CN101503960A - Multi-pump combined driving shield-tunneling blade disc hydraulic system - Google Patents
Multi-pump combined driving shield-tunneling blade disc hydraulic system Download PDFInfo
- Publication number
- CN101503960A CN101503960A CNA2009100964082A CN200910096408A CN101503960A CN 101503960 A CN101503960 A CN 101503960A CN A2009100964082 A CNA2009100964082 A CN A2009100964082A CN 200910096408 A CN200910096408 A CN 200910096408A CN 101503960 A CN101503960 A CN 101503960A
- Authority
- CN
- China
- Prior art keywords
- valve
- hydraulic fluid
- fluid port
- way
- oil
- 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.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims description 132
- 238000006073 displacement reaction Methods 0.000 claims description 72
- 239000002828 fuel tank Substances 0.000 claims description 33
- 239000002243 precursor Substances 0.000 claims description 17
- 230000008878 coupling Effects 0.000 claims description 15
- 238000010168 coupling process Methods 0.000 claims description 15
- 238000005859 coupling reaction Methods 0.000 claims description 15
- 238000000034 method Methods 0.000 abstract description 6
- 230000000694 effects Effects 0.000 abstract description 2
- 230000001105 regulatory effect Effects 0.000 abstract description 2
- 230000001276 controlling effect Effects 0.000 abstract 4
- 239000003921 oil Substances 0.000 description 59
- 230000002457 bidirectional effect Effects 0.000 description 12
- 238000005516 engineering process Methods 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 239000010720 hydraulic oil Substances 0.000 description 3
- 239000002689 soil Substances 0.000 description 3
- 230000009977 dual effect Effects 0.000 description 2
- 238000004134 energy conservation Methods 0.000 description 2
- 239000011435 rock Substances 0.000 description 2
- 230000005641 tunneling Effects 0.000 description 2
- 238000009412 basement excavation Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000003750 conditioning effect Effects 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
Images
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to a shield-structured cutter head hydraulic system driven by multi-pump combination. The system comprises a motor, a proportion variable pump, a check valve, a pilot overflow valve, a governing valve, a power limiting valve, a proportion overflow valve, a two-way cartridge valve, a two-position three-way reversing valve, a three -position four-way reversing valve, an oil separating quick valve and a two-point controlling bi-directional variable motor. The system drives a shield-structured cutter head to move by adopting the combination of a main driving proportion variable pump group having large discharge capacity and an auxiliary driving proportion variable pump group having small discharge capacity, and the control mode is an electric proportion variable mode. The speed of the cutter head can be continuously regulated in a wide range by controlling the discharge capacity of the proportion pump group. A high-speed gear and a low-speed gear can be switched by controlling the discharge capacity of the two-point controlling bi-directional variable motor. The method has the advantages of moderate assembling power, flexible combination of a hydraulic pump, high load rate of the single hydraulic pump under normal working condition, power source efficiency improvement, reliability improvement, and good energy saving effect of the system.
Description
Technical field
The invention belongs to field of mechanical technique, relate to fluid pressure actuator, relate in particular to the many pump combinations of a kind of employing shield-structured cutter head hydraulic system driven.
Background technology
Along with the development of modern society, the mankind develop the underground space more and more, and the demand of various construction of tunnel is had higher requirement to construction technology, have promoted the development of tunnel construction technology.Modern shield machine not only can be realized tunneling, and safety, driving speed is fast, automaticity is high, can be applied in the tunnelling of all kinds of soil properties and soft rock strata.Along with development in science and technology and social progress, shield driving will progressively replace conventional method.
Cutter-devices system is that shield excavation machine is finished the important component part of excavating function, drives the soil body that cutterhead rotates cutting shield structure the place ahead.At present, cutter-devices system is a kind of typically high-power, multi executors system.Because geological conditions is complicated and changeable in tunneling process, cutter-devices system must satisfy the needs of various stratum driving from the weak soil to the hard rock, and the rotation speed change scope is very big.Variable pump-variable displacement motor volume speed-modulating loop combines variable pump and variable displacement motor, continuous speed adjustment in wide range.At present, generally adopted this Hydraulic Adjustable Speed loop in the world, normally several big discharge capacity variable pumps are united several variable displacement motors of driving, by automatically controlled or hydraulic control proportional technique centralized Control, become the change discharge capacity control of discharge capacity, the control of permanent power and each motor when realizing each pump.The characteristics of this drive scheme are that the element of hydraulic system is few, control is simple, but power source efficient is lower.And adopt main driving pump and assistive drive pump assembly power source, and although it is complicated that control is gone up, can reduce the component purchase cost, improve power source efficient, increase reliability, be more suitable for China's national situation.
Summary of the invention
The object of the present invention is to provide the many pump combinations of a kind of employing shield-structured cutter head hydraulic system driven, can satisfy the shield cutter speed governing, improve power source efficient and energy-conservation requirement.
The present invention includes fuel tank, first motor, second motor, the 3rd motor, the 4th motor, the 5th motor, first proportional variable pump, second proportional variable pump, the 3rd proportional variable pump, the 4th proportional variable pump, the 5th proportional variable pump, first two-way plug-in valve, second two-way plug-in valve, the 3rd two-way plug-in valve, the 4th two-way plug-in valve, the 5th two-way plug-in valve, first precursor overflow valve, second precursor overflow valve, first liang of point control type double-action variable displacement motor, second liang of point control type double-action variable displacement motor, the 3rd liang of point control type double-action variable displacement motor, the 4th liang of point control type double-action variable displacement motor, the 5th liang of point control type double-action variable displacement motor, the 6th liang of point control type double-action variable displacement motor, the 7th liang of point control type double-action variable displacement motor, the 8th liang of point control type double-action variable displacement motor, two position three way directional control valve, three position four-way directional control valve, the Power Limitation valve, proportional pressure control valve, flow speed control valve.
