CN101798909A - Drilling column heave compensation device of marine floating type drilling platform - Google Patents
Drilling column heave compensation device of marine floating type drilling platform Download PDFInfo
- Publication number
- CN101798909A CN101798909A CN 201010140448 CN201010140448A CN101798909A CN 101798909 A CN101798909 A CN 101798909A CN 201010140448 CN201010140448 CN 201010140448 CN 201010140448 A CN201010140448 A CN 201010140448A CN 101798909 A CN101798909 A CN 101798909A
- Authority
- CN
- China
- Prior art keywords
- valve
- links
- compensating
- outer shell
- mouth
- 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
Images
Landscapes
- Earth Drilling (AREA)
Abstract
The invention discloses a drilling column heave compensation device of a marine floating type drilling platform. A composite hydraulic cylinder is adopted as a heave compensation hydraulic cylinder in a crown block heave compensation device; the high-pressure hydraulic oil output by a hydraulic pump flows into a rodless cavity of an inner cylinder and a rod cavity of an outer cylinder of the composite compensation hydraulic cylinder by a compensation control valve to provide controllable additional force for a piston rod of the outer cylinder; and the resultant force of the force and the hydraulic force acted by the rodless cavity of the outer cylinder of the compensation hydraulic cylinder provides support force to a crown block. The direction and magnitude of the additional force are controlled according to the platform heave motion, and the compensation effect of a heave compensation system is improved. A control unit transmits a control command to the hydraulic system according to the motion speed of the platform in the vertical direction, wherein the motion speed is obtained by detection, drives a piston of the compensation hydraulic cylinder to push the crown block to move and compensates the heave motion of the platform so that the crown block, a traveling block and a large hook are in a static state in the vertical direction relative to the well bottom in the allowable range.
Description
Technical field
The present invention relates to the hydraulic control system that electrohydraulic control technology is a feature, relate in particular to a kind of marine drilling platform drill string heave compensator.
Background technology
Along with the exhaustion day by day of land resources, the strategic perspective of development of world economy just gathers on the ocean, and development ocean science and high-tech equipment are particularly important.In oil field, along with development of Chinese economy, particularly as the petrochemical industry and the rapid development of automobile industry of pillar industry, the contradiction that oil and natural gas is under-supply becomes increasingly conspicuous.Day by day exhausted in view of the land oil resource marches to the deep-sea and to become inexorable trend.Current, the offshore oil rig maximum operating water depth has surpassed 3000m, but also will continue to develop to darker direction.Under such depth condition, work, more harsh to the requirement of the each side of rig, and must adapt to some special circumstances that under deep water conditions, faced, many equipment need redesign and develop.
The drill string heave compensator is that the safety that ensures offshore drilling ship or semisubmersible drilling platform operation is carried out and increased work efficiency and one of requisite visual plant of quality.Semisubmersible drilling platform that deep sea drilling adopted and floating barge will produce periodic heave movement under the effect of wave, and drill string is pumped, cause the variation of shaft bottom the pressure of the drill, even make drill bit break away from the shaft bottom, the efficient that influence is crept into reduces drill bit and drilling rod life-span, produces the potential safety hazard of operation, even cause creeping into and being forced to stopping work, caused enormous economic loss.Therefore, in order to reduce the downtime, reduce drilling cost, floating drilling platform must be taked the suitable compensation measure to the drill string heave movement.
The fluid pressure type heave compensation system is used the most general on ocean floating type drilling platform, and form is many, can be divided into three kinds of forms according to its power presentation mode: active, passive type and semi-active type.
Active heave compensation system has compensation effect and stronger compliance preferably, but because the drill string quality is big, it is frequent to pump, so can consume lot of energy in the compensation process.
The passive type heave compensation system does not need system that energy additionally is provided in compensation process substantially, and system is simple, obtained using comparatively widely, but compensation effect is not really desirable, exists certain hysteresis.
The semi-active type heave compensation system is the advantage of the two comprehensively, but system architecture is comparatively complicated, and manufacturing cost is higher.
Summary of the invention
The objective of the invention is to provide a kind of heave compensator of floating offshore oil drilling platform, to satisfy the performance requirement of offshore oil drilling well.
For achieving the above object, general plotting of the present invention is to adopt composite hydraulic cylinder as the heave compensation hydraulic cylinder in crown-block heave compensator.High-pressure and hydraulic oil in the gas-liquid accumulator is led to the rodless cavity of combined type compensating hydraulic cylinder outer shell, thereby a hydraulic coupling of bearing the overhead traveling crane static load is provided; The high-pressure and hydraulic oil of hydraulic pump output is led to the rodless cavity of compound compensating hydraulic cylinder inner casing and the rod chamber of outer shell through compensating control valve, thereby provide the additional force that can control to internal cylinder piston rod, the hydraulic coupling of this power and the effect of compensating hydraulic cylinder outer shell rodless cavity provide support power to overhead traveling crane with joint efforts.
