EP2438264A2 - Pompe aspirante hydraulique pour champ pétrolifère - Google Patents

Pompe aspirante hydraulique pour champ pétrolifère

Info

Publication number
EP2438264A2
EP2438264A2 EP10721094A EP10721094A EP2438264A2 EP 2438264 A2 EP2438264 A2 EP 2438264A2 EP 10721094 A EP10721094 A EP 10721094A EP 10721094 A EP10721094 A EP 10721094A EP 2438264 A2 EP2438264 A2 EP 2438264A2
Authority
EP
European Patent Office
Prior art keywords
pumping unit
hydraulic
hydraulic cylinder
oil well
vertically orientated
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.)
Withdrawn
Application number
EP10721094A
Other languages
German (de)
English (en)
Inventor
Gerry L. Lorimer
Denis Blaquiere
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
National Oilwell Varco LP
Original Assignee
National Oilwell Varco LP
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 National Oilwell Varco LP filed Critical National Oilwell Varco LP
Publication of EP2438264A2 publication Critical patent/EP2438264A2/fr
Withdrawn legal-status Critical Current

Links

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
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
    • E21B43/121—Lifting well fluids
    • E21B43/126—Adaptations of down-hole pump systems powered by drives outside the borehole, e.g. by a rotary or oscillating drive
    • 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
    • F04B47/04—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps the driving mechanisms being situated at ground level the driving means incorporating fluid means

