CN203239914U - Hydraulic control system for automatic double-clutch speed changing box - Google Patents
Hydraulic control system for automatic double-clutch speed changing box Download PDFInfo
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- CN203239914U CN203239914U CN 201320277608 CN201320277608U CN203239914U CN 203239914 U CN203239914 U CN 203239914U CN 201320277608 CN201320277608 CN 201320277608 CN 201320277608 U CN201320277608 U CN 201320277608U CN 203239914 U CN203239914 U CN 203239914U
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Abstract
The utility model discloses a hydraulic control system for an automatic double-clutch speed changing box. The hydraulic control system comprises an odd-number gear and reverse gear control module and an even-number gear and new gear control module. In the odd-number gear and reverse gear control module, a first clutch hydraulic cylinder is correspondingly and respectively communicated with a first synchronizer hydraulic cylinder and a second synchronizer hydraulic cylinder through a first synchronizer flow proportional valve and a second synchronizer flow proportional valve; a first actuator pressure control valve is respectively communicated with the first clutch hydraulic cylinder, the first synchronizer flow proportional valve and the second synchronizer flow proportional valve. In the even-number gear and new gear control module, a second clutch hydraulic cylinder is correspondingly and respectively communicated with a third synchronizer hydraulic cylinder and a fourth synchronizer hydraulic cylinder through a third synchronizer flow proportional valve and a fourth synchronizer flow proportional valve; a second actuator pressure control valve is respectively communicated with the second clutch hydraulic cylinder, the third synchronizer flow proportional valve and the fourth synchronizer flow proportional valve. The hydraulic control system for the automatic double-clutch speed changing box is few in number of electromagnetic valves, simple to control, high in system response speed and low in cost.
Description
Technical field
The utility model relates to the automobile gearbox technical field, relates in particular to a kind of hydraulic control system for dual-clutch transmission.
Background technique
Typical transmission device of double clutch transmission is by two coaxial nested or clutches of being arranged in parallel, two input shafts of coaxial, inside and outside nested arrangement, two output shafts that are arranged in parallel are arranged in a plurality of synchromesh gears on the output shaft, a plurality of selector fork and 1 differential mechanism and form.Speed changer is strange, even number gear input gear is arranged on two input shafts, and switching and the action of different synchronizer by two clutches realize torque conversion and output via different output shafts.And the double clutch hydraulic control system refers to the control signal of accepting entire car controller, the action of controlling two clutches and selector fork final controlling element by various final controlling element adjusting oil liquid pressures, flow and direction realizes the various functions such as gear selecting gearshift, satisfies the automatic demand for control of vehicle.
The double clutch control system adopts too much mechanical slide valve even multi-way valve, control numerous and diverse, thereby cause that the whole system speed of response is slow, safety control risk height.
For overcoming defects, notification number is that the patent of 102230533A has disclosed a kind of like this hydraulic control system for dual-clutch transmission.Particularly, referring to figs. 1 through Fig. 4, a kind of hydraulic control system for dual-clutch transmission, suction filter 1 ' links to each other with the inlet port 2 ' P of oil pump 2 ', and the outlet 2 ' B of oil pump 2 ' is being communicated with respectively the filler opening 33 ' P of main oil pressure Proportional valve 33 ', filler opening 34 ' the P of main oil pressure guiding valve 34 ' and left end control mouthful 34 ' A1, filler opening 21 ' the P of first clutch pressure controlled valve 21 ', filler opening 22 ' the P of second clutch pressure controlled valve 22 ', filler opening 27 ' the P of the first gearshift pressure proportioning valve 27 ', filler opening 28 ' the P of the second gearshift pressure proportioning valve 28 ', oil-feed port 3 ' the P of relief valve 3 '; Main oil pressure Proportional valve 33 ' is for often driving the two-bit triplet solenoid valve, main oil pressure guiding valve 34 ' is the 3-position-3-way guiding valve, first clutch pressure controlled valve 21 ', second clutch pressure controlled valve 22 ' are normally closed two-bit triplet solenoid valve, and the first gearshift pressure proportioning valve 27 ', the second gearshift pressure proportioning valve 28 ' are normally closed two-bit triplet solenoid valve.
Oil outlet 33 ' the B of main oil pressure Proportional valve 33 ' is being communicated with the right-hand member control mouthful 34 ' A2 of main oil pressure guiding valve 34 ', and the return opening 33 ' T of main oil pressure Proportional valve 33 ' is being communicated with fuel tank by oil pipe.
Oil outlet 34 ' the B of main oil pressure guiding valve 34 ' is divided into two-way, and one the tunnel is being communicated with the import of cooler 4 ', and another road is being communicated with filler opening 35 ' P and the left end first control mouthful 35 ' A1 of lubricated guiding valve 35 ', and lubricated guiding valve 35 ' is the 2/2-way guiding valve; The outlet of cooler 4 ' is being communicated with the import of filter-press 6 ' and the import of one-way valve 5 '; Oil outlet 35 ' the B of lubricated guiding valve 35 ' is divided into two-way, the first via is being communicated with the control mouth 35 ' A2 of lubricated guiding valve 35 ' right-hand member, the second the tunnel is divided into again four branch roads, one branch road is being communicated with the outlet of filter-press 6 ' and the outlet of one-way valve 5 ', two branch roads are being communicated with gear, bearing lubricating oil circuit 7 ', three branch roads are being communicated with filler opening 36 ' P and the right-hand member control mouthful 36 ' A1 of clutch cooling guiding valve 36 ', and four branch roads are being communicated with the filler opening 37 ' P of clutch cooling Proportional valve 37 '; Clutch cooling guiding valve 36 ' is the 2/2-way guiding valve, and described clutch cooling Proportional valve 37 ' is for often driving the 2/2-way solenoid valve; Oil outlet 36 ' the B of clutch cooling guiding valve 36 ' is being communicated with the inlet port of oil pump by oil pipe; Oil outlet 37 ' the B of clutch cooling Proportional valve 37 ' is divided into two-way, and one the tunnel is being communicated with clutch cooling oil path 8 ', and another road is being communicated with the left end control mouthful 36 ' A2 of clutch cooling guiding valve 36 '.
Oil outlet 21 ' the B of first clutch pressure controlled valve 21 ' is divided into two-way, the first via is being communicated with the oil-feed port 23 ' P of first clutch safety valve 23 ', pipeline between first clutch pressure controlled valve 21 ' and the first clutch safety valve 23 ' is provided with the first accumulator 25 ', the the second tunnel feedback is communicated to the right-hand member control mouthful 21 ' A of first clutch pressure controlled valve 21 ', the pressure of dynamic adjustments oil outlet 21 ' B, the return opening 21 ' T of first clutch pressure controlled valve 21 ' communicates with fuel tank.
