CN105804675A - Hydraulic driving system for offshore drilling compensation winch - Google Patents
Hydraulic driving system for offshore drilling compensation winch Download PDFInfo
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- CN105804675A CN105804675A CN201610382999.XA CN201610382999A CN105804675A CN 105804675 A CN105804675 A CN 105804675A CN 201610382999 A CN201610382999 A CN 201610382999A CN 105804675 A CN105804675 A CN 105804675A
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- 238000005553 drilling Methods 0.000 title claims abstract description 30
- 230000009977 dual effect Effects 0.000 claims description 39
- 230000002706 hydrostatic effect Effects 0.000 claims description 29
- 238000006073 displacement reaction Methods 0.000 claims description 27
- 239000012530 fluid Substances 0.000 claims description 24
- 230000033001 locomotion Effects 0.000 claims description 22
- 206010008469 Chest discomfort Diseases 0.000 claims description 20
- 241001074085 Scophthalmus aquosus Species 0.000 claims description 11
- 230000008878 coupling Effects 0.000 claims description 9
- 238000010168 coupling process Methods 0.000 claims description 9
- 238000005859 coupling reaction Methods 0.000 claims description 9
- 239000002828 fuel tank Substances 0.000 claims description 8
- 238000005096 rolling process Methods 0.000 claims description 4
- 239000000203 mixture Substances 0.000 claims description 3
- 208000002925 dental caries Diseases 0.000 claims description 2
- 238000000034 method Methods 0.000 abstract description 10
- 238000004146 energy storage Methods 0.000 abstract description 9
- 238000011084 recovery Methods 0.000 abstract description 4
- 238000005381 potential energy Methods 0.000 abstract 2
- 230000003068 static effect Effects 0.000 abstract 1
- 238000005265 energy consumption Methods 0.000 description 6
- 239000007788 liquid Substances 0.000 description 5
- 101100408352 Drosophila melanogaster Plc21C gene Proteins 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 238000007667 floating Methods 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000011217 control strategy Methods 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000000737 periodic effect Effects 0.000 description 2
- 230000001737 promoting effect Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 239000011800 void material Substances 0.000 description 1
Classifications
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
- E21B19/002—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables specially adapted for underwater drilling
- E21B19/004—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables specially adapted for underwater drilling supporting a riser from a drilling or production platform
- E21B19/006—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables specially adapted for underwater drilling supporting a riser from a drilling or production platform including heave compensators
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/08—Driving gear incorporating fluid motors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/14—Power transmissions between power sources and drums or barrels
- B66D1/22—Planetary or differential gearings, i.e. with planet gears having movable axes of rotation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Geology (AREA)
- Life Sciences & Earth Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Environmental & Geological Engineering (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Earth Drilling (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a hydraulic driving system for an offshore drilling compensation winch.A hydraulic secondary regulation element and a driven hydraulic cylinder jointly drive the winch to fulfill a heave compensation function, and a bit feeding hydraulic motor drives the winch to fulfill an automatic bit feeding function.During compensation, the driven hydraulic cylinder and a liquid-gas energy storage device thereof are used or bearing all static loads of a drilling rig and periodically recovering and releasing gravitational potential energy of loads; the hydraulic secondary regulation element operates in a constant-pressure network to overcome other loads in the compensation process, and the liquid-gas energy storage device periodically recovers and releases inertia kinetic energy of the a winch rotary system.During bit feeding, the driven hydraulic cylinder and the liquid-gas energy storage device thereof recover the gravitational potential energy of the loads of the drilling rig and release in lifting of a drilling rig traveling system.The hydraulic driving system is integrally compact in structure, a hydraulic energy recovery system is high in operation efficiency and long in service life, and an engine is low in power and power consumption.
Description
Technical field:
The present invention relates to a kind of marine drilling and compensate the fluid power system of winch, be a kind of driving device being feature with hydraulic energy recovery and electrohydraulic control technology.