Definitions

  • This invention relates to lift pumps suitable for producing hydrocarbons and other liquids from the earth.
  • this invention is drawn to a very long stroke hydraulically operated lift pump using a combination of single and double acting hydraulic cylinders that are actuated with an energy efficient hydraulic fluid accumulator system.
  • Hydraulically operated Oilfield lift pumping units are well known and have been used in the industry for many years. Typically, these units mimic the non-hydraulic mechanical 'walking beam' design similar to the pumping unit 10 illustrated in Figure 1. These conventional units are more commonly driven directly by electric motors through gear boxes, but many are also hydraulically driven as shown for example in U.S. Patents 4,201,115; 4,198,820; 3,405,605. These hydraulic units are typically configured similarly to the motor driven units, but have hydraulic cylinders fitted in place of the linkages and gearing of the mechanical system.
  • Limitations of the 'walking beam' design include limited stroke variability, the need for a rotating counter weight of roughly the same weight as the sucker rods and other devices suspended in the borehole, and a stroke limited by the length of the 'walking beam' and/or the height above the ground of the mast upon which the beam is mounted.
  • Described herein is a new type of hydraulically driven oilfield lift pump unit which features a simplified hydraulic system.
  • This system comprises a hydraulic power section and a wellhead mounted lifting section.
  • the hydraulic power section is typically, but not limited to, a flow controlled, pressure compensated hydraulic pump system that can readily be optimally sized to meet the desired lifting speed and weight parameters of the lift section and an electrically controlled 4-way type variable displacement control valve, or other types of suitable control valves.
  • These types of 'power units' are well known and are in common use in the industry.
  • the lifting section comprises a plurality (typically a pair) of single acting hydraulic cylinders, and a plurality (typically a pair) of double acting hydraulic cylinders.
  • the cylinders are mechanically mounted on common end plates such that they all must extend and retract simultaneously.
  • the cap ends of the double acting cylinders are 'closed-coupled' to one or more hydraulic accumulators so that in normal operation all the flow into and out of the cap ends of the cylinders is into or out of the hydraulic accumulators.
  • the accumulators are pre-charged with gas at a pressure such that when the cylinders are fully extended and the accumulators nearly depleted of hydraulic fluid, the double acting cylinders are nonetheless able to statically hold a high percentage, of the lifting load. This may also effectively balance the pump motor' s load between the upstroke and the downstroke cycles, and may permit use of a prime mover motor or engine to run under a relatively constant load (compared to conventional pumps) regardless of whether in both the upstroke mode and the downstroke mode.
  • Typical load variations may be in the range of 70% to 130% of the average load, but as will be described, these variations may be reduced even more than this, if desired.
  • the load balancing effect of the accumulators allows the use of a motor with a significantly less horsepower rating (or capacity) than the prior art units.
  • the lower peak power consumption may allow for a lower effective electric rate, as in many locations the electric rate is based on, or at least affected, by the peak load instead of the average load.
  • the load on the down stroke may typically be about two-thirds of the load on the up stroke. This difference is caused by a transfer of fluid column weight onto the down hole lifting valves.
  • the pressurized fluid from the hydraulic power unit is applied only to the 'rod' ends of the double acting hydraulic cylinders.
  • the combination of the weight of the load and this hydraulic pressure on the top end of the cylinder causes all the cylinders to retract. This in turn forces the hydraulic fluid on the cap ends of the double acting cylinders back into the accumulators - and therefore filling them.
  • the relative horsepower required for each of the 'extend' and 'retract' cycles may be changed and/or more nearly equalized by adjusting the pre-charge pressure of the accumulators to account for variations in the average lifting load, permitting usage of the smallest possible engine or motor for the hydraulics. Furthermore, this may also help reduce large load fluctuations, reducing stress on the system. However, because in some instances the actual loading may vary over time, an intermediate pre-charge pressure may be chosen.
  • Figure 1 is side view of a typical 'walking beam' oilfield lift pump of the prior art.
  • Figure 2 is an overall perspective view of the oilfield lift pump of the present invention.
  • Figure 3 is a perspective view of just the mast section of lifting section of the oilfield lift pump of the present invention.
  • Figure 4 is a hydraulic schematic diagram of the hydraulic power unit of the present invention.
  • Figure 5 is a portion of the hydraulic diagram of the lifting portion of the lifting portion of the oilfield pump of the present invention showing the hydraulic flow arrangement for the "up stroke" portion of the pumping cycle.
  • Figure 6 is a portion of the hydraulic diagram of the lifting portion of the oilfield pump of the present invention showing the hydraulic flow arrangement for the "down stroke" portion of the pumping cycle.
  • the hydraulically driven surface oil well pumping unit 12 of the present invention comprises a base portion 14, including a hydraulic power unit (not shown) and a mast portion 16 comprising a pair of single acting hydraulic cylinders 18 and a pair of double acting hydraulic cylinders 20.
  • Figure 2 shows the hydraulic cylinders 18, 20 of the hydraulically driven oil field pumping unit 12 fully extended
  • figure 3 shows the mast portion 16 separated from the rest of the oilfield pumping unit 12 of figure 2 with the hydraulic cylinders 18, 20 fully retracted.
  • the new oil well pumping unit 12 of the present invention is useful in reciprocating a "load" in the wellbore; particularly a load which is substantially higher as the load is being raised, than when the load is being lowered - as is typically the case when pumping oil in an oil well.
  • the cap ends 22a and 22b of the hydraulic cylinders 18, 20 are shown mounted to a common rigid base plate 24.
  • the rod ends 26a 26b of the hydraulic cylinders 18, 20 are shown mounted to a common rigid end plate 28.
  • the hydraulic cylinders 18, 20 will typically oriented with their cap ends 22a and 22b secured to the base plate 24, but it is also possible to mount them such that the cap ends 22a and 22b are mounted to the end plate 28, and use tension members to 'suspend' the load.
  • the lifting mechanism is then suspended in a framework (not shown) using an intermediate support structure. It is preferred, however, to mount the cylinders 18, 20 with the cap ends 22a and 22b secured to the base plate 24 as shown, as this allows the forces from the 'load' to pass in compression directly from the cap ends 22a and 22b to the base plate 24.
  • a frame with sufficient strength - or a separate base - may be needed to support the mast.
  • the hydraulic schematic 40 of the hydraulic power unit (shown generally as 30) of the hydraulically driven oil field pumping unit 12 is shown in figure 4 and is typical for pressure compensated power units.
  • the hydraulic power unit 30 typically comprises but is not limited to one or more pumps 42, 44 powered by one or more engine 46 (or alternatively, motors). Hydraulic oil contained in a reservoir 48 is pumped into a control valve 50 which may be a proportional-volume controlled pressure balanced valve as illustrated, or may be a solenoid valve that is essentially open or closed.
  • the valve 50 is configured to reversibly provide pressurized hydraulic fluid to either of line 52a or 52b with the other line being the return.
  • the operation of this valve 50 controls the extension and retraction of the hydraulic cylinders 18, 20.
  • This hydraulic configuration may be comprised of, but not limited to a closed loop, solenoid operated hydraulic pumping unit.
  • the mast 16 lifting section comprises a pair of single acting hydraulic cylinders 18, and a pair of double acting hydraulic cylinders 20. As shown in Figs. 5 and 6, the cylinders 18, 20 are mechanically mounted on common end plates 24, 28 such that they all must extend and retract simultaneously.
  • the cap ends 54, 56 of the double acting cylinders 20 are 'closed-coupled' to one or more hydraulic accumulators 58, 60 so that in normal operation all the flow into and out of the cap ends 54, 56 of the cylinders flows into or out of the hydraulic accumulators 58, 60.
  • the accumulators 58, 60 are pre-charged with an inert gas to a pressure depending upon the weight of the load such that when the double acting cylinders 20 are fully extended they are able to hold a high percentage of the lifting load.
  • pressurized fluid from the hydraulic power unit 30 is applied only to the cap ends 66, 68 of the single acting cylinders 18 through line 52a, causing all four of the cylinders 18, 20 to extend.
  • the pair of single acting hydraulic cylinders 18 can only be powered in the extended direction.
  • the pre-charge pressures of the accumulators 58, 60 are 'tuned' so that in conjunction with the weight of the load, the horsepower to raise and lower the load is substantially the same throughout the entire extend/retract cycle.
  • This allows optimal sizing of the engine(s) 46 (or motors) driving the hydraulic pumps 42, 44; and may improve the overall useful lifetime of the oil well pumping unit 12, by reducing the accompanying cyclic fatigue.
  • the lowering load may be set within a range of about 60% to 95% of the raising load. In other selected embodiments it may be preferable to limit the lowering load to no lower than about 70% of the raising load. In still other selected embodiments, it may be desirable to maintain the lowering load in a range of 75% to 85% of the raising load.
  • this ratio of lowering load to raising load may be further adjusted by varying the pre-charge pressures among the accumulators 58, 60. In this embodiment three or four or more than four accumulations with varying pre-charge pressures may be useful.
  • the ratio of lowering load to raising load may be adjusted by varying the distribution of swept volumes among the accumulators. In still other selected embodiments the ratio of lowering load to raising load may be adjusted by using different volume capacities among the accumulators.
  • accumulators 58, 60 may be arranged with both different pre-charge pressures, and with different volume capacities, which may 'tuning' even more precise.

