EP2142806B1 - Système compresseur pour une utilisation sous-marine dans le domaine offshore - Google Patents

Système compresseur pour une utilisation sous-marine dans le domaine offshore Download PDF

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Publication number
EP2142806B1
EP2142806B1 EP08759450.3A EP08759450A EP2142806B1 EP 2142806 B1 EP2142806 B1 EP 2142806B1 EP 08759450 A EP08759450 A EP 08759450A EP 2142806 B1 EP2142806 B1 EP 2142806B1
Authority
EP
European Patent Office
Prior art keywords
housing
compressor system
cooling
compressor
electric motor
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.)
Active
Application number
EP08759450.3A
Other languages
German (de)
English (en)
Other versions
EP2142806A1 (fr
Inventor
Maria Bade
Joachim Mucha
Axel MÖHLE
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.)
Siemens AG
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Siemens AG
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Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP2142806A1 publication Critical patent/EP2142806A1/fr
Application granted granted Critical
Publication of EP2142806B1 publication Critical patent/EP2142806B1/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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • 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
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0686—Units comprising pumps and their driving means the pump being electrically driven specially adapted for submerged use
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5826—Cooling at least part of the working fluid in a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine

Definitions

  • the invention relates to a compressor system, in particular for the promotion of gases or gas / oil mixtures in the offshore sector.
  • the compressor system has a seawater-resistant housing with at least one access opening for gases or gas / oil mixtures to be compressed and with at least one outlet opening for the compressed gases or gas / oil mixtures. It has a compressor arranged in the housing, which is connected on the input side to the access opening and on the output side to the output opening.
  • an electric motor is arranged with a stator core which can be cooled via an inner side of the housing and with a rotor core for driving the compressor.
  • German patent DE 37 29 486 C1 is a compressor unit for the production of natural gas in the offshore area with drive by a high-frequency motor for the compression of gases is known, which is suitable for large water depths.
  • the high-frequency motor of the compressor unit is magnetically mounted and drives the compressor stages in a common gas-tight housing. The cooling of the engine, the bearings and the compressor stages takes place through the liquid surrounding the common housing.
  • German patent application DE 42 09 118 A1 is an electric motor with a motor pressure housing, filled with gas. under high pressure, known.
  • a capsule is provided which surrounds the rotor rods on the drive side and / or side.
  • a compressor which has a compressor unit and an electric motor driving the same via a common shaft.
  • the shaft is mounted on a liquid cooled axle.
  • the compressor systems can be driven by an electric motor or by a gas turbine.
  • the electric motor is preferably a brushless asynchronous motor.
  • a high-speed turbine is used for compression, in which case the turbine and the electric motor are preferably arranged on a common shaft.
  • the brush and gearless drive allows virtually maintenance-free operation of such compressor systems.
  • screw or reciprocating compressors can be used for compression.
  • the considered compressor systems may be installed in coastal petrochemical facilities, on drilling platforms or under water. In the latter case, the drive of the compressor is typically carried out with an electric motor.
  • the supply of the gas or the gas / oil mixture is usually via a pipe which is flanged to the outside of the housing of the compressor system. In a corresponding manner, the further transport of the compressed gas or gas / oil mixture takes place on the output side via another Pipeline.
  • a pressure hose can be used instead of a pipe.
  • the high electrical connection capacity of the electric motors used in the range of several 100 kW requires cooling of the electric motors.
  • an oil recooling system is used, which is connected as a separate unit via oil supply lines and oil return lines to the compressor system.
  • Such compressor systems are disadvantageously expansive because of the externally arranged oil recooling.
  • Another disadvantage is that the external oil recooling systems may leak over time.
  • the oil feed pipes and the oil return pipes themselves may become leaky, in particular due to corrosion caused by sea water or due to mechanical effects, such as corrosion. by waves.
  • pressure-tight connection connections of the pipelines to the housing of the compressor system can become leaky over time. Escaping oil and oil / gas mixtures in this context represents a potential ecological hazard to the surrounding waters.
  • the stator core is spaced from the inside of the housing.
  • the stator in this case forms with at least one opposite part of the inside of the housing an annular cooling chamber.
  • a coolant is present in the cooling chamber.
  • the coolant is a liquid, especially an oil, e.g. a silicone or mineral oil. In addition to the high specific heat capacity, this has an advantageous electrically insulating effect with regard to the live winding ends.
  • other cooling liquids may be used, such as e.g. Water based coolants.
  • the coolant may alternatively be a refrigerant, such as e.g. Freon® R134a.
  • the coolant is a sol, that is, a liquid / gas mixture.
  • cooling passages extending essentially axially to the axis of rotation of the electric motor are provided in the stator core.
  • the compressor system comprises a circulation pump for the coolant.
