EP1642029B1 - Pump for tail production of oil - Google Patents
Pump for tail production of oil Download PDFInfo
- Publication number
- EP1642029B1 EP1642029B1 EP04748779A EP04748779A EP1642029B1 EP 1642029 B1 EP1642029 B1 EP 1642029B1 EP 04748779 A EP04748779 A EP 04748779A EP 04748779 A EP04748779 A EP 04748779A EP 1642029 B1 EP1642029 B1 EP 1642029B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- piston
- cylinder
- section
- interlock
- 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 - Lifetime
Links
- 238000004519 manufacturing process Methods 0.000 title description 17
- 239000003129 oil well Substances 0.000 claims abstract description 6
- 230000000712 assembly Effects 0.000 claims description 18
- 238000000429 assembly Methods 0.000 claims description 18
- 238000005086 pumping Methods 0.000 claims description 6
- 239000010720 hydraulic oil Substances 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 43
- 239000012530 fluid Substances 0.000 description 12
- 238000000034 method Methods 0.000 description 4
- 230000002706 hydrostatic effect Effects 0.000 description 2
- 230000006698 induction Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000009491 slugging Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 230000003245 working effect Effects 0.000 description 1
Images
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
- F04B47/06—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps having motor-pump units situated at great depth
-
- 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
- F04B47/06—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps having motor-pump units situated at great depth
- F04B47/08—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps having motor-pump units situated at great depth the motors being actuated by fluid
Definitions
- the pump cylinder section 8, the interlock section 10 and the drive cylinder section 12 all are provided with a centrally provided oil outlet channel 18, which is best shown in figures 6 and 7. Oil, which is sucked in through the mouth piece 4 by means of the piston pump 2, is guided into the oil outlet channel 18 by means of prior art control valves arranged in the pump valve section 6. The oil outlet channel 18 also continues through the control valve section 14 and the hydraulic drive unit 16 and exits in the well's production string 20. Thus, recovered oil may be pumped onwards to the surface.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
Description
- This invention concerns a piston pump for tail production of oil from oil wells having low pressure.
- During an initial production period, which may last several years, a typical oil well in the North Sea, for example, will be self-producing. During this production period, the pressure in the oil in the subsurface structure is sufficiently large for the oil to flow up through the well production string by itself. As the oil production period continues, the pressure in the oil-containing structure decreases until the well is not self-producing any more. At this production stage, however, large amounts of oil still remain in the structure, often as much as 80% of the original amount of oil.
- According to prior art, mainly three methods of enhanced recovery are used to recover more of the remaining amount of oil in the structure.
- One method comprises so-called gas lift, in which gas is injected down via an annulus of the well, after which it mixes with the oil flowing in from the surrounding oil structure and onwards up through the production string of the well. The admixing of gas lowers the specific gravity and hence the hydrostatic pressure of the emanating fluid column. Thereby, the reduced pressure in the oil structure may still be sufficiently large to overcome the flow friction and the hydrostatic bottom pressure of the fluid column, thus allowing further amounts of oil to be produced from the oil structure during a new time period.
- Another method consists in injecting water down into an injection well and into said oil-containing structure, thereby increasing or maintaining the pressure in the oil structure. Further amounts of oils are thus forced out of the structure and produced to the surface via one or more cooperating production wells.
- A third method consists in installing a pump downhole in a production string of an oil well. Oil is then pumped up to the surface. Such a pump must be designed for use under extreme conditions. As such, consideration must be given to the fact that the production string is of a relatively small diameter, and that the pump therefore must be formed having dimensions that fit within the production string. Consideration must also be given to the fact that the pump potentially must overcome lifting heights of several thousand meters, and that the pump therefore must be able to operate at very large pressures.
- Such prior art pumps usually consist of a large number of axial pumps provided on a long, common shaft, and they have a driving motor provided either below or above the pump itself, insofar as this pump may be 10-20 meters long. The total pump pressure delivered by such a pump results from a successive pressure build-up in several pressure stages, each pressure stage corresponding to one of said axial pumps along said common shaft. A big problem of these pumps is that they are very sensitive to gas in the oil flow, and they do not operate satisfactorily even when a relatively small gas concentration is present in the outflow. This problem is enhanced when the pressure in said oil structure is reduced in response to oil production, whereby increasingly larger amounts of gas are liberated from the oil, thereby increasing the gas concentration in the oil flow.