Background technology:
The floating drilling rig that offshore oil drilling adopts will produce periodic heave movement under the effect of the natural causes such as stormy waves, thus driving drilling equipment and drill string to carry out heave movement, have impact on drilling efficiency, add drilling cost, even cause security incident.Therefore must be equipped with a set of heave compensation system on floating drilling platform or drill ship, be used for stablizing Bottom Hole Bit Weight In A, alleviate rig dynamic loading, the quality of its combination property directly affects the development cost of offshore oil.Heave compensation system be integrate mechanical, electrical, air-liquid, automatically control, the complex equipment of Intelligent Measurement, there is the features such as high-tech, high investment, excessive risk.
Heave compensation system can be divided into according to its installation site: heave compensator between crown-block heave compensator, tourist bus and hook and winch heave compensator；Wherein winch heave compensation technology is as a new technique, has the performance advantage of its uniqueness, including drilling efficiency height, transmission is simple, equipment center of gravity is low, platform load with occupy little space etc. performance advantage, paid close attention in the industry gradually.
In recent years, the external research that marine drilling compensates winch has been achieved with bigger progress, and existing electric compensating winch product emerges, newly-built deepwater drilling platform obtains effective application, its cardinal principle is to increase power of motor on the basis of tradition well drilling hoist, adopt alternating-current variable frequency motor active compensation techniques, multiple electric motors combines driving, by sensor, controller is sent in drill string position and platform Heaving Signal, control the rotating speed of winch motor in real time and turn to, it is achieved heave compensation function；Electric compensating winch has many performance advantages, but there is also installed power and measure the technical problems such as big, frequency conversion motor poor in anti-explosion property with energy consumption is too high, the motor feels hot.
Summary of the invention:
The invention aims to the fluid power system providing a kind of marine drilling to compensate winch, meet the performance requirement of offshore oil drilling, reduce installed power and energy consumption, the raising marine drilling work efficiency of system simultaneously.
For achieving the above object, the general plotting of the present invention is: utilize Hydrostatic secondary control element and passive hydraulic cylinder to combine the external toothing driving differential planetary decelerator, completes heave compensation motion；Utilize and send the sun gear boring fluid motor-driven differential planetary decelerator, complete automatic bit feed motion；So that planet carrier drives winch to complete compound motion.In heave compensation motor process, utilize passive hydraulic cylinder and liquid gas energy storage equipment thereof to undertake whole dead loads of rig, utilize Hydrostatic secondary control element to overcome all the other load, and utilize liquid gas energy storage equipment to carry out the gravitional force of drill load and the inertia kinetic energy of winch rotary system periodically reclaiming and release；In automatic bit feed motor process, utilize and send brill hydraulic motor and liquid gas energy storage equipment thereof to reclaim and the gravitional force storing drill load, then discharge when promoting rig traveling system.
The technical solution adopted in the present invention is by electromotor, electromotor, Active Compensation motor, passively compensate hydraulic motor, send brill motor, differential planetary decelerator, cylinder, hydraulic disc brake, the hydraulic-driven scheme developed on the basis of the winch heave compensator that PLC is constituted, Active Compensation motor is replaced with Hydrostatic secondary control element, replace with passive hydraulic cylinder and passively compensate hydraulic motor, brill motor is sent with sending brill hydraulic motor to replace, air-liquid converter and top petrol tank is replaced with dual Piston accumulator, also add constant pressure variable displacement pump, overflow valve, air relief valve, electrohydraulic servo valve, variable delivery hydraulic cylinder, obliquity sensor, relief valve, motor, screw rod, nut, flange.The external toothing power input shaft of Hydrostatic secondary control element and differential planetary decelerator is mechanically connected；The piston rod of passive hydraulic cylinder is mechanically connected with one end of shaft coupling, and the other end of shaft coupling is connected with screw rod mechanism, screw rod and nut composition rolling screw pair, and one end of nut and flange is mechanically connected, the other end of flange and external toothing power input shaft mechanical connection；Brill hydraulic motor is sent to be connected with the sun gear power input shaft of differential planetary decelerator；The piston rod of the swash plate of Hydrostatic secondary control element and variable delivery hydraulic cylinder is mechanically connected；The swash plate boring hydraulic motor is sent to be mechanically connected with