CN102913614B - Hydraulic control system of automatic gearshift automobile transmission - Google Patents
Hydraulic control system of automatic gearshift automobile transmission Download PDFInfo
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- CN102913614B CN102913614B CN201210407240.4A CN201210407240A CN102913614B CN 102913614 B CN102913614 B CN 102913614B CN 201210407240 A CN201210407240 A CN 201210407240A CN 102913614 B CN102913614 B CN 102913614B
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Abstract
The invention discloses a hydraulic control system of an automatic gearshift automobile transmission. The hydraulic control system of the automatic gearshift automobile transmission comprises an oil pump, a filter, a walking high-gear clutch hydraulic cylinder, a walking low-gear clutch hydraulic cylinder and a reverse gear clutch hydraulic cylinder, and also comprises a lubricating slide valve, a lubricating oil way and a cooling electromagnetic valve; a main switch electromagnetic valve is utilized to achieve switching between a parking gear and a driving gear; a reverse gear electromagnetic valve is utilized to achieve advancing between the driving gear and the reversing gear, and the reverse gear hydraulic slide valve is switched to achieve switching between a low gear and a high gear. According to the hydraulic control system of the automatic gearshift automobile transmission, a plurality of clutch hydraulic cylinders are utilized, and then clutch hydraulic cylinders are controlled by matching of the electromagnetic valves and a hydraulic valve, so that the clutch at each gear can be respectively controlled; and meanwhile, the hydraulic control system of the automatic gearshift automobile transmission also has the advantages of being simple in structure and convenient to control.
Description
Technical field
The invention belongs to automobile gearbox technical field, be specifically related to a kind of hydraulic control system of automatic gear automobile gearbox.
Background technique
Gearbox is the gear drive fixing or change output shaft and input shaft velocity ratio, gearbox on automobile is by changing velocity ratio, change the torsion of engine crankshaft, to adapt to starting to walk, accelerate, travel and overcoming under the different driving conditions such as different kinds of roads obstruction, to the needs driving net tractive force of wheel and speed of a motor vehicle difference to require, be one of topmost parts in automotive transmission.Current automatic gear automobile is not owing to generally having clutch between the engine and the gearbox, connection between them realizes by fluid torque converter, so not for the hydraulic control system of multi-clutch, and the effect one of fluid torque converter be transmit rotating speed and moment of torsion, two be make between motor and automatic transmission case be connected to become nonrigid to facilitate automatic transmission case automaitc shfit.But adopt fluid torque converter speed ratio change when starting to walk less, when high gear is run, energy loss is larger.If adopt multiple clutch to control each gear respectively, Hydraulic System Oil route can be caused again in complexity, be not easy to control.
Summary of the invention
In order to enable system adopt different clutches to control respectively to each gear, the invention provides the hydraulic control system that a kind of structure simply adopts the automatic gear automobile gearbox of multi-clutch.