- Onshore, for example in the USA, it is well known to use piston pumps in relatively shallow wells. Generally, the pump piston downhole in the well is run up and down by means of a wire attached to an eccentric shaft connected to the piston. Each time the piston is moved upwards, such a pump will deliver a pulsating oil flow. This pump solution is acceptable in order to overcome a relatively small oil column pressure at the bottom of a relatively shallow well.
- Generally, a piston pump is suitable for providing a large pump pressure in a single pressure stage, which implies that this pressure is provided in the course of one stroke of piston travel within an associated cylinder. Under certain conditions, a piston pump may also handle a relatively large amount of gas in the liquid that it is pumping. For this reason, a piston pump is very much suitable for recovering oil from deep wells having a low pressure in the subsurface structure. Piston-based pumps are disclosed in, for example, publications NO
305667 ;US 3.625.288 ;US 4.268.277 ;US 4.536.137 andGB 2.100.362 - In deep wells, such as those in the North Sea and other offshore regions, a production string oftentimes may be many kilometres long, and the lifting height of the oil column may be 3000-5000 meters. When employing a prior art piston pump to pump out oil in a slugging and pulsating manner from a well, a large proportion of the pump pressure, and hence the pump power, will be used to accelerate the oil column for each pump pulse. Using this pumping principle in a deep well therefore will require an unrealistically large pump pressure and -power to accelerate such a long oil column in a pulsating manner towards the surface. Allowing the oil column overlying the pump to flow having a relatively continuous and even flow out of the well may reduce this disadvantage, thereby avoiding or greatly reducing the pulsating course of acceleration.
- The object of the invention is to avoid or reduce said disadvantages of prior art piston pumps. More specifically, the object is to provide a piston pump suitable for mounting downhole in a production string in a deep well; which is of a design capable of delivering a relatively even pump flow of oil to the surface; and which can tolerate relatively large gas amounts in its inflow induction region, the pump simultaneously having very small or no vibration-producing and free mass forces.
- The object of the invention is achieved as disclosed in the following description and in the subsequent claims.
- The invention concerns a piston pump for pumping out oil from a subsurface structure via an oil well. The piston pump is connected to necessary control- and driving means for controlling and driving the pump, respectively, when placed in the well. The characterising features of the invention is that the pump has four piston assemblies that, by means of a fixed interlock between two opposite piston assemblies, and by means of a cog wheel interlock between said two piston assemblies and the other two opposite piston assemblies, are provided as two oncoming piston assembly pairs.
- With the exception of a short interval when reciprocating, this piston pump design provides the advantageous operation of one piston pump assembly pair always being in a pumping stroke mode, whereas the other pair always is in a concurrent induction stroke mode. The piston pump according to the invention therefore provides the advantage of a virtually continuous and uninterrupted pumping action when operational in a well.
- In a preferred embodiment of the invention, the piston pump includes, in sequence: a pump cylinder section; an interlock section; and a drive cylinder section. All of these sections are provided with a centrally provided oil outlet channel through which recovered oil may flow onwards and out of the well. Internally, the pump cylinder section, the interlock section and the drive cylinder section are provided with four axial cylinder assemblies distributed peripherally about the oil outlet channel. Each cylinder assembly comprises: a pump cylinder in the pump cylinder section; an inwardly open movement region in the interlock section; and a drive cylinder in the drive cylinder section. Internally, each cylinder assembly is provided with an axially movable piston assembly, each piston assembly comprising: a pump piston in the pump cylinder; a piston rod in the inwardly open movement region; and a drive piston in the drive cylinder. Two diametrically opposite piston rods are mechanically connected by means of a linkage that is provided between them. Each of said two mechanically connected piston rods is movably connected to one of the other two piston rods via a cog wheel provided therebetween, both of said cog wheels being supported in the interlock section. Each piston rod is also provided with a pitch rack portion facing towards said cog wheel and having a length corresponding to at least the stroke length of said pistons.
- Said four axial cylinder assemblies distributed peripherally about the oil outlet channel may also be distributed at an equal angle distance between each another. Moreover, said inwardly open movement region in the interlock section may be comprised of a partially cylinder-shaped groove (as viewed in cross section). Furthermore, said mechanical linkage in the interlock section may be comprised of a tie-plate.