motor；Electromotor is mechanically connected with constant pressure variable displacement pump；Piston in dual Piston accumulator high pressure chest and low pressure chamber is mechanically connected with same piston rod, and the piston movement in two cavitys synchronizes.Obliquity sensor is connected with the piston rod of variable delivery hydraulic cylinder, and rotary encoder is connected with external toothing power input shaft, and measuring device of underwell drill pressure is arranged in the drill collar of drilling tool bottom, and motion reference units and drilling platforms connect firmly.The oil-in of constant pressure variable displacement pump is connected with fuel tank, and an oil-out of constant pressure variable displacement pump is connected with the P mouth of electrohydraulic servo valve by air relief valve；The A mouth of electrohydraulic servo valve and B mouth are connected with a mouth of variable delivery hydraulic cylinder and b mouth respectively, and the T mouth of electrohydraulic servo valve is connected with fuel tank；Another oil-out of constant pressure variable displacement pump and the high pressure chest of the first dual Piston accumulator connect；Overflow valve is parallel to constant pressure variable displacement pump two ends；The high pressure hydraulic fluid port of Hydrostatic secondary control element and low pressure hydraulic fluid port are connected with the high pressure chest of the first dual Piston accumulator, low pressure chamber respectively；The high pressure hydraulic fluid port boring hydraulic motor and low pressure hydraulic fluid port is sent to be connected with the high pressure chest of the first dual Piston accumulator, low pressure chamber respectively；The rodless cavity of passive hydraulic cylinder, rod chamber are connected with the high pressure chest of the second dual Piston accumulator, low pressure chamber respectively；First gas cylinder is connected with the air cavity of the first dual Piston accumulator, the first relief valve respectively；Second gas cylinder is connected with the air cavity of the second dual Piston accumulator, the second relief valve respectively；One end of Fill valve is connected with the oil-out of constant pressure variable displacement pump, and the high pressure chest of the other end and the second dual Piston accumulator connects.The signal of telecommunication of obliquity sensor, rotary encoder, motion reference units and measuring device of underwell drill pressure accesses PLC, PLC output control signal and is connected with electrohydraulic servo valve, motor, Fill valve.
The present invention compared with prior art, has following beneficial effect:
1. adopt hydraulic driving mode, electromotor directly drive constant pressure variable displacement pump, decrease energy conversion links；Hydraulic system adopts volumetric void fraction mode, without spill losses, improves the transmission efficiency of system；Additionally, hydraulic system power density is big, compact conformation, decrease platform load and take up room.
2. adopt Hydrostatic secondary control element to combine driving winch with passive hydraulic cylinder and realize heave compensation function, passive hydraulic cylinder is utilized to undertake whole dead loads of rig, reduce output and the energy consumption of electromotor and Hydrostatic secondary control element, also have that leakage rate is little, energy recovery efficiency is high, the advantage of long working life；Utilize Hydrostatic secondary control element to overcome all the other load, and the inertia kinetic energy of winch rotary system is carried out recycle and reuse, reduce further the power of electromotor and energy consumption.
3. send brill hydraulic motor to work in hydraulic pump operating mode, the load gravitional force in drill-through journey will be sent to store in energy storage equipment, then discharge when promoting rig traveling system, reduce further the power of electromotor and energy consumption.
4. adopt dual Piston accumulator as energy storage equipment, improve the Hydrostatic secondary control element oil absorption when pump condition, reduce the pressure oscillation of high-voltage oil cavity and low pressure oil pocket simultaneously, improve the energy storage capacity of accumulator.
Accompanying drawing illustrates:
The present invention is further described below in conjunction with drawings and Examples.
The marine drilling that Fig. 1 is proposed by the invention compensates the schematic diagram of winch fluid power system.
In figure: 1 constant pressure variable displacement pump；2 electromotors；3 overflow valves；4 fuel tanks；5 air relief valve；6.1 first dual Piston accumulators；6.2 second dual Piston accumulators；7.1 first gas cylinders；7.2 second gas cylinders；8.1 first relief valves；8.2 second relief valves；9 Fill valves；10 passive hydraulic cylinders；11 shaft couplings；12 screw rods；13 nuts；14 flanges；15 motors；16 send brill hydraulic motor；17 obliquity sensors；18 variable delivery hydraulic cylinders；19 electrohydraulic servo valves；20 Hydrostatic secondary control elements；21—PLC；22 rotary encoders；23 measuring device of underwell drill pressures；24 motion reference units；25 differential planetary decelerators；26 external toothing power input shafts；27 sun gear power input shafts；28 planet carrier power output shafts；G air cavity；H high pressure chest；L low pressure chamber.
