EP0143684B1 - Mehrstufiger Serienverdichter - Google Patents

Mehrstufiger Serienverdichter Download PDF

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Publication number
EP0143684B1
EP0143684B1 EP84402052A EP84402052A EP0143684B1 EP 0143684 B1 EP0143684 B1 EP 0143684B1 EP 84402052 A EP84402052 A EP 84402052A EP 84402052 A EP84402052 A EP 84402052A EP 0143684 B1 EP0143684 B1 EP 0143684B1
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EP
European Patent Office
Prior art keywords
gas
compressor
compressors
machine
machine according
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
Application number
EP84402052A
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English (en)
French (fr)
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EP0143684A1 (de
Inventor
Pierre Ferdinand Jean Sagnes
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.)
Bertin Technologies SAS
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Bertin et Cie SA
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Publication date
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Publication of EP0143684B1 publication Critical patent/EP0143684B1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows

Definitions

  • the invention relates to a gas compression machine, comprising several compression stages in series constituted by compressors of different types.
  • This known method of exploiting an oil field is characterized, among other things, by a reduction in the gas flow rate required as the oil is extracted.
  • This reduction in flow rate constitutes a major drawback when the compressed gas is supplied by a set of centrifugal compressors and piston or screw compressors, since there is then a risk of reaching the "pumping limit", below which occur very large pressure oscillations and vibrations that can destroy the compressors.
  • piston or screw compressors which are associated with centrifugal compressors have their own drawbacks: significant cost and size, frequent and expensive maintenance, noise and vibrations in operation. They must also be connected by gear boxes to the drive means of the centrifugal compressors.
  • Document FR-2 149 128 discloses a gas compression machine comprising an inlet stage formed by a liquid ring pump and, downstream, a side channel compressor with one or more stages. This downstream compressor is calculated solely on the basis of the flow rate and compresses the gas regardless of its suction pressure. This type of machine is therefore not capable of solving the aforementioned problems.
  • Document DE-1 403 579 also discloses a turbo-blower with two compression stages and two fluid circuits, comprising a centrifugal stage associated with a side channel stage arranged radially around the centrifugal stage, for produce a relatively large gas flow at a relatively high pressure.
  • This turbo-blower also does not solve the problems posed above.
  • the invention particularly relates to a gas compression machine, operating in the above range of flow rates and pressures, which has none of the drawbacks of the prior art.
  • the invention also relates to a machine of this type which is compact, unitary and compact.
  • the invention also relates to a machine of this type having a reliability much higher than that of equivalent machines of the prior art.
  • a gas compression machine intended in particular to deliver a gas flow rate of the order of a few hundred to a few tens of thousands of cubic meters per hour at a pressure of between 150 and 300 bars approximately.
  • a gas compression machine comprising several compression stages in series constituted by compressors of different types, characterized in that the different compressors comprise rotors having roughly equal diameters and which are mounted on the same drive shaft inside a single casing, an inlet stage consisting of at least one centrifugal compressor, while an outlet stage consisting of at least one peripheral compressor.
  • peripheral compressors which can also be called in the pulse compressors, recovery compressors, friction compressors
  • centrifugal compressors makes it possible to obtain a particularly compact machine in which the rotors of the peripheral compressors have diameters at roughly equal to those of the rotors of centrifugal compressors and can be driven at the same speed of rotation as the rotors of centrifugal compressors, which allows all the compressors to be mounted on the same rotary drive shaft.
  • peripheral compressors do not exhibit any pumping phenomenon when the fluid flow rate decreases and make it possible to obtain manometric powers several times higher than those of centrifugal compressors.
  • the machine according to the invention can therefore comprise centrifugal compressors which are less loaded than those of equivalent prior machines and which are less sensitive to the pumping phenomenon, without having to multiply their number.
  • centrifugal compressors and the peripheral compressors mounted on the same drive shaft can be housed in the same casing, possibly only one end of which is sealed through the drive shaft, the free end of this shaft being received with the interposition of a thrust bearing in a blind housing at the other end of the casing.
  • the drive shaft of the centrifugal and peripheral compressors of the machine can be in direct engagement with an appropriate motor means, such as a gas turbine.
  • the machine according to the invention thus combines, in the same casing and on the same drive shaft in direct engagement with the motor means, centrifugal compressors and peripheral compressors ensuring all the compression of the fluid.
  • FIG. 1 shows, by way of example, a particularly advantageous application of the invention to an enhanced oil recovery process.
  • This method consists in injecting a pressurized gas, for example carbon dioxide, into an oil field 10 which can be underground or underwater, to assist the ascent of oil to the surface in a well or a extraction duct 12.
  • a pressurized gas for example carbon dioxide
