CN101575978B - Pressure-speed mixed control shield propulsion hydraulic system - Google Patents
Pressure-speed mixed control shield propulsion hydraulic system Download PDFInfo
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- CN101575978B CN101575978B CN2009100992928A CN200910099292A CN101575978B CN 101575978 B CN101575978 B CN 101575978B CN 2009100992928 A CN2009100992928 A CN 2009100992928A CN 200910099292 A CN200910099292 A CN 200910099292A CN 101575978 B CN101575978 B CN 101575978B
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Abstract
The invention discloses a pressure-speed mixed control shield propulsion hydraulic system, comprising a three-position four-way directional control valve, three two-position three-way directional control valves, a proportional pressure reducing valve, a proportional speed regulating valve, two one-way valves, a cartridge valve, a relief valve, a pressure transducer and a hydraulic cylinder. The propulsion system adopts the proportional speed control valve to control the speed and the proportional pressure reducing valve to reduce the pressure; and the pressure and speed control mode can be switched in real time according to actual needs, thus satisfying the requirements of shield earth pressure balance and attitude control. The two-position three-way directional control valves are used forcontrolling the opening and closing of the cartridge valve port, thus being capable of realizing the working conditions of fast forwarding, quick returning and reliable locking, and improving the fle xibility of the system. The pressure-speed mixed control shield propulsion hydraulic control system can adapt to complex tunneling conditions in geological environment and is suitable for controlling the propelling movement of the shield tunneling equipment under various geological conditions.
Description
Technical field
The present invention relates to fluid pressure actuator, especially relate to the shield propulsion hydraulic system that a kind of pressure-speed mixes control.
Background technology
Shield propelling system is the important component part of shield excavation machine, is bearing the propelling task of whole shield excavation machine.Propulsion system not only can realize promoting the proal function of shield structure, and relevant complex task such as the curve that will finish the shield structure is advanced, correction and attitude control.Propulsion system can adapt to the variation of different construction stratum soil properties and water and soil pressure, export suitable propelling pressure and fltting speed and parameters such as shield structure front sealing cabin soil pressure, cutterhead rotating speed and deslagging speed are complementary, realize safe, fast, efficient driving jointly.
Adopt electro-hydraulic proportional valve can realize that the real-time continuous of hydraulic system pressure and speed parameter is adjustable.Thereby pressure control mode down can be realized the attitude control of shield driving by regulating the propulsion system pressure that respectively divides into groups, thereby speed control mode matches with the control of conveying worm rotating speed down and reaches excavation and casting Balance Control, keep the stabilising surface of excavation face, can satisfy shield driving better advancing the requirement of control.
Summary of the invention
The object of the present invention is to provide a kind of pressure-speed to mix the shield propulsion hydraulic system of control, adopt proportioning valve can realize that the real-time continuous of propulsion hydraulic system pressure and speed parameter is adjustable, to satisfy the need of work of propulsion system under the different geological environments.
The technical solution adopted in the present invention is:
The present invention includes: the hydraulic cylinder of three position four-way directional control valve, first two position three way directional control valve, second two position three way directional control valve, proportional pressure-reducing valve, proportional velocity regulating valve, first one way valve, cartridge valve, the 3rd two position three way directional control valve, second one way valve, overflow valve, pressure sensor, inbuilt displacement sensor; The oil inlet P 1 of three position four-way directional control valve links to each other with main in-line, oil return inlet T 1 links to each other with main oil return line, and oil-out A1 links to each other with the hydraulic cylinder rod chamber and the second one way valve oil-out B9 of first two position three way directional control valve oil inlet P 2 and inbuilt displacement sensor respectively with B1; First two position three way directional control valve oil-out A2 links to each other with cartridge valve oil-in A7 with second two position three way directional control valve oil inlet P 3 respectively with B2; Second two position three way directional control valve oil-out A3 links to each other with proportional pressure-reducing valve oil inlet P 4 with proportional velocity regulating valve oil inlet P 5 respectively with B3; Proportional velocity regulating valve oil-out T5 links to each other with the first one way valve oil-in A6 with proportional pressure-reducing valve oil-out T4; The first one way valve oil-out B6 all links to each other with the hydraulic cylinder rodless cavity of inbuilt displacement sensor with cartridge valve oil-out B7, the 3rd two position three way directional control valve oil-out A8, overflow valve oil inlet P 10 and pressure sensor; Cartridge valve control port K7 links to each other with the 3rd two position three way directional control valve oil inlet P 8; The 3rd two position three way directional control valve oil-out B8 links to each other with cartridge valve oil-in A7; Overflow valve oil-out T10 links to each other with the second one way valve oil-in A9.