First motor is rigidly connected through the shaft coupling and first proportional variable pump, the oil-in of first proportional variable pump is communicated with fuel tank, the oil-out of first proportional variable pump is communicated with the oil-in of first one way valve, and the oil-out of first one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
Second motor is rigidly connected through the shaft coupling and second proportional variable pump, the oil-in of second proportional variable pump is communicated with fuel tank, the oil-out of second proportional variable pump is communicated with the oil-in of second one way valve, and the oil-out of second one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
The 3rd motor is rigidly connected through shaft coupling and the 3rd proportional variable pump, the oil-in of the 3rd proportional variable pump is communicated with fuel tank, the oil-out of the 3rd proportional variable pump is communicated with the oil-in of the 3rd one way valve, and the oil-out of the 3rd one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
The 4th motor is rigidly connected through shaft coupling and the 4th proportional variable pump, the oil-in of the 4th proportional variable pump is communicated with fuel tank, the oil-out of the 4th proportional variable pump is communicated with the oil-in of the 4th one way valve, and the oil-out of the 4th one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
Second hydraulic fluid port of the 5th two-way plug-in valve is communicated with fuel tank, and the 3rd hydraulic fluid port of the 5th two-way plug-in valve is communicated with first hydraulic fluid port of two position three way directional control valve; Second hydraulic fluid port of two position three way directional control valve is communicated with the oil-in of first precursor overflow valve, and the oil-out of first precursor overflow valve is communicated with fuel tank; The 3rd hydraulic fluid port of two position three way directional control valve is communicated with the oil-in of second precursor overflow valve, and the oil-out of second precursor overflow valve is communicated with fuel tank; The oil-out of the 6th one way valve is communicated with second hydraulic fluid port of Power Limitation valve; First hydraulic fluid port of first two-way plug-in valve is communicated with second hydraulic fluid port of second two-way plug-in valve; Second hydraulic fluid port of first two-way plug-in valve is communicated with fuel tank; The 3rd hydraulic fluid port of first two-way plug-in valve is communicated with the 3rd hydraulic fluid port of three position four-way directional control valve; Second hydraulic fluid port of second two-way plug-in valve is communicated with the first separating valve piece, one end hydraulic fluid port; The 3rd hydraulic fluid port of second two-way plug-in valve is communicated with second hydraulic fluid port of three position four-way directional control valve; Second hydraulic fluid port of the 3rd two-way plug-in valve is communicated with the second separating valve piece, one end hydraulic fluid port; The 3rd hydraulic fluid port of the 3rd two-way plug-in valve is communicated with the 3rd hydraulic fluid port of three position four-way directional control valve; First hydraulic fluid port of the 4th two-way plug-in valve is communicated with second hydraulic fluid port of the 3rd two-way plug-in valve; Second hydraulic fluid port of the 4th two-way plug-in valve is communicated with fuel tank; The 3rd hydraulic fluid port of the 4th two-way plug-in valve is communicated with second hydraulic fluid port of three position four-way directional control valve; The 4th hydraulic fluid port of three position four-way directional control valve is communicated with fuel tank; The other end hydraulic fluid port of the first separating valve piece respectively with first hydraulic fluid port of first liang of point control type double-action variable displacement motor, first hydraulic fluid port of second liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 3rd liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 4th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 5th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 6th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 7th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 8th liang of point control type double-action variable displacement motor is communicated with; The other end hydraulic fluid port of the second separating valve piece respectively with second hydraulic fluid port of first liang of point control type double-action variable displacement motor, second hydraulic fluid port of second liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 3rd liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 4th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 5th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 6th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 7th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 8th liang of point control type double-action variable displacement motor is communicated with;
The 5th motor is rigidly connected through shaft coupling and the 5th proportional variable pump, the oil-in of the 5th proportional variable pump is communicated with fuel tank, the oil-out of the 5th proportional variable pump is communicated with the oil-in of the 5th one way valve, the oil-out of the 5th one way valve is communicated with the oil-in of flow speed control valve, the oil-out of flow speed control valve is communicated with the control port of first proportional variable pump, the control port of second proportional variable pump, first hydraulic fluid port of Power Limitation valve, the oil-in of proportional pressure control valve respectively, the 3rd hydraulic fluid port of Power Limitation valve is communicated with fuel tank, and the oil-out of proportional pressure control valve is communicated with fuel tank.
The present invention adopts big discharge capacity master to drive proportional variable pump group and the motion of float amount assistive drive proportional variable pump group combination driving shield cutterhead.During cutterhead work, two proportional variable pumps that big discharge capacity master drives the proportional variable pump group are worked simultaneously, two proportional variable pumps of float amount assistive drive proportional variable pump group are incorporated system into when main driving power is not enough, improve the load factor and the power source efficient of single hydraulic pump.By electric-control system, regulate the rate variable pump delivery to realize adjusting to cutterhead speed.
System of the present invention adopts big discharge capacity proportional variable pump group and the combination of float amount proportional variable pump group to drive, control mode is automatically controlled rate variable, installed power is moderate, hydraulic pump can flexible combination, under the nominal situation, the load factor height of single hydraulic pump can improve the efficient of power source, has energy-conservation effect.Because proportional variable pump adopts the speed governing of automatically controlled change discharge capacity, and adopts two point control type double-action variable displacement motors, can make shield cutter speed governing in wide range, satisfies working condition requirement.
Description of drawings
Fig. 1 is the structural representation of a specific embodiment of the present invention.
The specific embodiment
The invention will be further described below in conjunction with drawings and Examples.
