CN101503960B - Shield cutter head hydraulic system driven by multi-pump combination - Google Patents
Shield cutter head hydraulic system driven by multi-pump combination Download PDFInfo
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- CN101503960B CN101503960B CN2009100964082A CN200910096408A CN101503960B CN 101503960 B CN101503960 B CN 101503960B CN 2009100964082 A CN2009100964082 A CN 2009100964082A CN 200910096408 A CN200910096408 A CN 200910096408A CN 101503960 B CN101503960 B CN 101503960B
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- 230000001105 regulatory effect Effects 0.000 claims abstract description 5
- 230000002457 bidirectional effect Effects 0.000 claims abstract 21
- 239000002828 fuel tank Substances 0.000 claims description 23
- 230000008878 coupling Effects 0.000 claims description 10
- 238000010168 coupling process Methods 0.000 claims description 10
- 238000005859 coupling reaction Methods 0.000 claims description 10
- 238000006073 displacement reaction Methods 0.000 abstract description 52
- 238000000034 method Methods 0.000 abstract description 6
- 230000000694 effects Effects 0.000 abstract description 2
- 230000001276 controlling effect Effects 0.000 abstract 1
- 238000000926 separation method Methods 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 71
- 239000003921 oil Substances 0.000 description 30
- 239000002243 precursor Substances 0.000 description 11
- 238000005516 engineering process Methods 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 239000010720 hydraulic oil Substances 0.000 description 3
- 239000002689 soil Substances 0.000 description 3
- 238000004134 energy conservation Methods 0.000 description 2
- 239000011435 rock Substances 0.000 description 2
- 230000005641 tunneling Effects 0.000 description 2
- 238000009412 basement excavation Methods 0.000 description 1
- 230000003750 conditioning effect Effects 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
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Abstract
本发明涉及一种采用多泵组合驱动的盾构刀盘液压系统。本发明包括电机、比例变量泵、单向阀、先导溢流阀、调速阀、功率限制阀、比例溢流阀、二通插装阀、二位三通换向阀、三位四通换向阀、分油阀快、两点控制型双向变量马达。该系统中采用大排量主驱动比例变量泵组和小排量辅助驱动比例变量泵组组合驱动盾构刀盘运动，控制方式为电控比例变量。通过对比例泵组的排量控制可以实现刀盘在很宽范围连续调速。通过对两点控制型双向变量马达的排量控制，实现高低速档的切换。本发明装机功率适中，液压泵可灵活组合，正常工况下，单个液压泵的负载率高，可以提高动力源效率，增加可靠性，系统节能效果好。
The invention relates to a shield cutter head hydraulic system driven by multi-pump combination. The invention includes a motor, a proportional variable pump, a one-way valve, a pilot relief valve, a speed regulating valve, a power limiting valve, a proportional relief valve, a two-way cartridge valve, a two-position three-way reversing valve, a three-position four-way changeover Directional valve, fast oil separation valve, two-point control type bidirectional variable motor. In this system, the large-displacement main drive proportional variable pump unit and the small displacement auxiliary drive proportional variable pump unit are combined to drive the movement of the shield cutter head, and the control method is electronically controlled proportional variable. Continuous speed regulation of the cutter head in a wide range can be realized by controlling the displacement of the proportional pump group. Through the displacement control of the two-point control bidirectional variable motor, the switch between high and low gears is realized. The invention has moderate installed power, flexible combination of hydraulic pumps, high load rate of a single hydraulic pump under normal working conditions, can improve power source efficiency, increase reliability, and has good energy-saving effect of the system.
Description
Technical field
The invention belongs to field of mechanical technique, relate to fluid pressure actuator, relate in particular to the many pump combinations of a kind of employing shield-structured cutter head hydraulic system driven.
Background technology
Along with the development of modern society, the mankind develop the underground space more and more, and the demand of various construction of tunnel is had higher requirement to construction technology, have promoted the development of tunnel construction technology.Modern shield machine not only can be realized tunneling, and safety, driving speed is fast, automaticity is high, can be applied in the tunnelling of all kinds of soil properties and soft rock strata.Along with development in science and technology and social progress, shield driving will progressively replace conventional method.