First clutch safety valve 23 ' oil outlet 23 ' B is being communicated with first clutch oil hydraulic cylinder 9 ', pipeline between first clutch safety valve 23 ' and the first clutch oil hydraulic cylinder 9 ' is provided with the first pressure transducer 15 ', and the return opening 23 ' T of first clutch safety valve 23 ' communicates with fuel tank.
Oil outlet 22 ' the B of second clutch pressure controlled valve 22 ' is divided into two-way, the first via is being communicated with the oil-feed port 24 ' P of second clutch safety valve 24 ', pipeline between second clutch pressure controlled valve 22 ' and the second clutch safety valve 24 ' is provided with the second accumulator 26 ', the the second tunnel feedback is communicated to the right-hand member control mouthful 22 ' A of second clutch pressure controlled valve 22 ', the pressure of dynamic adjustments oil outlet 22 ' B, the return opening 22 ' T of second clutch pressure controlled valve 22 ' communicates with fuel tank.
Second clutch safety valve 24 ' oil outlet 24 ' B is being communicated with second clutch oil hydraulic cylinder 10 ', pipeline between second clutch safety valve 24 ' and the second clutch oil hydraulic cylinder 10 ' is provided with the second pressure transducer 16 ', and the return opening 24 ' T of second clutch safety valve 24 ' communicates with fuel tank.
The first gearshift pressure proportioning valve 27 ' is the two-bit triplet proportional electromagnetic valve; Oil outlet 27 ' the B of the first gearshift pressure proportioning valve 27 ' is being communicated with the filler opening 29 ' P of odd number shift speed control valve 29 ' and the control mouth 27 ' A of the first gearshift pressure proportioning valve 27 ', and the return opening 27 ' T of the first gearshift pressure proportioning valve 27 ' communicates with fuel tank.
Odd number shift speed control valve 29 ' is four four-way proportional electromagnetic valves; Oil outlet 29 ' the B of odd number shift speed control valve 29 ' is being communicated with the first filler opening 31 ' P1 and the 3rd filler opening 31 ' P3 of odd number gear selector valve 31 ', the first oil outlet 29 ' B1 of odd number shift speed control valve 29 ' is being communicated with the second filler opening 31 ' P2 and the 4th filler opening 31 ' P4 of odd number gear selector valve 31 ', and the return opening 29 ' T of odd number shift speed control valve 29 ' communicates with fuel tank.
Odd number gear selector valve 31 ' is two nine and opens up the pass solenoid valve; The first oil outlet 31 ' B1 of odd number gear selector valve 31 ' and the second oil outlet 31 ' B2 are being communicated with respectively a gear end and the three gear ends of the first synchronizer oil hydraulic cylinder 11 ', the 3rd oil outlet 31 ' B3 of odd number gear selector valve 31 ' and the 4th oil outlet 31 ' B4 are being communicated with respectively new gear end and the five gear ends of the second synchronizer oil hydraulic cylinder 12 ', and the return opening 31 ' T of odd number gear selector valve 31 ' is being communicated with fuel tank.
The second gearshift pressure proportioning valve 28 ' is the two-bit triplet proportional electromagnetic valve; Oil outlet 28 ' the B of the second gearshift pressure proportioning valve 28 ' is being communicated with the filler opening 30 ' P of even number shift speed control valve 30 ' and the control mouth 28 ' A of the second gearshift pressure proportioning valve 28 ', and the return opening 28 ' T of the second gearshift pressure proportioning valve 28 ' communicates with fuel tank.
Even number shift speed control valve 30 ' is four four-way proportional electromagnetic valves; Oil outlet 30 ' the B of even number shift speed control valve 30 ' is being communicated with the first filler opening 32 ' P1 and the 3rd filler opening 32 ' P3 of even number gear selector valve 32 ', the first oil outlet 30 ' B1 of even number shift speed control valve 30 ' is being communicated with the second filler opening 32 ' P2 and the 4th filler opening 32 ' P4 of even number gear selector valve 32 ', and the return opening 30 ' T of even number shift speed control valve 30 ' communicates with fuel tank.
Even number gear selector valve 32 ' is two nine and opens up the pass solenoid valve; The first oil outlet 32 ' B1 of even number gear selector valve 32 ' and the second oil outlet 32 ' B2 are being communicated with respectively four gear end and the ends that reverse gear of the 3rd synchronizer oil hydraulic cylinder 13 ', the 3rd oil outlet 32 ' B3 of even number gear selector valve 32 ' and the 4th oil outlet 32 ' B4 are being communicated with respectively six gear ends and the two gear ends of the 4th synchronizer oil hydraulic cylinder 14 ', and the return opening 32 ' T of even number gear selector valve 32 ' is being communicated with fuel tank.
The first synchronizer oil hydraulic cylinder 11 ', the second synchronizer oil hydraulic cylinder 12 ', the 3rd synchronizer oil hydraulic cylinder 13 ', the 4th synchronizer oil hydraulic cylinder 14 ' are common double-action thrust oil hydraulic cylinder; First clutch oil hydraulic cylinder 9 ' and second clutch oil hydraulic cylinder 10 ' are common spring return single action piston oil hydraulic cylinder.
1 gear, 3 gears, 5 gears and new gear share first clutch; 2 gears, 4 gears, 6 gear and the shared second clutches that reverse gear.1 gear and 3 gears share a gearshift final controlling element; 5 gears and new gear share a gearshift final controlling element; 4 gears and the shared gearshift final controlling element that reverses gear; 2 gears and 6 gears share a gearshift final controlling element.
The defective of above-mentioned hydraulic control system is:
(1) first clutch with the odd number gear corresponding with it, newly the gear synchronizer separates control, uses respectively independently pressure controlled valve: first clutch pressure controlled valve 21 ' and first the gearshift pressure proportioning valve 27 '; And second clutch separates control with corresponding even number gear with it, the gear synchronizer that reverses gear, and uses respectively independently pressure controlled valve: second clutch pressure controlled valve 22 ' and the second gearshift pressure proportioning valve 28 '.Like this, so that have 4 pressure controlled valves in the whole hydraulic control system, when having increased cost and oil circuit design complexity, reduced the speed of response of system;
(2) has a mechanical valve (clutch cooling guiding valve 36 ' in the clutch cooling branch road, it is the 2/2-way guiding valve) and a solenoid valve (clutch cooling Proportional valve 37 ', it is the 2/2-way solenoid valve), when having increased cost and oil circuit design complexity, reduced the speed of response of system.
The model utility content
The purpose of this utility model is to overcome deficiency of the prior art, and a kind of hydraulic control system for dual-clutch transmission is provided.
