EP2886811B1 - Method for condenser control in a thermal cycle arrangement and thermal cycle arrangement - Google Patents
Method for condenser control in a thermal cycle arrangement and thermal cycle arrangement Download PDFInfo
- Publication number
- EP2886811B1 EP2886811B1 EP13198793.5A EP13198793A EP2886811B1 EP 2886811 B1 EP2886811 B1 EP 2886811B1 EP 13198793 A EP13198793 A EP 13198793A EP 2886811 B1 EP2886811 B1 EP 2886811B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- condensation
- determined
- rotational speed
- setpoint
- 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.)
- Active
Links
- 238000000034 method Methods 0.000 title claims description 29
- 230000005494 condensation Effects 0.000 claims description 79
- 238000009833 condensation Methods 0.000 claims description 79
- 238000001816 cooling Methods 0.000 claims description 21
- 230000001276 controlling effect Effects 0.000 claims description 17
- 230000001105 regulatory effect Effects 0.000 claims description 14
- 239000007788 liquid Substances 0.000 claims description 7
- 238000001704 evaporation Methods 0.000 claims description 5
- 230000033228 biological regulation Effects 0.000 claims description 3
- 238000005070 sampling Methods 0.000 claims 1
- 239000003990 capacitor Substances 0.000 description 8
- 239000012530 fluid Substances 0.000 description 8
- 238000005259 measurement Methods 0.000 description 7
- 238000011161 development Methods 0.000 description 6
- 230000018109 developmental process Effects 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 230000008901 benefit Effects 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 230000005855 radiation Effects 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000013021 overheating Methods 0.000 description 3
- 230000002040 relaxant effect Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 108090000623 proteins and genes Proteins 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 238000009529 body temperature measurement Methods 0.000 description 1
- 238000011217 control strategy Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
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 thermal 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 document GB 2 473 543 A discloses an optimization and control system for a power plant that uses condensers based on cooling fans and controls the operation of the power generation system at the plant in conjunction with the operation of the air condensers to operate the power plant at an optimal operating point.
- the document US 6128905 A discloses a method and apparatus for increasing the energy efficiency of a power plant. In doing so, the power consumption of a power plant subsystem is monitored, whereby the monitored subsystem influences a measurable state with respect to a generator output.
- 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 evaporation and optionally additional overheating of the working fluid with the supply of heat, an expansion machine for generating mechanical energy by relaxing the vaporized working fluid, 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 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 method is characterized in that the temperature sensorless determination of the cooling air temperature includes calculating the temperature from a determined speed of the generator or the expansion machine, a determined speed of the condenser fan and a determined condensation pressure; or wherein the temperature sensorless determination of the cooling air temperature comprises a reading of the temperature from a predetermined table as a function of a determined speed of the generator or the expansion machine, a determined speed of the condenser fan and a determined condensation pressure.
- 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 in that the determined speed of the generator or the expansion machine is a measured speed of the generator or the expansion machine, and / or the determined speed of the condenser fan is a measured speed of the condenser fan and / or the determined condensation pressure is a measured Condensation pressure is.
- the determination of the temperature of the cooling air thus takes place via model-predictive control strategies (MPC), in which defined process variables from other process variables are determined with the aid of the knowledge of the process and its components via models.
- 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 optimal condensation pressure can decrease too fast, so that at the pump too low Pressure compared to the fluid temperature is applied, so that the pump kavitiert.
- 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 from a determined speed of the generator or the expansion machine, a determined speed of the condenser fan and a determined condensation pressure; Determining a nominal condensation 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 is characterized by a speed sensor for measuring a rotational speed of the generator or the expansion machine; one another speed sensor for measuring a condenser fan speed; and 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 However, it 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 s KOND , and the condensation pressure p KOND are included in 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 various ways by means of 4 variables, namely T ⁇ , s KOND , s GEN , and p KOND . Based on these Connections can then be derived by eliminating the heat dissipation in the equations a correlation between the 4 variables. 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 controlling a capacitor in the thermal cycle device comprising the following steps: determining, 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.