The technical solution used in the present invention is to improve on the basis of the conventional passive type heave compensator that is made of overhead traveling crane, two heave compensation hydraulic cylinders, rocking arm, gas-liquid accumulator, tourist buses, has increased acceleration transducer, fuel tank, motor, hydraulic pump, hydraulic pump outlet one way valve, compensating control valve, inner casing rodless cavity pressure sensor, outer shell rod chamber pressure sensor, bypass valve, governor valve, repairing one way valve, Safety control valve, loss protecting valve and system control unit.Compensating hydraulic cylinder cylinder body and derrick are hinged, and piston rod upper end is hinged with overhead traveling crane, setting pressure sensor on the rodless cavity of the rod chamber of compensating hydraulic cylinder outer shell and inner casing.The inner casing ram area of compensating hydraulic cylinder is 1: 1 with the ratio of outer shell rod chamber work area.The inlet of hydraulic pump links to each other with fuel tank, and outlet links to each other with the P mouth of compensating control valve through one way valve; The T mouth of compensating control valve links to each other with fuel tank; The A mouth of compensating control valve links to each other with the inner casing rodless cavity or the outer shell rod chamber of two combined type compensating hydraulic cylinders with the B mouth; One end of bypass valve links to each other with the inner casing rodless cavity of two combined type compensating hydraulic cylinders, the outer shell rod chamber of the other end and two combined type compensating hydraulic cylinders; The A mouth of governor valve links to each other with the outer shell rod chamber of two combined type compensating hydraulic cylinders, and the B mouth links to each other with the A mouth of compensating control valve; The A mouth of stop valve of surging links to each other with the outer shell rodless cavity of two combined type compensating hydraulic cylinders, and the P mouth links to each other with the A mouth of loss protecting valve; The P mouth of loss protecting valve links to each other with the outlet of air-liquid converter, repairing one way valve and the inlet of Safety control valve simultaneously; The other end of air-liquid converter links to each other with the work gas cylinder by gate valve; The work gas cylinder links to each other with the venting gate valve, and links to each other with gas cylinder by gate valve; Gas cylinder links to each other with pneumatic supply by gate valve; The inlet of repairing one way valve connects together with the outlet of Safety control valve and links to each other with fuel tank; Control module is electrically connected with the control signal interface of compensating control valve, bypass valve, loss protecting valve, adjustable frequency motor respectively, and the signal of telecommunication that obtains outer shell rod chamber pressure sensor, inner casing rodless cavity pressure sensor and be connected in the acceleration transducer on the platform.Hydraulic pump and variable-frequency motor mechanical connection.Control module is the Industrial Personal Computer (IPC) or the single-chip microcomputer that have modulus A/D and digital-to-analogue D/A function switching signal.
The present invention compares with background technology, and the useful effect that has is:
1. compensating hydraulic cylinder adopts composite construction in the system, high-pressure and hydraulic oil in the air-liquid converter bears static load on the overhead traveling crane by the outer shell rodless cavity, hydraulic pump communicates with inner casing rodless cavity or outer shell rod chamber through compensating control valve, overcome in the movement compensation process because frictional force and work storage pressure change the dynamic loading that causes, thereby limited extra energy consumption effectively, and improved compensation effect.
2. lose suddenly when carrying when system, combined type compensating hydraulic cylinder piston rod can fast uplink, and the flow that flows out the outer shell rod chamber increases, but governor valve can be lower than a certain value by limited flow, thus the up speed of limited piston; The pressure of outer shell rod chamber increases simultaneously, and the pressure channel between gas-liquid converter and the combined type compensating hydraulic cylinder is cut off in the stop valve commutation that promotes to surge; The pressure signal that outer shell rod chamber pressure sensor records exceeds allowed band, and control module sends the power supply that control instruction is cut off the loss protecting valve immediately, makes it be in closed condition.By above-mentioned triple protection measure, avoid causing serious accident to take place owing to losing to carry.
3. the loss protecting valve has been installed between gas-liquid converter and the compensating hydraulic cylinder, and when system lost supply of electric power for a certain reason, the loss protecting valve resetted under the effect of spring, cut off the oil circuit between accumulator and the compensating hydraulic cylinder, avoided accident to take place.
4. the control module acceleration signal that can send according to the acceleration transducer of installing on the offshore boring island and the pressure signal of combined type compensating hydraulic cylinder, send instruction to adjustable frequency motor and compensating control valve, control flows to the hydraulic fluid flow rate of combined type compensating hydraulic cylinder inner casing rodless cavity, reduce of the influence of platform heave movement, and then make shaft bottom the pressure of the drill keep constant within the specific limits hook.
Description of drawings
Fig. 1 is the structural representation according to ocean floating type drilling platform crown-block drill string heave compensator proposed by the invention.
Fig. 2 is the hydraulic system principle figure of drilling column heave compensation device of marine floating type drilling platform proposed by the invention.
Among the figure: 1-tourist bus, 2-combined type heave compensation hydraulic cylinder, 3-derrick, 4-rocking arm; the 5-overhead traveling crane, 6-pulley, 7-overhead traveling crane guide rail; the 8-acceleration transducer, 9-fuel tank, 10-hydraulic pump; the 11-adjustable frequency motor, 12-hydraulic pump outlet one way valve, 13-compensating control valve; 14-outer shell rod chamber pressure sensor, 15-inner casing rodless cavity pressure sensor, 16-bypass valve; 17-governor valve, the 18-stop valve that surges, 19-loss protecting valve; 20-air-liquid converter, 21-gate valve, the 22-gas cylinder of working; the 23-gate valve, 24-pneumatic supply, 25-gate valve; the 26-gate valve of exitting, 27-gate valve, 28-gas cylinder; 29-repairing one way valve, 30-Safety control valve, 31-control module.
The specific embodiment
The invention will be further described below in conjunction with drawings and Examples.