Shown in Figure 1, the use of multiple pump assembly driven shield cutter hydraulic system first motor 1.1
After coupling with the first variable pump 2.1 rigid connection; first proportional variable pump inlet 2.1
15.1 with the tank 14 through line connectivity; first proportional variable pump 2.1 16.1 outlet port via a line with
The first one-way inlet valve 3.1 connectivity; first check valve 3.1 17.1 outlet port through line,
18.1,19,20.1 fifth two-way cartridge valve 6.5 is the first port connectivity; first check valve 3.1
The outlet port through line 17.1,18.1,19,20.2 and sixth check valve inlet 3.6 connectivity;
The first one-way valve 3.1 17.1,18.1,19,20.3 oil outlet via a line with a second two-way cartridge valves
The first port communicates 6.2; 3.1 out of the first check valve port via line 17.1,18.1,19,
20.4 and the third two-way cartridge valve 6.3 first port connectivity; first check valve outlet port through 3.1
Piping 17.1,18.1,19 with three way valve 7 is the first port connectivity; second motor 1.2
After coupling with the second variable pump 2.2 rigid connection; second variable pump inlet 2.2
15.2 with the tank 14 through line connectivity; proportional variable pump 2.2 second outlet port via a line 16.2 and
The second check valve inlet 3.2 connectivity; 3.2 second check valve outlet port through line 17.2,
18.1,19,20.1 fifth two-way cartridge valve 6.5 is the first port connectivity; second check valve 3.2
The outlet port through line 17.2,18.1,19,20.2 and sixth check valve inlet 3.6 connectivity;
The second check valve 3.2 through line 17.2,18.1,19,20.3 oil outlet and a second two-way cartridge valves
The first port communicates 6.2; 3.2 second check valve outlet port via line 17.2,18.1,19,
20.4 and the third two-way cartridge valve 6.3 first port connectivity; 3.2 second check valve outlet port through
Piping 17.2,18.1,19 with three way valve 7 is the first port connectivity; third motor 1.3
After coupling with the third variable pump 2.3 rigid connection; third proportional variable pump inlet 2.3
15.3 with the tank 14 through line connectivity; third proportional variable pump 2.3 16.3 outlet port via a line with
The third one-way inlet valve 3.3 connectivity; third check valve 3.3 17.3 outlet port through line,
18.2,19,20.1 fifth two-way cartridge valve 6.5 is the first port connectivity; third check valve 3.3
The outlet port through line 17.3,18.2,19,20.2 and sixth check valve inlet 3.6 connectivity;
The third one-way valve 3.3 through line 17.3,18.2,19,20.3 oil outlet and a second two-way cartridge valves
6.2 The first port connectivity; third check valve 3.3 out of oil port through line 17.3,18.2,19,
20.4 and the third two-way cartridge valve 6.3 first port connectivity; third check valve 3.3 out of oil Mouth
Piping 17.3,18.2,19 with three way valve 7 is the first port connectivity; fourth motor 1.4
After coupling with the fourth proportional variable pump 2.4 rigid connection; fourth proportional variable pump inlet 2.4
15.4 with the tank 14 through line connectivity; fourth proportional variable pump 2.4 16.4 outlet port via a line with
The fourth one-way inlet valve 3.4 connectivity; fourth check valve 3.4 17.4 outlet port through line,
18.2,19,20.1 fifth two-way cartridge valve 6.5 is the first port connectivity; fourth check valve 3.4
The outlet port through line 17.4,18.2,19,20.2 and sixth check valve inlet 3.6 connectivity;
The fourth one-way valve 3.4 through line 17.4,18.2,19,20.3 oil outlet and a second two-way cartridge valves
The first port communicates 6.2; fourth unidirectional valve 3.4 17.4,18.2,19 the outlet port via line,
20.4 and the third two-way cartridge valve 6.3 first port connectivity; fourth check valve 3.4 out of oil Mouth
Piping 17.4,18.2,19 with three way valve 7 is the first port connectivity; fifth two-way cartridge
The second oil port valve 6.5 39.3 with the tank 14 through line connectivity, and the fifth two-way cartridge valves 6.5
The third port through line 21 and two of the first three-way valve 5 port connectivity; 3/2-way valve
The second port 5 via the line 22.1 of the first pilot relief valve communicates the inlet of 4.1, and the first first
Guide the oil port relief valve 4.1 39.1 with the tank 14 through line connectivity; 3/2-way valve 5
The third port via the line 22.2 and the second pilot relief valve communicates the inlet of 4.2, and the second pilot overflow
Flow of the oil outlet valve 4.2 39.2 with the tank 14 through line connectivity; sixth check valve outlet port 3.6
Power limit through line 38 and valve 13 is connected to the second port; first two-way cartridge valve 6.1 first
Port through line 23.1 and the second two-way cartridge valve 6.2 second oil port connectivity; first two-way cartridge valves
6.1 39.6 second oil port with the tank 14 through line connectivity; first two-way cartridge valve 6.1's third oil
Administered by oral route with three way valve 7 24.1 third port connectivity; second two-way cartridge valves 6.2
The second port of the first points via a line 25.1,26.1,26.2,26.3,26.4 Ported 8.1 a
End Ports connectivity; second two-way cartridge valve 6.2 ports administered by a third way and three-way commutation 24.2
The second oil port valve 7 connectivity; third two-way cartridge valve 6.3 second port via a line 25.2,
27.1,27.2,27.3,27.4 with the second end of Ported 8.2 port connectivity; third two-way cartridge
The third valve 6.3 port via a line with three way valve 7 24.3 third port connectivity; Section
Forty-two cartridge valve 6.4 ports administered by the first and the third two-pass road 23.2 Cartridge 6.3 second oil