  • the compressor system for the intended use is installed such that the axis of rotation of the electric motor is substantially in the vertical direction.
  • the present arrangement causes automatically adjusts a cooling circuit within the cooling chamber. Because the heating of the coolant in the respective cooling channels causes it to rise and flow out of the upper axial face of the stator core. Subsequent coolant forcibly conveys the heated coolant to the inside of the housing that is cold compared to the coolant temperature. The subsequent cooling causes an increase in specific gravity and a decrease in the coolant. At the lower end of the cooling chamber, the cooled coolant is sucked in the direction of the axially lower end face of the stator core. The cooling circuit is closed.
  • the cold outside of the outside of the housing which has typical temperatures in the single-digit Celsius range, acts as a heat sink.
  • the large temperature gradient between heated coolant and cold seawater causes a large heat flow from the coolant through the housing wall to the seawater.
  • baffles For the purpose of directing the circulating liquid flow forming in the cooling chamber, baffles, e.g. be arranged at the axial ends of the stator.
  • the housing has an outer housing side, on which a plurality of cooling fins is arranged.
  • the cooling fins cause a significant increase in the cooling surface to the sea water.
  • the enlarged cooling surface may, depending on the shape and number of existing cooling fins, be a multiple of the otherwise existing outer surface of the housing of the compressor system.
  • the cooling fins are away from the outside of the housing.
  • the housing has a cylindrical shape.
  • the heat sinks are radially away from the outside of the housing.
  • With “radial" directions are referred to the axis of symmetry of the cylindrical housing to and away from her.
  • the axis of symmetry coincides with the axis of rotation of the electric motor.
  • FIG. 1 shows a sectional view of a non-inventive compressor system 1 along the axis of rotation DA of an electric motor 7 and a compressor eighth
  • a housing 2 is seawater resistant.
  • the housing 2 is preferably made of steel and may have a protective coating to prevent corrosion.
  • the steel used may alternatively or additionally be a stainless steel.
  • the housing 2 may be made of a seawater resistant aluminum.
  • the housing is pressure-tight, in accordance with the intended for operation of the compressor system 1 depth of use under the sea water level or on the seabed.
  • the pressure-tight requirements relate not only to the housing 2 itself, but also implementations in the housing, such as for power and control cables for power supply and for controlling and / or monitoring of the compressor system. 1
  • the housing 2 has, for example, an access opening 3 for the gases or gas / oil mixtures to be compressed and an outlet opening 4 for the compressed gases or gas / oil mixtures.
  • a plurality of openings 3, 4 may be present.
  • At the two openings 3, 4 are usually connecting elements, such as couplings or flanges, mounted in order to connect to these pipes or pressure hoses.
  • the connection elements and the pipes are to be designed in a technically robust manner with regard to the respectively required pressure tightness.
  • the compressor 8 is arranged, which is the input side connected to the access opening 3 and the output side to the output port 4.
  • the arrows shown in the region of the openings 3, 4 indicate the flow directions.
  • the compressor 8 has a turbine 81 with turbine blades not further specified. Their diameter decreases in the axial direction, that is, in the flow direction, whereby the pressure increases due to the compression at the same time.
  • the reference numeral 83 denotes a high-pressure discharge. From there, via a pipe connection, not further described, inside the housing 2, the transport of the compressed gas to the exit opening 3 takes place.
  • the electric motor 7 is further arranged for driving the compressor 8.
  • the electric motor 7 has a stator 71 and a rotor package 72. Furthermore, in the example of the FIG. 1 both the compressor 8 and the electric motor 7 on a common, guided in bearings 6 shaft 5.
  • the stator 71 of the electric motor 7 is cooled via a housing inner side GI of the housing 2 of the compressor system 1.
  • cooling takes place via a stator outer side SA, which rests flush against the inside of the housing GI.
  • the arrows entered in the contact area between the outside of the stator SA and the inside of the housing GI symbolize the heat flow.
  • a good thermal conductivity mass such as a good thermal conductivity paste, a grease or the like.
  • the compressor system 1 shown is installed such that the axis of rotation DA of the electric motor 7 extends substantially in the vertical direction. It can alternatively be aligned in a horizontal position.
  • the housing 2 has a housing outside GA, on which a plurality of projecting cooling fins 21 is arranged.
  • the cooling fins 21 are radially away from the housing outside GA.
  • the compressor system 1 according to the invention and an embodiment according to FIG. 2 and FIG. 3 have such a cylindrical design.
  • FIG. 2 shows a sectional view of a compressor system according to the invention 1.
  • the compressor system 1 shown is in turn mounted vertically with respect to the axis of rotation DA of the electric motor 7.
  • stator 71 In contrast to the compressor system according to FIG. 1 is the stator 71 according to the invention from the inside GI of the housing 2 spaced.
  • the mean radial distance is preferably in a range of 5 cm to 15 cm. Depending on the electrical connection performance of the electric motor 7, the distance values can also be above, for example, at 20 cm, or below, such as at 3 cm.
  • the stator 71 forms with at least one opposite part of the housing inner side GI an annular cooling chamber 9, in which a coolant 9 is present.
  • the cooling chamber 9 In the cooling chamber 9 are also the winding heads 73 of the stator 71, which protrude axially from the stator 71.
