EP2886811A1 - Procédé de régulation de condenseur dans un cycle thermique - Google Patents

Procédé de régulation de condenseur dans un cycle thermique Download PDF

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Publication number
EP2886811A1
EP2886811A1 EP13198793.5A EP13198793A EP2886811A1 EP 2886811 A1 EP2886811 A1 EP 2886811A1 EP 13198793 A EP13198793 A EP 13198793A EP 2886811 A1 EP2886811 A1 EP 2886811A1
Authority
EP
European Patent Office
Prior art keywords
pressure
condensation
nominal
temperature
cycle device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13198793.5A
Other languages
German (de)
English (en)
Other versions
EP2886811B1 (fr
Inventor
Jens-Patrick Springer
Andreas Grill
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.)
Orcan Energy AG
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Orcan Energy AG
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Filing date
Publication date
Application filed by Orcan Energy AG filed Critical Orcan Energy AG
Priority to EP13198793.5A priority Critical patent/EP2886811B1/fr
Priority to US15/106,709 priority patent/US10329961B2/en
Priority to PCT/EP2014/068740 priority patent/WO2015090648A1/fr
Publication of EP2886811A1 publication Critical patent/EP2886811A1/fr
Application granted granted Critical
Publication of EP2886811B1 publication Critical patent/EP2886811B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
    • F01K9/003—Plants characterised by condensers arranged or modified to co-operate with the engines condenser cooling circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B11/00—Controlling arrangements with features specially adapted for condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours

Definitions

  • the invention relates to a method for controlling a capacitor in a thermal cycle device, in particular in an ORC device and a corresponding device.
  • a system for the recovery of electrical energy from heat energy with the Organic Rankine Cycle as a thermodynamic cycle consists of the following main components: A feed pump, which promotes the liquid working fluid with pressure increase to an evaporator, the evaporator itself, in which the working medium vaporized with the addition of heat and optionally additionally superheated, an expansion machine in which the high pressure steam is expanded, thereby generating mechanical energy, which is converted by a generator into electrical energy, and a condenser, in which the low pressure steam from the Expansion machine is liquefied. From the condenser, the liquid working fluid returns to the feed pump of the system via an optional reservoir (food container) and a suction line.
  • condensation pressure For each load condition of an ORC plant, there is a condensing pressure that maximizes net output within the plant specification (optimal condensing pressure).
  • the condensation pressure here and below refers to the pressure at the outlet of the condenser.
  • the usable electrical power resulting from the ORC process is the net power. This is composed of the gross output less the own demand of the system.
  • the personal need is independent of the load condition Variables, such as the power supply of the controller, and load-dependent variables together.
  • Important dependent variables are the power requirement of the feed pump and the power requirement of the fan or the fans of the condenser. When the power requirement of the fan of the condenser shows a very strong, disproportionate relationship between the self-consumption and the fan speed. At higher speeds, the condensation pressure decreases, which increases the enthalpy gradient of the upstream expansion machine. Thus, this can achieve a higher (gross) performance. The question now arises as to whether this increase in gross output exceeds or even exceeds the increased domestic demand due to the increased electrical power consumption of the condenser fan.
  • condensation pressure is in a given load state. Which condensation pressure is optimal depends on the plant condition. The condition of the system is influenced by two factors: the actual power (thermal power, gross power) and the ambient conditions (temperature).
  • the condenser should therefore always regulate the pressure at which the best possible net yield can be achieved.
  • This pressure depends on the load condition, the specifications of the condenser and the air temperature, possibly also on the condition of the condenser, for example, when the heat transfer coefficient or the available area changes due to soiling.
  • the load condition can be measured or calculated.
  • the properties of the capacitor are known.
  • the outside temperature must be measured. However, this measurement is often unreliable and error prone. This is because, for example, the solar radiation can falsify the measurement result.
  • the measurement result depends on the exact location of the temperature sensor on the system and thus requires a respective calibration.
  • a reliable measurement of the outside temperature with the desired accuracy is therefore in many cases a difficult task, as influencing factors such as solar radiation, thermal radiation of buildings and facilities, exhaust air from Processes, etc. can significantly complicate or distort the measurement.
  • it is not the general ambient temperature but the average temperature of the air at the inlet to the condenser that determines the condensation.
  • a measurement with several sensors in the supply air (supplied air), which are shielded from the heat radiation of the condensation surfaces, is economically unfavorable.
  • the object of the invention is at least partially overcome the disadvantages described above. If possible, a temperature measurement should be avoided. Furthermore, suitable setpoint values of the condensation pressure for the starting process of the system are preferably to be defined.
  • a method for controlling a capacitor in a thermal cycle device in particular in an ORC device provided, wherein the thermal cycle device a feed pump for conveying liquid working fluid with pressure increase to an evaporator, the Evaporator for vaporizing and optionally additional overheating of the working medium with the supply of heat, an expansion machine for generating mechanical energy by relaxing the vaporized working medium, a generator for at least partially converting the mechanical energy into electrical energy, and the condenser for condensing the expanded working medium
  • the method comprises the following steps: determining, in particular measuring a rotational speed of the generator or of the expansion machine; temperature sensorless determining a temperature of the condenser supplied cooling air; Determining a nominal condensing pressure at which the net electrical output of the thermal cycle device is at a maximum from the determined, in particular measured generator or expansion engine speed and the determined cooling air temperature; and controlling or regulating the condensation pressure with the nominal condensing pressure as a target
  • the advantages are that it is always possible to control the optimum condensation pressure, resulting in a higher net yield.
  • no outside temperature must be measured, resulting in a cost reduction and a lower installation error probability result, since the determination of the temperature of the cooling air, which is supplied to the capacitor without temperature sensor.
  • the temperature thus determined may also be referred to as the effective outside temperature or effective air temperature.
  • the determination of the rotational speed of the generator can be carried out, for example, from the electrical signals to or from the generator, or by measuring by means of a rotational speed sensor.
  • the inventive method can be further developed such that the temperature sensorless determination of the cooling air temperature comprises calculating the temperature from a determined, in particular measured speed of the generator or the expansion machine, a determined, in particular measured speed of the condenser fan and a determined, in particular measured condensation pressure comprises; or wherein the temperature sensorless determination of the cooling air temperature comprises a readout of the temperature from a predetermined table as a function of a determined, in particular measured speed of the generator or the expansion machine, a determined, in particular measured speed of the condenser fan and a determined, in particular measured condensation pressure.
  • MPC model-predictive control strategies
  • Determining the speed of the condenser fan can be done for example from the electrical signals from or to the condenser fan.
  • the condensation pressure can also be determined, for example, from a measured temperature of the condensate.
  • thermodynamic cycle device when the thermodynamic cycle device is started up, the following steps can first be carried out: determining a starting value for the nominal condensation pressure; Starting the thermodynamic cycle device and controlling the condensation pressure with the start value of the nominal condensing pressure as the target value by adjusting the condenser fan speed; and replacing the starting value for the nominal condensing pressure with the condensing nominal pressure determined during operation of the thermodynamic cycle device.
  • the desired subcooling designates the temperature difference by which the condensate is undercooled with respect to the condensation saturation temperature. This has the advantage that the risk of cavitation in the feed pump is reduced.
  • the replacement during start-up by means of controlling or regulating the condensation pressure takes place from the start value of the condensation pressure to the condensation nominal pressure determined after the start during the operation of the thermodynamic cycle device.
  • This has the advantage that a smooth transition of the control or regulation takes place, and thus sudden changes are avoided. It should be a transition from a starting value to the optimum condensation nominal pressure.