For achieving the above object, described hydraulic control system for dual-clutch transmission, it comprises the odd number gear, a control module of reversing gear and even number gear, new shift control module, described odd number gear, a control module of reversing gear comprise the first synchronizer oil hydraulic cylinder, the second synchronizer oil hydraulic cylinder and the first actuator pressure control valve, and described even number gear, new shift control module comprise the 3rd synchronizer oil hydraulic cylinder, the 4th synchronizer oil hydraulic cylinder and the second actuator pressure control valve; Be characterized in,
Described odd number gear, a control module of reversing gear also comprise first clutch oil hydraulic cylinder, the first synchronizer flow proportion valve and the second synchronizer flow proportion valve; Described first clutch oil hydraulic cylinder is connected with described the first synchronizer oil hydraulic cylinder and the second synchronizer oil hydraulic cylinder correspondingly by described the first synchronizer flow proportion valve and the second synchronizer flow proportion valve respectively; Described the first actuator pressure control valve is connected with first clutch oil hydraulic cylinder, the first synchronizer flow proportion valve and the second synchronizer flow proportion valve respectively; And,
Described even number gear, new shift control module also comprise second clutch oil hydraulic cylinder, the 3rd synchronizer flow proportion valve and the 4th synchronizer flow proportion valve; Described second clutch oil hydraulic cylinder is connected with described the 3rd synchronizer oil hydraulic cylinder and the 4th synchronizer oil hydraulic cylinder correspondingly by described the 3rd synchronizer flow proportion valve and the 4th synchronizer flow proportion valve respectively; Described the second actuator pressure control valve is connected with second clutch oil hydraulic cylinder, the 3rd synchronizer flow proportion valve and the 4th synchronizer flow proportion valve respectively.
Preferably, described the first synchronizer flow proportion valve, the second synchronizer flow proportion valve, the 3rd synchronizer flow proportion valve and the 4th synchronizer flow proportion valve are the 3-position 4-way proportional electromagnetic valve; Described the first actuator pressure Proportional valve and the second actuator pressure Proportional valve are two position four-way solenoid valves.
Preferably, the pipeline between described first clutch oil hydraulic cylinder and the first synchronizer flow proportion valve or the second synchronizer flow proportion valve is provided with the first pressure transducer, the first accumulator and first clutch safety valve; And,
Pipeline between described second clutch oil hydraulic cylinder and the 3rd synchronizer flow proportion valve or the 4th synchronizer flow proportion valve is provided with the second pressure transducer, the second accumulator and second clutch safety valve.
Preferably, described first clutch safety valve and second clutch safety valve are normally closed switch electromagnetic valve.
Preferably, described hydraulic control system also comprises the clutch cooling Proportional valve for the solenoidoperated cluthes cooling oil path, the 3-position-3-way solenoid valve of described clutch cooling Proportional valve for often opening.
The beneficial effects of the utility model are, hydraulic control system described in the utility model, and the solenoid valve quantity of required simultaneously action is few when shifting, and control is simple, adopts direct electromagnetic valve controlling system fast response time.Particularly:
(1) first clutch and the odd number gear corresponding with it, newly the gear synchronizer only needs to use a pressure controlled valve: the first actuator pressure control valve in conjunction with control; And second clutch and corresponding even number gear with it, the gear synchronizer that reverses gear only need to use a pressure controlled valve: the second actuator pressure control valve in conjunction with control.Like this, so that have 2 pressure controlled valves in the whole hydraulic control system, when having reduced cost and oil circuit design complexity, increased the speed of response of system;
(2) only use a solenoid valve in the clutch cooling branch road: clutch cooling Proportional valve, replace a mechanical valve of the prior art and a solenoid valve, reduce the quantity of valve, thereby when having reduced cost and oil circuit design complexity, increased the speed of response of system.
Description of drawings
Fig. 1 shows the structural representation of the hydraulic control system for dual-clutch transmission described in the prior art.
Fig. 2 shows the partial enlarged drawing of the working connection shown in Fig. 1 and lubrication oil circuit part.
It is double clutch part partial enlarged drawing among Fig. 1 that Fig. 3 shows.
Fig. 4 shows the partial enlarged drawing of gearshift final controlling element part among Fig. 1.
It is the structural representation of the hydraulic control system for dual-clutch transmission described in the utility model that Fig. 5 shows.
Fig. 6 shows the partial enlarged drawing of the working connection shown in Fig. 5 and lubrication oil circuit part.
Fig. 7 shows the shift control part partial enlarged drawing shown in Fig. 5.
Description of reference numerals
1, suction filter; 2, oil pump; 3, relief valve; 4, cooler; 5, one-way valve; 6, filter-press; 7, gear, bearing lubricating oil circuit; 8, clutch cooling oil path; 9, first clutch oil hydraulic cylinder; 10, the first synchronizer oil hydraulic cylinder; 11, the second synchronizer oil hydraulic cylinder; 12, second clutch oil hydraulic cylinder; 13, the 3rd synchronizer oil hydraulic cylinder; 14, the 4th synchronizer oil hydraulic cylinder; 15, the first displacement transducer; 16, second displacement sensor; 17, triple motion sensor; 18, the 4th displacement transducer; 19, the first actuator pressure Proportional valve (two position four-way solenoid valves); 20, the second actuator pressure Proportional valve (two position four-way solenoid valves); 21, the first pressure transducer; 22, the first accumulator; 23, first clutch safety valve (two-bit triplet solenoid valve); 24, the first synchronizer flow proportion valve (three position four-way electromagnetic valve); 25, the second synchronizer flow proportion valve (three position four-way electromagnetic valve); 26, the second pressure transducer; 27, the second accumulator; 28, second clutch safety valve (two-bit triplet solenoid valve); 29, the 3rd synchronizer flow proportion valve (three position four-way electromagnetic valve); 30, the 4th synchronizer flow proportion valve (three position four-way electromagnetic valve); 31, main oil pressure Proportional valve (two-bit triplet solenoid valve); 32, main oil pressure guiding valve (3-position-3-way guiding valve); 33, lubricated guiding valve (3-position-3-way solenoid valve); 34, clutch cooling Proportional valve (3-position-3-way solenoid valve).
Embodiment
The below describes embodiment of the present utility model in detail, and embodiment's example is shown in the drawings, and wherein identical or similar label represents identical or similar element or the element with identical or similar functions from start to finish.Be exemplary below by the embodiment who is described with reference to the drawings, only be used for explaining the utility model, and can not be interpreted as restriction of the present utility model.
