CN103398170B

CN103398170B - Hydraulic control system for parallel planetary gear train transmission of automobile

Info

Publication number: CN103398170B
Application number: CN201310359137.1A
Authority: CN
Inventors: 孙保群; 汪韶杰; 夏光; 李磊; 彭建刚; 盛楠; 王阳洋
Original assignee: HEFEI GONGDA AUTOMOBILE ENGINEERING TECHNOLOGY RESEARCH INSTITUTE Co Ltd; Hefei University of Technology
Current assignee: HEFEI GONGDA AUTOMOBILE ENGINEERING TECHNOLOGY RESEARCH INSTITUTE Co Ltd; Hefei University of Technology
Priority date: 2013-08-19
Filing date: 2013-08-19
Publication date: 2015-06-10
Anticipated expiration: 2033-08-19
Also published as: CN103398170A

Abstract

The invention relates to a hydraulic control system for a parallel planetary gear train transmission of an automobile. The hydraulic control system comprises a hand-controlled slide valve, three double-acting oil cylinders, four single-acting cylinders, an external control type two positions nine ports slide valve, two energy accumulators, three shuttle valves, an external control type two positions five ports slide valve, two check valves, four external control type two positions three ports electromagnetic valves, seven external control type two positions three ports slide valves, two external control type two positions three ports slide valve type interlock valves, four internal control type pulse-width modulation (PWM) type electromagnetic relief valves, a high-pressure oil pipe, a reverse gear oil pipe, a forward gear oil pipe and a control oil pipe. According to the invention, the transmission can be provided with four states: parking (P), reversing (R), neutral gear (N) and driving (D) through hand-controlled valve under manual control; through hydraulic control and combination of valve positions of different valves in an execution module (III), eight forward gears and two reverse gears of the transmission can be realized, the presetting of tap position change and limp functions of an automobile during the process of gear shifting of the forward gears are realized.

Description

The hydraulic control system of vehicle parallel planetary gear train transmission

Technical field

The invention belongs to the hydraulic control system for transmission for vehicles, what be specifically related to is a kind of hydraulic control system for vehicle parallel planetary gear train transmission.

Background technique

Transmission for vehicles is divided into manual transmission and automatic transmission, and manual transmission is shifted gears by manual hand manipulation, can not realize automatic gear change function; Automatic transmission can realize self shifter, is divided into several patterns such as automatic mechanical transmission (AMT), power gear shifting automatic transmission (AT), stepless speed variator (CVT) and dual-clutch transmission (DSG).At present, the automatic gear change function of automatic transmission generally controls indexing servo by transmission electronic control unit (TCU) and executive system realizes; Indexing servo and executive system can be divided into again electronic, pneumatic and hydraulic pressure three types, and the mainly hydraulic control system usually adopted at most.In hydraulic gear-shifting servo and executive control system, according to control signal, servoelement and actuator's type, all-hydraulic control and the large class of electrichydraulic control two can be divided into again.All-hydraulic control refers to that control signal and servo implementation are all hydraulic way, owing to driver's operation must be intended to, motor and vehicle operating status etc. be all converted to hydraulic pressure signal in order to control automatic speed changing, cause that system complex, control accuracy are low, low-response, rate of fault are high, no longer adopt in modern vehicle automatic shift control; Electrichydraulic control uses solenoid valve to control the actuator of gearshift executive system to realize automatic speed changing as servo control element, and what current most of auto gearbox adopted is all this pattern.In automatic speed changing electrohydraulic control system, according to the control mode of solenoid valve to gear shifting actuating mechanism actuator oil circuit, direct control type and indirect control formula two type can be divided into again; Direct control type has controlled gearshift with proportional electromagnetic valve to actuator oil circuit, its advantage is that system architecture is relatively simple, gearshift precision is high, response is fast, shortcoming is that electromagnetic valve structure is complicated, manufacture cost is high, it is high, responsive to hydraulic oil pollution to require magnetic valve performance and control accuracy, and system failure rate is relatively high; Indirect control formula utilizes the simple switching mode solenoid valve of structure or pwm switch type solenoid valve (PWM), by the control to servo guiding valve, indirect control actuator oil circuit completes gearshift, although its system parts is more, structure relative complex, control response are relatively slow, but electromagnetic valve structure used is simple, require low to magnetic valve performance and control accuracy, system is insensitive to hydraulic oil pollution, and system failure rate, manufacturing difficulty and cost are also relatively low.

Summary of the invention

In order to reduce gearshift of vehicle transmission hydraulic control system parts machining difficulty and manufacture cost, improve system reliability, the present invention proposes a kind of hydraulic control system for parallel planetary gear train transmission.

The hydraulic control system of vehicle parallel planetary gear train transmission comprises manual guiding valve 11; Three double-action rams, are respectively the first two-way cylinder 12, second two-way cylinder 13 and the 3rd two-way cylinder 14; Four single-acting cylinders, are respectively the unidirectional oil cylinder 16 of the first unidirectional oil cylinder 15, second, the 3rd unidirectional oil cylinder 17 and the 4th unidirectional oil cylinder 18; External control type 29 logical guiding valves 19; Two accumulators, are respectively the first accumulator 20 and the second accumulator 21; Three shuttle valves, are respectively the first shuttle valve 22, second shuttle valve 23 and the 3rd shuttle valve 24; External control type 25 logical guiding valves 25; Two one-way valves, are respectively the first one-way valve 26 and the second one-way valve 37; Four external control types, 23 three-way electromagnetic valves, are respectively the one 23 three-way electromagnetic valves the 27, the 223 three-way electromagnetic valves the 38, the 323 three-way electromagnetic valves 39 and the 423 three-way electromagnetic valves 40; Seven external control types, 23 logical guiding valves, are respectively the first guiding valve 30, second guiding valve 31, the 3rd guiding valve 32, the 4th guiding valve 33, the 5th guiding valve 34, the 6th guiding valve 35 and the 7th guiding valve 36; Two external control types, 23 logical sliding valve style interlock valve, are respectively the first interlock valve 28 and the second interlock valve 29; Four internal controlling pulse-width modulation type (PWM) electromagnetic relief valves, are respectively the first relief valve 41, second relief valve 42, the 3rd relief valve 43 and the 4th relief valve 44, restriction 45; High-pressure oil pipe 301, reverse gear oil pipe 302, forward gear oil pipe 303 and control oil pipe 304;

Described manual guiding valve 11 is 45 logical guiding valves, and its second oil inlet P 2 is communicated with high-pressure oil pipe 301, and oil return inlet T is drain tap, and the first oil outlet A is communicated with the oil pipe 302 that reverses gear, and the second oil outlet B is communicated with forward gear oil pipe 303;

The rodless cavity of described first two-way cylinder 12 is communicated with the first hydraulic fluid port A of external control type 25 logical guiding valves 25, its rod chamber is communicated with the second hydraulic fluid port B of external control type 25 logical guiding valves 25, the oil inlet P of external control type 25 logical guiding valves 25 is communicated with the hydraulic fluid port A of the first guiding valve 30, and the oil inlet P of the first guiding valve 30 is communicated with forward gear oil pipe 303; The control port X of the first guiding valve 30 is communicated with the hydraulic fluid port A of the 223 three-way electromagnetic valves 38, and the oil inlet P of the 223 three-way electromagnetic valves 38 is communicated with control oil pipe 304; Control oil pipe 304 is communicated with one end of low pressure fuel pipe 202;

The rodless cavity of described second two-way cylinder 13 is communicated with the first hydraulic fluid port A1 of external control type 29 logical guiding valves 19, its rod chamber is communicated with the second hydraulic fluid port B1 of external control type 29 logical guiding valves 19, first oil inlet P 1 of external control type 29 logical guiding valves 19 is communicated with the hydraulic fluid port A of the second guiding valve 31, and the oil inlet P of the second guiding valve 31 is communicated with forward gear oil pipe 303; The control port X of the second guiding valve 31 is communicated with the hydraulic fluid port A of the 323 three-way electromagnetic valves 39, and the oil inlet P of the 323 three-way electromagnetic valves 39 is communicated with control oil pipe 304;

The rodless cavity of described 3rd two-way cylinder 14 is communicated with the 3rd hydraulic fluid port A2 of external control type 29 logical guiding valves 19, its rod chamber is communicated with the 4th hydraulic fluid port B2 of external control type 29 logical guiding valves 19, second oil inlet P 2 of external control type 29 logical guiding valves 19 is communicated with the hydraulic fluid port A of the 3rd guiding valve 32, and the oil inlet P of the 3rd guiding valve 32 is communicated with forward gear oil pipe 303; The control port X of the 3rd guiding valve 32 is communicated with the hydraulic fluid port A of the 423 three-way electromagnetic valves 40, and the oil inlet P of the 423 three-way electromagnetic valves 40 is communicated with control oil pipe 304;

The control port X of described external control type 29 logical guiding valves 19 is communicated with the hydraulic fluid port A of the one 23 three-way electromagnetic valves 27 and the second oil inlet P 2 of the first shuttle valve 22 simultaneously, and the oil inlet P of the one 23 three-way electromagnetic valves 27 is communicated with control oil pipe 304; First oil inlet P 1 of the first shuttle valve 22 is communicated with the one end of the oil pipe 302 that reverses gear and the oil inlet P of the second one-way valve 37 simultaneously, the hydraulic fluid port A of the first shuttle valve 22 is communicated with the outlet A of the first one-way valve 26, and the hydraulic fluid port A of the first shuttle valve 22 is also communicated with the import P of the first one-way valve 26 and control port X of external control type 25 logical guiding valves 25 by restriction 45; The oil outlet A of described second one-way valve 37 is communicated with forward gear oil pipe 303;

