WO2008071089A1 - Unité de pompage de double puits de pétrole par entraînement par traction - Google Patents

Unité de pompage de double puits de pétrole par entraînement par traction Download PDF

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Publication number
WO2008071089A1
WO2008071089A1 PCT/CN2007/003591 CN2007003591W WO2008071089A1 WO 2008071089 A1 WO2008071089 A1 WO 2008071089A1 CN 2007003591 W CN2007003591 W CN 2007003591W WO 2008071089 A1 WO2008071089 A1 WO 2008071089A1
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WO
WIPO (PCT)
Prior art keywords
weight
bracket
wheel
traction
suspension
Prior art date
Application number
PCT/CN2007/003591
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English (en)
Chinese (zh)
Inventor
Gangdu Cui
Original Assignee
Gangdu Cui
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Gangdu Cui filed Critical Gangdu Cui
Publication of WO2008071089A1 publication Critical patent/WO2008071089A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B47/00—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps
    • F04B47/02—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps the driving mechanisms being situated at ground level
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells

Definitions

  • the invention relates to a double fine oil machine, in particular to a traction double oil machine.
  • the total strength of the Guoqi pumping unit is: super large load, long stroke, low stroke; precise balance; automation, intelligent; energy saving, high adaptability; no long beam stroke; large size.
  • pumping unit wells account for 82.1% of the total number of wells. Due to the low system efficiency of pumping unit wells, a large number, or even more than 70%, of energy is lost during the transfer process. Therefore, at home and abroad. All are committed to the development of energy-saving pumping units.
  • Low-profile pumping unit front-mounted pumping unit, front-mounted gas-balanced pumping unit, long-stroke pumping without beam, wheeled pumping unit and out-of-phase pumping unit.
  • China National Petroleum Corporation averages about 20-30% of the electricity cost per ton of oil cost, and the electricity cost of local oilfield production costs is larger.
  • the electricity consumption of pumping units accounts for a considerable proportion of electricity expenditure. All of them are developing low-cost, high-efficiency, maximizing the potential for saving electricity, saving energy from the mechanical system and electrical control system of the pumping unit, which can bring considerable economic benefits and improve the green GDP index. .
  • crank balance beam pumping unit is an old product that has been consistently produced for decades. It is the standard design of the American Petroleum Institute.
  • the biggest advantages of this machine are:) Simple structure and convenient installation; ( ⁇ ) Beam-type polished rod shifting movement The speed curve is in accordance with the liquid twitch theory.
  • the biggest disadvantages of this machine are:) Low efficiency and large reactive loss; ( ⁇ ) High failure rate and large downtime loss; (iii) Stroke balance must be coordinated by the crane to make the female high.
  • crank-balanced beam pumping units In China's industry, almost no update has been made from theory to practice, all of which are crank-balanced beam pumping units.
  • the long stroke and low stroke pumping method has many significant advantages, such as improving pump efficiency and extending the life of the rod string.
  • the method of switching reluctance motor and linear motor uses the method of reversing the pumping unit. This inevitably promotes the pumping unit to long strokes Direction development. Friction wheel pumping units, linear motor pumping units and electric drum pumping units have emerged in recent years. After 4 years, Dagang Drilling and Drilling Institute developed a linear motor-driven pumping unit, but the ait ship is high, and the price of a u ⁇ stroke pumping unit is about one million. The world's highest-stroke American 30-meter stroke pumping unit is more expensive.
  • Oilfield non-self-injection wells use pumping units to raise the pump's up and down reciprocating motion for pumping, according to international standards.
  • GB11649-49 stipulates that the current structural forms of pumping units mainly include: conventional type beam type, gas balance beam type, front type beam type and special type beam type.
  • the main disadvantages are: heavy weight, low efficiency, and transmission efficiency of only 0. 125- 0. 54.
  • Chinese patent CN1375618A discloses a "rope double-well interactive self-balancing pumping unit", which uses a steering motor to drive the reel with a rope and a guide wheel to separate the front and rear balance weights of the front beams of the two well beams. Connected to realize the reciprocating motion of the two oil thin oil rods up and down.
  • the main disadvantages are: two oil wells still need two sets of hoes, beams, balance weights, etc.
  • the added connectors, overload protection devices, commutators, limiters and other mechanisms make the equipment costly, and the gears of the reducer are meshed.
  • Xiao staff is expensive! Low mechanical efficiency and frequent maintenance.