Referring to Fig. 5, hydraulic control system for dual-clutch transmission described in the utility model comprises suction filter 1, oil pump 2, cooler 4, first clutch oil hydraulic cylinder 9, second clutch oil hydraulic cylinder 12, the first synchronizer oil hydraulic cylinder 10, the second synchronizer oil hydraulic cylinder 11, the 3rd synchronizer oil hydraulic cylinder 13 and the 4th synchronizer oil hydraulic cylinder 14, described suction filter 1 links to each other with oil pump 2 inlet port 2P, and the outlet 2B of oil pump 2 is being communicated with respectively the filler opening 31P of main oil pressure Proportional valve 31, the filler opening 32P of main oil pressure guiding valve 32 and left end control mouthful 32A1, the oil-feed port 19P of the first actuator pressure control valve 19, the filler opening 20P of the second actuator pressure control valve 20, the oil-feed port 3P of relief valve 3; The two-bit triplet solenoid valve of described main oil pressure Proportional valve 31 for often opening, described main oil pressure guiding valve 32 is the 3-position-3-way guiding valve, described the first actuator pressure control valve 19, the second actuator pressure control valve 20 are normally closed two-bit triplet solenoid valve, and described relief valve 3 is the spring steel ball check valve.
Referring to Fig. 6, the oil outlet 31B of main oil pressure Proportional valve 31 is being communicated with the right-hand member control mouthful 32A2 of main oil pressure guiding valve 32, a pressure feedback of control mouth 31A of giving simultaneously main oil pressure Proportional valve 31, and the return opening 31T of main oil pressure Proportional valve 31 is being communicated with fuel tank by oil pipe.
The oil outlet 32B of described main oil pressure guiding valve 32 is divided into two-way, and one the tunnel is being communicated with the import of cooler 4, and another road is being communicated with filler opening 33P and the left end first control mouthful 33A1 of lubricated guiding valve 33, and lubricated guiding valve 33 is the 2/2-way guiding valve; The outlet of cooler 4 is being communicated with the import of filter-press 6 and the import of one-way valve 5; The oil outlet 33B of lubricated guiding valve 33 is divided into two-way, the first via is being communicated with the control mouth 33A2 of lubricated guiding valve 33 right-hand members, the second the tunnel is divided into again three branch roads, one branch road is being communicated with the outlet of filter-press 6 and the outlet of one-way valve 5, two branch roads are being communicated with gear, bearing lubricating oil circuit 7, three branch roads are communicated with the filler opening 34P that clutch cools off Proportional valve 34; Described clutch cooling Proportional valve 34 is the 3-position-3-way solenoid valve of often opening; The oil outlet 34B of described clutch cooling Proportional valve 34 is divided into two-way, and one the tunnel is being communicated with clutch cooling oil path 8, and another road is being communicated with its right-hand member control mouthful 34A, and the return opening 34T of clutch cooling Proportional valve 34 is being communicated with the inlet port of oil pump by oil pipe.
Referring to Fig. 7, the oil outlet 19B of the first actuator pressure control valve 19 is divided into the right-hand member control mouthful 19A that four tunnel, one tunnel feedback is communicated to the first actuator pressure control valve 19; Two the tunnel are being communicated with the filler opening 23P of first clutch safety valve 23; Three the tunnel are communicated to the filler opening 24P of the first synchronizer flow proportion valve 24; Four the tunnel are communicated to the filler opening 25P of the second synchronizer flow proportion valve 25; The return opening 19T of the first actuator pressure control valve 19 communicates with fuel tank.
First clutch safety valve 23 is normally closed switch electromagnetic valve, first clutch safety valve 23 oil outlet 23B are being communicated with first clutch oil hydraulic cylinder 9, pipeline between first clutch safety valve 23 and the first clutch oil hydraulic cylinder 9 is provided with the first pressure transducer 21 and the first accumulator 22, and first clutch safety valve 23 return opening 23T communicate with fuel tank.
The first synchronizer flow proportion valve 24 is the 3-position 4-way proportional electromagnetic valve; The oil outlet 24B of the first synchronizer flow proportion valve 24 is being communicated with a gear end of the first synchronizer oil hydraulic cylinder 10, the first oil outlet 24B1 of the first synchronizer flow proportion valve 24 is being communicated with three gear ends of the first synchronizer oil hydraulic cylinder 10, and the return opening 24T of the first synchronizer flow proportion valve 24 communicates with fuel tank.
The second synchronizer flow proportion valve 25 is the 3-position 4-way proportional electromagnetic valve; The oil outlet 25B of the second synchronizer flow proportion valve 25 is being communicated with the new gear end of the second synchronizer oil hydraulic cylinder 11, the first oil outlet 25B1 of the second synchronizer flow proportion valve 25 is being communicated with five gear ends of the second synchronizer oil hydraulic cylinder 11, and the return opening 25T of the second synchronizer flow proportion valve 25 communicates with fuel tank.
The oil outlet 20B of the second actuator pressure control valve 20 is divided into the right-hand member control mouthful 20A that four tunnel, one tunnel feedback is communicated to the second actuator pressure control valve 20; Two the tunnel are being communicated with the filler opening 28P of second clutch safety valve 28; Three the tunnel are communicated to the filler opening 29P of the 3rd synchronizer flow proportion valve 29; Four the tunnel are communicated to the filler opening 30P of the 4th synchronizer flow proportion valve 30; The return opening 20T of the second actuator pressure control valve 20 communicates with fuel tank.
Second clutch safety valve 28 is normally closed switch electromagnetic valve, the oil outlet 28B of second clutch safety valve 28 is being communicated with second clutch oil hydraulic cylinder 12, pipeline between second clutch safety valve 28 and the second clutch oil hydraulic cylinder 12 is provided with the second pressure transducer 26 and the first accumulator 27, and second clutch safety valve 28 return opening 28T communicate with fuel tank.
The 3rd synchronizer flow proportion valve 29 is the 3-position 4-way proportional electromagnetic valve; The oil outlet 29B of the 3rd synchronizer flow proportion valve 29 is being communicated with six gear ends of the 3rd synchronizer oil hydraulic cylinder 13, the first oil outlet 29B1 of the 3rd synchronizer flow proportion valve 29 is being communicated with two gear ends of the 3rd synchronizer oil hydraulic cylinder 13, and the return opening 29T of the 3rd synchronizer flow proportion valve 29 communicates with fuel tank.
The 4th synchronizer flow proportion valve 30 is the 3-position 4-way proportional electromagnetic valve; The oil outlet 30B of the 4th synchronizer flow proportion valve 30 is being communicated with four gear ends of the 4th synchronizer oil hydraulic cylinder 14, the first oil outlet 30B1 of the 4th synchronizer flow proportion valve 30 is being communicated with the end that reverses gear of the 4th synchronizer oil hydraulic cylinder 14, and the return opening 30T of the 4th synchronizer flow proportion valve 30 communicates with fuel tank.