  • the gas used is supplied by an appropriate source 14, for example a combustion unit supplied by a natural gas field, a urea synthesis plant, etc.
  • the carbon dioxide supplied by the source 14 is at a pressure of, for example, between 1 and 20 bars, which can be raised to 150 bars by a compression station 16 supplying a gas pipeline 18 bringing the compressed gas into the region of the oilfield.
  • Recompression stations 20 are provided from place to place on the pipeline 18 to compensate for the pressure losses, for example by raising the pressure of the carbon dioxide from 80 bars to approximately 150 bars.
  • a final compression station 22 increases the pressure of the carbon dioxide from 80 bars to around 250 or 300 bars, for injection into the oil field 10.
  • Carbon dioxide flow rates are typically of the order of a few hundred to several thousand tonnes per day, and the flow of compressed carbon dioxide which must be injected into the oil table gradually decreases as the deposit is exploited. .
  • the compression machines according to the invention are particularly intended to equip stations 16, 20 and 22.
  • the machine of FIG. 2 comprises a single casing constituted by a cylindrical tubular body 24 and two end flanges 26 and 28 fixed to sealing on the ends of the body 24.
  • a drive shaft 30 extends axially in the body 24 and is received at its end in a blind housing 32 of the end flange 28, by means of a rotation bearing 34 and an axial thrust bearing 36.
  • the shaft 30 sealingly passes through a cylindrical passage 38 of the end plate 26, by means of seals 40, and of rotation bearings 42.
  • the end of the shaft 30 external to the casing is driven in rotation in direct engagement by a suitable motor, for example a gas turbine.
  • the stators (not shown) of the centrifugal compressors C1, C2, ..., and those S ,,, S n of the peripheral compressors are contained in the body 24 of the casing and are supported directly by the latter.
  • a gas supply conduit 44 passes through the body 24 of the casing in leaktightness and leads to the inlet of the first centrifugal compressor C1.
  • the output of this compressor C1 is connected, inside the body 24, to the input of the second centrifugal compressor C2, as indicated diagrammatically at 46, and so on.
  • a heat exchanger 48 outside the casing of the machine.
  • the exchanger 48 is connected, through the body 24, to the outlet of a compressor and to the inlet of the next compressor, as shown diagrammatically at 50 and 52 in the drawing.
  • the output of the peripheral compressor P n-1 is connected to the input of the peripheral compressor P " as shown diagrammatically at 54, and that the output of this compressor P ,, which forms the last compression stage of the machine, is sealingly connected through the body 24 to the outlet duct 56 of the machine.
  • a peripheral compressor or recovery compressor comprises a rotor R with blades or blades rotating in an annular compression chamber formed by the stator of the compressor.
  • annular compression chamber In this annular compression chamber is fixed a sealing cap O having a slot through which the vanes a of the rotor R pass through with a small clearance.
  • the inlet and outlet conduits of the fluid open into the annular compression chamber respectively. and on the other side of the seal O.
  • the centrifugal compressors and the peripheral compressors are mounted on the drive shaft 30 so that the axial thrust F1 developed by the centrifugal compressors is opposite to the axial thrust F2 developed by the peripheral compressors, which allows, if not cancel, at least reduce the axial thrust exerted by the shaft 30 on the end plate 28 of the housing.
  • the operation of the machine obviously follows from the above:
  • the rotors of centrifugal compressors and peripheral compressors C1, C2, ..., P O-1 ' P " are driven at the same speed of rotation by their common shaft 30, which is itself driven in direct drive by a turbine
  • the gas to be compressed is introduced into the machine through line 44 passing through the body 24 of the casing, undergoes stepwise compression in the various centrifugal and peripheral compression stages and leaves the machine at a pressure of between 150 and around 300 bars.
  • the heat exchangers 48 cool the compressed gas whenever necessary between two compression stages.
  • the machine according to the invention is intended in particular for the compression of a gas whose flow rate varies between a few hundred and a few thousand tonnes per day, and is moreover capable of gradually decreasing over time.
  • the use of peripheral compressors in machine output stages makes it possible, on the one hand, to make the centrifugal compressors forming the machine input stages less sensitive to the pumping phenomenon and, on the other hand, to associate in the same casing and on the same drive shaft, the various compression stages, thanks to the identity of the dimensions and the speeds of rotation of the centrifugal compressors and of the peripheral compressors.
  • the invention is also applicable to the supply of a pressurized liquid, for example by compression of a gas by centrifugal compressors, liquefaction of this gas by passage through a heat exchanger external to the machine, then by compression of the liquid by peripheral compressors.
  • a machine equipping the station 22 for injecting compressed carbon dioxide into the oil table 10
  • a gas turbine supplying a power of the order of a few megawatts and driving the shaft 30 at a speed of the order of 10,000-12,000 revolutions per minute, the shaft 30 having a diameter of about 200 mm, the rotors of the centrifugal compressors and of the peripheral compressors having diameters on the order of 400 to 500 mm.
  • the flow of carbon dioxide supplying the machine can be of the order of 800-1000 tonnes per day, the inlet pressure is around 80 bars, the outlet pressure is around 250- 300 bars.
  • another gas for example nitrogen, could be used to propel carbon dioxide.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (7)

