EP0143684A1 - Mehrstufiger Serienverdichter - Google Patents

Mehrstufiger Serienverdichter Download PDF

Info

Publication number
EP0143684A1
EP0143684A1 EP84402052A EP84402052A EP0143684A1 EP 0143684 A1 EP0143684 A1 EP 0143684A1 EP 84402052 A EP84402052 A EP 84402052A EP 84402052 A EP84402052 A EP 84402052A EP 0143684 A1 EP0143684 A1 EP 0143684A1
Authority
EP
European Patent Office
Prior art keywords
compressors
machine
machine according
compressor
shaft
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.)
Granted
Application number
EP84402052A
Other languages
English (en)
French (fr)
Other versions
EP0143684B1 (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
Original Assignee
Bertin et Cie SA
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 Bertin et Cie SA filed Critical Bertin et Cie SA
Publication of EP0143684A1 publication Critical patent/EP0143684A1/de
Application granted granted Critical
Publication of EP0143684B1 publication Critical patent/EP0143684B1/de
Expired legal-status Critical Current

Links

Images

Classifications

    • 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 machine for compressing a fluid, comprising several compression stages in series constituted by compressors of different types.
  • centrifugal compressors When it is desired to obtain fluid flow rates of the order of a few hundred to a few tens of thousands of m 3 per hour at a pressure between approximately 100-150 and 300-350 bars, it is already known to associate centrifugal compressors to reciprocating piston compressors or to screw compressors, the fluid being compressed first by centrifugal compressors, then by piston or screw compressors.
  • Such a set of compressors can in particular produce compressed gas intended to be injected into an oil table (which can be underground or underwater) for enhanced oil recovery.
  • 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 there are oscillated very high pressure 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.
  • the invention particularly relates to a fluid 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 fluid compression machine intended in particular to deliver a fluid flow rate of the order of a few hundred to a few tens of thousands of m 3 per hour at a pressure of between 150 and 300 bars approximately.
  • a fluid compression machine comprising several compression stages in series constituted by compressors of different types, characterized by the combination of at least one centrifugal compressor forming an input stage of the machine and at least one peripheral compressor forming a stage of out of this machine.
  • 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, of which possibly only one end is leaktightly crossed by 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 medium motor, centrifugal compressors and peripheral compressors ensuring all the compression of the fluid.
  • FIG. 1 represents, 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 gas 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 a few 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 n-1 , S of the peripheral compressors are contained in the body 24 of the casing and are supported directly by the latter.
  • a gas supply pipe 44 passes through the body 24 of the casing in leaktightness and leads to the inlet of the first centrifugal compressor C1.
  • the outlet of this compressor C1 is connected, inside the body 24, to the inlet of the second centrifugal compressor C2, as shown diagrammatically in 46, and so on.
  • provision may be made to cool the compressed gas by passage through an outside heat exchanger 48 laughing at the machine housing.
  • 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 n 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 pipe 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 0 having a slot through which the vanes a of the rotor R pass through with a small clearance.
  • the fluid inlet and outlet conduits 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 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.
  • peripheral compressors in output stages of the machine makes it possible, on the one hand, to make the centrifugal compressors forming the input stages of the machine 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 approximately 200 mm, the rotors of the centrifugal compressors and of the peripheral compressors having diameters of in the range of 400 to 500 mm.
  • the flow of carbon dioxide supplied to the machine can be of the order of 800-1000 tonnes per day, the inlet pressure is of the order of 80 bars, the outlet pressure is of the order of 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)
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 true EP0143684A1 (de) 1985-06-05
EP0143684B1 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)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0226039A1 (de) * 1985-11-13 1987-06-24 Hitachi, Ltd. Vakuumpumpe
ITFI20110262A1 (it) * 2011-12-06 2013-06-07 Nuovo Pignone Spa "heat recovery in carbon dioxide compression and compression and liquefaction systems"

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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.
EP2984344B1 (de) * 2013-04-08 2020-03-25 Dresser-Rand Company System und verfahren zum komprimieren von kohlendioxid

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2149128A5 (de) * 1971-07-31 1973-03-23 Siemens Ag

Family Cites Families (14)