Detailed description of the invention:
The present invention is further described below in conjunction with drawings and Examples.
As it is shown in figure 1, fluid power system mainly includes Hydrostatic secondary control element 20, passive hydraulic cylinder 10, send brill hydraulic motor the 16, first dual Piston accumulator the 6.1, second dual Piston accumulator the 6.2, first gas cylinder the 7.1, second gas cylinder 7.2, constant pressure variable displacement pump 1, variable delivery hydraulic cylinder 18, electrohydraulic servo valve 19, motor 10.During installation, the external toothing power input shaft 26 of Hydrostatic secondary control element 20 and differential planetary decelerator 25 is mechanically connected, and the piston rod of the swash plate of Hydrostatic secondary control element 20 and variable delivery hydraulic cylinder 18 is mechanically connected；The piston rod of passive hydraulic cylinder 10 is mechanically connected with one end of shaft coupling 11, the other end of shaft coupling 11 and screw rod 12 are mechanically connected, screw rod 12 and nut 13 form rolling screw pair, and one end of nut 13 and flange 14 is mechanically connected, and the other end of flange 14 and external toothing power input shaft 26 are mechanically connected；Send the sun gear power input shaft 27 boring hydraulic motor 16 and differential planetary decelerator 25 to be mechanically connected, send the swash plate boring hydraulic motor 16 and motor 10 to be mechanically connected；Electromotor 2 and constant pressure variable displacement pump 1 are mechanically connected.Obliquity sensor 17 is connected with the piston rod of variable delivery hydraulic cylinder 18, and rotary encoder 22 is connected with external toothing power input shaft 26, and measuring device of underwell drill pressure 23 is arranged in the drill collar of drilling tool bottom, and motion reference units 24 and drilling platforms connect firmly.
The oil-in of constant pressure variable displacement pump 1 is connected with fuel tank 4, the oil-out of constant pressure variable displacement pump 1 is connected with the P mouth of electrohydraulic servo valve 19 by air relief valve 5, overflow valve 3 is parallel to the two ends of constant pressure variable displacement pump 1, the A mouth of electrohydraulic servo valve 19, B mouth are connected with a mouth of variable delivery hydraulic cylinder 18, b mouth respectively, and the T mouth of electrohydraulic servo valve 19 is connected with fuel tank 4；Another oil-out of constant pressure variable displacement pump 1 and the high pressure chest H of the first dual Piston accumulator 6.1 connect, and the high pressure hydraulic fluid port of Hydrostatic secondary control element 20, low pressure hydraulic fluid port are connected with high pressure chest H, the low pressure chamber L of the first dual Piston accumulator 6.1 respectively；Brill the high pressure hydraulic fluid port of hydraulic motor 16, low pressure hydraulic fluid port is sent to be connected with high pressure chest H, the low pressure chamber L of the first dual Piston accumulator 6.1 respectively；The rodless cavity of passive hydraulic cylinder 10, rod chamber are connected with high pressure chest H, the low pressure chamber L of the second dual Piston accumulator 6.2 respectively；First gas cylinder 7.1 is connected with the air cavity G of the first dual Piston accumulator 6.1, the first relief valve 8.1 respectively；Second gas cylinder 7.2 is connected with the air cavity G of the second dual Piston accumulator 6.2, the second relief valve 8.2 respectively；One end of Fill valve 9 is connected with the oil-out of constant pressure variable displacement pump 1, and the high pressure chest H of the other end and the second dual Piston accumulator 6.2 connects.Rotary encoder 22, measuring device of underwell drill pressure 23, motion reference units 24, obliquity sensor 17 the signal of telecommunication access PLC21, PLC21 output control the signal of telecommunication be connected with electrohydraulic servo valve 19, motor 15, Fill valve 9.Second dual Piston accumulator 6.2 and the second gas cylinder 7.2 undertake the rig dead load compensated in motor process by passive hydraulic cylinder 10；First dual Piston accumulator the 6.1, first gas cylinder 7.1 and constant pressure variable displacement pump 1 form constant pressure network, drive Hydrostatic secondary control element 20 to overcome all the other load compensated in motor process, and driving send brill hydraulic motor 16 to overcome the rig load sent in drill-through journey.