Oral communication; fourth two-way cartridge valve 6.4 39.7 second oil port with the tank 14 through line connectivity; Section
Forty-two cartridge valve 6.4 ports administered by a third way and three-way valve 7 24.4 second oil port
Connectivity; three way valve 7 to the fourth port with the tank 14 via a line 39.8 connectivity; first points
Ported 8.1 ports administered by the other side of road 28.1,28.2,28.3,28.4, toroidal flow diversion
Line 30, line 32.1 and the first two-point control type bidirectional variable motor 9.1 first port connectivity;
The first sub-Ported 8.1 ports administered by the other side of road 28.1,28.2,28.3,28.4, the ring of
Flow manifold pipe 30, pipe 32.2 points and second variable motor control type bidirectional port 9.2 first
Connectivity; first points Ported 8.1 ports administered by the other side of road 28.1,28.2,28.3,28.4,
Toroidal flow diversion line 30, line 32.3 and the third two-point control type bidirectional variable motor section 9.3
An oil port connectivity; first sub-Ported 8.1 ports administered by the other side of road 28.1,28.2,28.3,
28.4, ring flow diversion line 30, line 32.4 and fourth two-point control type bidirectional variable motor
9.4 The first port connectivity; first sub-Ported 8.1 ports administered by the other side of road 28.1,
28.2,28.3,28.4, toroidal flow diversion line 30, line 32.5 and fifth two-point control Dual
Variable motor 9.5 to the first port connectivity; first points Ported 8.1 ports administered by the other side of road
28.1,28.2,28.3,28.4, toroidal flow diversion line 30, line 32.6 and sixth two o'clock control
A built-in two-way variable motor 9.6 first port connectivity; first sub-Ported 8.1 other end of the oil port
Administered by road 28.1,28.2,28.3,28.4, ring flow diversion line 30, with the first line 32.7
Seven two-point control type bidirectional variable motor 9.7 first port connectivity; first sub-Ported 8.1 Another
End of the oil port through line 28.1,28.2,28.3,28.4, ring flow diversion line 30, line
32.8 and eighth two-point control type bidirectional variable motor 9.8 first port connectivity; second sub-Ported
8.2 The other end of the oil port through line 29.1,29.2,29.3,29.4, ring flow diversion pipe
31, 33.1 and the first two lines controlled variable motor 9.1 second bidirectional port connectivity; second
Points Ported 8.2 ports administered by the other side of road 29.1,29.2,29.3,29.4, split ring set
Flow line 31, line 33.2 and the second two-point control type bidirectional variable motor 9.2 port connected to the second
Pass; second sub-Ported 8.2 ports administered by the other side of road 29.1,29.2,29.3,29.4, ring
Shunt manifold pipe 31, pipe 33.3 and the third two-point control type bidirectional variable motor 9.3 second
Port connectivity; second sub-Ported 8.2 ports administered by the other side of road 29.1,29.2,29.3,
29.4, ring flow diversion line 31, line 33.4 and fourth two-point control type bidirectional variable motor
9.4 The second port connectivity; second sub-Ported 8.2 ports administered by the other side of road 29.1,
29.2,29.3,29.4, toroidal flow diversion line 31, line 33.5 and fifth two-point control Dual
9.5 second to the variable motor oil port connectivity; second sub-Ported 8.2 ports administered by the other side of road
29.1,29.2,29.3,29.4, toroidal flow diversion line 31, line 33.6 and sixth two o'clock control
A built-in two-way variable motor 9.6 second port connectivity; second sub-Ported 8.2 other end of the oil port
Administered by road 29.1,29.2,29.3,29.4, ring flow diversion pipe 31, pipe 33.7 first
Seven two-point control type variable motor 9.7 second bidirectional port connectivity; second sub-Ported 8.2 Another
End of the oil port through line 29.1,29.2,29.3,29.4, ring flow diversion pipe 31, pipe
33.8 and eighth two-point control type bidirectional variable motor 9.8 second oil port connectivity; fifth motor 1.5
After coupling with the fifth variable pump 2.5 rigid connection; fifth proportional variable pump inlet 2.5
15.5 with the tank 14 through line connectivity; fifth proportional variable pump 2.5 16.5 outlet port via a line with
Fifth one-way inlet valve 3.5 connectivity; fifth check valve 3.5 out of oil port via a line 35 with governor
The inlet valve 11 communicates; governor oil outlet valve 11 through line 36,37.1 and second proportional variable
Pump control port 2.2 connectivity; governor oil outlet valve 11 through line 36,37.2 first scale
Variable pump control port 2.1 connectivity; governor oil outlet valve 11 through line 36,37.3 and power
Limiting valve 13 is first port connectivity; governor oil outlet valve 11 through line 36,37.4 and proportional overflow
Flow in the inlet valve 12 communicates; power limitation third port valve 13 to the tank 14 via line 39.4
Connectivity; proportional relief valve 12 through line 39.5 outlet port communicates with the tank 14.
...
The operating principle of this shield-structured cutter head hydraulic system is as follows:
First motor 1.1 and second motor 1.2 get electric startup, drive first proportional variable pump 2.1 and 2.2 rotations of second proportional variable pump respectively, and first proportional variable pump 2.1 and second proportional variable pump 2.2 are the main proportional variable pump group that drives.15.1,15.2 oil suctions from fuel tank 14 by the road of main driving proportional variable pump group, the pressure oil that main driving proportional variable pump group is got is delivered to pipeline 18.1,19,20.1,20.2,20.3,20.4 through pipeline 16.1, first one way valve 3.1, pipeline 17.1 and pipeline 16.2, second one way valve 3.2, pipeline 17.2.