1. Verdichtervorrichtung für ein Gas, die insbesondere bestimmt ist, einen Gasdurchfluß der Ordnung vor einigen hunderten bis einigen zehntausenden Kubikmetern pro Stunde bei einem Druck von ungefähr zwischen 150 und 300 bar zu liefern, mit mehreren Verdichterstufen in Serie, die durch Verdichter verschiedener Typen gebildet werden, dadurch gekennzeichnet, daß die verschiedenen Verdichter (C1, C2, ..., Pn-1, Pn) Rotoren aufweisen, die ungefähr gleiche Durchmesser besitzen und die auf einer und derselben Antriebswelle (30) im Inneren eines Einheitsgehäuses (24, 26, 28) montiert sind, eine Eintrittsstufe von zumindest einem Radialverdichter (C1, C2) gebildet wird, wogegen eine Austrittsstufe von zumindest einem Peripheralverdichter (Pn-1, Pn) gebildet wird.
2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Verdichter (C1, C2, ..., Pn-1, Pn) auf der Welle (30) derart montiert sind, daß der axiale Schub (F1), welcher durch den oder die Radialverdichter (C1, C2) entwickelt wird, entgegengesetzt dem axialen Schub (F2) ist, welcher durch den oder die Peripheralverdichter (Pn-1, Pn) entwickelt wird.
3. Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Ende der Antriebswelle (30) der Verdichter über ein Längslager (36) in einem Blindlager (32) einer Stirnwand (28) des Gehäuses aufgenommen wird.
4. Vorrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß sich die Antriebswelle (3) der Verdichter in unmittelbaren Eingriff mit der antreibenden Welle eines Antriebsmittels, wie einer Gasturbine, befindet.
5. Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß Wärmetauscher (48) für das Abkühlen des verdichteten Gases zwischen zumindest gewissen der Verdichterstufen außerhalb des Gehäuses (24, 26, 28) vorgesehen sind.
6. Vorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Gas Kohlendioxid ist.
7. Vorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß sie für das Verdichten und den Transport eines Gases zum Einblasen in eine unterirdische oder unterseeische Erdöllagerstätte für die unterstütze Gewinnung des Erdöls verwendet wird.
EP84402052A 1983-10-25 1984-10-11 Mehrstufiger Serienverdichter Expired EP0143684B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8317000A FR2553835B1 (fr) 1983-10-25 1983-10-25 Machine de compression d'un fluide, a plusieurs etages de compression en serie
FR8317000 1983-10-25

Publications (2)

Publication Number Publication Date
EP0143684A1 EP0143684A1 (de) 1985-06-05
EP0143684B1 true EP0143684B1 (de) 1989-12-20

Family

ID=9293504

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84402052A Expired EP0143684B1 (de) 1983-10-25 1984-10-11 Mehrstufiger Serienverdichter

Country Status (5)