Cutter-devices system is that shield excavation machine is finished the important component part of excavating function, drives the soil body that cutterhead rotates cutting shield structure the place ahead.At present, cutter-devices system is a kind of typically high-power, multi executors system.Because geological conditions is complicated and changeable in tunneling process, cutter-devices system must satisfy the needs of various stratum driving from the weak soil to the hard rock, and the rotation speed change scope is very big.Variable pump-variable displacement motor volume speed-modulating loop combines variable pump and variable displacement motor, continuous speed adjustment in wide range.At present, generally adopted this Hydraulic Adjustable Speed loop in the world, normally several big discharge capacity variable pumps are united several variable displacement motors of driving, by automatically controlled or hydraulic control proportional technique centralized Control, become the change discharge capacity control of discharge capacity, the control of permanent power and each motor when realizing each pump.The characteristics of this drive scheme are that the element of hydraulic system is few, control is simple, but power source efficient is lower.And adopt main driving pump and assistive drive pump assembly power source, and although it is complicated that control is gone up, can reduce the component purchase cost, improve power source efficient, increase reliability, be more suitable for China's national situation.
Summary of the invention
The object of the present invention is to provide the many pump combinations of a kind of employing shield-structured cutter head hydraulic system driven, can satisfy the shield cutter speed governing, improve power source efficient and energy-conservation requirement.
The present invention includes fuel tank, first motor, second motor, the 3rd motor, the 4th motor, the 5th motor, first proportional variable pump, second proportional variable pump, the 3rd proportional variable pump, the 4th proportional variable pump, the 5th proportional variable pump, first two-way plug-in valve, second two-way plug-in valve, the 3rd two-way plug-in valve, the 4th two-way plug-in valve, the 5th two-way plug-in valve, first precursor overflow valve, second precursor overflow valve, first liang of point control type double-action variable displacement motor, second liang of point control type double-action variable displacement motor, the 3rd liang of point control type double-action variable displacement motor, the 4th liang of point control type double-action variable displacement motor, the 5th liang of point control type double-action variable displacement motor, the 6th liang of point control type double-action variable displacement motor, the 7th liang of point control type double-action variable displacement motor, the 8th liang of point control type double-action variable displacement motor, two position three way directional control valve, three position four-way directional control valve, the Power Limitation valve, proportional pressure control valve, flow speed control valve.
First motor is rigidly connected through the shaft coupling and first proportional variable pump, the oil-in of first proportional variable pump is communicated with fuel tank, the oil-out of first proportional variable pump is communicated with the oil-in of first one way valve, and the oil-out of first one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
Second motor is rigidly connected through the shaft coupling and second proportional variable pump, the oil-in of second proportional variable pump is communicated with fuel tank, the oil-out of second proportional variable pump is communicated with the oil-in of second one way valve, and the oil-out of second one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
The 3rd motor is rigidly connected through shaft coupling and the 3rd proportional variable pump, the oil-in of the 3rd proportional variable pump is communicated with fuel tank, the oil-out of the 3rd proportional variable pump is communicated with the oil-in of the 3rd one way valve, and the oil-out of the 3rd one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
The 4th motor is rigidly connected through shaft coupling and the 4th proportional variable pump, the oil-in of the 4th proportional variable pump is communicated with fuel tank, the oil-out of the 4th proportional variable pump is communicated with the oil-in of the 4th one way valve, and the oil-out of the 4th one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
