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WO2014191312A1 - Procédé de fonctionnement d'un compresseur et système équipé d'un compresseur - Google Patents

Procédé de fonctionnement d'un compresseur et système équipé d'un compresseur Download PDF

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Publication number
WO2014191312A1
WO2014191312A1 PCT/EP2014/060660 EP2014060660W WO2014191312A1 WO 2014191312 A1 WO2014191312 A1 WO 2014191312A1 EP 2014060660 W EP2014060660 W EP 2014060660W WO 2014191312 A1 WO2014191312 A1 WO 2014191312A1
Authority
WO
WIPO (PCT)
Prior art keywords
bypass
flow
bfl
compressor
line
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.)
Ceased
Application number
PCT/EP2014/060660
Other languages
German (de)
English (en)
Inventor
Georg Winkes
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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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 Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to US14/893,185 priority Critical patent/US20160102671A1/en
Priority to CN201480031294.2A priority patent/CN105829730B/zh
Priority to EP14728117.4A priority patent/EP3004650A1/fr
Publication of WO2014191312A1 publication Critical patent/WO2014191312A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F04D27/0215—Arrangements therefor, e.g. bleed or by-pass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F04D27/0223—Control schemes therefor
    • 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

Definitions

  • the invention relates to a method for operating a compressor with the following steps:
  • the invention also relates to an arrangement with which the method is feasible.
  • Compressors in particular turbocompressors usually require a bypass line, so that when starting or in operating states with little promotion always a sufficient flow or mass flow or flow or volume flow can be promoted through the compressor in order not to fall below the surge limit.
  • the surge limit - a limit line in the map of the compressor - can only be approximated to a certain safety distance by operating the compressor.
  • a surge limit controller determines a critical proximity to the surge limit in the characteristic map of the compressor and causes it to react accordingly.
  • the opening of a bypass valve in order to relax the gas at an elevated pressure in an outlet line of the compressor, so that it can be fed back on the suction side of the compressor.
  • the compressor in this case usually means a compression unit, which promotes a process gas flow to an elevated pressure.
  • the compressor is also often referred to as a process stage.
  • cooled bypass lines Basically, a distinction is made between cooled bypass lines and uncooled bypass lines.
  • the gas is withdrawn either directly after the last stage of the compressor - before an eventually existing aftercooler - or downstream of a cooler located behind the last stage - so that it is either an uncooled or cooled bypass.
  • a cooler only for the bypass line, so that the outlet of the compressor is uncooled in normal operation with closed bypass line.
  • the uncooled bypass is mainly used on media with a pronounced Joule-Thomson effect. By throttling in the bypass valve, the temperature of the medium decreases, so that additional cooling of the blown amount of these gases is often not required. The amount is dependent on the final pressure.
  • the suction temperature of the compressor changes regularly when a bypass valve is opened.
  • JP 2003 287 299 A and US 2011/0048046 A1 already disclose turbocompressors with bypasses, which in the case of pumping can be used to leave the critical operating state.
  • the invention has set itself the task of eliminating the above-described problems with the surge limit control and the opening of the bypass valve and thus to give the compressor a higher availability.
  • the solution according to the invention provides a method of the aforementioned type with the additional characterizing features of claim 1.
  • an arrangement according to the independent device claim is proposed.
  • a compressor according to the invention is also often referred to as a process stage, which process stage regularly has several stages or wheels. While the invention is preferred for use in turbocompressors, in principle a use in reciprocating engines is also possible. The invention enables rapid control of the thermodynamic parameters of the
  • the first bypass flow, the second bypass flow and a mixture of the two bypass flows are controllable according to the invention, so that an advantageous condition for the intake condition of the compressor. te temperature can be set. In this way, in addition to the avoidance of pumping, an efficiency optimization of the overall system can take place with the aid of the surge limit controller. Since a bypass station according to the invention regularly by means of valves the size of the first bypass stream, the second
  • An advantageous development of the invention provides that the operating parameters of the compressor for controlling the supply of the first bypass current and / or the second
  • Bypass flow or the temperature of the second bypass flow or the temperature of a mixture of the first bypass flow and the second bypass flow or the mass flow of the first bypass flow or the mass flow of the second bypass flow or the chemical composition of the intake flow or the chemical composition of the first bypass flow or the chemical composition of the second Bypass current or a speed of the compressor or a pressure ratio or a pressure ratio of the compressor can be.
  • a combination of the aforementioned parameters is the basis for the control of the supply line of the first bypass flow or the second bypass flow.
  • the chemical composition of the bypass streams are particularly useful as a control basis, because the outlet stream from the compressor after cooling is often thermodynamically in the two-phase region and can fail with a corresponding cooling liquid components, so that the outlet stream may have a different chemical composition than the suction flow of the compressor. This difference can have a significant influence on the characteristic map of the compressor when the bypass flow is fed into the intake flow. Is it the process medium or intake, for example moist air or humid carbon dioxide can cause the
  • Bypass flow and / or the second bypass flow configured such that the intake flow into the inlet of the compressor after supplying the first bypass flow and / or the second bypass flow approaches a first set temperature.
  • Bypass flow or a mixture thereof and a thermodynamic in the control of the resulting temperature in the inlet of the compressor Furthermore, it is conceivable for the first bypass flow and the second bypass flow or a mixture of the two bypass flows to be released before entry into the intake flow by means of a valve or another throttle and the resulting Joule-Thomson effect from the control algorithm of the control is taken into account as a temperature change, so that temperature measurements upstream of this expansion valve or of this expansion throttle are sufficient to determine the temperature of the supply line of the bypass flow into the intake flow with sufficient accuracy.
  • a regulation of the process fluid is stored in the control.
  • the mass flow of the first bypass flow and / or the second bypass flow and / or a mixture of the two bypass flows - for example by means of a differential pressure measurement via a throttle - and to forward this measured value to the control of the bypass station, so that the sum of bypass streams fed into the intake stream as a function of their temperature and composition leads to the desired thermodynamics, in particular to the desired temperature of the intake stream entering the compressor.
  • the control bypass valves it is the task of the control bypass valves to adjust the first bypass flow, the second bypass flow and / or a mixture of the two
  • thermodynamic parameters Composition of the intake flow, wherein the real gas factor is dependent on the composition of the intake flow, the pressure of the intake flow and the temperature of the intake flow.
  • the corresponding equations of state for determining these thermodynamic parameters may preferably be implemented in the controller according to the invention.
  • FIG. 1 shows a basic schematic representation of a flowchart of an arrangement according to the invention or a method, in each case a more specific exemplary embodiment of the invention as a schematic flow diagram, a simplified schematic representation of the logic of the controller for controlling the
  • FIGS. 1 to 5 each show a schematic flow diagram of an arrangement according to the invention for illustration of the invention inventive method.
  • FIG. 1 is somewhat more general in the description of the invention.
  • FIG. 6 shows a logic diagram for the exemplary illustration of the method according to the invention for the example of an arrangement according to FIG. 2.
  • FIG. 1 shows an inventive arrangement with a compressor CO, which is shown here by way of example with a stage STI, which compresses a suction flow MF to an outlet flow VF, wherein the compressor CO is cooled by means of an intermediate cooling IC.
  • a cooler COL On the outlet side of the compressor CO is a cooler COL, which cools the compressed outlet flow VF or a partial flow thereof.
  • FIG. 1 shows two different alternatives ALT1, ALT2, how the compressed fluid of the outlet flow is to be supplied to any subsequent consumer. In the first alternative ALTl, any consumer CON receives exclusively cooled outlet flow VF, the second alternative ALT2 providing that the consumer CON receives uncooled outlet flow VF.
  • a flap valve CV is provided on the output side prior to the connection of a consumer CON, so that the arrangement can be disconnected by the consumer, for example when it is at a standstill.
  • FIG. 1 and FIGS. 2-5 each have a bypass station BST, which taps off substreams of the compressed outlet flow VF from the outlet EX of the compressor CO.
  • An outlet line EXL of the compressor CO has the radiator COL.
  • Upstream of the cooler COL is the
  • Bypassstation a first bypass flow BFl supplied by means of a first bypass line BLl. Downstream of the radiator COL of the bypass station BS, a second bypass stream BF2 means a second bypass line BL2 supplied.
  • the bypass station BST controls the amount of the bypass flows BF2, BF2 depending on operating parameters of the compressor and passes the first bypass flow BFl and the second bypass flow BF2 - here as a mixture through a third bypass line BL3 as a mixed third bypass flow BF3 upstream of the inlet IN of the compressor CO the Intake flow MF too.
  • a controller CU controls the bypass station BST in such a way that, depending on operating parameters of the compressor CO, a specific bypass flow or supply line of the first bypass flow BF1 and of the second bypass flow BF2 takes place in each case.
  • the main objective of the control is to prevent the state of pumping the compressor CO.
  • the controller can also serve to improve the efficiency.
  • the compressor CO there has an inlet guide IGV in the region of the inlet IN.
  • the inlet guide IGV allows the adjustment of inlet guide vanes such that a certain inflow angle l of the intake flow MF takes place in the first stage STl of the compressor CO.
  • the compressor CO has two intermediate cooling circuits IC1, IC2, which are arranged between the first stage ST1 and a second stage ST2 or the second stage ST2 and a third stage ST3. Downstream of the third stage ST3 is the outlet EX of the compressor CO, where the compressed outlet stream VF is introduced into an outlet line EXL. Upstream of the following cooler COL is possibly.
  • a second bypass flow BF2 is fed by means of a second bypass line BL2 to a surge limit valve PGV or to the second bypass valve BV2 of the bypass valves BV, which controls the supply of this cold bypass flow to a mixer MX, in which the two bypass flows BF1, BF2 with each other be mixed.
  • a surge limit controller ASC of a control unit CU of the bypass station BST signals a ratio calculator PCU the specifications for controlling the supply line of the bypass currents BF1, BF2, which ratio computer PCU controls the bypass valves BV accordingly.
  • Control of the supply line takes place in dependence on operating parameters of the compressor CO in a broader sense.
  • the temperatures are measured by means of temperature measuring points, wherein the temperature of the intake flow by means of a first temperature measuring point TTl, the temperature of the outlet flow VF by means of a second temperature measuring point TT2, the temperature of the third bypass flow BF3 by means of a third temperature measuring point TT3 and optionally the temperature downstream of Cooler COL is measured by means of a fourth temperature measuring point TT4.
  • the pressure of the intake flow is determined by means of a first pressure measuring point PT1 and the pressure of the outlet flow VF is determined by means of a second pressure measuring point PT2.
  • FIG. 3 shows that the first bypass flow BF1 and the second bypass flow BV2 are fed directly to a first bypass valve BV2 designed as a 3-way proportional valve, which is directly controlled by the ratio calculator PCU.
  • the total amount of the resulting third bypass flow BV3 is set by the second bypass valve BV2, which is controlled by the surge limit regulator ASC.
  • the 3-way proportional valve or mixing valve builds in this arrangement no significant pressure and can therefore be designed inexpensively in flap construction.
  • a third non-return valve CV3 is downstream
  • the first bypass valve BV1 would be provided in the second bypass line BL2, so that the outlet flow VF does not flow to the pressure-side process while bypassing the cooler COL through the first bypass valve BV1.
  • the outlet flow VF in front of the radiator COL is at a slightly higher pressure than downstream of the radiator, so that when the first bypass valve BV1 is partially open, still some of the warm first bypass flow enters the first bypass line BL1 .
  • this effect can be additionally supported by selecting a smaller cross-section for the part of the second bypass line BL2 between the tap behind the cooler COL and the junction of the warmer first bypass flow BV1, or by installing a screen.
  • FIG. 5 A further modification of the system is shown in FIG. 5, in which a first orifice TH1 causes a certain back pressure in the second bypass line BL2.
  • the measurement of a differential pressure PDT via the first orifice TH1 makes it possible for the ratio calculator PCU to set the first bypass valve BV1, which is also designed here as a mixing valve, such that at the third temperature measuring point TT3 in the third bypass line BL3 downstream of the second
  • FIG. 6 shows the mode of operation of the controller CU with the ratio calculator PCU and the surge limit regulator ASC.
  • the diagram shown there refers to the interconnection according to the FIG. 2.
  • a first module IZHGV calculates the resulting first temperature THl of the isenthalpic state change in the first bypass valve BV1.
  • a second module IZPGV of the ratio calculator calculates from the fourth temperature TT4, as a result of the second pressure measurement PT2 and the result of the first pressure measurement PT1, a second temperature TP as a result of the relaxation of the second bypass flow as a consequence of an isenthalpic state change in the second bypass valve BV2.
  • the proportion a is multiplied by the signal X of the surge limit controller ASC for the position of the second bypass valve BV2.
  • the difference of the proportion a to 1 is multiplied by the signal X of the surge limit regulator ASC and used as a setpoint for the opening of the first bypass valve BVl.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

L'invention concerne un procédé de fonctionnement d'un compresseur (CO), et un système correspondant. Pour pallier les problèmes de l'art antérieur, l'invention propose un procédé comprenant les étapes consistant à : amener un flux d'aspiration (MF) à une entrée (IN) du compresseur (CO), compresser le flux d'aspiration (MF) au moyen du compresseur (CO) pour obtenir un flux de sortie (VF), introduire au moins un premier flux partiel du flux de sortie (FM) dans une station de dérivation (BS) en tant que premier flux de dérivation (BF1), commander l'amenée du premier flux de dérivation (BF1) de la station de dérivation (BS) à l'entrée (IN) du compresseur (CO) en fonction de paramètres de fonctionnement du compresseur (CO). L'invention est caractérisée par les étapes consistant à : refroidir au moins un deuxième flux partiel du flux d'aspiration (MF), commander l'amenée du deuxième flux partiel refroidi, en tant que deuxième flux de dérivation (BF2), à l'entrée (IN) du compresseur (CO) en fonction de paramètres de fonctionnement du compresseur (CO).
PCT/EP2014/060660 2013-05-29 2014-05-23 Procédé de fonctionnement d'un compresseur et système équipé d'un compresseur Ceased WO2014191312A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US14/893,185 US20160102671A1 (en) 2013-05-29 2014-05-23 Method for operating a compressor, and arrangement with a compressor
CN201480031294.2A CN105829730B (zh) 2013-05-29 2014-05-23 用于运行压缩机的方法和具有压缩机的装置
EP14728117.4A EP3004650A1 (fr) 2013-05-29 2014-05-23 Procédé de fonctionnement d'un compresseur et système équipé d'un compresseur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013210067.1 2013-05-29
DE102013210067 2013-05-29

Publications (1)

Publication Number Publication Date
WO2014191312A1 true WO2014191312A1 (fr) 2014-12-04

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PCT/EP2014/060660 Ceased WO2014191312A1 (fr) 2013-05-29 2014-05-23 Procédé de fonctionnement d'un compresseur et système équipé d'un compresseur

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Country Link
US (1) US20160102671A1 (fr)
EP (1) EP3004650A1 (fr)
CN (1) CN105829730B (fr)
WO (1) WO2014191312A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITUB20151979A1 (it) * 2015-07-09 2017-01-09 Nuovo Pignone Tecnologie Srl Sistema di compressore con un controllo della temperatura del gas all'ingresso della linea di anti-pompaggio e relativo metodo
ITUB20152030A1 (it) * 2015-07-09 2017-01-09 Nuovo Pignone Tecnologie Srl Sistema di compressore con una disposizione di raffreddamento tra la valvola di anti-pompaggio ed il lato di aspirazione del compressore, e relativo metodo
WO2017040807A1 (fr) * 2015-09-02 2017-03-09 Woodward, Inc. Système anti-pompage de turbomachine
EP3594506A1 (fr) 2018-07-12 2020-01-15 Siemens Aktiengesellschaft Bague de contour pour un compresseur
US12454959B2 (en) 2020-05-06 2025-10-28 Karl Morgenbesser Actuating device, having two valves which are connected in parallel, for the sensitive and full range regulation of any volumetric flow

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4921399A (en) * 1989-02-03 1990-05-01 Phillips Petroleum Company Gas pipeline temperature control
WO2009050175A1 (fr) * 2007-10-17 2009-04-23 Shell Internationale Research Maatschappij B.V. Procédé et appareil de commande d'un compresseur frigorifique et utilisation de celui-ci dans un procédé de refroidissement d'un courant d'hydrocarbures
WO2012007553A1 (fr) * 2010-07-14 2012-01-19 Statoil Asa Procédé et appareil de commande d'un compresseur et de surveillance de ses performances sur la base d'une composition
WO2012013530A1 (fr) * 2010-07-29 2012-02-02 Siemens Aktiengesellschaft Procédé pour faire fonctionner un compresseur

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7069733B2 (en) * 2003-07-30 2006-07-04 Air Products And Chemicals, Inc. Utilization of bogdown of single-shaft gas turbines to minimize relief flows in baseload LNG plants
WO2012132062A1 (fr) * 2011-03-31 2012-10-04 三菱重工業株式会社 Procédé de commande d'un compresseur à gaz, et turbine à gaz pourvue du compresseur à gaz

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4921399A (en) * 1989-02-03 1990-05-01 Phillips Petroleum Company Gas pipeline temperature control
WO2009050175A1 (fr) * 2007-10-17 2009-04-23 Shell Internationale Research Maatschappij B.V. Procédé et appareil de commande d'un compresseur frigorifique et utilisation de celui-ci dans un procédé de refroidissement d'un courant d'hydrocarbures
WO2012007553A1 (fr) * 2010-07-14 2012-01-19 Statoil Asa Procédé et appareil de commande d'un compresseur et de surveillance de ses performances sur la base d'une composition
WO2012013530A1 (fr) * 2010-07-29 2012-02-02 Siemens Aktiengesellschaft Procédé pour faire fonctionner un compresseur

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITUB20151979A1 (it) * 2015-07-09 2017-01-09 Nuovo Pignone Tecnologie Srl Sistema di compressore con un controllo della temperatura del gas all'ingresso della linea di anti-pompaggio e relativo metodo
ITUB20152030A1 (it) * 2015-07-09 2017-01-09 Nuovo Pignone Tecnologie Srl Sistema di compressore con una disposizione di raffreddamento tra la valvola di anti-pompaggio ed il lato di aspirazione del compressore, e relativo metodo
WO2017005842A1 (fr) * 2015-07-09 2017-01-12 Nuovo Pignone Tecnologie Srl Système de compresseur avec un arrangement de refroidissement entre la soupape anti-surpression et le côté d'aspiration du compresseur, et procédé associé
WO2017005843A3 (fr) * 2015-07-09 2017-05-26 Nuovo Pignone Tecnologie Srl Système de compresseur avec régulation de la température du gaz au niveau de l'admission de la conduite anti-pompage, et procédé approprié
US10907642B2 (en) 2015-07-09 2021-02-02 Nuovo Pignone Srl Compressor system with a gas temperature control at the inlet of the anti-surge line and relevant method
US10995762B2 (en) 2015-07-09 2021-05-04 Nuovo Pignone Srl Compressor system with a cooling arrangement between the anti-surge valve and the compressor suction side and relevant method
EP4421327A3 (fr) * 2015-07-09 2024-11-20 Nuovo Pignone Tecnologie SrL Système de compresseur avec un agencement de refroidissement entre la soupape anti-surpression et le côté d'aspiration du compresseur et procédé associé
WO2017040807A1 (fr) * 2015-09-02 2017-03-09 Woodward, Inc. Système anti-pompage de turbomachine
CN108291553A (zh) * 2015-09-02 2018-07-17 伍德沃德有限公司 涡轮机械防喘振系统
EP3594506A1 (fr) 2018-07-12 2020-01-15 Siemens Aktiengesellschaft Bague de contour pour un compresseur
WO2020011471A1 (fr) 2018-07-12 2020-01-16 Siemens Aktiengesellschaft Turbomachine radiale et procédé pour son fonctionnement
US12454959B2 (en) 2020-05-06 2025-10-28 Karl Morgenbesser Actuating device, having two valves which are connected in parallel, for the sensitive and full range regulation of any volumetric flow

Also Published As

Publication number Publication date
EP3004650A1 (fr) 2016-04-13
US20160102671A1 (en) 2016-04-14
CN105829730A (zh) 2016-08-03
CN105829730B (zh) 2018-09-21

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