CN106089127B - A kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation - Google Patents
A kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation Download PDFInfo
- Publication number
- CN106089127B CN106089127B CN201610595540.8A CN201610595540A CN106089127B CN 106089127 B CN106089127 B CN 106089127B CN 201610595540 A CN201610595540 A CN 201610595540A CN 106089127 B CN106089127 B CN 106089127B
- Authority
- CN
- China
- Prior art keywords
- hydraulic
- overhead traveling
- traveling crane
- valve
- directive wheel
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 238000005553 drilling Methods 0.000 title claims abstract description 52
- 238000007667 floating Methods 0.000 claims abstract description 104
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 41
- 239000010959 steel Substances 0.000 claims abstract description 41
- 239000002965 rope Substances 0.000 claims abstract description 39
- 230000000875 corresponding Effects 0.000 claims abstract description 14
- 230000002441 reversible Effects 0.000 claims description 23
- 239000010720 hydraulic oil Substances 0.000 claims description 17
- 239000007788 liquid Substances 0.000 claims description 13
- 238000009434 installation Methods 0.000 claims description 12
- 238000004804 winding Methods 0.000 claims description 2
- 238000000034 method Methods 0.000 abstract description 28
- 230000000694 effects Effects 0.000 abstract description 6
- 239000003921 oil Substances 0.000 description 12
- 238000010586 diagram Methods 0.000 description 8
- 239000012530 fluid Substances 0.000 description 8
- 238000006073 displacement reaction Methods 0.000 description 7
- 239000003208 petroleum Substances 0.000 description 7
- 238000007906 compression Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 241001074085 Scophthalmus aquosus Species 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 2
- 230000001808 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000003068 static Effects 0.000 description 2
- 235000002912 Salvia officinalis Nutrition 0.000 description 1
- 238000011030 bottleneck Methods 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000002708 enhancing Effects 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000035800 maturation Effects 0.000 description 1
- 238000005065 mining Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 235000002020 sage Nutrition 0.000 description 1
- 239000001296 salvia officinalis l. Substances 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 230000003245 working Effects 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP 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
- E21B19/08—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods
- E21B19/09—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods specially adapted for drilling underwater formations from a floating support using heave compensators supporting the drill string
Abstract
The present invention relates to a kind of semi-active type overhead traveling crane heave compensation systems for deepwater drilling operation, it includes floating overhead traveling crane, gear-rack drive compensation device, hydraulic pressure support locking device, guider, the passive compensation components such as steel wire rope rocker arm body and corresponding control system, and gear-rack drive compensation system improves the stability and reliability of floating overhead traveling crane heave compensation；Floating overhead traveling crane hydraulic pressure support locking system improves the stability of hydraulic support system, increases emergency lock function；Guider can control the swing in heave compensation so that floating overhead traveling crane being capable of even running in heave compensation process；Passive compensation steel wire rope rocker arm body can realize passive compensation function, and improve the capacity usage ratio and compensation efficiency of heave compensation movement.The beneficial effects of the invention are as follows：Overhead traveling crane heave compensation system is improved, improves the stability, reliability and compensation efficiency of travelling hoist compensating system.
Description
Technical field
The present invention relates to deepwater drilling equipment technical fields, particularly a kind of semi-active type day for deepwater drilling operation
Vehicle heave compensation system.
Background technology
With the fast development of national economy in recent years, demand of the China to petroleum resources sharply increases, imbalance between supply and demand day
It is beneficial severe, have become and restrict the bottleneck problem that China's future economy further develops in a healthy way.For this purpose, national tailor
《China's 21 century sustainable development petroleum resources strategical planning》, the Major Strategic target call of the planning " from global strategy
Eye, ensures the supply steady in a long-term of petroleum resources ", it is necessary to fully " the basic guaranteeing role for playing domestic petroleum resources ", and
Ensure that the external dependence degree of the oil gas supply in 20 years from now on is less than 60% safety line.Simultaneously《National economy and social development
12 five-year-plan outlines》Also clearly proposing will " rational exploitation and utilization marine resources, positive Development of Marine oil gas, ocean fortune
The new industries such as defeated, marine engineering equipment manufacture, strengthen basic, perspective, key technique the R＆D intensity in ocean ", it carries
High China's ocean science is horizontal, enhances ocean exploitation ability.It is marched to deep-sea, progress oil and gas development, which utilizes, has become China
The main direction of development of Oil Strategy from now on pushes the degree domestic and technical merit of marine oil and gas equipment, this is China's reality
Oil and gas development is applied to move towards deep-sea and safeguard the technical foundation of maritime rights and interests.（Liao's plan sage's Chinese Sea petroleum drilling and mining equipment manufacturing industries
Progress and suggestion [C] Chinese ocean petroleum and gas world summit collection of thesis, 2006. Zhou Shouwei, Jin Xiaojian, Zeng Hengyi wait extra large
Platform [J] the China engineering science of foreign petroleum equipment and facility-support Offshore Oil Industry, 2010,12 (5)：102-
112. Liu Qing is friendly, Xu Tao deep sea drilling heave compensator present status in China and thinking of development [J] Southwest Petrol University journal
(natural science edition), 2014,36 (3)：1-8.）
In deep-sea oil gas exploitation drilling operation course is carried out, need by the use of floating drilling platform as Active workings and people
Member's recycle base, since the effect of the natural load such as external wind, wave can transport the heave of semisubmersible drilling platform generating period
Dynamic, which will make the drill string that hook is hung that platform be followed to do reciprocal heave movement together.When drilling platforms rises displacement
Greatly, hook drives drillstring motion and drill bit is made to be detached from shaft bottom, influences the drilling efficiency of drill bit；When drilling platforms declines displacement
Greatly, drill string, which is compressed, causes Bottom Hole Bit Weight In A to be more than regulation bit pressure, may damage drill bit or damage drill string by pressure, cause drilling safety hidden
Suffer from.To avoid the generation of drilling safety accident and reducing drillng operation cost, need to hang deep sea drilling platform drill string system
The heave movement of system takes appropriate motion compensation measure.
Heave compensator, can be to because of floating as the drillng operation key equipment during deep-sea oil gas utilization
Drill string heave displacement carries out effective compensation caused by drilling platforms heave movement, so as to ensure drillng operation efficiency and use peace
Entirely, drillng operation period and cost are reduced.Floating drilling platform is broadly divided into two kinds for the compensation way of drill string heave movement：
1. add telescopic drill rod in drill string pipe string；2. increase various types drill string heave compensator on drilling platforms.It is flexible to bore
For bar due to that can not adjust Bottom Hole Bit Weight In A, operation difficulty is big, is gradually replaced in recent years by the latter.Drill string heave compensator according to
Power presentation mode can be divided into passive type, semi-active type and active three classes in compensation process；According to compensation device structure type
Crown-block heave compensator, hook block heave compensator, dead line heave compensator and winch heave compensation dress can be divided into
Put four classes.
Crown-block heave compensator develops all a kind of earlier rise as the actual use of input scene and correlative compensation technology
Heavy compensation device, because of its technology maturation and high safety and reliability, obtains in deep water floating drilling platform and drill ship at present
Extensive use.The device is mainly by floating overhead traveling crane, driving compensation system, hydraulic support system（By compensation hydraulic cylinder assembly, hydraulic pressure
The compositions such as pipeline, control valve, accumulator）, guider（It is made of directive wheel, guide support frame etc.）, steel wire rope rocker arm body
And the components composition such as corresponding control system.