The beneficial effect that the present invention has is:
1) adopts proportional velocity regulating valve to control the speed of PF cylinder pressure, make fltting speed accurately controlled, be easy to cooperate conveying worm to realize earth pressure balance control;
2) adopt proportional pressure-reducing valve to control the size of PF cylinder pressure power output, be easy to realize shield attitude coordination control;
3) adopt the action of cartridge valve group control hydraulic cylinder to lock, increased the flexibility of system with reliable;
4) adopt a direction valve on the working connection to cooperate the cartridge valve group of each hydraulic cylinder to realize that each PF cylinder pressure advances and rollback, significantly reduced the quantity that advances electromagnetic direction valve in the multi-cylinder system, improved the electric reliability of system.
Description of drawings
Accompanying drawing is the shield propulsion hydraulic system single cylinder control principle figure that pressure-speed mixes control among the present invention.
Among the figure: 1. three position four-way directional control valve, 2,3,8. two position three way directional control valve, 4. proportional pressure-reducing valve, 5. proportional velocity regulating valve, 6,9. one way valve, 7. cartridge valve, 10. overflow valve, 11. pressure sensors, the hydraulic cylinder of 12. inbuilt displacement sensors.
The specific embodiment
The invention will be further described below in conjunction with drawings and Examples.
As shown in drawings, the present invention includes: the hydraulic cylinder 12 of three position four-way directional control valve 1, first two position three way directional control valve 2, second two position three way directional control valve 3, proportional pressure-reducing valve 4, proportional velocity regulating valve 5, first one way valve 6, cartridge valve 7, the 3rd two position three way directional control valve 8, second one way valve 9, overflow valve 10, pressure sensor 11, inbuilt displacement sensor; The oil inlet P 1 of three position four-way directional control valve 1 links to each other with main in-line, oil return inlet T 1 links to each other with main oil return line, and oil-out A1 links to each other with hydraulic cylinder 12 rod chambers and second one way valve, the 9 oil-out B9 of first two position three way directional control valve 2 oil inlet P 2 and inbuilt displacement sensor respectively with B1; First two position three way directional control valve 2 oil-out A2 link to each other with cartridge valve 7 oil-in A7 with second two position three way directional control valve, 3 oil inlet P 3 respectively with B2; Second two position three way directional control valve 3 oil-out A3 links to each other with proportional pressure-reducing valve 4 oil inlet P 4 with proportional velocity regulating valve 5 oil inlet P 5 respectively with B3; Proportional velocity regulating valve 5 oil-out T5 link to each other with first one way valve, 6 oil-in A6 with proportional pressure-reducing valve 4 oil-out T4; First one way valve, 6 oil-out B6 all link to each other with hydraulic cylinder 12 rodless cavities of inbuilt displacement sensor with cartridge valve 7 oil-out B7, the 3rd two position three way directional control valve 8 oil-out A8, overflow valve 10 oil inlet P 10 and pressure sensor 11; Cartridge valve 7 control port K7 link to each other with the 3rd two position three way directional control valve 8 oil inlet P 8; The 3rd two position three way directional control valve 8 oil-out B8 link to each other with cartridge valve 7 oil-in A7; Overflow valve 10 oil-out T10 link to each other with second one way valve, 9 oil-in A9.
Operating principle of the present invention is as follows:
As shown in drawings, when the shield structure is pushed ahead, three position four-way directional control valve 1 left side electromagnet energising, working connection pressure oil enters through the P1 of three position four-way directional control valve 1 mouth, and the A1 mouth flows out to oil inlet P 2 and other group hydraulic cylinder control valve of propulsion system of two position three way directional control valve 2.
When two position three way directional control valve 2 electromagnet are switched on, be operated in position, a left side, pressure oil flow to the P3 mouth through P2 mouth, A2 mouth.
When two position three way directional control valve 3 electromagnet cut off the power supply, the pressure oil of P3 mouth enters hydraulic cylinder 12 rodless cavities of inbuilt displacement sensor through the B3 of two position three way directional control valve 3 mouth, proportional pressure-reducing valve 4, one way valve 6, the promotion hydraulic cylinder piston rod stretches out, and the shield structure is pushed ahead under pressure control mode.At this moment, the outage of two position three way directional control valve 8 electromagnet, cartridge valve 7 is in closed condition because of its control port K7 is communicated with hydraulic cylinder rodless cavity hydraulic oil through position, two position three way directional control valve 8 left side.
When two position three way directional control valve 3 electromagnet are switched on, the pressure oil of P3 mouth enters hydraulic cylinder 12 rodless cavities of inbuilt displacement sensor through two position three way directional control valve A3 mouth, proportional velocity regulating valve 5, one way valve 6, the promotion hydraulic cylinder piston rod stretches out, and the shield structure is pushed ahead under speed control mode.At this moment, the outage of two position three way directional control valve 8 electromagnet, cartridge valve 7 is in closed condition because of its control port K7 is communicated with hydraulic cylinder rodless cavity hydraulic oil through position, two position three way directional control valve 8 left side.