* 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
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
US3385225A (en) * 1965-06-29 1968-05-28 Siemen & Hinsch Gmbh Rotary pump
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
DE3128374A1 (de) * 1981-07-17 1983-02-17 Friedrich 8541 Röttenbach Schweinfurter Radialschaufelunterstuetzte seitenkanalpumpe
DE3128372A1 (de) * 1981-07-17 1983-02-03 Friedrich 8541 Röttenbach Schweinfurter "peripheralkanalpumpe"
US4431371A (en) * 1982-06-14 1984-02-14 Rockwell International Corporation Gas turbine with blade temperature control

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2149128A5 (de) * 1971-07-31 1973-03-23 Siemens Ag

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0226039A1 (de) * 1985-11-13 1987-06-24 Hitachi, Ltd. Vakuumpumpe
ITFI20110262A1 (it) * 2011-12-06 2013-06-07 Nuovo Pignone Spa "heat recovery in carbon dioxide compression and compression and liquefaction systems"
EP2602445A1 (de) * 2011-12-06 2013-06-12 Nuovo Pignone S.p.A. Wärmerückgewinnung bei der Kohlendioxidverdichtung sowie Verdichtungs- und Verflüssigungssystem
US10487697B2 (en) 2011-12-06 2019-11-26 Nuovo Pignone S.P.S. Heat recovery in carbon dioxide compression and compression and liquefaction systems

Also Published As

Publication number Publication date
FR2553835B1 (fr) 1986-02-28
JPS60166791A (ja) 1985-08-30
US4747749A (en) 1988-05-31
EP0143684B1 (de) 1989-12-20
FR2553835A1 (fr) 1985-04-26
DE3480803D1 (de) 1990-01-25

Similar Documents

Publication Publication Date Title
EP0435291B1 (de) Kombinierte Turbomolekularpumpe mit zwei Wellen und atmosphärischem Auslass
BE1014892A5 (fr) Compresseur a vis sans huile.
EP0401741B1 (de) Zweistufige Trockenprimärpumpe
EP0499504B1 (de) Turbomaschine - vom Typ Kompressor oder Turbine - zur Verdichtung oder Entspannung eines gefährlichen Gases
EP2909450B1 (de) Strahlpumpe zur druckentlastung von schmierkammern einer turbomaschine mit unabhängigen doppelten injektoren
FR2907495A1 (fr) Turbomachine
FR2628790A1 (fr) Propulseur combine turbofusee aerobie
FR2610039A1 (fr) Moyen d'equilibrage a piston de vapeur dans un moteur a turbine et procede de fonctionnement de ce moteur
WO2008071651A2 (fr) Procede et systeme de lubrification d'une turbomachine
EP0143684B1 (de) Mehrstufiger Serienverdichter
FR3027625A1 (fr) Turbomachine comprenant un generateur de courant electrique permettant l'injection d'huile depuis l'interieur d'un arbre de turbine
FR3002271A1 (fr) Roue de turbine, de compresseur ou de pompe.
FR2784143A1 (fr) Pompe volumetrique a carburant a diminution du bruit par cavitation
EP3833872B1 (de) Mehrstufige turbomaschine
EP1477684B1 (de) Molekular, Turbomolekular oder Hybridpumpe mit intergriertem Ventil
FR2492475A1 (fr) Procede pour assembler une pompe a vide turbomoleculaire a simple flux et pompe ainsi assemblee
EP0277861A1 (de) Hydraulische Schraubenmotoren
FR2735531A1 (fr) Pompe de carburant
EP1473462B1 (de) Patrone zum Zusammenbau eines Verdichters
FR2496162A1 (fr) Turbine a refoulement
FR2482675A1 (fr) Turbine a palettes
EP2472126B1 (de) Verdichter mit Antrieb und verstellbarer, aerodynamischer Geometrie
WO1988005118A1 (fr) Profils de rotors, du type a vis, pour machines tournantes vehiculant un fluide gazeux
FR2531744A1 (fr) Turbine a pales croisees
BE521295A (de)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): CH DE GB IT LI

17P Request for examination filed

Effective date: 19851005

17Q First examination report despatched

Effective date: 19860812

D17Q First examination report despatched (deleted)
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE GB IT LI

REF Corresponds to:

Ref document number: 3480803

Country of ref document: DE

Date of ref document: 19900125

ITF It: translation for a ep patent filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19950922

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19951004

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19951021

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19961011

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19961031

Ref country code: CH

Effective date: 19961031

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19961011

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19970701