Abstract

La présente invention concerne une unité de pompe aspirante pour champ pétrolifère à entraînement hydraulique orientée verticalement présentant un système hydraulique simplifié. Le système utilise une paire de vérins hydrauliques de levage à simple effet en tandem avec une paire de vérins hydrauliques de levage à double effet réagissant mutuellement avec des accumulateurs hydrauliques pour former un système hydraulique robuste efficace sur le plan énergétique conçu avec un nombre réduit de composants.
EP10721094A 2009-06-02 2010-06-01 Pompe aspirante hydraulique pour champ pétrolifère Withdrawn EP2438264A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US18326409P 2009-06-02 2009-06-02
PCT/US2010/036807 WO2010141405A2 (fr) 2009-06-02 2010-06-01 Pompe aspirante hydraulique pour champ pétrolifère

Publications (1)

Publication Number Publication Date
EP2438264A2 true EP2438264A2 (fr) 2012-04-11

Family

ID=43218903

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10721094A Withdrawn EP2438264A2 (fr) 2009-06-02 2010-06-01 Pompe aspirante hydraulique pour champ pétrolifère

Country Status (6)

Country Link
US (1) US20100300679A1 (fr)
EP (1) EP2438264A2 (fr)
AU (1) AU2010256864B2 (fr)
CA (1) CA2763162C (fr)
MX (1) MX2011012819A (fr)
WO (1) WO2010141405A2 (fr)

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US20120224977A1 (en) * 2011-03-04 2012-09-06 Sotz Leonard C Method and Apparatus for Fluid Pumping
US9291036B2 (en) * 2011-06-06 2016-03-22 Reel Power Licensing Corp. Method for increasing subsea accumulator volume
CN103291247B (zh) * 2012-02-27 2015-12-09 姜成华 立式液压抽油机
US9822777B2 (en) 2014-04-07 2017-11-21 i2r Solutions USA LLC Hydraulic pumping assembly, system and method
US9828979B2 (en) * 2014-07-08 2017-11-28 Halliburton Energy Services, Inc. Accumulator over hydraulic pump double-acting cylinder for artificial lift operations
WO2016007131A1 (fr) * 2014-07-08 2016-01-14 Halliburton Energy Services, Inc. Cylindre à trois chambre à contrepoids pour accumulateur pour des opérations de levage artificiel
US9631464B2 (en) 2014-07-08 2017-04-25 Halliburton Energy Services, Inc. Pneumatic-on-top counterbalanced three-chamber cylinder for artificial lift operations
US10047739B2 (en) 2014-12-31 2018-08-14 Zedi Canada Inc. Pump jack system and method
CN108843275B (zh) * 2018-06-12 2020-11-20 刘长年 第四代高效长冲程长寿命智能式机电液抽油机
CN108798605A (zh) * 2018-08-23 2018-11-13 穆牧之 智能化控制数字液压抽油机
RU187964U1 (ru) * 2018-12-13 2019-03-26 Общество с ограниченной ответственностью "Пермская нефтяная инжиниринговая компания" Устройство установки на скважине гидравлического цилиндра привода штангового скважинного насоса
RU188939U1 (ru) * 2019-02-08 2019-04-30 Общество с ограниченной ответственностью "Пермская нефтяная инжиниринговая компания" Гидравлический привод штангового скважинного насоса
CA3080552A1 (fr) 2020-05-01 2021-11-01 Richard K. Young Ascenseurs a tige polie et methodes d`utilisation connexes
RU2754247C1 (ru) * 2020-12-18 2021-08-31 Публичное акционерное общество «Татнефть» имени В.Д. Шашина Способ добычи высоковязкой нефти на малых глубинах и устройство для его осуществления
CN115126418B (zh) * 2022-08-30 2022-12-09 东营市昆昆科技有限责任公司 一种基于一口井位钻出多个井眼的钻井方法

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US3405605A (en) * 1966-06-14 1968-10-15 Milburn M. Ross Hydraulic pump jack means
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Also Published As

Publication number Publication date
CA2763162C (fr) 2014-08-12
CA2763162A1 (fr) 2010-12-09
AU2010256864B2 (en) 2015-01-22
MX2011012819A (es) 2011-12-16
US20100300679A1 (en) 2010-12-02
AU2010256864A1 (en) 2011-12-08
WO2010141405A3 (fr) 2011-03-31
WO2010141405A2 (fr) 2010-12-09
WO2010141405A4 (fr) 2011-06-09

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