Technological scheme of the present invention is as follows: a kind of hydraulic control system of automatic gear automobile gearbox, comprise oil pump (1), filter cleaner (2), walking high-gear clutch oil hydraulic cylinder (6), walking low regime clutch oil hydraulic cylinder (7) and reverse clutch oil hydraulic cylinder (3), it is characterized in that: the inlet port of described oil pump (1) is connected with filter cleaner (2), the outlet of this oil pump (1) is connected with the imported oil (19P) of main switch solenoid valve (19) with the filler opening (4P) of main switch hydrovalve (4) respectively, described main switch solenoid valve (19) is 2/2-way solenoid valve, the oil outlet (19B) of this main switch solenoid valve (19) is connected with the control mouth (4A) of main switch hydrovalve (4), the return opening (19T) of main switch solenoid valve (19) is communicated with fuel tank by oil pipe, described main switch hydrovalve (4) is 2/2-way hydrovalve, the oil outlet (4B) of this main switch hydrovalve (4) is connected with the filler opening (5P) of reverse gear solenoid valve (5), described reverse gear solenoid valve (5) is two position four-way solenoid valves, first oil outlet (5B1) of this reverse gear solenoid valve (5) is connected with first filler opening (10P1) of shuttle valve (10) with the filler opening (9P) of the low-grade pressure valve of walking (9) respectively, second oil outlet (5B2) of reverse gear solenoid valve (5) is connected with second filler opening (10P2) of shuttle valve (10) with the control mouth (11A) of reverse gear hydraulic efficiency slide valve (11) respectively, the return opening (5T) of this reverse gear solenoid valve (5) is communicated with fuel tank by oil pipe, the oil outlet (10B) of described shuttle valve (10) is connected with the filler opening (8P) of the high-grade pressure valve of walking (8), the oil outlet (9B) of the low-grade pressure valve of described walking (9) is connected with the filler opening (7P) of walking low regime clutch oil hydraulic cylinder (7), the return opening (9T) of the low-grade pressure valve (9) of this walking is communicated with fuel tank by oil pipe, the oil outlet (8B) of high-grade pressure valve (8) of walking is connected with the filler opening (11P) of reverse gear hydraulic efficiency slide valve (11), the return opening (8T) of the high-grade pressure valve (8) of this walking is communicated with fuel tank by oil pipe, described reverse gear hydraulic efficiency slide valve (11) is two four port valves, first oil outlet (11B1) of this reverse gear hydraulic efficiency slide valve (11) is connected with the filler opening (11B1) of reverse clutch oil hydraulic cylinder (3) with the filler opening (6P) of walking high-gear clutch oil hydraulic cylinder (6) respectively with the second oil outlet (11B2), the return opening (11T) of this reverse gear hydraulic efficiency slide valve (11) is communicated with fuel tank by oil pipe.
When adopting above hydraulic control system, by main switch solenoid valve, main switch hydrovalve is switched, thus can switch between park and driving shelves, when being in driving shelves, main oil pressure is through reverse gear solenoid valve, the switching of reverse gear solenoid valve can switch between low-regime clutch oil hydraulic cylinder and high-regime clutch oil hydraulic cylinder, reverse clutch oil hydraulic cylinder, the switching of reverse gear hydraulic efficiency slide valve can also be controlled by reverse gear solenoid valve, thus realize switching between high-regime clutch oil hydraulic cylinder and reverse clutch oil hydraulic cylinder.Control each gear respectively owing to have employed multiple clutch, enable the clutch of each gear adapt to different driving situation.The low-grade pressure valve of different clutch, high-grade pressure valve and Reverse range pressure valve are controlled by a reverse gear solenoid valve and a reverse gear hydraulic efficiency slide valve 11, and structure is simple.
The outlet of described oil pump (1) is also connected with the filler opening (15P) of pressure valve (15) with the filler opening (12P) of lubrication valve (12), described pressure valve (15) is 2/2-way pressure proportioning valve, the oil outlet (15B) of this pressure valve (15) is connected with the control mouth (12A) of lubrication valve (12), described lubrication valve (12) is two-bit triplet hydrovalve, the return opening (12T) of this lubrication valve (12) is connected with the inlet port of oil pump (1), the oil outlet (12B) of lubrication valve (12) is connected with the filler opening of cooler (14), the oil outlet of described cooler (14) is connected with the filler opening (16P) lubricating guiding valve (16) with the filler opening (22P) of cooling guiding valve (22) respectively, the oil outlet (16B) of this lubrication guiding valve (16) is connected with the filler opening (17P) of lubricating oil path (17), the control mouth (16A) of this lubrication guiding valve (16) is connected with the oil outlet (18B) of cooling electric magnet valve (18), and the return opening (16T) of lubrication guiding valve (16) is connected by the filler opening of oil pipe with oil pump (1), first oil outlet (22B1) of described cooling guiding valve (22) is connected with the cooling hydraulic fluid port of reverse clutch oil hydraulic cylinder (3) with the cooling hydraulic fluid port of walking low regime clutch oil hydraulic cylinder (7) respectively with the second oil outlet (22B2), the control mouth (22A) of this cooling guiding valve (22) is also connected with the oil outlet (18B) of cooling electric magnet valve (18), the filler opening of described cooling electric magnet valve (18) is connected with the oil outlet (4B) of main switch hydrovalve (4), the return opening (18T) of this cooling electric magnet valve (18) is communicated with fuel tank by oil pipe.After main oil pressure enters pressure valve, lubrication valve is controlled by pressure valve, main oil pressure enters cooler via lubrication valve, cooled hydraulic oil enters in lubrication guiding valve and cooling guiding valve again, the oil outlet 16B UNICOM of described lubrication guiding valve be the oil leab in gearbox, each axle offered, described cooling guiding valve is by cooling electromagnetic valve, and the cold oil flowed out from cooling guiding valve enters in walking low regime clutch oil hydraulic cylinder and reverse clutch oil hydraulic cylinder again.
