CN203175567U - Energy-saving type shield segment assembling positioning electrohydraulic control system adopting load-sensitive technology - Google Patents
Energy-saving type shield segment assembling positioning electrohydraulic control system adopting load-sensitive technology Download PDFInfo
- Publication number
- CN203175567U CN203175567U CN 201320004112 CN201320004112U CN203175567U CN 203175567 U CN203175567 U CN 203175567U CN 201320004112 CN201320004112 CN 201320004112 CN 201320004112 U CN201320004112 U CN 201320004112U CN 203175567 U CN203175567 U CN 203175567U
- Authority
- CN
- China
- Prior art keywords
- oil
- valve
- control valves
- pressure
- direction control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 238000005516 engineering process Methods 0.000 title claims abstract description 18
- 238000006073 displacement reaction Methods 0.000 claims abstract description 17
- 239000012530 fluid Substances 0.000 claims description 55
- 230000033001 locomotion Effects 0.000 claims description 29
- 239000002828 fuel tank Substances 0.000 claims description 20
- 239000000523 sample Substances 0.000 claims description 8
- 230000000694 effects Effects 0.000 abstract description 9
- 230000008859 change Effects 0.000 abstract description 5
- 230000008901 benefit Effects 0.000 abstract description 3
- 239000002699 waste material Substances 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 175
- 238000000034 method Methods 0.000 description 18
- 230000008569 process Effects 0.000 description 15
- 238000010276 construction Methods 0.000 description 10
- 230000005611 electricity Effects 0.000 description 6
- 239000010720 hydraulic oil Substances 0.000 description 6
- 238000009412 basement excavation Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000011897 real-time detection Methods 0.000 description 3
- 230000035939 shock Effects 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000003044 adaptive effect Effects 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
The utility model discloses an energy-saving type shield segment assembling positioning electrohydraulic control system adopting the load-sensitive technology. The energy-saving type shield segment assembling positioning electrohydraulic control system adopting the load-sensitive technology comprises a motor, a variable pump, a two-position and three-way proportional directional valve, a variable cylinder, an overflow valve, a reducing valve, a pressure-compensated valve, a one-way valve, a multiway valve, a balance valve, a hydraulic lock, a hydraulic motor, hydraulic cylinders, a torque rotation speed sensor, a displacement sensor and a pressure sensor. According to the energy-saving type shield segment assembling positioning electrohydraulic control system adopting the load-sensitive technology, the multiway valve provided with the pressure-compensated valve is adopted to control the rotating speed of the hydraulic motor driving a segment erector to rotate and the moving speeds of the hydraulic cylinders, the pressure sensor detects the pressure of the main oil circuit of the system and the working pressures of actuators, a computer control unit determines a variable pump control signal according to a pressure signal of the system to enable the output of the variable pump to change along with load change, and then load sensitive control is achieved. The energy-saving type shield segment assembling positioning electrohydraulic control system adopting the load-sensitive technology has the advantages that energy waste of a traditional system due to the fact that oil is supplied according to the maximum working pressure all the time is avoided, throttling loss and spill loss are greatly reduced, and the remarkable energy-saving effect is achieved.
Description
Technical field
The utility model relates to fluid pressure actuator, relates in particular to a kind of energy-saving type shield pipe sheet assembling location electrohydraulic control system that adopts the load-sensitive technology.
Background technology
Shield excavation machine is a kind of modernized high-tech digging device that is widely used in the subterranean tunnel engineering construction, and technology such as its collection is mechanical, electrical, liquid, control are one, have realized mechanization, the automation of tunnel excavation.Compare with traditional job practices, have construction safety, fast, advantage such as workmanship is high, the ground disturbance is little, labour intensity is low.As the construction machinery of highly energy-consuming, shield excavation machine just develops towards the direction of high efficiency, low energy consumption.
Duct piece assembling machine is the important component part of shield structure, after shield structure advance distance reaches an endless tube sheet width, duct piece assembling machine grasping pipe piece from the waggon of section of jurisdiction, shield structure rear, by rotation, radial expansion and three setting movements of horizontal sliding the section of jurisdiction is transported to space appointed positions point then, after the one endless tube sheet installation, tighten the connecting bolt between the section of jurisdiction, form lining cutting, to support the tunnel of firm excavation, the shield structure begins the propelling operation of next ring then.Pipe sheet assembling is that the shield-tunneling construction tunnel is shaped a most key step, and the operating characteristic of assembly unit mechanism is directly connected to tunnel quality and efficiency of construction.
The shield segment assembling system has the advantages that the assembly unit workload is big, the load variations scope is wide.The loading moment of duct piece assembling machine motor in rotary course rotates with assembling machine and changes, there is very big-difference in load between this inner rotary, radial expansion and three motions of horizontal sliding, the horse-controlling of in-line throttle grverning valve reaches, the system form of valve control hydraulic cylinder if adopt, the system charge oil pressure inevitable during according to the maximum functional load required system pressure set, this makes when system works under low loading condition, system effectiveness is low, system's heating is serious, this will influence equipment life, and tunnel construction environment is worsened.Adopting the energy-saving type shield pipe sheet assembling location electrohydraulic control system of load-sensitive technology is to improve the effective way of assembling system efficient, can realize the Adaptive Control of system pressure, reduces throttling and the spill losses of system.Usually the tunnel is formed by tens0000 even hundreds of thousands piece pipe sheet assembling, and it is very apparent therefore to improve assembling system operating efficiency energy-saving effect in the shield-tunneling construction process.
Summary of the invention
Take into account the requirement of satisfying shield-tunneling construction in order to overcome the problem that exists in the shield-tunneling construction process in the background technology, the utility model provides a kind of energy-saving type shield pipe sheet assembling location electrohydraulic control system that adopts the load-sensitive technology, both can realize pipe sheet assembling accurate positioning control, can realize the control of total system load-sensitive again, greatly reduce energy loss, improve lifetime of system, improve construction environment.