When three position four-way directional control valve 7 left electromagnet get when electric, the working chamber that hydraulic oil process three position four-way directional control valve 7 in the pipeline 19, pipeline 24.2 act on the 3rd hydraulic fluid port place of second two-way plug-in valve 6.2, the process of the hydraulic oil in the pipeline 19 three position four-way directional control valve 7, pipeline 24.4 act on the working chamber at the 3rd hydraulic fluid port place of the 4th two-way plug-in valve 6.4, and this moment, second two-way plug-in valve 6.2 and the 4th two-way plug-in valve 6.4 were in closed condition.The working chamber at the 3rd hydraulic fluid port place of first two-way plug-in valve 6.1 communicates through pipeline 24.1, three position four-way directional control valve 7 and fuel tank, the working chamber at the 3rd hydraulic fluid port place of the 3rd two-way plug-in valve 6.3 communicates through pipeline 24.3, three position four-way directional control valve 7 and fuel tank, and this moment, first two-way plug-in valve 6.1 and the 3rd two-way plug-in valve 6.3 were in opening.Hydraulic oil in the pipeline 19 is by the 3rd two-way plug-in valve 6.3, pipeline 23.2,25.2,27.1,27.2,27.3,27.4 deliver to separating valve piece 8.2, the pressure oil that separating valve piece 8.2 is sent by the road 29.1,29.2,29.3,29.4 deliver to ring-like flow distributing and collecting pipeline 31, the pressure oil that ring-like flow distributing and collecting pipeline 31 is sent 33.1 enters first liang of point control type double-action variable displacement motor 9.1 by the road, 33.2 enter second liang of point control type double-action variable displacement motor 9.2 by the road, 33.3 enter the 3rd liang of point control type double-action variable displacement motor 9.3 by the road, 33.4 enter the 4th liang of point control type double-action variable displacement motor 9.4 by the road, 33.5 enter the 5th liang of point control type double-action variable displacement motor 9.5 by the road, 33.6 enter the 6th liang of point control type double-action variable displacement motor 9.6 by the road, 33.7 enter the 7th liang of point control type double-action variable displacement motor 9.7 by the road, 33.8 enter the 8th liang of point control type double-action variable displacement motor 9.8 by the road.First liang of point control type double-action variable displacement motor 9.1 oil return opening oil return is delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.1, second liang of point control type double-action variable displacement motor 9.2 oil return opening oil return is delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.2, the 3rd liang of point control type double-action variable displacement motor 9.3 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.3, the 4th liang of point control type double-action variable displacement motor 9.4 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.4, the 5th liang of point control type double-action variable displacement motor 9.5 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.5, the 6th liang of point control type double-action variable displacement motor 9.6 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.6, the 7th liang of point control type double-action variable displacement motor 9.7 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.7, the 8th liang of point control type double-action variable displacement motor 9.8 oil return opening oil returns are delivered to ring-like flow distributing and collecting pipeline 30 through pipeline 32.8, pressure oil by the road 28.1 in the ring-like flow distributing and collecting pipeline 30,28.2,28.3,28.4 deliver to separating valve piece 8.1, by the road 26.1,26.2,26.3,26.4,25.1,23.1 deliver to first two-way plug-in valve 6.1,39.6 deliver to fuel tank 14 and finish oil return by the road, thereby two point control type double-action variable displacement motors 9.1,9.2,9.3,9.4,9.5,9.6,9.7,9.8 under the pressure reduction at two ends, rotate, drive cutterhead and rotate.
When three position four-way directional control valve 7 right electromagnet get when electric, situation is similar to the above, this moment, second two-way plug-in valve 6.2 and the 4th two-way plug-in valve 6.4 were in opening, first two-way plug-in valve 6.1 and the 3rd two-way plug-in valve 6.3 are in closed condition, the oil-feed oil return of two point control type double-action variable displacement motors realizes the reverse rotation of cutterhead with above-mentioned opposite.
The 5th motor 1.5, the 5th proportional variable pump 2.5, the 5th one way valve 3.5, flow speed control valve 11, proportional pressure control valve 12, Power Limitation valve 13, the 6th one way valve 3.6 are formed first proportional variable pump 2.1 and second proportional variable pump, 2.2 discharge capacities control oil return line.The 5th motor 1.5 gets electric startup, drives the 5th proportional variable pump 2.5.The 5th proportional variable pump 2.5 is 15.5 oil suctions from fuel tank 14 by the road, pressure oil that the 5th proportional variable pump 2.5 is got is delivered to flow speed control valve 11 through pipeline 16.5, the 5th one way valve 3.5, pipeline 35,36 and 37.1 delivers to the control port of second proportional variable pump 2.2 by the road after flow speed control valve 11 carries out Flow-rate adjustment, 36 and 37.2 deliver to the control port of first proportional variable pump 2.1 by the road, 36 and 37.3 delivers to first hydraulic fluid port of Power Limitation valve 13,36 and 37.4 oil-ins of delivering to proportional pressure control valve 12 by the road by the road.Pressure oil in the pipeline 19 is delivered to second hydraulic fluid port of Power Limitation valve 13 by the 6th one way valve 3.6, and the pressure in the pipeline 19 is system pressure.When system pressure did not reach the initial setting value of Power Limitation valve 13, the pressure of the control port of first proportional variable pump 2.1 and second proportional variable pump 2.2 was by proportional pressure control valve 12 decision, and proportional with its conditioning signal.Because the control port pressure of first proportional variable pump 2.1 and second proportional variable pump 2.2 and first proportional variable pump 2.1 and second proportional variable pump, 2.2 discharge capacities are proportional, so adjustable continuously, and then realize that the cutterhead rotating speed is adjustable continuously by regulating proportional pressure control valve 12 realization first proportional variable pumps 2.1 and second proportional variable pump, 2.2 discharge capacities; When system pressure surpasses Power Limitation valve 13 initial setting values, the Power Limitation valve 13 beginning overflow of working, cause the pressure in the pipeline 36 to reduce, the control port pressure of first proportional variable pump 2.1 and second proportional variable pump 2.2 is reduced, thereby first proportional variable pump 2.1 and second proportional variable pump, 2.2 discharge capacities are reduced, cutterhead speed reduces, keep first proportional variable pump 2.1 and second proportional variable pump, 2.2 power outputs constant, prevent first proportional variable pump 2.1 and second proportional variable pump, 2.2 power overloads.