Second hydraulic fluid port of the 5th two-way plug-in valve is communicated with fuel tank, and the 3rd hydraulic fluid port of the 5th two-way plug-in valve is communicated with first hydraulic fluid port of two position three way directional control valve; Second hydraulic fluid port of two position three way directional control valve is communicated with the oil-in of first precursor overflow valve, and the oil-out of first precursor overflow valve is communicated with fuel tank; The 3rd hydraulic fluid port of two position three way directional control valve is communicated with the oil-in of second precursor overflow valve, and the oil-out of second precursor overflow valve is communicated with fuel tank; The oil-out of the 6th one way valve is communicated with second hydraulic fluid port of Power Limitation valve; First hydraulic fluid port of first two-way plug-in valve is communicated with second hydraulic fluid port of second two-way plug-in valve; Second hydraulic fluid port of first two-way plug-in valve is communicated with fuel tank; The 3rd hydraulic fluid port of first two-way plug-in valve is communicated with the 3rd hydraulic fluid port of three position four-way directional control valve; Second hydraulic fluid port of second two-way plug-in valve is communicated with the first separating valve piece, one end hydraulic fluid port; The 3rd hydraulic fluid port of second two-way plug-in valve is communicated with second hydraulic fluid port of three position four-way directional control valve; Second hydraulic fluid port of the 3rd two-way plug-in valve is communicated with the second separating valve piece, one end hydraulic fluid port; The 3rd hydraulic fluid port of the 3rd two-way plug-in valve is communicated with the 3rd hydraulic fluid port of three position four-way directional control valve; First hydraulic fluid port of the 4th two-way plug-in valve is communicated with second hydraulic fluid port of the 3rd two-way plug-in valve; Second hydraulic fluid port of the 4th two-way plug-in valve is communicated with fuel tank; The 3rd hydraulic fluid port of the 4th two-way plug-in valve is communicated with second hydraulic fluid port of three position four-way directional control valve; The 4th hydraulic fluid port of three position four-way directional control valve is communicated with fuel tank; The other end hydraulic fluid port of the first separating valve piece respectively with first hydraulic fluid port of first liang of point control type double-action variable displacement motor, first hydraulic fluid port of second liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 3rd liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 4th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 5th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 6th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 7th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 8th liang of point control type double-action variable displacement motor is communicated with; The other end hydraulic fluid port of the second separating valve piece respectively with second hydraulic fluid port of first liang of point control type double-action variable displacement motor, second hydraulic fluid port of second liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 3rd liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 4th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 5th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 6th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 7th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 8th liang of point control type double-action variable displacement motor is communicated with;
The 5th motor is rigidly connected through shaft coupling and the 5th proportional variable pump, the oil-in of the 5th proportional variable pump is communicated with fuel tank, the oil-out of the 5th proportional variable pump is communicated with the oil-in of the 5th one way valve, the oil-out of the 5th one way valve is communicated with the oil-in of flow speed control valve, the oil-out of flow speed control valve is communicated with the control port of first proportional variable pump, the control port of second proportional variable pump, first hydraulic fluid port of Power Limitation valve, the oil-in of proportional pressure control valve respectively, the 3rd hydraulic fluid port of Power Limitation valve is communicated with fuel tank, and the oil-out of proportional pressure control valve is communicated with fuel tank.
The present invention adopts big discharge capacity master to drive proportional variable pump group and the motion of float amount assistive drive proportional variable pump group combination driving shield cutterhead.During cutterhead work, two proportional variable pumps that big discharge capacity master drives the proportional variable pump group are worked simultaneously, two proportional variable pumps of float amount assistive drive proportional variable pump group are incorporated system into when main driving power is not enough, improve the load factor and the power source efficient of single hydraulic pump.By electric-control system, regulate the rate variable pump delivery to realize adjusting to cutterhead speed.
System of the present invention adopts big discharge capacity proportional variable pump group and the combination of float amount proportional variable pump group to drive, control mode is automatically controlled rate variable, installed power is moderate, hydraulic pump can flexible combination, under the nominal situation, the load factor height of single hydraulic pump can improve the efficient of power source, has energy-conservation effect.Because proportional variable pump adopts the speed governing of automatically controlled change discharge capacity, and adopts two point control type double-action variable displacement motors, can make shield cutter speed governing in wide range, satisfies working condition requirement.
Description of drawings
Fig. 1 is the structural representation of a specific embodiment of the present invention.
The specific embodiment
The invention will be further described below in conjunction with drawings and Examples.