Be provided with reduction valve (13) between the oil outlet (12B) of described lubrication valve (12) and the filler opening of cooler (14), this reduction valve (13) is connected with cooler (14) with lubrication valve (12) by oil pipe.The effect of reduction valve reduces the oil pressure of the hydraulic oil flowed out by lubrication guiding valve, makes the oil pressure of the hydraulic oil entering into cooler remain on a below fixed value, better protects cooler.
Need higher oil pressure to control when being switched to low-grade gear and reverse gear, be connected with accumulator (20) between the low-grade pressure valve of described walking (9) and walking low regime clutch oil hydraulic cylinder (7), between the high-grade pressure valve of described walking (8) and reverse gear hydraulic efficiency slide valve (11), be also connected with accumulator (20).
In order to better detect the pressure of hydraulic oil in hydraulic system, be provided with pressure transducer (21) at first oil outlet (5B1) of described reverse gear solenoid valve (5) and between the filler opening (9P) of the low-grade pressure valve of walking (9) and first filler opening (10P1) of shuttle valve (10), between second oil outlet (11B2) of described reverse gear hydraulic efficiency slide valve (11) and the filler opening (3P) of reverse clutch oil hydraulic cylinder (3), be also provided with pressure transducer (21).
The oil outlet of described oil pump (1) is connected with the filler opening of relief valve (23).
Beneficial effect: present invention uses multiple clutch hydraulic cylinder, is then controlled clutch hydraulic cylinder by the cooperation of solenoid valve and hydrovalve, and the clutch of each gear is controlled respectively, also has structure simple simultaneously, is convenient to the advantages such as control.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the embodiment of the present invention one.
Fig. 2 is the schematic diagram of the embodiment of the present invention two.
Embodiment
Below in conjunction with drawings and Examples, the invention will be further described.