The operation principle of the present invention is as follows:
When floating marine drilling platforms rises with wave, sinks, the Hydrostatic secondary control element swash plate angle signal compensating moving angular displacement signal, the platform heave movement signal of motion reference units 24 detection, swashplate angle sensor 17 detection that PLC21 detects according to rotary encoder 22, and send control signal according to the control strategy made to electrohydraulic servo valve 19, the swashplate angle of Hydrostatic secondary control element 20 is controlled, thus driving the forward and reverse rotation of external toothing power input shaft 26 to realize heave compensation function by the position of regulated variable hydraulic cylinder 18 piston rod.In compensating motor process, passive hydraulic cylinder 10 drives external toothing jointly with Hydrostatic secondary control element 20；The rectilinear motion of piston rod is converted to the rotary motion of external toothing power input shaft 26 by passive hydraulic cylinder 10 by worm drive, the power that piston rod exports is converted to moment of torsion and acts on external toothing power input shaft 26, assume responsibility for whole dead loads of rig, and utilize the second dual Piston accumulator 6.2 and the second gas cylinder 7.2 that drill load gravitional force is carried out recycle and reuse；Hydrostatic secondary control element 20 overcomes all the other load compensated in motor process, and utilize the first dual Piston accumulator 6.1 and the first gas cylinder 7.1 that the inertia kinetic energy of winch rotary system is carried out recycle and reuse: when winch needs retarded motion, Hydrostatic secondary control element 20 works in hydraulic pump operating mode, so that the inertia kinetic energy of winch and assembly pulley is stored in the first dual Piston accumulator 6.1 and the first gas cylinder 7.1, when winch accelerated motion, Hydrostatic secondary control element 20 works in hydraulic motor operating mode, the energy that release has stored.
Send in drill-through journey at rig, the Bottom Hole Bit Weight In A signal that PLC21 detects according to measuring device of underwell drill pressure 23, and send control signal according to the control strategy made to motor 15, control to send the swashplate angle boring hydraulic motor 16 by regulating the angular displacement of motor 15, it is made to drive sun gear power input shaft 27 to rotate continuously, realize permanent the pressure of the drill automatic bit feed, the drill load gravitional force in drill-through journey will be sent to store in the first dual Piston accumulator 6.1 and the first gas cylinder 7.1 simultaneously.
Hydraulic energy-saving actuation techniques is applied to marine drilling and compensates winch by the present invention, winch is driven by the system of the device compositions such as Hydrostatic secondary control element, hydraulic cylinder, constant pressure variable displacement pump, accumulator, bolt and nut, while realizing heave compensation and automatic bit feed function, drill load gravitional force and winch rotary system inertia kinetic energy have been carried out periodic recycle and reuse, improve efficiency and the service life of hydraulic energy recovery system, reduce the installed power and energy consumption that compensate winch；Additionally, the present invention adopts hydraulic volume control mode, there is the advantages such as transmission efficiency height, compact conformation, explosion-proof performance be good.