The operating principle of this shield-structured cutter head hydraulic system is as follows:
First motor 1.1 and second motor 1.2 get electric startup, drive first proportional variable pump 2.1 and 2.2 rotations of second proportional variable pump respectively, and first proportional variable pump 2.1 and second proportional variable pump 2.2 are the main proportional variable pump group that drives.15.1,15.2 oil suctions from fuel tank 14 by the road of main driving proportional variable pump group, the pressure oil that main driving proportional variable pump group is got is delivered to pipeline 18.1,19,20.1,20.2,20.3,20.4 through pipeline 16.1, first one way valve 3.1, pipeline 17.1 and pipeline 16.2, second one way valve 3.2, pipeline 17.2.
When three position four-way directional control valve 7 left electromagnet get when electric, the working chamber that hydraulic oil process three position four-way directional control valve 7 in the pipeline 19, pipeline 24.2 act on the 3rd hydraulic fluid port place of second two-way plug-in valve 6.2, the process of the hydraulic oil in the pipeline 19 three position four-way directional control valve 7, pipeline 24.4 act on the working chamber at the 3rd hydraulic fluid port place of the 4th two-way plug-in valve 6.4, and this moment, second two-way plug-in valve 6.2 and the 4th two-way plug-in valve 6.4 were in closed condition.The working chamber at the 3rd hydraulic fluid port place of first two-way plug-in valve 6.1 communicates through pipeline 24.1, three position four-way directional control valve 7 and fuel tank, the working chamber at the 3rd hydraulic fluid port place of the 3rd two-way plug-in valve 6.3 communicates through pipeline 24.3, three position four-way directional control valve 7 and fuel tank, and this moment, first two-way plug-in valve 6.1 and the 3rd two-way plug-in valve 6.3 were in opening.Hydraulic oil in the pipeline 19 is by the 3rd two-way plug-in valve 6.3, pipeline 23.2,25.2,27.1,27.2,27.3,27.4 deliver to separating valve piece 8.2, the pressure oil that separating valve piece 8.2 is sent by the road 29.1,29.2,29.3,29.4 deliver to ring-like flow distributing and collecting pipeline 31, the pressure oil that ring-like flow distributing and collecting pipeline 31 is sent 33.1 enters first liang of point control type double-action variable displacement motor 9.1 by the road, 33.2 enter second liang of point control type double-action variable displacement motor 9.2 by the road, 33.3 enter the 3rd liang of point control type double-action variable displacement motor 9.3 by the road, 33.4 enter the 4th liang of point control type double-action variable displacement motor 9.4 by the road, 33.5 enter the 5th liang of point control type double-action variable displacement motor 9.5 by the road, 33.6 enter the 6th liang of point control type double-action variable displacement motor 9.6 by the road, 33.7 enter the 7th liang of point control type double-action variable displacement motor 9.7 by the road, 33.8 enter the 8th liang of point control type double-action variable displacement motor 9.8 by the road.First liang of point control type double-action variable displacement motor 9.1 oil return opening oil return is delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.1, second liang of point control type double-action variable displacement motor 9.2 oil return opening oil return is delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.2, the 3rd liang of point control type double-action variable displacement motor 9.3 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.3, the 4th liang of point control type double-action variable displacement motor 9.4 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.4, the 5th liang of point control type double-action variable displacement motor 9.5 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.5, the 6th liang of point control type double-action variable displacement motor 9.6 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.6, the 7th liang of point control type double-action variable displacement motor 9.7 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.7, the 8th liang of point control type double-action variable displacement motor 9.8 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.8, pressure oil by the road 28.1 in the ring-like flow distributing and collecting pipeline 30,28.2,28.3,28.4 deliver to separating valve piece 8.1, by the road 26.1,26.2,26.3,26.4,25.1,23.1 deliver to first two-way plug-in valve 6.1,39.6 deliver to fuel tank 14 and finish oil return by the road, thereby two point control type double-action variable displacement motors 9.1,9.2,9.3,9.4,9.5,9.6,9.7,9.8 under the pressure reduction at two ends, rotate, drive cutterhead and rotate.