The crown-block heave compensator used at present mainly using hydraulic-driven compensating form, in fluid power system due to
There are the hydraulic components such as a large amount of fluid pressure lines and control valve so that compensation system rings the compensation of drilling platforms heave movement
The compensation speed of crown-block heave compensator can should be had an impact with efficiency there are certain hysteresis quality；
Since there are a large amount of hydraulic components in compensation system, hydraulic system is made easily to be let out under larger pressure condition
Dew influences safety and the use reliability of compensation system, the problems such as due to hydraulic system leakage or hydraulic valve Pipeline Failure
Caused work accident can cause compensation system to need shut-down (breakdown) mainteance, thus increase system maintenance difficulty and overall operation into
This.In overhead traveling crane heave compensation motion process, some drillng operations need floating overhead traveling crane to be locked in a certain level altitude position,
Convenient for the progress of the operating processes such as the upper, shackle in operation process.
Floating overhead traveling crane can make the power end of Mechanical Driven mode to be located at Drilling derrick in heave compensation motion process
Floating overhead traveling crane generation in top is waved, and is unfavorable for the steady progress of movement compensation process.
Steel wire rope rocker arm body is in the crown-block heave compensator for carry out heaving movement compensation to floating drilling platform
Important component, steel wire rope rocker arm body mainly play drilling line guiding role and reduce steel wire rope and twisted in drilling well
Winding number on vehicle realizes the abrasion for reducing steel wire rope and the purpose for improving service life.The existing mechanism does not have energy
Amount storage and the passive compensation function of release, but the drill string weight that drilling line is hung has tons up to a hundred, is heaved using overhead traveling crane
Compensation device is in drillstring motion compensation process, steel wire rope rocker arm body part has a large amount of available energy, this part energy
Amount can not be all utilized during the motion.
Existing overhead traveling crane heave compensation system does not have locking work(using hydraulic-driven compensating form, hydraulic support system
Can, and can generate and wave in compensation process, in addition, steel wire rope rocker arm body kinergety can not be used.Conventional overhead traveling crane liter
The compensation efficiency of heavy compensation system generally existing floating overhead traveling crane is not high, and floating overhead traveling crane is not sufficiently stable during pumping
And each mechanism reliability it is not high the problems such as.
Invention content
The shortcomings that it is an object of the invention to overcome the prior art, provides a kind of semi-active type for deepwater drilling operation
Overhead traveling crane heave compensation system, the device using mechanically driver type replace original compensation system in hydraulic drive type, increase it is floating
Dynamic overhead traveling crane locks guide function and improves the passive compensation function of steel wire rope rocker arm body, and with simple in structure, reliability
Good, the advantages that compensation efficiency is high and system response time is fast.
The purpose of the present invention is achieved through the following technical solutions：A kind of semi-active type overhead traveling crane for deepwater drilling operation
Heave compensation system including derrick frame, gear-rack drive compensation mechanism, hydraulic pressure support locking mechanism, guider, has
Passive compensation steel wire rope rocker arm body, floating overhead traveling crane and the tourist bus of passive compensation function, the gear-rack drive compensation mechanism
The top of derrick frame is fixedly mounted on, guider is mounted in derrick frame, and floating overhead traveling crane is slidably mounted on guider
On, and can float up and down along guider, the hydraulic pressure support locking mechanism is mounted on the bottom of derrick frame, and with floating
Overhead traveling crane connects, and the hydraulic pressure support locking mechanism can lock floating overhead traveling crane at an arbitrary position, and the passive compensation steel wire rope shakes
Arm mechanism is mounted on the two bottom sides of derrick frame, and the passive steel wire rope rocker arm body that compensates is connect with floating overhead traveling crane, the tourist bus
It is lifted on floating overhead traveling crane by steel wire rope, hook is installed on tourist bus.
The gear-rack drive compensation mechanism includes location and installation platform, spur rack track one, spur rack track two, driving
Gear one and drive gear two, the location and installation platform are fixed on the top of derrick frame, are symmetrically installed on location and installation platform
Small electromotor one and small electromotor two, output terminal and the drive gear one of small electromotor one are sequentially connected, small electromotor two it is defeated
Outlet is sequentially connected with drive gear two, and spur rack track one and spur rack track two are placed in the one of location and installation platform back-to-back
Side, spur rack track one are engaged with drive gear one, and spur rack track two is engaged with drive gear two, spur rack track one and straight
The lower end of rack-track two is fixed on the upper end of floating overhead traveling crane.
The hydraulic pressure support locking mechanism includes hydraulic support cylinder one, hydraulic support cylinder two and can store hydraulic pressure support
The accumulator of the hydraulic energy of cylinder one and hydraulic support cylinder two, hydraulic support cylinder one and hydraulic support cylinder two are fixed on derrick frame
Bottom, the telescopic rod of hydraulic support cylinder one and hydraulic support cylinder two is respectively symmetrically supported on the lower section of floating overhead traveling crane, accumulator
It is connect respectively with hydraulic support cylinder one and hydraulic support cylinder two.
The first interface of the rodless cavity of the hydraulic support cylinder one and hydraulic support cylinder two and two-way cover-plate type inserted valve one
Connection, the second interface of two-way cover-plate type inserted valve one are connect with the first interface of two-way cover-plate type inserted valve two, two-way cover board
The second interface of formula inserted valve two is connect with accumulator；The rod chamber of the hydraulic support cylinder one and hydraulic support cylinder and three four
The first interface connection of logical electro-hydraulic proportion reversing valve, the second interface of 3-position 4-way electro-hydraulic proportion reversing valve respectively with unidirectional variable
The outlet of hydraulic pump is connected with the first interface of direct acting type overflow valve, third interface and the back of the body of 3-position 4-way electro-hydraulic proportion reversing valve
The first interface connection of pressure valve, the entrance of unidirectional volume adjustable hydraulic pump, the second interface of direct acting type overflow valve and counterbalance valve the
Two interfaces are connect respectively with hydraulic oil container, and unidirectional volume adjustable hydraulic pump is by motor drive.
Main line between the hydraulic support cylinder one and the rodless cavity of hydraulic support cylinder and two-way cover-plate type inserted valve one
On the rod chamber and 3-position 4-way of hydraulic support cylinder rodless cavity pressure gauge, the hydraulic support cylinder one and hydraulic support cylinder are installed
Hydraulic support cylinder rod chamber pressure gauge, the two-way lid are installed on the main line between the first interface of electro-hydraulic proportion reversing valve
Bi-bit bi-pass Hydraulic guide control reversal valve, two-way cover board are installed between board-like inserted valve one and two-way cover-plate type inserted valve two
The side of formula inserted valve two is equipped with two-position two-way electromagnetic directional valve.
The hydraulic pressure support locking mechanism further includes hydraulic locking circuit, and the hydraulic locking circuit includes filter, two
Position two-way pilot operated directional control valve, hydraulic pilot valve, single-acting pneumatic operation valve and gas tank, the both ends difference of single-acting pneumatic operation valve
It is connected with gas tank, the first control terminal of two-position two-way hydraulic control reversal valve is connect with accumulator, and filter is changed with two-position two-way hydraulic control
Connect to the first interface of valve with filter, the second interface of two-position two-way hydraulic control reversal valve respectively with hydraulic pilot valve first
Control terminal is connected with hydraulic oil container, and the second control terminal of hydraulic pilot valve controls respectively with the second of two-position two-way hydraulic control reversal valve
End is connected with third interface, and the first control terminal of two-position two-way hydraulic control reversal valve connects with the first entrance of single-acting pneumatic operation valve
It connects, second entrance of the filter also with single-acting pneumatic operation valve is connect, the first outlet and hydraulic pressure of single-acting pneumatic operation valve
Fuel tank connects, and check valve, the entrance of check valve are equipped on the pipeline between two-position two-way hydraulic control reversal valve and hydraulic pilot valve
Side is connect with the second outlet of single-acting pneumatic operation valve, and outlet side is connect with the first control terminal of single-acting pneumatic operation valve.