As shown in the figure, the cylinder body of compensating hydraulic cylinder 2 and derrick 3 are hinged, and its piston rod upper end is hinged with overhead traveling crane 5, at the rod chamber setting pressure sensor 14 of compensating hydraulic cylinder 2 outer shells, setting pressure sensor 15 on the rodless cavity of inner casing.The inner casing ram area of compensating hydraulic cylinder is 1: 1 with the ratio of outer shell rod chamber work area.Acceleration transducer 8 connects firmly with platform; The inlet of hydraulic pump 10 links to each other with fuel tank 9, and outlet links to each other with the P mouth of compensating control valve 13 through one way valve 12; The T mouth of compensating control valve 13 links to each other with fuel tank 9; The A mouth of compensating control valve 13 links to each other with the inner casing rodless cavity or the outer shell rod chamber of two combined type compensating hydraulic cylinders 2 with the B mouth; One end of bypass valve 16 links to each other with the inner casing rodless cavity of two combined type compensating hydraulic cylinders 2, and the other end links to each other with the outer shell rod chamber of two combined type compensating hydraulic cylinders 2; The A mouth of governor valve 17 links to each other with the outer shell rod chamber of two combined type compensating hydraulic cylinders 2, and the other end links to each other with the A mouth of compensating control valve 13; The A mouth of stop valve 18 of surging links to each other with the outer shell rodless cavity of two combined type compensating hydraulic cylinders 2, and the P mouth links to each other with the A mouth of loss protecting valve 19; The P mouth of loss protecting valve 19 links to each other with the outlet of air-liquid converter 20, repairing one way valve 29 and the inlet of Safety control valve 30 simultaneously; The other end of air-liquid converter 20 links to each other with work gas cylinder 22 by gate valve 21,23; Work gas cylinder 22 links to each other with venting gate valve 26, links to each other with gas cylinder 28 by gate valve 27; Gas cylinder 28 links to each other with pneumatic supply 24 by gate valve 25; The outlet of the inlet of repairing one way valve 29 and Safety control valve 30 connects together and links to each other with fuel tank 9; Control module 31 is electrically connected with the control signal interface of compensating control valve 13, bypass valve 16, loss protecting valve 19, adjustable frequency motor 11 respectively, and is connected with outer shell rod chamber pressure sensor 14, inner casing rodless cavity pressure sensor 15 and the signal of telecommunication that is connected in the acceleration transducer 8 on the platform.Hydraulic pump 10 and variable-frequency motor 11 mechanical connections.Control module 31 is the Industrial Personal Computer (IPC) or the single-chip microcomputer that have modulus A/D and digital-to-analogue D/A function switching signal.High-pressure and hydraulic oil in the air-liquid converter 20 leads to the rodless cavity of combined type compensating hydraulic cylinder 2 outer shells, and a hydraulic coupling of bearing the overhead traveling crane static load is provided; Hydraulic pump 10 communicates with inner casing rodless cavity or outer shell rod chamber by compensating control valve 13, overcomes in the compensation process owing to pressure in frictional force and the work gas cylinder 22 changes the dynamic loading that causes.Bypass valve 16 two ends link to each other with the outer shell rod chamber with the inner casing rodless cavity of compensating hydraulic cylinder 2, and when bypass valve 16 conductings, system can realize the function of passive compensation.Compensating hydraulic cylinder 2 outer shell rod chambers are connected to governor valve 17, prevent because drilling rod takes off the piston rod hypervelocity upper punch of the disconnected compensating hydraulic cylinder 2 that causes.The control mouth of stop valve 18 of surging links to each other with the rod chamber of combined type compensating hydraulic cylinder 2 outer shells, when piston rod exceeds the speed limit when up, the connecting line of air-liquid converter 20 and combined type compensating hydraulic cylinder 2 is cut off in elevated pressure stop valve 18 commutations that promote to surge, and avoids serious accident to take place.Loss protecting valve 19 is installed between air-liquid converter 20 and the compensating hydraulic cylinder 2, cuts off oil circuit during dead electricity automatically, stops to the compensating hydraulic cylinder fuel feeding.
Operating principle of the present invention is as follows:
During operate as normal; the energising of loss protecting valve is in the next conducting state; the stop valve that surges is in the next conducting state under the effect of spring, the hydraulic oil in the air-liquid converter 20 communicates with the outer shell rodless cavity of combined type compensating hydraulic cylinder 2, in order to support the static load on the overhead traveling crane.If bypass valve 16 is in right position conducting state, the inner casing rodless cavity of combined type compensating hydraulic cylinder 2 communicates with the outer shell rod chamber, not redeeming, and this moment, system was conventional passive type heave compensation system.If bypass valve 16 is in position, left side off-state, the inner casing rodless cavity of combined type compensating hydraulic cylinder 2 does not communicate with the outer shell rod chamber, redeeming, and this moment, system was the semi-active type heave compensation system.
When the floating marine drilling platform sinks with wave, derrick can be with combined type compensating hydraulic cylinder 2 to descend, the distortion of the drill string elasticity of elongation reduces, load on the overhead traveling crane 5 reduces, the piston rod of combined type compensating hydraulic cylinder 2 is overhanging, the hydraulic oil of air-liquid converter 20 flows into compensating hydraulic cylinder 2, work gas cylinder 22 pressure reduce, and balances each other with the overhead traveling crane load that has reduced.Be installed in the acceleration of motion that acceleration transducer 8 on the compensating hydraulic cylinder body detects platform, and this signal is passed to control module 31.The pressure signal that while outer shell rod chamber pressure sensor 14 and inner casing rodless cavity pressure sensor 15 detect two chambeies also passes to control module 31.Control module 31 sends control instruction to compensating control valve 13 it is moved to left according to detected above-mentioned signal and according to formulating good control strategy, the P mouth is communicated with the B mouth, the A mouth communicates with the T mouth, hydraulic pump 10 is to combined type compensating hydraulic cylinder 2 inner casing rodless cavity fuel feeding, make inner casing rodless cavity pressure raise, offset because the work storage pressure reduces supporting capacity decline and the overhanging frictional force of piston rod that causes, simultaneously the outer shell rod chamber is communicated with the realization oil return by the A mouth to the passage of T mouth with fuel tank, thereby make overhead traveling crane 5 up with respect to platform, constant to keep the absolute position, load rises to original setting value simultaneously.In this process, the displacement that can regulating spool moves to left changes the flow area of valve port, thereby the control flow improves the compensation effect of system with the movement velocity of control piston.