- An example of an embodiment of the present piston pump will be described hereinafter whilst referring to the accompanying figures, in which:
- Figure 1 shows a lower portion of a production string of a well, within which portion a piston pump according to the invention is provided;
- Figure 2 shows a schematic, radial cross section through the piston pump, also indicating a section line III-III through the pump;
- Figure 3 shows an eccentric axial section through the piston pump as viewed along section line III-III of figure 2, figure 3 also showing a section line VI-VI through the pump;
- Figure 4 shows another schematic, radial cross section through the piston pump, also indicating a section line IV-IV through the pump;
- Figure 5 shows a central axial section through the piston pump as viewed along section line IV-IV of figure 4, figure 5 also showing a section line VII-VII through the pump;
- Figure 6 shows an enlarged and further detailed radial cross section through the piston pump as viewed along section line VI-VI of figure 3; and
- Figure 7 shows an enlarged and further detailed radial cross section through the piston pump as viewed along section line VII-VII of figure 5.
- Figure 1 shows a
piston pump 2 according to the invention. Viewed from below and up, thepump 2 comprises: asuction mouth piece 4; apump valve section 6; apump cylinder section 8; aninterlock section 10; adrive cylinder section 12; acontrol valve section 14; and ahydraulic drive unit 16 on top. A pump (not shown) in thedrive unit 16 pumps hydraulic fluid in a loop between a bistable 3-5 port valve (not shown) in thecontrol valve section 14, and thedrive unit 16. In thecontrol valve section 14, the hydraulic fluid is guided further through suitable hydraulic fluid channels (not shown) onwards torespective drive cylinders drive cylinder section 12. Supply of driving power and control signals to thedrive unit 16, as well as conveyance and control of the hydraulic fluid flow paths within thepump 2, constitutes prior art and will not be described any further hereinafter. - The
pump cylinder section 8, theinterlock section 10 and thedrive cylinder section 12 all are provided with a centrally providedoil outlet channel 18, which is best shown in figures 6 and 7. Oil, which is sucked in through themouth piece 4 by means of thepiston pump 2, is guided into theoil outlet channel 18 by means of prior art control valves arranged in thepump valve section 6. Theoil outlet channel 18 also continues through thecontrol valve section 14 and thehydraulic drive unit 16 and exits in the well'sproduction string 20. Thus, recovered oil may be pumped onwards to the surface. - Four cylinder assemblies A, B, C and D are provided radially outside of the
oil outlet channel 18 and surround thechannel 18. As shown for example in figures 3 and 5, internally thepump cylinder section 8 is provided with fouraxial pump cylinders interlock section 10 is provided with four axial and partially cylinder-shapedgrooves drive cylinder section 12 is provided with said fouraxial drive cylinders pump cylinder groove corresponding drive cylinder - Internally in each cylinder assembly A, B, C, D, an axially movable piston assembly a, b, c and d is provided, comprising, in sequence: a pump piston in one end; a piston rod; and a drive piston in the other end, cf. figures 3 and 5. Thus, four piston assemblies a, b, c, d are provided, one of which in each cylinder assembly A, B, C, D. The piston assemblies a, b, c, d comprise: four
respective pump pistons respective piston rods respective drive pistons pump cylinders drive cylinder interlock section 10, is provided with ashoulder 34 against which the rear side of each piston can stop when operational and reciprocating back and forth in its cylinder. - Two diametrically
opposite piston rods plate 36 provided between them. Thereby, piston assembly b will move uniformly together with piston assembly d throughout their reciprocating axial movements. The tie-plate 36 is best shown in figures 5 and 7. Two other diametricallyopposite piston rods 30a and 30c are not connected via such a mechanical linkage. - However,
piston rod 30a andpiston rod 30d, and piston rod 30c andpiston rod 30b, respectively, are movably connected with each other via acog wheel 38 and cog wheel 38', respectively, provided between them, both of saidcog wheels 38, 38' being supported in theinterlock section 10. In this connection, eachpiston rod pitch rack portion 40 facing in towards therespective cog wheel 38, 38' in order to engage and cooperate with thecog wheel 38, 38'. Thepitch rack portion 40 has a length corresponding to at least the stroke length of each piston. This tooth interaction is best shown in figures 3 and 6. When the two mechanically connected piston assemblies b and d move uniformly together in one axial direction, thecog wheels 38, 38' will ensure that a coordinated and uniform movement of the other two piston assemblies a and c in the opposite axial direction is provided. Thereby, two drive pistons as well as two pump pistons will always be active simultaneously during operation of thepiston pump 2. Moreover, this is a direct result of the four piston assemblies a, b, c, d of thepump 2 being provided as two oncoming piston assembly pairs b, d and a, c. This piston pump design also results in a complete balancing of the mass forces in thepump 2. Simultaneously, the emanating oil flow becomes relatively constant and even, even when a pressure surge arises when the pistons change their direction of movement due to their axial reciprocation. - Said pressure surge is used to switch said bistable 3-5 port valve in order to supply pump-driving hydraulic fluid alternately to a first
drive cylinder pair drive cylinder pair 26a, 26c. In relation to this, the opening of said hydraulic fluid channel in eachdrive cylinder drive piston respective drive cylinder drive piston piston pump 2.