The guider includes the linear guide, directive wheel and axial guidance supporting rack, the linear guide and is vertically installed at well
On frame frame, to be fixed between the linear guide and derrick frame by axial guidance supporting rack, directive wheel is mounted on floating overhead traveling crane,
Directive wheel coordinates with the linear guide.
The linear guide includes the linear guide one and the linear guide two mounted on derrick frame side, mounted on derrick
The linear guide three of frame opposite side and the linear guide four, directive wheel include with one corresponding directive wheel one of the linear guide, it is and straight
Two corresponding directive wheel two of line guide rail, with three corresponding directive wheel three of the linear guide and with four corresponding directive wheel of the linear guide
Four, directive wheel one is mounted on by guide wheel shaft one on floating overhead traveling crane, and directive wheel two is mounted on floating day by guide wheel shaft two
Che Shang, directive wheel three are mounted on by guide wheel shaft three on floating overhead traveling crane, and directive wheel four is mounted on by guide wheel shaft four and floated
On overhead traveling crane.
The passive compensation steel wire rope rocker arm body include rocking arm shoring one, rocking arm shoring two, rocking arm shoring three,
Rocking arm shoring four, rocking arm directive wheel one, rocking arm directive wheel two, hydraulic cylinder one and hydraulic cylinder two, the lower end of rocking arm shoring one
It is hingedly mounted on fast line directive wheel, quick directive wheel is mounted on the side of derrick frame, and upper end is hingedly equipped with rocking arm guiding
Wheel one, the one end of rocking arm directive wheel one also with rocking arm shoring two is hinged, and the other end and the floating overhead traveling crane of rocking arm shoring two are cut with scissors
Connect connected, the one end of rocking arm directive wheel one also with hydraulic cylinder one is hinged, and the other end of hydraulic cylinder one is hinged on derrick frame, is shaken
The lower end of arm shoring four is hingedly mounted on dead line directive wheel, and dead line directive wheel is mounted on the opposite side of derrick frame, upper end
Rocking arm directive wheel two is hingedly installed, the one end of rocking arm directive wheel two also with rocking arm shoring three is hinged, rocking arm shoring three
The other end is hinged and connected with floating overhead traveling crane, and the one end of rocking arm directive wheel two also with hydraulic cylinder two is hinged, the other end of hydraulic cylinder two
It is hinged on derrick frame, after fast line is around fast line directive wheel and rocking arm directive wheel one, into floating overhead traveling crane and the idler wheel of tourist bus
It is wound, after dead line is around dead line directive wheel and rocking arm directive wheel two, the idler wheel into floating overhead traveling crane and tourist bus is wound.
The side of the hydraulic cylinder one is additionally provided with accumulator one, and accumulator one is connect with the rodless cavity of hydraulic cylinder one, institute
The side for stating hydraulic cylinder two is additionally provided with accumulator two, and accumulator two is connect with the rodless cavity of hydraulic cylinder two.
The present invention has the following advantages：
1st, the present invention is the overhead traveling crane heave compensation system of half Active Compensation formula, with passive compensation and Active Compensation formula
The advantages of two class compensation device systems, therefore, such compensation device system, can realize two big work(of passive compensation and Active Compensation
Energy.
2nd, when floating overhead traveling crane is in the lock state, crown-block heave compensator does not generate active drive power to floating overhead traveling crane
Effect, floating overhead traveling crane static load pass through gas-liquid accumulator storage energy at this time by Double-hydraulic shoring system bearing；When overhead traveling crane liter
When heavy compensation device is in compensation process, which is released, and can effectively mitigate gear-rack drive compensation system and exist
The load born in engagement process ensures effective work of Mechanical Driven part.It floating overhead traveling crane and its hangs and is supported on liter
Any position in heavy compensation path is locked, even if the fuel lead rupture oil leak in drill rod breaking or hydraulic circuit is met with
During situation, it can also be closed automatically.
3rd, the linear guide upper and lower ends are fixed on upper derrick outer framework, are formed between directive wheel and the linear guide mutual
It squeezes, and is connected with floating overhead traveling crane, it can be achieved that guiding role to crown-block heave compensator in movement compensation process, and
The non-contact side setting axial guidance supporting rack of guide rail.
4th, the floating overhead traveling crane of crown-block heave compensator is oriented in movement compensation process by drilling line in rocking arm
The mobile pressure generated to hydraulic cylinder piston rod is shunk on wheel, at the same make the gas of air accumulator in gas-liquid accumulator by compression reality
The storage of existing energy, and can the energy that stored during upper one be discharged by gas-liquid accumulator, push hydraulic cylinder piston rod
Steel wire rope moves, and the heave movement of floating overhead traveling crane is passively compensated.
Description of the drawings
Fig. 1 is the structure diagram of the present invention；
Fig. 2 is gear-rack drive compensation system structure diagram of the present invention；
Fig. 3 is hydraulic support system schematic diagram；
Fig. 4 is hydraulic support system loop diagram；
Fig. 5 is hydraulic locking loop diagram；
Fig. 6 is guider schematic view of the mounting position；
Fig. 7 is guider structure diagram；
Fig. 8 is passive compensation steel wire rope rocker arm body structure diagram；
Fig. 9 is hydraulic cylinder-accumulator connection diagram；
In figure：1- derrick frames, 2- floating overhead traveling cranes, 3- gear-rack drive compensation mechanisms, 4- hydraulic pressure support locking mechanisms,
5- guiders, 6- passively compensate steel wire rope rocker arm body, 7- tourist buses, 8- steel wire ropes, 9- location and installations, 10- spur rack tracks
One, 11- spur rack track two, 12- drive gears one, 13- drive gears two, 14- small electromotors one, 15- small electromotors two,
16- hydraulic support cylinders one, 17- hydraulic support cylinders two, 18- accumulators, 19- two-way cover-plate types inserted valve one, 20- two-way cover-plate types
Inserted valve two, 21- 3-position 4-way electro-hydraulic proportion reversing valves, the unidirectional volume adjustable hydraulic pumps of 22-, 23- direct acting type overflow valves, 24- back pressures
Valve, 25- motor, 26- hydraulic support cylinder rodless cavity pressure gauges, 27- hydraulic support cylinder rod chamber pressure gauges, 28- bi-bit bi-pass
Hydraulic guide control reversal valve, 29- two-position two-way electromagnetic directional valves, 30- hydraulic oil containers, 31- filters, 32- bi-bit bi-pass liquid
Control reversal valve, 33- hydraulic pilot valves, 34- single-acting pneumatic operation valves, 35- gas tanks, 36- the linear guides, 37- directive wheels, 38-
Axial guidance supporting rack, 39- the linear guides one, 40- the linear guides two, 41- the linear guides three, 42- the linear guides four, 43- is led
To wheel one, 44- directive wheels two, 45- directive wheels three, 46- directive wheels four, 47- guide wheel shafts one, 48- guide wheel shafts two, 49- is led
To wheel shaft three, 50- guide wheel shafts four, 51- rocking arms shoring one, 52- rocking arms shoring two, 53- rocking arms shoring three, 54- shakes
Arm shoring four, 55- rocking arms directive wheel one, 56- rocking arms directive wheel two, 57- hydraulic cylinders one, 58- hydraulic cylinders two, 59- fast lines are led
To wheel, 60- dead line directive wheels, 61- fast lines, 62- dead lines, 63- accumulators one, 64- accumulators two.
Specific embodiment
The present invention will be further described below in conjunction with the accompanying drawings, but protection scope of the present invention is not limited to following institute
It states.