Otherwise, when the floating marine drilling platform rises with wave, derrick can be with combined type compensating hydraulic cylinder 2 to rise, the distortion of the drill string elasticity of elongation increases, load on the overhead traveling crane 5 increases, the piston rod retraction of combined type compensating hydraulic cylinder 2, the hydraulic oil flow return-air liquid converter 20 in the hydraulic cylinder, the pressure of work gas cylinder 22 increases, and balances each other with the overhead traveling crane load that has increased.Be installed in the acceleration of motion that acceleration transducer 8 on the compensating hydraulic cylinder body detects platform, and this signal is passed to control module 31.The pressure signal that while outer shell rod chamber pressure sensor 14 and inner casing rodless cavity pressure sensor 15 detect two chambeies also passes to control module 31.Control module 31 sends control instruction to compensating control valve 13 it is moved to right according to detected above-mentioned signal and according to formulating good control strategy, the P mouth is communicated with the A mouth, the B mouth communicates with the T mouth, hydraulic pump 10 is to combined type compensating hydraulic cylinder 2 outer shell rod chamber fuel feeding, the outer shell rod chamber pressure that makes raises, offset because the supporting capacity that the rising of work storage pressure causes increases and the frictional force of piston rod retraction, simultaneously the inner casing rodless cavity is communicated with the realization oil return by the B mouth to the passage of T mouth with fuel tank, thereby make overhead traveling crane 5 descending with respect to platform, constant to keep the absolute position, load drops to original setting value simultaneously.In this process, the displacement that can regulating spool moves to right changes the flow area of valve port, thereby the control flow improves the compensation effect of system with the movement velocity of control piston.
When system load changes, can keep the stress balance of combined type compensating hydraulic cylinder 2 piston rods by the pressure of adjusting work gas cylinder 22.When system load reduced, work gas cylinder 22 communicated with venting gate valve 26, by venting the pressure of work gas cylinder is reduced; When system load increased, work gas cylinder 22 communicated with gas cylinder 28, made the pressure increase of work gas cylinder by the inflation of gas cylinder.
Because drilling rod takes off accident such as disconnected causes losing suddenly when carrying, the piston rod of combined type compensating hydraulic cylinder 2 can fast uplink when system, and the flow that flows out the outer shell rodless cavity increases, but governor valve 17 can be lower than a certain value by limited flows, thus the up speed of limited piston; The pressure of outer shell rod chamber increases simultaneously, and the pressure channel between air-liquid converter 20 and the combined type compensating hydraulic cylinder 2 is cut off in stop valve 18 commutations that promote to surge; The pressure signal that outer shell rod chamber pressure sensor 14 records exceeds allowed band, and control module 31 sends the power supply that control instruction is cut off loss protecting valve 19 immediately, makes it be in closed condition.By above-mentioned triple protection measure, avoid causing serious accident to take place owing to losing to carry.
When system lost supply of electric power for a certain reason, loss protecting valve 20 resetted under the effect of spring, cut off the oil circuit between air-liquid converter 20 and the combined type compensating hydraulic cylinder 2, prevented unexpected generation.
The acceleration signal that control module 31 sends according to the acceleration transducer of installing on the offshore boring island 8 and the pressure signal of combined type compensating hydraulic cylinder 2, send instruction to adjustable frequency motor 11 and compensating control valve 13, control flows to the hydraulic fluid flow rate of combined type compensating hydraulic cylinder 2 inner casing rodless cavities or outer shell rod chamber.
The shortcoming that the present invention has overcome that traditional passive type heave compensation system compensatory reactionBu Changfanying speed is slow, energy storage pressure fluctuation and frictional force cause the compensation effect difference. Because hydraulic pump is only to the inner casing rodless cavity fuel feeding of little cylinder diameter, its power only is used for overcoming frictional resistance and system inertia, has therefore effectively controlled the consumption of energy, has reduced the running cost of system, improve compensation precision, had advantage simple in structure, that energy consumption is low, effective. In addition, compensation hydraulic cylinder cylinder body of the present invention is installed on the derrick, does not have relative motion with drilling rig, can adopt rigid line. Require to use flexible pipe to compare with the travelling block compensation arrangement, reduced the possibility that hydraulic line damages.