The hydraulic fluid port A of described first unidirectional oil cylinder 15 is communicated with the first hydraulic fluid port A, the first control port X of the first interlock valve 28 and the hydraulic fluid port A of the 4th guiding valve 33 of the first oil inlet P 1, first interlock valve 28 of the second shuttle valve 23 simultaneously, and the oil inlet P of the 4th guiding valve 33 is communicated with forward gear oil pipe 303; The control port X of the 4th guiding valve 33 is communicated with oil inlet P and the control oil pipe 304 of the first relief valve 41 simultaneously;

The hydraulic fluid port A of described second unidirectional oil cylinder 16 is communicated with the second hydraulic fluid port B, the second control port Y of the first interlock valve 28 and the hydraulic fluid port A of the 5th guiding valve 34 of the second oil inlet P 2, first interlock valve 28 of the second shuttle valve 23 simultaneously, and the oil inlet P of the 5th guiding valve 34 is communicated with forward gear oil pipe 303; The control port X of the 5th guiding valve 34 is communicated with oil inlet P and the control oil pipe 304 of the second relief valve 42 simultaneously; The hydraulic fluid port A of described second shuttle valve 23 is communicated with the hydraulic fluid port A of the first accumulator 20;

The hydraulic fluid port A of described 3rd unidirectional oil cylinder 17 is communicated with the first hydraulic fluid port A, the first control port X of the second interlock valve 29 and the hydraulic fluid port A of the 6th guiding valve 35 of the first oil inlet P 1, second interlock valve 29 of the 3rd shuttle valve 24 simultaneously, and the oil inlet P of the 6th guiding valve 35 is communicated with forward gear oil pipe 303; The control port X of the 6th guiding valve 35 is communicated with oil inlet P and the control oil pipe 304 of the 3rd relief valve 43 simultaneously;

The hydraulic fluid port A of described 4th unidirectional oil cylinder 18 is communicated with the second hydraulic fluid port B, the second control port Y of the second interlock valve 29 and the hydraulic fluid port A of the 7th guiding valve 36 of the second oil inlet P 2, second interlock valve 29 of the 3rd shuttle valve 24 simultaneously, and the oil inlet P of the 7th guiding valve 36 is communicated with forward gear oil pipe 303; The control port X of the 7th guiding valve 36 is communicated with oil inlet P and the control oil pipe 304 of the 4th relief valve 44 simultaneously; The hydraulic fluid port A of described 3rd shuttle valve 24 is communicated with the hydraulic fluid port A of the second accumulator 21.

Also comprise hydraulic oil supply system, described hydraulic oil supply system comprises oil pump 3, filler opening A and the low pressure filter cleaner 2 of connecting between oil groove 1 of oil pump 3, and the oil outlet B of oil pump 3 is communicated with the import A of the high pressure filter 4 and import P of the 3rd one-way valve 5 simultaneously; The outlet B of described high pressure filter 4 is communicated with the outlet A of the 3rd the one-way valve 5 and import P of the 5th relief valve 8 simultaneously, and the oil return inlet T of the 5th relief valve 8 is communicated with oil groove 1; The outlet B of high pressure filter 4 is also communicated with the filler opening A of cooler 6, the oil outlet B of cooler 6 is communicated with the hydraulic fluid port A of the 3rd accumulator 7 and one end of oil pipe 101 simultaneously, the other end of oil pipe 101 is communicated with one end and pressure regulation oil pipe 201 one end of high-pressure oil pipe 301 simultaneously, and the other end of high-pressure oil pipe 301 is communicated with the oil inlet P 2 of setting about control slide valve 11.

Also comprise voltage-regulation voltage-stabilization system, described voltage-regulation voltage-stabilization system comprises main pressure regulator valve 9, described main pressure regulator valve 9 is 23 logical internal control sliding valve style pressure regulator valves, the oil inlet P of main pressure regulator valve 9 is communicated with one end of pressure regulation oil pipe 201 and the oil inlet P of reduction valve 10 simultaneously, and the oil outlet A of main pressure regulator valve 9 is communicated with one end of pressure lubrication oil pipe 203; Described reduction valve 10 to leak formula pressure regulator valve for internal control, and the oil outlet A of reduction valve 10 is communicated with one end of low pressure fuel pipe 202.

Described first accumulator 20, second accumulator 21 and the 3rd accumulator 7 are spring piston type accumulator.

Advantageous Effects of the present invention embodies in the following areas:

1. hydraulic control system involved in the present invention, can make speed changer have parking (P), reversing (R), neutral (N) and (D) 4 kinds of states of advancing by manual guiding valve 11 under controlling manually; Combined from the different valve position of each valve in Executive Module (III) by hydraulic control, speed changer can be made to realize 8 forward gears and 2 reverse gear, and the preparatory function changing to gear in forward gear shift process can be realized;

2. hydraulic control system involved in the present invention, the operation by means of only manual guiding valve 11 speed changer just can be made to realize 1 forward gear and 1 reverse gear, thus speed changer is had make the function of vehicle " emergent walk lamely " when electronic control unit TCU total failure;

3. hydraulic control system involved in the present invention, there is provided pressure far below the control oil pressure of each actuator hlydro-cylinder working pressure by voltage-regulation voltage-stabilization system to each solenoid valve, thus solenoid valve is worked at lower pressures guarantee servocontrol precision and reliability, solenoid valve failure rate also can be made significantly to reduce;

4. the interlock valve 28 arranged in the present invention can realize the action interlocking between the first unidirectional oil cylinder 15 and the second unidirectional oil cylinder 16, the interlock valve 29 arranged in the present invention can realize the action interlocking between the 3rd unidirectional oil cylinder 17 and the 4th unidirectional oil cylinder 18, gearshift misoperation when TCU or section solenoid valve lost efficacy in shift process can be avoided, also can guarantee speed-change apparatus standby " emergent limping " function when TCU total failure;

5. hydraulic control system involved in the present invention, add automatic shift control software in the transmission electronic control unit TCU for controlling four external control types, 23 three-way electromagnetic valves (27,38,39,40) and four internal controlling pulse-width modulation type electromagnetic relief valves (41,42,43,44) after, can realize speed changer 2 reverse gear between or automatic speed changing between 8 forward gears.

Accompanying drawing explanation

Fig. 1 is hydraulic pressure symbol basis schematic diagram of the present invention.

Fig. 2 is the hydraulic pressure symbol basis schematic diagram of the present invention with hydraulic oil supply system and voltage-regulation voltage-stabilization system.

Fig. 3 is the partial enlarged drawing of hydraulic oil supply system in Fig. 2.

Fig. 4 is the partial enlarged drawing of voltage-regulation voltage-stabilization system in Fig. 2.

Sequence number in upper figure: oil groove 1, low pressure filter cleaner 2, oil pump 3, high pressure filter 4, 3rd one-way valve 5, cooler 6, 3rd accumulator 7, 5th relief valve 8, main pressure regulator valve 9, reduction valve 10, manual guiding valve 11, first two-way cylinder 12, second two-way cylinder 13, 3rd two-way cylinder 14, first unidirectional oil cylinder 15, second unidirectional oil cylinder 16, 3rd unidirectional oil cylinder 17, 4th unidirectional oil cylinder 18, external control type 29 logical guiding valves 19, first accumulator 20, second accumulator 21, first shuttle valve 22, second shuttle valve 23, 3rd shuttle valve 24, external control type 25 logical guiding valves 25, first one-way valve 26, one 23 three-way electromagnetic valves 27, first interlock valve 28, second interlock valve 29, first guiding valve 30, second guiding valve 31, 3rd guiding valve 32, 4th guiding valve 33, 5th guiding valve 34, 6th guiding valve 35, 7th guiding valve 36, second one-way valve 37, 223 three-way electromagnetic valves 38, 323 three-way electromagnetic valves 39, 423 three-way electromagnetic valves 40, first relief valve 41, second relief valve 42, 3rd relief valve 43, 4th relief valve 44, restriction 45, oil pipe 101, pressure regulation oil pipe 201, low pressure fuel pipe 202, pressure lubrication oil pipe 203, high-pressure oil pipe 301, reverse gear oil pipe 302, forward gear oil pipe 303, control oil pipe 304.

Embodiment

Below in conjunction with accompanying drawing, by embodiment, the present invention is further described.