Claims (4)
- null1. the fluid power system of a marine drilling compensation winch，Including constant pressure variable displacement pump (1)、Electromotor (2)、Overflow valve (3)、Fuel tank (4)、Air relief valve (5)、First dual Piston accumulator (6.1)、Second dual Piston accumulator (6.2)、First gas cylinder (7.1)、Second gas cylinder (7.2)、First relief valve (8.1)、Second relief valve (8.2)、Fill valve (9)、Passive hydraulic cylinder (10)、Shaft coupling (11)、Screw rod (12)、Nut (13)、Flange (14)、Motor (15)、Send brill hydraulic motor (16)、Obliquity sensor (17)、Variable delivery hydraulic cylinder (18)、Electrohydraulic servo valve (19)、Hydrostatic secondary control element (20)、PLC(21)、Rotary encoder (22)、Measuring device of underwell drill pressure (23)、Motion reference units (24)、Differential planetary decelerator (25)，It is characterized in that，The external toothing power input shaft (26) of Hydrostatic secondary control element (20) and differential planetary decelerator (25) is mechanically connected，The piston rod of the swash plate of Hydrostatic secondary control element (20) and variable delivery hydraulic cylinder (18) is mechanically connected；One end of the piston rod of passive hydraulic cylinder (10) and shaft coupling (11) is mechanically connected, the other end of shaft coupling (11) is mechanically connected with screw rod (12), screw rod (12) and nut (13) composition rolling screw pair, one end of nut (13) and flange (14) is mechanically connected, and the other end of flange (14) is mechanically connected with external toothing power input shaft (26)；Send and bore hydraulic motor (16) and is mechanically connected with the sun gear power input shaft (27) of differential planetary decelerator (25), send the swash plate boring hydraulic motor (16) and motor (10) mechanical connection；Electromotor (2) is mechanically connected with constant pressure variable displacement pump (1)；Obliquity sensor (17) is connected with the piston rod of variable delivery hydraulic cylinder (18), rotary encoder (22) is connected with external toothing power input shaft (26), measuring device of underwell drill pressure (23) is arranged in the drill collar of drilling tool bottom, and motion reference units (24) and drilling platforms connect firmly；The oil-in of described constant pressure variable displacement pump (1) is connected with fuel tank (4), the oil-out of constant pressure variable displacement pump (1) is connected with the P mouth of electrohydraulic servo valve (19) by air relief valve (5), overflow valve (3) is parallel to the two ends of constant pressure variable displacement pump (1), the A mouth of electrohydraulic servo valve (19) and B mouth are connected with a mouth of variable delivery hydraulic cylinder (18) and b mouth respectively, and the T mouth of electrohydraulic servo valve (19) is connected with fuel tank (4)；Another oil-out of constant pressure variable displacement pump (1) and the high pressure chest H of the first dual Piston accumulator (6.1) connect, and the high pressure hydraulic fluid port of Hydrostatic secondary control element (20), low pressure hydraulic fluid port are connected with high pressure chest H, the low pressure chamber L of the first dual Piston accumulator (6.1) respectively；Send and bore the high pressure hydraulic fluid port of hydraulic motor (16), low pressure hydraulic fluid port is connected with high pressure chest H, the low pressure chamber L of the first dual Piston accumulator (6.1) respectively；The rodless cavity of passive hydraulic cylinder (10), rod chamber are connected with high pressure chest H, the low pressure chamber L of the second dual Piston accumulator (6.2) respectively；First gas cylinder (7.1) respectively with the first dual Piston accumulator (6.1), air cavity G, the first relief valve (8.1) is connected；Second gas cylinder (7.2) respectively with the second dual Piston accumulator (6.2), air cavity G, the first relief valve (8.2) is connected；One end of Fill valve (9) is connected with the oil-out of constant pressure variable displacement pump (1), and the high pressure chest H of the other end and the second dual Piston accumulator (6.2) connects；The signal of telecommunication of obliquity sensor (17), rotary encoder (22), measuring device of underwell drill pressure (23) and motion reference units (24) all accesses PLC (21), PLC (21) the output control signal of telecommunication and is connected with electrohydraulic servo valve (19), motor (15), Fill valve (9).
- 2. fluid power system according to claim 1, it is characterized in that, the piston of the high pressure chest H and low pressure chamber L of described first dual Piston accumulator (6.1) is mechanically connected with same piston rod, piston movement in two cavitys synchronizes, when the fluid of Hydrostatic secondary control element (20) high pressure chest flows into the high pressure chest H of the first dual Piston accumulator (6.1), the fluid of low pressure chamber L is pressed into the low pressure chamber of Hydrostatic secondary control element (20) by the first dual Piston accumulator (6.1) simultaneously.
- 3. fluid power system according to claim 1, it is characterized in that, the piston rod of described passive hydraulic cylinder (10) is connected with external toothing power input shaft (26) by shaft coupling (11), screw rod (12), nut (13), flange (14), undertakes whole dead loads of rig.
