CN103398170A

CN103398170A - Hydraulic control system for parallel planetary gear train transmission of automobile

Info

Publication number: CN103398170A
Application number: CN2013103591371A
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: 2013-11-20
Anticipated expiration: 2033-08-19
Also published as: CN103398170B

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

Vehicle is the hydraulic control system of speed changer with parallel planet wheel

Technical field

The invention belongs to the hydraulic control system for transmission for vehicles, be specifically related to be a kind of for the vehicle parallel planet wheel, be the hydraulic control system of speed changer.

Background technique

Transmission for vehicles is divided into manual transmission and automatic transmission, and manual transmission is shifted gears by operation manually, 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 is generally realized with executive system by transmission electronic control unit (TCU) control gearshift is servo; Servo and the executive system of shifting gears can be divided into again electronic, pneumatic and hydraulic pressure three types, and what usually adopt at most is mainly hydraulic control system.In the servo and executive control system of hydraulic gear-shifting, according to control signal, servoelement and actuator's type, can be divided into again all-hydraulic control and the large class of electrichydraulic control two.All-hydraulic control refers to that control signal and servo implementation are all hydraulic way, owing to driver's operation intention, motor and vehicle operation state etc. all must being 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 be high, in the modern vehicle automatic shift control, no longer adopt; Electrichydraulic control is to realize automatic speed changing with the actuator that solenoid valve is controlled the gearshift executive system as servo control element, and what the most auto gearbox adopted is all this pattern.In the automatic speed changing electrohydraulic control system, according to the control mode of solenoid valve to gear shifting actuating mechanism actuator oil circuit, can be divided into again two types of direct control type and indirectly control formulas; Direct control type is, with proportional electromagnetic valve, the actuator oil circuit has been controlled to gearshift, its advantage is that system architecture is relatively simple, the gearshift precision is high, response is fast, shortcoming is that electromagnetic valve structure is complicated, manufacture cost is high, to magnetic valve performance and control accuracy require high, to the hydraulic oil pollution sensitivity, system failure rate is relatively high; The indirectly control formula is to utilize switching mode solenoid valve simple in structure or pwm switch type solenoid valve (PWM), by the control to the servo guiding valve, indirectly 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, low to magnetic valve performance and control accuracy requirement, 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, it is the hydraulic control system of speed changer for parallel planet wheel that the present invention proposes a kind of.

Vehicle comprises manual guiding valve 11 with the hydraulic control system that parallel planet wheel is speed changer; Three double-action rams, be respectively the first two-way cylinder 12, the second two-way cylinder 13 and the 3rd two-way cylinder 14; Four single-acting cylinders, be respectively unidirectional oil cylinder the 16, the 3rd unidirectional oil cylinder 17 of the first unidirectional oil cylinder 15, second and the 4th unidirectional oil cylinder 18; 29 logical guiding valves 19 of external control type; Two accumulators, be respectively the first accumulator 20 and the second accumulator 21; Three shuttle valves, be respectively the first shuttle valve 22, the second shuttle valve 23 and the 3rd shuttle valve 24; 25 logical guiding valves 25 of external control type; Two one-way valves, be respectively the first one-way valve 26 and the second one-way valve 37; 23 three-way electromagnetic valves of four external control types, be respectively the one 2 the 27, the 22 the 38, the 323 three-way electromagnetic valves 39 of 3 three-way electromagnetic valves of 3 three-way electromagnetic valves and the 423 three-way electromagnetic valves 40; 23 logical guiding valves of seven external control types, be 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; 23 logical sliding valve style interlock valve of two external control types, be respectively the first interlock valve 28 and the second interlock valve 29; Four internal controlling pulse-width modulation types (PWM) electromagnetic relief valve, be respectively the first relief valve 41, the second relief valve 42, the 3rd relief valve 43 and the 4th relief valve 44, restriction 45; High-pressure oil pipe 301, the oil pipe 302 that reverses gear, 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 being communicated with high-pressure oil pipe 301, and oil return inlet T is drain tap, and the first oil outlet A is being communicated with oil pipe 302, the second oil outlet B that reverse gear and is being communicated with forward gear oil pipe 303;