The technical scheme that the utility model technical solution problem adopts comprises:
A kind of energy-saving type shield pipe sheet assembling location electrohydraulic control system that adopts the load-sensitive technology is characterized in that comprising: motor, variable pump, the two-position three way proportional reversing valve, variable cylinder, first overflow valve, reducing valve, first pressure-compensated valve, second pressure-compensated valve, the 3rd pressure-compensated valve, first one way valve, second one way valve, the 3rd one way valve, first pressure sensor, second pressure sensor, the 3rd pressure sensor, the 4th pressure sensor, first banked direction control valves, second banked direction control valves, the 3rd banked direction control valves, first equalizing valve, second equalizing valve, the 3rd equalizing valve, the 4th equalizing valve, second overflow valve, the 3rd overflow valve, hydraulic motor, the moment speed probe, first hydraulic cylinder, second hydraulic cylinder, first displacement transducer, second displacement transducer, the 3rd hydraulic cylinder, hydraulic lock, the triple motion sensor, high-pressure oil pipe, low pressure pipe, oil return pipe; Motor and variable pump are rigidly connected; The inlet port S of variable pump is communicated with fuel tank, and the oil-out P of variable pump is communicated with the oil-in A4 of the oil inlet P 6 of the oil inlet P 5 of first overflow valve, reducing valve, pressure piping, variable cylinder respectively; The oil-out A5 of variable cylinder is communicated with two-position three way proportional reversing valve oil inlet P 3; Two-position three way proportional reversing valve oil-out B3 is communicated with the oil-in B4 of variable cylinder, and two-position three way proportional reversing valve oil return inlet T 3 is communicated with fuel tank; The oil-out T5 of first overflow valve is communicated with fuel tank; The oil-out T6 of reducing valve is communicated with guide's hydraulic fluid port x1, guide's hydraulic fluid port x2 of first banked direction control valves, guide's hydraulic fluid port x5, guide's hydraulic fluid port x6 of second banked direction control valves of second banked direction control valves, guide's hydraulic fluid port x9 of the 3rd banked direction control valves, guide's hydraulic fluid port x10 of the 3rd banked direction control valves of first banked direction control valves; High-pressure oil pipe is communicated with the oil inlet P 7 of first pressure-compensated valve, the oil inlet P 12 of second pressure-compensated valve, the oil inlet P 13 of the 3rd pressure-compensated valve respectively; The oil-out T7 of first pressure-compensated valve, the oil-out T12 of second pressure-compensated valve, the oil-out T13 of the 3rd pressure-compensated valve respectively with the oil inlet P 8 of first one way valve, the oil inlet P 14 of second one way valve, the oil inlet P 15 of the 3rd one way valve is communicated with, the oil-out T8 of first one way valve is communicated with the left control port x3 of the oil inlet P 10 of first banked direction control valves and first pressure-compensated valve, the oil-out T14 of second one way valve is communicated with the left control port x7 of the oil inlet P 16 of second banked direction control valves and second pressure-compensated valve, and the oil-out T15 of the 3rd one way valve is communicated with the left control port x11 of the oil inlet P 17 of the 3rd banked direction control valves and the 3rd pressure-compensated valve; The oil return inlet T 17b of the oil return inlet T 17a of the oil return inlet T 16b of the oil return inlet T 16a of the oil return inlet T 10b of the oil return inlet T 10a of first banked direction control valves, first banked direction control valves, second banked direction control valves, second banked direction control valves, the 3rd banked direction control valves, the 3rd banked direction control valves is communicated with low pressure pipe respectively, and low pressure pipe is communicated with fuel tank by oil return pipe; The oil-out B10a of first banked direction control valves and the oil-out A10b of first banked direction control valves link together and are communicated with the right control port x4 of first pressure-compensated valve, and the oil-out B10 of first banked direction control valves and the oil-out A10 of first banked direction control valves are communicated with the oil inlet P 11 of first equalizing valve 11.1 and the oil inlet P 21 of second equalizing valve respectively; The oil-out B16a of second banked direction control valves and the oil-out A16b of second banked direction control valves link together and are communicated with the right control port x8 of second pressure-compensated valve, and the oil-out B16 of second banked direction control valves and the oil-out A16 of second banked direction control valves are communicated with the oil inlet P 22 of the 3rd equalizing valve and the oil inlet P 23 of the 4th equalizing valve respectively; The oil-out B17a of the 3rd banked direction control valves and A17b link together and are communicated with the right control port x12 of the 3rd pressure-compensated valve, and the oil-out B17 of the 3rd banked direction control valves and the oil-out A17 of the 3rd banked direction control valves are communicated with the oil inlet P 18 of hydraulic lock and the oil inlet P 19 of hydraulic lock respectively; The oil-out T11 of first equalizing valve is communicated with oil inlet P 24, the oil-out T25 of the 3rd overflow valve, the actuator port A13 of hydraulic motor of the control port x14 of second equalizing valve, second overflow valve; The oil-out T21 of second equalizing valve is communicated with the oil-out T24 of the control port x13 of first equalizing valve, second overflow valve, the oil inlet P 25 of the 3rd overflow valve, the actuator port B13 of hydraulic motor; The oil-out T22 of the 3rd equalizing valve is communicated with the rodless cavity hydraulic fluid port of the control port x16 of the 4th equalizing valve, first hydraulic cylinder, the rodless cavity hydraulic fluid port of second hydraulic cylinder, and the 4th equalizing valve oil-out T23 is communicated with control port x15, the first hydraulic cylinder rod chamber hydraulic fluid port, the second hydraulic cylinder rod chamber hydraulic fluid port of the 3rd equalizing valve; The oil-out T18 of hydraulic lock is communicated with the 3rd hydraulic cylinder rodless cavity hydraulic fluid port, and the oil-out T19 of hydraulic lock is communicated with the rod chamber hydraulic fluid port of the 3rd hydraulic cylinder; The moment speed probe is fixedly mounted on the hydraulic motor output shaft; First displacement transducer, housing and the extension bar of second displacement transducer and triple motion sensor are separately fixed at first hydraulic cylinder, on the cylinder body and piston rod of second hydraulic cylinder and the 3rd hydraulic cylinder, first pressure sensor is communicated with the first banked direction control valves oil-out B10a and the first banked direction control valves oil-out A10b, second pressure sensor is communicated with the second banked direction control valves oil-out B16a and the second banked direction control valves oil-out A16b, the 3rd pressure sensor is communicated with the 3rd banked direction control valves oil-out B17a and the 3rd banked direction control valves oil-out A17b, and the 4th pressure sensor is installed on the oil-out P place oil pipe of variable pump.
The utility model is compared with background technology, and the beneficial effect that has is:
1) hydraulic motor and hydraulic cylinder are equipped with moment speed probe and displacement transducer respectively in the system, can realize rotatablely moving, the closed-loop control of radial expansion motion and horizontal sliding motion, realize the accurately control of pipe sheet assembling location, improve the constructing tunnel quality.
2) adopt the banked direction control valves have pressure-compensated valve can obtain good pressure flow characteristics auto as the control element of motor and hydraulic cylinder, reduce non-linear between valve control signal and the output flow, reduce the control difficulty, improve assembly unit motion control precision.
3) adopt the load-sensitive technology, make the output pressure of variable pump change with load variations, greatly reduced system's restriction loss and spill losses, improved system effectiveness, energy-saving effect is outstanding in growing apart from the constructing tunnel process.
Description of drawings
Fig. 1 is the concrete principle schematic of implementing of the utility model.
Among the figure: 1. motor, 2. variable pump, 3. two-position three way proportional reversing valve, 4. variable cylinder, 5. first overflow, 6. reducing valve, 7.1. first pressure-compensated valve, 7.2. second pressure-compensated valve, 7.3. the 3rd pressure-compensated valve, 8.1. first one way valve, 8.2. second one way valve, 8.3. the 3rd one way valve, 9.1. first pressure sensor, 9.2. second pressure sensor, 9.3. the 3rd pressure sensor, 10.1. first banked direction control valves, 10.2. second banked direction control valves, 10.3. the 3rd banked direction control valves, 11.1. first equalizing valve, 11.2. second equalizing valve, 11.3. the 3rd equalizing valve, 11.4. the 4th equalizing valve, 12.1. second overflow valve, 12.2. the 3rd overflow valve, 13. hydraulic motors, 14. moment speed probe, 15.1. first hydraulic cylinder, 15.2. second hydraulic cylinder, 16.1. first displacement transducer, 16.2. second displacement transducer 17. the 3rd hydraulic cylinder, 18. hydraulic lock, 19. triple motion sensors, 20. high-pressure oil pipes, 21. low pressure pipe, 22. oil return pipes.
The specific embodiment
The utility model is described in further detail below in conjunction with drawings and Examples.