Claims (5)
1. drilling column heave compensation device of marine floating type drilling platform; Comprise tourist bus (1); Combined type heave compensation hydraulic cylinder (2); Derrick (3); Rocking arm (4); Overhead traveling crane (5); Pulley (6) and overhead traveling crane guide rail (7); Dead line; Fast line; Acceleration transducer (8); Fuel tank (9); Hydraulic pump (10); Adjustable frequency motor (11); Hydraulic pump outlet check valve (12); Compensating control valve (13); Outer shell rod chamber pressure sensor (14); Inner casing rodless cavity pressure sensor (15); By-passing valve (16); Governor valve (17); Stop valve (18) surges; Loss protecting valve (19); Air-liquid converter (20); Gate valve (21) (23) (25) (26) (27); Work gas cylinder (22); Pneumatic supply (24); Gas cylinder (28); Repairing check valve (29); Safety control valve (30) and control module (31); The cylinder body of combined type heave compensation hydraulic cylinder (2) links to each other with derrick (3); The piston rod of hydraulic cylinder (2) links to each other with overhead traveling crane (5); Supporting overhead traveling crane moves along overhead traveling crane guide rail (7); Rocking arm (4) links to each other with overhead traveling crane (5) with derrick (3); Outer shell rod chamber setting pressure sensor (14) at combined type compensating hydraulic cylinder (2); Inner casing rodless cavity setting pressure sensor (15) at combined type compensating hydraulic cylinder (2) connects firmly acceleration transducer (8) at platform; It is characterized in that, the inlet of hydraulic pump (10) links to each other with fuel tank (9), the outlet of hydraulic pump (10) links to each other through the P mouth of one way valve (12) with compensating control valve (13), the T mouth of compensating control valve (13) links to each other with fuel tank (9), and the A mouth of compensating control valve (13) links to each other with the inner casing rodless cavity or the outer shell rod chamber of two combined type compensating hydraulic cylinders (2) with the B mouth; One end of bypass valve (16) links to each other with the inner casing rodless cavity of two combined type compensating hydraulic cylinders (2), and the other end links to each other with the outer shell rod chamber of two combined type compensating hydraulic cylinders (2); The A mouth of governor valve (17) links to each other with the outer shell rod chamber of two combined type compensating hydraulic cylinders (2), and the B mouth links to each other with the A mouth of compensating control valve (13); The A mouth of stop valve (18) of surging links to each other with the outer shell rodless cavity of two combined type compensating hydraulic cylinders (2), and the P mouth links to each other with the A mouth of loss protecting valve (19); The P mouth of loss protecting valve (19) links to each other with the outlet of air-liquid converter (20), repairing one way valve (29) and the inlet of Safety control valve (30) simultaneously; The other end of air-liquid converter (20) links to each other with work gas cylinder (22) by gate valve (21) (23); Work gas cylinder (22) links to each other with venting gate valve (26), links to each other with gas cylinder (28) by gate valve (27); Gas cylinder (28) links to each other with pneumatic supply (24) by gate valve (25); The outlet of the inlet of repairing one way valve (29) and Safety control valve (30) connects together and links to each other with fuel tank (9); Control module (31) is electrically connected with the control signal interface of compensating control valve (13), bypass valve (16), loss protecting valve (19), adjustable frequency motor (11) respectively, and is connected with outer shell rod chamber pressure sensor (14), inner casing rodless cavity pressure sensor (15) and the signal of telecommunication that is connected in the acceleration transducer (8) on the platform.
2. drilling column heave compensation device of marine floating type drilling platform according to claim 1, it is characterized in that, compensating hydraulic cylinder (2) adopts composite construction, air-liquid converter (20) bears static load on the overhead traveling crane (5) by the outer shell rodless cavity, hydraulic pump (10) communicates with inner casing rodless cavity or outer shell rod chamber through compensating control valve (13), overcomes the dynamic loading in the movement compensation process.
3. drilling column heave compensation device of marine floating type drilling platform according to claim 1, it is characterized in that, the compensating cylinder outer shell of combined type compensating hydraulic cylinder (2) is a piston rod, and inner casing is a plunger case, and the inner casing ram area is 1: 1 with the ratio of outer shell rod chamber work area.
4. drilling column heave compensation device of marine floating type drilling platform according to claim 1, it is characterized in that, dead line links to each other with overhead traveling crane (5) by the structure of being made up of rocking arm (4) and pulley (6) with fast line, keep overhead traveling crane (5) when moving up and down dead line point constant with the hoist room rope capacity, avoided working long hours and frequently commutating of boring winch.
5. drilling column heave compensation device of marine floating type drilling platform according to claim 1 is characterized in that, described signaling control unit (31) is an Industrial Personal Computer (IPC) that has modulus A/D and digital-to-analogue D/A function switching signal.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010101404485A CN101798909B (en) | 2010-04-01 | 2010-04-01 | Drilling column heave compensation device of marine floating type drilling platform |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010101404485A CN101798909B (en) | 2010-04-01 | 2010-04-01 | Drilling column heave compensation device of marine floating type drilling platform |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101798909A true CN101798909A (en) | 2010-08-11 |