Described the first synchronizer oil hydraulic cylinder 10, the second synchronizer oil hydraulic cylinder 11, the 3rd synchronizer oil hydraulic cylinder 13, the 4th synchronizer oil hydraulic cylinder 14 are common double-action thrust oil hydraulic cylinder; Described first clutch oil hydraulic cylinder 9 and second clutch oil hydraulic cylinder 12 are common spring return single action piston oil hydraulic cylinder.
1 gear, 3 gears, 5 gears and new gear share first clutch; 2 gears, 4 gears, 6 gear and the shared second clutches that reverse gear.1 gear and 3 gears share a gearshift final controlling element; 5 gears and new gear share a gearshift final controlling element; 4 gears and the shared gearshift final controlling element that reverses gear; 2 gears and 6 gears share a gearshift final controlling element.
Working principle of the present utility model is as follows:
1 gear working condition: referring to Fig. 7, pressure oil is out flowed through the oil-feed port 19P of the first actuator pressure control valve 19 to oil outlet 19B from the oil outlet 2B of oil pump 2, flow to the oil-feed port 24P of the first synchronizer flow proportion valve 24, give simultaneously pressure feedback of control mouth 19A of the first actuator pressure control valve 19, flow to the fluid of oil-feed port 24P of the first synchronizer flow proportion valve 24 through the first oil outlet 24B1 of the first synchronizer flow proportion valve 24, flow to the left chamber three gear ends of the first synchronizer oil hydraulic cylinder 10, one gear synchronizer engages the first displacement transducer 15 Real-Time Monitorings one, three gear gearshift actuator position; The right chamber fluid of the first synchronizer oil hydraulic cylinder 10 is advanced by the oil outlet 24B of the first synchronizer flow proportion valve 24, through drain tap 24T earial drainage oil sump tank, and pressure and engaging speed that above-mentioned control section major control 1 gear synchronizer engages.Referring to Fig. 7, then pressure oil is out flowed through the oil-feed port 19P of the first actuator pressure control valve 19 to oil outlet 19B from oil pump 2, flow to the oil-feed port 23P of first clutch safety valve 23, give simultaneously pressure feedback of control mouth 19A of the first actuator pressure control valve 19, oil outlet 23B through first clutch safety valve 23, flow to first clutch oil hydraulic cylinder 9, first clutch engages, one gear work, the oil pressure that has the first accumulator 22 absorption pressure pulses assurance to feed to first clutch in the way that flows to first clutch oil hydraulic cylinder 9 is stablized, the first pressure transducer 21 Real-Time Monitoring first clutch pressure oil pressure, the pressure of the joint of this control section major control first clutch.
2 gear working conditions: referring to Fig. 7, pressure oil is out flowed through the oil-feed port 20P of the second actuator pressure control valve 20 to oil outlet 20B from oil pump 2 oil outlet 2B, flow to the oil-feed port 29P of the 3rd synchronizer flow proportion valve 29, give simultaneously pressure feedback of control mouth 20A of the second actuator pressure control valve 20, flow to the fluid of the 3rd synchronizer flow proportion valve 29 oil-feed port 29P through the oil outlet 29B of the 3rd synchronizer flow proportion valve 29, flow to the right chamber six gear ends of the 3rd synchronizer oil hydraulic cylinder 13, two gear synchronizers engage triple motion sensor 17 Real-Time Monitorings two, six gear gearshift actuator position; The left chamber fluid of the 3rd synchronizer oil hydraulic cylinder 13 is advanced by the first oil outlet 28B1 of the 3rd synchronizer flow proportion valve 28, through drain tap 28T earial drainage oil sump tank, and pressure and engaging speed that above-mentioned control section major control 2 gear synchronizers engage.Referring to Fig. 7, then pressure oil is out flowed through the oil-feed port 20P of the second actuator pressure control valve 20 to oil outlet 20B from oil pump 2, flow to the oil-feed port 28P of second clutch safety valve 28, give simultaneously pressure feedback of control mouth 20A of the second actuator pressure control valve 20, oil outlet 28B through second clutch safety valve 28, flow to second clutch oil hydraulic cylinder 12, second clutch engages, two gear work, the oil pressure that has the second accumulator 27 absorption pressure pulses assurance to feed to second clutch in the way that flows to second clutch oil hydraulic cylinder 12 is stablized, the second pressure transducer 26 Real-Time Monitoring second clutch pressure oil pressure, the pressure of the joint of this control section major control second clutch.
3 gear working conditions: referring to Fig. 7, pressure oil is out flowed through the oil-feed port 19P of the first actuator pressure control valve 19 to oil outlet 19B from oil pump 2 oil outlet 2B, flow to the oil-feed port 24P of the first synchronizer flow proportion valve 24, give simultaneously pressure feedback of control mouth 19A of the first actuator pressure control valve 19, flow to the fluid of the first synchronizer flow proportion valve 24 oil-feed port 24P through the oil outlet 24B of the first synchronizer flow proportion valve 24, flow to the right chamber one gear end of the first synchronizer oil hydraulic cylinder 10, three gear synchronizers engage the first displacement transducer 15 Real-Time Monitorings one, three gear gearshift actuator position; The left chamber fluid of the first synchronizer oil hydraulic cylinder 10 is advanced by the first oil outlet 24B1 of the first synchronizer flow proportion valve 24, through drain tap 24T earial drainage oil sump tank, and pressure and engaging speed that above-mentioned control section major control 3 gear synchronizers engage.Referring to Fig. 7, then pressure oil is out flowed through the oil-feed port 19P of the first actuator pressure control valve 19 to oil outlet 19B from oil pump 2, flow to the oil-feed port 23P of first clutch safety valve 23, give simultaneously pressure feedback of control mouth 19A of the first actuator pressure control valve 19, oil outlet 23B through first clutch safety valve 23, flow to first clutch oil hydraulic cylinder 9, first clutch engages, three gear work, the oil pressure that has the first accumulator 22 absorption pressure pulses assurance to feed to first clutch in the way that flows to first clutch oil hydraulic cylinder 9 is stablized, the first pressure transducer 21 Real-Time Monitoring first clutch pressure oil pressure, the pressure of the joint of this control section major control first clutch.