  • Chinese patent CN2356162Y discloses an "ultra-low-cost double-well pumping unit", which uses a hydraulic pump, a hydraulic cylinder, a fuel tank, a commutator, and is connected to a sucker rod through a top fan-shaped body.
  • the hydraulic cylinder piston rod is composed of a hydraulic pump and a motor. Power is provided, and the reversing valve controls the hydraulic cylinder to move to the new position.
  • the hydraulic cylinder piston rod and commutator need to be replaced frequently under continuous working.
  • Fuel tank, hydraulic pump, hydraulic cylinder piston rod rubber seals are prone to aging and oil leakage under open air operation, so that? ? The pressure is unstable.
  • the top segment is composed of four large-sized, concentrically fixed, equal-phase arc segments, which are time-consuming and labor-intensive to process and install.
  • the rare earth permanent magnet synchronous gearless traction machine Compared with the traditional gear reduction technology, the rare earth permanent magnet synchronous gearless traction machine has high efficiency, simple structure, small volume and no pollution. It is suitable for low-speed and large-torque transmission. It is a modern mechanical equipment. The main development direction of the special system. In 1996, Finnish KONE took the lead in applying rare earth permanent magnet synchronous gearless traction machines to elevators, which is still the leading technology in the elevator industry.
  • Chinese patent 200510046026. 0, CN1664305A discloses an "electronic-electrical-mechanical integrated traction pumping unit", which eliminates the reducer, the efficiency can reach more than 90%, and the stroke and stroke are steplessly adjustable.
  • Synchronous gearless traction machine precise and stable operation, direct drag, low speed and large torque, the same volumetric efficiency, and other unique features, such as power-free parking autism and other unique features, the risk is continuous working all-weather open-air operation, from North to South climate change ambient temperature
  • the moisture dew point on the ocean has no effect on the functional stability and longevity of the electronic components of the control system.
  • the shortcomings are: Can not be used for double well pumping. A counterweight that matches one end of the sucker rod is required, that is, when the weight of the pumping unit is 18 tons, the other end also requires a balance weight of about 18 tons. Only one end works, and the other end loses power.
  • the telescopic mechanism of the head consists of the guide rail, handle and screw on the upper part of the rack.
  • the end of the load carrying body is the cantilever end.
  • the machining precision is high.
  • the guide screw needs to be lubricated and lubricated, and the manufacturing and safety are high.
  • a traction double oil machine comprising a bracket 16 and a transmission mechanism disposed on the bracket 16, wherein the transmission mechanism comprises: a traction drive small wheel 11 wound around the traction drive small wheel 11
  • the III drive guide wheel 303 of the drive wire rope 12 between the ropes 901 transmits the IV drive guide wheel 304 of the drive wire rope 12 between the VI drive guide wheel 306 and the II pulley suspension 902; the traction drive wheel 11 passes
  • the coaxially disposed tracing I transmission large wheel 7 is coupled to the towline I wheel 801 of the dragline machine 8 via a flexible conveyor belt 14.
  • the above-mentioned bracket 16 may be provided with a weight guiding wheel 4, and the weight guiding wheel 4 includes a weight guiding wheel 403 disposed on the bracket 16, and a weight-receiving wheel 403 is wound around the weight-receiving wheel 403.
  • One end of the household weight wire rope 13 is connected to the weight 10, and the other end of the weight wire rope 13 is connected to the I pulley suspension 901 via the I weight guide wheel 401 or to the II through the II weight guide wheel 402.
  • the bracket 16 described above may be provided with a weight guiding wheel 4, and the weight guiding wheel 4 includes an Ilffi heavy guiding wheel 403 and an IV weight guiding wheel 404 which are disposed at two ends of the bracket 16;
  • the I-weight wire rope 1301 is wound around the guide wheel 403. One end of the I-weight wire rope 1301 is connected to the I-weight 1001, and the other end of the I-weight wire rope 1301 is connected to the I pulley hanging rope via the I-weight guide wheel 401.
  • the IV weighting guide wheel 404 is wound around the II weight wire rope 1302. One end of the II weight wire rope 1302 is connected with the II weight 1002, and the other end of the II weight wire rope 1302 is II weighted.
  • Guide wheel 402 is coupled to II pulley suspension 902.
  • the above-mentioned I pulley suspension 901 is connected to the I sucker rod 1501, and the I pulley suspension 901 is wound with a transmission wire rope 12; the transmission wire rope wound around the I pulley suspension 901
  • One end of the driving wire 12 is fixed on the bracket 16, and the other end of the driving wire rope 12 drives the guiding wheel 303 and the V driving guiding wheel 305.
  • the bracket 16 is fixed to the bracket 16 on.
  • One end of the transmission wire rope 12 wound around the I pulley suspension 901 is fixed to the bracket 16 by the I rope tightener 101, and the other end of the transmission wire rope 12 is fixed to the bracket 16 .