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

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

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

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

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

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

The hydraulic fluid port A of described the 3rd unidirectional oil cylinder 17 is being communicated with the first oil inlet P 1, the first hydraulic fluid port A of the second interlock valve 29, 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 3rd shuttle valve 24 simultaneously, and the oil inlet P of the 6th guiding valve 35 is being communicated with forward gear oil pipe 303; The control port X of the 6th guiding valve 35 is being 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 the 4th unidirectional oil cylinder 18 is being communicated with the second oil inlet P 2, the second hydraulic fluid port B of the second interlock valve 29, 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 3rd shuttle valve 24 simultaneously, and the oil inlet P of the 7th guiding valve 36 is being communicated with forward gear oil pipe 303; The control port X of the 7th guiding valve 36 is being 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 the 3rd shuttle valve 24 is being 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, the low pressure filter cleaner 2 of connecting between the filler opening A of oil pump 3 and oil groove 1, and the oil outlet B of oil pump 3 is being 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 being 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 also is being communicated with the filler opening A of cooler 6, the oil outlet B of cooler 6 is being communicated with the hydraulic fluid port A of the 3rd accumulator 7 and an end of oil pipe 101 simultaneously, the other end of oil pipe 101 is being communicated with an end and pressure regulation oil pipe 201 1 ends 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 the 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 being communicated with the oil inlet P of an end and the reduction valve 10 of pressure regulation oil pipe 201 simultaneously, and the oil outlet A of main pressure regulator valve 9 is being communicated with an end of pressure lubrication oil pipe 203; Described reduction valve 10 is the internal control formula pressure regulator valve that leaks, and the oil outlet A of reduction valve 10 is being communicated with an end of low pressure fuel pipe 202.

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

Useful technique effect 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) the 4 kinds of states that advance under controlling manually by manual guiding valve 11; By the different valve position combinations of each valve in hydraulic control and Executive Module (III), can make speed changer realize that 8 forward gears and 2 reverse gear, and can realize changing in the forward gear shift process preparatory function of gear;

2. hydraulic control system involved in the present invention, only the operation by manual guiding valve 11 just can make speed changer realize that 1 forward gear and 1 reverses gear, thereby speed changer is had make the function of vehicle " the emergent limping " when electronic control unit TCU total failure;

3. hydraulic control system involved in the present invention, by the voltage-regulation voltage-stabilization system, to each solenoid valve, provide the control oil pressure of pressure far below each actuator hlydro-cylinder working pressure, thereby solenoid valve is worked under lower pressure, guarantee servocontrol precision and reliability, also can make solenoid valve failure rate decrease;

4. the interlock valve 28 that arranges 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 that arranges 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 in the time of can avoiding TCU in shift process or part solenoid valve to lose efficacy, also can guarantee when TCU total failure that speed changer possesses " the emergent limping " function;

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

The 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, the 3rd one-way valve 5, cooler 6, the 3rd accumulator 7, the 5th relief valve 8, main pressure regulator valve 9, reduction valve 10, manual guiding valve 11, the first two-way cylinder 12, the second two-way cylinder 13, the 3rd two-way cylinder 14, the first unidirectional oil cylinder 15, the second unidirectional oil cylinder 16, the 3rd unidirectional oil cylinder 17, the 4th unidirectional oil cylinder 18, 29 logical guiding valves 19 of external control type, the first accumulator 20, the second accumulator 21, the first shuttle valve 22, the second shuttle valve 23, the 3rd shuttle valve 24, 25 logical guiding valves 25 of external control type, the first one-way valve 26, the one 23 three-way electromagnetic valves 27, the first interlock valve 28, the second interlock valve 29, 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, the 7th guiding valve 36, the second one-way valve 37, the 223 three-way electromagnetic valves 38, the 323 three-way electromagnetic valves 39, the 423 three-way electromagnetic valves 40, the first relief valve 41, the second relief valve 42, the 3rd relief valve 43, the 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, oil pipe 302 reverses gear, 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