Embodiment one: as shown in Figure 1, comprises oil pump 1, filter cleaner 2, reverse clutch oil hydraulic cylinder 3, main switch hydrovalve 4, reverse gear solenoid valve 5, walking high-gear clutch oil hydraulic cylinder 6, walking low regime clutch oil hydraulic cylinder 7, high-grade pressure valve 8 of walking, low-grade pressure valve 9 of walking, shuttle valve 10, reverse gear hydraulic efficiency slide valve 11, lubrication valve 12, reduction valve 13, cooler 14, pressure valve 15, lubrication guiding valve 16, lubricating oil path 17, cooling electric magnet valve 18, main switch solenoid valve 19, accumulator 20, pressure transducer 21, cooling guiding valve 22 and relief valve 23.The inlet port of described oil pump 1 is connected with filter cleaner 2, the oil outlet of oil pump 1 is connected with the filler opening of relief valve 23, the oil outlet of this oil pump 1 is connected with the imported oil 19P of main switch solenoid valve 19 with the filler opening 4P of main switch hydrovalve 4 respectively, described main switch solenoid valve 19 is 2/2-way solenoid valve, the oil outlet 19B of this main switch solenoid valve 19 is connected with the control mouth 4A of main switch hydrovalve 4, the return opening 19T of main switch solenoid valve 19 is communicated with fuel tank by oil pipe, described main switch hydrovalve 4 is 2/2-way hydrovalve, the oil outlet 4B of this main switch hydrovalve 4 is connected with the filler opening 5P of reverse gear solenoid valve 5, described reverse gear solenoid valve 5 is two position four-way solenoid valves, first oil outlet 5B1 of this reverse gear solenoid valve 5 is connected with the first filler opening 10P1 of shuttle valve 10 with the walking filler opening 9P of low-grade pressure valve 9 respectively, pressure transducer 21 is also provided with between first oil outlet 5B1 of described reverse gear solenoid valve 5 and the filler opening 9P of low-grade pressure valve 9 of walking and the first filler opening 10P1 of shuttle valve 10, second oil outlet 5B2 of reverse gear solenoid valve 5 is connected with the second filler opening 10P2 of shuttle valve 10 with the control mouth 11A of reverse gear hydraulic efficiency slide valve 11 respectively, the return opening 5T of this reverse gear solenoid valve 5 is communicated with fuel tank by oil pipe, the oil outlet 10B of described shuttle valve 10 is connected with the filler opening 8P of the high-grade pressure valve 8 of walking, in the present embodiment, be provided with 4 low-grade pressure valve 9 of walking and 4 walking low regime clutch oil hydraulic cylinders 7, the filler opening 9P of 4 low-grade pressure valve 9 of described walking is connected with the first oil outlet 5B1 of reverse gear solenoid valve 5 is parallel, the filler opening 7P of the oil outlet 9B of 4 low-grade pressure valve of described walking 9 walking low regime clutch oil hydraulic cylinder 7 described with 4 is respectively connected, accumulator 20 is also connected with between the oil outlet 9B of one of them low-grade pressure valve 9 of walking and the filler opening 7P of walking low regime clutch oil hydraulic cylinder 7, the return opening 9T of the low-grade pressure valve 9 of this walking is communicated with fuel tank by oil pipe, the oil outlet 8B of high-grade pressure valve 8 that walks is connected with the filler opening 11P of reverse gear hydraulic efficiency slide valve 11, accumulator 20 is also connected with between the oil outlet 8B of the high-grade pressure valve 8 of described walking and the filler opening 11P of reverse gear hydraulic efficiency slide valve 11, the return opening 8T of the high-grade pressure valve 8 of this walking is communicated with fuel tank by oil pipe, described reverse gear hydraulic efficiency slide valve 11 is two four port valves, first oil outlet 11B1 of this reverse gear hydraulic efficiency slide valve 11 and being connected with the filler opening 6P of walking high-gear clutch oil hydraulic cylinder 6, second oil outlet 11B2 of reverse gear hydraulic efficiency slide valve 11 is connected with the filler opening 3P of reverse clutch oil hydraulic cylinder 3, pressure transducer 21 is also provided with between second oil outlet 11B2 of described reverse gear the hydraulic efficiency slide valve 11 and filler opening 3P of reverse clutch oil hydraulic cylinder 3, the return opening 11T of this reverse gear hydraulic efficiency slide valve 11 is communicated with fuel tank by oil pipe.