As shown in Figure 1, a kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation, including derrick frame
1st, gear-rack drive compensation mechanism 3, hydraulic pressure support locking mechanism 4, guider 5, the passive benefit for having passive compensation function
8 rocker arm body 6 of steel wire rope, floating overhead traveling crane 2 and tourist bus 7 are repaid, the gear-rack drive compensation mechanism 3 is fixedly mounted on derrick frame
The top of frame 1, guider 5 are mounted in derrick frame 1, and floating overhead traveling crane 2 is slidably mounted on guider 5, and being capable of edge
Guider 5 floats up and down, and the hydraulic pressure support locking mechanism 4 is mounted on the bottom of derrick frame 1, and connects with floating overhead traveling crane 2
It connects, the hydraulic pressure support locking mechanism 4 can lock floating overhead traveling crane 2, the passive compensation 8 rocking arm machine of steel wire rope at an arbitrary position
Structure 6 is mounted on the two bottom sides of derrick frame 1, and passive 8 rocker arm body 6 of steel wire rope that compensates is connect with floating overhead traveling crane 2, the tourist bus
7 are lifted on by steel wire rope 8 on floating overhead traveling crane 2, and hook is equipped on tourist bus 7.
As shown in Fig. 2, the gear-rack drive compensation mechanism 3 includes location and installation platform 9, spur rack track 1, straight
Rack-track 2 11, drive gear 1 and drive gear 2 13, the location and installation platform 9 are fixed on the top of derrick frame 1,
Small electromotor 1 and small electromotor 2 15, the output terminal of small electromotor 1 and driving are symmetrically installed on location and installation platform 9
Gear 1 is sequentially connected, and output terminal and the drive gear 2 13 of small electromotor 2 15 are sequentially connected, one 10 He of spur rack track
Spur rack track 2 11 is placed in the side of location and installation platform 9 back-to-back, and spur rack track 1 is engaged with drive gear 1,
Spur rack track 2 11 is engaged with drive gear 2 13, and the lower end of spur rack track 1 and spur rack track 2 11 is fixed on floating
The upper end of dynamic overhead traveling crane 2.In overhead traveling crane heave compensation motion process, small electromotor 1 and small electromotor 2 15 are in correlative compensation number
According to input control under, start and drive drive gear 1 and drive gear 2 13 rotate so that one 10 He of spur rack track
Spur rack track 2 11 moves up and down relative to drive gear 1 and drive gear 2 13, realizes to floating overhead traveling crane 2 and passes through
Steel wire rope 8 hangs the heave compensation movement of tubing string, by the rotating campaign of small electromotor 1 and small electromotor 2 15 with
Mechanical separator speed speed can control the compensation campaign direction for the floating overhead traveling crane 2 being connected with spur rack and compensation displacement.Use compensation
Motor 1 and small electromotor 2 15 provide the mechanical energy that floating overhead traveling crane 2 moves up and down, and use drive gear and spur rack rail
The purpose for improving overhead traveling crane compensation efficiency and precision is realized in the cooperation in road.
As shown in figure 3, the hydraulic pressure support locking mechanism 4 include hydraulic support cylinder 1, hydraulic support cylinder 2 17 and
The accumulator 18 of the hydraulic energy of hydraulic support cylinder 1 and hydraulic support cylinder 2 17, hydraulic support cylinder 1 and liquid can be stored
Pressure shoring 2 17 is fixed on the telescopic rod difference of the bottom of derrick frame 1, hydraulic support cylinder 1 and hydraulic support cylinder 2 17
Symmetric support is connect in the lower section of floating overhead traveling crane 2, accumulator 18 with hydraulic support cylinder 1 and hydraulic support cylinder 2 17 respectively.When
When floating overhead traveling crane 2 is in the lock state, crown-block heave compensator does not generate floating overhead traveling crane 2 effect of active drive power, floats
The Double-hydraulic shoring system bearing that 2 static load of overhead traveling crane is made of hydraulic support cylinder 1 and hydraulic support cylinder 2 17, leads at this time
Cross 18 storage energy of accumulator；When crown-block heave compensator is in compensation process, which is released, can be effective
Mitigate the load that gear-rack drive compensation system is born in engagement process, ensure effective work of Mechanical Driven part.
As shown in figure 4, the rodless cavity of the hydraulic support cylinder 1 and hydraulic support cylinder 2 17 is inserted with two-way cover-plate type
The first interface connection of valve 1, the of the second interface of two-way cover-plate type inserted valve 1 and two-way cover-plate type inserted valve 2 20
One interface connects, and the second interface of two-way cover-plate type inserted valve 2 20 is connect with accumulator 18；One 16 He of hydraulic support cylinder
The rod chamber of hydraulic support cylinder is connect with the first interface of 3-position 4-way electro-hydraulic proportion reversing valve 21, and 3-position 4-way electric-hydraulic proportion is changed
It is connect to first interface of the second interface respectively with the outlet of unidirectional volume adjustable hydraulic pump 22 and direct acting type overflow valve 23 of valve 21, three
The third interface of position four-way electro-hydraulic proportion reversing valve 21 is connect with the first interface of counterbalance valve 24, and unidirectional volume adjustable hydraulic pump 22 enters
The second interface of mouth, the second interface of direct acting type overflow valve 23 and counterbalance valve 24 is connect respectively with hydraulic oil container 30, unidirectional to become
Amount hydraulic pump 22 is driven by motor 25.Using 3-position 4-way electro-hydraulic proportion reversing valve 21 as connection one 16 He of hydraulic support cylinder
The control valve of 22 outlet pressure of rod chamber pressure and unidirectional volume adjustable hydraulic pump of hydraulic support cylinder 2 17.It compares and is controlled only with pump
The hydraulic circuit of mode, since in the movement compensation process of crown-block heave compensator, unidirectional volume adjustable hydraulic pump 22 is sometimes
There is the situation that entrance input pressure is more than hydraulic fluid pressure in outlet hydraulic shoring rod chamber so that the work work of hydraulic pump
Condition is changed into the hydraulic motor operating mode that motor 25 is driven to be in generating state, this in the process can consume part energy in electricity
On 25 resistance heating of motivation, system capacity utilization rate and the reliability of motor 25 are reduced.Therefore, the hydraulic pressure branch in the design
Cylinder hydraulic circuit system is supportted by the way of pump control plus valve control, avoids that hydraulic pump is made to be in hydraulic motor state, can effectively carry
High-energy utilization rate.