Under propelling pressure or speed control mode, can monitor shield structure propelling pressure and speed in real time by pressure sensor 11 and the displacement transducer that is built in hydraulic cylinder 12, thereby the signal of telecommunication is fed back to control system output appropriate signal control ratio valve.
The rod chamber of hydraulic cylinder 12 links to each other with the hydraulic fluid port B1 of three position four-way directional control valve 1 by pipeline, and when the shield structure was pushed ahead, the hydraulic oil of the rod chamber of hydraulic cylinder 12 connected main oil return line through hydraulic fluid port B1, the T1 of three position four-way directional control valve 1 and gets back to fuel tank.
In shield structure progradation, become big when load is unexpected, when causing hydraulic cylinder 12 rodless cavity pressure to raise suddenly, overflow valve 10 is opened.Meanwhile, the oil-out B6 that flow to one way valve 6 of the hydraulic oil in hydraulic cylinder 12 rodless cavities is cut off.Finally, the hydraulic oil in hydraulic cylinder 12 rodless cavities flows into fuel tank through overflow valve 10, one way valve 9, three position four-way directional control valve 1 to main oil return line, has realized under the sudden change load behavior defencive function to element.
When two position three way directional control valve 2 electromagnet cut off the power supply, be operated in right position, pressure oil flow to the A7 mouth through P2 mouth, B2 mouth, if two position three way directional control valve 8 electromagnet outage, cartridge valve 7 control port K7 are communicated with the hydraulic cylinder rodless cavity through position, two position three way directional control valve 8 left side, the hydraulic oil of A7 mouth is pushed spool open, enters hydraulic cylinder 12 rodless cavities from the hydraulic oil of working connection through cartridge valve 7, and hydraulic cylinder 12 is realized unloaded F.F. action; If two position three way directional control valve 8 electromagnet energising, cartridge valve 7 control port K7 are communicated with cartridge valve 7 oil-in A7 through two position three way directional control valve 8 right positions, the hydraulic oil of A7 mouth will flow to plug-in mounting spool top, because spool top and bottom product moment, spool is in closed condition, this moment, hydraulic cylinder 12 was failure to actuate, and the pressure oil that comes from the A1 hydraulic fluid port of three position four-way directional control valve 1 all flow in other group hydraulic cylinder control valve of propulsion system, thereby realized single group F.F. control of PF cylinder pressure, satisfied the needs of actual conditions such as single cylinder debugging.
When the shield segment assembling operation, PF cylinder pressure rollback, three position four-way directional control valve 1 the right electromagnet energising this moment, working connection pressure oil enters through the P1 of three position four-way directional control valve 1 mouth, and the B1 mouth flows out to hydraulic cylinder 12 and other group hydraulic cylinder rod chamber of propulsion system.
When the shield structure suspend to advance,, require the propulsion system can pressurize in order to keep the stable of the face that excavates.At this moment, all electromagnet outages of three position four-way directional control valve 1 are operated in meta, working connection pressure oil through the P1 mouth flow to, the T1 mouth flows out and gets back to fuel tank, makes system unloaded.The outage of two position three way directional control valve 8 electromagnet, cartridge valve 7 control port K7 are communicated with hydraulic cylinder 12 rodless cavities through position, two position three way directional control valve 8 left side, and rodless cavity hydraulic oil has certain pressure, will affact plug-in mounting spool top, because spool top and bottom product moment, spool is closed.Under the acting in conjunction of one way valve 6 and cartridge valve 7, hydraulic cylinder 12 rodless cavity hydraulic oil are realized reliable pressurize.