  • the cooling chamber 9 has in the example of FIG. 2 only one chamber up. It may alternatively have a plurality of chambers, in which case adjacent chambers are separated from each other by a radially axially extending bulkhead.
  • the cooling chamber 9 is formed by two ripeness 91, 92 and a circular disk 94.
  • the two ripen 91, 92 have an inner diameter which corresponds to the inner diameter of the stator 71.
  • the first hoop 91 is sealed to a lower axial end face of the stator pack 71, such as e.g. welded.
  • the axis of symmetry of this hoop 91 is aligned with the axis of rotation DA of the electric motor 7.
  • the axial height of the first hoop 91 corresponds to almost the axial distance of the stator 71 to a bottom plate 22 of the housing 2.
  • the lower edge of the first hoop 91 can via a sealing ring 93 for Bottom plate 22 to be sealed towards sealed or welded to the bottom plate 22.
  • the second hoop 92 is similarly attached to the upper axial end of the stator core 71.
  • the circular disk 94 has an inner diameter which corresponds approximately to the inner diameter of the maturity 91, 92.
  • the outer diameter corresponds approximately to the inner diameter of the housing 2.
  • the second hoop 92 and the circular disk 94 are preferably welded together tightly and together form a flange 92, 94.
  • the outer edge of the circular disk 94 and the flange 92, 94 can via another Gasket 95 may be sealed to the inside of the housing GI or tightly welded to the inside of the housing GI.
  • the maturity 91, 92, the circular disk 94, a radial inner side of the stator core 71 and the inside of the housing GI thus form a hollow cylinder.
  • a coolant preferably an oil
  • a so-called transformer oil based on mineral oil or silicone oil comes into consideration.
  • the entire cooling chamber 9 is filled with the cooling liquid.
  • a compensating vessel for the cooling liquid may be present to compensate for a temperature-induced change in volume of the coolant.
  • the coolant may alternatively be a refrigerant, such as a Freon®. It is particularly advantageous in terms environmental compatibility a CFC-free Freon®, such as Freon® R134a.
  • the cooling chamber 9 is filled with a sol, that is, with a liquid / gas mixture.
  • cooling passages 75 extending essentially axially to the axis of rotation DA of the electric motor 7 are present in the stator pack 71. Because of the embedding of the stator 71 in the coolant, these are also filled with the coolant.
  • a circulation of the coolant in the cooling chamber 9 is established. This is represented by flow arrows.
  • the coolant heated in the cooling channels 75 rises upward and cools in the reverse direction from top to bottom along the cold inside of the housing GI again.
  • the thermally particularly critical winding heads 73 are surrounded by the circulating coolant and thus effectively cooled.
  • the horizontal arrows symbolize the heat transfer from the coolant, continue on the wall of the housing 2 in the sea water, which surrounds the outside of the housing GA 2.
  • the adjusting in the cooling chamber 9 cooling circuit can also be referred to as a primary cooling circuit, while adjusts to the outside of the housing, but only in the case of a stationary water, a counterflow, which sweeps from bottom to top along the outside of the housing GA.
  • the cooling by the seawater can also be called secondary cooling.
  • the compressor system 1 may comprise a circulation pump for the coolant.
  • the circulating pump is e.g. a centrifugal pump which is mounted in or on the cooling chamber 9.
  • cooling fins 21 are formed on the outside of the housing 2 GA shorter in length. They extend only in the axial "hot" region of the housing 2, which is opposite to the cooling chamber 9.
  • the cooling of the compressor 8 takes place in this context on the gases to be compressed or gas / oil mixtures themselves.
  • FIG. 3 shows a sectional view of a compressor system 1 according to a third embodiment of the invention.
  • the cooling chamber 9 is substantially torus-shaped, wherein the cooling chamber 9 curved cooling chamber walls 96, 97 which favor the circulating flow through their shape.
  • the cooling capacity of this embodiment is therefore larger in comparison to the second embodiment with the same construction volume.
  • the cooling chamber walls 96, 97 fulfill in addition to the formation of the cooling chamber 9 and a Strömungsleitfunktion.
  • Reference numerals 98, 99 denote further sealing rings for sealing the cooling chamber walls 96, 97 with the inside of the housing GI.
  • the cooling chamber walls 96, 97 may be tightly welded to the inside of the housing GI.
  • FIG. 4 shows a side view of the compressor system 1 according to FIG. 3 according to the in FIG. 3 marked line of vision IV.
  • FIG. 4 shows the view into the access opening 3, that is in the direction of the compressor.
  • the stator 71 has a plurality of circumferentially uniformly distributed cooling channels 75 on.
  • the cooling channels 75 are arranged with respect to their radial position to the winding heads 73 on both sides of the winding heads 73 (see also FIG. 2 and FIG. 3 ).
  • the arrangement of the cooling channels 75 is preferably carried out in the magnetically less active region of the stator 71.
  • the plurality of cooling channels 75 allows effective cooling of the stator 71 from the inside out.
  • cooling fins 21 On the outer side of the housing GA there is a large number of cooling fins 21 arranged radially away from the outside of the housing to see.
  • the cooling fins 21 cause a drastic increase in the cooling surface available for cooling by seawater.
  • the cooling fins 21 are an integral part of the housing 2 of the compressor system 1.
  • the housing 2 is made of a casting.
  • the compressor system according to the invention is also suitable for high-speed compressor systems at speeds of up to 15,000 rpm and powers of a few 100 kW up to 10 MW and more.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (6)

  1. Système compresseur, notamment pour véhiculer des gaz ou des mélanges de gaz et de pétrole dans le domaine offshore, comprenant une enveloppe (2) résistante à l'eau de mer et ayant au moins une ouverture (3) d'entrée pour des gaz ou des mélanges de gaz et de pétrole à comprimer et au moins une ouverture (4) de sortie pour les gaz ou les mélanges de gaz et de pétrole comprimés, comprenant un compresseur (8), qui est disposé dans l'enveloppe (2) et qui communique, du côté de l'entrée, avec l'ouverture (3) d'entrée et, du côté de la sortie, avec l'ouverture (4) de sortie et comprenant un moteur (7) électrique, qui est disposé dans l'enveloppe (2) et qui a un paquet (71) statorique pouvant être refroidi par l'intermédiaire d'une face (GI) intérieure de l'enveloppe (2) et un paquet (72) rotorique pour entraîner le compresseur (8),
    caractérisé
    - en ce que le paquet (71) statorique est à distance de la face (GI) intérieure de l'enveloppe (10),
    - en ce que le paquet (71) statorique constitue une chambre (9) de refroidissement annulaire avec au moins une partie opposée à la face (GI) intérieure de l'enveloppe et
    - en ce qu'il y a un fluide de refroidissement dans la chambre (9) de refroidissement.
  2. Système compresseur suivant la revendication 1, caractérisé en ce que le fluide de refroidissement est une huile.
  3. Système compresseur suivant la revendication 1 ou 2, caractérisé en ce qu'il y a dans le paquet (71) statorique des canaux (75) de refroidissement, s'étendant sensiblement axialement par rapport à l'axe (DA) de rotation du moteur (7) électrique.
  4. Système compresseur suivant l'une des revendications précédentes, caractérisé en ce que le système compresseur a une pompe de circulation du fluide de refroidissement.
  5. Système compresseur suivant l'une des revendications précédentes, caractérisé en ce que le système compresseur est, en utilisation conforme aux prescriptions, installé de manière à ce que l'axe (DA) de rotation du moteur (7) électrique s'étende sensiblement dans la direction verticale.
  6. Système compresseur suivant l'une des revendications précédentes, caractérisé en ce que l'enveloppe (2) a une face (GA) extérieure et en ce qu'une pluralité d'ailettes (21) de refroidissement sont disposées sur la face (GA) extérieure de l'enveloppe.
EP08759450.3A 2007-05-09 2008-05-07 Système compresseur pour une utilisation sous-marine dans le domaine offshore Active EP2142806B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007021720.1A DE102007021720B4 (de) 2007-05-09 2007-05-09 Verdichtersystem für den Unterwassereinsatz im Offshore-Bereich
PCT/EP2008/055629 WO2008138829A1 (fr) 2007-05-09 2008-05-07 Système compresseur pour une utilisation sous-marine dans le domaine offshore