Embodiment 1

See Fig. 1, the hydraulic control system of vehicle parallel planetary gear train transmission comprises manual guiding valve 11; Three double-action rams, are respectively the first two-way cylinder 12, second two-way cylinder 13 and the 3rd two-way cylinder 14; Four single-acting cylinders, are respectively the unidirectional oil cylinder 16 of the first unidirectional oil cylinder 15, second, the 3rd unidirectional oil cylinder 17 and the 4th unidirectional oil cylinder 18; External control type 29 logical guiding valves 19; Two accumulators, are respectively the first accumulator 20 and the second accumulator 21, and are spring piston type accumulator; Three shuttle valves, are respectively the first shuttle valve 22, second shuttle valve 23 and the 3rd shuttle valve 24; External control type 25 logical guiding valves 25; Two one-way valves, are respectively the first one-way valve 26 and the second one-way valve 37; Four external control types, 23 three-way electromagnetic valves, are respectively the one 23 three-way electromagnetic valves the 27, the 223 three-way electromagnetic valves the 38, the 323 three-way electromagnetic valves 39 and the 423 three-way electromagnetic valves 40; Seven external control types, 23 logical guiding valves, are respectively the first guiding valve 30, second guiding valve 31, the 3rd guiding valve 32, the 4th guiding valve 33, the 5th guiding valve 34, the 6th guiding valve 35 and the 7th guiding valve 36; Two external control types, 23 logical sliding valve style interlock valve, are respectively the first interlock valve 28 and the second interlock valve 29; Four internal controlling pulse-width modulation type (PWM) electromagnetic relief valves, are respectively the first relief valve 41, second relief valve 42, the 3rd relief valve 43 and the 4th relief valve 44; Restriction 45; High-pressure oil pipe 301, reverse gear oil pipe 302, forward gear oil pipe 303 and control oil pipe 304;

The rodless cavity of described first two-way cylinder 12 is communicated with the first hydraulic fluid port A of external control type 25 logical guiding valves 25, its rod chamber is communicated with the second hydraulic fluid port B of external control type 25 logical guiding valves 25, the oil inlet P of external control type 25 logical guiding valves 25 is communicated with the hydraulic fluid port A of the first guiding valve 30, and the oil inlet P of the first guiding valve 30 is communicated with forward gear oil pipe 303; The control port X of the first guiding valve 30 is communicated with the oil outlet A of the 223 three-way electromagnetic valves 38, and the oil inlet P of the 223 three-way electromagnetic valves 38 is communicated with control oil pipe 304; Control oil pipe 304 is connected to one end of low pressure fuel pipe 202;

The oil outlet A of described 4th unidirectional oil cylinder 18 is communicated with the second oil outlet B, the second control port Y of the second interlock valve 29 and the hydraulic fluid port A of the 7th guiding valve 36 of the second oil inlet P 2, second interlock valve 29 of the 3rd shuttle valve 24 simultaneously, and the oil inlet P of the 7th guiding valve 36 is communicated with forward gear oil pipe 303; The control port X of the 7th guiding valve 36 is communicated with oil inlet P and the control oil pipe 304 of the 4th relief valve 44 simultaneously; The hydraulic fluid port A of described 3rd shuttle valve 24 is communicated with the hydraulic fluid port A of the second accumulator 21; First accumulator 20 and the second accumulator 21 are spring piston type accumulator.

Embodiment 2

See Fig. 2, the hydraulic control system of vehicle parallel planetary gear train transmission comprises hydraulic oil supply system, voltage-regulation voltage-stabilization system and hydraulic control system, and wherein the structure of hydraulic control system is with embodiment 1.See Fig. 3, hydraulic oil supply system comprises oil pump 3, filler opening A and the low pressure filter cleaner 2 of connecting between oil groove 1 of oil pump 3, and the oil outlet B of oil pump 3 is communicated with the import A of the high pressure filter 4 and import P of the 3rd one-way valve 5 simultaneously; The outlet B of described high pressure filter 4 is communicated with the outlet A of the 3rd the one-way valve 5 and import P of the 5th relief valve 8 simultaneously, and the oil return inlet T of the 5th relief valve 8 is communicated with oil groove 1; The outlet B of high pressure filter 4 is also communicated with the filler opening A of cooler 6, the oil outlet B of cooler 6 is communicated with the hydraulic fluid port A of the 3rd accumulator 7 and one end of oil pipe 101 simultaneously, the other end of oil pipe 101 is communicated with one end and pressure regulation oil pipe 201 one end of high-pressure oil pipe 301 simultaneously, and the other end of high-pressure oil pipe 301 is communicated with the oil inlet P 2 of setting about control slide valve 11; Described 3rd accumulator 7 is spring piston type accumulator.

See Fig. 4, described voltage-regulation voltage-stabilization system comprises main pressure regulator valve 9, described main pressure regulator valve 9 is 23 logical internal control sliding valve style pressure regulator valves, the oil inlet P of main pressure regulator valve 9 is communicated with one end of pressure regulation oil pipe 201 and the oil inlet P of reduction valve 10 simultaneously, and the oil outlet A of main pressure regulator valve 9 is communicated with one end of pressure lubrication oil pipe 203; Described reduction valve 10 to leak formula pressure regulator valve for internal control, and the oil outlet A of reduction valve 10 is communicated with one end of low pressure fuel pipe 202.

Working principle of the present invention is as follows:

When engine start and after entering normal idle running, each solenoid valve and guiding valve are in normality during engine idling operation, the normality of the one 23 three-way electromagnetic valves 27 is that power-off makes it be in left position, the hydraulic fluid port A of the one 23 three-way electromagnetic valves 27 is communicated with the oil return inlet T of the one 23 three-way electromagnetic valves 27, make the control port X of the logical guiding valves 19 of external control type 29 by the hydraulic fluid port A of the one 23 three-way electromagnetic valves 27 and oil return inlet T pressure release, external control type 29 logical guiding valves 19 are made to be in left position, make the control port X of the logical guiding valves 25 of external control type 25 can first simultaneously by restriction 45, the oil inlet P of the first one-way valve 26 and the oil outlet A of the first one-way valve 26, then by the hydraulic fluid port A of the first shuttle valve 22, second oil inlet P 2 of the first shuttle valve 22, the hydraulic fluid port A of the one 23 three-way electromagnetic valves 27 and oil return inlet T pressure release, external control type 25 logical guiding valves 25 are made to be in left position, the normality of the 223 three-way electromagnetic valves 38 is that energising makes it be in right position, the oil-feed port P of the oil return inlet T cut-off of the 223 three-way electromagnetic valves 38, the 223 three-way electromagnetic valves 38 is communicated with the hydraulic fluid port A of the 223 three-way electromagnetic valves 38, makes control oil pipe 304 make the first guiding valve 30 be in right position by the oil-feed port P of the 223 three-way electromagnetic valves 38 and hydraulic fluid port A to the control port X fuel feeding of the first guiding valve 30, the normality of the 323 three-way electromagnetic valves 39 is that energising makes it be in right position, the oil-feed port P of the oil return inlet T cut-off of the 323 three-way electromagnetic valves 39, the 323 three-way electromagnetic valves 39 is communicated with the hydraulic fluid port A of the 323 three-way electromagnetic valves 39, makes control oil pipe 304 make the second guiding valve 31 be in right position by the oil-feed port P of the 323 three-way electromagnetic valves 39 and hydraulic fluid port A to the control port X fuel feeding of the second guiding valve 31, the normality of the 423 three-way electromagnetic valves 40 is that energising makes it be in right position, the oil-feed port P of the oil return inlet T cut-off of the 423 three-way electromagnetic valves 40, the 423 three-way electromagnetic valves 40 is communicated with the hydraulic fluid port A of the 423 three-way electromagnetic valves 40, makes control oil pipe 304 make the 3rd guiding valve 32 be in right position by the oil-feed port P of the 423 three-way electromagnetic valves 40 and hydraulic fluid port A to the control port X fuel feeding of the 3rd guiding valve 32, the normality of the first relief valve 41 is energising, the oil inlet P of the first relief valve 41 is not communicated with the oil drain out T of the first relief valve 41, shunting pressure release can not be carried out to the next oily of control oil pipe 304, make control oil pipe 304 to the control port X fuel feeding of the 4th guiding valve 33 and make the 4th guiding valve 33 be in right position, the normality of the second relief valve 42 is energising, the oil inlet P of the second relief valve 42 is not communicated with the oil drain out T of the second relief valve 42, shunting pressure release can not be carried out to the next oily of control oil pipe 304, make control oil pipe 304 to the control port X fuel feeding of the 5th guiding valve 34 and make the 5th guiding valve 34 be in right position, the normality of the 3rd relief valve 43 is power-off, the oil inlet P of the 3rd relief valve 43 is communicated with oil drain out T, makes the oil drain out T pressure release of the next oily oil inlet P by the 3rd relief valve 43 of control oil pipe 304 and the 3rd relief valve 43 and make the 6th guiding valve 35 be in left position, the normality of the 4th relief valve 44 is power-off, the oil inlet P of the 4th relief valve 44 is communicated with the oil drain out T of the 4th relief valve 44, makes the oil drain out T pressure release of the next oily oil inlet P by the 4th relief valve 44 of control oil pipe 304 and the 4th relief valve 44 and make the 7th guiding valve 36 be in left position.

During parking, manual guiding valve 11 is placed in parking gear P position, manual first oil inlet P 1 of guiding valve 11, the second oil inlet P 2 of manual guiding valve 11 are ended, manual first oil outlet A of guiding valve 11 is communicated with the oil return inlet T of manual guiding valve 11 with the second oil outlet B of manual guiding valve 11, reverse gear oil pipe 302 and the forward gear oil pipe 303 oil return inlet T draining by manual guiding valve 11; First hydraulic fluid port A and the second hydraulic fluid port B of the first hydraulic fluid port A of the first hydraulic fluid port A of the first two-way cylinder 12 and the second hydraulic fluid port B, the second two-way cylinder 13 and the second hydraulic fluid port B, the 3rd two-way cylinder 14 are all in draining state ,thus be all in meta N, realize putting into gear without any gear, the hydraulic fluid port A of the first unidirectional oil cylinder 15, the hydraulic fluid port A of the second unidirectional oil cylinder 16, the hydraulic fluid port A of the 3rd unidirectional oil cylinder 17, the hydraulic fluid port A of the 4th unidirectional oil cylinder 18 is all in draining state makes it all to be in left position, does not transmit any power.