  • the starting value can be determined using various methods and is set once when the system starts up. Now, however, should be transferred from this value to the optimum condensation target pressure without too rapid pressure changes take place, as would be the case, for example, in a sudden switching to the optimum condensing nominal pressure. Therefore, the setpoint should be changed from the start value with a maximum rate of change to the optimum condensation target pressure. As soon as the desired value has reached the optimum condensation nominal pressure, it is possible to switch over to the control method according to the invention already described.
  • thermodynamic cycle device when the thermodynamic cycle device is shut down, the following steps can then be carried out: determination of a departure value for the nominal condensation pressure; Replacing the condensing setpoint pressure determined during operation of the thermodynamic cycle apparatus with the value of the condensation nominal pressure; and controlling or regulating the condensation pressure with the departure value of the nominal condensing pressure as the target value by adjusting the condenser fan speed and stopping the operation of the thermodynamic cycle device.
  • the substitution during shutdown by means of controlling or regulating the condensation pressure is carried out by the condensation target pressure determined during operation of the thermodynamic cycle device to the value for the nominal condensation pressure.
  • the optimum condensation pressure may decrease too quickly, so that the pump is under-pressurized compared to the fluid temperature, causing the pump to cavitate.
  • the rate of change of the nominal condensing pressure is limited to a maximum rate of pressure change even in normal operation (after start-up operation). This value can be different for positive and negative pressure changes in amount.
  • the thermal cycle device in particular an ORC device, comprises: a feed pump for conveying liquid working fluid under pressure increase to an evaporator; the evaporator for evaporation and optionally additional overheating of the working medium with the supply of heat; an expansion machine for generating mechanical energy by relaxing the vaporized working medium; a generator for at least partially converting the mechanical energy into electrical energy; the condenser for condensing the expanded working medium; and a control or regulating device for temperature sensorless determination of a temperature of the condenser supplied cooling air; Determining a nominal condensing pressure at which the net electrical output of the thermal cycle device is at a maximum from a determined or measured generator or expansion engine speed and the determined cooling air temperature; and controlling or regulating the condensation pressure with the nominal condensing pressure as a target value, in particular by setting a condenser fan speed.
  • the device according to the invention can be further developed in that it further comprises a speed sensor for measuring a rotational speed of the generator or the expansion machine; and / or another speed sensor for measuring a condenser fan speed; and / or may include a pressure sensor for measuring the condensation pressure.
  • the said developments can be used individually or combined with each other.
  • FIG. 1 shows an embodiment of the device according to the invention. For the description of the method according to the invention is also referred to.
  • the thermal cycle device comprises a feed pump 1 for conveying liquid working fluid under pressure increase to an evaporator 2, the evaporator 2 for evaporation and optionally additional overheating of the working medium with the supply of heat, an expansion machine 3 for generating mechanical energy by relaxing the vaporized working medium, a Generator 4 for at least partially converting the mechanical energy into electrical energy, and the condenser 5 for condensing the relaxed working medium.
  • a speed sensor 6 may be provided for measuring the rotational speed of the generator 4.
  • the generator speed can also be determined from electrical signals to or from the generator 4.
  • a control device 7 for temperature sensorless determination of an effective temperature of the cooling air, which is supplied to the capacitor; for determining a condensing setpoint pressure at which the net electrical output of the thermal cycle device is at a maximum, from the determined or measured generator speed and the determined cooling air temperature; and for controlling the condensing pressure with the condensing target pressure as the target value by adjusting a condenser fan speed.
  • a rotational speed sensor 8 for measuring the rotational speed of the condenser fan and a pressure sensor 9 for measuring the condensation pressure in the condenser 5 may be provided.
  • the essential idea of the invention is to control the condensation pressure in the condenser 5 without using a temperature sensor in such a way that the greatest possible net energy yield is achieved.
  • T ⁇ * f s GENE s COND p COND
  • This calculated value T ⁇ * for the outside temperature can be used in the equation (1) for the optimum condensation nominal pressure.
  • the generator speed S GEN , the condenser fan speed SKOND, and the condensation pressure P KOND enter into the calculation.
  • the generator speed S GEN is used. At higher speed (with a given live steam condition) more medium will be pumped through the system. The feed pump has to promote more accordingly. This also requires a higher thermal input power. Consequently, the generator speed can be used as a measure of the power supplied. In particular, when using volumetric expansion machines and approximately constant live steam parameters, this is an easy way to quantify the thermal performance, since the volume flow is then in a very good approximation proportional to the speed of the expansion machine. Due to the direct coupling of the generator, S GEN is equivalent to the expansion engine speed.
  • the condensation pressure prevailing in the condenser during operation is influenced by the heat dissipated in the condenser.
  • the heat dissipation of the capacitor can be described in different ways by means of 4 variables, namely T ⁇ , S KOND , S GEN , and P KOND . Because of these relationships, by eliminating heat dissipation in the equations, a relationship between the 4 variables can be derived. By determining this mathematical relationship, it is thus possible to present a quantitative statement about the current ambient conditions influencing the condensation. From this context, the temperature of the supplied air T ⁇ (ie the effective temperature T ⁇ *) can then be determined from the other three variables. The size, which can only be calculated from plant-internal variables, can thus be incorporated into the described capacitor control.
  • a method for regulating a capacitor in the thermal cycle device comprising the following steps: in particular measuring a rotational speed of the generator 4 or the expansion machine 3; temperature sensorless determination of a temperature T ⁇ * of the condenser 5 supplied cooling air; Determining a nominal condensation pressure at which the net electrical output of the thermal cycle device is at a maximum from the measured generator or expansion engine speed and the determined cooling air temperature; and controlling or regulating the condensation pressure with the nominal condensing pressure as a target value by adjusting a condenser fan speed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Turbines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP13198793.5A 2013-12-20 2013-12-20 Procédé de régulation de condenseur dans un cycle thermique et cycle thermique Active EP2886811B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP13198793.5A EP2886811B1 (fr) 2013-12-20 2013-12-20 Procédé de régulation de condenseur dans un cycle thermique et cycle thermique
US15/106,709 US10329961B2 (en) 2013-12-20 2014-09-03 Sensorless condenser regulation for power optimization for ORC systems
PCT/EP2014/068740 WO2015090648A1 (fr) 2013-12-20 2014-09-03 Procédé de régulation sans capteur d'un condenseur permettant d'optimiser la puissance de systèmes orc