Claims (5)
- A piston pump (2) for pumping out oil from a subsurface structure via an oil well, said pump (2) being connected to control- and driving means for controlling and driving the pump (2), respectively, when placed in the well,
characterised in that the pump (2) has
four piston assemblies (a, b, c, d) that, by means of a fixed interlock (36) between two opposite piston assemblies (b, d), and by means of a cog wheel interlock (38, 38') between said two piston assemblies (b, d) and the other two opposite piston assemblies (a, c), are provided as two oncoming piston assembly pairs (b, d and a, c). - The piston pump (2) according to claim 1,
characterised in that the piston pump includes, in sequence:- a pump cylinder section (8);- an interlock section (10); and- a drive cylinder section (12);
all of which are provided with a centrally provided oil outlet channel (18);- wherein the pump cylinder section (8), the interlock section (10) and the drive cylinder section (12) internally are provided with four axial cylinder assemblies (A, B, C, D) distributed peripherally about the oil outlet channel (18), each cylinder assembly (A, B, C, D) comprising:- a pump cylinder (22a, 22b, 22c, 22d) in the pump cylinder section (8);- an inwardly open movement region (24a, 24b, 24c, 24d) in the interlock section (10); and- a drive cylinder (26a, 26b, 26c, 26d) in the drive cylinder section (12);- wherein each cylinder assembly (A, B, C, D) internally is provided with an axially movable piston assembly (a, b, c, d), each piston assembly comprising:- a pump piston (28a, 28b, 28c and 28d) in the pump cylinder (8);- a piston rod (30a, 30b, 30c and 30d) in the inwardly open movement region (24a, 24b, 24c, 24d); and- a drive piston (32a, 32b, 32c and 32d) in the drive cylinder (26a, 26b, 26c, 26d);- wherein two diametrically opposite piston rods (30b, 30d) are mechanically connected by means of a linkage (36) provided between them;- wherein each of said two mechanically connected piston rods (30b, 30d) is movably connected to one of the other two piston rods (30a, 30c) via a cog wheel (38, 38') provided therebetween, both of said cog wheels (38, 38') being supported in the interlock section (10); and- wherein each piston rod (30a, 30b, 30c and 30d) is provided with a pitch rack portion (40) facing towards said cog wheel (38, 38') and having a length corresponding to at least the stroke length of said pistons. - The piston pump (2) according to claim 2,
characterised in that said four axial cylinder assemblies (A, B, C, D) distributed peripherally about the oil outlet channel (18) are distributed at an equal angle distance between each another. - The piston pump (2) according to claim 2 or 3,
characterised in that said inwardly open movement region in the interlock section (10) is comprised of a partially cylinder-shaped grooves (24a, 24b, 24c, 24d). - The piston pump (2) according to claim 2, 3 or 4,
characterised in that said mechanical linkage in the interlock section (10) is comprised of a tie-plate (36).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NO20033044A NO319468B1 (en) | 2003-07-03 | 2003-07-03 | Pump for tail production of oil |
PCT/NO2004/000203 WO2005017299A2 (en) | 2003-07-03 | 2004-07-02 | Pump for tail production of oil |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1642029A2 EP1642029A2 (en) | 2006-04-05 |
EP1642029B1 true EP1642029B1 (en) | 2007-08-22 |
Family
ID=27800759
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04748779A Expired - Lifetime EP1642029B1 (en) | 2003-07-03 | 2004-07-02 | Pump for tail production of oil |
Country Status (9)
Country | Link |
---|---|
US (1) | US20060153720A1 (en) |
EP (1) | EP1642029B1 (en) |
AT (1) | ATE371110T1 (en) |
AU (1) | AU2004265529B2 (en) |
BR (1) | BRPI0412293A (en) |
CA (1) | CA2532224A1 (en) |
DE (1) | DE602004008470T2 (en) |
NO (1) | NO319468B1 (en) |
WO (1) | WO2005017299A2 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101892817A (en) * | 2010-06-29 | 2010-11-24 | 中国石油化工股份有限公司胜利油田分公司采油工艺研究院 | Gas balance assembly of gas balance oil pumping unit |
CN103437984B (en) * | 2013-08-14 | 2016-04-13 | 陕西延长石油(集团)有限责任公司研究院 | Multi-functional solid plunger tubing pump |
CN104632592B (en) * | 2014-12-04 | 2017-01-04 | 丁新建 | Ultralong-stroke oil extraction pump |
CN107075924B (en) * | 2014-12-30 | 2021-03-12 | 哈里伯顿能源服务公司 | Constant velocity joint apparatus, systems, and methods |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US722240A (en) * | 1902-09-18 | 1903-03-10 | Sandusky Foundry And Machine Company | Multiple-cylinder pump. |
US1420052A (en) * | 1919-08-18 | 1922-06-20 | Cleo H Brand | Pump |
US1711582A (en) * | 1926-04-14 | 1929-05-07 | Ralph R Bostic | Deep-well pump |
US2534436A (en) * | 1948-05-13 | 1950-12-19 | Gibson Glenn Dean | Double-action pump |
US3625288A (en) * | 1970-04-14 | 1971-12-07 | George K Roeder | Method and apparatus for venting gas through a downhole pump assembly |
US4084923A (en) * | 1975-11-07 | 1978-04-18 | Roeder George K | Double-acting, downhole pump assembly |
US4097199A (en) * | 1976-10-14 | 1978-06-27 | Arrow Machine, Inc. | Double acting rack and gear-driven piston pump |
US4268277A (en) * | 1978-09-14 | 1981-05-19 | Combustion Engineering, Inc. | Multi-tubular centrifugal liquid separator and method of separation |
US4536137A (en) * | 1982-09-30 | 1985-08-20 | Trw Inc. | Submergible pumping apparatus |
US5290159A (en) * | 1993-03-04 | 1994-03-01 | Exxon Production Research Company | Downhole pump of constant differential hydraulic pressure |
-
2003
- 2003-07-03 NO NO20033044A patent/NO319468B1/en unknown
-
2004
- 2004-07-02 EP EP04748779A patent/EP1642029B1/en not_active Expired - Lifetime
- 2004-07-02 US US10/562,780 patent/US20060153720A1/en not_active Abandoned
- 2004-07-02 CA CA002532224A patent/CA2532224A1/en not_active Abandoned
- 2004-07-02 WO PCT/NO2004/000203 patent/WO2005017299A2/en active IP Right Grant
- 2004-07-02 BR BRPI0412293-3A patent/BRPI0412293A/en not_active IP Right Cessation
- 2004-07-02 DE DE602004008470T patent/DE602004008470T2/en not_active Expired - Fee Related
- 2004-07-02 AU AU2004265529A patent/AU2004265529B2/en not_active Ceased
- 2004-07-02 AT AT04748779T patent/ATE371110T1/en not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
NO20033044D0 (en) | 2003-07-03 |
CA2532224A1 (en) | 2005-02-24 |
AU2004265529B2 (en) | 2008-06-12 |
US20060153720A1 (en) | 2006-07-13 |
NO20033044L (en) | 2005-01-04 |
WO2005017299A2 (en) | 2005-02-24 |
ATE371110T1 (en) | 2007-09-15 |
WO2005017299A3 (en) | 2005-05-06 |
DE602004008470D1 (en) | 2007-10-04 |
AU2004265529A1 (en) | 2005-02-24 |
DE602004008470T2 (en) | 2008-04-30 |
BRPI0412293A (en) | 2006-09-05 |
EP1642029A2 (en) | 2006-04-05 |
NO319468B1 (en) | 2005-08-15 |
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