As shown in drawings, a kind of energy-saving type shield pipe sheet assembling location electrohydraulic control system that adopts the load-sensitive technology is characterized in that comprising: motor 1, variable pump 2, two-position three way proportional reversing valve 3, variable cylinder 4, first overflow valve 5, reducing valve 6, first pressure-compensated valve 7.1, second pressure-compensated valve 7.2, the 3rd pressure-compensated valve 7.3, first one way valve 8.1, second one way valve 8.2, the 3rd one way valve 8.3, first pressure sensor 9.1, second pressure sensor 9.2, the 3rd pressure sensor 9.3, the 4th pressure sensor 9.4, first banked direction control valves 10.1, second banked direction control valves 10.2, the 3rd banked direction control valves 10.3, first equalizing valve 11.1, second equalizing valve 11.2, the 3rd equalizing valve 11.3, the 4th equalizing valve 11.4, second overflow valve 12.1, the 3rd overflow valve 12.2, hydraulic motor 13, moment speed probe 14, first hydraulic cylinder 15.1, second hydraulic cylinder 15.2, first displacement transducer 16.1, second displacement transducer 16.2, the 3rd hydraulic cylinder 17, hydraulic lock 18, triple motion sensor 19, high-pressure oil pipe 20, low pressure pipe 21, oil return pipe 22; Motor 1 is rigidly connected with variable pump 2; The inlet port S of variable pump 2 is communicated with fuel tank, and the oil-out P of variable pump 2 is communicated with the oil-in A4 of the oil inlet P 6 of the oil inlet P 5 of first overflow valve 5, reducing valve 6, pressure piping 20, variable cylinder 4 respectively; The oil-out A5 of variable cylinder 4 is communicated with two-position three way proportional reversing valve 3 oil inlet P 3; Two-position three way proportional reversing valve 3 oil-out B3 are communicated with the oil-in B4 of variable cylinder 4, and two-position three way proportional reversing valve 3 oil return inlet T 3 are communicated with fuel tank; The oil-out T5 of first overflow valve 5 is communicated with fuel tank; The oil-out T6 of reducing valve 6 is communicated with guide's hydraulic fluid port x1, guide's hydraulic fluid port x2 of first banked direction control valves 10.1, guide's hydraulic fluid port x5, guide's hydraulic fluid port x6 of second banked direction control valves 10.2 of second banked direction control valves 10.2, guide's hydraulic fluid port x9 of the 3rd banked direction control valves 10.3, guide's hydraulic fluid port x10 of the 3rd banked direction control valves 10.3 of first banked direction control valves 10.1; High-pressure oil pipe 20 is communicated with the oil inlet P 7 of first pressure-compensated valve 7.1, the oil inlet P 12 of second pressure-compensated valve 7.2, the oil inlet P 13 of the 3rd pressure-compensated valve 7.3 respectively; The oil-out T7 of first pressure-compensated valve 7.1, the oil-out T12 of second pressure-compensated valve 7.2, the oil-out T13 of the 3rd pressure-compensated valve 7.3 respectively with the oil inlet P 8 of first one way valve 8.1, the oil inlet P 14 of second one way valve 8.2, the oil inlet P 15 of the 3rd one way valve 8.3 is communicated with, the oil-out T8 of first one way valve 8.1 is communicated with the left control port x3 of the oil inlet P 10 of first banked direction control valves 10.1 and first pressure-compensated valve 7.1, the oil-out T14 of second one way valve 8.2 is communicated with the left control port x7 of the oil inlet P 16 of second banked direction control valves 10.2 and second pressure-compensated valve 7.2, and the oil-out T15 of the 3rd one way valve 8.3 is communicated with the left control port x11 of the oil inlet P 17 of the 3rd banked direction control valves 10.3 and the 3rd pressure-compensated valve 7.3; The oil return inlet T 17b of the oil return inlet T 17a of the oil return inlet T 16b of the oil return inlet T 16a of the oil return inlet T 10b of the oil return inlet T 10a of first banked direction control valves 10.1, first banked direction control valves 10.1, second banked direction control valves 10.2, second banked direction control valves 10.2, the 3rd banked direction control valves 10.3, the 3rd banked direction control valves 10.3 is communicated with low pressure pipe 21 respectively, and low pressure pipe 21 is communicated with fuel tank by oil return pipe 22; The oil-out A10b of the oil-out B10a of first banked direction control valves 10.1 and first banked direction control valves 10.1 links together and is communicated with the right control port x4 of first pressure-compensated valve 7.1, and the oil-out A10 of the oil-out B10 of first banked direction control valves 10.1 and first banked direction control valves 10.1 is communicated with the oil inlet P 11 of first equalizing valve 11.1 and the oil inlet P 21 of second equalizing valve respectively; The oil-out A16b of the oil-out B16a of second banked direction control valves 10.2 and second banked direction control valves 10.2 links together and is communicated with the right control port x8 of second pressure-compensated valve 7.2, and the oil-out A16 of the oil-out B16 of second banked direction control valves 10.2 and second banked direction control valves 10.2 is communicated with the oil inlet P 22 of the 3rd equalizing valve 11.3 and the oil inlet P 23 of the 4th equalizing valve 11.4 respectively; The oil-out B17a of the 3rd banked direction control valves 10.3 and A17b link together and are communicated with the right control port x12 of the 3rd pressure-compensated valve 7.3, and the oil-out A17 of the oil-out B17 of the 3rd banked direction control valves 10.3 and the 3rd banked direction control valves 10.3 is communicated with the oil inlet P 18 of hydraulic lock 18 and the oil inlet P 19 of hydraulic lock 18 respectively; The oil-out T11 of first equalizing valve 11.1 is communicated with control port x14, the oil inlet P 24 of second overflow valve 12.1, the oil-out T25 of the 3rd overflow valve 12.2, the actuator port A13 of hydraulic motor 13 of second equalizing valve 11.2; The oil-out T21 of second equalizing valve 11.2 is communicated with the control port x13 of first equalizing valve 11.1, the oil-out T24 of second overflow valve 12.1, the oil inlet P 25 of the 3rd overflow valve 12.2, the actuator port B13 of hydraulic motor 13; The oil-out T22 of the 3rd equalizing valve 11.3 is communicated with the control port x16 of the 4th equalizing valve 11.4, the rodless cavity hydraulic fluid port of first hydraulic cylinder 15.1, the rodless cavity hydraulic fluid port of second hydraulic cylinder 15.2, and the 4th equalizing valve 11.4 oil-out T23 are communicated with control port x15, first hydraulic cylinder, 15.1 rod chamber hydraulic fluid ports, second hydraulic cylinder, the 15.2 rod chamber hydraulic fluid ports of the 3rd equalizing valve 11.3; The oil-out T18 of hydraulic lock 18 is communicated with the 3rd hydraulic cylinder 17 rodless cavity hydraulic fluid ports, and the oil-out T19 of hydraulic lock 18 is communicated with the rod chamber hydraulic fluid port of the 3rd hydraulic cylinder 17; Moment speed probe 14 is fixedly mounted on the output shaft of hydraulic motor 13; First displacement transducer 16.1, housing and the extension bar of second displacement transducer 16.2 and triple motion sensor 19 are separately fixed at first hydraulic cylinder 15.1, on the cylinder body and piston rod of second hydraulic cylinder 15.2 and the 3rd hydraulic cylinder 17, first pressure sensor 9.1 is communicated with first banked direction control valves, 10.1 oil-out B10a and first banked direction control valves, 10.1 oil-out A10b, second pressure sensor 9.2 is communicated with second banked direction control valves, 10.2 oil-out B16a and second banked direction control valves, 10.2 oil-out A16b, the 3rd pressure sensor 9.3 is communicated with the 3rd banked direction control valves 10.3 oil-out B17a and the 3rd banked direction control valves 10.3 oil-out A17b, and the 4th pressure sensor 9.4 is installed on the oil-out P place oil pipe of variable pump 3.Operating principle of the present utility model is as follows:
Motor 1 gets electric startup, driving variable pump 2 rotates, variable pump 2 is by inlet port S oil suction from fuel tank, and the pressure oil of variable pump 2 outputs is by the oil-in A4 of oil-out P difference entering variable cylinder 4, the oil inlet P 5 of overflow valve 5, oil inlet P 6 and the high-pressure oil pipe 20 of reducing valve 6.