  • the above-mentioned I pulley suspension 901 is connected to the I sucker rod 1501, and the I pulley suspension 901 is wound around the transmission wire rope 12; 1
  • One end of the transmission wire rope 12 on the pulley suspension 901 is fixed On the bracket 16, the other end of the transmission wire 12 first passes around the III drive guide wheel 303 and the V drive guide wheel 305, then bypasses the traction drive wheel 11 and then passes through the VI drive guide wheel 306, and then ⁇ !
  • the VI weight guide wheel 406 fixed to the II weight 1002 is fixed to the bracket 16.
  • One end of the transmission wire 12 wound on the I pulley suspension 901 is fixed to the bracket 16 by the I weight tightening rope 103, and the other end of the transmission wire 12 is fixed by the II weight tightener 104. On the bracket 16.
  • the I pulley suspension 901 and the II pulley suspension 902 described above are pulley suspensions composed of a single pulley or a pulley block; the pulley suspension consisting of the pulley block is 4: 1 or 6: 1 or 8: 1 pulley block consisting of a pulley suspension.
  • the diameter ratio of the traction sheave 801 of the hoisting machine 8 to the traction drive wheel 7 is 1: 2 to 4.
  • the I rope tightener 101 described above is fixed to the bracket 16 by the I suspension bracket 601, which is perpendicular to the I sucker rod 1501; the II rope tightener 102 passes the II suspension bracket 602. Fixed to the bracket 16, the II suspension bracket 602 is perpendicular to the II sucker rod 1502.
  • the portion of the bracket 16 above the well, the I suspension bracket 601 and the II suspension bracket 602 constitute a rotary head 2, and the rotary head 2 is coupled to the other portions of the bracket 16 by at least two axle pins 5. Fixed, the at least two pins 5 are disposed on two sides of the rotating machine head 2.
  • a permanent magnet synchronous motor directly drives the double #3 ⁇ 4 oil. Structure optimization, safety and convenience.
  • the equipment has high reliability, long trouble-free operation time and low maintenance cost. It has a well-repairing function in addition to the pumping function.
  • Long stroke, low stroke, stroke can be adjusted freely.
  • the long stroke makes the pump full of high coefficient and the hydraulic impact is small; the low stroke makes the downhole equipment wear less and the operation cost is low.
  • Extra long stroke, according to the actual application stroke can be much larger than 30 meters, in addition to the pumping function, it also has a workover function.
  • the design has a weight compensation device. When a well needs to be repaired, the rotating machine head can deviate from the upper part of the well to give up the maintenance space; while the other oil well and the weight compensation are balanced and can work normally. 4. Wire rope drive. The long-life heavy load and the wire rope transmit power, and the elastic buffering action can reduce the commutation shock and make the sucker rod column run smoothly.
  • Permanent magnet synchronous motor is directly driven. Due to the direct drive of the permanent magnet synchronous motor and the weight balance of the two wells, the low power motor can be selected without the reducer, the energy saving is 40-60%, the weight of the equipment is reduced by 1/3, the daily maintenance cost is reduced by about 1/2, and the capital cost is reduced. 1/2.
  • Fig. 1 is a schematic view showing the structure of a first embodiment of the present invention.
  • Fig. 2 is a schematic view showing the structure of a second embodiment of the present invention.
  • 1_suspension rope tightener 10 I I tight rope, 102- II tight rope, 103-I weight tight rope, 104- ⁇ weight tight rope; 2-rotary machine Head; 3-drive guide wheel; 30-I drive guide wheel, 302- ⁇ drive guide wheel, 303-III drive guide wheel, 304-IV drive guide wheel, 305-V drive guide wheel, 306-VI drive guide wheel; 4-weight guide wheel; 401-I counterweight guide wheel, 402-11 counterweight guide wheel, 403-11 top heavy guide wheel, 404-IV counterweight guide wheel; 405-V counterweight guide wheel, 406- VI counterweight guide wheel; 5-axis pin; 6-suspension bracket; 601-I suspension bracket, 602-II suspension bracket; 7 - traction drive large wheel; 8- traction machine; 80 pulley traction wheel 9-pulley suspension rope; 90-I pulley suspension, 902-II pulley suspension; 10-weight; 100-I weight, 1002-II weight; 1 traction drive wheel; - Transmission wire rope;
  • the pulley suspension device 9 of the present invention includes an I pulley suspension 901 and an II pulley suspension 902, which may be a pulley suspension constructed of a pulley set of 4:1 or 6:1 or 8:1.
  • 1 is a schematic structural view of an embodiment of the present invention with a transmission ratio of 12:1.
  • the I drive guide wheel 301 is a drive guide wheel of the pulley block of the I pulley suspension 901
  • the II drive guide wheel 302 is a II pulley suspension.
  • the I pulley suspension 901 is connected to the I sucker rod 1501 of the one side well, and the transmission rope 12 is wound around the I pulley suspension 901.
  • the suspension rope tightener 1 of the present invention includes an I tight rope cutter 101, an II tight rope cutter 102, a I weight tight rope cutter 103, a II weight tight rope cutter 104, and the like.
  • the suspension bracket 6 includes an I suspension bracket 601 and an II suspension bracket 602 and the like.