4 gear working conditions: pressure oil is out flowed through the oil-feed port 20P of the second actuator pressure control valve 20 to oil outlet 20B from oil pump 2 oil outlet 2B, flow to the oil-feed port 29P of the 3rd synchronizer flow proportion valve 29, give simultaneously pressure feedback of control mouth 20A of the second actuator pressure control valve 20, flow to the fluid of the 4th synchronizer flow proportion valve 30 oil-feed port 30P through the first oil outlet 30B1 of the 4th synchronizer flow proportion valve 30, end reverses gear in the left chamber that flows to the 4th synchronizer oil hydraulic cylinder 14, four gear synchronizers engage the 4th displacement transducer 18 Real-Time Monitorings four, the gearshift actuator position of reversing gear; The right chamber fluid of the 4th synchronizer oil hydraulic cylinder 14 is advanced by the oil outlet 30B of the 4th synchronizer flow proportion valve 30, through drain tap 30T earial drainage oil sump tank, and pressure and engaging speed that above-mentioned control section major control 4 gear synchronizers engage.Referring to Fig. 7, then pressure oil is out flowed through the oil-feed port 20P of the second actuator pressure control valve 20 to oil outlet 20B from oil pump 2, flow to the oil-feed port 28P of second clutch safety valve 28, give simultaneously pressure feedback of control mouth 20A of the second actuator pressure control valve 20, oil outlet 28B through second clutch safety valve 28, flow to second clutch oil hydraulic cylinder 12, second clutch engages, four gear work, the oil pressure that has the second accumulator 27 absorption pressure pulses assurance to feed to second clutch in the way that flows to second clutch oil hydraulic cylinder 12 is stablized, the second pressure transducer 26 Real-Time Monitoring second clutch pressure oil pressure, the pressure of the joint of this control section major control second clutch.
5 gear working conditions: referring to Fig. 7, pressure oil is out flowed through the oil-feed port 19P of the first actuator pressure control valve 19 to oil outlet 19B from oil pump 2 oil outlet 2B, flow to the oil-feed port 25P of the second synchronizer flow proportion valve 25, give simultaneously pressure feedback of control mouth 19A of the first actuator pressure control valve 19, flow to the fluid of the second synchronizer flow proportion valve 25 oil-feed port 25P through the oil outlet 25B of the second synchronizer flow proportion valve 25, the right chamber that flows to the second synchronizer oil hydraulic cylinder 11 newly keeps off end, five gear synchronizers engage second displacement sensor 16 Real-Time Monitorings five, new gear gearshift actuator position; The left chamber fluid of the second synchronizer oil hydraulic cylinder 11 is advanced by the first oil outlet 25B1 of the second synchronizer flow proportion valve 25, through drain tap 25T earial drainage oil sump tank, and pressure and engaging speed that above-mentioned control section major control 5 gear synchronizers engage.Referring to Fig. 7, then pressure oil is out flowed through the oil-feed port 19P of the first actuator pressure control valve 19 to oil outlet 19B from oil pump 2, flow to the oil-feed port 23P of first clutch safety valve 23, give simultaneously pressure feedback of control mouth 19A of the first actuator pressure control valve 19, oil outlet 23B through first clutch safety valve 23, flow to first clutch oil hydraulic cylinder 9, first clutch engages, five gear work, the oil pressure that has the first accumulator 22 absorption pressure pulses assurance to feed to first clutch in the way that flows to first clutch oil hydraulic cylinder 9 is stablized, the first pressure transducer 21 Real-Time Monitoring first clutch pressure oil pressure, the pressure of the joint of this control section major control first clutch.
6 gear working conditions: pressure oil is out flowed through the oil-feed port 20P of the second actuator pressure control valve 20 to oil outlet 20B from oil pump 2 oil outlet 2B, flow to the oil-feed port 29P of the 3rd synchronizer flow proportion valve 29, give simultaneously pressure feedback of control mouth 20A of the second actuator pressure control valve 20, flow to the fluid of the 3rd synchronizer flow proportion valve 29 oil-feed port 29P through the first oil outlet 29B1 of the 3rd synchronizer flow proportion valve 29, flow to the left chamber two gear ends of the 3rd synchronizer oil hydraulic cylinder 13, six gear synchronizers engage triple motion sensor 17 Real-Time Monitorings two, six gear gearshift actuator position; The right chamber fluid of the 3rd synchronizer oil hydraulic cylinder 13 is advanced by the oil outlet 28B of the 3rd synchronizer flow proportion valve 28, through drain tap 28T earial drainage oil sump tank, and pressure and engaging speed that above-mentioned control section major control 6 gear synchronizers engage.Referring to Fig. 7, then pressure oil is out flowed through the oil-feed port 20P of the second actuator pressure control valve 20 to oil outlet 20B from oil pump 2, flow to the oil-feed port 28P of second clutch safety valve 28, give simultaneously pressure feedback of control mouth 20A of the second actuator pressure control valve 20, oil outlet 28B through second clutch safety valve 28, flow to second clutch oil hydraulic cylinder 12, second clutch engages, six gear work, the oil pressure that has the second accumulator 27 absorption pressure pulses assurance to feed to second clutch in the way that flows to second clutch oil hydraulic cylinder 12 is stablized, the second pressure transducer 26 Real-Time Monitoring second clutch pressure oil pressure, the pressure of the joint of this control section major control second clutch.
The working condition of reversing gear: pressure oil is out flowed through the oil-feed port 20P of the second actuator pressure control valve 20 to oil outlet 20B from oil pump 2 oil outlet 2B, flow to the oil-feed port 29P of the 3rd synchronizer flow proportion valve 29, give simultaneously pressure feedback of control mouth 20A of the second actuator pressure control valve 20, flow to the fluid of the 4th synchronizer flow proportion valve 30 oil-feed port 30P through the oil outlet 30B of the 4th synchronizer flow proportion valve 30, flow to the right chamber four gear ends of the 4th synchronizer oil hydraulic cylinder 14, reverse gear synchronizer engages, the 4th displacement transducer 18 Real-Time Monitorings four, the gearshift actuator position of reversing gear; The left chamber fluid of the 4th synchronizer oil hydraulic cylinder 14 is advanced by the first oil outlet 30B1 of the 4th synchronizer flow proportion valve 30, through drain tap 30T earial drainage oil sump tank, and pressure and engaging speed that above-mentioned control section major control reverse gear synchronizer engages.Referring to Fig. 7, then pressure oil is out flowed through the oil-feed port 20P of the second actuator pressure control valve 20 to oil outlet 20B from oil pump 2, flow to the oil-feed port 28P of second clutch safety valve 28, give simultaneously pressure feedback of control mouth 20A of the second actuator pressure control valve 20, oil outlet 28B through second clutch safety valve 28, flow to second clutch oil hydraulic cylinder 12, second clutch engages, the work of reversing gear, the oil pressure that has the second accumulator 27 absorption pressure pulses assurance to feed to second clutch in the way that flows to second clutch oil hydraulic cylinder 12 is stablized, the second pressure transducer 26 Real-Time Monitoring second clutch pressure oil pressure, the pressure of the joint of this control section major control second clutch.