When the hydraulic motor 13 that drives the duct piece assembling machine rotation turns clockwise, the actuator port A13 of motor is the high pressure hydraulic fluid port, actuator port B13 is the low pressure hydraulic fluid port, this moment, the pilot valve electromagnet b1 of banked direction control valves 10.1 got, enter banked direction control valves 10.1 main valve plug cavity of resorptions from system's control oil that the oil-out T6 of reducing valve 6 flows out by control port x2, make the oil inlet P 10 of banked direction control valves 10.1 be communicated with B10, B10a, oil return inlet T 10b is communicated with A10.System pressure oil flows out the oil inlet P 7 that enters pressure-compensated valve 7.1 from high-pressure oil pipe 20, flow out the oil inlet P 8 that enters one way valve 8.1 from pressure-compensated valve 7.1 oil-out T7 then, flow out the oil inlet P 10 that enters banked direction control valves 10.1 from the oil-out T8 of one way valve 8.1, enter the oil inlet P 11 of equalizing valve 11.1 by the oil-out B10 of banked direction control valves 10.1, enter the actuator port A13 of hydraulic motor 13 then by the oil-out T11 of equalizing valve 11.1, motor 13 clockwise rotates, hydraulic oil flows out the oil-out T21 that enters equalizing valve 11.2 by the actuator port B13 of hydraulic motor 13, oil inlet P 21 from equalizing valve 11.2 flows out the oil-out A10 that enters banked direction control valves 10.1 then, oil return inlet T 10b from banked direction control valves 10.1 flows into low pressure pipe 21 subsequently, and low pressure pipe 21 is communicated with fuel tank by oil return pipe 22.In the revolution process, the oil inlet P 10 of banked direction control valves 10.1 is communicated with the control port x3 of pressure-compensated valve 7.1, the oil-out B10 of banked direction control valves 10.1 is communicated with the control port x4 of pressure-compensated valve 7.1, thereby is making the oil inlet P 10 of banked direction control valves 10.1 and the pressure differential between its oil-out B10 keep a constant value under the effect of pressure-compensated valve 7.1.Behind the revolution predetermined angular, the pilot valve electromagnet b1 dead electricity of banked direction control valves 10.1, banked direction control valves 10.1 is operated in meta, the oil inlet P 10 of banked direction control valves 10.1 is closed, oil-out A10, B10 are communicated with T10a with oil return inlet T 10b respectively, equalizing valve 11.1 is operated in position, a left side, and duct piece assembling machine is locked at the target location.
When the hydraulic motor 13 that drives the duct piece assembling machine rotation is rotated counterclockwise, the actuator port B13 of motor is the high pressure hydraulic fluid port, actuator port A13 is the low pressure hydraulic fluid port, this moment, the pilot valve electromagnet a1 of banked direction control valves 10.1 got, enter banked direction control valves 10.1 main valve plug epicoeles from system's control oil that the oil-out T6 of reducing valve 6 flows out by control port x1, make the oil inlet P 10 of banked direction control valves 10.1 be communicated with A10, A10b, oil return inlet T 10a is communicated with B10.System pressure oil flows out the oil inlet P 7 that enters pressure-compensated valve 7.1 from high-pressure oil pipe 20, flow out the oil inlet P 8 that enters one way valve 8.1 from pressure-compensated valve 7.1 oil-out T7 then, flow out the oil inlet P 10 that enters banked direction control valves 10.1 from the oil-out T8 of one way valve 8.1, enter the oil inlet P 21 of equalizing valve 11.2 by the oil-out A10 of banked direction control valves 10.1, enter the actuator port B13 of hydraulic motor 13 then by the oil-out T21 of equalizing valve 11.2, motor 13 rotates counterclockwise, hydraulic oil flows out the oil-out T11 that enters equalizing valve 11.1 by the actuator port A13 of hydraulic motor 13, oil inlet P 11 from equalizing valve 11.1 flows out the oil-out B10 that enters banked direction control valves 10.1 then, oil return inlet T 10a from banked direction control valves 10.1 flows into low pressure pipe 21 subsequently, and low pressure pipe 21 is communicated with fuel tank by oil return pipe 22.In the revolution process, the oil inlet P 10 of banked direction control valves 10.1 is communicated with the control port x3 of pressure-compensated valve 7.1, the oil-out B10 of banked direction control valves 10.1 is communicated with the control port x4 of pressure-compensated valve 7.1, thereby is making the oil inlet P 10 of banked direction control valves 10.1 and the pressure differential between its oil-out B10 keep a constant value under the effect of pressure-compensated valve 7.1.Behind the revolution predetermined angular, the pilot valve electromagnet a1 dead electricity of banked direction control valves 10.1, banked direction control valves 10.1 is operated in meta, the oil inlet P 10 of banked direction control valves 10.1 is closed, oil-out A10, B10 are communicated with T10a with oil return inlet T 10b respectively, equalizing valve 11.2 is operated in right position, and duct piece assembling machine is locked at the target location.
When driving duct piece assembling machine radial expansion hydraulic cylinder 15.1,15.2 when up, hydraulic cylinder 15.1,15.2 rod chamber actuator port are the high pressure hydraulic fluid port, the rodless cavity actuator port is the low pressure hydraulic fluid port, this moment, the pilot valve electromagnet a2 of banked direction control valves 10.2 got, enter banked direction control valves 10.2 main valve plug epicoeles from system's control oil that the oil-out T6 of reducing valve 6 flows out by control port x5, make the oil inlet P 16 of banked direction control valves 10.2 be communicated with A16, A16b, oil return inlet T 16a is communicated with B16.System pressure oil flows out the oil inlet P 12 that enters pressure-compensated valve 7.2 from high-pressure oil pipe 20, flow out the oil inlet P 14 that enters one way valve 8.2 from pressure-compensated valve 7.2 oil-out T12 then, flow out the oil inlet P 16 that enters banked direction control valves 10.2 from the oil-out T14 of one way valve 8.2, enter the oil inlet P 23 of equalizing valve 11.4 by the oil-out A16 of banked direction control valves 10.2, oil-out T23 by equalizing valve 11.4 enters hydraulic cylinder 15.1 then, 15.2 the rod chamber actuator port, hydraulic cylinder 15.1,15.2 move upward, hydraulic oil is by hydraulic cylinder 15.1,15.2 the rodless cavity actuator port flows out the oil-out T22 that enters equalizing valve 11.3, oil inlet P 22 from equalizing valve 11.3 flows out the oil-out B16 that enters banked direction control valves 10.2 then, oil return inlet T 16a from banked direction control valves 10.2 flows into low pressure pipe 21 subsequently, and low pressure pipe 21 is communicated with fuel tank by oil return pipe 22.In the hydraulic cylinder motion process, the oil inlet P 16 of banked direction control valves 10.2 is communicated with the control port x7 of pressure-compensated valve 7.2, the oil-out A16 of banked direction control valves 10.2 is communicated with the control port x8 of pressure-compensated valve 7.2, thereby is making the oil inlet P 16 of banked direction control valves 10.2 and the pressure differential between its oil-out B16 keep a constant value under the effect of pressure-compensated valve 7.2.After hydraulic cylinder moves to the precalculated position, the pilot valve electromagnet a2 dead electricity of banked direction control valves 10.2, banked direction control valves 10.2 is operated in meta, the oil inlet P 16 of banked direction control valves 10.2 is closed, oil-out A16, B16 are communicated with T16a with oil return inlet T 16b respectively, equalizing valve 11.4 is operated in right position, and duct piece assembling machine is locked at the target location.