Publications (2)

Publication Number Publication Date
EP2142806A1 EP2142806A1 (fr) 2010-01-13
EP2142806B1 true EP2142806B1 (fr) 2018-02-28

Family

ID=39645280

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08759450.3A Active EP2142806B1 (fr) 2007-05-09 2008-05-07 Système compresseur pour une utilisation sous-marine dans le domaine offshore

Country Status (8)

Country Link
US (1) US8313316B2 (fr)
EP (1) EP2142806B1 (fr)
CN (1) CN101675249B (fr)
BR (1) BRPI0811221B1 (fr)
CA (1) CA2686794A1 (fr)
DE (1) DE102007021720B4 (fr)
RU (1) RU2470190C2 (fr)
WO (1) WO2008138829A1 (fr)

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Publication number Publication date
CN101675249A (zh) 2010-03-17
CN101675249B (zh) 2013-01-09
US20100239441A1 (en) 2010-09-23
BRPI0811221B1 (pt) 2019-09-03
BRPI0811221A2 (pt) 2014-10-29
RU2470190C2 (ru) 2012-12-20
EP2142806A1 (fr) 2010-01-13
US8313316B2 (en) 2012-11-20
RU2009145531A (ru) 2011-06-20
DE102007021720A1 (de) 2008-11-13
WO2008138829A1 (fr) 2008-11-20
CA2686794A1 (fr) 2008-11-20
DE102007021720B4 (de) 2014-01-23

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