As shown in Figure 1, the outlet of described oil pump 1 is also connected with the filler opening 15P of pressure valve 15 with the filler opening 12P of lubrication valve 12, described pressure valve 15 is 2/2-way pressure proportioning valve, the oil outlet 15B of this pressure valve 15 is connected with the control mouth 12A of lubrication valve 12, described lubrication valve 12 is two-bit triplet hydrovalve, the return opening 12T of this lubrication valve 12 is connected with the inlet port of oil pump 1, and the oil outlet 12B of lubrication valve 12 is connected through the filler opening of reduction valve 13 with cooler 14; The oil outlet of described cooler 14 is connected with the filler opening 16P lubricating guiding valve 16 with the filler opening 22P of cooling guiding valve 22 respectively, the oil outlet 16B of this lubrication guiding valve 16 is connected with the filler opening 17P of lubricating oil path 17, the control mouth 16A of this lubrication guiding valve 16 is connected with the oil outlet 18B of cooling electric magnet valve 18, and the return opening 16T of lubrication guiding valve 16 is connected by the filler opening of oil pipe with oil pump 1; First oil outlet 22B1 of described cooling guiding valve 22 is connected with the cooling hydraulic fluid port of reverse clutch oil hydraulic cylinder 3 with the cooling hydraulic fluid port of walking low regime clutch oil hydraulic cylinder 7 respectively with the second oil outlet 22B2, the control mouth 22A of this cooling guiding valve 22 is also connected with the oil outlet 18B of cooling electric magnet valve 18, the filler opening of described cooling electric magnet valve 18 is connected with the oil outlet 4B of main switch hydrovalve 4, and the return opening 18T of this cooling electric magnet valve 18 is communicated with fuel tank by oil pipe.
The working principle of the present embodiment is as follows:
Driving 1-4 shelves working condition: pressure oil out flows through the imported oil 19P of main switch solenoid valve 19 from the oil outlet of oil pump 1, the control mouth entering main switch hydrovalve 4 is flowed out again from the oil outlet of main switch solenoid valve 19, the main switch hydrovalve given 4 one control signals, pressure oil out flows through the oil outlet 4B of filler opening 4P to switch hydrovalve 4 of main switch hydrovalve 4 from the oil outlet of oil pump 1 simultaneously, give reverse gear solenoid valve 5 one control signals simultaneously, the pressure oil flowed out from the oil outlet 4B of switch hydrovalve 4 flows through the first oil outlet 5B1 of filler opening 5P to reverse gear solenoid valve 5 of reverse gear solenoid valve 5, give the low-grade pressure valve of corresponding walking 9 one control signals simultaneously, pressure oil out flows through the filler opening 9P of low-grade pressure valve 9 of walking from the first oil outlet 5B1 of reverse gear solenoid valve 5, flow into corresponding walking low regime clutch oil hydraulic cylinder 7 from the oil outlet 9B of the low-grade pressure valve 9 of walking again.
To drive a vehicle 5 grades of working conditions: pressure oil out flows through the imported oil 19P of main switch solenoid valve 19 from the oil outlet of oil pump 1, the control mouth entering main switch hydrovalve 4 is flowed out again from the oil outlet of main switch solenoid valve 19, the main switch hydrovalve given 4 one control signals, pressure oil out flows through the oil outlet 4B of filler opening 4P to switch hydrovalve 4 of main switch hydrovalve 4 from the oil outlet of oil pump 1 simultaneously, give reverse gear solenoid valve 5 one control signals simultaneously, the pressure oil flowed out from the oil outlet 4B of switch hydrovalve 4 flows through the second fuel-displaced 5B2 of filler opening 5P to reverse gear solenoid valve 5 of reverse gear solenoid valve 5, high-grade pressure valve of simultaneously walking 8 one control signals, pressure oil out flows through from the second fuel-displaced 5B2 of reverse gear solenoid valve 5 the filler opening 8P of high-grade the pressure valve 8 and control mouth 11A of reverse gear hydraulic efficiency slide valve 11 that walks, give reverse gear hydraulic efficiency slide valve 11 1 control signals, the filler opening 11P of reverse gear hydraulic efficiency slide valve 11 is entered into from the pressure oil of the filler opening 8P outflow of the high-grade pressure valve 8 of walking, the first oil outlet 11B1 again via reverse gear hydraulic efficiency slide valve 11 enters into walking high-gear clutch oil hydraulic cylinder 6.