When driving duct piece assembling machine radial expansion hydraulic cylinder 15.1,15.2 when descending, hydraulic cylinder 15.1,15.2 rodless cavity actuator port are the high pressure hydraulic fluid port, the rod chamber actuator port is the low pressure hydraulic fluid port, this moment, the pilot valve electromagnet b2 of banked direction control valves 10.2 got, enter banked direction control valves 10.2 main valve plug cavity of resorptions from system's control oil that the oil-out T6 of reducing valve 6 flows out by control port x6, make the oil inlet P 16 of banked direction control valves 10.2 be communicated with B16, B16a, oil return inlet T 16b is communicated with A16.System pressure oil flows out the oil inlet P 12 that enters pressure-compensated valve 7.2 from high-pressure oil pipe 20, flow out the oil inlet P 14 that enters one way valve 8.2 from pressure-compensated valve 7.2 oil-out T12 then, flow out the oil inlet P 16 that enters banked direction control valves 10.2 from the oil-out T14 of one way valve 8.2, enter the oil inlet P 22 of equalizing valve 11.3 by the oil-out B16 of banked direction control valves 10.2, oil-out T22 by equalizing valve 11.3 enters hydraulic cylinder 15.1 then, 15.2 the rodless cavity actuator port, hydraulic cylinder 15.1,15.2 move downward, hydraulic oil is by hydraulic cylinder 15.1,15.2 the rod chamber actuator port flows out the oil-out T23 that enters equalizing valve 11.4, oil inlet P 23 from equalizing valve 11.4 flows out the oil-out A16 that enters banked direction control valves 10.2 then, oil return inlet T 16b from banked direction control valves 10.2 flows into low pressure pipe 21 subsequently, and low pressure pipe 21 is communicated with fuel tank by oil return pipe 22.In the hydraulic cylinder motion process, the oil inlet P 16 of banked direction control valves 10.2 is communicated with the control port x7 of pressure-compensated valve 7.2, the oil-out B16 of banked direction control valves 10.2 is communicated with the control port x8 of pressure-compensated valve 7.2, thereby is making the oil inlet P 16 of banked direction control valves 10.2 and the pressure differential between its oil-out B16 keep a constant value under the effect of pressure-compensated valve 7.2.After hydraulic cylinder moves to the precalculated position, the pilot valve electromagnet b2 dead electricity of banked direction control valves 10.2, banked direction control valves 10.2 is operated in meta, the oil inlet P 16 of banked direction control valves 10.2 is closed, oil-out A16, B16 are communicated with T16a with oil return inlet T 16b respectively, equalizing valve 11.3 is operated in position, a left side, and duct piece assembling machine is locked at the target location.
When driving hydraulic cylinder 17 right laterals of duct piece assembling machine horizontal sliding, the rodless cavity actuator port of hydraulic cylinder 17 is the high pressure hydraulic fluid port, the rod chamber actuator port is the low pressure hydraulic fluid port, this moment, the pilot valve electromagnet b3 of banked direction control valves 10.3 got, enter banked direction control valves 10.3 main valve plug cavity of resorptions from system's control oil that the oil-out T6 of reducing valve 6 flows out by control port x10, make the oil inlet P 17 of banked direction control valves 10.3 be communicated with B17, B17a, oil return inlet T 17b is communicated with A17.System pressure oil flows out the oil inlet P 13 that enters pressure-compensated valve 7.3 from high-pressure oil pipe 20, flow out the oil inlet P 15 that enters one way valve 8.3 from pressure-compensated valve 7.3 oil-out T13 then, flow out the oil inlet P 17 that enters banked direction control valves 10.3 from the oil-out T15 of one way valve 8.3, enter the oil inlet P 18 of hydraulic lock 18 by the oil-out B17 of banked direction control valves 10.3, enter the rodless cavity actuator port of hydraulic cylinder 17 then by the oil-out T18 of hydraulic lock 18, hydraulic cylinder 17 moves right, hydraulic oil flows out by hydraulic cylinder 17 rod chamber actuator ports and enters the oil-out T19 of hydraulic lock 18, oil inlet P 19 from hydraulic lock 18 flows out the oil-out A17 that enters banked direction control valves 10.3 then, oil return inlet T 17b from banked direction control valves 10.3 flows into low pressure pipe 21 subsequently, and low pressure pipe 21 is communicated with fuel tank by oil return pipe 22.In the hydraulic cylinder motion process, the oil inlet P 17 of banked direction control valves 10.3 is communicated with the control port x11 of pressure-compensated valve 7.3, the oil-out B17 of banked direction control valves 10.3 is communicated with the control port x12 of pressure-compensated valve 7.3, thereby is making the oil inlet P 17 of banked direction control valves 10.3 and the pressure differential between its oil-out B17 keep a constant value under the effect of pressure-compensated valve 7.3.After hydraulic cylinder moves to the precalculated position, the pilot valve electromagnet b3 dead electricity of banked direction control valves 10.3, banked direction control valves 10.3 is operated in meta, the oil inlet P 17 of banked direction control valves 10.3 is closed, oil-out A17, B17 are communicated with T17a with oil return inlet T 17b respectively, hydraulic lock 18 left and right sides two-way are closed, and duct piece assembling machine is locked at the target location.
When driving hydraulic cylinder 17 left lateral of duct piece assembling machine horizontal sliding, the rod chamber actuator port of hydraulic cylinder 17 is the high pressure hydraulic fluid port, the rodless cavity actuator port is the low pressure hydraulic fluid port, this moment, the pilot valve electromagnet a3 of banked direction control valves 10.3 got, enter banked direction control valves 10.3 main valve plug epicoeles from system's control oil that the oil-out T6 of reducing valve 6 flows out by control port x9, make the oil inlet P 17 of banked direction control valves 10.3 be communicated with A17, A17b, oil return inlet T 17a is communicated with B17.System pressure oil flows out the oil inlet P 13 that enters pressure-compensated valve 7.3 from high-pressure oil pipe 20, flow out the oil inlet P 15 that enters one way valve 8.3 from pressure-compensated valve 7.3 oil-out T13 then, flow out the oil inlet P 17 that enters banked direction control valves 10.3 from the oil-out T15 of one way valve 8.3, enter the oil inlet P 19 of hydraulic lock 18 by the oil-out A17 of banked direction control valves 10.3, enter the rod chamber actuator port of hydraulic cylinder 17 then by the oil-out T19 of hydraulic lock 18, hydraulic cylinder 17 is to left movement, hydraulic oil flows out by hydraulic cylinder 17 rodless cavity actuator ports and enters the oil-out T18 of hydraulic lock 18, oil inlet P 18 from hydraulic lock 18 flows out the oil-out B17 that enters banked direction control valves 10.3 then, oil return inlet T 17a from banked direction control valves 10.3 flows into low pressure pipe 21 subsequently, and low pressure pipe 21 is communicated with fuel tank by oil return pipe 22.In the hydraulic cylinder motion process, the oil inlet P 17 of banked direction control valves 10.3 is communicated with the control port x11 of pressure-compensated valve 7.3, the oil-out A17 of banked direction control valves 10.3 is communicated with the control port x12 of pressure-compensated valve 7.3, thereby is making the oil inlet P 17 of banked direction control valves 10.3 and the pressure differential between its oil-out A17 keep a constant value under the effect of pressure-compensated valve 7.3.After hydraulic cylinder moves to the precalculated position, the pilot valve electromagnet a3 dead electricity of banked direction control valves 10.3, banked direction control valves 10.3 is operated in meta, the oil inlet P 17 of banked direction control valves 10.3 is closed, oil-out A17, B17 are communicated with T17a with oil return inlet T 17b respectively, hydraulic lock 18 left and right sides two-way are closed, and duct piece assembling machine is locked at the target location.