Reach when setting rotating speed when the output flow of first proportional variable pump 2.1 and second proportional variable pump 2.2 is enough to drive cutterhead, only open first proportional variable pump 2.1 and second proportional variable pump 2.2; When the output flow of first proportional variable pump 2.1 and second proportional variable pump 2.2 is not enough to drive cutterhead and reaches the rotating speed of setting, motor 1.3 and motor 1.4 get electric startup, drive float flow control three proportional variable pumps 2.3 and 2.4 rotations of the 4th proportional variable pump respectively, the 3rd proportional variable pump 2.3 and the 4th proportional variable pump 2.4 are assistive drive proportional variable pump group, and the analysis of hydraulic circuit and above-mentioned situation are similar.Assistive drive proportional variable pump group carries persevering powered controls, by special electric control system controls.Big discharge capacity master drives the proportional variable pump group and the combination of float amount assistive drive proportional variable pump group drives to provide the cutterhead rotating speed needed flow.
Two point control type double-action variable displacement motors 9.1,9.2,9.3,9.4,9.5,9.6,9.7,9.8, can make motor displacement be set in minimum injection rate or maximum pump discharge place by special control device, thereby be implemented in two grades of switchings of cutterhead high, low speed under the given flow.
The 5th two-way plug-in valve 6.5, two position three way directional control valve 5 are formed the voltage-limiting protection loop with precursor overflow valve 4.1,4.2.System pressure oil in the pipeline 19 20.1 is communicated with the 5th two-way plug-in valve 6.5 first hydraulic fluid ports by the road, system pressure oil by after the damping port in the 5th two-way plug-in valve 6.5 by the road 21 and first hydraulic fluid port of two position three way directional control valve 5 be communicated with.When cutterhead is worked under the nominal situation pattern, the outage of two position three way directional control valve 5 electromagnet, precursor overflow valve 4.1 inserts the loop, if system pressure surpasses precursor overflow valve 4.1 pressure set points, precursor overflow valve 4.1 beginning overflows, make the 5th two-way plug-in valve 6.5 be in opening, system pressure oil begins overflow by second hydraulic fluid port of the 5th two-way plug-in valve 6.5, thereby plays the voltage-limiting protection of nominal situation; When working under cutterhead is being got rid of poverty pattern, two position three way directional control valve 5 electromagnet get electric, and precursor overflow valve 4.2 inserts the loop, and principle is similar to the above, plays the voltage-limiting protection of the operating mode of getting rid of poverty.
Claims (1)
1, adopt many pump combination shield-structured cutter head hydraulic system driven, comprise fuel tank, first motor, second motor, the 3rd motor, the 4th motor, the 5th motor, first proportional variable pump, second proportional variable pump, the 3rd proportional variable pump, the 4th proportional variable pump, the 5th proportional variable pump, first two-way plug-in valve, second two-way plug-in valve, the 3rd two-way plug-in valve, the 4th two-way plug-in valve, the 5th two-way plug-in valve, first precursor overflow valve, second precursor overflow valve, first liang of point control type double-action variable displacement motor, second liang of point control type double-action variable displacement motor, the 3rd liang of point control type double-action variable displacement motor, the 4th liang of point control type double-action variable displacement motor, the 5th liang of point control type double-action variable displacement motor, the 6th liang of point control type double-action variable displacement motor, the 7th liang of point control type double-action variable displacement motor, the 8th liang of point control type double-action variable displacement motor, two position three way directional control valve, three position four-way directional control valve, the Power Limitation valve, proportional pressure control valve, flow speed control valve is characterized in that:
First motor is rigidly connected through the shaft coupling and first proportional variable pump, the oil-in of first proportional variable pump is communicated with fuel tank, the oil-out of first proportional variable pump is communicated with the oil-in of first one way valve, and the oil-out of first one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
Second motor is rigidly connected through the shaft coupling and second proportional variable pump, the oil-in of second proportional variable pump is communicated with fuel tank, the oil-out of second proportional variable pump is communicated with the oil-in of second one way valve, and the oil-out of second one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
The 3rd motor is rigidly connected through shaft coupling and the 3rd proportional variable pump, the oil-in of the 3rd proportional variable pump is communicated with fuel tank, the oil-out of the 3rd proportional variable pump is communicated with the oil-in of the 3rd one way valve, and the oil-out of the 3rd one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
The 4th motor is rigidly connected through shaft coupling and the 4th proportional variable pump, the oil-in of the 4th proportional variable pump is communicated with fuel tank, the oil-out of the 4th proportional variable pump is communicated with the oil-in of the 4th one way valve, and the oil-out of the 4th one way valve is communicated with first hydraulic fluid port of the 5th two-way plug-in valve, the oil-in of the 6th one way valve, first hydraulic fluid port of second two-way plug-in valve, first hydraulic fluid port of the 3rd two-way plug-in valve and first hydraulic fluid port of three position four-way directional control valve respectively;