Landscapes
- 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)
Description
Die Erfindung betrifft ein Verfahren zur Regelung eines Kondensators in einer thermischen Kreisprozessvorrichtung, insbesondere in einer ORC Vorrichtung und eine entsprechende Vorrichtung.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.
Ein System zur Gewinnung von elektrischer Energie aus Wärmeenergie mit dem Organic Rankine Cycle als thermodynamischen Kreisprozess (ORC System), besteht aus den folgenden Hauptkomponenten: Eine Speisepumpe, die das flüssige Arbeitsmedium unter Druckerhöhung zu einem Verdampfer fördert, dem Verdampfer selbst, in dem das Arbeitsmedium unter Zuführung von Wärme verdampft und optional zusätzlich überhitzt wird, eine Expansionsmaschine, in welcher der unter hohem Druck stehende Dampf entspannt wird und dabei mechanische Energie erzeugt, welche über einen Generator zu elektrischer Energie gewandelt wird, und einem Kondensator, in dem der Niederdruckdampf aus der Expansionsmaschine verflüssigt wird. Aus dem Kondensator gelangt das flüssige Arbeitsmedium über einen optionalen Vorratsbehälter (Speisebehälter) und eine Saugleitung wieder zur Speisepumpe des Systems.A system for the recovery of electrical energy from thermal energy with the Organic Rankine Cycle as a thermodynamic cycle (ORC system), 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.
Zu jedem Lastzustand einer ORC-Anlage existiert ein Kondensationsdruck, der die Nettoleistung innerhalb der Anlagenspezifikation maximiert (optimaler Kondensationsdruck). Der Kondensationsdruck bezeichnet hier und im Folgenden den Druck am Auslass des Kondensators.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.
Die aus dem ORC-Prozess resultierende nutzbare elektrische Leistung ist die Nettoleistung. Diese setzt sich aus der Bruttoleistung abzüglich des Eigenbedarfs der Anlage zusammen. Der Eigenbedarf setzt sich aus vom Lastzustand unabhängigen Größen, wie zum Beispiel der Stromversorgung der Steuerung, und vom Lastzustand abhängigen Größen zusammen. Wichtige abhängige Größen sind der Leistungsbedarf der Speisepumpe und der Leistungsbedarf des Ventilators oder der Ventilatoren des Kondensators. Bei Leistungsbedarf des Ventilators des Kondensators zeigt sich ein sehr starker, überproportionaler Zusammenhang zwischen dem Eigenverbrauch und der Ventilatordrehzahl. Bei höherer Drehzahl sinkt der Kondensationsdruck, womit sich das Enthalpiegefälle der vorgelagerten Expansionsmaschine erhöht. Damit kann diese eine höhere (Brutto-) Leistung erzielen. Es stellt sich nun die Frage, ob diese Erhöhung der Bruttoleistung den gestiegenen Eigenbedarf durch die erhöhte elektrische Leistungsaufnahme des Kondensatorventilators übersteigt oder nicht.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.
Es muss nun betrachtet werden, wie sich der Eigenbedarf und die Bruttoleistung bei gegebenen Umgebungsbedingungen über den Kondensationsdruck verhalten. An dem Punkt, an dem die Bruttoleistung langsamer steigt als der Eigenbedarf des Kondensators abfällt, liegt das Optimum des Kondensationsdrucks in einem gegeben Lastzustand. Welcher Kondensationsdruck optimal ist, hängt vom Anlagenzustand ab. Der Zustand der Anlage wird durch zwei Faktoren beeinflusst: Die aktuelle Leistung (Thermische Leistung, Bruttoleistung) und die Umgebungsbedingungen (Temperatur).It now has to be considered how the intrinsic demand and the gross power behave above the condensation pressure under given ambient conditions. At the point where the gross power increases more slowly than the condenser's own demand drops, the optimum of the condensing 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).
