CN201696054U - Closed-type hydraulic driving system with variable-speed variable-displacement combined control of shield cutter head - Google Patents
Closed-type hydraulic driving system with variable-speed variable-displacement combined control of shield cutter head Download PDFInfo
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- CN201696054U CN201696054U CN2010201922723U CN201020192272U CN201696054U CN 201696054 U CN201696054 U CN 201696054U CN 2010201922723 U CN2010201922723 U CN 2010201922723U CN 201020192272 U CN201020192272 U CN 201020192272U CN 201696054 U CN201696054 U CN 201696054U
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Abstract
The utility model discloses a closed-type hydraulic driving system with variable-speed variable-displacement combined control of a shield cutter head. The main oil path of the system adopts a pump-controlled motor closed-type system in which the variable-speed control serves as the first-stage speed control and the variable-displacement speed control serves as the second-stage speed control, so that the variable-frequency speed control has good energy-saving effect and high efficiency, the variable-displacement pump-controlled motor closed-type system reduces the overflow loss and the throttling loss and increases the efficiency of the system, and the limitation that the range of variable-frequency speed control exceeds the speed limits of the pump is eliminated. Since the shield cutter head has wide speed range and large power range, the variable-speed variable-displacement combined control increases the range of speed control of the shield cutter head. The combination of a one-way valve and a proportional overflow valve can achieve the two-way continuous pressure control of the shield cutter head. Energy accumulators mounted at the two ends of a variable pump can absorb the shock and vibration of the system oil to reduce the installed power of the system.
Description
Technical field
The utility model relates to a kind of fluid pressure actuator, relates in particular to a kind of shield cutter closed type energy-saving hydraulic control system that adopts variable speed to become the compound control of discharge capacity.
Background technology
Shield excavation machine is a kind of modernized high-tech digging device that is exclusively used in the subterranean tunnel engineering construction.Compare with traditional job practices, shield method have construction safety, fast, many advantages such as workmanship is high, the ground disturbance is little, labour intensity is low.Owing to adopted advanced excavation face stabilization technique, showed special advantages in the construction of tunnel construction that shield driving is especially complicated and changeable at geological conditions and construction environment is abominable.In addition, the shield structure is also being brought into play the irreplaceable effect of other driving form aspect the complex course driving satisfying.Along with development in science and technology and social progress, shield driving will progressively replace conventional method.
Cutter-devices system is the important component part of shield excavation machine, cutterhead rotates the soil body of being responsible for cutting the place ahead, institute of cutterhead system energy requirement is big, plays the part of more and more important effect in shield machine, and same propulsion system, conveying worm, pipe sheet assembling system have constituted complete shield machine.These a few part system synchronization operate, closely cooperate, and finish the shield driving task jointly.Because shield structure condition of work is abominable and load is very big, cutterhead system, propulsion system, spiral system, pipe sheet assembling system all adopt hydraulic-driven.
It is a kind of typically high-power, heavy load operating mode that shield cutter drives, big according to different geological conditions cutterhead rotation speed change scopes, the power excursion is wide, and in the so big system of energy consumption, operating efficiency is an extremely important influence factor for systematic function.Adopt valve prosecutor formula in the tradition shield cutter mostly, open system, this control mode can cause very big throttling and spill losses to a certain extent, finally causes the loss of reduction of entire system efficient and energy.System effectiveness is hanged down has not only wasted energy, influenced equipment life, and has worsened construction environment, brings many unfavorable factors.The efficient that though the enclosed speed control system with adjustable displacement of pump-control-motor can height-adjusting system for valve control system, pump control system can limit the scope of speed governing separately, and low-response is arranged simultaneously, has the shortcoming that lags behind, and pressure can not be adjustable continuously.Independent variable speed control can be subjected to the restriction of the revolution speed limit, therefore how these problems may influence the raising of the overall performance of shield structure in some cases, realize the realization fast-response of hydraulic system under the situation of driving task and widen the cutterhead speed adjustable range to be a key technical problem in the shield driving guaranteeing that the shield driving system correctly efficiently finishes.
The utility model content
The purpose of this utility model is to have in order to overcome existing shield cutter system that system responses is slow, the limited problem of cutterhead speed adjustable range in work progress, provides a kind of variable speed to become the cutterhead Closed Hydraulic Driving system of the compound control of discharge capacity.
The purpose of this utility model and effect are achieved through the following technical solutions: a kind of variable speed becomes the cutterhead Closed Hydraulic Driving system of the compound control of discharge capacity, comprising: high pressure accumulator, low pressure accumulator, the two-position four-way cartridge valve, first pressure meter, second pressure meter, first pressure sensor, second pressure sensor, first strainer, second strainer, the frequency converter and first motor, first shaft coupling, two-way variable displacement pump, electromagnet cut off valve, first safety valve, second safety valve, first one way valve, second one way valve, the 3rd one way valve, the 4th one way valve, the 5th one way valve, the 6th one way valve, proportional pressure control valve, shuttle valve, groups of motors, second motor, second shaft coupling, constant displacement pump, the inlet port strainer, fuel tank, the oil-out strainer, electromagnetic relief valve.
The frequency converter and first motor are rigidly connected by first shaft coupling and two-way variable displacement pump, the inlet port of two-way variable displacement pump is communicated with the inlet port strainer of band oil news generating means, the oil-out of two-way variable displacement pump is connected with the oil-out strainer oil-in that has oil news generating means, and oil-out strainer oil-out is connected with working connection; One end of the oil-in T of two-position four-way cartridge valve, first one way valve, one end, the 4th one way valve one end, the 5th one way valve one end, first safety valve, one end, second safety valve, one end, second pressure meter and groups of motors is connected with working connection, and the other end of the other end of the P mouth of two-position four-way cartridge valve, first pressure meter, the first safety valve other end, second safety valve, second one way valve, one end, the 3rd one way valve one end, the 6th one way valve one end and groups of motors is connected with main oil return line; The port of export of the other end of first one way valve, the second one way valve other end and proportional pressure control valve is connected; The 3rd one way valve other end, the 4th one way valve other end link to each other with the proportional pressure control valve oil-in; An oil-in of shuttle valve and an end of groups of motors are connected, and another oil-in of shuttle valve and the other end of groups of motors are connected, and the outlet of shuttle valve links to each other with electromagnet cut off valve, and the other end of electromagnet cut off valve is connected with the control mouth of two-way variable displacement pump; Constant displacement pump is rigidly connected by second shaft coupling and second motor, and the inlet port of constant displacement pump is connected with the oil drain out of inlet port strainer, and the oil drain out of constant displacement pump is connected with the oil drain out of oil-out strainer and an end of electromagnetic relief valve respectively; The other end of oil-out strainer is connected with the 6th one way valve other end with the 5th one way valve other end respectively, the electromagnetic relief valve oil-out respectively with the inlet port of inlet port strainer be connected with fuel tank.
The utility model is compared with background technology, and the beneficial effect that has is:
1) combination by one way valve and proportional pressure control valve can realize shield cutter in the rotating process, realizes the adjustable continuously of system pressure.
2) in tunneling process, the variable speed speed regulating control is as the first order, and the transmission efficiency height responds soon, when system's rotating speed is restricted, can control by the regulated variable pump delivery, greatly the range of speeds of the cutterhead of Ti Gaoing.
3) regulate pump delivery by the shuttle valve pressure that the motor two ends are higher as feedback pressure, response is high, and reaction is fast.
4) oil-out of accumulator can in time change direction by control two-position four-way cartridge valve according to the rotating of cutterhead, all the time high pressure accumulator can be connected with high-pressure side, low pressure accumulator is connected with low-pressure end, accumulator can serve as the effect of supplementary energy in crucial moment, simultaneously can well absorbing vibration when running into impact load, reduce installed power.
5) hydraulic system adopts closed-loop system, so fluid circulates, needed fuel tank is less, and it is smaller to take up room simultaneously, and this has certain practical value for the shield driving of underground construction.
Description of drawings
Fig. 1 is the cutterhead Closed Hydraulic Driving systematic schematic diagram that the utility model variable speed becomes the compound control of discharge capacity;
Among the figure: high pressure accumulator 1, low pressure accumulator 2, two-position four-way cartridge valve 3, first pressure meter 4.1, second pressure meter 4.2, first pressure sensor 5.1, second pressure sensor 5.2, first strainer 6.1, second strainer 6.2, the frequency converter and first motor 7, first shaft coupling 8, two-way variable displacement pump 9, electromagnet cut off valve 10, first safety valve 11.1, second safety valve 11.2, first one way valve 12.1, second one way valve 12.2, the 3rd one way valve 12.3, the 4th one way valve 12.4, the 5th one way valve 12.5, the 6th one way valve 12.6, proportional pressure control valve 13, shuttle valve 14, groups of motors 15, second motor 16, second shaft coupling 17, constant displacement pump 18, inlet port strainer 19, fuel tank 20, oil-out strainer 21, electromagnetic relief valve 22.
The specific embodiment
Describe the utility model below with reference to the accompanying drawings in detail, it is more obvious that the purpose of this utility model and effect will become.
As shown in Figure 1, the cutterhead Closed Hydraulic Driving system of the compound control of the utility model variable speed change discharge capacity comprises: high pressure accumulator 1, low pressure accumulator 2, two-position four-way cartridge valve 3, first pressure meter 4.1, second pressure meter 4.2, first pressure sensor 5.1, second pressure sensor 5.2, first strainer 6.1, second strainer 6.2, the frequency converter and first motor 7, first shaft coupling 8, two-way variable displacement pump 9, electromagnet cut off valve 10, first safety valve 11.1, second safety valve 11.2, first one way valve 12.1, second one way valve 12.2, the 3rd one way valve 12.3, the 4th one way valve 12.4, the 5th one way valve 12.5, the 6th one way valve 12.6, proportional pressure control valve 13, shuttle valve 14, groups of motors 15, second motor 16, second shaft coupling 17, constant displacement pump 18, inlet port strainer 19, fuel tank 20, oil-out strainer 21, electromagnetic relief valve 22.
The frequency converter and first motor 7 are by first shaft coupling 8) be rigidly connected with two-way variable displacement pump 9, the inlet port of two-way variable displacement pump 9 is communicated with the inlet port strainer 6.1 of band oil news generating means, the oil-out of two-way variable displacement pump 9 is connected with oil-out strainer 6.2 oil-ins that have oil news generating means, and oil-out strainer 6.2 oil-outs are connected with working connection; One end of the oil-in T of two-position four-way cartridge valve 3, first one way valve, 13.1 one ends, the 4th one way valve 13.4 one ends, the 5th one way valve 13.5 one ends, first safety valve, 11.1 one ends, second safety valve, 11.2 one ends, second pressure meter 4.2 and groups of motors 16 is connected with working connection, and the other end of the other end of the P mouth of two-position four-way cartridge valve 3, first pressure meter 4.1, first safety valve, 11.1 other ends, second safety valve 11.2, second one way valve, 12.2 one ends, the 3rd one way valve 12.3 one ends, the 6th one way valve 12.6 one ends and groups of motors 16 is connected with main oil return line; The port of export of the other end of first one way valve 12.1, second one way valve, 12.2 other ends and proportional pressure control valve 13 is connected; The 3rd one way valve 12.3 other ends, the 4th one way valve 12.4 other ends link to each other with proportional pressure control valve 13 oil-ins; An oil-in of shuttle valve 15 and an end of groups of motors 16 are connected, another oil-in of shuttle valve 15 is connected with the other end of groups of motors 16, the outlet of shuttle valve 15 links to each other with electromagnet cut off valve 10, and the other end of electromagnet cut off valve 10 is connected with the control mouth of two-way variable displacement pump 9; Constant displacement pump 18 is rigidly connected by second shaft coupling 17 and second motor 16, the inlet port of constant displacement pump 18 is connected with the oil drain out of inlet port strainer 19, and the oil drain out of constant displacement pump 18 is connected with the oil drain out of oil-out strainer 21 and an end of electromagnetic relief valve 22 respectively; The other end of oil-out strainer 21 is connected with the 6th one way valve 12.6 other ends with the 5th one way valve 12.5 other ends respectively, electromagnetic relief valve 22 oil-outs respectively with the inlet port of inlet port strainer 19 be connected with fuel tank 20.
The course of work of the present utility model is as follows:
First motor 7 gets electric startup, driving two-way variable displacement pump 9 rotates, the inlet port of two-way variable displacement pump 9 links to each other from fuel tank 20 oil suctions with inlet port strainer 19, the pressure oil that two-way variable displacement pump 9 is discharged is delivered in the constant voltage pipeline by oil-out strainer 21, simultaneously some fluid enter respectively first safety valve 11.1, second safety valve 11.2, shuttle valve 14 and groups of motors 15 oil-in, an end of the bridge circuit of forming from one way valve and proportional pressure control valve 13 enters into the oil-in of proportional pressure control valve 13.The detection system pressure that the pressure sensor at two-way variable displacement pump 9 two ends is real-time also is delivered in the adjuster, changes motor speed by the frequency of regulating frequency converter and makes flow system flow and pressure be complementary.Shuttle valve 14 is the hydraulic oil at groups of motors 15 two ends to be incorporated into two-way variable displacement pump 9 control mouths through electromagnet cut off valve 10 control discharge capacity, when system requirements is satisfied in variable speed control, electromagnet cut off valve 10 is closed, when variable speed control reaches capacity can not satisfy system requirements the time, electromagnet cut off valve 10 must be established by cable logical, directly control two-way variable displacement pump 9 by the control oil of groups of motors 15 high-pressure sides and carry out speed governing, this hydraulic direct-regulating mode can improve response speed.First safety valve 11.1, second safety valve 11.2 are to be used for guaranteeing hydraulic oil forward and reverse mobile the time, guarantee that restriction system is the highest when the cutterhead system pressure is too high pressure is by entering low oil pressure end from the hydraulic oil end.The purpose of connecting of two-position four-way cartridge valve 3 and high pressure accumulator 1 and low pressure accumulator 2 mainly is that high-low pressure accumulator and two-way variable displacement pump 9 height pressure sides are complementary in order to realize the cutterhead rotating time, better absorbing vibration and impact, the simultaneity factor flow is big, selects the cartridge valve design for use in order to reduce the restriction loss event.Constant displacement pump 18 systems compensate leakage in order in time to replenish fluid in system.Proportional pressure control valve 13 is used for guaranteeing the step-less adjustment of system pressure.The connection of first one way valve 12.1, second one way valve 12.2, the 3rd one way valve 12.3, the 4th one way valve 12.4 mainly be for the oil drain out that in shield cutter rotating process, can both guarantee variable pump can both be consistent with the oil-in of proportional pressure control valve 13; The 5th one way valve 12.5, the 6th one way valve 12.6 mainly are to avoid the hydraulic oil in the closed system to be back to constant displacement pump 18 systems.
Because the work geological environment of shield structure is complicated and changeable, so we are respectively with sandy stratum, cohesive soil, compound geological conditions such as ground consisting of hard rock get off to analyze this system principle.
At first second motor 16 starts, driving constant displacement pump 18 by second shaft coupling 17 starts, constant displacement pump 18 passes through inlet port strainer 19 from fuel tank 20 oil suctions, thereby the oil-out of constant displacement pump 18 enters closed oil circuit by oil-out strainer 21 and leaks with compensation to the closed oil circuit fuel feeding, electromagnetic relief valve 22 gets when system pressure is stablized, thereby constant displacement pump 18 off-loads reducing overflow and restriction loss, during the closed system insufficient pressure, electromagnetic relief valve 22 must electricly carry out fuel feeding to closed system.When second motor 16 is just changeing, two-way variable displacement pump 9 clockwise rotates, fluid also clockwise rotates in system, end pressure is higher than end pressure down on the two-way variable displacement pump 9 at this moment, electromagnetic valve on this moment two-position four-way cartridge valve 3 gets the electric high pressure accumulator 1 that makes and links to each other with the upper end of two-way variable displacement pump 9, and low pressure accumulator 2 links to each other with the lower end of two-way variable displacement pump 9; When second motor, 16 rotating speeds are opposite, electromagnetic valve dead electricity on the two-position four-way cartridge valve 3, because the effect of spring makes it be operated in position, a left side, because second motor, 16 rotating speeds are opposite, 9 times end pressures of two-way variable displacement pump are higher than end pressure, make the high-low pressure accumulator still consistent with the height pressure side of variable pump.
Just transferring example to second motor 16, the discharge oil of variable pump enters working connection by second strainer 6.2 through second pressure meter 4.2, and a branch directly arrives the oil-in of groups of motors 15, enters into the oil back region after the groups of motors of flowing through 15; Another branch road enters into the inlet of proportional pressure control valve 13 by the 4th one way valve 12.4, and some overflows from proportional pressure control valve 13, enters the oil back region through second one way valve 12.2; All the other branch roads are connected respectively to the oil return opening of first safety valve, 11.1 oil-ins, second safety valve 11.2.The fluid of oil return line enters into the inlet port of two-way variable displacement pump 9 through first strainer 6.1, first pressure meter 4.1.
When the shield structure tunnels in different geology, because the hydraulic system parameters needed is very big such as pressure, changes in flow rate in the different geology, so the scope of its adjusting is also very big, when entering into another kind of geological process from a kind of geology, systematic parameter often alters a great deal.
When shield machine is worked on sandy stratum, lower owing to water content in sandy stratum, so its soil property viscosity ratio is lower, it is bigger to the surrounding soil disturbance to move simultaneously, and the suffered torque ratio of cutterhead is lower under this operating mode, and rotating speed is medium simultaneously, at this time the pressure setting of proportional pressure control valve 13 is medium, variable speed control simultaneously can be satisfied system requirements, and electromagnet cut off valve 10 is closed, and can satisfy system requirements by the variable speed speed regulating control.When entering into the hard rock district, rotating speed improves, and forward displacement reduces, moment of torsion reduces, owing to consider that the variable speed speed governing has certain hysteresis, at this time, make it by regulating electromagnet cut off valve 10, when load pressure changes, at first change rotating speed by hydraulic direct-regulating, control by variable speed when stable back and regulate, when system's adjusting range of speeds is restricted, variable speed and change discharge capacity control effect simultaneously can be widened speed adjustable range.When shield cutter is operated in argillic horizon, the work characteristics on this stratum is that rotating speed is lower, moment of torsion is bigger, and the rotation of cutterhead is bigger to the surrounding soil disturbance, the pressure that regulate proportional pressure control valve 13 this moment is heavily loaded pattern, rotating speed is on the low side simultaneously, so in time, carry out to be regulated variable speed control and can satisfy system requirements, in tunneling process because the randomness and the polytropy of load, regulating system flow that can be real-time and pressure adapt in real time to satisfy with geological condition, by accumulator can absorption system some impact shocks, make system stable operation.
The effect of shuttle valve 14 mainly is for the hydraulic oil that extracts in-line and oil return line comes the regulated variable pump delivery, realizes the control of load-sensitive and constant voltage.Second one way valve 12.2 and the 3rd one way valve 12.3 play and prevent that fluid from flowing backwards and play the anti-empty effect of inhaling simultaneously.
The above-mentioned specific embodiment is used for the utility model of explaining; rather than the utility model limited; in the protection domain of spirit of the present utility model and claim, any modification and change to the utility model is made all fall into protection domain of the present utility model.
Claims (1)
1. a variable speed becomes the cutterhead Closed Hydraulic Driving system of the compound control of discharge capacity, it is characterized in that, comprise high pressure accumulator (1), low pressure accumulator (2), two-position four-way cartridge valve (3), first pressure meter (4.1), second pressure meter (4.2), first pressure sensor (5.1), second pressure sensor (5.2), first strainer (6.1), second strainer (6.2), frequency converter and first motor (7), first shaft coupling (8), two-way variable displacement pump (9), electromagnet cut off valve (10), first safety valve (11.1), second safety valve (11.2), first one way valve (12.1), second one way valve (12.2), the 3rd one way valve (12.3), the 4th one way valve (12.4), the 5th one way valve (12.5), the 6th one way valve (12.6), proportional pressure control valve (13), shuttle valve (14), groups of motors (15), second motor (16), second shaft coupling (17), constant displacement pump (18), inlet port strainer (19), fuel tank (20), oil-out strainer (21), electromagnetic relief valve (22); Wherein, described frequency converter and first motor (7) are rigidly connected by first shaft coupling (8) and two-way variable displacement pump (9); The inlet port of two-way variable displacement pump (9) is communicated with the inlet port strainer (6.1) of band oil news generating means; The oil-out of two-way variable displacement pump (9) is connected with oil-out strainer (6.2) oil-in that has oil news generating means, and oil-out strainer (6.2) oil-out is connected with working connection; The oil-in T of two-position four-way cartridge valve (3), first one way valve (13.1) one ends, the 4th one way valve (13.4) one ends, the 5th one way valve (13.5) one ends, first safety valve (11.1) one ends, second safety valve (11.2) one ends, second pressure meter (4.2) is connected with working connection with an end of groups of motors (16), the P mouth of two-position four-way cartridge valve (3), first pressure meter (4.1) other end, first safety valve (11.1) other end, the other end of second safety valve (11.2), second one way valve (12.2) one ends, the 3rd one way valve (12.3) one ends, the other end of the 6th one way valve (12.6) one ends and groups of motors (16) is connected with main oil return line; The port of export of the other end of first one way valve (12.1), second one way valve (12.2) other end and proportional pressure control valve (13) is connected; The 3rd one way valve (12.3) other end, the 4th one way valve (12.4) other end and proportional pressure control valve (13) oil-in link to each other; An oil-in of shuttle valve (15) and an end of groups of motors (16) are connected, another oil-in of shuttle valve (15) is connected with the other end of groups of motors (16), the same electromagnet cut off valve of outlet (10) of shuttle valve (15) links to each other, and the control mouth of the same two-way variable displacement pump of the other end (9) of electromagnet cut off valve (10) is connected; Constant displacement pump (18) is rigidly connected by second shaft coupling (17) and second motor (16), the inlet port of constant displacement pump (18) is connected with the oil drain out of inlet port strainer (19), and the oil drain out of constant displacement pump (18) is connected with the oil drain out of oil-out strainer (21) and an end of electromagnetic relief valve (22) respectively; The other end of oil-out strainer (21) is connected with the 6th one way valve (12.6) other end with the 5th one way valve (12.5) other end respectively, electromagnetic relief valve (22) oil-out respectively with the inlet port of inlet port strainer (19) be connected with fuel tank (20).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201922723U CN201696054U (en) | 2010-05-17 | 2010-05-17 | Closed-type hydraulic driving system with variable-speed variable-displacement combined control of shield cutter head |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201922723U CN201696054U (en) | 2010-05-17 | 2010-05-17 | Closed-type hydraulic driving system with variable-speed variable-displacement combined control of shield cutter head |
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| CN201696054U true CN201696054U (en) | 2011-01-05 |
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| CN2010201922723U Expired - Lifetime CN201696054U (en) | 2010-05-17 | 2010-05-17 | Closed-type hydraulic driving system with variable-speed variable-displacement combined control of shield cutter head |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101967980A (en) * | 2010-05-17 | 2011-02-09 | 浙江大学 | Cutterhead closed type hydraulic drive system adopting revolving speed-variable and displacement-variable compound control |
| CN103953356A (en) * | 2014-04-28 | 2014-07-30 | 北京市三一重机有限公司 | Open type shield machine, support device and control system and control method of support device |
| CN104019064A (en) * | 2014-06-03 | 2014-09-03 | 三一汽车制造有限公司 | Closed pump hydraulic system, closed pump and engineering machinery |
| CN104196785A (en) * | 2014-07-22 | 2014-12-10 | 西安交通大学 | Closed type energy-saving type shielding propelling hydraulic system adopting multi-union-pump driving |
| CN105179330A (en) * | 2015-09-09 | 2015-12-23 | 华澳轮胎设备科技（苏州）股份有限公司 | Hydraulic station control system and control method thereof |
| CN108286544A (en) * | 2018-02-05 | 2018-07-17 | 北京航空航天大学 | The high rotating speed of aviation pump of throttling volume complex controll drives servo-drive system |
| CN110633525A (en) * | 2019-09-12 | 2019-12-31 | 辽宁石油化工大学 | Method and device for optimizing energy consumption of earth pressure balance shield machine system |
-
2010
- 2010-05-17 CN CN2010201922723U patent/CN201696054U/en not_active Expired - Lifetime
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101967980A (en) * | 2010-05-17 | 2011-02-09 | 浙江大学 | Cutterhead closed type hydraulic drive system adopting revolving speed-variable and displacement-variable compound control |
| CN101967980B (en) * | 2010-05-17 | 2012-12-12 | 浙江大学 | Cutterhead closed type hydraulic drive system adopting revolving speed-variable and displacement-variable compound control |
| CN103953356A (en) * | 2014-04-28 | 2014-07-30 | 北京市三一重机有限公司 | Open type shield machine, support device and control system and control method of support device |
| CN104019064A (en) * | 2014-06-03 | 2014-09-03 | 三一汽车制造有限公司 | Closed pump hydraulic system, closed pump and engineering machinery |
| CN104196785A (en) * | 2014-07-22 | 2014-12-10 | 西安交通大学 | Closed type energy-saving type shielding propelling hydraulic system adopting multi-union-pump driving |
| CN105179330A (en) * | 2015-09-09 | 2015-12-23 | 华澳轮胎设备科技（苏州）股份有限公司 | Hydraulic station control system and control method thereof |
| CN105179330B (en) * | 2015-09-09 | 2018-04-17 | 华澳轮胎设备科技（苏州）股份有限公司 | A kind of hydraulic station control system and its control method |
| CN108286544A (en) * | 2018-02-05 | 2018-07-17 | 北京航空航天大学 | The high rotating speed of aviation pump of throttling volume complex controll drives servo-drive system |
| CN110633525A (en) * | 2019-09-12 | 2019-12-31 | 辽宁石油化工大学 | Method and device for optimizing energy consumption of earth pressure balance shield machine system |
| CN110633525B (en) * | 2019-09-12 | 2023-04-07 | 辽宁石油化工大学 | Method and device for optimizing energy consumption of earth pressure balance shield machine system |
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