During reversing, manual guiding valve 11 is placed in R position of reversing gear (being allocated to R position by P position), manual first oil inlet P 1 of guiding valve 11, the second oil inlet P 2 of manual guiding valve 11 are communicated with the first oil outlet A of manual guiding valve 11, the second oil outlet B of manual guiding valve 11, the oil return inlet T cut-off of manual guiding valve 11, fluid from high-pressure oil pipe 301 handles the second oil inlet P 2 of control slide valve 11 and the first oil inlet P 1 of manual guiding valve 11, two-way is divided into: the first oil inlet P 1 of the first shuttle valve 22 is delivered on a road after first oil outlet A of manual guiding valve 11 and the oil pipe 302 that reverses gear, make the first oil inlet P 1 of the first shuttle valve 22 and the hydraulic fluid port A conducting of the first shuttle valve 22, and make external control type 25 logical guiding valves 25 be in right position through the hydraulic fluid port A of the first shuttle valve 22 and the control port X fuel feeding of restriction 45 pairs of external control types 25 logical guiding valves 25, the oil inlet P of external control type 25 logical guiding valves 25 is communicated with the first hydraulic fluid port A of external control type 25 logical guiding valves 25, the oil inlet P that the second one-way valve 37 is delivered on another road makes it conducting, and is delivered to the oil inlet P of the first guiding valve 30, second guiding valve 31, the 3rd guiding valve 32, the 4th guiding valve 33, the 5th guiding valve 34, the 6th guiding valve 35, the 7th guiding valve 36 through the oil outlet A of the second one-way valve 37, the hydraulic fluid port A that 223 three-way electromagnetic valve 38 power-off make the first left position of guiding valve 30, the oil inlet P of the first guiding valve 30 is communicated with the first guiding valve 30, fluid oil-filledly makes its piston move to right through the rodless cavity of the first hydraulic fluid port A to the first two-way cylinder 12 of the oil inlet P of the first guiding valve 30, the hydraulic fluid port A of the first guiding valve 30, the oil inlet P of external control type 25 logical guiding valves 25, the first hydraulic fluid port A of external control type 25 logical guiding valves 25 and the first two-way cylinder 12, the commutation preset (commutation is put into gear) of R1, R2 gear that realizes reversing gear, 323 three-way electromagnetic valve 39 power-off make the second left position of guiding valve 31, second guiding valve 31 oil inlet P is communicated with the hydraulic fluid port A of the second guiding valve 31, now the one 23 three-way electromagnetic valves 27 are normality, external control type 29 logical guiding valves 19 are in left position, first oil inlet P 1 of external control type 29 logical guiding valves 19 is communicated with the first hydraulic fluid port A1 of external control type 29 logical guiding valves 19, fluid is through the oil inlet P of the second guiding valve 31, the hydraulic fluid port A of the second guiding valve 31, first oil inlet P 1 of external control type 29 logical guiding valves 19, external control type 29 logical first hydraulic fluid port A1 of guiding valve 19 and oil-filled its piston that makes of the rodless cavity of the first hydraulic fluid port A to the second two-way cylinder 13 of the second two-way cylinder 13 move to right, realization is reversed gear R1, the gear of R2 is preset, first relief valve 41 power-off subsequently makes the oil inlet P of the first relief valve 41 be communicated with the oil return inlet T of the first relief valve 41 and make it to be in left position to the control port X pressure release of the 4th guiding valve 33, the oil inlet P of the 4th guiding valve 33 is communicated with the hydraulic fluid port A of the 4th guiding valve 33, fluid in forward gear oil pipe 303 is through the oil inlet P of the 4th guiding valve 33, the hydraulic fluid port A of the 4th guiding valve 33 is to the hydraulic fluid port A of the first unidirectional oil cylinder 15, first control port X of the first interlock valve 28 and the first oil inlet P 1 fuel feeding of the second shuttle valve 23, the piston of the first unidirectional oil cylinder 15 is moved to right, realize R1 and keep off transmission, the first interlock valve 28 is made to be in left position, second hydraulic fluid port B of the first interlock valve 28 is communicated with the oil return inlet T of the first interlock valve 28, second unidirectional oil cylinder 16 is in draining state thus locks it in left position, first oil inlet P 1 of the second shuttle valve 23 is communicated with the hydraulic fluid port A of the second shuttle valve 23, fluid can enter the first accumulator 20 when entering the first unidirectional oil cylinder 15 simultaneously thus produce buffer function to the oil pressure of the first unidirectional oil cylinder 15.

When changing to R2 gear by R1 gear, first relief valve 41 is energized, make the first relief valve 41 oil inlet P cut-off, make the oil return inlet T that control oil pipe 304 can make the 4th right position of guiding valve 33 to the control port X fuel feeding of the 4th guiding valve 33, the hydraulic fluid port A of the 4th guiding valve 33 is communicated with the 4th guiding valve 33, the fluid in the first unidirectional oil cylinder 15 makes its piston get back to left position through the oil return inlet T pressure release of the hydraulic fluid port A of the first unidirectional oil cylinder 15, the hydraulic fluid port A of the 4th guiding valve 33 and the 4th guiding valve 33, interrupts the transmission of R1 gear, afterwards, second relief valve 42 power-off, the oil inlet P of the second relief valve 42 is made to be communicated with the oil return inlet T of the second relief valve 42 and to make it to be in left position to the control port X pressure release of the 5th guiding valve 34, the oil inlet P of the 5th guiding valve 34 is communicated with the hydraulic fluid port A of the 5th guiding valve 34, fluid in forward gear oil pipe 303 is through the oil inlet P of the 5th guiding valve 34, the hydraulic fluid port A of the 5th guiding valve 34 is to the hydraulic fluid port A of the second unidirectional oil cylinder 16, second control port Y of the first interlock valve 28 and the second oil inlet P 2 fuel feeding of the second shuttle valve 23, the piston of the second unidirectional oil cylinder 16 is moved to right, realize R2 and keep off transmission, the first interlock valve 28 is made to be in right position, first hydraulic fluid port A of the first interlock valve 28 is communicated with the oil return inlet T of the first interlock valve 28, first unidirectional oil cylinder 15 is in draining state thus locks it in left position, the second oil inlet P 2 of the second shuttle valve 23 is made to be communicated with the hydraulic fluid port A of the second shuttle valve 23, fluid can enter the first accumulator 20 when entering the second unidirectional oil cylinder 16 simultaneously thus produce buffer function to the oil pressure of the second unidirectional oil cylinder 16.

By R2 keep off change to R1 keep off time, the second relief valve 42 is energized, the first relief valve 41 power-off, namely interruptible price R2 shelves power, realize the transmission of R1 shelves; When changing to P shelves by R1 shelves, R2 shelves, as long as control four 23 three-way electromagnetic valves (27,38,39,40) and four relief valves (41,42,43,44) return to normal.

During neutral, control four 23 three-way electromagnetic valves (27, 38, 39, 40) and four relief valves (41, 42, 43, 44) be normality, manual guiding valve 11 is placed in neutral N position (being allocated to N position by R position), the first oil inlet P 1 of manual guiding valve 11, second oil inlet P 2 of manual guiding valve 11 is ended, the first oil outlet A of manual guiding valve 11, second oil outlet B of manual guiding valve 11 is communicated with the oil return inlet T of manual guiding valve 11, reverse gear oil pipe 302 and the forward gear oil pipe 303 oil return inlet T draining by manual guiding valve 11, now the oil pressure of the control port X of external control type 25 logical guiding valves 25 is higher than the oil pressure reversed gear in oil pipe 302, makes the first one-way valve 26 conducting, the oil inlet P of the first one-way valve 26 is communicated with the oil outlet A of the first one-way valve 26, and the control port X of external control type 25 logical guiding valves 25 is first simultaneously through restriction 45, the filler opening 26P of the first one-way valve 26 and oil outlet 26A of the first one-way valve 26, subsequently through the hydraulic fluid port A of the first shuttle valve 22, first oil inlet P 1 of the first shuttle valve 22, reverse gear oil pipe 302, first oil outlet A of hand control valve 11, the oil return inlet T pressure release of manual guiding valve 11, left position is got back in right position when external control type 25 logical guiding valves 25 are kept off by R, first hydraulic fluid port A of external control type 25 logical guiding valves 25 is communicated with external control type 25 logical oil return inlet T of guiding valve 25 and the first hydraulic fluid port A draining to the first two-way cylinder 12, the oil inlet P of external control type 25 logical guiding valves 25 is communicated with the second hydraulic fluid port B of external control type 25 logical guiding valves 25, 3rd two-way cylinder 14 is in meta N, unreal what gear incumbent is preset, now, although the gear that commutation is preset, the second two-way cylinder 13 is still in right position formation R1 and R2 that the first two-way cylinder 12 is still in right position formation R1 and R2 is preset, but because of the hydraulic fluid port A of the first unidirectional oil cylinder 15, the second unidirectional oil cylinder 16 hydraulic fluid port A, the hydraulic fluid port A of the 3rd unidirectional oil cylinder 17, the hydraulic fluid port A of the 4th unidirectional oil cylinder 18 is all in draining state makes it all to be in left position, do not transmit any power thus form neutral.

By neutral N change to reverse gear R1 time, manual guiding valve 11 is placed in R position of reversing gear (being allocated to R position by N position), now the first two-way cylinder 12 is still in right position to form the commutation of R1 shelves and R2 shelves preset, the gear that second two-way cylinder 13 is still in right position formation R1 shelves and R2 shelves is preset, first relief valve 41 power-off, the oil inlet P of the first relief valve 41 is made to be communicated with the oil return inlet T of the first relief valve 41 and to make it to be in left position to the control port X pressure release of the 4th guiding valve 33, the oil inlet P of the 4th guiding valve 33 is communicated with the hydraulic fluid port A of the 4th guiding valve 33, fluid in forward gear oil pipe 303 is through the oil inlet P of the 4th guiding valve 33, the hydraulic fluid port A of the 4th guiding valve 33 is to the hydraulic fluid port A fuel feeding of the first unidirectional oil cylinder 15, the piston of the first unidirectional oil cylinder 15 is moved to right, realize R1 and keep off transmission.

When vehicle advances, manual guiding valve 11 is placed in forward gear D position (being allocated to D position by N position), first oil inlet P 1 of manual guiding valve 11 is ended, first oil outlet A of manual guiding valve 11 is communicated with the oil return inlet T of manual guiding valve 11, reverse gear oil pipe 302 draining, second oil inlet P 2 of manual guiding valve 11 is communicated with the second oil outlet B of manual guiding valve 11, high-pressure oil pipe 301 handles the second oil inlet P 2 of control slide valve 11, second oil outlet B of manual guiding valve 11, forward gear oil pipe 303 is to the first guiding valve 30, second guiding valve 31, 3rd guiding valve 32, 4th guiding valve 33, 5th guiding valve 34, 6th guiding valve 35, the oil inlet P fuel feeding of the 7th guiding valve 36, during D1 gear, the 223 three-way electromagnetic valve 38 power-off, make the first left position of guiding valve 30, the oil inlet P of the first guiding valve 30 is communicated with the hydraulic fluid port A of the first guiding valve 30, and the fluid in forward gear oil pipe 303 is through the oil inlet P of the first guiding valve 30, the hydraulic fluid port A of the first guiding valve 30, the oil inlet P of external control type 25 logical guiding valves 25, the rod chamber that second hydraulic fluid port B of external control type 25 logical guiding valves 25 and the first two-way cylinder 12 second hydraulic fluid port B enters the first two-way cylinder 12 makes its piston move to left, realize D1, D2, D5, the commutation preset (commutation is put into gear) of D6 gear, controls the 323 three-way electromagnetic valve 39 power-off simultaneously, makes the second left position of guiding valve 31, the oil inlet P of the second guiding valve 31 is communicated with the second guiding valve 31 hydraulic fluid port A, and the fluid in forward gear oil pipe 303 is through the oil inlet P of the second guiding valve 31, the hydraulic fluid port A of the second guiding valve 31, external control type 29 logical guiding valve 19 first oil inlet P 1, the rodless cavity that external control type 29 logical first hydraulic fluid port A1 of guiding valve 19 and the first hydraulic fluid port A of the second two-way cylinder 13 enter the second two-way cylinder 13 makes its piston move to right, realize D1, the gear preset (putting into gear) of D5 gear, after this, first relief valve 41 power-off makes the first relief valve 41 oil inlet P be communicated with the first relief valve 41 oil return inlet T, the 4th left position of guiding valve 33 is made to the control port X pressure release of the 4th guiding valve 33, 4th guiding valve 33 oil inlet P is communicated with the hydraulic fluid port A of the 4th guiding valve 33, fluid in forward gear oil pipe 303 is through the 4th guiding valve 33 oil inlet P, the hydraulic fluid port A of the 4th guiding valve 33 is to the hydraulic fluid port A of the first unidirectional oil cylinder 15, first control port X of the first interlock valve 28 and the first oil inlet P 1 fuel feeding of the second shuttle valve 23, first unidirectional oil cylinder 15 piston is moved to right, realize D1 and keep off transmission, the first interlock valve 28 is made to be in left position, second unidirectional oil cylinder 16 is in draining state thus locks it in left position, the first oil inlet P 1 of the second shuttle valve 23 is made to be communicated with the second shuttle valve 23 hydraulic fluid port A, fluid can enter the first accumulator 20 when entering the first unidirectional oil cylinder 15 simultaneously thus produce buffer function to the oil pressure of the first unidirectional oil cylinder 15.

When changing to neutral N by D1 gear, manual guiding valve 11 is placed in neutral N position (being allocated to N position by D position), first oil inlet P 1 of manual guiding valve 11, second oil inlet P 2 of manual guiding valve 11 is ended, first oil outlet A of manual guiding valve 11, second oil outlet B of manual guiding valve 11 is communicated with the oil return inlet T of manual guiding valve 11, reverse gear oil pipe 302 and the forward gear oil pipe 303 oil return inlet T draining by manual guiding valve 11, first unidirectional oil cylinder 15, second unidirectional oil cylinder 16, 3rd unidirectional oil cylinder 17, 4th unidirectional oil cylinder 18 is all in draining state and makes it all to be in left position, do not transmit any power thus form neutral.

When changing to D2 gear by D1 gear, one 23 three-way electromagnetic valve 27 power-off make external control type 29 logical left positions of guiding valve 19, second oil inlet P 2 of external control type 29 logical guiding valves 19 is communicated with the 3rd hydraulic fluid port A2 of external control type 29 logical guiding valves 19, 423 three-way electromagnetic valve 40 power-off make the 3rd left position of guiding valve 32, the oil inlet P of the 3rd guiding valve 32 is communicated with the hydraulic fluid port A of the 3rd guiding valve 32, in forward gear oil pipe 303, fluid is through the 3rd guiding valve 32 oil inlet P, the hydraulic fluid port A of the 3rd guiding valve 32, second oil inlet P 2 of external control type 29 logical guiding valves 19, the rodless cavity that external control type 29 logical 3rd hydraulic fluid port A2 of guiding valve 19 and the first hydraulic fluid port A of the 3rd two-way cylinder 14 enter the 3rd two-way cylinder 14 makes its piston move to right, realize D2, the gear of D6 gear is preset, afterwards, the oil return inlet T that first relief valve 41 energising makes the 4th right position of guiding valve 33, the hydraulic fluid port A of the 4th guiding valve 33 is communicated with the 4th guiding valve 33, first unidirectional oil cylinder 15 makes its piston move to left by the hydraulic fluid port A of the first unidirectional oil cylinder 15, the hydraulic fluid port A of the 4th guiding valve 33 and the 4th guiding valve 33 oil return inlet T pressure release, and D1 keeps off power interruption, subsequently, the hydraulic fluid port A that 3rd relief valve 43 energising makes the 6th right position of guiding valve 35, the oil inlet P of the 6th guiding valve 35 is communicated with the 6th guiding valve 35, in forward gear oil pipe 303, fluid enters the 3rd unidirectional oil cylinder 17 through the hydraulic fluid port A of the oil inlet P of the 6th guiding valve 35, the hydraulic fluid port A of the 6th guiding valve 35 and the 3rd unidirectional oil cylinder 17 its piston is moved to right, and realizes D2 and keeps off transmission, meanwhile, in forward gear oil pipe 303, fluid is through the oil inlet P of the 6th guiding valve 35, the hydraulic fluid port A of the 6th guiding valve 35 to the first control port X fuel feeding of the second interlock valve 29, makes the second interlock valve 29 be in left position, the 4th unidirectional oil cylinder 18 is in draining state thus locks it in left position.

By D2 keep off change to D1 keep off time, the 3rd relief valve 43 power-off, the first relief valve 41 power-off, namely interruptible price D2 shelves power, realize the transmission of D1 shelves.

When changing to D3 gear by D2 gear, one 23 three-way electromagnetic valve 27 energisings make external control type 29 logical right positions of guiding valve 19, first hydraulic fluid port A1 of external control type 29 logical guiding valves 19 is communicated with the first oil return inlet T 1 of external control type 29 logical guiding valves 19, first oil inlet P 1 of external control type 29 logical guiding valves 19 is communicated with the second hydraulic fluid port B1 of external control type 29 logical guiding valves 19, 323 three-way electromagnetic valve 39 power-off make the second left position of guiding valve 31, the oil inlet P of the second guiding valve 31 is communicated with the hydraulic fluid port A of the second guiding valve 31, in forward gear oil pipe 303, fluid is through the oil inlet P of the second guiding valve 31, the hydraulic fluid port A of the second guiding valve 31, first oil inlet P 1 of external control type 29 logical guiding valves 19, the rod chamber that external control type 29 logical second oil outlet B1 of guiding valve 19 and the second hydraulic fluid port B of the second two-way cylinder 13 enter the second two-way cylinder 13 makes its piston move to left, realize D3, the gear of D7 gear is preset, the oil return inlet T that 3rd relief valve 43 power-off makes the 6th left position of guiding valve 35, the hydraulic fluid port A of the 6th guiding valve 35 is communicated with the 6th guiding valve 35,3rd unidirectional oil cylinder 17 makes its piston move to left by the oil return inlet T pressure release of the hydraulic fluid port A of the 3rd unidirectional oil cylinder 17, the hydraulic fluid port A of the 6th guiding valve 35 and the 6th guiding valve 35, and D2 keeps off power interruption, first relief valve 41 power-off makes the hydraulic fluid port A that the oil inlet P of the first relief valve 41 is communicated with the oil return inlet T of the first relief valve 41, the control port X pressure release of the 4th guiding valve 33 makes the 4th left position of guiding valve 33, the oil inlet P of the 4th guiding valve 33 is communicated with the 4th guiding valve 33, fluid in forward gear oil pipe 303 moves to right to oil-filled its piston that makes of the first unidirectional oil cylinder 15 through the oil inlet P of the 4th guiding valve 33, the hydraulic fluid port A of the 4th guiding valve 33, the first unidirectional oil cylinder 15 hydraulic fluid port A, realizes D3 and keeps off transmission, meanwhile, in forward gear oil pipe 303, fluid is through the oil inlet P of the 4th guiding valve 33, the hydraulic fluid port A of the 4th guiding valve 33 to the first control port X fuel feeding of the first interlock valve 28, makes the first interlock valve 28 be in left position, the second unidirectional oil cylinder 16 is in draining state thus locks it in left position.