Master between the hydraulic support cylinder 1 and the rodless cavity of hydraulic support cylinder and two-way cover-plate type inserted valve 1
Hydraulic support cylinder rodless cavity pressure gauge 26 is installed on pipeline, the rod chamber of the hydraulic support cylinder 1 and hydraulic support cylinder with
Hydraulic support cylinder rod chamber pressure gauge is installed on the main line between the first interface of 3-position 4-way electro-hydraulic proportion reversing valve 21
27, bi-bit bi-pass hydraulic pilot control is installed between the two-way cover-plate type inserted valve 1 and two-way cover-plate type inserted valve 2 20
Reversal valve 28 processed, the side of two-way cover-plate type inserted valve 2 20 are equipped with two-position two-way electromagnetic directional valve 29.In the hydraulic system
In circuit, when the rod chamber of hydraulic support cylinder 1 and hydraulic support cylinder 2 17 needs feed flow, the unidirectional variable liquid in circuit
Press pump 22 is in running order under the drive of motor 25, and unidirectional 22 outlet pressure of volume adjustable hydraulic pump is more than its entrance pressure at this time
Power；When finding that pressure increases in rod chamber by hydraulic support cylinder rod chamber pressure gauge 27, show hydraulic support cylinder inner carrier
A distance is moved up relative to cylinder body, 3-position 4-way electro-hydraulic proportion reversing valve 21 is in running order, by hydraulic pressure support
Circuit between cylinder rod chamber and hydraulic oil container 30 is connected so that hydraulic oil liquid is changed by 3-position 4-way electric-hydraulic proportion in rod chamber
Hydraulic oil container 30 is flowed back to valve 21 and counterbalance valve 24；When the circuit between unidirectional volume adjustable hydraulic pump 22 and hydraulic support cylinder is truncated
When, hydraulic pump flow is zero at this time, will can effectively avoid the appearance of hydraulic motor operating mode.It is transported in crown-block heave compensator
In dynamic compensation process, hydraulic support cylinder rodless cavity is connected with accumulator 18, since hydraulic oil liquid flow is larger in pipeline, by two
Cone valve in logical cover-plate type inserted valve is inserted into as master element in hydraulic circuit, in conjunction with two groups of commutations in hydraulic circuit
Valve realizes and works fluid with small flow to control the mode of big flow work fluid, have flow resistance is small, negotiability is big,
The characteristics of good airproof performance, high quick action and reliability.When drill string is in normal drilling process, shut-off valve is opened, and two
Two electric change valves 29 of position are closed, and two-way cover-plate type inserted valve 2 20 is opened, bi-bit bi-pass Hydraulic guide control reversal valve 28
It is closed under action of hydraulic force, as soon as two-way cover-plate type inserted valve 19 connected to it is opened, accumulator 18 and two groups at this time
The rodless cavity of hydraulic support cylinder is connected.When mechanical driving mechanism provide active drive power under the action of, to floating overhead traveling crane 2 into
During the upward motion compensation of row, piston in two groups of hydraulic support cylinders is needed to move upwards generation hydraulic thrust relative to cylinder body, is stored
Energy device 18 pours fluid by shut-off valve and two two-way cover-plate type inserted valves to two groups of hydraulic support cylinder rodless cavities.It is same with this
When, the spool of 3-position 4-way electro-hydraulic proportion reversing valve 21 is operated in right position, and hydraulic oil passes through in two groups of hydraulic support cylinder rod chambers
3-position 4-way electro-hydraulic proportion reversing valve 21 and counterbalance valve 24 are flowed into hydraulic oil container 30 so that two groups of hydraulic support cylinder rodless cavities
Interior hydraulic coupling is more than hydraulic coupling in rod chamber, and the piston in cylinder body generates floating overhead traveling crane 2 under the action of two chamber pressure force differences
Effective push to mitigate the input of driving force in mechanical driving mechanism, ensures the reliable movement of crown-block heave compensator.
During needing to be adjusted Bottom Hole Bit Weight In A using crown-block heave compensator, using hydraulic support cylinder cylinder
Internal hydraulic fluid pressure is effectively adjusted.In the process, after drilling platforms operating personnel receive the instruction for adjusting bit pressure, to
The controller of control 25 rotating speed of motor sends out adjustment of rotational speed order, and motor 25 is by driving the row of unidirectional volume adjustable hydraulic pump 22
Amount changes so that the hydraulic fluid flow rate variation being flowed into hydraulic support cylinder rod chamber, so as to fulfill to Bottom Hole Bit Weight In A
Adjustment effect.
As shown in figure 5, the hydraulic pressure support locking mechanism 4 further includes hydraulic locking circuit, the hydraulic locking circuit packet
Include filter 31, two-position two-way hydraulic control reversal valve 32, hydraulic pilot valve 33, single-acting pneumatic operation valve 34 and gas tank 35, nonoculture
It is connected respectively with gas tank 35 with the both ends of pneumatic operation valve 34, the first control terminal and accumulator of two-position two-way hydraulic control reversal valve 32
18 connections, filter 31 are connect with the first interface of two-position two-way hydraulic control reversal valve 32 with filter 31, and two-position two-way hydraulic control changes
It is connected respectively with the first control terminal of hydraulic pilot valve 33 and hydraulic oil container 30 to the second interface of valve 32, hydraulic pilot valve 33
Second control terminal is connect respectively with the second control terminal of two-position two-way hydraulic control reversal valve 32 and third interface, and two-position two-way hydraulic control changes
It is connect to the first control terminal of valve 32 with the first entrance of single-acting pneumatic operation valve 34, filter 31 is also pneumatically grasped with single-acting
Make the second entrance connection of valve 34, the first outlet of single-acting pneumatic operation valve 34 is connected with hydraulic oil container 30, bi-bit bi-pass liquid
Check valve is installed on pipeline between control reversal valve 32 and hydraulic pilot valve 33, the entrance side of check valve is pneumatically grasped with single-acting
Make the second outlet connection of valve 34, outlet side is connect with the first control terminal of single-acting pneumatic operation valve 34.Hydraulic circuit
In bi-bit bi-pass Hydraulic guide control reversal valve 28 at, two groups of combination hydraulic locking/deceleration valves and bi-bit bi-pass liquid are set
Pressure pilot control change-over valve 28 collectively constitutes hydraulic locking circuit, this two groups of valve group conjunctions enable to floating overhead traveling crane 2 and its hang
It hangs any position being supported in heave compensation path to be locked, even if fuel feeding is soft in drill rod breaking or hydraulic circuit is met with
During tracheal rupture oil leak situation, it can also be closed automatically.34 both ends of single-acting pneumatic operation valve are connected with gas tank 35, by gas tank
35 realize its opening and closing.Single-acting pneumatic operation valve 34 can carry out manual operation by handle, and the right end position of the operation valve is closes
Closed state, left position are in an open state, and centre position is auto state.When 34 handle of single-acting pneumatic operation valve is in right end
During position, hydraulic locking valve is closed, and the circuit that the hydraulic oil in two groups of hydraulic support cylinders flows into hydraulic cylinder is truncated so that
Hydraulic pressure support cylinder piston rod is fixed at the latched position in heave compensation path；When 34 handle of single-acting pneumatic operation valve is in
When at left position, two chamber of hydraulic support cylinder to the circuit of hydraulic cylinder is in unimpeded state；When single-acting pneumatic operation valve
34 handles from left position be moved to centre position when, the hydraulic circuit of hydraulic support cylinder is in unimpeded state, and can ensure work as
During floating 2 suddenly change of overhead traveling crane, hydraulic locking valve can be automatically closed；When 34 handle of single-acting pneumatic operation valve is moved from right end
During to centre position, hydraulic locking valve is still within closed state, and the oil return speed in hydraulic circuit at this time can be accelerated.If
When being automatically brought into operation, need 34 handle of single-acting pneumatic operation valve being moved at left position, and keep the state
34 middle position of single-acting pneumatic operation valve is moved the handle into after several seconds again.
As shown in fig. 6, the guider 5 includes the linear guide 36, directive wheel 37 and axial guidance supporting rack 38, straight line
Guide rail 36 is vertically installed on derrick frame 1, solid by axial guidance supporting rack 38 between the linear guide 36 and derrick frame 1
Fixed, directive wheel 37 is mounted on floating overhead traveling crane 2, and directive wheel 37 coordinates with the linear guide 36.36 upper and lower ends of the linear guide are fixed
It is formed and mutually squeezed, and be connected with floating overhead traveling crane 2, it can be achieved that right on derrick frame 1, between directive wheel 37 and the linear guide 36
Guiding role of the crown-block heave compensator in movement compensation process, simultaneously as 36 length of the linear guide is longer, in straight line
36 non-contact side of guide rail setting axial guidance supporting rack 38, guider 5 can effectively avoid floating overhead traveling crane 2 from generating larger horizontal stroke
To swing.