New gear working condition: referring to Fig. 7, pressure oil is out flowed through the oil-feed port 19P of the first actuator pressure control valve 19 to oil outlet 19B from the oil outlet 2B of oil pump 2, flow to the oil-feed port 25P of the second synchronizer flow proportion valve 25, give simultaneously pressure feedback of control mouth 19A of the first actuator pressure control valve 19, flow to the fluid of the second synchronizer flow proportion valve 25 oil-feed port 25P through the first oil outlet 25B1 of the second synchronizer flow proportion valve 25, flow to the left chamber five gear ends of the second synchronizer oil hydraulic cylinder 11, new gear synchronizer engages second displacement sensor 16 Real-Time Monitorings five, new gear gearshift actuator position; The right chamber fluid of the second synchronizer oil hydraulic cylinder 11 is advanced by the oil outlet 25B of the second synchronizer flow proportion valve 25, through drain tap 25T earial drainage oil sump tank, and pressure and engaging speed that above-mentioned control section major control 5 gear synchronizers engage.Referring to Fig. 7, then pressure oil is out flowed through the oil-feed port 19P of the first actuator pressure control valve 19 to oil outlet 19B from oil pump 2, flow to the oil-feed port 23P of first clutch safety valve 23, give simultaneously pressure feedback of control mouth 19A of the first actuator pressure control valve 19, oil outlet 23B through first clutch safety valve 23, flow to first clutch oil hydraulic cylinder 9, first clutch engages, new gear work, the oil pressure that has the first accumulator 22 absorption pressure pulses assurance to feed to first clutch in the way that flows to first clutch oil hydraulic cylinder 9 is stablized, the first pressure transducer 21 Real-Time Monitoring first clutch pressure oil pressure, the pressure of the joint of this control section major control first clutch.
The following describes the utility model system to the safety protection effect of first clutch and second clutch.
Safety protection about first clutch: referring to Fig. 7, when first clutch in running order, this moment is because the needs of gearshift, first clutch is thrown off, but clamping stagnation occurs in the first actuator pressure control valve 19, and the oil-feed port 19P of the first actuator pressure control valve 19 is communicated with oil outlet 19B always; Disconnect 23 power supplies of first clutch safety valve, the oil-feed port 21P of first clutch safety valve 23 is not communicated with oil outlet 21B, pressure oil in the first clutch oil hydraulic cylinder 9 passes through the oil outlet 23B of first clutch safety valve 23 from return opening 23T earial drainage oil sump tank, and first clutch is thrown off.
Safety protection about second clutch: referring to Fig. 7, when second clutch in running order, this moment is because the needs of gearshift, must make its disengagement of second clutch, but clamping stagnation occurs in the second actuator pressure control valve 20, and the oil-feed port 20P of the second actuator pressure control valve 20 is communicated with oil outlet 20B always; Disconnect 28 power supplies of second clutch safety valve, the oil-feed port 28P of second clutch safety valve 28 is not communicated with oil outlet 28B, pressure oil in the second clutch oil hydraulic cylinder 12 passes through the oil outlet 28B of second clutch safety valve 28 from return opening 28T earial drainage oil sump tank, and second clutch is thrown off.
Regulate about main oil pressure: referring to Fig. 6, pressure oil out flows to the oil-feed port 32P of main oil pressure guiding valve 32, the first control mouthful 32A1 of left end and the oil-feed port 31P of main oil pressure Proportional valve 31 simultaneously from the oil outlet 2B of oil pump 2; The fluid that flows to main oil pressure Proportional valve 31 is gone out by oil-feed port 31P oil inlet and outlet 31B, and the first via feeds back to the control mouth 31A of main oil pressure Proportional valve 31, and the second the road flows to the second control mouthful 32A2 of main oil pressure guiding valve 32 right-hand members; The oil outlet 32B openings of sizes of under the second control mouthful 32A2 two ends differential pressure action of the first control mouthful 32A1 of the left end of main oil pressure guiding valve 32 and right-hand member, regulating main oil pressure guiding valve 32, thus flow and the pressure that flows to oil outlet 32B fluid from the oil-feed port 32P of main oil pressure guiding valve 32 regulated.
Lubricated guiding valve 33 is regulated: referring to Fig. 6, pressure oil is from the oil outlet 32B of main oil pressure guiding valve 32, and the first via flows to the oil-feed port 33P of lubricated guiding valve 33, and the second the road flows to the first control mouthful 33A1 of lubricated guiding valve 33 left ends; The fluid that flows to lubricated guiding valve 33 oil-feed port 33P flows out from oil outlet 33B, and a part that flows out fluid feeds back to the second control mouthful 33A2 of lubricated guiding valve 33 right-hand members; Control second of mouthful 33A1 and right-hand member at first of the left end that lubricates guiding valve 33 and control the oil outlet 33B openings of sizes that guiding valve 33 is lubricated in adjusting under mouthful 33A2 two ends differential pressure action, thereby regulate flow and the pressure that flows to oil outlet 33B fluid from the oil-feed port 33P that lubricates guiding valve 33.
Low-temperature lubrication, cooling work situation: referring to Fig. 6, pressure oil is from the oil outlet 32B of main oil pressure guiding valve 32, flow to the oil-feed port 33P of lubricated guiding valve 33, oil outlet 33B through lubricated guiding valve 33, two branch road gears, bearing lubricating oil circuit 7 by the second tunnel realize gear, bearing etc. is lubricated; The second tunnel three branch roads flow to the oil-feed port 34P of clutch cooling Proportional valve 34, through the return opening 34T of clutch cooling Proportional valve 34, flow back to the inlet port 2P of oil pump 2 by pipeline.
Normal condition is lubricated, cooling work: referring to Fig. 6, pressure oil is from the oil outlet 32B of main oil pressure guiding valve 32, and the first via flows to cooler 4 and filter-press 6; The second the road flows to the oil-feed port 33P of lubricated guiding valve 33, oil outlet 33B through lubricated guiding valve 33, communicate with the outlet of a branch road filter-press 6 and the outlet of one-way valve 5, pass through again the second tunnel two branch road gears, bearing lubricating oil circuit 7, realize gear, bearing etc. is lubricated; The second tunnel three branch roads flow to the oil-feed port 34P of clutch cooling Proportional valve 34, a part is through the oil outlet 34B of clutch cooling Proportional valve 34, the fluid that flows out is by clutch cooling oil path 8, realization is cooled off clutch, another part flows back to the inlet port 2P of oil pump 2 through the return opening 34T of clutch cooling Proportional valve 34 by pipeline.