By D3 keep off change to D2 keep off time, the first relief valve 41 is energized, the 3rd relief valve 43 is energized, namely interruptible price D3 shelves power, realize the transmission of D2 shelves.

When changing to D4 gear by D3 gear, one 23 three-way electromagnetic valve 27 energisings make external control type 29 logical right positions of guiding valve 19, second oil inlet P 2 of external control type 29 logical guiding valves 19 is communicated with the 4th hydraulic fluid port B2 of external control type 29 logical guiding valves 19, 423 three-way electromagnetic valve 40 power-off make the 3rd left position of guiding valve 32, the oil inlet P of the 3rd guiding valve 32 is communicated with the hydraulic fluid port A of the 3rd guiding valve 32, in forward gear oil pipe 303, fluid is through the 3rd guiding valve 32 oil inlet P, 3rd guiding valve 32 hydraulic fluid port A, external control type 29 logical guiding valve 19 second oil inlet P 2, the rod chamber that external control type 29 logical 4th hydraulic fluid port B2 of guiding valve 19 and the second hydraulic fluid port B of the 3rd two-way cylinder 14 enter the 3rd two-way cylinder 14 makes its piston move to left, realize D4, the gear of D8 gear is preset, the oil return inlet T that first relief valve 41 energising makes the 4th right position of guiding valve 33, the hydraulic fluid port A of the 4th guiding valve 33 is communicated with the 4th guiding valve 33, first unidirectional oil cylinder 15 makes its piston move to left by hydraulic fluid port A, the 4th guiding valve 33 hydraulic fluid port A of the first unidirectional oil cylinder 15 and the oil return inlet T pressure release of the 4th guiding valve 33, and D3 keeps off power interruption, the hydraulic fluid port A that 3rd relief valve 43 energising makes the 6th right position of guiding valve 35, the oil inlet P of the 6th guiding valve 35 is communicated with the 6th guiding valve 35, in forward gear oil pipe 303, fluid enters the 3rd unidirectional oil cylinder 17 through the hydraulic fluid port A of the oil inlet P of the 6th guiding valve 35, the hydraulic fluid port A of the 6th guiding valve 35 and the 3rd unidirectional oil cylinder 17 its piston is moved to right, and realizes D4 and keeps off transmission, meanwhile, in forward gear oil pipe 303, fluid is through the oil inlet P of the 6th guiding valve 35, the hydraulic fluid port A of the 6th guiding valve 35 to the first control port X fuel feeding of the second interlock valve 29, makes the second interlock valve 29 be in left position, the 4th unidirectional oil cylinder 18 is in draining state thus locks it in left position.

By D4 keep off change to D3 keep off time, the 3rd relief valve 43 power-off, the first relief valve 41 power-off, namely interruptible price D4 shelves power, realize the transmission of D3 shelves.

When changing to D5 gear by D4 gear, one 23 three-way electromagnetic valve 27 power-off make external control type 29 logical left positions of guiding valve 19, first oil inlet P 1 of external control type 29 logical guiding valves 19 is communicated with the first hydraulic fluid port A1 of external control type 29 logical guiding valves 19, 323 three-way electromagnetic valve 39 power-off make the second left position of guiding valve 31, the oil inlet P of the second guiding valve 31 is communicated with the hydraulic fluid port A of the second guiding valve 31, in forward gear oil pipe 303, fluid is through the oil inlet P of the second guiding valve 31, the hydraulic fluid port A of the second guiding valve 31, first oil inlet P 1 of external control type 29 logical guiding valves 19, the rodless cavity that external control type 29 logical first hydraulic fluid port A1 of guiding valve 19 and the first hydraulic fluid port A of the second two-way cylinder 13 enter the second two-way cylinder 13 makes its piston move to right, realize D1, the gear of D5 gear is preset, the oil return inlet T that 3rd relief valve 43 power-off makes the 6th left position of guiding valve 35, the hydraulic fluid port A of the 6th guiding valve 35 is communicated with the 6th guiding valve 35,3rd unidirectional oil cylinder 17 makes its piston move to left by the oil return inlet T pressure release of the hydraulic fluid port A of the 3rd unidirectional oil cylinder 17, the hydraulic fluid port A of the 6th guiding valve 35 and the 6th guiding valve 35, and D4 keeps off power interruption, the hydraulic fluid port A that second relief valve 42 power-off makes the 5th left position of guiding valve 34, the oil inlet P of the 5th guiding valve 34 is communicated with the 5th guiding valve 34, in forward gear oil pipe 303, fluid enters the second unidirectional oil cylinder 16 through the hydraulic fluid port A of the oil inlet P of the 5th guiding valve 34, the hydraulic fluid port A of the 5th guiding valve 34 and the second unidirectional oil cylinder 16 its piston is moved to right, and realizes D5 and keeps off transmission, meanwhile, in forward gear oil pipe 303, fluid is through the oil inlet P of the 5th guiding valve 34, the hydraulic fluid port A of the 5th guiding valve 34 to the second control port Y fuel feeding of the first interlock valve 28, makes the first interlock valve 28 be in right position, the first unidirectional oil cylinder 15 is in draining state thus locks it in left position.

By D5 keep off change to D4 keep off time, the second relief valve 42 is energized, the 3rd relief valve 43 is energized, namely interruptible price D5 shelves power, realize the transmission of D4 shelves.

When changing to D6 gear by D5 gear, one 23 three-way electromagnetic valve 27 power-off make external control type 29 logical left positions of guiding valve 19, second oil inlet P 2 of external control type 29 logical guiding valves 19 is communicated with the 3rd hydraulic fluid port A2 of external control type 29 logical guiding valves 19, 423 three-way electromagnetic valve 40 power-off make the 3rd left position of guiding valve 32, the oil inlet P of the 3rd guiding valve 32 is communicated with the hydraulic fluid port A of the 3rd guiding valve 32, in forward gear oil pipe 303, fluid is through the 3rd guiding valve 32 oil inlet P, the hydraulic fluid port A of the 3rd guiding valve 32, second oil inlet P 2 of external control type 29 logical guiding valves 19, the rodless cavity that external control type 29 logical 3rd hydraulic fluid port A2 of guiding valve 19 and the first hydraulic fluid port A of the 3rd two-way cylinder 14 enter the 3rd two-way cylinder 14 makes its piston move to right, D2, it is preset that D6 realizes gear, the oil return inlet T that second relief valve 42 energising makes the 5th right position of guiding valve 34, the hydraulic fluid port A of the 5th guiding valve 34 is communicated with the 5th guiding valve 34, second unidirectional oil cylinder 16 makes its piston move to left by the oil return inlet T pressure release of the hydraulic fluid port A of the second unidirectional oil cylinder 16, the hydraulic fluid port A of the 5th guiding valve 34 and the 5th guiding valve 34, and D5 keeps off power interruption, the hydraulic fluid port A that 4th relief valve 44 energising makes the 7th right position of guiding valve 36, the oil inlet P of the 7th guiding valve 36 is communicated with the 7th guiding valve 36, in forward gear oil pipe 303, fluid enters the 4th unidirectional oil cylinder 18 through the hydraulic fluid port A of the oil inlet P of the 7th guiding valve 36, the hydraulic fluid port A of the 7th guiding valve 36 and the 4th unidirectional oil cylinder 18 its piston is moved to right, and realizes D6 and keeps off transmission, meanwhile, in forward gear oil pipe 303, fluid is through the oil inlet P of the 7th guiding valve 36, the hydraulic fluid port A of the 7th guiding valve 36 to the second control port Y fuel feeding of the second interlock valve 29, makes the second interlock valve 29 be in right position, the 3rd unidirectional oil cylinder 17 is in draining state thus locks it in left position.

By D6 keep off change to D5 keep off time, the 4th relief valve 44 power-off, the second relief valve 42 power-off, namely interruptible price D6 shelves power, realize the transmission of D5 shelves.

When changing to D7 gear by D6 gear, one 23 three-way electromagnetic valve 27 energisings make external control type 29 logical right positions of guiding valve 19, first oil inlet P 1 of external control type 29 logical guiding valves 19 is communicated with the second hydraulic fluid port B1 of external control type 29 logical guiding valves 19, 323 three-way electromagnetic valve 39 power-off make the second left position of guiding valve 31, the oil inlet P of the second guiding valve 31 is communicated with the hydraulic fluid port A of the second guiding valve 31, in forward gear oil pipe 303, fluid is through the oil inlet P of the second guiding valve 31, the hydraulic fluid port A of the second guiding valve 31, first oil inlet P 1 of external control type 29 logical guiding valves 19, the rod chamber that external control type 29 logical second hydraulic fluid port B1 of guiding valve 19 and the second hydraulic fluid port B of the second two-way cylinder 13 enter the second two-way cylinder 13 makes its piston move to left, realize D3, the gear of D7 gear is preset, the oil return inlet T that 4th relief valve 44 power-off makes the 7th left position of guiding valve 36, the hydraulic fluid port A of the 7th guiding valve 36 is communicated with the 7th guiding valve 36,4th unidirectional oil cylinder 18 makes its piston move to left by the oil return inlet T pressure release of the hydraulic fluid port A of the 4th unidirectional oil cylinder 18, the hydraulic fluid port A of the 7th guiding valve 36 and the 7th guiding valve 36, and D6 keeps off power interruption, the hydraulic fluid port A that second relief valve 42 power-off makes the 5th left position of guiding valve 34, the oil inlet P of the 5th guiding valve 34 is communicated with the 5th guiding valve 34, in forward gear oil pipe 303, fluid enters the second unidirectional oil cylinder 16 through the hydraulic fluid port A of the oil inlet P of the 5th guiding valve 34, the hydraulic fluid port A of the 5th guiding valve 34 and the second unidirectional oil cylinder 16 its piston is moved to right, and realizes D7 and keeps off transmission, meanwhile, in forward gear oil pipe 303, fluid is through the oil inlet P of the 5th guiding valve 34, the hydraulic fluid port A of the 5th guiding valve 34 to the second control port Y fuel feeding of the first interlock valve 28, makes the first interlock valve 28 be in right position, the first unidirectional oil cylinder 15 is in draining state thus locks it in left position.

By D7 keep off change to D6 keep off time, the second relief valve 42 is energized, the 4th relief valve 44 is energized, namely interruptible price D7 shelves power, realize the transmission of D6 shelves.

When changing to D8 gear by D7 gear, one 23 three-way electromagnetic valve 27 energisings make external control type 29 logical right positions of guiding valve 19, second oil inlet P 2 of external control type 29 logical guiding valves 19 is communicated with the 4th hydraulic fluid port B2 of external control type 29 logical guiding valves 19, 423 three-way electromagnetic valve 40 power-off make the 3rd left position of guiding valve 32, 3rd guiding valve 32 oil inlet P is communicated with the hydraulic fluid port A of the 3rd guiding valve 32, in forward gear oil pipe 303, fluid is through the 3rd guiding valve 32 oil inlet P, the hydraulic fluid port A of the 3rd guiding valve 32, second oil inlet P 2 of external control type 29 logical guiding valves 19, the rod chamber that external control type 29 logical 4th hydraulic fluid port B2 of guiding valve 19 and the second hydraulic fluid port B of the 3rd two-way cylinder 14 enter the 3rd two-way cylinder 14 makes its piston move to left, realize D4, the gear of D8 gear is preset, the oil return inlet T that second relief valve 42 energising makes the 5th right position of guiding valve 34, the hydraulic fluid port A of the 5th guiding valve 34 is communicated with the 5th guiding valve 34, second unidirectional oil cylinder 16 makes its piston move to left by the oil return inlet T pressure release of the hydraulic fluid port A of the second unidirectional oil cylinder 16, the hydraulic fluid port A of the 5th guiding valve 34 and the 5th guiding valve 34, and D7 keeps off power interruption, the hydraulic fluid port A that 4th relief valve 44 energising makes the 7th right position of guiding valve 36, the oil inlet P of the 7th guiding valve 36 is communicated with the 7th guiding valve 36, in forward gear oil pipe 303, fluid enters the 4th unidirectional oil cylinder 18 through the hydraulic fluid port A of the oil inlet P of the 7th guiding valve 36, the hydraulic fluid port A of the 7th guiding valve 36 and the 4th unidirectional oil cylinder 18 its piston is moved to right, and realizes D8 and keeps off transmission, meanwhile, in forward gear oil pipe 303, fluid is through the oil inlet P of the 7th guiding valve 36, the hydraulic fluid port A of the 7th guiding valve 36 to the second control port Y fuel feeding of the second interlock valve 29, makes the second interlock valve 29 be in right position, the 3rd unidirectional oil cylinder 17 is in draining state thus locks it in left position.

By D8 keep off change to D7 keep off time, the 4th relief valve 44 power-off, the second relief valve 42 power-off, namely interruptible price D8 shelves power, realize the transmission of D7 shelves.

Reversing gear under fail safe " emergent walk lamely " function: when motor and hydraulic work system normal, but when electronic control unit TCU breaks down, all external control types 23 three-way electromagnetic valves (27,38,39,40) and internal controlling pulse-width modulation type (PWM) electromagnetic relief valve (41,42,43,44) are all in off-position, now, when manual guiding valve 11 is placed in R position, manual guiding valve 11 first oil inlet P 1 of second oil inlet P 2 UNICOM of manual guiding valve 11 and manual guiding valve 11 first oil outlet A, second oil outlet B of manual guiding valve 11 and the oil return inlet T cut-off of manual guiding valve 11, the fluid of high-pressure oil pipe 301 handles the second oil inlet P 2 of control slide valve 11, first oil outlet A of manual guiding valve 11 first oil inlet P 1 and manual guiding valve 11 enters the oil pipe 302 that reverses gear, the fluid reversed gear in oil pipe 302 is divided into 2 tunnels: first oil inlet P 1 fuel feeding of a road to the first shuttle valve 22 is made the first shuttle valve 22 first oil inlet P 1 be communicated with the hydraulic fluid port A of the first shuttle valve 22 and led to the control port X fuel feeding of guiding valves 25 by restriction 45 pairs of external control types 25, external control type 25 logical guiding valves 25 are made to be in right position, first hydraulic fluid port A of oil inlet P and external control type 2 the 5 logical guiding valves 25 of external control type 25 logical guiding valves 25 is communicated with, the second oil return inlet T 2 and external control type 25 logical guiding valve 25 second hydraulic fluid port B of external control type 25 logical guiding valves 25 are communicated with, the oil inlet P fuel feeding of another road binders liquid to the second one-way valve 37 makes the oil inlet P of the second one-way valve 37 be communicated with the oil outlet A of the second one-way valve 37 and make fluid enter forward gear oil pipe 303, fluid in forward gear oil pipe 303 is simultaneously to the oil inlet P of the first guiding valve 30, the oil inlet P of the second guiding valve 31 and the oil inlet P fuel feeding of the 4th guiding valve 33, fluid in forward gear oil pipe 303 is through the oil inlet P of the first guiding valve 30, the hydraulic fluid port A of the first guiding valve 30, the oil inlet P of external control type 25 logical guiding valves 25 and external control type 25 logical guiding valve 25 first hydraulic fluid port A are to the first hydraulic fluid port A fuel feeding of the first two-way cylinder 12, make the rodless cavity of the first two-way cylinder 12 oil-filled and make its piston move to right realize reverse gear R1 and R2 gear commutation preset (commutation is put into gear), fluid in forward gear oil pipe 303 is through the oil inlet P of the second guiding valve 31, the hydraulic fluid port A of the second guiding valve 31, first oil inlet P 1 of external control type 29 logical guiding valves 19 and the first hydraulic fluid port A1 of external control type 29 logical guiding valves 19 are to the first hydraulic fluid port A fuel feeding of the second two-way cylinder 13, make the rodless cavity of the second two-way cylinder 13 oil-filled and make its piston realization R1 and R2 gear that reverses gear that moves to right preset, fluid in forward gear oil pipe 303 through the oil inlet P of the 4th guiding valve 33 and the 4th guiding valve 33 hydraulic fluid port A to the hydraulic fluid port A fuel feeding of the first unidirectional oil cylinder 15, make the first unidirectional oil cylinder 15 oil-filled and its piston moved to right to realize the transmission of R1 gear.

Forward gear under fail safe " emergent walk lamely " function: when motor and hydraulic work system normal, but when electronic control unit TCU breaks down, all external control types 23 three-way electromagnetic valves (27,38,39,40) and internal controlling pulse-width modulation type (PWM) electromagnetic relief valve (41,42,43,44) are all in off-position, now, when manual guiding valve 11 is in D position, first oil inlet P 1 of manual guiding valve 11 is ended, second oil inlet P 2 of manual guiding valve 11 is communicated with the second oil outlet B of manual guiding valve 11, the first oil outlet A that simultaneously manual guiding valve 11 oil return inlet T is communicated with manual guiding valve 11 makes the control port X of external control type 25 logical guiding valves 25 first simultaneously through restriction 45, the oil inlet P of the first one-way valve 26 and the oil outlet A of the first one-way valve 26, then through hydraulic fluid port A and first shuttle valve 22 first oil inlet P 1 of the first shuttle valve 22, reverse gear oil pipe 302, manual first oil outlet A of guiding valve 11 and the oil return inlet T oil extraction of manual guiding valve 11, external control type 25 logical guiding valves 25 are made to be in left position, second hydraulic fluid port B of oil inlet P and external control type 2 the 5 logical guiding valves 25 of external control type 25 logical guiding valves 25 is communicated with, fluid in high-pressure oil pipe 301 handles the second oil inlet P 2 of control slide valve 11 and manual guiding valve 11 second oil outlet B enters forward gear oil pipe 303, fluid in forward gear oil pipe 303 is simultaneously to the oil inlet P of the first guiding valve 30, the oil inlet P of the second guiding valve 31 and the oil inlet P fuel feeding of the 4th guiding valve 33, fluid in forward gear oil pipe 303 is through the first guiding valve 30 oil inlet P, the hydraulic fluid port A of the first guiding valve 30, the oil inlet P of external control type 25 logical guiding valves 25 and external control type 25 logical guiding valve 25 second hydraulic fluid port B are to the second hydraulic fluid port B fuel feeding of the first two-way cylinder 12, make the rod chamber of the first two-way cylinder 12 oil-filled and its piston moved to left to realize forward gear D1, D2, the commutation preset (commutation is put into gear) of D5 and D6 gear, fluid in forward gear oil pipe 303 is through the oil inlet P of the second guiding valve 31, the hydraulic fluid port A of the second guiding valve 31, first oil inlet P 1 of external control type 29 logical guiding valves 19 and external control type 29 logical guiding valve 19 first hydraulic fluid port A1 are to the first hydraulic fluid port A fuel feeding of the second two-way cylinder 13, make the rodless cavity of the second two-way cylinder 13 oil-filled and the gear its piston being moved to right realize forward gear D1 and D5 is preset, fluid in forward gear oil pipe 303 through the oil inlet P of the 4th guiding valve 33 and the hydraulic fluid port A of the 4th guiding valve 33 to the hydraulic fluid port A fuel feeding of the first unidirectional oil cylinder 15, make the first unidirectional oil cylinder 15 oil-filled and its piston moved to right to realize the transmission of D1 gear.