As shown in fig. 7, the linear guide 1 and straight line that the linear guide 36 includes mounted on 1 side of derrick frame are led
Rail 2 40, mounted on the linear guide 3 41 of 1 opposite side of derrick frame and the linear guide 4 42, directive wheel 37 includes leading with straight line
One 39 corresponding directive wheel 1 of rail, with 2 40 corresponding directive wheel 2 44 of the linear guide, corresponding with the linear guide 3 41 lead
To wheel 3 45 and with 4 42 corresponding directive wheel 4 46 of the linear guide, directive wheel 1 is mounted on floating by guide wheel shaft 1
On dynamic overhead traveling crane 2, directive wheel 2 44 is mounted on by guide wheel shaft 2 48 on floating overhead traveling crane 2, and directive wheel 3 45 passes through guide wheel shaft
3 49 are mounted on floating overhead traveling crane 2, and directive wheel 4 46 is mounted on by 50 axis four of directive wheel on floating overhead traveling crane 2.
As shown in figure 8,8 rocker arm body 6 of the passive compensation steel wire rope includes rocking arm shoring 1, rocking arm shoring two
52nd, rocking arm shoring 3 53, rocking arm shoring 4 54, rocking arm directive wheel 1, rocking arm directive wheel 2 56, hydraulic cylinder 1 and liquid
Cylinder pressure 2 58, the lower end of rocking arm shoring 1 are hingedly mounted on fast line directive wheel 59, and quick directive wheel is mounted on derrick frame
The side of frame 1, upper end are hingedly equipped with rocking arm directive wheel 1, the one end of rocking arm directive wheel 1 also with rocking arm shoring 2 52
Hinged, the other end and the floating overhead traveling crane 2 of rocking arm shoring 2 52 are hinged and connected, rocking arm directive wheel 1 also with hydraulic cylinder 1
One end is hinged, and the other end of hydraulic cylinder 1 is hinged on derrick frame 1, and the lower end of rocking arm shoring 4 54 is hingedly mounted on extremely
It restricts on directive wheel 60, dead line directive wheel 60 is mounted on the opposite side of derrick frame 1, and upper end is hingedly equipped with rocking arm directive wheel two
56, the one end of rocking arm directive wheel 2 56 also with rocking arm shoring 3 53 is hinged, the other end and the floating day of rocking arm shoring 3 53
Vehicle 2 is hinged and connected, and the one end of rocking arm directive wheel 2 56 also with hydraulic cylinder 2 58 is hinged, and the other end of hydraulic cylinder 2 58 is hinged on well
On frame frame 1, after fast line 61 is around fast line directive wheel 59 and rocking arm directive wheel 1, into floating overhead traveling crane 2 and the idler wheel of tourist bus 7
It is wound, after dead line 62 is around dead line directive wheel 60 and rocking arm directive wheel 2 56, into floating overhead traveling crane 2 and the idler wheel of tourist bus 7
It is wound.Rocking arm directive wheel 1 and rocking arm directive wheel 2 56 determine the situation of movement locus in guarantee fast line 61 and dead line 62
Under, help to mitigate the abrasion of fast line 61 and dead line 62 in heave compensation motion process, while rocking arm supporting rod one, rocking arm branch
Strut two and rocking arm supporting rod three, rocking arm supporting rod four can carry out flexible rotating around mobile cut with scissors.Accumulator 1 and accumulator two
64 are separately mounted to hydraulic cylinder 1 and 2 58 inferior part of the cylinder block side of hydraulic cylinder and carry out inner cylinder body to be connected.
As shown in Figure 8 and Figure 9, the side of the hydraulic cylinder 1 is additionally provided with accumulator 1, accumulator 1 and liquid
The rodless cavity connection of cylinder pressure 1, the side of the hydraulic cylinder 2 58 is additionally provided with accumulator 2 64, accumulator 2 64 and hydraulic pressure
The rodless cavity connection of cylinder 2 58, passive 8 rocker arm body 6 of steel wire rope that compensates is in passive compensation process, by hydraulic cylinder piston rod, steel
Gas constitutes a complete energy stores and release cycle system in hydraulic oil and accumulator in cord 8, hydraulic cylinder.Overhead traveling crane
The floating overhead traveling crane 2 of heave compensator is in movement compensation process, the passive passive compensation energy for compensating 8 rocker arm body 6 of steel wire rope
Amount is mainly derived from and shrinks the mobile pressure generated to hydraulic cylinder piston rod on rocking arm directive wheel 37 by steel wire rope 8, simultaneously
The gas of air accumulator 35 in accumulator is made to be realized the storage of energy by compression, and institute during accumulator release upper one can be passed through
The energy of storage makes hydraulic cylinder piston rod that steel wire rope 8 be pushed to move, the heave movement of floating overhead traveling crane 2 is passively compensated.
The passive compensation process of passive compensation 8 rocker arm body of steel wire rope is specific as follows：Floating drilling platform is in ocean ring
Under the load effect of border, when upward heave movement is generated in heave movement plane, the floating overhead traveling crane 2 of crown-block heave compensator
Under mechanical driving mechanism driving, driving is engaged by hydraulic support cylinder and drive gear and the spur rack gear teeth so that floating
Overhead traveling crane 2 is realized in the guide rail of guider 5 to be moved downward to carry out motion compensation to the displacement of generation, passively compensates steel at this time
Two amplitude shifts in 8 rocker arm body 6 of cord are moved hinge and inwardly carry out contractile motion, the floating overhead traveling crane 2 hung by drilling line 8
Weight is larger, it is made to generate larger pressure to rocking arm directive wheel 1 and rocking arm directive wheel 2 56 during rocker motion, leads to
It crosses when moving hydraulic cylinder 1 and hydraulic cylinder 2 58 that hinge is connected with rocking arm directive wheel 1 and rocking arm directive wheel 2 56 by pressure
Contraction is generated, gas carries out in pair accumulator 1 being connected with each other with hydraulic cylinder 1 and hydraulic cylinder 2 58 and accumulator 2 64
Compression, and utilize the storage of accumulator 1 and the realization energy of accumulator 2 64；When floating drilling platform generates downward movement
When, floating overhead traveling crane 2 is needed to move upwards carry out motion compensation, the passive mobile hinge for compensating 8 rocker arm body 6 of steel wire rope is outside therewith
It puts on display, accumulator 1 and accumulator 2 64 discharge the energy stored in previous motion process at this time, for pushing hydraulic cylinder one
57 and hydraulic cylinder 2 58 move out, drive what steel wire rope 8 was hung by rocking arm directive wheel 1 and rocking arm directive wheel 2 56
Floating overhead traveling crane 2 moves upwards, and mitigates the supply of extraneous compensation energy.
The course of work of the present invention is as follows：During being compensated to drill string heave movement, when floating drilling platform or brill
When well ship rises with wave, hook and 7 load of tourist bus can be caused to increase, drive hydraulic support cylinder in hydraulic pressure support locking mechanism 4
1 and 2 17 inner piston rod of hydraulic support cylinder move out, expand gas in accumulator 18, thus drive floating day
Vehicle 2 is moved upwards relative to derrick frame 1, and passive 8 rocker arm body 6 of steel wire rope that compensates extends to the outside, and is tensioned fast line 61, and compensation is big
Hook and drill string rise the moving displacement of generation due to floating drilling platform or drill ship.When floating drilling platform or drill ship are with wave
When wave declines, hook load can be caused to reduce, drive hydraulic support cylinder 1 and hydraulic support cylinder in hydraulic pressure support locking mechanism 4
2 17 inner piston rods inwardly move so that gas is compressed in accumulator 18, thus drives the opposite derrick frame 1 of floating overhead traveling crane 2
It moves downward, passive 8 rocker arm body 6 of steel wire rope that compensates loosens drilling well fast line 61, compensate tourist bus 7 and hook and brill to contract
Column declines the moving displacement generated due to floating drilling platform or drill ship.