Referring to Fig. 1, vehicle comprises manual guiding valve 11 with the hydraulic control system that parallel planet wheel is speed changer; Three double-action rams, be respectively the first two-way cylinder 12, the second two-way cylinder 13 and the 3rd two-way cylinder 14; Four single-acting cylinders, be respectively unidirectional oil cylinder the 16, the 3rd unidirectional oil cylinder 17 of the first unidirectional oil cylinder 15, second and the 4th unidirectional oil cylinder 18; 29 logical guiding valves 19 of external control type; Two accumulators, be respectively the first accumulator 20 and the second accumulator 21, and be the spring piston type accumulator; Three shuttle valves, be respectively the first shuttle valve 22, the second shuttle valve 23 and the 3rd shuttle valve 24; 25 logical guiding valves 25 of external control type; Two one-way valves, be respectively the first one-way valve 26 and the second one-way valve 37; 23 three-way electromagnetic valves of four external control types, be respectively the one 2 the 27, the 22 the 38, the 323 three-way electromagnetic valves 39 of 3 three-way electromagnetic valves of 3 three-way electromagnetic valves and the 423 three-way electromagnetic valves 40; 23 logical guiding valves of seven external control types, be 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; 23 logical sliding valve style interlock valve of two external control types, be respectively the first interlock valve 28 and the second interlock valve 29; Four internal controlling pulse-width modulation types (PWM) electromagnetic relief valve, be respectively the first relief valve 41, the second relief valve 42, the 3rd relief valve 43 and the 4th relief valve 44; Restriction 45; High-pressure oil pipe 301, the oil pipe 302 that reverses gear, forward gear oil pipe 303 and control oil pipe 304;

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

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

Embodiment 2

Referring to Fig. 2, vehicle comprises hydraulic oil supply system, voltage-regulation voltage-stabilization system and hydraulic control system with the hydraulic control system that parallel planet wheel is speed changer, and wherein the structure of hydraulic control system is with embodiment 1.Referring to Fig. 3, hydraulic oil supply system comprises oil pump 3, the low pressure filter cleaner 2 of connecting between the filler opening A of oil pump 3 and oil groove 1, and the oil outlet B of oil pump 3 is being 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 being 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 also is being communicated with the filler opening A of cooler 6, the oil outlet B of cooler 6 is being communicated with the hydraulic fluid port A of the 3rd accumulator 7 and an end of oil pipe 101 simultaneously, the other end of oil pipe 101 is being communicated with an end and pressure regulation oil pipe 201 1 ends 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 the 3rd accumulator 7 is the spring piston type accumulator.

Referring to 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 being communicated with the oil inlet P of an end and the reduction valve 10 of pressure regulation oil pipe 201 simultaneously, and the oil outlet A of main pressure regulator valve 9 is being communicated with an end of pressure lubrication oil pipe 203; Described reduction valve 10 is the internal control formula pressure regulator valve that leaks, and the oil outlet A of reduction valve 10 is being communicated with an end of low pressure fuel pipe 202.

Working principle of the present invention is as follows:

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

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

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

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

While by the R2 gear, changing to the R1 gear, the second relief valve 42 energisings, the first relief valve 41 outages, can interrupt R2 shelves power, realize the transmission of R1 shelves; By the R1 shelves, when the R2 shelves change to the P 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 the N position by the R position), the first oil inlet P 1 of manual guiding valve 11, the second oil inlet P 2 cut-offs of manual guiding valve 11, the first oil outlet A of manual guiding valve 11, the 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 forward gear oil pipe 303 by the oil return inlet T draining of manual guiding valve 11, the oil pressure of the control port X of 25 logical guiding valves 25 of external control type this moment, higher than the oil pressure in the oil pipe 302 that reverses gear, makes the first one-way valve 26 conductings, 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 25 logical guiding valves 25 of external control type passes through restriction 45 at first simultaneously, the oil outlet 26A of the filler opening 26P of the first one-way valve 26 and the first one-way valve 26, subsequently through the hydraulic fluid port A of the first shuttle valve 22, the first oil inlet P 1 of the first shuttle valve 22, oil pipe 302 reverses gear, the 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 25 logical guiding valves 25 of external control type are kept off by R, the first hydraulic fluid port A of the logical guiding valves 25 of 25 of external control types is communicated with the oil return inlet T of 25 logical guiding valves 25 of external control type and to the first hydraulic fluid port A draining of the first two-way cylinder 12, the oil inlet P of 25 logical guiding valves 25 of external control type is communicated with the second hydraulic fluid port B of 25 logical guiding valves 25 of external control type, the 3rd two-way cylinder 14 is in meta N, unreal incumbent what gear is preset, at this moment, the gear that the commutation of right position formation R1 and R2 is preset although the first two-way cylinder 12 still is in, the second two-way cylinder 13 still is in right position formation R1 and R2 is preset, but because the hydraulic fluid port A of the hydraulic fluid port A of the hydraulic fluid port A of the hydraulic fluid port A of the first unidirectional oil cylinder 15, the second unidirectional oil cylinder 16, the 3rd unidirectional oil cylinder 17, the 4th unidirectional oil cylinder 18 all is in the draining state, make it all to be in left position, thereby do not transmit any power, form neutral.

by neutral N, changed to while reversing gear R1, manual guiding valve 11 is placed in the R position of reversing gear (being allocated to the R position by the N position), it is preset that this moment, the first two-way cylinder 12 still was in right commutation that forms R1 shelves and R2 shelves, it is preset that the second two-way cylinder 13 still is in right gear that forms R1 shelves and R2 shelves, the first relief valve 41 outages, make 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 fuel feeding of the hydraulic fluid port A of the 4th guiding valve 33 to the first unidirectional oil cylinder 15, the piston of the first unidirectional oil cylinder 15 is moved to right, realize the transmission of R1 gear.

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

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

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

While by the D2 gear, changing to the D1 gear, the 3rd relief valve 43 outages, the first relief valve 41 outages, can interrupt D2 shelves power, realize the transmission of D1 shelves.

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

While by the D3 gear, changing to the D2 gear, the first relief valve 41 energisings, the 3rd relief valve 43 energisings, can interrupt D3 shelves power, realize the transmission of D2 shelves.

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

While by the D4 gear, changing to the D3 gear, the 3rd relief valve 43 outages, the first relief valve 41 outages, can interrupt D4 shelves power, realize the transmission of D3 shelves.

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

While by the D5 gear, changing to the D4 gear, the second relief valve 42 energisings, the 3rd relief valve 43 energisings, can interrupt D5 shelves power, realize the transmission of D4 shelves.

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

While by the D6 gear, changing to the D5 gear, the 4th relief valve 44 outages, the second relief valve 42 outages, can interrupt D6 shelves power, realize the transmission of D5 shelves.

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

While by the D7 gear, changing to the D6 gear, the second relief valve 42 energisings, the 4th relief valve 44 energisings, can interrupt D7 shelves power, realize the transmission of D6 shelves.

