EP3167197B1 - Verfahren zur druck- und temperaturreglung eines fluids in einer serie von kryogenen verdichtern - Google Patents

Verfahren zur druck- und temperaturreglung eines fluids in einer serie von kryogenen verdichtern Download PDF

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Publication number
EP3167197B1
EP3167197B1 EP15733630.6A EP15733630A EP3167197B1 EP 3167197 B1 EP3167197 B1 EP 3167197B1 EP 15733630 A EP15733630 A EP 15733630A EP 3167197 B1 EP3167197 B1 EP 3167197B1
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soll
compressor
rotational speed
red
actual
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German (de)
English (en)
French (fr)
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EP3167197A1 (de
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Can Üresin
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Linde GmbH
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Linde GmbH
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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
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/006—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by influencing fluid temperatures
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/001—Pumps adapted for conveying materials or for handling specific elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/001—Pumps adapted for conveying materials or for handling specific elastic fluids
    • F04D23/003—Pumps adapted for conveying materials or for handling specific elastic fluids of radial-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/001—Pumps adapted for conveying materials or for handling specific elastic fluids
    • F04D23/005—Pumps adapted for conveying materials or for handling specific elastic fluids of axial-flow type
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • 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
    • F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
    • 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
    • F04D27/004—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying driving speed
    • 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
    • F04D27/0261—Surge control by varying driving speed
    • 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
    • F04D27/0276—Surge control by influencing fluid temperature
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/27—Problems to be solved characterised by the stop of the refrigeration cycle
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/17—Speeds
    • F25B2700/171—Speeds of the compressor
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor

Definitions

  • the invention relates to a method for controlling the pressure and temperature of a fluid, in particular helium, in particular when starting up a cryogenic cooling system, or during the cooling process (cool-down) in a series of cryogenic compressors according to claim 1.
  • compressors Radial or turbo compressors (hereafter referred to as compressors) in series are used to overcome or create large pressure differences (of the order of 1 bar).
  • Such compressors are known from the prior art and usually have a shaft with at least one impeller (compressor wheel) or directly connected to the shaft blades, with which the fluid is compressed during rotation of the shaft.
  • the speed of the compressor means the number of complete rotations (360 °) of the shaft about the shaft axis per unit of time.
  • Compressor such as Turbo compressors, are divided in particular in radial and axial compressors. In the radial compressor, the fluid flows axially to the shaft and is deflected in the radial direction to the outside. In the case of the axial compressor, on the other hand, the fluid to be compressed flows through the compressor in a direction parallel to the shaft.
  • the inlet pressure of the fluid to a first compressor that is, the pressure at an input of the most upstream compressor of the series, regulated.
  • the entry states are also established at the respective inlet of the other compressor arranged downstream of the first compressor.
  • An entry condition is determined by the pressure and the temperature at the inlet of the respective compressor.
  • the respective entry state on a compressor corresponds in each case to the state of Fluids at the output of the previous compressor.
  • cryogenic systems ie cooling systems that are designed for very low temperatures (1.5K-100K), especially for temperatures between 1.5K and 2.2K
  • the desired saturation temperature for the cold liquid is controlled by regulating the inlet pressure the suction side, that is the side from which the compressors suck the gas phase (vapor).
  • the pressure at the outlet of the series and the temperature of the fluid flowing through the compressor is increased (polytropic compression process).
  • so-called reduced variables are used, such as the reduced mass flow through the compressor or the reduced speed for the compressor in the control.
  • the design values are the operating conditions of a compressor where the compressor operates with the greatest efficiency (most economically).
  • Compressors have design values, for example, with regard to the speed, the temperature and the pressure above the respective compressor. The goal is to operate the compressors of the series close to their design points.
  • the fluid on the suction side of the compressor series is cooled down very far (for example, from 300K to 4K). This can be done at atmospheric pressure, ie 1 bar. Lower temperatures are then realized with suppression. This process is also called cool-down.
  • the pressure reduction on the suction side of the system is achieved by commissioning the compressor series. In particular, it serves to further lower the temperature above the fluid (pump-down).
  • the temperature increase of the fluid due to the compression process when flowing through the compressor series, for example, three to four compressors is in the range of about 4K to 23K.
  • a heat exchanger arranged downstream of the compressor series, which is used for cooling a parallel mass flow is designed for example at 23K. However, if this heat exchanger is flowed through by the 4K cold mass flow from the compressor series for a long time, the parallel mass flow in the heat exchanger is cooled very far. However, since this parallel mass flow downstream is still being expanded by a turbine, condensation of the parallel mass flow within the turbine could occur. To avoid this condensation, the turbine is switched off, whereby the cooling process is temporarily interrupted. These operating conditions are to be avoided and are referred to as trip the system.
  • the compression of the fluid in the compressor series would have to be interrupted again and again, so that the temperature in the compressors is not too high.
  • the temperature is included in the reduced control quantities, such as the reduced speed, i.e., an increase in the temperature at the compressor causes the reduced speed to increase. It would therefore be desirable to have a temperature control for the entry of the compressor series in particular for the cool-down or the pump-down phase, which ensures an uninterrupted pump-down with simultaneous cool-down.
  • k is a proportionality factor.
  • the priority value determines which of the two values, the proportional value or the smallest of the rotational speed indices, is used to regulate the compressor series. If the priority value corresponds, for example, to the proportional value, then the priority of the regulation lies on the pressure regulation (thus in particular the pump-down), since the proportional value particularly reflects the pressure difference as a control value. If the priority value corresponds to the lowest speed index, then the priority of the control is in particular the regulation of the inlet temperature at the first compressor. In this scheme, the speeds of the compressor should not increase.
  • the respective inlet temperature is detected, in particular at the input of each compressor of the series.
  • the pump-down process can take place parallel to the cool-down.
  • the temperature no longer drops as soon as the cooling-down process is ended.
  • the temperature of the fluid at the outlet is already regulated in a temperature range, which are favorable for downstream components, such as heat exchangers.
  • Another advantage is that overspeeds are avoided in all compressors, since in particular a reduction in the inlet temperature pulls lower speeds. Moreover, it is advantageous in the method according to the invention that the pump-down process without interruption, which would be necessary for example due to excessive speeds of the compressors, can take place.
  • the influence of unwanted heat input through the environment, ie from the outside, can be minimized. Furthermore, it is particularly advantageous that during pump-down operation, the desired inlet temperature can be regulated transiently and automatically.
  • the inventive method is especially suitable for temperature control in supercritical helium pumps.
  • the priority value influences the control such that, if the smallest speed index of all compressors is smaller than the proportional value, the actual inlet temperature is lowered, in particular by stepwise or continuous lowering of the determined target inlet temperature, until the proportional value is smaller than the smallest speed index is, and that in particular the actual speed of the respective compressor is not increased as long as the smallest speed index is smaller than the proportional value.
  • the proportional value is used in particular for controlling the actual input pressure.
  • the actual speed of each compressor from a reduced actual speed and the target speed of each compressor is determined from a reduced target speed, wherein the reduced actual speed of the actual speed and an actual temperature is determined at the input of the respective compressor, and wherein the reduced target speed is determined from the desired speed and the actual temperature at the input of the respective compressor.
  • an integral value is determined from the priority value, the integral value being used in particular for determining the reduced setpoint rotational speed.
  • an actual total pressure ratio is determined, the actual total pressure ratio being equal to the quotient of an actual discharge pressure, which corresponds to the pressure at an outlet of the compressor located farthest downstream, and the actual inlet pressure of the first compressor ,
  • a capacitance factor is determined from the actual total pressure ratio and a proportional integral value determined from the priority value and the integral value, wherein the reduced target rotational speed for each compressor is determined as a function value of a control function assigned to the respective compressor in particular assigns a reduced desired speed to each value pair of capacity factor and model total pressure ratio, which is determined in particular from the actual total pressure ratio.
  • FIG. 1 is a schematic diagram shown schematically, with which the inventive method can be performed.
  • Four compressors V 1, V 2, V 3, V 4 are arranged in series and have, on their suction side of a respective inlet pressure p, p is the first p 2, p 3, and a temperature at its input T, T 1, T 2, T 3.
  • Upstream of the first compressor V 1 of the series is an inlet for cool fluid having a temperature T coldbox (for example 200K, 100K, 50K, 20K and / or 4K) that can be supplied in particular via a valve to the fluid to be cooled.
  • T coldbox for example 200K, 100K, 50K, 20K and / or 4K
  • a model total pressure ratio ⁇ model is determined, which is then to the control function F to determine the reduced setpoint speeds n 1, red , n 2 soll, red , n Let 3, red , n 4 should, be given red .
  • the model total pressure ratio ⁇ Model is equal to the actual total pressure ratio n ist when the determined capacity factor X is between the minimum and maximum values X min , X max . If the capacity factor X is outside this value range, then the model total pressure ratio ⁇ model is modified via a saturation function SF.
  • the capacity factor X is limited to its minimum or maximum value X min , X max and then, in particular together with the model total pressure ratio ⁇ Model , forwarded to the control function F, the off these arguments the reduced target speed n 1 should red , n 2 should, red , n 3 should, red , n 4 is determined, red for the respective compressor V 1 , V 2 , V 3 , V 4 .
  • This modification of the model total pressure ratio ⁇ model ensures that in operating conditions in which the capacity factor X is saturated, the control still has an influence on the compressors V 1 , V 2 , V 3 , V 4 , because then instead of the capacity factor X, the model total pressure ratio ⁇ model is changed, whereby the control function F reduced target speeds n 1 should red , n 2 should, red n 3 should, red n 4 should, call red , which lead out of these operating conditions.
  • the reduced setpoint speeds n 1 should, red , n 2 should, red , n 3 should, red , n 4 should, red for each compressor V 1 , V 2 , V 3 , V 4, in particular in a table (look up table).
  • this table can be constructed by model calculations using Eulerian Turbomachine equations.
  • a software for reading the reduced target speeds n 1 soll, red , n 2 soll, red , n 3 soll, red , n 4 soll, red n red from the table be used.
  • the capacity factor X is dependent on the model total pressure ratio ⁇ Model and the reduced speeds n 1 soll, red , n 2 soll, red , n 3 soll, red , n 4 soll, red n red chosen so that by the scheme the control function F, the actual inlet pressure p is the desired inlet pressure p is intended to equalize.
  • the smaller of the two values is assigned to the priority value PW, which is then used to determine further control values (such as the reduced setpoint speeds n 1, red , n 2 soll , red , n 3 soll , red , n 4 soll , red , in particular using the capacity factor or the target inlet temperature T soll ) is used. That is, if a compressor V i already has very high speeds n i , its speed index D i will be almost or equal to zero. As a result, the control of the plant is prioritized so that cold fluid is added via a cold reservoir upstream of the input of the first compressor V 1 , so that the actual inlet temperature T is reduced.
  • PW the priority value
  • a temperature control unit TE determines the target inlet temperature T soll .
  • the calculation is qualitatively such that at a low priority value PW, the target inlet temperature T soll is gradually reduced.
  • the target inlet temperature T setpoint is set to 90% of the measured actual inlet temperature T ist .
  • the downgrading to this value is realized, for example, by a ramp function. If, during the downgrading of the target inlet temperature T soll, the speed indices still have control priority, a new downgrade of the set inlet temperature T soll to 90% of the last measured actual inlet temperature T ist is performed.
  • the target inlet temperature T soll is greater than a design temperature at the inlet of the compressor series. If the design temperature is 4K and the temperature setpoint is 3.8K, the value is limited to 4K. Via a cooling reservoir control box C, the corresponding amount of cold fluid upstream of the inlet of the first compressor V 1 is acted upon by the warm fluid, so that by mixing the two differently warm fluids, the fluid has a mixing temperature which is smaller than previously measured Actual inlet temperature T is is.
  • the fluid at the inlet of the first compressor V 1 is not acted upon or with only a small amount of cold fluid, since the compressors V 1 , V 2 , V 3 , V 4 of the series already not with too high speeds n i run.
  • the calculation of the target inlet temperature T should be affected - for example, so that a Smoothing or a certain slope of a temperature ramp for T soll is achieved.
  • n i n i . red ⁇ n i . design ⁇ T i - 1 T i .
  • n i is the speed of the compressor (target, or actual speed)
  • n i, red is the reduced speed (target or actual speed) of the compressor V i
  • T i-1 is the temperature at the inlet of the compressor V i and T i, design the design or design temperature of the compressor V i .
  • ⁇ red is the reduced mass flow through the compressor
  • ⁇ is the instantaneous mass flow
  • ⁇ Design designates the mass flow for which the particular compressor is designed
  • p Design represents the design pressure at the respective compressor
  • T Design is the design temperature
  • p is the actual inlet pressure at the respective compressor is.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP15733630.6A 2014-07-08 2015-07-02 Verfahren zur druck- und temperaturreglung eines fluids in einer serie von kryogenen verdichtern Active EP3167197B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014010102.9A DE102014010102A1 (de) 2014-07-08 2014-07-08 Verfahren zur Druck- und Temperaturreglung eines Fluids in einer Serie von kryogenen Verdichtern
PCT/EP2015/001341 WO2016005037A1 (de) 2014-07-08 2015-07-02 Verfahren zur druck- und temperaturreglung eines fluids in einer serie von kryogenen verdichtern

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EP3167197A1 EP3167197A1 (de) 2017-05-17
EP3167197B1 true EP3167197B1 (de) 2018-10-17

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US (1) US10215183B2 (enrdf_load_stackoverflow)
EP (1) EP3167197B1 (enrdf_load_stackoverflow)
JP (1) JP6654190B2 (enrdf_load_stackoverflow)
KR (1) KR102437553B1 (enrdf_load_stackoverflow)
CN (1) CN106662112B (enrdf_load_stackoverflow)
DE (1) DE102014010102A1 (enrdf_load_stackoverflow)
WO (1) WO2016005037A1 (enrdf_load_stackoverflow)

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DE102014010104A1 (de) * 2014-07-08 2016-01-14 Linde Aktiengesellschaft Verfahren zur Regelung der Drehzahl von seriengeschalteten kryogenen Verdichtern zur Kühlung von tiefkaltem, kryogenen Helium
ES2905429T3 (es) * 2017-04-27 2022-04-08 Cryostar Sas Método para controlar un compresor de varias cámaras
USD982375S1 (en) 2019-06-06 2023-04-04 Sharkninja Operating Llc Food preparation device
CN117847872B (zh) * 2024-02-01 2024-07-26 中国科学院合肥物质科学研究院 一种氦压缩机系统全自动运行的控制方法
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KR102437553B1 (ko) 2022-08-26
CN106662112B (zh) 2019-01-15
EP3167197A1 (de) 2017-05-17
WO2016005037A1 (de) 2016-01-14
CN106662112A (zh) 2017-05-10
US10215183B2 (en) 2019-02-26
JP2017524101A (ja) 2017-08-24
JP6654190B2 (ja) 2020-02-26
US20170159666A1 (en) 2017-06-08
KR20170055470A (ko) 2017-05-19
DE102014010102A1 (de) 2016-01-14

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