| CN101798909B CN101798909B (en) | 2012-02-22 |
Family
ID=42594735
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010101404485A Expired - Fee Related CN101798909B (en) | 2010-04-01 | 2010-04-01 | Drilling column heave compensation device of marine floating type drilling platform |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101798909B (en) |
Cited By (34)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102602840A (en) * | 2012-03-27 | 2012-07-25 | 中国水产科学研究院渔业机械仪器研究所 | Heave compensating control system of ocean exploration equipment and control method |
| CN102606087A (en) * | 2012-04-01 | 2012-07-25 | 西南石油大学 | Gear-rack drill string heave compensator for floating drilling platform |
| CN102691484A (en) * | 2012-06-06 | 2012-09-26 | 中国石油大学(华东) | Winch heave compensation device of marine floating drilling platform |
| CN102691682A (en) * | 2011-03-21 | 2012-09-26 | 杨双来 | Method and device for potential energy recovery and storage by utilizing deadweight of crane jib |
| CN102943636A (en) * | 2012-11-22 | 2013-02-27 | 中国石油大学(北京) | Winch heave compensation device for ocean floating drilling platform |
| CN103527146A (en) * | 2013-10-09 | 2014-01-22 | 中国海洋石油总公司 | Screw pump liquid draining well mouth operating platform used on floating type drilling platform |
| CN104627881A (en) * | 2015-03-04 | 2015-05-20 | 广东工业大学 | Super deep floating type drilling multifunctional energy-saving type heavy compensation winch and operation method thereof |
| CN104854300A (en) * | 2012-12-10 | 2015-08-19 | Mhw股份有限公司 | Multi capacity riser tensioners |
| CN104870741A (en) * | 2012-12-12 | 2015-08-26 | 脚轮钻方案解决公司 | Device for connection and disconnection of an active heave compensator |
| CN104912494A (en) * | 2015-05-27 | 2015-09-16 | 中国船舶重工集团公司第七0四研究所 | Deep-water drilling overhead traveling crane type wave compensation device |
| CN105649560A (en) * | 2016-03-31 | 2016-06-08 | 中国石油大学(华东) | Marine floating type drilling riser flexible hanger |
| CN105804675A (en) * | 2016-06-01 | 2016-07-27 | 中国石油大学(华东) | Hydraulic driving system for offshore drilling compensation winch |
| WO2016122321A1 (en) * | 2015-01-29 | 2016-08-04 | Ihc Holland Ie B.V. | Compensator device |
| 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 |
| CN106458302A (en) * | 2014-03-03 | 2017-02-22 | 伊特里克公司 | offshore drilling system, vessel and method |
| CN106499685A (en) * | 2016-11-01 | 2017-03-15 | 中国石油大学(华东) | A kind of semi-active type heave compensator electric-control system |
| CN107060662A (en) * | 2017-02-27 | 2017-08-18 | 中建钢构有限公司 | Half active compensation apparatus control system |
| CN107131163A (en) * | 2017-05-02 | 2017-09-05 | 南华大学 | It is a kind of for it is long when stable loading hydraulic loading system |
| CN108204209A (en) * | 2016-12-19 | 2018-06-26 | Ifp新能源公司 | For mobile unit it is suspended load, there is the motion compensating system of master cylinder and countercylinder |
| CN108278232A (en) * | 2018-02-05 | 2018-07-13 | 浙江大学 | A kind of passive heave compensation system of hydraulic cylinder type based on hydraulic transformer |
| CN108408611A (en) * | 2018-05-08 | 2018-08-17 | 山东大学 | A kind of movable type active compensation device and its working method |
| CN108625801A (en) * | 2018-04-27 | 2018-10-09 | 山东科技大学 | Lifting Pipe in Deep Sea Mining heave compensator |
| CN108757610A (en) * | 2018-06-27 | 2018-11-06 | 山东大学 | A kind of half Active Heave Compensation System of pump control type and its working method |
| WO2018214102A1 (en) * | 2017-05-25 | 2018-11-29 | 深圳配天智能技术研究院有限公司 | Vibration suppression device and robot |
| CN109025854A (en) * | 2018-09-28 | 2018-12-18 | 西南石油大学 | A kind of mounting structure of the mechanically driver type crown-block heave compensator directive wheel for ocean platform drilling well |
| CN109398602A (en) * | 2017-08-15 | 2019-03-01 | 上海船厂船舶有限公司 | The installation method of high pressure air bottle component for drill ship |
| CN109505536A (en) * | 2018-11-12 | 2019-03-22 | 宝鸡石油机械有限责任公司 | Ocean hydraulic drill rig is promoted and compensation device |
| CN109987530A (en) * | 2019-04-01 | 2019-07-09 | 南通力威机械有限公司 | Compensation of undulation piston tensioner and its application method |
| CN110077538A (en) * | 2014-10-24 | 2019-08-02 | 伊特里克公司 | offshore drilling system, vessel and method |
| CN110552928A (en) * | 2019-09-24 | 2019-12-10 | 江苏徐工工程机械研究院有限公司 | Integrated valve and floating hydraulic system |
| CN112046708A (en) * | 2020-09-16 | 2020-12-08 | 中国石油大学(华东) | Hyperstatic-prevention lifting device and offshore platform lifting method |
| CN112678704A (en) * | 2021-01-12 | 2021-04-20 | 湖南科技大学 | Real-time compensation method for given rotating speed of active heave compensation electric transmission system of marine winch |
| CN112943121A (en) * | 2021-03-09 | 2021-06-11 | 中国地质科学院勘探技术研究所 | Linkage pressure regulating device of passive heave compensation system and regulating method thereof |
| CN112943727A (en) * | 2021-02-21 | 2021-06-11 | 广东工业大学 | Heavy-load motion compensation system of mooring winch of crude oil transfer ship |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5209302A (en) * | 1991-10-04 | 1993-05-11 | Retsco, Inc. | Semi-active heave compensation system for marine vessels |
| WO2004001193A2 (en) * | 2002-06-21 | 2003-12-31 | Hydralift Asa | Compensation device |