When three position four-way directional control valve 7 right electromagnet get when electric, situation is similar to the above, this moment, second two-way plug-in valve 6.2 and the 4th two-way plug-in valve 6.4 were in opening, first two-way plug-in valve 6.1 and the 3rd two-way plug-in valve 6.3 are in closed condition, the oil-feed oil return of two point control type double-action variable displacement motors realizes the reverse rotation of cutterhead with above-mentioned opposite.
The 5th motor 1.5, the 5th proportional variable pump 2.5, the 5th one way valve 3.5, flow speed control valve 11, proportional pressure control valve 12, Power Limitation valve 13, the 6th one way valve 3.6 are formed first proportional variable pump 2.1 and second proportional variable pump, 2.2 discharge capacities control oil return line.The 5th motor 1.5 gets electric startup, drives the 5th proportional variable pump 2.5.The 5th proportional variable pump 2.5 is 15.5 oil suctions from fuel tank 14 by the road, pressure oil that the 5th proportional variable pump 2.5 is got is delivered to flow speed control valve 11 through pipeline 16.5, the 5th one way valve 3.5, pipeline 35,36 and 37.1 delivers to the control port of second proportional variable pump 2.2 by the road after flow speed control valve 11 carries out Flow-rate adjustment, 36 and 37.2 deliver to the control port of first proportional variable pump 2.1 by the road, 36 and 37.3 delivers to first hydraulic fluid port of Power Limitation valve 13,36 and 37.4 oil-ins of delivering to proportional pressure control valve 12 by the road by the road.Pressure oil in the pipeline 19 is delivered to second hydraulic fluid port of Power Limitation valve 13 by the 6th one way valve 3.6, and the pressure in the pipeline 19 is system pressure.When system pressure did not reach the initial setting value of Power Limitation valve 13, the pressure of the control port of first proportional variable pump 2.1 and second proportional variable pump 2.2 was by proportional pressure control valve 12 decision, and proportional with its conditioning signal.Because the control port pressure of first proportional variable pump 2.1 and second proportional variable pump 2.2 and first proportional variable pump 2.1 and second proportional variable pump, 2.2 discharge capacities are proportional, so adjustable continuously, and then realize that the cutterhead rotating speed is adjustable continuously by regulating proportional pressure control valve 12 realization first proportional variable pumps 2.1 and second proportional variable pump, 2.2 discharge capacities; When system pressure surpasses Power Limitation valve 13 initial setting values, the Power Limitation valve 13 beginning overflow of working, cause the pressure in the pipeline 36 to reduce, the control port pressure of first proportional variable pump 2.1 and second proportional variable pump 2.2 is reduced, thereby first proportional variable pump 2.1 and second proportional variable pump, 2.2 discharge capacities are reduced, cutterhead speed reduces, keep first proportional variable pump 2.1 and second proportional variable pump, 2.2 power outputs constant, prevent first proportional variable pump 2.1 and second proportional variable pump, 2.2 power overloads.
Reach when setting rotating speed when the output flow of first proportional variable pump 2.1 and second proportional variable pump 2.2 is enough to drive cutterhead, only open first proportional variable pump 2.1 and second proportional variable pump 2.2; When the output flow of first proportional variable pump 2.1 and second proportional variable pump 2.2 is not enough to drive cutterhead and reaches the rotating speed of setting, motor 1.3 and motor 1.4 get electric startup, drive float flow control three proportional variable pumps 2.3 and 2.4 rotations of the 4th proportional variable pump respectively, the 3rd proportional variable pump 2.3 and the 4th proportional variable pump 2.4 are assistive drive proportional variable pump group, and the analysis of hydraulic circuit and above-mentioned situation are similar.Assistive drive proportional variable pump group carries persevering powered controls, by special electric control system controls.Big discharge capacity master drives the proportional variable pump group and the combination of float amount assistive drive proportional variable pump group drives to provide the cutterhead rotating speed needed flow.
Two point control type double-action variable displacement motors 9.1,9.2,9.3,9.4,9.5,9.6,9.7,9.8, can make motor displacement be set in minimum injection rate or maximum pump discharge place by special control device, thereby be implemented in two grades of switchings of cutterhead high, low speed under the given flow.
The 5th two-way plug-in valve 6.5, two position three way directional control valve 5 are formed the voltage-limiting protection loop with precursor overflow valve 4.1,4.2.System pressure oil in the pipeline 19 20.1 is communicated with the 5th two-way plug-in valve 6.5 first hydraulic fluid ports by the road, system pressure oil by after the damping port in the 5th two-way plug-in valve 6.5 by the road 21 and first hydraulic fluid port of two position three way directional control valve 5 be communicated with.When cutterhead is worked under the nominal situation pattern, the outage of two position three way directional control valve 5 electromagnet, precursor overflow valve 4.1 inserts the loop, if system pressure surpasses precursor overflow valve 4.1 pressure set points, precursor overflow valve 4.1 beginning overflows, make the 5th two-way plug-in valve 6.5 be in opening, system pressure oil begins overflow by second hydraulic fluid port of the 5th two-way plug-in valve 6.5, thereby plays the voltage-limiting protection of nominal situation; When working under cutterhead is being got rid of poverty pattern, two position three way directional control valve 5 electromagnet get electric, and precursor overflow valve 4.2 inserts the loop, and principle is similar to the above, plays the voltage-limiting protection of the operating mode of getting rid of poverty.
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| Application Number | Priority Date | Filing Date | Title |
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| CN2009100964082A CN101503960B (en) | 2009-03-02 | 2009-03-02 | Shield cutter head hydraulic system driven by multi-pump combination |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2009100964082A CN101503960B (en) | 2009-03-02 | 2009-03-02 | Shield cutter head hydraulic system driven by multi-pump combination |
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| CN101503960B true CN101503960B (en) | 2010-12-08 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106762882A (en) * | 2016-12-21 | 2017-05-31 | 浙江大学 | The double mode electro-hydraulic drive system of development machine cutterhead |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101691877B (en) * | 2009-09-04 | 2012-03-07 | 佛山市顺德区震德塑料机械有限公司 | Servo motor control-based multi-pump combination controlled hydraulic power system |
| CN102032232B (en) * | 2010-12-27 | 2013-01-09 | 清华大学深圳研究生院 | Proportional control type power limitation valve |
| CN102996138B (en) * | 2012-11-30 | 2015-02-18 | 中煤科工集团重庆研究院有限公司 | Hydraulic control system integrating dust removal and outburst prevention for integrated excavator |
| CN105864132B (en) * | 2015-01-23 | 2017-09-08 | 鞍钢股份有限公司 | Constant-pressure variable pump system and energy-saving method |
| US11028691B2 (en) * | 2016-12-21 | 2021-06-08 | Zhejiang University | Drive system with both fixed-displacement hydraulic motors and variable-displacement hydraulic motors for cutter head of boring machine and control method thereof |
| CN110439882B (en) * | 2018-05-03 | 2020-07-28 | 杭州诺云科技有限公司 | Energy-saving optimization method and system for centralized hydraulic station |
| CN109268344B (en) * | 2018-10-24 | 2020-06-09 | 武汉科技大学 | Device and method for testing instantaneous flow characteristic of speed limiting valve |
| CN109505812B (en) * | 2019-01-17 | 2020-11-03 | 中国铁建重工集团股份有限公司 | Variable pump dual-mode control hydraulic system and tunnel operation vehicle |
| CN110273896B (en) * | 2019-07-02 | 2021-09-24 | 江苏钧微动力科技有限公司 | An integrated hydraulic digital pump station |
| CN114198349B (en) * | 2021-12-20 | 2024-06-14 | 中国铁建重工集团股份有限公司 | Continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment |
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2009
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106762882A (en) * | 2016-12-21 | 2017-05-31 | 浙江大学 | The double mode electro-hydraulic drive system of development machine cutterhead |
| CN106762882B (en) * | 2016-12-21 | 2018-05-08 | 浙江大学 | The electro-hydraulic drive system of development machine cutterhead double mode |
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| CN101503960A (en) | 2009-08-12 |
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