When occurring abnormal conditions in the system work process and cause system pressure to exceed normal value, overflow valve 5 is opened, and the fluid that variable pump 2 oil-out P flow out flows to overflow valve 5 through the oil inlet P 5 of overflow valve 5, flows back to fuel tank from the oil-out T5 of overflow valve 5, realizes off-load.In the rotation process of section of jurisdiction, because dynamic moment of inertia is bigger, the compression shock that produces in rotating starting and stopped process is eliminated by overflow valve 12.1,12.2, when surge during greater than the setting value of overflow valve 12.1 and 12.1, the compression shock at motor 13 actuator port A13 places enters overflow valve 12.1 by the oil inlet P 24 of overflow valve 12.1, pressure oil enters low pressure pipeline between motor hydraulic fluid port B13 and equalizing valve 11.1 oil-out T21 by 12.1 oil-out then, finishes pressure and discharges; The compression shock at motor 13 actuator port B13 places enters overflow valve 12.2 by the oil inlet P 25 of overflow valve 12.2, and pressure oil enters low pressure pipeline between motor hydraulic fluid port A13 and equalizing valve 11.2 oil-out T11 by 12.2 oil-out then, finishes pressure and discharges.
In the pipe sheet assembling position fixing process, system load is that the variation with duty changes.When duct piece assembling machine rotatablely moves, in the anglec of rotation from 0 ° to 90 ° the process, loading moment increases gradually with the increase of the anglec of rotation, experience is from 0 variation to maximum load moment, in the anglec of rotation from 90 ° to 180 ° the process, loading moment with the anglec of rotation reduce reduce gradually, experience is from the variation of maximum load moment to 0; In addition, when duct piece assembling machine is rotated motion, radial expansion motion and three kinds of motions of horizontal sliding respectively, load pressure also has nothing in common with each other, rotatablely moving will be much larger than the load of horizontal sliding with the load of radial expansion motion, adopt the energy-saving type shield pipe sheet assembling location electrohydraulic control system of load-sensitive technology can realize system's charge oil pressure with the load real-time change, the variable pump output pressure is complementary with load pressure all the time.Concrete control measure are:
Computer control unit control variables pumpage realizes that the course of work of load-sensitive is: computer control unit output control signal, control signal passes to the proportional amplifier of two-position three way proportional reversing valve 3 after the D/A conversion, control signal after the amplification passes to the proportion electro-magnet of two-position three way proportional reversing valve 3, the pressure of the more big then two-position three way of the input signal of proportion electro-magnet proportional reversing valve 3 output oil port B3 is more high, thereby make that the rodless cavity pressure of variable cylinder 4 is more high, it is more big that variable cylinder is moved to the left displacement, and pump delivery is more big; Otherwise, if the more little then variable of the output signal pump delivery of computer control unit is more little.I. duct piece assembling machine carries out gyration: be installed in the pressure sensor 9.4 real-time detection variable pump 2 output hydraulic fluid pressures on system's working connection; Load pressure when the pressure sensor 9.1 that is communicated with banked direction control valves 10.1 actuator port A10b and B10a detects hydraulic motor 13 rotations in real time.The motor operations pressure signal that pressure sensor 9.1 and 9.4 records and system's working connection pressure signal pass to computer control unit after changing through A/D, the difference of computer control unit computing system working connection pressure and motor operations pressure, the actual pressure difference and the set pressure differential that obtain are compared, when reducing to make the actual pressure difference greater than set pressure differential owing to load pressure, reduce the computer control unit output signal, thereby reduce pump delivery, the output flow of pump is reduced, the pressure of system's major loop reduces, and equates with set pressure differential until the actual pressure difference; Otherwise, when the increase owing to load pressure makes the actual pressure difference less than set pressure differential, then increase the computer control unit output signal, make variable cylinder to left movement, thereby increase pump delivery, make the output flow of pump become big, improve the pressure of system's major loop, equal set pressure differential until the actual pressure difference.This is pipe sheet assembling rotary system load-sensitive control procedure.II. duct piece assembling machine carries out the radial expansion motion: be installed in the pressure sensor 9.4 real-time detection variable pump 2 output hydraulic fluid pressures on system's working connection; Load pressure when the pressure sensor 9.2 that is communicated with banked direction control valves 10.2 actuator port A16b and B16a detects hydraulic cylinder 15.1,15.2 motions in real time.The hydraulic cylinder works pressure signal that pressure sensor 9.2 and 9.4 records and system's working connection pressure signal pass to computer control unit after changing through A/D, the difference of computer control unit computing system working connection pressure and hydraulic cylinder works pressure, the actual pressure difference and the set pressure differential that obtain are compared, when reducing to make the actual pressure difference greater than set pressure differential owing to load pressure, reduce the computer control unit output signal, thereby reduce pump delivery, the output flow of pump is reduced, the pressure of system's major loop reduces, and equates with set pressure differential until the actual pressure difference; Otherwise, when the increase owing to load pressure makes the actual pressure difference less than set pressure differential, then increase the computer control unit output signal, make variable cylinder to left movement, thereby increase pump delivery, make the output flow of pump become big, improve the pressure of system's major loop, equal set pressure differential until the actual pressure difference.This is the responsive control procedure of pipe sheet assembling radial expansion system load.III. duct piece assembling machine carries out the horizontal sliding motion: be installed in the pressure sensor 9.4 real-time detection variable pump 2 output hydraulic fluid pressures on system's working connection; Load pressure when the pressure sensor 9.3 that is communicated with banked direction control valves 10.3 actuator port A17b and B17a detects hydraulic cylinder 17 motions in real time.The hydraulic cylinder works pressure signal that pressure sensor 9.3 and 9.4 records and system's working connection pressure signal pass to computer control unit after changing through A/D, the difference of computer control unit computing system working connection pressure and hydraulic cylinder works pressure, the actual pressure difference and the set pressure differential that obtain are compared, when reducing to make the actual pressure difference greater than set pressure differential owing to load pressure, reduce the computer control unit output signal, thereby reduce pump delivery, the output flow of pump is reduced, the pressure of system's major loop reduces, and equates with set pressure differential until the actual pressure difference; Otherwise, when the increase owing to load pressure makes the actual pressure difference less than set pressure differential, then increase the computer control unit output signal, make variable cylinder to left movement, thereby increase pump delivery, make the output flow of pump become big, improve the pressure of system's major loop, equal set pressure differential until the actual pressure difference.This is the responsive control procedure of pipe sheet assembling horizontal sliding system load.