Meanwhile crown-block heave compensator can also be achieved following functions：1. driller personnel can be put down by adjusting positioned at drilling well
Pressure-regulating valve on platform spar deck changes the pressure of compensating hydraulic cylinder, can realize the quick work(for adjusting Bottom Hole Bit Weight In A
Energy；2. when carrying out normal drilling operability, if by compensating hydraulic cylinder inner piston rod in hydraulic pressure support locking mechanism 4 to floating overhead traveling crane
2 thrust is adjusted in the range of slightly below hook load, and floating overhead traveling crane 2 is enable to be moved down along guider 5, can
Realize automatic drilling depth function, when floating overhead traveling crane 2 runs down to minimum point, the driller personnel on spar deck can pass through
Loosen the fast line 61 on well drilling hoist, tourist bus 7 and hook is made to continue to move down, realize automatic bit feed function；3. pass through hydraulic pressure
The hydraulic locking exchange rate set in support locking mechanism 4 when carrying out round trip, can lock floating overhead traveling crane 2 in derrick frame
1 top of frame prevents floating overhead traveling crane 2 to ensure effective benefit of the overhead traveling crane heave compensation apparatus to drill string heave movement from being moved with drill string
It repays and is smoothed out with drillng operation.
Claims (8)
1. a kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation, it is characterised in that：Including derrick frame,
Gear-rack drive compensation mechanism, hydraulic pressure support locking mechanism, guider, the passive compensation steel wire for having passive compensation function
Rope rocker arm body, floating overhead traveling crane and tourist bus, the gear-rack drive compensation mechanism are fixedly mounted on the top of derrick frame, lead
It being mounted in derrick frame to device, floating overhead traveling crane is slidably mounted on guider, and can be floated up and down along guider,
The hydraulic pressure support locking mechanism is mounted on the bottom of derrick frame, and is connect with floating overhead traveling crane, and the hydraulic pressure support locks machine
Structure can lock floating overhead traveling crane at an arbitrary position, and the passive compensation steel wire rope rocker arm body is mounted on the bottom two of derrick frame
Side, the passive steel wire rope rocker arm body that compensates are connect with floating overhead traveling crane, and the tourist bus is lifted on by steel wire rope on floating overhead traveling crane, trip
Hook is installed on vehicle；
The hydraulic pressure support locking mechanism includes hydraulic support cylinder one, hydraulic support cylinder two and can store hydraulic support cylinder one
With the accumulator of the hydraulic energy of hydraulic support cylinder two, hydraulic support cylinder one and hydraulic support cylinder two are fixed on the bottom of derrick frame
The telescopic rod of portion, hydraulic support cylinder one and hydraulic support cylinder two is respectively symmetrically supported on the lower section of floating overhead traveling crane, accumulator difference
It is connect with hydraulic support cylinder one and hydraulic support cylinder two；
The rodless cavity of the hydraulic support cylinder one and hydraulic support cylinder two is connect with the first interface of two-way cover-plate type inserted valve one,
The second interface of two-way cover-plate type inserted valve one is connect with the first interface of two-way cover-plate type inserted valve two, the inserting of two-way cover-plate type
The second interface of valve two is connect with accumulator；The rod chamber and 3-position 4-way of the hydraulic support cylinder one and hydraulic support cylinder are electro-hydraulic
The first interface connection of proportional reversing valve, the second interface of 3-position 4-way electro-hydraulic proportion reversing valve respectively with unidirectional volume adjustable hydraulic pump
Outlet connected with the first interface of direct acting type overflow valve, the third interface of 3-position 4-way electro-hydraulic proportion reversing valve and counterbalance valve
First interface connects, entrance, the second interface of direct acting type overflow valve and the second interface of counterbalance valve of unidirectional volume adjustable hydraulic pump
It is connect respectively with hydraulic oil container, unidirectional volume adjustable hydraulic pump is by motor drive.
2. a kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation according to claim 1, feature
It is：The gear-rack drive compensation mechanism includes location and installation platform, spur rack track one, spur rack track two, sliding tooth
Wheel one and drive gear two, the location and installation platform are fixed on the top of derrick frame, benefit are symmetrically installed on location and installation platform
Motor one and small electromotor two are repaid, output terminal and the drive gear one of small electromotor one are sequentially connected, the output of small electromotor two
End is sequentially connected with drive gear two, and spur rack track one and spur rack track two are placed in the one of location and installation platform back-to-back
Side, spur rack track one are engaged with drive gear one, and spur rack track two is engaged with drive gear two, spur rack track one and straight
The lower end of rack-track two is fixed on the upper end of floating overhead traveling crane.
3. a kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation according to claim 1, feature
It is：Pacify on main line between the hydraulic support cylinder one and the rodless cavity of hydraulic support cylinder and two-way cover-plate type inserted valve one
Equipped with hydraulic support cylinder rodless cavity pressure gauge, the rod chamber and 3-position 4-way of the hydraulic support cylinder one and hydraulic support cylinder are electro-hydraulic
Hydraulic support cylinder rod chamber pressure gauge, the two-way cover-plate type are installed on the main line between the first interface of proportional reversing valve
Bi-bit bi-pass Hydraulic guide control reversal valve is installed, two-way cover-plate type is inserted between inserted valve one and two-way cover-plate type inserted valve two
The side of dress valve two is equipped with two-position two-way electromagnetic directional valve.
4. a kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation according to claim 1, feature
It is：The hydraulic pressure support locking mechanism further includes hydraulic locking circuit, the hydraulic locking circuit include filter, two two
Logical pilot operated directional control valve, hydraulic pilot valve, single-acting pneumatic operation valve and gas tank, the both ends of single-acting pneumatic operation valve respectively with gas
Tank connects, and the first control terminal of two-position two-way hydraulic control reversal valve is connect with accumulator, filter and two-position two-way hydraulic control reversal valve
First interface connect with filter, the second interface of two-position two-way hydraulic control reversal valve respectively with the first control of hydraulic pilot valve
End is connected with hydraulic oil container, the second control terminal of hydraulic pilot valve respectively with the second control terminal of two-position two-way hydraulic control reversal valve and
Third interface connects, and the first control terminal of two-position two-way hydraulic control reversal valve is connect with the first entrance of single-acting pneumatic operation valve,
Second entrance of the filter also with single-acting pneumatic operation valve is connect, the first outlet and hydraulic oil container of single-acting pneumatic operation valve
Connection, is equipped with check valve on the pipeline between two-position two-way hydraulic control reversal valve and hydraulic pilot valve, the entrance side of check valve with
The second outlet connection of single-acting pneumatic operation valve, outlet side are connect with the first control terminal of single-acting pneumatic operation valve.
5. a kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation according to claim 1, feature
It is：The guider includes the linear guide, directive wheel and axial guidance supporting rack, and the linear guide is vertically installed at derrick frame
It on frame, is fixed between the linear guide and derrick frame by axial guidance supporting rack, directive wheel is mounted on floating overhead traveling crane, is oriented to
Wheel coordinates with the linear guide.
6. a kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation according to claim 5, feature
It is：The linear guide includes the linear guide one and the linear guide two mounted on derrick frame side, mounted on derrick frame
The linear guide three of frame opposite side and the linear guide four, directive wheel include with one corresponding directive wheel one of the linear guide, with straight line
Two corresponding directive wheel two of guide rail, with three corresponding directive wheel three of the linear guide and with four corresponding directive wheel of the linear guide
Four, directive wheel one is mounted on by guide wheel shaft one on floating overhead traveling crane, and directive wheel two is mounted on floating day by guide wheel shaft two
Che Shang, directive wheel three are mounted on by guide wheel shaft three on floating overhead traveling crane, and directive wheel four is mounted on by guide wheel shaft four and floated
On overhead traveling crane.