High temperature lubricating, cooling work situation: referring to Fig. 6, pressure oil is from the oil outlet 32B of main oil pressure guiding valve 32 flow through cooler 4 and filter-press 6, and two branch road gears, bearing oil 7 by the second tunnel are realized gear, bearing etc. is lubricated; The second tunnel three branch roads flow to the oil-feed port 34P of clutch cooling Proportional valve 34, and through the oil outlet 34B of clutch cooling Proportional valve 34, the fluid of outflow is realized clutch is cooled off by clutch cooling oil path 8.
Embodiment shown in above foundation is graphic describes structure of the present utility model, feature and action effect in detail; it below only is preferred embodiment of the present utility model; but the utility model does not limit practical range with shown in the drawing; every change of doing according to conception of the present utility model; or be revised as the equivalent embodiment of equivalent variations; when not exceeding yet specification and illustrating contain spiritual, all should be in protection domain of the present utility model.
Claims (5)
1. hydraulic control system that is used for dual-clutch transmission, it comprises the odd number gear, a control module of reversing gear and even number gear, new shift control module, described odd number gear, a control module of reversing gear comprise the first synchronizer oil hydraulic cylinder, the second synchronizer oil hydraulic cylinder and the first actuator pressure control valve, and described even number gear, new shift control module comprise the 3rd synchronizer oil hydraulic cylinder, the 4th synchronizer oil hydraulic cylinder and the second actuator pressure control valve; It is characterized in that:
Described odd number gear, a control module of reversing gear also comprise first clutch oil hydraulic cylinder, the first synchronizer flow proportion valve and the second synchronizer flow proportion valve; Described first clutch oil hydraulic cylinder is connected with described the first synchronizer oil hydraulic cylinder and the second synchronizer oil hydraulic cylinder correspondingly by described the first synchronizer flow proportion valve and the second synchronizer flow proportion valve respectively; Described the first actuator pressure control valve is connected with first clutch oil hydraulic cylinder, the first synchronizer flow proportion valve and the second synchronizer flow proportion valve respectively; And,
Described even number gear, new shift control module also comprise second clutch oil hydraulic cylinder, the 3rd synchronizer flow proportion valve and the 4th synchronizer flow proportion valve; Described second clutch oil hydraulic cylinder is connected with described the 3rd synchronizer oil hydraulic cylinder and the 4th synchronizer oil hydraulic cylinder correspondingly by described the 3rd synchronizer flow proportion valve and the 4th synchronizer flow proportion valve respectively; Described the second actuator pressure control valve is connected with second clutch oil hydraulic cylinder, the 3rd synchronizer flow proportion valve and the 4th synchronizer flow proportion valve respectively.
2. the hydraulic control system for dual-clutch transmission according to claim 1, it is characterized in that: described the first synchronizer flow proportion valve, the second synchronizer flow proportion valve, the 3rd synchronizer flow proportion valve and the 4th synchronizer flow proportion valve are the 3-position 4-way proportional electromagnetic valve; Described the first actuator pressure Proportional valve and the second actuator pressure Proportional valve are two position four-way solenoid valves.
3. the hydraulic control system for dual-clutch transmission according to claim 1, it is characterized in that: the pipeline between described first clutch oil hydraulic cylinder and the first synchronizer flow proportion valve or the second synchronizer flow proportion valve is provided with the first pressure transducer, the first accumulator and first clutch safety valve; And,
Pipeline between described second clutch oil hydraulic cylinder and the 3rd synchronizer flow proportion valve or the 4th synchronizer flow proportion valve is provided with the second pressure transducer, the second accumulator and second clutch safety valve.
4. the hydraulic control system for dual-clutch transmission according to claim 3, it is characterized in that: described first clutch safety valve and second clutch safety valve are normally closed switch electromagnetic valve.
5. the described hydraulic control system for dual-clutch transmission of any one in 4 according to claim 1, it is characterized in that: described hydraulic control system also comprises the clutch cooling Proportional valve for the solenoidoperated cluthes cooling oil path, the 3-position-3-way solenoid valve of described clutch cooling Proportional valve for often opening.
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| Application Number | Priority Date | Filing Date | Title |
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| CN 201320277608 CN203239914U (en) | 2013-05-21 | 2013-05-21 | Hydraulic control system for automatic double-clutch speed changing box |
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| Application Number | Priority Date | Filing Date | Title |
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| CN 201320277608 CN203239914U (en) | 2013-05-21 | 2013-05-21 | Hydraulic control system for automatic double-clutch speed changing box |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104948729A (en) * | 2015-05-11 | 2015-09-30 | 合肥工业大学 | Electrohydraulic control system for seven-speed oppositely-arranged dual-clutch transmission |
| CN105736691A (en) * | 2014-12-11 | 2016-07-06 | 上海汽车集团股份有限公司 | Dual clutch transmission, hydraulic control system and control method for clutch engagement |
| CN106763722A (en) * | 2017-03-06 | 2017-05-31 | 同济大学 | Double-clutch automatic gearbox hydraulic system |
| CN108626270A (en) * | 2017-03-22 | 2018-10-09 | 徐工集团工程机械股份有限公司 | Hydraulic control system, control method and construction machinery gear box |
| CN109505973A (en) * | 2018-11-29 | 2019-03-22 | 陕西法士特齿轮有限责任公司 | A kind of hydraulic control system of automatic speed changer |
-
2013
- 2013-05-21 CN CN 201320277608 patent/CN203239914U/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105736691A (en) * | 2014-12-11 | 2016-07-06 | 上海汽车集团股份有限公司 | Dual clutch transmission, hydraulic control system and control method for clutch engagement |
| CN105736691B (en) * | 2014-12-11 | 2018-03-30 | 上海汽车集团股份有限公司 | The control method that clutch combines in a kind of double-clutch speed changer |
| CN104948729A (en) * | 2015-05-11 | 2015-09-30 | 合肥工业大学 | Electrohydraulic control system for seven-speed oppositely-arranged dual-clutch transmission |
| CN106763722A (en) * | 2017-03-06 | 2017-05-31 | 同济大学 | Double-clutch automatic gearbox hydraulic system |
| CN108626270A (en) * | 2017-03-22 | 2018-10-09 | 徐工集团工程机械股份有限公司 | Hydraulic control system, control method and construction machinery gear box |
| CN109505973A (en) * | 2018-11-29 | 2019-03-22 | 陕西法士特齿轮有限责任公司 | A kind of hydraulic control system of automatic speed changer |
| CN109505973B (en) * | 2018-11-29 | 2023-10-10 | 陕西法士特齿轮有限责任公司 | Hydraulic control system of automatic transmission |
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Address after: Hefei City, Anhui Province, 230022 East Road No. 176 Patentee after: Anhui Jianghuai Automobile Group Limited by Share Ltd Address before: Hefei City, Anhui Province, 230022 East Road No. 176 Patentee before: Anhui Jianghuai Automobile Co., Ltd. |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20131016 Termination date: 20190521 |