Reverse gear working condition: pressure oil out flows through the imported oil 19P of main switch solenoid valve 19 from the oil outlet of oil pump 1, the control mouth entering main switch hydrovalve 4 is flowed out again from the oil outlet of main switch solenoid valve 19, the main switch hydrovalve given 4 one control signals, pressure oil out flows through the oil outlet 4B of filler opening 4P to switch hydrovalve 4 of main switch hydrovalve 4 from the oil outlet of oil pump 1 simultaneously, give reverse gear solenoid valve 5 one control signals simultaneously, the pressure oil flowed out from the oil outlet 4B of switch hydrovalve 4 flows through the second fuel-displaced 5B2 of filler opening 5P to reverse gear solenoid valve 5 of reverse gear solenoid valve 5, high-grade pressure valve of simultaneously walking 8 one control signals, pressure oil out flows through from the second fuel-displaced 5B2 of reverse gear solenoid valve 5 the filler opening 8P of high-grade the pressure valve 8 and control mouth 11A of reverse gear hydraulic efficiency slide valve 11 that walks, give reverse gear hydraulic efficiency slide valve 11 1 control signals, the filler opening 11P of reverse gear hydraulic efficiency slide valve 11 is entered into from the pressure oil of the filler opening 8P outflow of the high-grade pressure valve 8 of walking, the second oil outlet 11B2 again via reverse gear hydraulic efficiency slide valve 11 enters into reverse clutch oil hydraulic cylinder 3.
Park working condition: pressure oil out flows through the imported oil 19P of main switch solenoid valve 19 from the oil outlet of oil pump 1, the control mouth entering main switch hydrovalve 4 is flowed out again from the oil outlet of main switch solenoid valve 19, the main switch hydrovalve given 4 one control signals, main switch hydrovalve 4 is switched to closed state.
Lubrication, cooling work situation: pressure oil out flows through the filler opening 12P of lubrication the valve 12 and filler opening 15P of pressure valve 15 from the oil outlet of oil pump 1, give pressure valve 15 1 control signals simultaneously, the control mouth that the pressure oil flowed out from the oil outlet 15B of pressure valve 15 enters into lubrication valve 12 gives lubrication valve 12 1 control signals, the pressure oil flowed out from the oil outlet 12B of lubrication valve 12 enters into cooler 14 again through the decompression of reduction valve 13, the cold oil flowed out from cooler 14 enters into the filler opening 16P of lubrication the guiding valve 16 and filler opening 22P of cooling guiding valve 22.Pressure oil out flows through the imported oil 19P of main switch solenoid valve 19 from the oil outlet of oil pump 1 simultaneously, the control mouth entering main switch hydrovalve 4 is flowed out again from the oil outlet of main switch solenoid valve 19, the main switch hydrovalve given 4 one control signals, pressure oil out flows through the oil outlet 4B of filler opening 4P to switch hydrovalve 4 of main switch hydrovalve 4 from the oil outlet of oil pump 1 simultaneously, the pressure oil flowed out from the oil outlet 4B of switch hydrovalve 4 flows through the filler opening 18P of cooling electric magnet valve 18, the hydraulic oil flowed out from the oil outlet 18B of cooling electric magnet valve 18 enters into the control mouth 16A lubricating guiding valve 16, the control mouth 22A of cooling guiding valve 22, give lubrication guiding valve 16 and cooling guiding valve 22 1 control signals, the pressure oil flowed out from the oil outlet 16B of lubrication guiding valve 16 enters into lubricating oil path 17 from the filler opening 17P of lubricating oil path 17, the pressure oil flowed out from the oil outlet 22P of cooling guiding valve 22 enters into reverse clutch oil hydraulic cylinder 3 and walking low regime clutch oil hydraulic cylinder 7.
Embodiment two: the present embodiment is provided with 1 low-grade pressure valve 9 of walking and 1 walking low regime clutch oil hydraulic cylinder 7, the filler opening 9P of the low-grade pressure valve of described walking 9 is connected with the first oil outlet 5B1 of reverse gear solenoid valve 5 is capable, and the remaining part of the present embodiment is identical with embodiment one.