7. a kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation according to claim 1, feature
It is：The passive compensation steel wire rope rocker arm body includes rocking arm shoring one, rocking arm shoring two, rocking arm shoring three, shakes
Arm shoring four, rocking arm directive wheel one, rocking arm directive wheel two, hydraulic cylinder one and hydraulic cylinder two, the lower end hinge of rocking arm shoring one
It connects on fast line directive wheel, quick directive wheel is mounted on the side of derrick frame, and upper end is hingedly equipped with rocking arm directive wheel
One, the one end of rocking arm directive wheel one also with rocking arm shoring two is hinged, and the other end and the floating overhead traveling crane of rocking arm shoring two are hinged
It is connected, the one end of rocking arm directive wheel one also with hydraulic cylinder one is hinged, and the other end of hydraulic cylinder one is hinged on derrick frame, rocking arm
The lower end of shoring four is hingedly mounted on dead line directive wheel, and dead line directive wheel is mounted on the opposite side of derrick frame, upper end hinge
Connect and rocking arm directive wheel two be installed, the one end of rocking arm directive wheel two also with rocking arm shoring three is hinged, rocking arm shoring three it is another
One end is hinged and connected with floating overhead traveling crane, and the one end of rocking arm directive wheel two also with hydraulic cylinder two is hinged, the other end hinge of hydraulic cylinder two
Be connected on derrick frame, fast line around after fast line directive wheel and rocking arm directive wheel one, into the idler wheel of floating overhead traveling crane and tourist bus into
Row winding, after dead line is around dead line directive wheel and rocking arm directive wheel two, the idler wheel into floating overhead traveling crane and tourist bus is wound.
8. a kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation according to claim 7, feature
It is：The side of the hydraulic cylinder one is additionally provided with accumulator one, and accumulator one is connect with the rodless cavity of hydraulic cylinder one, the liquid
The side of cylinder pressure two is additionally provided with accumulator two, and accumulator two is connect with the rodless cavity of hydraulic cylinder two.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610595540.8A CN106089127B (en) | 2016-07-27 | 2016-07-27 | A kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610595540.8A CN106089127B (en) | 2016-07-27 | 2016-07-27 | A kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106089127A CN106089127A (en) | 2016-11-09 |
| CN106089127B true CN106089127B (en) | 2018-06-15 |
Family
ID=57450617
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610595540.8A Expired - Fee Related CN106089127B (en) | 2016-07-27 | 2016-07-27 | A kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106089127B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106801585A (en) * | 2017-01-10 | 2017-06-06 | 中国石油大学(华东) | A kind of floating drilling platform semi-active type crown-block heave compensator |
| EP3363989B1 (en) * | 2017-02-16 | 2019-03-27 | National Oilwell Varco Norway AS | Drilling unit comprising an electric heave-compensation system |
| CN106638623B (en) * | 2017-02-20 | 2018-07-27 | 长江勘测规划设计研究有限责任公司 | Load-compensating support device and method |
| CN107060662B (en) * | 2017-02-27 | 2019-07-12 | 中建钢构有限公司 | Half active compensation apparatus control system |
| CN107060663B (en) * | 2017-03-29 | 2019-01-25 | 西南石油大学 | A kind of heave compensator and its scheme based on hydraulic machinery |
| CN108533192A (en) * | 2018-04-27 | 2018-09-14 | 山东科技大学 | Ore-raising pipe heave compensation system and the method that ore-raising pipe is compensated |
| 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 |
| CN111236863A (en) * | 2020-01-10 | 2020-06-05 | 山东科技大学 | Deep sea mining ore lifting pipe heave compensation system and compensation method |
| CN111561299B (en) * | 2020-05-26 | 2022-05-17 | 中海石油(中国)有限公司 | Liquid drainage and gas production operation system and operation method suitable for engineering ship |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3653635A (en) * | 1969-11-17 | 1972-04-04 | Joe Stine Inc | Wave motion compensating apparatus for use with floating hoisting systems |
| US3760889A (en) * | 1969-01-07 | 1973-09-25 | A Nelson | Apparatus and method to modify and service a subaqueous strata drilling 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 |
| CN204283252U (en) * | 2014-11-27 | 2015-04-22 | 宝鸡石油机械有限责任公司 | A kind of semi-active type drilling platform crown-block heave compensator |
| CN204402396U (en) * | 2014-12-30 | 2015-06-17 | 西南石油大学 | A kind of Novel crown block heave compensator driving mechanism |
-
2016
- 2016-07-27 CN CN201610595540.8A patent/CN106089127B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3760889A (en) * | 1969-01-07 | 1973-09-25 | A Nelson | Apparatus and method to modify and service a subaqueous strata drilling system |
| US3653635A (en) * | 1969-11-17 | 1972-04-04 | Joe Stine Inc | Wave motion compensating apparatus for use with floating hoisting systems |
| 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 |
| CN204283252U (en) * | 2014-11-27 | 2015-04-22 | 宝鸡石油机械有限责任公司 | A kind of semi-active type drilling platform crown-block heave compensator |
| CN204402396U (en) * | 2014-12-30 | 2015-06-17 | 西南石油大学 | A kind of Novel crown block heave compensator driving mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106089127A (en) | 2016-11-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106089127B (en) | A kind of semi-active type overhead traveling crane heave compensation system for deepwater drilling operation | |
| CN106241633B (en) | A kind of towing winch hydraulic control system peculiar to vessel and transmission device and control method | |
| CN101746680B (en) | Device for rapidly collecting and releasing boats | |
| CN204283252U (en) | A kind of semi-active type drilling platform crown-block heave compensator | |
| CN105417381A (en) | Direct pump control type electro-hydraulic heaving compensation device | |
| CN101798909A (en) | Drilling column heave compensation device of marine floating type drilling platform | |
| CN202466553U (en) | Full-level balanced vertical ship elevator suitable for ship reception chamber to go in and go out of water | |
| CN109098675A (en) | A kind of deep compensation device of passive type deep-sea liter for ocean platform drilling well | |
| CN208327199U (en) | A kind of movable type active compensation device | |
| CN106286428A (en) | A kind of semi-active type heave compensator hydraulic control system | |
| CN102535424B (en) | Full flat type balance vertical ship lift adaptive to ship reception chamber outlet-inlet water | |
| CN101654145A (en) | Ocean floating type drilling platform crown-block heave compensator | |
| EP3155206B1 (en) | Winches and hoisting systems with heave compensation | |
| CN106640780B (en) | A kind of positive displacement heave compensation hydraulic system and heave compensation Lift-on/Lift-off System | |
| CN108408611A (en) | A kind of movable type active compensation device and its working method | |
| CN205605141U (en) | Rack and pinion formula drilling string heave compensator | |
| CN108716371A (en) | The reverse experimental rig of compensation function and its control method of drill string heave compensation system | |
| CN108425315A (en) | A kind of position compensation extension type is gone on board trestle | |
| CN107060662A (en) | Half active compensation apparatus control system | |
| CN102410010B (en) | Rotary drilling rig and main winding floating system thereof | |
| CN103241668A (en) | Device and method for installing deep sea submarine storage tank | |
| CN209133001U (en) | A kind of experimental provision of active/passive compensation of undulation | |
| CN103979416A (en) | Wave compensation execution device for crane ship A support | |
| CN103614995A (en) | Full-hydraulic-lifting type ship lifter | |
| CN2488894Y (en) | Passive wave compensator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20180615 Termination date: 20200727 |