Country Link
US (1) US4747749A (de)
EP (1) EP0143684B1 (de)
JP (1) JPS60166791A (de)
DE (1) DE3480803D1 (de)
FR (1) FR2553835B1 (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62113887A (ja) * 1985-11-13 1987-05-25 Hitachi Ltd 真空ポンプ
JPH0886298A (ja) * 1994-09-19 1996-04-02 Hitachi Ltd ドライターボ真空ポンプ
DE102009031309A1 (de) * 2009-06-30 2011-01-05 Ksb Aktiengesellschaft Verfahren zur Förderung von Fluiden mit Kreiselpumpen
IT1398142B1 (it) * 2010-02-17 2013-02-14 Nuovo Pignone Spa Sistema singolo con compressore e pompa integrati e metodo.
ITFI20110262A1 (it) * 2011-12-06 2013-06-07 Nuovo Pignone Spa "heat recovery in carbon dioxide compression and compression and liquefaction systems"
EP2984344B1 (de) * 2013-04-08 2020-03-25 Dresser-Rand Company System und verfahren zum komprimieren von kohlendioxid

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1152887B (de) * 1955-03-16 1963-08-14 Roth Co Roy E Mehrstufige Pumpe zum Foerdern von siedenden oder nahezu siedenden Fluessigkeiten bzw. verfluessigten Gasen
DE1403579A1 (de) * 1961-03-04 1969-07-17 Obermaier & Cie Turbogeblaese
EP0070530A1 (de) * 1981-07-17 1983-01-26 Friedrich Schweinfurter Radialschaufelunterstützte Seitenkanalpumpe
EP0070529A1 (de) * 1981-07-17 1983-01-26 Friedrich Schweinfurter Peripheralkanalpumpe

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE513423A (de) *
US1601402A (en) * 1921-01-15 1926-09-28 Lorenzen Christian Gas turbine
DE711791C (de) * 1938-04-28 1941-10-07 Anna Dickow Geb Driemeyer Anordnung des Antriebes fuer eine nicht selbstansaugende Kreiselpumpe
US2748714A (en) * 1952-10-17 1956-06-05 Fred W Henry Thrust bearing
US3385225A (en) * 1965-06-29 1968-05-28 Siemen & Hinsch Gmbh Rotary pump
DE2138383A1 (de) * 1971-07-31 1973-02-08 Siemens Ag Pumpenaggregat zur mehrstufigen verdichtung von gasen
JPS529107A (en) * 1975-07-11 1977-01-24 Matsushita Electric Ind Co Ltd Pump
SU612072A1 (ru) * 1975-10-02 1978-06-25 Предприятие П/Я Р-6956 Вихрева машина
NZ197872A (en) * 1980-08-05 1985-03-20 Sihi Gmbh & Co Kg Self priming multi-stage centrifugal pump for liquids near boiling point
JPS57168091A (en) * 1981-04-10 1982-10-16 Hitachi Ltd Horizontal shaft double suction centrifugal pump with submerged bearing
US4431371A (en) * 1982-06-14 1984-02-14 Rockwell International Corporation Gas turbine with blade temperature control

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1152887B (de) * 1955-03-16 1963-08-14 Roth Co Roy E Mehrstufige Pumpe zum Foerdern von siedenden oder nahezu siedenden Fluessigkeiten bzw. verfluessigten Gasen
DE1403579A1 (de) * 1961-03-04 1969-07-17 Obermaier & Cie Turbogeblaese
EP0070530A1 (de) * 1981-07-17 1983-01-26 Friedrich Schweinfurter Radialschaufelunterstützte Seitenkanalpumpe
EP0070529A1 (de) * 1981-07-17 1983-01-26 Friedrich Schweinfurter Peripheralkanalpumpe

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"Technisches Handbuch Verdichter", 3ème édition 1983, VEB Verlag Technik, Berlin, pages 422-427 *
Troskolanski: "Kreiselpumpen", 3ème édition 1976, Birkhäuserverlag, page 611 *

Also Published As

Publication number Publication date
FR2553835B1 (fr) 1986-02-28
US4747749A (en) 1988-05-31
JPS60166791A (ja) 1985-08-30
FR2553835A1 (fr) 1985-04-26
DE3480803D1 (de) 1990-01-25
EP0143684A1 (de) 1985-06-05

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