Der Kondensator soll also immer auf den Druck regeln, bei dem ein möglichst optimaler Nettoertrag erzielt werden kann. Dieser Druck hängt vom Lastzustand, den Spezifikationen des Kondensators und der Lufttemperatur ab, möglicherweise auch vom Zustand des Kondensators, nämlich beispielsweise dann, wenn sich der Wärmeübergangskoeffizient oder die zur Verfügung stehende Fläche aufgrund von Verschmutzung ändert. Der Lastzustand kann gemessen bzw. berechnet werden. Die Eigenschaften des Kondensators sind bekannt. Die Außentemperatur muss gemessen werden. Diese Messung ist jedoch oft unzuverlässig und fehleranfällig. Dies liegt daran, dass beispielsweise die Sonneneinstrahlung das Messergebnis verfälschen kann. Zudem hängt das Messergebnis von der genauen Standortwahl des Temperatursensors an der Anlage ab und erfordert somit eine jeweilige Kalibrierung.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. In addition, the measurement result depends on the exact location of the temperature sensor on the system and thus requires a respective calibration.
Eine zuverlässige Messung der Außentemperatur mit gewünschter Genauigkeit ist daher in vielen Fällen eine schwierige Aufgabe, da Einflussfaktoren wie Sonneneinstrahlung, Wärmestrahlung von Gebäuden und Anlagen, Abluft von Prozessen usw. die Messung signifikant erschweren oder verfälschen können. Hinzu kommt, dass nicht die allgemeine Umgebungstemperatur, sondern die mittlere Temperatur der Luft am Eintritt in den Kondensator die Kondensation bestimmt. Eine Messung mit mehreren Sensoren in der Zuluft (zugeführte Luft), welche jedoch von der Wärmestrahlung der Kondensationsflächen abgeschirmt sind, ist wirtschaftlich ungünstig.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. In addition, 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.
Das Dokument
Das Dokument
Aufgabe der Erfindung ist es, die oben beschriebenen Nachteile zumindest teilweise zu überwinden. Wenn möglich, sollte auf eine Temperaturmessung verzichtet werden. Weiter sind vorzugsweise geeignete Sollwerte des Kondensationsdrucks für den Anfahrvorgang der Anlage festzulegen.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.
Diese Aufgabe wird gelöst durch ein Verfahren nach Anspruch 1. Erfindungsgemäß wird ein Verfahren zur Regelung eines Kondensators in einer thermischen Kreisprozessvorrichtung, insbesondere in einer ORC Vorrichtung, bereitgestellt, wobei die thermische Kreisprozessvorrichtung eine Speisepumpe zum Fördern von flüssigem Arbeitsmedium unter Druckerhöhung zu einem Verdampfer, den Verdampfer zum Verdampfen und optional zusätzlichen Überhitzen des Arbeitsmediums unter Zuführung von Wärme, eine Expansionsmaschine zum Erzeugen von mechanischer Energie durch Entspannen des verdampften Arbeitsmediums, einen Generator zum zumindest teilweisen Wandeln der mechanischen Energie in elektrischer Energie, und den Kondensator zum Kondensieren des entspannten Arbeitsmediums umfasst, und wobei das Verfahren die folgenden Schritte umfasst: Ermitteln, insbesondere Messen einer Drehzahl des Generators oder der Expansionsmaschine; temperatursensorloses Ermitteln einer Temperatur von dem Kondensator zugeführter Kühlluft; Ermitteln eines Kondensationssolldrucks, bei welchem die elektrische Nettoleistung der thermischen Kreisprozessvorrichtung maximal ist, aus der ermittelten, insbesondere gemessenen Generator- oder Expansionsmaschinendrehzahl und der ermittelten Kühllufttemperatur; und Steuern oder Regeln des Kondensationsdrucks mit dem Kondensationssolldruck als Zielwert, insbesondere mittels Einstellen einer Kondensatorlüfterdrehzahl. Das Verfahren ist dadurch gekennzeichnet, dass das temperatursensorlose Ermitteln der Kühllufttemperatur ein Berechnen der Temperatur aus einer ermittelten Drehzahl des Generators oder der Expansionsmaschine, einer ermittelten Drehzahl des Kondensatorlüfters und einem ermittelten Kondensationsdruck umfasst; oder wobei das temperatursensorlose Ermitteln der Kühllufttemperatur ein Auslesen der Temperatur aus einer vorbestimmten