16 | 2015-07-15 | 浙江吉利汽车研究院有限公司 | Clutch hydraulic control device of double-clutch automatic transmission |
| CN102062204A (en) * | 2010-11-16 | 2011-05-18 | 浙江吉利汽车研究院有限公司 | Clutch hydraulic control device of double-clutch automatic transmission |
| CN103403402A (en) * | 2011-03-30 | 2013-11-20 | 爱信艾达株式会社 | Hydraulic control device |
| CN102230534A (en) * | 2011-04-22 | 2011-11-02 | 安徽江淮汽车股份有限公司 | Hydraulic control system for double-clutch automatic gearbox |
| CN102230533A (en) * | 2011-04-22 | 2011-11-02 | 安徽江淮汽车股份有限公司 | Hydraulic control system for dual-clutch automatic transmission |
| CN102230534B (en) * | 2011-04-22 | 2013-08-14 | 安徽江淮汽车股份有限公司 | Hydraulic control system for double-clutch automatic gearbox |
| CN102230533B (en) * | 2011-04-22 | 2013-08-14 | 安徽江淮汽车股份有限公司 | Hydraulic control system for dual-clutch automatic transmission |
| EP2735754A4 (en) * | 2011-07-20 | 2016-06-08 | Aisin Ai Co Ltd | Transmission |
| CN103542019A (en) * | 2013-09-24 | 2014-01-29 | 浙江吉利控股集团有限公司 | Clutch hydraulic control device of double-clutch automatic transmission |
| CN105465355A (en) * | 2014-09-03 | 2016-04-06 | 上海汽车集团股份有限公司 | Dual-clutch transmission and hydraulic control system thereof |
| CN105465355B (en) * | 2014-09-03 | 2018-03-06 | 上海汽车集团股份有限公司 | Double-clutch speed changer and its hydraulic control system |
| CN105299213A (en) * | 2015-11-11 | 2016-02-03 | 安徽江淮汽车股份有限公司 | Oil pre-charging system of dual-clutch automatic transmission |
| 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 |
| CN107061547B (en) * | 2017-05-24 | 2022-11-08 | 捷孚传动科技有限公司 | Hybrid electric vehicle and gearbox hydraulic control system thereof |
| CN108006015A (en) * | 2017-11-24 | 2018-05-08 | 四川凌峰航空液压机械有限公司 | Dynamic test stand supplies oil return hydraulic system |
| CN108006015B (en) * | 2017-11-24 | 2023-08-15 | 四川凌峰航空液压机械有限公司 | Hydraulic circulation system for oil supply and return of dynamic test bed |
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