Second hydraulic fluid port of the 5th two-way plug-in valve is communicated with fuel tank, and the 3rd hydraulic fluid port of the 5th two-way plug-in valve is communicated with first hydraulic fluid port of two position three way directional control valve; Second hydraulic fluid port of two position three way directional control valve is communicated with the oil-in of first precursor overflow valve, and the oil-out of first precursor overflow valve is communicated with fuel tank; The 3rd hydraulic fluid port of two position three way directional control valve is communicated with the oil-in of second precursor overflow valve, and the oil-out of second precursor overflow valve is communicated with fuel tank; The oil-out of the 6th one way valve is communicated with second hydraulic fluid port of Power Limitation valve; First hydraulic fluid port of first two-way plug-in valve is communicated with second hydraulic fluid port of second two-way plug-in valve; Second hydraulic fluid port of first two-way plug-in valve is communicated with fuel tank; The 3rd hydraulic fluid port of first two-way plug-in valve is communicated with the 3rd hydraulic fluid port of three position four-way directional control valve; Second hydraulic fluid port of second two-way plug-in valve is communicated with the first separating valve piece, one end hydraulic fluid port; The 3rd hydraulic fluid port of second two-way plug-in valve is communicated with second hydraulic fluid port of three position four-way directional control valve; Second hydraulic fluid port of the 3rd two-way plug-in valve is communicated with the second separating valve piece, one end hydraulic fluid port; The 3rd hydraulic fluid port of the 3rd two-way plug-in valve is communicated with the 3rd hydraulic fluid port of three position four-way directional control valve; First hydraulic fluid port of the 4th two-way plug-in valve is communicated with second hydraulic fluid port of the 3rd two-way plug-in valve; Second hydraulic fluid port of the 4th two-way plug-in valve is communicated with fuel tank; The 3rd hydraulic fluid port of the 4th two-way plug-in valve is communicated with second hydraulic fluid port of three position four-way directional control valve; The 4th hydraulic fluid port of three position four-way directional control valve is communicated with fuel tank; The other end hydraulic fluid port of the first separating valve piece respectively with first hydraulic fluid port of first liang of point control type double-action variable displacement motor, first hydraulic fluid port of second liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 3rd liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 4th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 5th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 6th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 7th liang of point control type double-action variable displacement motor, first hydraulic fluid port of the 8th liang of point control type double-action variable displacement motor is communicated with; The other end hydraulic fluid port of the second separating valve piece respectively with second hydraulic fluid port of first liang of point control type double-action variable displacement motor, second hydraulic fluid port of second liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 3rd liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 4th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 5th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 6th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 7th liang of point control type double-action variable displacement motor, second hydraulic fluid port of the 8th liang of point control type double-action variable displacement motor is communicated with;
The 5th motor is rigidly connected through shaft coupling and the 5th proportional variable pump, the oil-in of the 5th proportional variable pump is communicated with fuel tank, the oil-out of the 5th proportional variable pump is communicated with the oil-in of the 5th one way valve, the oil-out of the 5th one way valve is communicated with the oil-in of flow speed control valve, the oil-out of flow speed control valve is communicated with the control port of first proportional variable pump, the control port of second proportional variable pump, first hydraulic fluid port of Power Limitation valve, the oil-in of proportional pressure control valve respectively, the 3rd hydraulic fluid port of Power Limitation valve is communicated with fuel tank, and the oil-out of proportional pressure control valve is communicated with fuel tank.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100964082A CN101503960B (en) | 2009-03-02 | 2009-03-02 | Multi-pump combined driving shield-tunneling blade disc hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100964082A CN101503960B (en) | 2009-03-02 | 2009-03-02 | Multi-pump combined driving shield-tunneling blade disc hydraulic system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101503960A true CN101503960A (en) | 2009-08-12 |
| CN101503960B CN101503960B (en) | 2010-12-08 |
Family
ID=40976323
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100964082A Expired - Fee Related CN101503960B (en) | 2009-03-02 | 2009-03-02 | Multi-pump combined driving shield-tunneling blade disc hydraulic system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101503960B (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102032232A (en) * | 2010-12-27 | 2011-04-27 | 清华大学深圳研究生院 | Proportional control type power limitation valve |
| CN101691877B (en) * | 2009-09-04 | 2012-03-07 | 佛山市顺德区震德塑料机械有限公司 | Servo motor control-based multi-pump combination controlled hydraulic power system |
| CN102996138A (en) * | 2012-11-30 | 2013-03-27 | 中煤科工集团重庆研究院 | Hydraulic control system of dust removal and outburst prevention integrated heading machine |
| CN105864132A (en) * | 2015-01-23 | 2016-08-17 | 鞍钢股份有限公司 | Constant-pressure variable pump system and energy-saving method |
| WO2018112792A1 (en) * | 2016-12-21 | 2018-06-28 | 浙江大学 | Heading machine cutterhead fixed and variable displacement combined hydraulic motor drive system and control method |
| CN109268344A (en) * | 2018-10-24 | 2019-01-25 | 武汉科技大学 | A kind of governor valve Instantaneous Flow test device and its test method |