  • the sucker rod 15 includes an I sucker rod 1501, a II sucker rod 1502, and the like.
  • the I pulley suspension 901 is coupled to the I sucker rod 1501.
  • One end of the drive wire 12 wound around the I pulley suspension 901 is fixed to the bracket 16, and the other end is wound around the III drive guide wheel 303 and the V drive guide wheel 305, then the traction drive wheel 11 is bypassed, and then wound around The VI-driven guide wheels 306 and IV drive the guide wheels 304, and then bypass the II pulley suspension 902 connected to the other side well II sucker rod 1502, and then fixed to the bracket 16.
  • it is attached to the II tightener 102 on the bracket 16.
  • the II suspension bracket 602 of the fixed II tightener 102 is perpendicular to the II sucker rod 1502.
  • the traction sheave of the traction machine 8 The 801 conveyor belt 14 is connected to the traction drive large wheel 7, and the traction drive small wheel 11 and the traction drive large wheel 7 are arranged coaxially.
  • the flexible conveyor belt 14 may specifically be a steel cord, a V-belt or a flat belt.
  • the traction machine 8—3 ⁇ 4 uses a permanent magnet synchronous traction machine.
  • the diameter ratio of the traction sheave 801 of the hoisting machine 8 to the traction drive wheel 7 is generally 1: 2 to 4.
  • the diameter of the traction sheave 801 of the hoisting machine 8 is similar to the diameter of the traction drive small wheel 11 and the drive guide wheel 3.
  • the lifting gravity is equal, that is, when the load gravity of the two oil wells is in an equilibrium state, the weight 10 is not required to be compensated.
  • the counterweight 10 can be placed on the side of the gravity to compensate, so that the dynamic load of the oil wells of the two wells is balanced by gravity.
  • the bracket 16 is provided with a counterweight guide wheel 4, and the counterweight guide wheel 4 includes 11 top weight guide wheels 403 and IV weight guide wheels 404 which are disposed at two ends of the bracket 16.
  • the IISS weight guide wheel 403 is wound with an I weight wire rope 1301. One end of the I weight wire rope 1301 is connected to the I weight 1001; the other end of the I weight wire rope 1301 is connected to the I pulley suspension 901 via the I weight guide wheel 401.
  • the IV weight guide wheel 404 is wound with a second weight wire rope 1302. II One end of the weight wire rope 1302 is connected to the II weight 1002, and the other end of the II weight wire rope 1302 is connected to the II pulley suspension 902 via the II weight guide wheel 402.
  • the I pulley suspension 901 and the II pulley suspension 902 are pulley suspensions composed of a single pulley.
  • the suspension ratio of a single pulley suspension is 2 : 1.
  • the I pulley suspension 901 is coupled to the I sucker rod 1501.
  • One end of the drive wire 12 wound around the I pulley suspension 901 is fixed to the bracket 16, and the other end of the winding II drives the guide wheel 303 and the V drive guide wheel 305, and then bypasses the traction drive wheel 11, and then rewinds
  • the VI drives the guide wheel 306, it is fixed to the bracket 16 by bypassing the VI weight guide wheel 406 fixed to the II weight 1002.
  • One end of the drive wire 12 wound around the I pulley suspension 901 is fixed to the bracket 16 by the I weight tightener 103, and the other end is fixed to the bracket 16 by the II weight tightener 104.
  • the portion of the bracket 16 above the well, the I suspension bracket 601 and the II suspension bracket 602 constitute a rotating head 2, and the rotating head 2 ® 1 at least two pins 5 are fixed to the other portions of the bracket 16, at least two axle pins 5 is set on the two sides of the rotating machine head 2.
  • the other side of the well can work normally alone.
  • the I pulley suspension 901 is removed, the transmission wire 12 of the I clamp 101 is removed, and the I sucker 1501 and the I pulley suspension 901 are disconnected, and the I weight wire rope 1301
  • One end of the connection to the I pulley suspension 901 is disconnected.
  • One end of the transmission wire rope 12 is fixed to the II suspension rope bracket 602 through the II clamp 102; the other end of the transmission wire rope 12 3 ⁇ 4M I weight tight rope cutter 103 is directly fixed to the I suspension support 601, and passes through IV in the middle.
  • the drive guide wheel 304, the VI drive guide wheel 306, the traction drive small wheel 11, and the V drive guide wheel 305 are connected to the I counterweight 1001.
  • the weight of the I counterweight 1001 should be equal to the working load of the well B.
  • the I counterweight 1001 and the II counterweight 1002 on both sides of the present invention can be adjusted according to the working load of the two wells, and the driving torque of the traction machine 8 should be balanced.
  • the invention is applicable to two straight wells, one inclined well, two inclined wells, and one well to repair another well, the single well boot work, the double well work at the same time, and the double well work load are not equal.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Geology (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Lift-Guide Devices, And Elevator Ropes And Cables (AREA)
  • Load-Engaging Elements For Cranes (AREA)