Tabelle in Abhängigkeit von einer ermittelten Drehzahl des Generators oder der Expansionsmaschine, einer ermittelten Drehzahl des Kondensatorlüfters und einem ermittelten Kondensationsdruck umfasst.This object is achieved by a method according to claim 1. According to the invention, 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 evaporation and optionally additional overheating of the working fluid with the supply of heat, an expansion machine for generating mechanical energy by relaxing the vaporized working fluid, a generator for at least partially converting the mechanical energy into electrical energy, and the condenser for condensing the expanded working medium, and wherein the method comprises the following steps: determining, in particular measuring a rotational speed of the generator or 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 value, in particular by setting a condenser fan speed. The method is characterized in that the temperature sensorless determination of the cooling air temperature includes calculating the temperature from a determined speed of the generator or the expansion machine, a determined speed of the condenser fan and a determined condensation pressure; or wherein the temperature sensorless determination of the cooling air temperature comprises a reading of the temperature from a predetermined table as a function of a determined speed of the generator or the expansion machine, a determined speed of the condenser fan and a determined condensation pressure.
Die Vorteile bestehen darin, dass stets auf den optimalen Kondensationsdruck geregelt werden kann, woraus sich ein höherer Nettoertrag ergibt. Zudem muss keine Außentemperatur gemessen werden, was eine Kostenreduktion und eine geringere Installationsfehlerwahrscheinlichkeit zur Folge hat, da die Ermittlung der Temperatur der Kühlluft, die dem Kondensator zugeführt wird, ohne Temperatursensor erfolgt. Die so ermittelte Temperatur kann auch als effektive Außentemperatur oder effektive Lufttemperatur bezeichnet werden. Das Ermitteln der Drehzahl des Generators kann beispielsweise aus den elektrischen Signalen vom oder zum Generator erfolgen, oder durch Messen mittels eines Drehzahlsensors.The advantages are that it is always possible to control the optimum condensation pressure, resulting in a higher net yield. In addition, 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.
Das erfindungsgemäße Verfahren kann dahingehend weitergebildet werden, dass das die ermittelte Drehzahl des Generators oder der Expansionsmaschine eine gemessene Drehzahl des Generators oder der Expansionsmaschine ist, und/oder die ermittelte Drehzahl des Kondensatorlüfters eine gemessene Drehzahl des Kondensatorlüfters ist und/oder der ermittelte Kondensationsdruck ein gemessener Kondensationsdruck ist.The inventive method can be further developed in that the determined speed of the generator or the expansion machine is a measured speed of the generator or the expansion machine, and / or the determined speed of the condenser fan is a measured speed of the condenser fan and / or the determined condensation pressure is a measured Condensation pressure is.
Die Ermittlung der Temperatur der Kühlluft erfolgt somit über modellprädiktive Regelungsstrategien (MPC), in denen definierte Prozessvariablen aus anderen Prozessvariablen unter Zuhilfenahme der Kenntnis des Prozesses und deren Komponenten über Modelle ermittelt werden. Das Ermitteln der Drehzahl des Kondensatorlüfters kann beispielsweise aus den elektrischen Signalen vom oder zum Kondensatorlüfter erfolgen. Die Ermittlung des Kondensationsdrucks kann beispielsweise auch aus einer gemessenen Temperatur des Kondensats erfolgen.The determination of the temperature of the cooling air thus takes place via model-predictive control strategies (MPC), in which defined process variables from other process variables are determined with the aid of the knowledge of the process and its components via models. 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.