Claims (1)
1. a pressure-speed mixes the shield propulsion hydraulic system of controlling, and it is characterized in that comprising: the hydraulic cylinder (12) of three position four-way directional control valve (1), first two position three way directional control valve (2), second two position three way directional control valve (3), proportional pressure-reducing valve (4), proportional velocity regulating valve (5), first one way valve (6), cartridge valve (7), the 3rd two position three way directional control valve (8), second one way valve (9), overflow valve (10), pressure sensor (11), inbuilt displacement sensor; The oil inlet P 1 of three position four-way directional control valve (1) links to each other with main in-line, oil return inlet T 1 links to each other with main oil return line, oil-out A1 links to each other with first two position three way directional control valve (2) oil inlet P 2, and oil-out B1 links to each other with hydraulic cylinder (12) rod chamber and second one way valve (9) the oil-out B9 of inbuilt displacement sensor; First two position three way directional control valve (2) oil-out A2 links to each other with cartridge valve (7) oil-in A7 with second two position three way directional control valve (3) oil inlet P 3 respectively with B2; Second two position three way directional control valve (3) oil-out A3 links to each other with proportional pressure-reducing valve (4) oil inlet P 4 with proportional velocity regulating valve (5) oil inlet P 5 respectively with B3; Proportional velocity regulating valve (5) oil-out T5 links to each other with first one way valve (6) oil-in A6 with proportional pressure-reducing valve (4) oil-out T4; First one way valve (6) oil-out B6 all links to each other with hydraulic cylinder (12) rodless cavity of inbuilt displacement sensor with cartridge valve (7) oil-out B7, the 3rd two position three way directional control valve (8) oil-out A8, overflow valve (10) oil inlet P 10 and pressure sensor (11); Cartridge valve (7) control port K7 links to each other with the 3rd two position three way directional control valve (8) oil inlet P 8; The 3rd two position three way directional control valve (8) oil-out B8 links to each other with cartridge valve (7) oil-in A7; Overflow valve (10) oil-out T10 links to each other with second one way valve (9) oil-in A9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100992928A CN101575978B (en) | 2009-06-01 | 2009-06-01 | Pressure-speed mixed control shield propulsion hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100992928A CN101575978B (en) | 2009-06-01 | 2009-06-01 | Pressure-speed mixed control shield propulsion hydraulic system |
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| Publication Number | Publication Date |
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| CN101575978A CN101575978A (en) | 2009-11-11 |
| CN101575978B true CN101575978B (en) | 2011-05-04 |
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| CN2009100992928A Expired - Fee Related CN101575978B (en) | 2009-06-01 | 2009-06-01 | Pressure-speed mixed control shield propulsion hydraulic system |
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Families Citing this family (16)
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|---|---|---|---|---|
| CN101864965B (en) * | 2010-05-17 | 2012-08-08 | 浙江大学 | Pressure flow rate composite synchronization control energy-saving type shield propelling system |
| CN102278124B (en) * | 2011-06-24 | 2014-02-26 | 北京市三一重机有限公司 | Energy-saving hydraulic shield propulsion system |
| CN102562703A (en) * | 2011-11-18 | 2012-07-11 | 北京曙光航空电气有限责任公司 | Input-pressure-variable oil circuit structure of oil cylinder |
| CN102410821B (en) * | 2011-12-10 | 2013-10-23 | 中铁隧道装备制造有限公司 | Displacement detection method and device for shield over cutter |
| CN104033430B (en) * | 2014-06-05 | 2016-02-17 | 浙江大学 | Comply with the TBM Laboratory Furniture propulsion hydraulic system of sudden change load |
| CN105291471B (en) * | 2015-08-21 | 2017-03-01 | 浙江大学舟山海洋研究中心 | The fluid power system of the big stroke high velocity ram machine of heavy duty |
| CN105387009B (en) * | 2015-12-04 | 2018-06-08 | 天水锻压机床(集团)有限公司 | Motor-car stator numerical control dead slow speed pressurized hydraulic control system |
| CN106438582A (en) * | 2016-10-09 | 2017-02-22 | 上海市基础工程集团有限公司 | Protecting device of shield tunneling machine thrust hydraulic system |
| CN108035723B (en) * | 2017-12-30 | 2019-01-29 | 浙江大学 | Pressure tracking valve controls shield propulsion hydraulic system |
| CN108316936B (en) * | 2018-03-13 | 2019-06-25 | 中铁隧道局集团有限公司 | Shield machine fltting speed control device |
| CN108317119A (en) * | 2018-04-09 | 2018-07-24 | 徐州燕大传动与控制技术有限公司 | A kind of proportional multi-way valve that hydraulic control inlet and outlet throttling side can be separately adjustable |
| CN108999820A (en) * | 2018-08-27 | 2018-12-14 | 中国空气动力研究与发展中心高速空气动力研究所 | A kind of soft wall coordinated control system of wind-tunnel and method |
| CN108869438A (en) * | 2018-09-07 | 2018-11-23 | 中国铁建重工集团有限公司 | Double shield TBM and its featured oil cylinder control hydraulic system |
| CN110578529B (en) * | 2019-09-20 | 2021-02-09 | 上海隧道工程有限公司 | Shield tunneling machine excavation attitude vector self-adaptive adjustment method and system |
| CN111997949B (en) * | 2020-09-07 | 2022-08-26 | 中国铁建重工集团股份有限公司 | Passive hinge hydraulic control system and control method for shield tunneling machine |
| CN112814692B (en) * | 2021-01-19 | 2022-03-15 | 中铁工程装备集团有限公司 | Shield machine and posture deviation rectifying system thereof |
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