| CN101130949A (en) * | 2007-09-12 | 2008-02-27 | 中国石油大学(华东) | Drilling column heave compensator for floating drill platform in the sea |
| CN101382042A (en) * | 2008-10-17 | 2009-03-11 | 中国石油大学(华东) | Ocean floating drill platform string heave compensation device |
| CN201236640Y (en) * | 2008-07-25 | 2009-05-13 | 宝鸡石油机械有限责任公司 | Novel travelling hoist compensating system |
| CN101654145A (en) * | 2009-09-30 | 2010-02-24 | 宝鸡石油机械有限责任公司 | Ocean floating type drilling platform crown-block heave compensator |
-
2010
- 2010-04-01 CN CN2010101404485A patent/CN101798909B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5209302A (en) * | 1991-10-04 | 1993-05-11 | Retsco, Inc. | Semi-active heave compensation system for marine vessels |
| WO2004001193A2 (en) * | 2002-06-21 | 2003-12-31 | Hydralift Asa | Compensation device |
| CN101130949A (en) * | 2007-09-12 | 2008-02-27 | 中国石油大学(华东) | Drilling column heave compensator for floating drill platform in the sea |
| CN201236640Y (en) * | 2008-07-25 | 2009-05-13 | 宝鸡石油机械有限责任公司 | Novel travelling hoist compensating system |
| CN101382042A (en) * | 2008-10-17 | 2009-03-11 | 中国石油大学(华东) | Ocean floating drill platform string heave compensation device |
| CN101654145A (en) * | 2009-09-30 | 2010-02-24 | 宝鸡石油机械有限责任公司 | Ocean floating type drilling platform crown-block heave compensator |
Cited By (56)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102691682A (en) * | 2011-03-21 | 2012-09-26 | 杨双来 | Method and device for potential energy recovery and storage by utilizing deadweight of crane jib |
| CN102602840A (en) * | 2012-03-27 | 2012-07-25 | 中国水产科学研究院渔业机械仪器研究所 | Heave compensating control system of ocean exploration equipment and control method |
| CN102602840B (en) * | 2012-03-27 | 2014-10-29 | 中国水产科学研究院渔业机械仪器研究所 | Heave compensating control method of ocean exploration equipment |
| CN102606087A (en) * | 2012-04-01 | 2012-07-25 | 西南石油大学 | Gear-rack drill string heave compensator for floating drilling platform |
| CN102606087B (en) * | 2012-04-01 | 2014-04-09 | 西南石油大学 | Gear-rack drill string heave compensator for floating drilling platform |
| CN102691484B (en) * | 2012-06-06 | 2014-04-16 | 中国石油大学(华东) | Winch heave compensation device of marine floating drilling platform |
| CN102691484A (en) * | 2012-06-06 | 2012-09-26 | 中国石油大学(华东) | Winch heave compensation device of marine floating drilling platform |
| CN102943636B (en) * | 2012-11-22 | 2014-07-23 | 中国石油大学(北京) | Winch heave compensation device for ocean floating drilling platform |
| CN102943636A (en) * | 2012-11-22 | 2013-02-27 | 中国石油大学(北京) | Winch heave compensation device for ocean floating drilling platform |
| CN104854300A (en) * | 2012-12-10 | 2015-08-19 | Mhw股份有限公司 | Multi capacity riser tensioners |
| CN104854300B (en) * | 2012-12-10 | 2017-05-10 | Mhw股份有限公司 | Multi capacity riser tensioners |
| CN104870741A (en) * | 2012-12-12 | 2015-08-26 | 脚轮钻方案解决公司 | Device for connection and disconnection of an active heave compensator |
| US9371705B2 (en) | 2012-12-12 | 2016-06-21 | Castor Drilling Solution As | Device for connection and disconnection of an active heave compensator |
| CN103527146A (en) * | 2013-10-09 | 2014-01-22 | 中国海洋石油总公司 | Screw pump liquid draining well mouth operating platform used on floating type drilling platform |
| CN106458302B (en) * | 2014-03-03 | 2019-03-19 | 伊特里克公司 | offshore drilling system, vessel and method |
| CN106458302A (en) * | 2014-03-03 | 2017-02-22 | 伊特里克公司 | offshore drilling system, vessel and method |
| CN110077538B (en) * | 2014-10-24 | 2021-01-15 | 伊特里克公司 | Offshore drilling system, vessel and method |
| CN110077538A (en) * | 2014-10-24 | 2019-08-02 | 伊特里克公司 | offshore drilling system, vessel and method |
| US10619693B2 (en) | 2015-01-29 | 2020-04-14 | Ihc Holland Ie B.V. | Compensator device |
| NL2014212A (en) * | 2015-01-29 | 2016-09-28 | Ihc Holland Ie Bv | Compensator device. |
| WO2016122321A1 (en) * | 2015-01-29 | 2016-08-04 | Ihc Holland Ie B.V. | Compensator device |
| CN107208402B (en) * | 2015-01-29 | 2020-03-06 | Ihc荷兰Ie有限公司 | Compensator device |
| CN107208402A (en) * | 2015-01-29 | 2017-09-26 | Ihc荷兰Ie有限公司 | Compensator device |
| CN104627881A (en) * | 2015-03-04 | 2015-05-20 | 广东工业大学 | Super deep floating type drilling multifunctional energy-saving type heavy compensation winch and operation method thereof |
| CN104912494A (en) * | 2015-05-27 | 2015-09-16 | 中国船舶重工集团公司第七0四研究所 | Deep-water drilling overhead traveling crane type wave compensation device |
| CN105649560B (en) * | 2016-03-31 | 2018-05-04 | 中国石油大学(华东) | Marine floating type drilling water-separation pipe flexible suspender |
| CN105649560A (en) * | 2016-03-31 | 2016-06-08 | 中国石油大学(华东) | Marine floating type drilling riser flexible hanger |
| CN105804675A (en) * | 2016-06-01 | 2016-07-27 | 中国石油大学(华东) | Hydraulic driving system for offshore drilling compensation winch |
| CN105804675B (en) * | 2016-06-01 | 2017-10-20 | 中国石油大学(华东) | Marine drilling compensates the fluid power system of winch |
| CN106321534B (en) * | 2016-09-21 | 2018-02-16 | 中国石油大学(华东) | Marine floating type well drilling traveling block hook heave compensator |
| 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 |
| CN106499685B (en) * | 2016-11-01 | 2018-04-20 | 中国石油大学(华东) | A kind of semi-active type heave compensator electric-control system |
| CN106499685A (en) * | 2016-11-01 | 2017-03-15 | 中国石油大学(华东) | A kind of semi-active type heave compensator electric-control system |
| CN108204209A (en) * | 2016-12-19 | 2018-06-26 | Ifp新能源公司 | For mobile unit it is suspended load, there is the motion compensating system of master cylinder and countercylinder |
| CN107060662A (en) * | 2017-02-27 | 2017-08-18 | 中建钢构有限公司 | Half active compensation apparatus control system |