| CN109505812A (en) * | 2019-01-17 | 2019-03-22 | 中国铁建重工集团有限公司 | A kind of variable pump bi-mode control hydraulic system and tunneling operation vehicle |
| CN110273896A (en) * | 2019-07-02 | 2019-09-24 | 江苏钧微动力科技有限公司 | A kind of integrated hydraulic number pumping plant |
| CN110439882A (en) * | 2018-05-03 | 2019-11-12 | 杭州诺云科技有限公司 | A kind of concentration hydraulic station energy conservation optimizing method and system |
| CN114198349A (en) * | 2021-12-20 | 2022-03-18 | 中国铁建重工集团股份有限公司 | Continuous wall chain cutter rotary closed hydraulic system and continuous wall equipment |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106762882B (en) * | 2016-12-21 | 2018-05-08 | 浙江大学 | The electro-hydraulic drive system of development machine cutterhead double mode |
-
2009
- 2009-03-02 CN CN2009100964082A patent/CN101503960B/en not_active Expired - Fee Related
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101691877B (en) * | 2009-09-04 | 2012-03-07 | 佛山市顺德区震德塑料机械有限公司 | Servo motor control-based multi-pump combination controlled hydraulic power system |
| CN102032232B (en) * | 2010-12-27 | 2013-01-09 | 清华大学深圳研究生院 | Proportional control type power limitation valve |
| CN102032232A (en) * | 2010-12-27 | 2011-04-27 | 清华大学深圳研究生院 | Proportional control type power limitation valve |
| CN102996138A (en) * | 2012-11-30 | 2013-03-27 | 中煤科工集团重庆研究院 | Hydraulic control system of dust removal and outburst prevention integrated heading machine |
| CN102996138B (en) * | 2012-11-30 | 2015-02-18 | 中煤科工集团重庆研究院有限公司 | Hydraulic control system integrating dust removal and outburst prevention for integrated excavator |
| CN105864132A (en) * | 2015-01-23 | 2016-08-17 | 鞍钢股份有限公司 | Constant-pressure variable pump system and energy-saving method |
| WO2018112792A1 (en) * | 2016-12-21 | 2018-06-28 | 浙江大学 | Heading machine cutterhead fixed and variable displacement combined hydraulic motor drive system and control method |
| CN110439882A (en) * | 2018-05-03 | 2019-11-12 | 杭州诺云科技有限公司 | A kind of concentration hydraulic station energy conservation optimizing method and system |
| CN110439882B (en) * | 2018-05-03 | 2020-07-28 | 杭州诺云科技有限公司 | Energy-saving optimization method and system for centralized hydraulic station |
| CN109268344A (en) * | 2018-10-24 | 2019-01-25 | 武汉科技大学 | A kind of governor valve Instantaneous Flow test device and its test method |
| CN109505812A (en) * | 2019-01-17 | 2019-03-22 | 中国铁建重工集团有限公司 | A kind of variable pump bi-mode control hydraulic system and tunneling operation vehicle |
| CN109505812B (en) * | 2019-01-17 | 2020-11-03 | 中国铁建重工集团股份有限公司 | Variable pump dual-mode control hydraulic system and tunnel operation vehicle |
| CN110273896A (en) * | 2019-07-02 | 2019-09-24 | 江苏钧微动力科技有限公司 | A kind of integrated hydraulic number pumping plant |
| CN110273896B (en) * | 2019-07-02 | 2021-09-24 | 江苏钧微动力科技有限公司 | Integrated hydraulic digital pump station |
| CN114198349A (en) * | 2021-12-20 | 2022-03-18 | 中国铁建重工集团股份有限公司 | Continuous wall chain cutter rotary closed hydraulic system and continuous wall equipment |
| CN114198349B (en) * | 2021-12-20 | 2024-06-14 | 中国铁建重工集团股份有限公司 | Continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101503960B (en) | 2010-12-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101503960B (en) | Multi-pump combined driving shield-tunneling blade disc hydraulic system | |
| CN100520087C (en) | Rotating speed variable driving shield cutterhead energy-saving hydraulic control system | |
| CN100575717C (en) | A kind of energy-saving type shield hydraulic control system that adopts hydraulic transformer | |
| CN101967980B (en) | Cutterhead closed type hydraulic drive system adopting revolving speed-variable and displacement-variable compound control | |
| CN101550830B (en) | Energy-efficient shield cutterhead closed loop hydraulic control system adopting ganged accumulators | |
| CN101403309B (en) | Tunnel shielding blade disc hydraulic control system with widened timing range | |
| CN102747949A (en) | Fast propulsion hydraulic control loop of down-the-hole drill rig | |
| CN101408108B (en) | Shield cutter head hydraulic system driven by mixed motor serial connection and parallel connection | |
| CN106762888B (en) | The electro-hydraulic propulsion system of TBM variable speed variable-displacement pump control and control method | |
| CN201696054U (en) | Closed-type hydraulic driving system with variable-speed variable-displacement combined control of shield cutter head | |
| CN101718200B (en) | Shield cutter rotary drive pressure adapting hydraulic control system of proportional valve controlled energy accumulator | |
| CN108999826A (en) | Raise boring machine multifunction hydraulic integrates valve group | |
| CN105545882A (en) | Electro-hydraulic synchronous uniform loading cutter driving system of tunneling machine | |
| CN201372799Y (en) | Hydraulic device for shield cutterhead | |
| CN201407049Y (en) | Energy-saving shield cutterhead closed-loop hydraulic control system adopting grouped energy accumulator | |
| CN108953309B (en) | Energy recovery and recycling hydraulic system | |
| CN202718623U (en) | Key drilling action single-pump hydraulic control loop of cutting drilling machine | |
| CN201162738Y (en) | Energy-saving hydraulic control apparatus of variable rotation speed driving shield blade disc | |
| CN203548436U (en) | Directly-driven type differential-volume-controlled electro-hydraulic servo control system | |
| CN108150643A (en) | A kind of shift valve block, power head multi gear level controlling system and control method and rotary drilling rig | |
| CN207848069U (en) | A kind of rotation of horizontal directional drilling machine power head prevents reverse control system | |
| CN202148557U (en) | Hydraulic system of excavator | |
| CN102304934A (en) | Hydraulic system of excavator | |
| CN108050113B (en) | Control system for preventing reverse rotation of power head of horizontal directional drilling machine | |
| CN201288568Y (en) | Shield cutter head hydraulic system employing motor series and parallel hybrid driving |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| 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: 20101208 Termination date: 20180302 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |