EP3441621A1 - Turbocompresseur avec injection de gaz de compression liquéfié dans l'écoulement - Google Patents

Turbocompresseur avec injection de gaz de compression liquéfié dans l'écoulement Download PDF

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Publication number
EP3441621A1
EP3441621A1 EP17185707.1A EP17185707A EP3441621A1 EP 3441621 A1 EP3441621 A1 EP 3441621A1 EP 17185707 A EP17185707 A EP 17185707A EP 3441621 A1 EP3441621 A1 EP 3441621A1
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EP
European Patent Office
Prior art keywords
flow path
cpa
process fluid
compressor
pfl
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.)
Withdrawn
Application number
EP17185707.1A
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German (de)
English (en)
Inventor
Leonid Bleicher
Sven-Erik Brink
Uwe Martens
Dieter Nass
Attilla Yildiz
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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
Priority to EP17185707.1A priority Critical patent/EP3441621A1/fr
Publication of EP3441621A1 publication Critical patent/EP3441621A1/fr
Withdrawn legal-status Critical Current

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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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/701—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps
    • F04D29/705—Adding liquids
    • 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
    • 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
    • F04D29/5846—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0022—Hydrocarbons, e.g. natural gas
    • F25J1/0025—Boil-off gases "BOG" from storages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0045—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by vaporising a liquid return stream
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0203—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a single-component refrigerant [SCR] fluid in a closed vapor compression cycle
    • F25J1/0208—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a single-component refrigerant [SCR] fluid in a closed vapor compression cycle in combination with an internal quasi-closed refrigeration loop, e.g. with deep flash recycle loop
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0211—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a multi-component refrigerant [MCR] fluid in a closed vapor compression cycle
    • F25J1/0219—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a multi-component refrigerant [MCR] fluid in a closed vapor compression cycle in combination with an internal quasi-closed refrigeration loop, e.g. using a deep flash recycle loop
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0244—Operation; Control and regulation; Instrumentation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0292—Refrigerant compression by cold or cryogenic suction of the refrigerant gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/10—Stators
    • F05D2240/12—Fluid guiding means, e.g. vanes
    • F05D2240/122—Fluid guiding means, e.g. vanes related to the trailing edge of a stator vane
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/10—Stators
    • F05D2240/12—Fluid guiding means, e.g. vanes
    • F05D2240/123—Fluid guiding means, e.g. vanes related to the pressure side of a stator vane
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2210/00—Processes characterised by the type or other details of the feed stream
    • F25J2210/04—Mixing or blending of fluids with the feed stream
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2220/00—Processes or apparatus involving steps for the removal of impurities
    • F25J2220/60—Separating impurities from natural gas, e.g. mercury, cyclic hydrocarbons
    • F25J2220/62—Separating low boiling components, e.g. He, H2, N2, Air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/02—Compressor intake arrangement, e.g. filtering or cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/04—Compressor cooling arrangement, e.g. inter- or after-stage cooling or condensate removal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2235/00—Processes or apparatus involving steps for increasing the pressure or for conveying of liquid process streams
    • F25J2235/60—Processes or apparatus involving steps for increasing the pressure or for conveying of liquid process streams the fluid being (a mixture of) hydrocarbons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/90—External refrigeration, e.g. conventional closed-loop mechanical refrigeration unit using Freon or NH3, unspecified external refrigeration

Definitions

  • the invention relates to a compressor arrangement with at least one turbocompressor for compressing a process fluid.
  • the invention relates to a method for liquefying a gaseous process fluid, in particular natural gas by means of a liquefaction plant of the type defined.
  • a process for the liquefaction of a gaseous process fluid is already known from WO 2016/020282 known.
  • the process of liquefaction is described there in outline, where it consists essentially of the fact that gaseous natural gas is sucked in, compressed, cooled and relaxed. After cooling and the subsequent expansion, using the Joule-Thomson effect, a fraction of liquid natural gas is produced, which is stored in a container.
  • the process is in the WO 2016/020282 shown simplified and will turn out in the actual implementation usually more complex, for example, have further compression steps and / or require additional intermediate cooling or heat exchangers.
  • suitable turbocompressors are particularly single-shaft radial turbocompressors with preferably vertical parting line. These machines are particularly suitable for the thermodynamic boundary conditions, in particular for the regularly required intake volumes and ultimate pressures, so that a long service life with high availability is to be expected.
  • a compressor is for example from the WO 2007/137959 known.
  • the natural gas liquefaction arise at the intended for storage of the liquefied gas Containers always gas vapors - the so-called boil-off gas.
  • Natural gas is stored, for example, at a temperature of about - 161 ° C, so that it comes under the influence of the ambient temperature to corresponding amounts of gas vapors.
  • these gases are not simply flared, but compressed and at least partially used as fuel for different consumers.
  • the compressors used for this purpose must have a very wide range of application in terms of the volume flow to be compressed, because the amount incurred depends strongly on the instantaneous operation of the liquefaction plant.
  • the compression of the gas vapors usually requires additional heat exchangers, so that the final temperature of the compression is not too high.
  • This partial flow can be taken, for example, from a recirculation.
  • the invention has the object to develop a turbo-compressor and a method of the input called type, so that disadvantages in terms of efficiency and be reduced in terms of investment costs for such a system.
  • the compressor assembly may include a main flow path of the process fluid along which a pressure increase is imposed on the process fluid, more preferably the compressor assembly may include a recirculation line having a first position of the main flow path at a higher pressure level with a second position of the main flow path having a lower pressure level forming a bypass flow path, the at least one turbocompressor having a housing, wherein rotatable flow guide elements of a rotor of the turbocompressor are arranged in the housing along an inner flow path delimited by static flow guide elements, the inner flow path comprising the rotatable flow guide elements and static flow guide elements for compressing the gaseous process fluid is formed.
  • the invention means injection directly into the flow path of the process fluid without separate acceleration or retardation of the process fluid for the purpose of admixing the liquid phase.
  • no separate process container is provided for this purpose according to the invention.
  • the injector is simply inserted into an existing plant without otherwise changing the plant, for example into a pipeline or as a module into an otherwise unaltered recycling stage.
  • the injection devices may in this case be formed as part of the scan200191nbegrenzungslust or the guide vanes.
  • the turbocompressor according to the invention has the advantage that, as a result of the injected mass flow, both the temperature of the process fluid can be reduced and the volumetric flow to be compressed can be increased as needed, so that the compressor can be operated closer to its optimal efficiency. Accordingly, in small boil-off gas streams, one often comes out with a smaller additional mass flow admixed, which can be fed in from the recirculation. Since the mixing of the injection mass flow with the otherwise to be compressed mass flow according to a variant of the invention in the turbocompressor or according to the second variant in the recirculation takes place, also eliminates the need to provide an additional process vessel for mixing the mass flows. Due to the cooling admixing liquid process gas to the process gas to be compressed directly into the turbocompressor or the bypass flow path also results in a better approximation of the process to an isothermal process, so that is expected to further efficiency advantages.
  • the turbocompressor has an intake flange as part of the inner flow path, wherein an injection device for supplying the liquid process fluid is provided in the intake flange.
  • the attribute "in the intake flange” designates the circumstance that the intake flange defines a partial section at the beginning of the internal flow path of the process fluid through the turbo-compressor and the injection device feeds the liquid process fluid into this defined region.
  • the inner flow path has at least one injection device along a direction of flow at at least one intermediate position between two sections with rotatable flow guide elements.
  • the process fluid is cooled directly after the lossy supply of technical work by means of the injected liquid process fluid and, for example, an approximately isothermal compression is made possible.
  • the intermediate positions are formed as return stages, so that, for example, in the section of a 180 ° deflection, the injection of the cooling, liquid process fluid can take place.
  • the housing of the at least one turbocompressor has a suction flange and an outlet flange, which belong to the static flow guide elements of the turbocompressor, wherein along a flow direction of the suction flange, the beginning of the inner flow path and the outlet flange, the end of the inner flow path for form the at least one turbocompressor.
  • the inner flow path it is expedient for the inner flow path to have a region without rotatable flow guide elements along at least one intermediate position between two sections with rotatable flow guide elements along a throughflow direction and to have at least one injection device there.
  • the at least one turbocompressor is designed as a radial compressor and the at least one intermediate position as a return stage.
  • the return stage comprises guide vanes.
  • These guide vanes may be particularly useful according to the invention have mouth openings of the injector as part of the vanes.
  • these orifices of the injection device may be arranged in the circumferential direction between the guide vanes. If the orifices are disposed on the vane itself, it may be particularly useful if they are on a pressure side of the vanes or on a suction side of the vanes or at a trailing edge of the airfoil the vanes are arranged.
  • the orifices of the injection device For the smallest possible, possibly unintentional influencing of the flow, it may be expedient to design the orifices of the injection device as flat jet nozzles. Furthermore, the smallest possible influence on the flow pattern can be achieved if, in addition to or as an alternative to the flat jet design, the orifices of the injection device are each provided in a depression or recess in the surface of the respective location of the orifice.
  • the orifices may be arranged according to another advantageous embodiment of the invention also on a boundary contour of an annular space of a return stage. Under a boundary contour here the surface of standing flow guide is considered.
  • a further advantageous embodiment of the invention provides that at a low point of the inner flow path, a collector and / or a drain for temporary storage and / or removal of separated liquid is / are provided.
  • the separated liquid may in particular be non-evaporated liquid process fluid from an injection device.
  • This embodiment essentially serves to prevent the further transport of liquid, in particular through rotating flow guide elements, so that damage to downstream components can be avoided.
  • the inventive method provides that the turbo compressor gaseous process fluid is supplied and a compression of the gaseous process fluid by means of the turbo compressor under injection from an inflow of liquid process fluid into a main flow path inside a housing of the turbocompressor.
  • piping, containers can be saved and such an efficient cooling of the process fluid during the compression process in the turbo compressor expediently increases the efficiency. Due to the saved flow paths, which would conventionally cover the process fluid through other cooling devices, the flow loss of the entire assembly also decreases.
  • An advantageous development of the method according to the invention provides that a temperature of the gaseous process fluid is measured before or after entry into the turbocompressor and a regulation of the amount of inflow of the liquid process fluid to be injected in dependence on the measured temperature.
  • the measurement of the temperature can take place both before and after the entry into the turbocompressor and both temperature measurements can be based on a corresponding control for controlling the inflow.
  • FIG. 1 schematically shows in simplified form a turbocompressor TCP according to the invention, together with a simplified representation of a system plan showing the interaction of the turbo compressor TCP with other modules in the context of the inventive method for liquefying a gaseous process fluid PFL, in particular of natural gas NGS.
  • the process fluid PFL flows through the assembly along a flow path GPT.
  • the turbocompressor TCP comprises a rotor ROT with rotating flow guide elements RFG, which extends along an axis X. Surrounding substantially the rotor ROT rotatable about the axis X, the turbo-compressor TCP comprises a housing CAS. Static flow guiding elements SFG are arranged in the housing, which together with the rotatable flow guiding elements RFG define a main flow path MPT of the flow path GPT. At the entrance of the turbocompressor TCP, the stationary flow guide elements SFG also comprise an intake flange SFL, the flow path having an intake passage SCH upstream of the intake flange SFL.
  • the process fluid PFL enters the turbocompressor TCP through the intake flange SFL along a flow direction FTD and is guided along the main flow path MPT alternately by static flow guide SFG and rotating flow guide RFG up to a collection space COL and then out by means of a discharge flange EFL on the turbo-compressor TCP.
  • the turbo compressor TCP is designed as a radial turbo compressor and accordingly has from axially to radially deflecting wheels IMP.
  • the rotating impellers IMP are followed in the direction of the flow direction FTD along the main flow path MPT by a return stage RFS, which is provided in each case between two impellers IMP.
  • the turbocompressor TCP is, for example, according to FIG. 1 integral part of a procedure.
  • Liquid process fluid PFL here liquid natural gas NGS
  • a container TNK Under the influence of the higher outside temperature, parts of this process fluid PFL evaporate and leave the container TNK as a so-called boil-off gas BOG.
  • This gaseous process fluid PFL is sucked in by the turbo-compressor TCO, the temperature of the inflow being determined by means of a first temperature measuring point TPF1, TPF. Behind the outlet flange EFL of the turbo-compressor TCP, the temperature is also measured by means of a second temperature measuring point TPF2, TPF.
  • the thus compressed process fluid PFL is fed to a cooler COL for supplying heat energy Q.
  • the cooled process fluid PFL then reaches an expansion tank EDR in which a liquid phase of the process fluid PFL precipitates as liquid process fluid PFL.
  • a part of the process fluid PFL flowing into the expansion tank EDR leaves the expansion tank EDR as the gaseous process fluid GPFL and is optionally subjected to further treatments.
  • the liquid process fluid PFL is conveyed by means of a pump PMP back into the container TNK.
  • the turbocompressor TCP has injection devices INJ which serve for the injection of liquid process fluid PFL.
  • the process fluid PFL is injected by means of the injectors INJ in the liquid phase directly into the flow path GPT without special further precautions, such as a separate mixing container or the like.
  • the injection device INJ consists of at least one nozzle NZL and at least one supply line CCH.
  • injectors are formed in the region of their confluence with the main flow path MPT of the turbo-compressor TCP as throttle or nozzle, so that there arises a pressure loss under relaxation of the process fluid PFL from the injection device.
  • the Joule-Thomson effect caused thereby provides cooling in the turbo-compressor TCP depending on the type of process fluid PFL.
  • the amount of the inflow COS of the process fluid PFL by means of the injector INJ is controlled in total by means of a control valve CVV, wherein a central control CTL controls the position of the control valve CVV in dependence on the temperature measurements at the temperature measuring points TPF1, TPF2, TPF.
  • the regulation of the position of the control valve CVV can also be based on only a single temperature measurement TPF, which take place before or after the compression of the process fluid PFL by means of the turbo-compressor TCP can.
  • TPF temperature measurement
  • measuring points for pressure P and mass flow F are provided, which can advantageously serve to support the control CTL.
  • FIG. 2 schematically shows a flow diagram of a compressor arrangement CPA according to the invention with two turbo-compressors TCP for carrying out the method according to the invention.
  • the two turbo compressors TCP are arranged and are driven by a drive M.
  • a turbo-compressor TCP is single-flow equipped with a mecanicsleitapparat IGV and the other turbo-compressor TCP is double-flow, in the embodiment, the process fluid PFL from a container, not shown TNK as boil-off gas BOG the mecanicsleitapprat IGV flowing through first the single-flow turbocompressor TCP along a flows through the inner flow path PTI and then flows through a first tide of the twin-turbocompressor TCP (left side) and then the second tide of the twin-turbocompressor TCP to then be subjected to further process steps APS in a manner not shown.
  • a recirculation line BYP with a surge limit control valve ASV is provided before the supply to the other process steps APS as Mauströmungspfad SPT to the main flow path through the turbo compressor TCP, in the case of opening the surge control valve ASV at least a portion of the process fluid PFL back to the inlet of the first single-flow turbocompressor TCP to lead.
  • a corresponding secondary flow path SPT can be provided as the recirculation line BYP for any main flow path for compressing the process fluid PFL.
  • the two turbocompressors TCP each have a housing CAS, which encloses an inner flow path PTI and / or defines it as an outer boundary.
  • the actual inner flow path PTI is defined by stationary flow guide elements SFG and rotating flow guide elements RFG.
  • the FIG. 2 shows an injection device according to the invention INJ both to the single-flow downstream turbo-compressor TCP and before the supply of the process fluid PFL to the downstream turbo-compressor TCP in the intake passage (SCH) injection molding arranged and / or in the suction flange SFL and in the region of the bypass flow path SPT and in the recirculation line BYP.
  • the injection device INJ is provided here in the recirculation line BYP behind the surge limit control valve ASV.
  • the inflow of liquid process fluid PFL is regulated by means of control valves CVV.
  • a pressure adjusting device BOS each so that the liquid process fluid PFL can be efficiently injected into the respective flow path with the required pressure.
  • the injector INJ before entering the inlet guide IGV of the single-flow downstream turbo-compressor TCP may be 7 bar
  • the pressure for the injectors INJ in the single-flow turbo-compressor TCP may be 70 bar. Comparable to the example of FIG. 1 is also in the FIG.
  • FIGS. 3, 4 . 5, 6 . 7 and 8 each show different configurations of injectors INJ that inject process fluid PFL into the inner flow path PTI.
  • the FIGS. 3 and 4 show here an injection device INJ, the orifices ORF in the region of pressure sides PRS of vanes VNS a return stage RST in the region of an intermediate position IPS between two adjacent rotating flow guide RFG have.
  • the guide vanes VNS each have a pressure side PRS and a suction side SCS, an inlet edge LDE and an outlet edge TRE.
  • the liquid process fluid PFL is supplied.
  • the liquid process fluid PFL by means of a mouth opening ORF, preferably arranged in a trough RZS in the surface of a boundary contour LCT of the annulus of the feedback stage RST are supplied.
  • the orifice ORF is formed as a flat jet nozzle FJO, so that only a slight change in the flow pattern takes place through the injection.
  • Such injection in the region of the boundary contour LCT can take place both between the guide vanes VNS in the flow channels delimited by the guide vanes VNS in the circumferential direction, as well as upstream or downstream.
  • an arrangement of such injectors can take place both on the radially outer boundary contour LCT and on the radially inner boundary contour LCT of the inner flow path PTI.
  • Another way to arrange the injector INJ on the vanes VNS is to provide the injection ports ORF at the trailing edge TRE of the vanes VNS, as in FIGS FIGS. 7 and 8 shown.
  • FIG. 9 shows a turbocompressor TCP of a compressor assembly according to the invention with a housing CAS in a cross section, showing a short section of the inner flow path PTI.
  • a collector CLL and a drain DRN are arranged for temporarily storing or discharging separated liquid.
  • the outflow DRN is advantageously connected to a location of lower pressure level, wherein preferably a flow control valve VCL produces this connection only when required.
  • This need can either be determined automatically, for example by means of a metrological detection of a sufficient amount of liquid in the collector CLL or a sight glass GGL can indicate to the operator the presence of an appropriate amount of liquid which then manually opens the drain control valve VCL, if necessary, so that the failed liquid can be sucked to a location of lower pressure level.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP17185707.1A 2017-08-10 2017-08-10 Turbocompresseur avec injection de gaz de compression liquéfié dans l'écoulement Withdrawn EP3441621A1 (fr)

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EP17185707.1A EP3441621A1 (fr) 2017-08-10 2017-08-10 Turbocompresseur avec injection de gaz de compression liquéfié dans l'écoulement

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112032060A (zh) * 2020-08-07 2020-12-04 安徽埃斯克制泵有限公司 一种内循环冷却式多级离心泵
EP4170186A1 (fr) * 2021-10-21 2023-04-26 Siemens Energy Global GmbH & Co. KG Compresseur, en particulier compresseur radial

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE332846C (de) * 1919-11-16 1921-02-11 Escher Wyss Maschf Ag Verfahren zum Verdichten von Dampf in mehrstufigen Kreiselverdichtern
GB580458A (en) * 1943-06-22 1946-09-09 Escher Wyss Maschf Ag Improvements in or relating to combined axial-flow and centrifugal compressors
US2786626A (en) * 1952-08-07 1957-03-26 Gulf Oil Corp Process for the compression of gases
JP2000120595A (ja) * 1998-10-20 2000-04-25 Hitachi Ltd 冷却液噴射ノズル付き遠心圧縮機
WO2005068847A1 (fr) * 2004-01-16 2005-07-28 Cryostar Sas Compresseur
WO2007137959A1 (fr) 2006-05-26 2007-12-06 Siemens Aktiengesellschaft Turbocompresseur à plusieurs étages
DE112006001149T5 (de) * 2005-05-02 2008-05-15 Vast Power Portfolio, LLC, Elkhart Verfahren und Vorrichtung für die Nasskompression
JP2009221966A (ja) * 2008-03-17 2009-10-01 Tokyo Electric Power Co Inc:The 多段圧縮機、圧縮機、及び冷凍機
WO2016020282A2 (fr) 2014-08-06 2016-02-11 Siemens Aktiengesellschaft Procédé et installation de traitement de gaz naturel

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE332846C (de) * 1919-11-16 1921-02-11 Escher Wyss Maschf Ag Verfahren zum Verdichten von Dampf in mehrstufigen Kreiselverdichtern
GB580458A (en) * 1943-06-22 1946-09-09 Escher Wyss Maschf Ag Improvements in or relating to combined axial-flow and centrifugal compressors
US2786626A (en) * 1952-08-07 1957-03-26 Gulf Oil Corp Process for the compression of gases
JP2000120595A (ja) * 1998-10-20 2000-04-25 Hitachi Ltd 冷却液噴射ノズル付き遠心圧縮機
WO2005068847A1 (fr) * 2004-01-16 2005-07-28 Cryostar Sas Compresseur
DE112006001149T5 (de) * 2005-05-02 2008-05-15 Vast Power Portfolio, LLC, Elkhart Verfahren und Vorrichtung für die Nasskompression
WO2007137959A1 (fr) 2006-05-26 2007-12-06 Siemens Aktiengesellschaft Turbocompresseur à plusieurs étages
JP2009221966A (ja) * 2008-03-17 2009-10-01 Tokyo Electric Power Co Inc:The 多段圧縮機、圧縮機、及び冷凍機
WO2016020282A2 (fr) 2014-08-06 2016-02-11 Siemens Aktiengesellschaft Procédé et installation de traitement de gaz naturel

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112032060A (zh) * 2020-08-07 2020-12-04 安徽埃斯克制泵有限公司 一种内循环冷却式多级离心泵
EP4170186A1 (fr) * 2021-10-21 2023-04-26 Siemens Energy Global GmbH & Co. KG Compresseur, en particulier compresseur radial
WO2023066585A1 (fr) * 2021-10-21 2023-04-27 Siemens Energy Global GmbH & Co. KG Compresseur, en particulier compresseur radial

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