CN203383824U - Flow saturation resistant partitioned controlled energy saving type shield thrust hydraulic system - Google Patents
Flow saturation resistant partitioned controlled energy saving type shield thrust hydraulic system Download PDFInfo
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- CN203383824U CN203383824U CN201320348494.3U CN201320348494U CN203383824U CN 203383824 U CN203383824 U CN 203383824U CN 201320348494 U CN201320348494 U CN 201320348494U CN 203383824 U CN203383824 U CN 203383824U
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Abstract
The utility model discloses a flow saturation resistant partitioned controlled energy saving type shield thrust hydraulic system. Every area comprises a motor, a variable pump, a variable cylinder, a two-position three-way proportional reversing valve, a safety valve, a two-position two-way reversing valve, a proportional flow valve, a proportional overflow valve, four variable throttling openings, four pressure compensators, four one-way valves, four three-position four-way reversing valve, four hydraulic cylinders, oil inlet pipes, oil return pipes, compensatory pressure oil pipes and an oil tank. According to the flow saturation resistant partitioned controlled energy saving type shield thrust hydraulic system which is applied to shield thrust, every area adopts an independent oil source, large displacement pumps are replaced by small displacement pumps, areas can be independently controlled and coordinately controlled, a hydraulic oil source of every area only needs to output pressure oil which is suitable for working pressure, a flow saturation resistant design is adopted in the zones, and every hydraulic cylinder in the zones is always in a best working state and has a best energy saving effect.
Description
Technical field
The utility model relates to fluid pressure actuator, relates in particular to the subregion that a kind of anti-current amount is saturated and controls energy-saving type shield propulsion hydraulic system.
Background technology
Shield excavation machine is a kind of modernization high-tech digging device that is exclusively used in the subterranean tunnel engineering construction, has many advantages such as construction safety, quick, workmanship is high, ground perturbation is little, labour intensity is low.Along with development in science and technology and social progress, shield driving will progressively replace conventional method.
The propulsion system of shield excavation machine provides propulsive force for the shield structure advances, and is bearing the core missions of shield driving.The complex polygon of soil property stratum and Water And Earth Pressures thereof, and all unpredictable elements of existing of shield structure the place ahead, proposed very high control requirement to thrust output and the speed of propulsion system.Simultaneously, shield driving is also a kind of typically high-power, heavy load operating mode, so its installed power is huge.In energy consumption large system like this, operating efficiency is a very important influence factor for systematic function.
In traditional shield excavation machine, the hydraulic cylinder that propulsion system will circumferentially distribute along the shield structure is usually implemented subregion, adopts hydraulic valve to carry out pressure flow to unified oil sources and regulates and controls to realize to control target.And, in actual tunneling process, due to the load difference that each section post that makes progress in week bears, oil sources must carry out fuel feeding according to high capacity subregion, cause other subregion inefficiencies.Finally cause the entire system Efficiency Decreasing, not only waste energy, affect equipment life, and worsened construction environment, bring many unfavorable factors.CN101408107B has announced a kind of energy-saving type shield propulsion hydraulic system that adopts subregion to control, and the conventional method for the control of unified oil sources valve, proposed subregion control, and the method for the independent fuel feeding of each subregion, realized the raising of whole efficiency.But problem asynchronous for each hydraulic cylinder works of subregion inside, inefficiency, do not propose corresponding solution.
Summary of the invention
Take into account in order to overcome the problem existed in existing shield-tunneling construction process the requirement that meets shield-tunneling construction, the purpose of this utility model has been to provide the subregion that a kind of anti-current amount is saturated to control energy-saving type shield propulsion hydraulic system, what both can solve propulsive force and fltting speed contacts control in real time, increase propulsion system and coordinate the flexibility of controlling, also solved by stages and the interior inefficient problem of hydraulic cylinder works of subregion in propulsion system simultaneously.
The technical scheme that the utility model technical solution problem adopts is:
The subregion that the anti-current amount is saturated is controlled energy-saving type shield propulsion hydraulic system and is comprised that subregion oil sources and 4 of placing in parallel are uniformly distributed hydraulic cylinder in subregion, and the subregion oil sources comprises: motor, variable pump, variable cylinder, two-bit triplet proportional reversing valve, safety valve, 2/2-way reversal valve, proportional flow control valve, proportional pressure control valve, oil inlet pipe, oil return pipe, compensatory pressure oil pipe and fuel tank, in each subregion, hydraulic cylinder comprises: settable orifice, pressure compensator, one way valve, three position four-way directional control valve, hydraulic cylinder, in subregion oil sources and one of them subregion, the annexation of hydraulic cylinder is: motor and variable pump are rigidly connected, and the inlet port of variable pump is communicated with fuel tank, the second hydraulic fluid port of the oil-out of variable pump and variable cylinder, the oil-in of safety valve, the first hydraulic fluid port of 2/2-way reversal valve, the oil-in of proportional flow control valve is connected, the first hydraulic fluid port of variable cylinder is connected with the first hydraulic fluid port of two-position three-way proportional reversal valve, the second hydraulic fluid port of two-position three-way proportional reversal valve is connected with fuel tank, the 3rd hydraulic fluid port of two-position three-way proportional reversal valve is connected with the compensation oil pipe, the oil return opening of safety valve is connected with fuel tank, the second hydraulic fluid port of 2/2-way reversal valve, the oil return opening of proportional flow control valve, the oil-in of proportional pressure control valve, the oil-in of settable orifice is connected with oil inlet pipe, the oil return opening of settable orifice, the oil-in of pressure compensator is connected without spring cavity with pressure compensator, the oil return opening of pressure compensator, the oil-in of one way valve is connected with the first hydraulic fluid port of three position four-way directional control valve, pressure compensator spring cavity arranged, the oil return opening of one way valve is connected with the compensatory pressure pipe, the second hydraulic fluid port of three position four-way directional control valve is connected with the first hydraulic fluid port of hydraulic cylinder, the 3rd hydraulic fluid port of three position four-way directional control valve is connected with the second hydraulic fluid port of hydraulic cylinder, the 4th hydraulic fluid port of three position four-way directional control valve is connected with oil return pipe, oil return pipe is connected with fuel tank, in other three subregions, the annexation of hydraulic cylinder and subregion oil sources is the same.
The utility model is compared with background technology, and the beneficial effect had is:
1) by stages coordinates to control, and increases system flexibility.
2) independent oil sources is arranged in subregion, according to high load hydraulic cylinder in district, adjust in real time oil supply pressure and flow in subregion, realize the subregion pressure adaptive.Simultaneously, in district, a certain hydraulic cylinder other hydraulic cylinders in external interference produces pressure or changes in flow rate Shi， district will spontaneously carry out corresponding flow pressure adjustment, make each hydraulic cylinder of propulsion system all in optimum Working, the minimizing energy loss.
The accompanying drawing explanation
Fig. 1 is that the subregion that the anti-current amount is saturated is controlled the energy-saving type shield propulsion hydraulic system structural representation;
Fig. 2 is the shield driving hydraulic cylinder subregion schematic diagram that adopts system described in the utility model.
The specific embodiment
Below in conjunction with drawings and Examples, the utility model is further illustrated.
The subregion that the anti-current amount is saturated is controlled energy-saving type shield propulsion hydraulic system and is comprised that subregion oil sources and 4 of placing in parallel are uniformly distributed hydraulic cylinder in subregion, and the subregion oil sources comprises: motor 1, variable pump 2, variable cylinder 3, two-bit triplet proportional reversing valve 4, safety valve 5,2/2-way reversal valve 6, proportional flow control valve 7, proportional pressure control valve 8, oil inlet pipe 14, oil return pipe 15, compensatory pressure oil pipe 16 and fuel tank 17, in each subregion, hydraulic cylinder comprises: settable orifice 9, pressure compensator 10, one way valve 11, three position four-way directional control valve 12, hydraulic cylinder 13, in subregion oil sources and one of them subregion, the annexation of hydraulic cylinder is: motor 1 is rigidly connected with variable pump 2, and the inlet port S of variable pump 2 is communicated with fuel tank 17, the second hydraulic fluid port B3 of the oil-out P of variable pump 2 and variable cylinder 3, the oil inlet P 5 of safety valve 5, the first hydraulic fluid port P6 of 2/2-way reversal valve 6, the oil inlet P 7 of proportional flow control valve 7 is connected, the first hydraulic fluid port A3 of variable cylinder 3 is connected with the first hydraulic fluid port P4 of two-position three-way proportional reversal valve 4, the second hydraulic fluid port T4 of two-position three-way proportional reversal valve 4 is connected with fuel tank 17, the 3rd hydraulic fluid port A4 of two-position three-way proportional reversal valve 4 is connected with compensation oil pipe 16, the oil return inlet T 5 of safety valve 5 is connected with fuel tank, the second hydraulic fluid port T6 of 2/2-way reversal valve 6, the oil return inlet T 7 of proportional flow control valve 7, the oil inlet P 8 of proportional pressure control valve 8, the oil inlet P 9 of settable orifice 9 is connected with oil inlet pipe 14, the oil return inlet T 9 of settable orifice 9, the oil inlet P 10 of pressure compensator 10 and being connected without spring cavity of pressure compensator 10, the oil return inlet T 10 of pressure compensator 10, the oil inlet P 11 of one way valve 11 is connected with the first hydraulic fluid port P12 of three position four-way directional control valve 12, pressure compensator 11 spring cavity arranged, the oil return inlet T 11 of one way valve 11 is connected with compensatory pressure pipe 16, the second hydraulic fluid port A12 of three position four-way directional control valve 12 is connected with the first hydraulic fluid port P13 of hydraulic cylinder 13, the 3rd hydraulic fluid port of three position four-way directional control valve 12
b12 are connected with the second hydraulic fluid port T13 of hydraulic cylinder 13, and the 4th hydraulic fluid port T12 of three position four-way directional control valve 12 is connected with oil return pipe 15, and oil return pipe 15 is connected with fuel tank 17, and in other three subregions, the annexation of hydraulic cylinder and subregion oil sources is the same.
Operating principle of the present utility model is as follows:
Motor 1 obtains electric startup, drive variable pump 2 to rotate, variable pump 2 is by inlet port S from the fuel tank oil suction, and the pressure oil that variable pump 2 is got is by oil-out P difference entering variable cylinder 3 hydraulic fluid port B3, the oil inlet P 5 of safety valve 5, the hydraulic fluid port P6 of 2/2-way reversal valve 6 and the hydraulic fluid port P7 of proportional flow control valve.
When the shield structure is pushed ahead, 2/2-way reversal valve 6 dead electricity, pump discharge pressure oil flows to through proportional flow control valve 7 hydraulic fluid port P7, from proportional flow control valve, 7 hydraulic fluid port T7 flow out, and flow to hydraulic fluid port A4, the proportional pressure control valve 8 hydraulic fluid port P8 of oil inlet pipe 14, bi-bit bi-pass reversal valve 6 hydraulic fluid port T6, two-position three-way proportional reversal valve 4.Two-position three-way proportional reversal valve 4 dead electricity, the pressure oil flowed out from two-position three-way proportional reversal valve 4 hydraulic fluid port P4, through variable cylinder 3 hydraulic fluid port A3 entering variable cylinder 3 spring cylinders.The pressure oil flowed out from oil inlet pipe 14, flow into through settable orifice 9 oil inlet P 9, from settable orifice 9 oil return inlet T 9, flows out.The pressure oil flowed out from T9 flows to oil inlet P 11, the three position four-way directional control valve 12 hydraulic fluid port P12 of one way valve 11.The oil flowed out from the oil-out T11 of one way valve 11 enters pressure compensation pipeline 16.Three position four-way directional control valve 12 right-hand member electromagnet obtain electric, and pressure oil flows out from hydraulic fluid port A12 through three position four-way directional control valve 12, and through hydraulic cylinder, 13 hydraulic fluid port P13 enter hydraulic cylinder 13 rodless cavities, promote hydraulic cylinder and advance.Oil return is through hydraulic cylinder 13 hydraulic fluid port T13, and through three position four-way directional control valve, 12 hydraulic fluid port B12T12 enter return line 15, finally flow back to fuel tank 17.
The hydraulic fluid port A3 of variable cylinder 3 is connected with proportional flow control valve 7 oil inlet P 7 respectively with B3, making proportional flow control valve 7 two ends pressure reduction is the equivalent pressure that the variable cylinder spring produces, keep constant, the pump output pressure adapts with load pressure all the time, proportional flow control valve 7 is regulated fltting speed, and proportional pressure control valve 8 is regulated propelling pressure.
When hydraulic cylinder realizes that fallback action constantly, 2/2-way reversal valve 6 obtains electric, through proportional flow control valve 7, by short circuit, pump discharge pressure oil flows out from 2/2-way reversal valve 6, flows to hydraulic fluid port A4, the proportional pressure control valve 8 hydraulic fluid port P8 of oil inlet pipe 14 two-position three-way proportional reversal valves 4.Two-position three-way proportional reversal valve 4 obtains electric, and variable cylinder 3 spring cavitys directly are connected with fuel tank, realize off-load.The pressure oil flowed out from oil inlet pipe 14, flow into through settable orifice 9 oil inlet P 9, from settable orifice 9 oil return inlet T 9, flows out.The pressure oil flowed out from T9 flows to oil inlet P 11, the three position four-way directional control valve 12 hydraulic fluid port P12 of one way valve 11.The oil flowed out from the oil-out T11 of one way valve 11 enters pressure compensation pipeline 16.Three position four-way directional control valve 12 left end electromagnet obtain electric, and pressure oil flows out from hydraulic fluid port B12 through three position four-way directional control valve 12, and through hydraulic cylinder, 13 hydraulic fluid port T13 enter hydraulic cylinder 13 rod chambers, realize the hydraulic cylinder rollback.Oil return is through hydraulic cylinder 13 hydraulic fluid port P13, and through three position four-way directional control valve, 12 hydraulic fluid port A12T12 enter return line 15, finally flow back to fuel tank 17.
In back off procedure, variable cylinder 3 spring cavity off-loads, variable cylinder 3 pistons move to left, and variable pump 2 output flows increase, and realize quick rollback.Proportional flow control valve 7, by short circuit, reduces the restriction loss of system, reaches energy-conservation purpose.
When system pressure surpasses the setting safe pressure, safety valve 5 is opened, and the fluid that variable pump 2 oil-out P flow out flows to safety valve 5 through safety valve 5 oil inlet P 5, from the oil return inlet T 5 of safety valve 5, flows back to fuel tank, realizes off-load.
As shown in Figure 2, this propulsion system has 16 hydraulic cylinders, is divided into A, B, C, D 4th district, upwards is being evenly distributed four, ，Mei district hydraulic cylinder week.
Claims (1)
1. the saturated subregion of anti-current amount is controlled energy-saving type shield propulsion hydraulic system, it is characterized in that comprising that subregion oil sources and 4 of placing in parallel are uniformly distributed hydraulic cylinder in subregion, the subregion oil sources comprises: motor (1), variable pump (2), variable cylinder (3), two-bit triplet proportional reversing valve (4), safety valve (5), 2/2-way reversal valve (6), proportional flow control valve (7), proportional pressure control valve (8), oil inlet pipe (14), oil return pipe (15), compensatory pressure oil pipe (16) and fuel tank (17), in each subregion, hydraulic cylinder comprises: settable orifice (9), pressure compensator (10), one way valve (11), three position four-way directional control valve (12), hydraulic cylinder (13), in subregion oil sources and one of them subregion, the annexation of hydraulic cylinder is: motor (1) is rigidly connected with variable pump (2), and the inlet port (S) of variable pump (2) is communicated with fuel tank (17), the oil-out (P) of variable pump (2) and second hydraulic fluid port (B3) of variable cylinder (3), the oil-in (P5) of safety valve (5), first hydraulic fluid port (P6) of 2/2-way reversal valve (6), the oil-in (P7) of proportional flow control valve (7) is connected, first hydraulic fluid port (A3) of variable cylinder (3) is connected with first hydraulic fluid port (P4) of two-position three-way proportional reversal valve (4), second hydraulic fluid port (T4) of two-position three-way proportional reversal valve (4) is connected with fuel tank (17), the 3rd hydraulic fluid port (A4) of two-position three-way proportional reversal valve (4) is connected with compensation oil pipe (16), the oil return opening (T5) of safety valve (5) is connected with fuel tank, second hydraulic fluid port (T6) of 2/2-way reversal valve (6), the oil return opening (T7) of proportional flow control valve (7), the oil-in (P8) of proportional pressure control valve (8), the oil-in (P9) of settable orifice (9) is connected with oil inlet pipe (14), the oil return opening (T9) of settable orifice (9), the oil-in (P10) of pressure compensator (10) and being connected without spring cavity of pressure compensator (10), the oil return opening (T10) of pressure compensator (10), the oil-in (P11) of one way valve (11) is connected with first hydraulic fluid port (P12) of three position four-way directional control valve (12), pressure compensator (11) spring cavity arranged, the oil return opening (T11) of one way valve (11) is connected with compensatory pressure pipe (16), second hydraulic fluid port (A12) of three position four-way directional control valve (12) is connected with first hydraulic fluid port (P13) of hydraulic cylinder (13), the 3rd hydraulic fluid port of three position four-way directional control valve (12) (
b12) with second hydraulic fluid port (T13) of hydraulic cylinder (13), be connected, the 4th hydraulic fluid port (T12) of three position four-way directional control valve (12) is connected with oil return pipe (15), oil return pipe (15) is connected with fuel tank (17), and in other three subregions, the annexation of hydraulic cylinder and subregion oil sources is the same.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320348494.3U CN203383824U (en) | 2013-06-18 | 2013-06-18 | Flow saturation resistant partitioned controlled energy saving type shield thrust hydraulic system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320348494.3U CN203383824U (en) | 2013-06-18 | 2013-06-18 | Flow saturation resistant partitioned controlled energy saving type shield thrust hydraulic system |
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| CN203383824U true CN203383824U (en) | 2014-01-08 |
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| CN201320348494.3U Expired - Fee Related CN203383824U (en) | 2013-06-18 | 2013-06-18 | Flow saturation resistant partitioned controlled energy saving type shield thrust hydraulic system |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103291314A (en) * | 2013-06-18 | 2013-09-11 | 浙江大学 | Flow-saturation resistant zone-control energy-saving type shield thrust hydraulic system |
| CN103884586A (en) * | 2014-03-24 | 2014-06-25 | 上海交通大学 | Electro-hydraulic loading system of film biaxial tensile testing machine |
| CN111765132A (en) * | 2020-06-29 | 2020-10-13 | 圣邦集团有限公司 | Pilot-associated variable differential pressure compensation system |
| CN111765132B (en) * | 2020-06-29 | 2024-04-23 | 圣邦集团有限公司 | Pilot-related variable differential pressure compensation system |
-
2013
- 2013-06-18 CN CN201320348494.3U patent/CN203383824U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103291314A (en) * | 2013-06-18 | 2013-09-11 | 浙江大学 | Flow-saturation resistant zone-control energy-saving type shield thrust hydraulic system |
| CN103884586A (en) * | 2014-03-24 | 2014-06-25 | 上海交通大学 | Electro-hydraulic loading system of film biaxial tensile testing machine |
| CN111765132A (en) * | 2020-06-29 | 2020-10-13 | 圣邦集团有限公司 | Pilot-associated variable differential pressure compensation system |
| CN111765132B (en) * | 2020-06-29 | 2024-04-23 | 圣邦集团有限公司 | Pilot-related variable differential pressure compensation system |
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Legal Events
| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140108 Termination date: 20170618 |
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| CF01 | Termination of patent right due to non-payment of annual fee |