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

While by the D8 gear, changing to the D7 gear, the 4th relief valve 44 outages, the second relief valve 42 outages, can interrupt 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 broke down, 23 three-way electromagnetic valves of all external control types (27,38,39,40) and internal controlling pulse-width modulation type (PWM) electromagnetic relief valve (41,42,43,44) all were in off-position, at this moment, when manual guiding valve 11 is placed in the R position, the second manual guiding valve 11 first oil inlet P 1 of oil inlet P 2 UNICOMs and manual guiding valve 11 first oil outlet A of manual guiding valve 11, the second oil outlet B of manual guiding valve 11 and the cut-off of the oil return inlet T of manual guiding valve 11, the fluid of high-pressure oil pipe 301 is handled the second oil inlet P 2 of control slide valve 11, the 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 that reverses gear in oil pipe 302 is divided into 2 tunnels: a road makes the first shuttle valve 22 first oil inlet P 1 be communicated with the hydraulic fluid port A of the first shuttle valve 22 to the first oil inlet P 1 fuel feeding of the first shuttle valve 22 and passes through the control port X fuel feeding of 25 logical guiding valves 25 of 45 pairs of external control types of restriction, make 25 logical guiding valves 25 of external control type be in right position, the first hydraulic fluid port A of 25 logical guiding valves 25 of the oil inlet P of 25 logical guiding valves 25 of external control type and external control type is communicated with, 25 logical guiding valve 25 second hydraulic fluid port B of the second oil return inlet T 2 of 25 logical guiding valves 25 of external control type and external control type are communicated with, another road binders liquid makes the oil inlet P of the second one-way valve 37 be communicated with and make fluid enter forward gear oil pipe 303 with the oil outlet A of the second one-way valve 37 to the oil inlet P fuel feeding of the second one-way valve 37, fluid in forward gear oil pipe 303 is simultaneously to the oil inlet P of the first guiding valve 30, the oil inlet P fuel feeding of the oil inlet P of the second guiding valve 31 and 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 first hydraulic fluid port A fuel feeding of 25 logical guiding valve 25 first hydraulic fluid port A of the oil inlet P of 25 logical guiding valves 25 of external control type and external control type to the first two-way cylinder 12, make the commutation preset (commutation is put into gear) of the rodless cavity of the first two-way cylinder 12 oil-filled and its piston is moved to right realize to reverse gear R1 and R2 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, the first hydraulic fluid port A fuel feeding of the first hydraulic fluid port A1 of the first oil inlet P 1 of 29 logical guiding valves 19 of external control type and 29 logical guiding valves 19 of external control type to the second two-way cylinder 13, make the rodless cavity of the second two-way cylinder 13 oil-filled and its piston is moved to right realize reversing gear R1 and the R2 gear preset, fluid in forward gear oil pipe 303 is through the oil inlet P of the 4th guiding valve 33 and the 4th guiding valve 33 hydraulic fluid port A hydraulic fluid port A fuel feeding to the first unidirectional oil cylinder 15, make the first unidirectional oil cylinder 15 oil-filled and its piston is moved to right 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 broke down, 23 three-way electromagnetic valves of all external control types (27,38,39,40) and internal controlling pulse-width modulation type (PWM) electromagnetic relief valve (41,42,43,44) all were in off-position, at this moment, when manual guiding valve 11 is in the D position, the first oil inlet P 1 cut-off of manual guiding valve 11, the 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 are communicated with manual guiding valve 11 makes the control port X of 25 logical guiding valves 25 of external control type first simultaneously through restriction 45, the oil outlet A of the oil inlet P of the first one-way valve 26 and 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, oil pipe 302 reverses gear, the first oil outlet A of manual guiding valve 11 and the oil return inlet T oil extraction of manual guiding valve 11, make 25 logical guiding valves 25 of external control type be in left position, the second hydraulic fluid port B of 25 logical guiding valves 25 of the oil inlet P of 25 logical guiding valves 25 of external control type and external control type is communicated with, the second oil inlet P 2 and manual guiding valve 11 second oil outlet B that fluid in high-pressure oil pipe 301 is handled control slide valve 11 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 fuel feeding of the oil inlet P of the second guiding valve 31 and 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 second hydraulic fluid port B fuel feeding of 25 logical guiding valve 25 second hydraulic fluid port B of the oil inlet P of 25 logical guiding valves 25 of external control type and external control type to the first two-way cylinder 12, make the rod chamber of the first two-way cylinder 12 oil-filled and its piston is moved to left 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, the first hydraulic fluid port A fuel feeding of 29 logical guiding valve 19 first hydraulic fluid port A1 of the first oil inlet P 1 of 29 logical guiding valves 19 of external control type and external control type to the second two-way cylinder 13, make that the rodless cavity of the second two-way cylinder 13 is oil-filled and gear that its piston is moved to right realize forward gear D1 and D5 is preset, fluid in forward gear oil pipe 303 is through the hydraulic fluid port A of the oil inlet P of the 4th guiding valve 33 and the 4th guiding valve 33 hydraulic fluid port A fuel feeding to the first unidirectional oil cylinder 15, make the first unidirectional oil cylinder 15 oil-filled and its piston is moved to right realize the transmission of D1 gear.