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13198793.5A EP2886811B1 (fr) 2013-12-20 2013-12-20 Procédé de régulation de condenseur dans un cycle thermique et cycle thermique

Publications (2)

Publication Number Publication Date
EP2886811A1 true EP2886811A1 (fr) 2015-06-24
EP2886811B1 EP2886811B1 (fr) 2017-08-09

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EP13198793.5A Active EP2886811B1 (fr) 2013-12-20 2013-12-20 Procédé de régulation de condenseur dans un cycle thermique et cycle thermique

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US (1) US10329961B2 (fr)
EP (1) EP2886811B1 (fr)
WO (1) WO2015090648A1 (fr)

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Publication number Priority date Publication date Assignee Title
CN105756731A (zh) * 2016-03-01 2016-07-13 合肥通用机械研究院 一种可有效提升膨胀机效率的有机朗肯循环系统
CN105673106A (zh) * 2016-04-01 2016-06-15 上海开山能源装备有限公司 带组合冷凝器的有机朗肯循环膨胀机系统
WO2019055492A1 (fr) 2017-09-13 2019-03-21 Ethertronics, Inc. Antennes adaptatives pour gérer une sélection de canal dans des systèmes de communication
JP7034759B2 (ja) * 2018-02-23 2022-03-14 三菱重工マリンマシナリ株式会社 復水システムの制御方法並びに復水システム及びこれを備えた船舶

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6128905A (en) * 1998-11-13 2000-10-10 Pacificorp Back pressure optimizer
EP1624269A2 (fr) * 2003-10-02 2006-02-08 HONDA MOTOR CO., Ltd. Dispositif de régulation du refroidissement d'un condenseur
GB2473543A (en) * 2009-09-11 2011-03-16 Emerson Process Management Optimisation of steam power plant

Family Cites Families (8)

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JPS4926230B1 (fr) * 1968-02-09 1974-07-06
US3723018A (en) * 1970-12-16 1973-03-27 Hitachi Ltd Automatic valve changeover apparatus for a turbine
JPS5831602B2 (ja) * 1976-02-04 1983-07-07 株式会社日立製作所 二重系制御装置
JPS54111871A (en) * 1978-02-22 1979-09-01 Hitachi Ltd Frequency detecting method
AU2003273765A1 (en) * 2002-10-15 2004-05-04 Danfoss A/S A method and a device for detecting an abnormality of a heat exchanger, and the use of such a device
KR100865063B1 (ko) * 2003-05-22 2008-10-23 도오꾜오까고오교 가부시끼가이샤 화학증폭형 포지티브형 포토레지스트 조성물 및 레지스트패턴 형성방법
JP3930462B2 (ja) * 2003-08-01 2007-06-13 株式会社日立製作所 一軸コンバインドサイクル発電設備及びその運転方法
US9556747B2 (en) * 2012-12-04 2017-01-31 Dresser-Rand Company Methods for retrofitting a turbomachine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6128905A (en) * 1998-11-13 2000-10-10 Pacificorp Back pressure optimizer
EP1624269A2 (fr) * 2003-10-02 2006-02-08 HONDA MOTOR CO., Ltd. Dispositif de régulation du refroidissement d'un condenseur
GB2473543A (en) * 2009-09-11 2011-03-16 Emerson Process Management Optimisation of steam power plant

Also Published As

Publication number Publication date
US20170002693A1 (en) 2017-01-05
US10329961B2 (en) 2019-06-25
WO2015090648A1 (fr) 2015-06-25
EP2886811B1 (fr) 2017-08-09

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