Abstract

L'invention concerne une unité de pompage de double puits de pétrole par entraînement par traction qui comprend un cadre (16) et des mécanismes de transmission montés sur le cadre. Les mécanismes de transmission comprennent une roue d'entraînement de traction plus petite (11), un câble métallique (12) enroulé sur la roue d'entraînement de traction plus petite, une roue directrice V (305), une roue directrice VI (306), une roue directrice III (303) et une roue directrice IV (304).La roue directrice V (305) et la roue directrice VI (306) sont situées respectivement sur chaque côté de la roue d'entraînement de traction plus petite (11) et transmettent le câble métallique sur les deux côtés à la fois de la roue d'entraînement de traction plus petite. La roue directrice III (303) transmet le câble métallique entre la roue directrice V (305) et un dispositif de suspension de tête de balancier I (901). La roue directrice IV (304) transmet le câble métallique entre la roue directrice VI (306) et un dispositif de suspension de tête de balancier II (902). Une roue d'entraînement de traction plus grosse (7) est coaxiale par rapport à la roue d'entraînement de traction plus petite (11) qui est connectée à une roue de traction (801) d'un tracteur (8) par le biais d'une courroie de ligne flexible (14). Le dispositif comporte de nombreux avantages, tels que des coûts de fabrications plus faibles, une économie d'énergie, une course plus longue, etc.
PCT/CN2007/003591 2006-12-15 2007-12-14 Unité de pompage de double puits de pétrole par entraînement par traction WO2008071089A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CNU2006201363747U CN201021617Y (zh) 2006-12-15 2006-12-15 稀土永磁无齿轮同步曳引双井抽油机
CN200620136374.7 2006-12-15

Publications (1)