| CN107131163A (en) * | 2017-05-02 | 2017-09-05 | 南华大学 | It is a kind of for it is long when stable loading hydraulic loading system |
| CN109312805A (en) * | 2017-05-25 | 2019-02-05 | 深圳配天智能技术研究院有限公司 | Equipment for inhibiting of vibration and robot |
| WO2018214102A1 (en) * | 2017-05-25 | 2018-11-29 | 深圳配天智能技术研究院有限公司 | Vibration suppression device and robot |
| CN109312805B (en) * | 2017-05-25 | 2021-04-02 | 深圳配天智能技术研究院有限公司 | Vibration suppression device and robot |
| CN109398602A (en) * | 2017-08-15 | 2019-03-01 | 上海船厂船舶有限公司 | The installation method of high pressure air bottle component for drill ship |
| CN109398602B (en) * | 2017-08-15 | 2021-09-10 | 上海船厂船舶有限公司 | Method for installing high-pressure air bottle assembly for drilling ship |
| CN108278232A (en) * | 2018-02-05 | 2018-07-13 | 浙江大学 | A kind of passive heave compensation system of hydraulic cylinder type based on hydraulic transformer |
| CN108625801A (en) * | 2018-04-27 | 2018-10-09 | 山东科技大学 | Lifting Pipe in Deep Sea Mining heave compensator |
| CN108408611A (en) * | 2018-05-08 | 2018-08-17 | 山东大学 | A kind of movable type active compensation device and its working method |
| CN108757610A (en) * | 2018-06-27 | 2018-11-06 | 山东大学 | A kind of half Active Heave Compensation System of pump control type and its working method |
| CN109025854A (en) * | 2018-09-28 | 2018-12-18 | 西南石油大学 | A kind of mounting structure of the mechanically driver type crown-block heave compensator directive wheel for ocean platform drilling well |
| CN109505536A (en) * | 2018-11-12 | 2019-03-22 | 宝鸡石油机械有限责任公司 | Ocean hydraulic drill rig is promoted and compensation device |
| CN109505536B (en) * | 2018-11-12 | 2020-04-24 | 宝鸡石油机械有限责任公司 | Lifting and compensating device for marine hydraulic drilling machine |
| CN109987530A (en) * | 2019-04-01 | 2019-07-09 | 南通力威机械有限公司 | Compensation of undulation piston tensioner and its application method |
| CN110552928A (en) * | 2019-09-24 | 2019-12-10 | 江苏徐工工程机械研究院有限公司 | Integrated valve and floating hydraulic system |
| CN112046708A (en) * | 2020-09-16 | 2020-12-08 | 中国石油大学(华东) | Hyperstatic-prevention lifting device and offshore platform lifting method |
| CN112678704A (en) * | 2021-01-12 | 2021-04-20 | 湖南科技大学 | Real-time compensation method for given rotating speed of active heave compensation electric transmission system of marine winch |
| CN112678704B (en) * | 2021-01-12 | 2022-03-22 | 湖南科技大学 | Real-time compensation method for given rotating speed of active heave compensation electric transmission system of marine winch |
| CN112943727A (en) * | 2021-02-21 | 2021-06-11 | 广东工业大学 | Heavy-load motion compensation system of mooring winch of crude oil transfer ship |
| CN112943727B (en) * | 2021-02-21 | 2023-12-01 | 广东工业大学 | Heavy load motion compensation system of crude oil transfer ship mooring winch |
| CN112943121A (en) * | 2021-03-09 | 2021-06-11 | 中国地质科学院勘探技术研究所 | Linkage pressure regulating device of passive heave compensation system and regulating method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101798909B (en) | 2012-02-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101798909B (en) | Drilling column heave compensation device of marine floating type drilling platform | |
| CN100507202C (en) | Drilling column heave compensator for floating drill platform in the sea | |
| CN101382042B (en) | Ocean floating drill platform string heave compensation device | |
| CN102691484B (en) | Winch heave compensation device of marine floating drilling platform | |
| CN105649560B (en) | Marine floating type drilling water-separation pipe flexible suspender | |
| CN101654145B (en) | Ocean floating type drilling platform crown-block heave compensator | |
| CN109098675A (en) | A kind of deep compensation device of passive type deep-sea liter for ocean platform drilling well | |
| CN106321534B (en) | Marine floating type well drilling traveling block hook heave compensator | |
| CN102943636A (en) | Winch heave compensation device for ocean floating drilling platform | |
| CN204283252U (en) | A kind of semi-active type drilling platform crown-block heave compensator | |
| CN108408611A (en) | A kind of movable type active compensation device and its working method | |
| CN111573545B (en) | Distributed energy-saving active and passive composite heave compensation system and working method thereof | |
| CN106286428A (en) | A kind of semi-active type heave compensator hydraulic control system | |
| CN208327199U (en) | A kind of movable type active compensation device | |
| CN108757610B (en) | Pump control type semi-active heave compensation system and working method thereof | |
| CN104389533B (en) | Marine drilling multiple twin car heave compensation and automatic bit feed system | |
| CN108716371B (en) | Compensation function reverse test device of drill string heave compensation system and control method thereof | |
| CN106744308A (en) | Wave compensating device | |
| CN102330541A (en) | Marine drilling riser tensioning system | |
| US11059547B2 (en) | System arranged on a marine vessel or platform, such as for providing heave compensation and hoisting | |
| CN102556875B (en) | Wave compensation system for marine exploration device | |
| WO2021139305A1 (en) | Deep-sea mining field ore-raising pipe lifting/lowering compensation system and compensation method | |
| CN1657393A (en) | Push and pull cylinder variable frequency energy-saving hydraulic elevator system of balancing load by accumulator loop | |
| CN201236640Y (en) | Novel travelling hoist compensating system | |
| CN206555191U (en) | Wave compensating device |
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 | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20120222 Termination date: 20140401 |