Claims

1. vehicle is the hydraulic control system of speed changer with parallel planet wheel, it is characterized in that: comprise manual guiding valve (11); Three double-action rams, be respectively the first two-way cylinder (12), the second two-way cylinder (13) and the 3rd two-way cylinder (14); Four single-acting cylinders, be 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); 29 logical guiding valves (19) of external control type; Two accumulators, be respectively the first accumulator (20) and the second accumulator (21); Three shuttle valves, be respectively the first shuttle valve (22), the second shuttle valve (23) and the 3rd shuttle valve (24); 25 logical guiding valves (25) of external control type; Two one-way valves, be respectively the first one-way valve (26) and the second one-way valve (37); 23 three-way electromagnetic valves of four external control types, be respectively the one 23 three-way electromagnetic valves (27), the 223 three-way electromagnetic valves (38), the 323 three-way electromagnetic valves (39) and the 423 three-way electromagnetic valves (40); 23 logical guiding valves of seven external control types, be 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); 23 logical sliding valve style interlock valve of two external control types, be respectively the first interlock valve (28) and the second interlock valve (29); Four internal controlling pulse-width modulation types (PWM) electromagnetic relief valve, be 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, and its second oil inlet P 2 is being communicated with high-pressure oil pipe (301), and oil return inlet T is drain tap, and the first oil outlet A is being communicated with the oil pipe that reverses gear (302), and the second oil outlet B is being communicated with forward gear oil pipe (303);

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

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

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

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

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

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

The hydraulic fluid port A of described the 3rd unidirectional oil cylinder (17) is being communicated with the first oil inlet P 1, the first hydraulic fluid port A of the second interlock valve (29), 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 3rd shuttle valve (24) simultaneously, and the oil inlet P of the 6th guiding valve (35) is being communicated with forward gear oil pipe (303); The control port X of the 6th guiding valve (35) is being 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 the 4th unidirectional oil cylinder (18) is being communicated with the second oil inlet P 2, the second hydraulic fluid port B of the second interlock valve (29), 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 3rd shuttle valve (24) simultaneously, and the oil inlet P of the 7th guiding valve (36) is being communicated with forward gear oil pipe (303); The control port X of the 7th guiding valve (36) is being 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 the 3rd shuttle valve (24) is being communicated with the hydraulic fluid port A of the second accumulator (21).

2. vehicle according to claim 1 is the hydraulic control system of speed changer with parallel planet wheel, it is characterized in that: also comprise hydraulic oil supply system, described hydraulic oil supply system comprises oil pump (3), the low pressure filter cleaner (2) of connecting between the filler opening A of oil pump (3) and oil groove (1), the oil outlet B of oil pump (3) is being 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 being 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) also is being communicated with the filler opening A of cooler (6), the oil outlet B of cooler (6) is being communicated with the hydraulic fluid port A of the 3rd accumulator (7) and an end of oil pipe (101) simultaneously, the other end of oil pipe (101) is being communicated with an end and pressure regulation oil pipe (201) one ends 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. vehicle according to claim 1 and 2 is the hydraulic control system of speed changer with parallel planet wheel, it is characterized in that: also comprise the 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 being communicated with the oil inlet P of an end and the reduction valve (10) of pressure regulation oil pipe (201) simultaneously, and the oil outlet A of main pressure regulator valve (9) is being communicated with an end of pressure lubrication oil pipe (203); Described reduction valve (10) is the internal control formula pressure regulator valve that leaks, and the oil outlet A of reduction valve (10) is being communicated with an end of low pressure fuel pipe (202).

4. vehicle according to claim 1 is the hydraulic control system of speed changer with parallel planet wheel, it is characterized in that: described the first accumulator (20), the second accumulator (21) and the 3rd accumulator (7) are the spring piston type accumulator.