Publication Number Publication Date
WO2008071089A1 true WO2008071089A1 (fr) 2008-06-19

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CN (2) CN201021617Y (fr)
WO (1) WO2008071089A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101899964A (zh) * 2010-06-25 2010-12-01 河南南阳市油田机械制造有限公司 长冲程双井塔式抽油机
CN102052062A (zh) * 2010-07-26 2011-05-11 马丙辉 一种节能型塔架式抽油装置
CN102155191A (zh) * 2011-05-11 2011-08-17 陕西金福源投资有限公司 一种分体式双井抽油机
CN102182427A (zh) * 2011-03-29 2011-09-14 山东创新石油技术有限公司 数控测距刹车滚筒抽油机
CN102493789A (zh) * 2011-12-23 2012-06-13 田园 一种下置卷轮式抽油机
CN108843279A (zh) * 2018-08-03 2018-11-20 西安石油大学 一种齿轮式双井抽油机
CN117090523A (zh) * 2023-10-20 2023-11-21 大庆市华禹石油机械制造有限公司 一种碳纤维连续抽油杆自动化作业车

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CN108150131B (zh) * 2018-02-12 2023-10-20 中国地质大学（北京） 一种用于位置定位的压力波发生器及固井装置
CN111101904A (zh) * 2020-01-19 2020-05-05 胡勇 绞车式无游梁抽油机双机双井互动平衡装置
CN113638716B (zh) * 2021-06-26 2024-06-04 中电天威（锦州）石油技术装备有限公司 井下配重全密封抽油机

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CN2721910Y (zh) * 2004-09-02 2005-08-31 赵华春 卷筒式长冲程抽油机
CN2816349Y (zh) * 2005-08-19 2006-09-13 吴昱 一机多井往复式抽油机
CN200989195Y (zh) * 2006-12-28 2007-12-12 蔡光宇 无齿轮传动节能抽油机

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2425585Y (zh) * 2000-05-11 2001-04-04 盛建国 一种电动摇床
RU2205978C2 (ru) * 2001-07-09 2003-06-10 Богатырев Павел Иванович Станок-качалка с цепной передачей для двух скважин
CN1432717A (zh) * 2002-01-07 2003-07-30 李红岩 液压滚筒式双井抽油机
CN1386955A (zh) * 2002-07-10 2002-12-25 李征 丛式井互动自平衡机电一体化智能抽油机采油技术
CN2575294Y (zh) * 2002-07-10 2003-09-24 李征 丛式井“t”形下置式互动自平衡机电一体化智能抽油机
CN2637718Y (zh) * 2002-07-10 2004-09-01 李征 丛式井“t”形上置式互动自平衡机电一体化智能抽油机
CN2721910Y (zh) * 2004-09-02 2005-08-31 赵华春 卷筒式长冲程抽油机
CN2816349Y (zh) * 2005-08-19 2006-09-13 吴昱 一机多井往复式抽油机
CN200989195Y (zh) * 2006-12-28 2007-12-12 蔡光宇 无齿轮传动节能抽油机

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101899964A (zh) * 2010-06-25 2010-12-01 河南南阳市油田机械制造有限公司 长冲程双井塔式抽油机
CN102052062A (zh) * 2010-07-26 2011-05-11 马丙辉 一种节能型塔架式抽油装置
CN102182427A (zh) * 2011-03-29 2011-09-14 山东创新石油技术有限公司 数控测距刹车滚筒抽油机
CN102155191A (zh) * 2011-05-11 2011-08-17 陕西金福源投资有限公司 一种分体式双井抽油机
CN102493789A (zh) * 2011-12-23 2012-06-13 田园 一种下置卷轮式抽油机
CN108843279A (zh) * 2018-08-03 2018-11-20 西安石油大学 一种齿轮式双井抽油机
CN108843279B (zh) * 2018-08-03 2024-01-26 西安石油大学 一种齿轮式双井抽油机
CN117090523A (zh) * 2023-10-20 2023-11-21 大庆市华禹石油机械制造有限公司 一种碳纤维连续抽油杆自动化作业车
CN117090523B (zh) * 2023-10-20 2024-01-12 大庆市华禹石油机械制造有限公司 一种碳纤维连续抽油杆自动化作业车

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