Claims

1. the hydraulic control system of vehicle parallel planetary gear train transmission, is characterized in that: comprise manual guiding valve (11); Three double-action rams, are respectively the first two-way cylinder (12), the second two-way cylinder (13) and the 3rd two-way cylinder (14); Four single-acting cylinders, are respectively the first unidirectional oil cylinder (15), the second unidirectional oil cylinder (16), the 3rd unidirectional oil cylinder (17) and the 4th unidirectional oil cylinder (18); External control type 29 logical guiding valves (19); Two accumulators, are respectively the first accumulator (20) and the second accumulator (21); Three shuttle valves, are respectively the first shuttle valve (22), the second shuttle valve (23) and the 3rd shuttle valve (24); External control type 25 logical guiding valves (25); Two one-way valves, are respectively the first one-way valve (26) and the second one-way valve (37); Four external control types, 23 three-way electromagnetic valves, are respectively the one 23 three-way electromagnetic valve (27), the 223 three-way electromagnetic valve (38), the 323 three-way electromagnetic valve (39) and the 423 three-way electromagnetic valve (40); Seven external control types, 23 logical guiding valves, are respectively the first guiding valve (30), the second guiding valve (31), the 3rd guiding valve (32), the 4th guiding valve (33), the 5th guiding valve (34), the 6th guiding valve (35) and the 7th guiding valve (36); Two external control types, 23 logical sliding valve style interlock valve, are respectively the first interlock valve (28) and the second interlock valve (29); Four internal controlling pulse-width modulation type (PWM) electromagnetic relief valves, are respectively the first relief valve (41), the second relief valve (42), the 3rd relief valve (43) and the 4th relief valve (44); High-pressure oil pipe (301), the oil pipe that reverses gear (302), forward gear oil pipe (303) and control oil pipe (304);

Described manual guiding valve (11) is 45 logical guiding valves, its second oil inlet P 2 is communicated with high-pressure oil pipe (301), oil return inlet T is drain tap, first oil outlet A is communicated with the oil pipe that reverses gear (302), and the second oil outlet B is communicated with forward gear oil pipe (303);

The rodless cavity of described first two-way cylinder (12) is communicated with the first hydraulic fluid port A of external control type 25 logical guiding valves (25), its rod chamber is communicated with the second hydraulic fluid port B of external control type 25 logical guiding valves (25), the oil inlet P of external control type 25 logical guiding valves (25) is communicated with the hydraulic fluid port A of the first guiding valve (30), and the oil inlet P of the first guiding valve (30) is communicated with forward gear oil pipe (303); The control port X of the first guiding valve (30) is communicated with the hydraulic fluid port A of the 223 three-way electromagnetic valve (38), and the oil inlet P of the 223 three-way electromagnetic valve (38) is communicated with control oil pipe (304); Control oil pipe (304) is communicated with one end of low pressure fuel pipe (202);

The rodless cavity of described second two-way cylinder (13) is communicated with the first hydraulic fluid port A1 of external control type 29 logical guiding valves (19), its rod chamber is communicated with the second hydraulic fluid port B1 of external control type 29 logical guiding valves (19), first oil inlet P 1 of external control type 29 logical guiding valves (19) is communicated with the hydraulic fluid port A of the second guiding valve (31), and the oil inlet P of the second guiding valve (31) is communicated with forward gear oil pipe (303); The control port X of the second guiding valve (31) is communicated with the hydraulic fluid port A of the 323 three-way electromagnetic valve (39), and the oil inlet P of the 323 three-way electromagnetic valve (39) is communicated with control oil pipe (304);

The rodless cavity of described 3rd two-way cylinder (14) is communicated with the 3rd hydraulic fluid port A2 of external control type 29 logical guiding valves (19), its rod chamber is communicated with the 4th hydraulic fluid port B2 of external control type 29 logical guiding valves (19), second oil inlet P 2 of external control type 29 logical guiding valves (19) is communicated with the hydraulic fluid port A of the 3rd guiding valve (32), and the oil inlet P of the 3rd guiding valve (32) is communicated with forward gear oil pipe (303); The control port X of the 3rd guiding valve (32) is communicated with the hydraulic fluid port A of the 423 three-way electromagnetic valve (40), and the oil inlet P of the 423 three-way electromagnetic valve (40) is communicated with control oil pipe (304);

The control port X of described external control type 29 logical guiding valves (19) is communicated with the hydraulic fluid port A of the one 23 three-way electromagnetic valve (27) and the second oil inlet P 2 of the first shuttle valve (22) simultaneously, and the oil inlet P of the one 23 three-way electromagnetic valve (27) is communicated with control oil pipe (304); First oil inlet P 1 of the first shuttle valve (22) is communicated with one end of the oil pipe that reverses gear (302) and the oil inlet P of the second one-way valve (37) simultaneously, and the hydraulic fluid port A of the first shuttle valve (22) is communicated with the hydraulic fluid port A of the first one-way valve (26) and the control port X of external control type 25 logical guiding valves (25) simultaneously;

The hydraulic fluid port A of described first unidirectional oil cylinder (15) is communicated with the first hydraulic fluid port A of the first oil inlet P 1, first interlock valve (28), the first control port X of the first interlock valve (28) of the second shuttle valve (23) and the hydraulic fluid port A of the 4th guiding valve (33) simultaneously, and the oil inlet P of the 4th guiding valve (33) is communicated with forward gear oil pipe (303); The control port X of the 4th guiding valve (33) is communicated with oil inlet P and the control oil pipe (304) of the first relief valve (41) simultaneously;

The hydraulic fluid port A of described second unidirectional oil cylinder (16) is communicated with the second hydraulic fluid port B of the second oil inlet P 2, first interlock valve (28), the second control port Y of the first interlock valve (28) of the second shuttle valve (23) and the hydraulic fluid port A of the 5th guiding valve (34) simultaneously, and the oil inlet P of the 5th guiding valve (34) is communicated with forward gear oil pipe (303); The control port X of the 5th guiding valve (34) is communicated with oil inlet P and the control oil pipe (304) of the second relief valve (42) simultaneously; The hydraulic fluid port A of described second shuttle valve (23) is communicated with the hydraulic fluid port A of the first accumulator (20);

The hydraulic fluid port A of described 3rd unidirectional oil cylinder (17) is communicated with the first hydraulic fluid port A of the first oil inlet P 1, second interlock valve (29), the first control port X of the second interlock valve (29) of the 3rd shuttle valve (24) and the hydraulic fluid port A of the 6th guiding valve (35) simultaneously, and the oil inlet P of the 6th guiding valve (35) is communicated with forward gear oil pipe (303); The control port X of the 6th guiding valve (35) is communicated with oil inlet P and the control oil pipe (304) of the 3rd relief valve (43) simultaneously;

The hydraulic fluid port A of described 4th unidirectional oil cylinder (18) is communicated with the second hydraulic fluid port B of the second oil inlet P 2, second interlock valve (29), the second control port Y of the second interlock valve (29) of the 3rd shuttle valve (24) and the hydraulic fluid port A of the 7th guiding valve (36) simultaneously, and the oil inlet P of the 7th guiding valve (36) is communicated with forward gear oil pipe (303); The control port X of the 7th guiding valve (36) is communicated with oil inlet P and the control oil pipe (304) of the 4th relief valve (44) simultaneously; The hydraulic fluid port A of described 3rd shuttle valve (24) is communicated with the hydraulic fluid port A of the second accumulator (21).

2. the hydraulic control system of vehicle parallel planetary gear train transmission according to claim 1, it is characterized in that: also comprise hydraulic oil supply system, described hydraulic oil supply system comprises oil pump (3), filler opening A and the low pressure filter cleaner (2) of connecting between oil groove (1) of oil pump (3), the oil outlet B of oil pump (3) is communicated with the import A of high pressure filter (4) and the import P of the 3rd one-way valve (5) simultaneously; The outlet B of described high pressure filter (4) is communicated with the outlet A of the 3rd one-way valve (5) and the import P of the 5th relief valve (8) simultaneously, and the oil return inlet T of the 5th relief valve (8) is communicated with oil groove (1); The outlet B of high pressure filter (4) is also communicated with the filler opening A of cooler (6), the oil outlet B of cooler (6) is communicated with the hydraulic fluid port A of the 3rd accumulator (7) and one end of oil pipe (101) simultaneously, the other end of oil pipe (101) is communicated with one end and pressure regulation oil pipe (201) one end of high-pressure oil pipe (301) simultaneously, and the other end of high-pressure oil pipe (301) is communicated with the oil inlet P 2 of setting about control slide valve (11).

3. the hydraulic control system of vehicle parallel planetary gear train transmission according to claim 1 and 2, it is characterized in that: also comprise voltage-regulation voltage-stabilization system, described voltage-regulation voltage-stabilization system comprises main pressure regulator valve (9), described main pressure regulator valve (9) is 23 logical internal control sliding valve style pressure regulator valves, the oil inlet P of main pressure regulator valve (9) is communicated with one end of pressure regulation oil pipe (201) and the oil inlet P of reduction valve (10) simultaneously, and the oil outlet A of main pressure regulator valve (9) is communicated with one end of pressure lubrication oil pipe (203); Described reduction valve (10) to leak formula pressure regulator valve for internal control, and the oil outlet A of reduction valve (10) is communicated with one end of low pressure fuel pipe (202).

4. the hydraulic control system of vehicle parallel planetary gear train transmission according to claim 2, is characterized in that: described first accumulator (20), the second accumulator (21) and the 3rd accumulator (7) are spring piston type accumulator.