- 4. fluid power system according to claim 1, it is characterized in that, nut (12) adopts rolling spiral drive mode with screw rod (13), and the linear reciprocating motion of passive hydraulic cylinder (10) piston rod is converted to the crankmotion of external toothing power input shaft (26).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610382999.XA CN105804675B (en) | 2016-06-01 | 2016-06-01 | Marine drilling compensates the fluid power system of winch |
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| CN201610382999.XA CN105804675B (en) | 2016-06-01 | 2016-06-01 | Marine drilling compensates the fluid power system of winch |
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| CN105804675A true CN105804675A (en) | 2016-07-27 |
| CN105804675B CN105804675B (en) | 2017-10-20 |
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Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106286428A (en) * | 2016-11-01 | 2017-01-04 | 中国石油大学(华东) | A kind of semi-active type heave compensator hydraulic control system |
| CN106321534A (en) * | 2016-09-21 | 2017-01-11 | 中国石油大学(华东) | Heave compensation device of hook block assembly for marine floating drilling |
| CN106499683A (en) * | 2016-11-22 | 2017-03-15 | 天津苑博科技有限公司 | Electrohydraulic controlling mechanism |
| CN108547833A (en) * | 2018-05-14 | 2018-09-18 | 山东大学 | It is a kind of to be used for the electrohydraulic system and working method that heave compensator energy regenerating utilizes |
| CN109738218A (en) * | 2018-12-28 | 2019-05-10 | 宝鸡石油机械有限责任公司 | A kind of external pressure Work condition analogue experimental rig of drilling and extracting equipment |
| CN110040642A (en) * | 2019-03-29 | 2019-07-23 | 宝鸡石油机械有限责任公司 | A kind of half active compensation of undulation winch |
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| CN110040642A (en) * | 2019-03-29 | 2019-07-23 | 宝鸡石油机械有限责任公司 | A kind of half active compensation of undulation winch |
| CN110040642B (en) * | 2019-03-29 | 2020-11-20 | 宝鸡石油机械有限责任公司 | Semi-active heave compensation winch |
| GB2603351A (en) * | 2019-09-16 | 2022-08-03 | Mhwirth As | Hydraulic tensioner system |
| WO2021054837A1 (en) * | 2019-09-16 | 2021-03-25 | Mhwirth As | Hydraulic tensioner system |
| GB2603351B (en) * | 2019-09-16 | 2023-08-02 | Mhwirth As | Hydraulic tensioner system |
| CN111720387A (en) * | 2020-06-12 | 2020-09-29 | 山东交通学院 | Motion control method for agricultural equipment mobile operation platform |
| CN112125194A (en) * | 2020-09-23 | 2020-12-25 | 中国石油大学(华东) | Energy-saving driving system of ocean drilling compensation winch |
| CN112125194B (en) * | 2020-09-23 | 2022-02-01 | 中国石油大学(华东) | Energy-saving driving system of ocean drilling compensation winch |
| CN112594262A (en) * | 2020-12-16 | 2021-04-02 | 徐州徐工挖掘机械有限公司 | Energy recovery system for construction machine and construction machine |
| CN113357234A (en) * | 2021-07-09 | 2021-09-07 | 合肥工业大学 | Energy recovery system of energy accumulator group engineering machinery rotating device based on digital control |
| CN113357234B (en) * | 2021-07-09 | 2023-01-17 | 合肥工业大学 | Energy recovery system of energy accumulator group engineering machinery rotating device based on digital control |
| CN113942951A (en) * | 2021-09-24 | 2022-01-18 | 浙江汉德瑞智能科技有限公司 | Marine winch heave compensation device and method |
| CN114427551A (en) * | 2022-03-14 | 2022-05-03 | 合肥工业大学 | Energy recovery system of anchor and mooring equipment hydraulic system based on energy accumulator |
| CN114427551B (en) * | 2022-03-14 | 2023-06-30 | 合肥工业大学 | Energy accumulator-based energy recovery system of hydraulic system of anchor winch |
| RU2819462C1 (en) * | 2023-12-07 | 2024-05-21 | Федеральное государственное бюджетное учреждение науки Тихоокеанский океанологический институт им. В.И. Ильичева Дальневосточного отделения Российской академии наук | Winch with torque transformer |
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