Load-sensitive control through above three systems, make the pump output pressure adapt with load pressure all the time, the generation of the two also keeps a rational difference, has both prevented from that flow system flow is too small to cause influencing motion control, can prevent from again that flow system flow is excessive to cause a large amount of spill lossess.
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. an energy-saving type shield pipe sheet assembling location electrohydraulic control system that adopts the load-sensitive technology is characterized in that comprising: motor (1), variable pump (2), two-position three way proportional reversing valve (3), variable cylinder (4), first overflow valve (5), reducing valve (6), first pressure-compensated valve (7.1), second pressure-compensated valve (7.2), the 3rd pressure-compensated valve (7.3), first one way valve (8.1), second one way valve (8.2), the 3rd one way valve (8.3), first pressure sensor (9.1), second pressure sensor (9.2), the 3rd pressure sensor (9.3), the 4th pressure sensor (9.4), first banked direction control valves (10.1), second banked direction control valves (10.2), the 3rd banked direction control valves (10.3), first equalizing valve (11.1), second equalizing valve (11.2), the 3rd equalizing valve (11.3), the 4th equalizing valve (11.4), second overflow valve (12.1), the 3rd overflow valve (12.2), hydraulic motor (13), moment speed probe (14), first hydraulic cylinder (15.1), second hydraulic cylinder (15.2), first displacement transducer (16.1), second displacement transducer (16.2), the 3rd hydraulic cylinder (17), hydraulic lock (18), triple motion sensor (19), high-pressure oil pipe (20), low pressure pipe (21), oil return pipe (22); Motor (1) is rigidly connected with variable pump (2); The inlet port S of variable pump (2) is communicated with fuel tank, and the oil-out P of variable pump (2) is communicated with the oil-in A4 of the oil inlet P 6 of the oil inlet P 5 of first overflow valve (5), reducing valve (6), pressure piping (20), variable cylinder (4) respectively; The oil-out A5 of variable cylinder (4) is communicated with two-position three way proportional reversing valve (3) oil inlet P 3; Two-position three way proportional reversing valve (3) oil-out B3 is communicated with the oil-in B4 of variable cylinder (4), and two-position three way proportional reversing valve (3) oil return inlet T 3 is communicated with fuel tank; The oil-out T5 of first overflow valve (5) is communicated with fuel tank; The oil-out T6 of reducing valve (6) is communicated with guide's hydraulic fluid port x1, guide's hydraulic fluid port x2 of first banked direction control valves (10.1), guide's hydraulic fluid port x5, guide's hydraulic fluid port x6 of second banked direction control valves (10.2) of second banked direction control valves (10.2), guide's hydraulic fluid port x9 of the 3rd banked direction control valves (10.3), guide's hydraulic fluid port x10 of the 3rd banked direction control valves (10.3) of first banked direction control valves (10.1); High-pressure oil pipe (20) is communicated with the oil inlet P 7 of first pressure-compensated valve (7.1), the oil inlet P 12 of second pressure-compensated valve (7.2), the oil inlet P 13 of the 3rd pressure-compensated valve (7.3) respectively; The oil-out T7 of first pressure-compensated valve (7.1), the oil-out T12 of second pressure-compensated valve (7.2), the oil-out T13 of the 3rd pressure-compensated valve (7.3) respectively with the oil inlet P 8 of first one way valve (8.1), the oil inlet P 14 of second one way valve (8.2), the oil inlet P 15 of the 3rd one way valve (8.3) is communicated with, the oil-out T8 of first one way valve (8.1) is communicated with the oil inlet P 10 of first banked direction control valves (10.1) and the left control port x3 of first pressure-compensated valve (7.1), the oil-out T14 of second one way valve (8.2) is communicated with the oil inlet P 16 of second banked direction control valves (10.2) and the left control port x7 of second pressure-compensated valve (7.2), and the oil-out T15 of the 3rd one way valve (8.3) is communicated with the oil inlet P 17 of the 3rd banked direction control valves (10.3) and the left control port x11 of the 3rd pressure-compensated valve (7.3); The oil return inlet T 17b of the oil return inlet T 17a of the oil return inlet T 16b of the oil return inlet T 16a of the oil return inlet T 10b of the oil return inlet T 10a of first banked direction control valves (10.1), first banked direction control valves (10.1), second banked direction control valves (10.2), second banked direction control valves (10.2), the 3rd banked direction control valves (10.3), the 3rd banked direction control valves (10.3) is communicated with low pressure pipe (21) respectively, and low pressure pipe (21) is communicated with fuel tank by oil return pipe (22); The oil-out A10b of the oil-out B10a of first banked direction control valves (10.1) and first banked direction control valves (10.1) links together and is communicated with the right control port x4 of first pressure-compensated valve (7.1), and the oil-out A10 of the oil-out B10 of first banked direction control valves (10.1) and first banked direction control valves (10.1) is communicated with the oil inlet P 11 of first equalizing valve 11.1 and the oil inlet P 21 of second equalizing valve respectively; The oil-out A16b of the oil-out B16a of second banked direction control valves (10.2) and second banked direction control valves (10.2) links together and is communicated with the right control port x8 of second pressure-compensated valve (7.2), and the oil-out A16 of the oil-out B16 of second banked direction control valves (10.2) and second banked direction control valves (10.2) is communicated with the oil inlet P 22 of the 3rd equalizing valve (11.3) and the oil inlet P 23 of the 4th equalizing valve (11.4) respectively; The oil-out B17a of the 3rd banked direction control valves (10.3) and A17b link together and are communicated with the right control port x12 of the 3rd pressure-compensated valve (7.3), and the oil-out A17 of the oil-out B17 of the 3rd banked direction control valves (10.3) and the 3rd banked direction control valves (10.3) is communicated with the oil inlet P 18 of hydraulic lock (18) and the oil inlet P 19 of hydraulic lock (18) respectively; The oil-out T11 of first equalizing valve (11.1) is communicated with control port x14, the oil inlet P 24 of second overflow valve (12.1), the oil-out T25 of the 3rd overflow valve (12.2), the actuator port A13 of hydraulic motor (13) of second equalizing valve (11.2); The oil-out T21 of second equalizing valve (11.2) is communicated with the control port x13 of first equalizing valve (11.1), the oil-out T24 of second overflow valve (12.1), the oil inlet P 25 of the 3rd overflow valve (12.2), the actuator port B13 of hydraulic motor (13); The oil-out T22 of the 3rd equalizing valve (11.3) is communicated with the control port x16 of the 4th equalizing valve (11.4), the rodless cavity hydraulic fluid port of first hydraulic cylinder (15.1), the rodless cavity hydraulic fluid port of second hydraulic cylinder (15.2), and the 4th equalizing valve (11.4) oil-out T23 is communicated with control port x15, first hydraulic cylinder (15.1) rod chamber hydraulic fluid port, second hydraulic cylinder (15.2) the rod chamber hydraulic fluid port of the 3rd equalizing valve (11.3); The oil-out T18 of hydraulic lock (18) is communicated with the 3rd hydraulic cylinder (17) rodless cavity hydraulic fluid port, and the oil-out T19 of hydraulic lock (18) is communicated with the rod chamber hydraulic fluid port of the 3rd hydraulic cylinder (17); Moment speed probe (14) is fixedly mounted on the output shaft of hydraulic motor (13); First displacement transducer (16.1), housing and the extension bar of second displacement transducer (16.2) and triple motion sensor (19) are separately fixed at first hydraulic cylinder (15.1), on the cylinder body and piston rod of second hydraulic cylinder (15.2) and the 3rd hydraulic cylinder (17), first pressure sensor (9.1) is communicated with first banked direction control valves (10.1) oil-out B10a and first banked direction control valves (10.1) oil-out A10b, second pressure sensor (9.2) is communicated with second banked direction control valves (10.2) oil-out B16a and second banked direction control valves (10.2) oil-out A16b, the 3rd pressure sensor (9.3) is communicated with the 3rd banked direction control valves (10.3) oil-out B17a and the 3rd banked direction control valves (10.3) oil-out A17b, and the 4th pressure sensor (9.4) is installed on the oil-out P place oil pipe of variable pump (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320004112 CN203175567U (en) | 2013-01-06 | 2013-01-06 | Energy-saving type shield segment assembling positioning electrohydraulic control system adopting load-sensitive technology |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320004112 CN203175567U (en) | 2013-01-06 | 2013-01-06 | Energy-saving type shield segment assembling positioning electrohydraulic control system adopting load-sensitive technology |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203175567U true CN203175567U (en) | 2013-09-04 |
Family
ID=49072282
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320004112 Expired - Fee Related CN203175567U (en) | 2013-01-06 | 2013-01-06 | Energy-saving type shield segment assembling positioning electrohydraulic control system adopting load-sensitive technology |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203175567U (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104088830A (en) * | 2014-07-30 | 2014-10-08 | 徐州重型机械有限公司 | Hydraulic system of crane and pilot type control valve thereof |
| CN104791310A (en) * | 2015-02-06 | 2015-07-22 | 湘潭大学 | Flow recycling energy-saving type segment erector horizontal movement hydraulic control system |
| CN105035979A (en) * | 2015-08-05 | 2015-11-11 | 常德中联重科液压有限公司 | Balance valve group and hydraulic system |
| CN105465072A (en) * | 2015-12-22 | 2016-04-06 | 武汉船用机械有限责任公司 | Double-cylinder control system |
| CN108661967A (en) * | 2018-06-29 | 2018-10-16 | 无锡市钻通工程机械有限公司 | A kind of load sensitive control system |
| CN108980126A (en) * | 2018-08-29 | 2018-12-11 | 武汉船用机械有限责任公司 | A kind of synchronization hydraulic system of meter out |
| CN109538231A (en) * | 2018-12-17 | 2019-03-29 | 中铁工程装备集团隧道设备制造有限公司 | Cantilever excavator digital intellectualization Hydraulic system and control method |
| CN110030220A (en) * | 2018-01-12 | 2019-07-19 | 伊顿智能动力有限公司 | Hydraulic valve with pressure restrictor function |
-
2013
- 2013-01-06 CN CN 201320004112 patent/CN203175567U/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104088830A (en) * | 2014-07-30 | 2014-10-08 | 徐州重型机械有限公司 | Hydraulic system of crane and pilot type control valve thereof |
| CN104791310A (en) * | 2015-02-06 | 2015-07-22 | 湘潭大学 | Flow recycling energy-saving type segment erector horizontal movement hydraulic control system |
| CN105035979A (en) * | 2015-08-05 | 2015-11-11 | 常德中联重科液压有限公司 | Balance valve group and hydraulic system |
| CN105465072A (en) * | 2015-12-22 | 2016-04-06 | 武汉船用机械有限责任公司 | Double-cylinder control system |
| CN105465072B (en) * | 2015-12-22 | 2018-01-26 | 武汉船用机械有限责任公司 | A kind of double cylinder control systems |
| CN110030220A (en) * | 2018-01-12 | 2019-07-19 | 伊顿智能动力有限公司 | Hydraulic valve with pressure restrictor function |
| CN108661967A (en) * | 2018-06-29 | 2018-10-16 | 无锡市钻通工程机械有限公司 | A kind of load sensitive control system |
| CN108980126A (en) * | 2018-08-29 | 2018-12-11 | 武汉船用机械有限责任公司 | A kind of synchronization hydraulic system of meter out |
| CN108980126B (en) * | 2018-08-29 | 2020-06-26 | 武汉船用机械有限责任公司 | Return-oil throttling synchronous hydraulic system |
| CN109538231A (en) * | 2018-12-17 | 2019-03-29 | 中铁工程装备集团隧道设备制造有限公司 | Cantilever excavator digital intellectualization Hydraulic system and control method |
| CN109538231B (en) * | 2018-12-17 | 2023-11-21 | 中铁工程装备集团隧道设备制造有限公司 | Digital intelligent hydraulic system of cantilever heading machine and control method |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103032396B (en) | Energy-saving shield segment assembling and positioning electro-hydraulic control system adopting load-sensitive technology | |
| CN203175567U (en) | Energy-saving type shield segment assembling positioning electrohydraulic control system adopting load-sensitive technology | |
| CN102278124B (en) | Energy-saving hydraulic shield propulsion system | |
| CN101408107B (en) | Energy-saving type shield propulsion hydraulic system by using zone control | |
| CN101864965B (en) | Pressure flow rate composite synchronization control energy-saving type shield propelling system | |
| CN1287094C (en) | Hydraulic propelling system for mining tunnel driving machine controlled by ratio flow pressure | |
| CN103032397B (en) | Multi-degree-of-freedom parallel tube segment assembling and locating electrohydraulic control system and method thereof | |
| CN109654074A (en) | A kind of construction machinery hydraulic system | |
| CN201554009U (en) | Piston-type double hanging point hydraulic headstock gear | |
| CN201288566Y (en) | Energy-saving shield advance hydraulic system employing zone control | |
| CN101571155A (en) | Digital electric-hydraulic synchronous control system | |
| CN108488112B (en) | Differential loop of large-flow hydraulic system and control method thereof | |
| CN104564863A (en) | Electrohydraulic control system for rotation motion of pipe splicing machine | |
| CN103727099A (en) | Pressure-flow whole-process-adaptive TBM (tunnel boring machine) propelling hydraulic system | |
| CN201396344Y (en) | Digital electro-hydraulic isochronous control system | |
| CN204163138U (en) | Super-tonnage excavator straight line moving hydraulic system | |
| CN201696054U (en) | Closed-type hydraulic driving system with variable-speed variable-displacement combined control of shield cutter head | |
| CN105275044A (en) | Hydraulic energy-saving control system and method for excavator | |
| CN104389830A (en) | Intelligent synchronous type hydraulic hoist | |
| CN103291314A (en) | Flow-saturation resistant zone-control energy-saving type shield thrust hydraulic system | |
| CN203051268U (en) | Multi-degree-freedom parallel pipe piece assembly positioning electrohydraulic control system | |
| CN205677896U (en) | EHA VPVM drives helm gear | |
| CN108915005B (en) | Excavator movable arm compensation hydraulic system | |
| CN204113783U (en) | A kind of for the hydraulic pressure synchronous drive device in nuclear fusion device | |
| CN203383824U (en) | Flow saturation resistant partitioned controlled energy saving type shield thrust hydraulic system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 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: 20130904 Termination date: 20160106 |