The foregoing is only preferred embodiment of the present invention; it is not restriction with the present invention; all any amendments done within the spirit and principles in the present invention, the equivalent quantity etc. replaced and improve as changed dial framework and benchmark post, all should be included within protection scope of the present invention.
Claims (6)
1. the hydraulic control system of an automatic gear automobile gearbox, comprise oil pump (1), filter cleaner (2), walking high-gear clutch oil hydraulic cylinder (6), walking low regime clutch oil hydraulic cylinder (7) and reverse clutch oil hydraulic cylinder (3), it is characterized in that: the inlet port of described oil pump (1) is connected with filter cleaner (2), the oil outlet of this oil pump (1) is connected with the filler opening (19P) of main switch solenoid valve (19) with the filler opening (4P) of main switch hydrovalve (4) respectively, described main switch solenoid valve (19) is 2/2-way solenoid valve, the oil outlet (19B) of this main switch solenoid valve (19) is connected with the control mouth (4A) of main switch hydrovalve (4), the return opening (19T) of main switch solenoid valve (19) is communicated with fuel tank by oil pipe, described main switch hydrovalve (4) is 2/2-way hydrovalve, the oil outlet (4B) of this main switch hydrovalve (4) is connected with the filler opening (5P) of reverse gear solenoid valve (5), described reverse gear solenoid valve (5) is two position four-way solenoid valves, first oil outlet (5B1) of this reverse gear solenoid valve (5) is connected with first filler opening (10P1) of shuttle valve (10) with the filler opening (9P) of the low-grade pressure valve of walking (9) respectively, second oil outlet (5B2) of reverse gear solenoid valve (5) is connected with second filler opening (10P2) of shuttle valve (10) with the control mouth (11A) of reverse gear hydraulic efficiency slide valve (11) respectively, the return opening (5T) of this reverse gear solenoid valve (5) is communicated with fuel tank by oil pipe, the oil outlet (10B) of described shuttle valve (10) is connected with the filler opening (8P) of the high-grade pressure valve of walking (8), the oil outlet (9B) of the low-grade pressure valve of described walking (9) is connected with the filler opening (7P) of walking low regime clutch oil hydraulic cylinder (7), the return opening (9T) of the low-grade pressure valve (9) of this walking is communicated with fuel tank by oil pipe, the oil outlet (8B) of high-grade pressure valve (8) of walking is connected with the filler opening (11P) of reverse gear hydraulic efficiency slide valve (11), the return opening (8T) of the high-grade pressure valve (8) of this walking is communicated with fuel tank by oil pipe, described reverse gear hydraulic efficiency slide valve (11) is two four port valves, first oil outlet (11B1) of this reverse gear hydraulic efficiency slide valve (11) is connected with the filler opening (3P) of reverse clutch oil hydraulic cylinder (3) with the filler opening (6P) of walking high-gear clutch oil hydraulic cylinder (6) respectively with the second oil outlet (11B2), the return opening (11T) of this reverse gear hydraulic efficiency slide valve (11) is communicated with fuel tank by oil pipe.
