EP2142806A1 - Compressor system for underwater use in the offshore area - Google Patents
Compressor system for underwater use in the offshore areaInfo
- Publication number
- EP2142806A1 EP2142806A1 EP08759450A EP08759450A EP2142806A1 EP 2142806 A1 EP2142806 A1 EP 2142806A1 EP 08759450 A EP08759450 A EP 08759450A EP 08759450 A EP08759450 A EP 08759450A EP 2142806 A1 EP2142806 A1 EP 2142806A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- housing
- compressor system
- stator
- compressor
- cooling
- 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
Links
- 239000007789 gas Substances 0.000 claims abstract description 37
- 239000000203 mixture Substances 0.000 claims abstract description 19
- 238000001816 cooling Methods 0.000 claims description 71
- 239000002826 coolant Substances 0.000 claims description 33
- 239000013535 sea water Substances 0.000 claims description 13
- 238000004519 manufacturing process Methods 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 24
- 238000004804 winding Methods 0.000 description 7
- 239000007788 liquid Substances 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000007797 corrosion Effects 0.000 description 3
- 238000005260 corrosion Methods 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 239000004519 grease Substances 0.000 description 2
- 239000002480 mineral oil Substances 0.000 description 2
- 235000010446 mineral oil Nutrition 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 239000003643 water by type Substances 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000001914 calming effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000012809 cooling fluid Substances 0.000 description 1
- 239000000110 cooling liquid Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 230000005415 magnetization Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 229920001296 polysiloxane Polymers 0.000 description 1
- 239000011253 protective coating Substances 0.000 description 1
- 229920002545 silicone oil Polymers 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 238000009736 wetting Methods 0.000 description 1
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 production 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 and a rotor package for driving the compressor.
- 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 almost 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.
- 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.
- the further transport of the compressed gas or gas / oil mixture takes place on the output side via a further 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 makes cooling of the electric motors necessary.
- 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 object of the invention is achieved by a compressor system having the features of claim 1. Further advantageous embodiments are specified in the dependent claims 2 to 8.
- the stator core of the electric motor can be cooled via an inner side of the housing of the compressor system.
- Another great advantage is that the risk of pollution is significantly reduced, since all components of the cooling system are housed in the housing. Potentially leaking connection points for connecting an otherwise required recooling system to the housing are not even available.
- the stator of the electric motor on a stator outside, which rests at least almost flush on the inside of the housing.
- a good thermal conductivity mass is introduced between the Statorau type and the inside of the housing.
- the good heat conductive mass may be e.g. a thermal grease or a good heat conductive plastic.
- 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 off. In the cooling chamber, a coolant is present.
- stator pack with its particularly hot spots, such as with its axially projecting end windings, completely immersed in the coolant.
- the cooling of these hot and critical points is therefore particularly effective. With "axial" directions are designated parallel to the axis of rotation of the electric motor.
- the coolant is a liquid, in particular an oil, such as 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 coolants may be used, such as water-based coolants.
- the coolant may alternatively be a refrigerant such as Freon ® R134a.
- the coolant is a sol, that is, a liquid / gas mixture.
- cooling passages extending substantially axially relative to the axis of rotation of the electric motor are provided in the stator core.
- the compressor system has a circulation pump for the coolant. By the circulation a more even and also higher cooling achievement is achieved.
- the compressor system for the intended use is installed such that the axis of rotation of the electric motor extends substantially in the vertical direction.
- the present arrangement causes self-acting sets a cooling circuit within the cooling chamber. Because the heating of the coolant in the respective cooling channels causes this rises and flows out of the upper axial end face of the stator. 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. Arrived at the lower end of the cooling chamber, the cooled coolant is in the direction of the axial lower end of the
- 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.
- radial are meant directions toward and away from the axis of symmetry of the cylindrical housing, and typically the axis of symmetry coincides with the axis of rotation of the electric motor.
- FIG. 1 is a sectional view of a compressor system along the axis of rotation of an electric motor and a compressor according to a first embodiment of the invention
- FIG. 2 shows a sectional view of a compressor system according to a second embodiment of the invention
- FIG. 3 shows a sectional view of a compressor system according to a third embodiment of the invention and FIG. 4 shows a side view of the compressor system according to FIG. 3 corresponding to the viewing direction IV shown in FIG.
- FIG. 1 shows a sectional view of a compressor system 1 along the axis of rotation DA of an electric motor 7 and a compressor 8 according to a first embodiment of the invention.
- 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.
- 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 interpreted in a technically robust manner with respect to the required pressure tightness.
- the compressor 8 is arranged in the housing 2, which is connected on the input side to the access opening 3 and on the output side to the outlet opening 4.
- the arrows shown in the region of the openings 3, 4 indicate the flow directions.
- the compressor 8 a turbine 81 with not further designated turbine blades. 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, the transport of the compressed gas to the outlet opening 3 takes place via a pipe connection (not further described) in the interior of the housing 2.
- 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 FIG 1, both the compressor 8 and the
- the stator 71 of the electric motor 7 can be cooled via a housing inner side GI of the housing 2 of the compressor system 1.
- the cooling via a stator outside SA, which rests flush against the inside of the housing GI.
- a good heat-conductive mass may be introduced between the stator outside SA and the inside of the housing GI, such as a good heat-conductive paste, a grease or the like.
- the compressor system 1 shown is installed in such a way that the axis of rotation DA of the electric motor 7 extends essentially 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 alternative embodiments of the compressor system 1 according to FIG. 2 and FIG. 3 also have such a cylindrical design.
- FIG. 2 shows a sectional view of a compressor system 1 according to a second embodiment of the invention.
- the compressor system 1 shown is in turn vertically installed with respect to the axis of rotation DA of the electric motor 7.
- the stator 71 is spaced from the inside GI of the housing 2.
- the mean radial distance is preferably in a range of 5 cm to 15 cm. Depending on the electrical connection power of the electric motor 7, the distance values can also lie above it, such as, for example, at 20 cm or below, for example at 3 cm.
- the stator core 71 forms with at least one opposite part of the inside of the housing 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 only one chamber in the example of FIG. It can alternatively have several chambers. sen, in which case adjacent chambers are each separated by a radially axially extending bulkhead from each other.
- 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 disc 94, a radial inner side of the stator packet 71 and the housing inner side GI thus form a hollow cylinder.
- a coolant preferably an oil
- a so-called transformer oil based on mineral oil or silicone oil is considered.
- Coolant filled In the housing 2 and outside the cooling chamber 9, a compensating vessel for the cooling liquid be present to compensate for a temperature-induced change in volume of the coolant.
- the coolant may be a refrigerant as an alternative to oil, such as Freon ® a.
- a CFC-free Freon ® is particularly advantageous in terms of environmental compatibility, 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 upwards and cools down in the reverse direction from top to bottom along the cold inside of the housing GI.
- the thermally particularly critical winding heads 73 are surrounded by the circulating coolant and thus effectively cooled.
- the cooling circuit established in the cooling chamber 9 can also be referred to as the primary cooling circuit, while at the outside of the housing, but only in the case of a calming body of water, a counterflow is established which sweeps from the bottom upwards along the exterior 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, for example, a centrifugal pump which is mounted in or on the cooling chamber 9.
- the 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 lies opposite the cooling chamber 9. The cooling of the compressor 8 takes place in this connection via the gases or gas / oil mixtures themselves to be compressed.
- FIG 3 shows a sectional view of a compressor system 1 according to a third embodiment of the invention.
- the cooling chamber 9 is formed substantially toroidal, 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.
- the reference numerals 98, 99 further sealing rings for sealing the cooling chamber walls 96, 97 are designated with the housing inner side 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 corresponding to the viewing direction IV shown in FIG.
- 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 an effective cooling of the stator 71 almost from the inside out.
- cooling fins 21 On the outer side of the housing GA, a plurality of radially directed from the outside of the housing facing away arranged cooling fins 21 can be seen.
- 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 cast.
- 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.
Landscapes
- 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)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007021720.1A DE102007021720B4 (en) | 2007-05-09 | 2007-05-09 | Compressor system for underwater use in the offshore sector |
PCT/EP2008/055629 WO2008138829A1 (en) | 2007-05-09 | 2008-05-07 | Compressor system for underwater use in the offshore area |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2142806A1 true EP2142806A1 (en) | 2010-01-13 |
EP2142806B1 EP2142806B1 (en) | 2018-02-28 |
Family
ID=39645280
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08759450.3A Active EP2142806B1 (en) | 2007-05-09 | 2008-05-07 | Compressor system for underwater use in the offshore area |
Country Status (8)
Country | Link |
---|---|
US (1) | US8313316B2 (en) |
EP (1) | EP2142806B1 (en) |
CN (1) | CN101675249B (en) |
BR (1) | BRPI0811221B1 (en) |
CA (1) | CA2686794A1 (en) |
DE (1) | DE102007021720B4 (en) |
RU (1) | RU2470190C2 (en) |
WO (1) | WO2008138829A1 (en) |
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DE102009045633A1 (en) * | 2009-10-13 | 2011-04-14 | Man Diesel & Turbo Se | Underwater compressor assembly and underwater process fluid conveyor assembly equipped therewith |
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AU2012389801B2 (en) * | 2012-09-12 | 2017-12-14 | Fmc Technologies, Inc. | Subsea multiphase pump or compressor with magnetic coupling and cooling or lubrication by liquid or gas extracted from process fluid |
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EP3035501A1 (en) * | 2014-12-18 | 2016-06-22 | Siemens Aktiengesellschaft | Stator for an electric machine |
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2007
- 2007-05-09 DE DE102007021720.1A patent/DE102007021720B4/en not_active Expired - Fee Related
-
2008
- 2008-05-07 WO PCT/EP2008/055629 patent/WO2008138829A1/en active Application Filing
- 2008-05-07 RU RU2009145531/06A patent/RU2470190C2/en active
- 2008-05-07 EP EP08759450.3A patent/EP2142806B1/en active Active
- 2008-05-07 US US12/599,160 patent/US8313316B2/en active Active
- 2008-05-07 CN CN2008800148336A patent/CN101675249B/en active Active
- 2008-05-07 BR BRPI0811221A patent/BRPI0811221B1/en not_active IP Right Cessation
- 2008-05-07 CA CA002686794A patent/CA2686794A1/en not_active Abandoned
Non-Patent Citations (1)
Title |
---|
See references of WO2008138829A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2008138829A1 (en) | 2008-11-20 |
DE102007021720B4 (en) | 2014-01-23 |
BRPI0811221A2 (en) | 2014-10-29 |
CN101675249A (en) | 2010-03-17 |
US8313316B2 (en) | 2012-11-20 |
RU2470190C2 (en) | 2012-12-20 |
RU2009145531A (en) | 2011-06-20 |
CA2686794A1 (en) | 2008-11-20 |
EP2142806B1 (en) | 2018-02-28 |
US20100239441A1 (en) | 2010-09-23 |
BRPI0811221B1 (en) | 2019-09-03 |
CN101675249B (en) | 2013-01-09 |
DE102007021720A1 (en) | 2008-11-13 |
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