2. the hydraulic control system of a kind of automatic gear automobile gearbox according to claim 1, it is characterized in that: the oil outlet of described oil pump (1) is also connected with the filler opening (15P) of pressure valve (15) with the filler opening (12P) of lubrication valve (12), described pressure valve (15) is 2/2-way pressure proportioning valve, the oil outlet (15B) of this pressure valve (15) is connected with the control mouth (12A) of lubrication valve (12), described lubrication valve (12) is two-bit triplet hydrovalve, the return opening (12T) of this lubrication valve (12) is connected with the inlet port of oil pump (1), the oil outlet (12B) of lubrication valve (12) is connected with the filler opening of cooler (14), the oil outlet of described cooler (14) is connected with the filler opening (16P) lubricating guiding valve (16) with the filler opening (22P) of cooling guiding valve (22) respectively, the oil outlet (16B) of this lubrication guiding valve (16) is connected with the filler opening (17P) of lubricating oil path (17), the control mouth (16A) of this lubrication guiding valve (16) is connected with the oil outlet (18B) of cooling electric magnet valve (18), and the return opening (16T) of lubrication guiding valve (16) is connected by the filler opening of oil pipe with oil pump (1), first oil outlet (22B1) of described cooling guiding valve (22) is connected with the cooling hydraulic fluid port of reverse clutch oil hydraulic cylinder (3) with the cooling hydraulic fluid port of walking low regime clutch oil hydraulic cylinder (7) respectively with the second oil outlet (22B2), the control mouth (22A) of this cooling guiding valve (22) is also connected with the oil outlet (18B) of cooling electric magnet valve (18), the filler opening of described cooling electric magnet valve (18) is connected with the oil outlet (4B) of main switch hydrovalve (4), the return opening (18T) of this cooling electric magnet valve (18) is communicated with fuel tank by oil pipe.
3. the hydraulic control system of a kind of automatic gear automobile gearbox according to claim 2, it is characterized in that: be provided with reduction valve (13) between the oil outlet (12B) of described lubrication valve (12) and the filler opening of cooler (14), this reduction valve (13) is connected with cooler (14) with lubrication valve (12) by oil pipe.
4. the hydraulic control system of a kind of automatic gear automobile gearbox according to claim 1 or 2 or 3, it is characterized in that: be connected with accumulator (20) between the low-grade pressure valve of described walking (9) and walking low regime clutch oil hydraulic cylinder (7), between the high-grade pressure valve of described walking (8) and reverse gear hydraulic efficiency slide valve (11), be also connected with accumulator (20).
5. the hydraulic control system of a kind of automatic gear automobile gearbox according to claim 1, it is characterized in that: be provided with pressure transducer (21) at first oil outlet (5B1) of described reverse gear solenoid valve (5) and between the filler opening (9P) of the low-grade pressure valve of walking (9) and first filler opening (10P1) of shuttle valve (10), between second oil outlet (11B2) of described reverse gear hydraulic efficiency slide valve (11) and the filler opening (3P) of reverse clutch oil hydraulic cylinder (3), be also provided with pressure transducer (21).
6. the hydraulic control system of a kind of automatic gear automobile gearbox according to claim 1, is characterized in that: the oil outlet of described oil pump (1) is connected with the filler opening of relief valve (23).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201210407240.4A CN102913614B (en) | 2012-10-23 | 2012-10-23 | Hydraulic control system of automatic gearshift automobile transmission |
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| CN201210407240.4A CN102913614B (en) | 2012-10-23 | 2012-10-23 | Hydraulic control system of automatic gearshift automobile transmission |
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| CN102913614B true CN102913614B (en) | 2015-07-01 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2014156944A1 (en) * | 2013-03-29 | 2014-10-02 | アイシン・エィ・ダブリュ株式会社 | Hydraulic control device |
| CN106838292B (en) * | 2016-12-26 | 2018-06-05 | 湖北航天技术研究院特种车辆技术中心 | A kind of self shifter hydraulic control system |
| CN107061723A (en) * | 2017-05-11 | 2017-08-18 | 陕西法士特齿轮有限责任公司 | A kind of hydraulic control system of automatic speed changer |
| CN109114217A (en) * | 2017-06-22 | 2019-01-01 | 内蒙古欧意德发动机有限公司 | Shift hydraulic control system, speed changer and automobile |
| CN115182972A (en) * | 2022-06-07 | 2022-10-14 | 陕西法士特齿轮有限责任公司 | P2 architecture-based hybrid power automatic transmission and starting control method |
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| CN202851930U (en) * | 2012-10-23 | 2013-04-03 | 重庆赛特尔机械有限公司 | Hydraulic control system for gearbox of automatic-transmission automobile |
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| CN102913614A (en) | 2013-02-06 |
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