Gemäß einer anderen Weiterbildung können bei einem Anfahren der thermodynamischen Kreisprozessvorrichtung zunächst die folgenden Schritte durchgeführt werden: Bestimmen eines Startwerts für den Kondensationssolldruck; Starten der thermodynamischen Kreisprozessvorrichtung und Steuern oder Regeln des Kondensationsdrucks mit dem Startwert des Kondensationssolldrucks als Zielwert mittels Einstellen der Kondensatorlüfterdrehzahl; und Ersetzen des Startwerts für den Kondensationssolldruck mit dem während des Betriebs der thermodynamischen Kreisprozessvorrichtung ermittelten Kondensationssolldruck.According to another development, 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.
Dies kann dahingehend weitergebildet werden, dass als Startwert für den Kondensationssolldruck der Sättigungsdruck des Arbeitsmediums bei aktueller Kondensattemperatur oder der Sättigungsdruck bei der Temperatur des Arbeitsmediums an einem Einlauf der Speisepumpe, insbesondere mit zusätzlicher Sollunterkühlung des Arbeitsmediums, der aktuelle Druck im Stillstand der thermodynamischen Kreisprozessvorrichtung, oder der letzte Kondensationssolldruck während des letzen Betriebs der thermodynamischen Kreisprozessvorrichtung bestimmt werden kann. Die Sollunterkühlung bezeichnet dabei die Temperaturdifferenz, um die das Kondensat gegenüber der Kondensationssättigungstemperatur unterkühlt ist. Dies hat den Vorteil, dass die Kavitationsgefahr in der Speisepumpe reduziert wird.This can be further developed to the effect that, as the starting value for the nominal condensing pressure, the saturation pressure of the working medium at the current condensate temperature or the saturation pressure at the temperature of the working medium at an inlet of the feed pump, in particular with additional desired subcooling of the working medium, the current pressure at standstill of the thermodynamic cycle apparatus, or the last condensation nominal pressure can be determined during the last 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.
Gemäß einer anderen Weiterbildung erfolgt das Ersetzen beim Anfahren mittels Steuern oder Regeln des Kondensationsdrucks vom Startwert des Kondensationsdrucks zum nach dem Start während des Betriebs der thermodynamischen Kreisprozessvorrichtung ermittelten Kondensationssolldruck. Dies hat den Vorteil, dass ein gleitender Übergang der Steuerung bzw. Regelung erfolgt, und somit sprungartige Veränderungen vermieden werden. Es soll ein Übergang von einem Startwert auf den optimalen Kondensationssolldruck erfolgen. Der Startwert kann mit verschiedenen Methoden ermittelt werden und wird beim Anfahren der Anlage einmalig festgelegt. Nun soll aber von diesem Wert auf den optimalen Kondensationssolldruck übergegangen werden, ohne dass zu schnelle Druckänderungen stattfinden, wie es z.B. bei einem schlagartigen Umschalten auf den optimalen Kondensationssolldruck der Fall wäre. Es soll daher der Sollwert ausgehend vom Startwert mit einer maximalen Änderungsgeschwindigkeit bis zum optimalen Kondensationssolldruck geändert werden. Sobald der Sollwert den optimalen Kondensationssolldruck erreicht hat, kann auf das bereits beschriebene erfindungsgemäße Regelverfahren umgeschaltet werden.According to another development, 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.
Nach einer anderen Weiterbildung können bei einem Abfahren der thermodynamischen Kreisprozessvorrichtung anschließend die folgenden Schritte durchgeführt werden: Bestimmen eines Abfahrwerts für den Kondensationssolldruck; Ersetzen des während des Betriebs der thermodynamischen Kreisprozessvorrichtung ermittelten Kondensationssolldruck mit dem Abfahrwert für den Kondensationssolldruck; und Steuern oder Regeln des Kondensationsdrucks mit dem Abfahrwert des Kondensationssolldrucks als Zielwert mittels Einstellen der Kondensatorlüfterdrehzahl und Stoppen des Betriebs der thermodynamischen Kreisprozessvorrichtung.According to another development, 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.
Dies kann dahingehend weitergebildet werden, dass als Abfahrwert der letzte Kondensationssolldruck während des letzten Betriebs der thermodynamischen Kreisprozessvorrichtung oder der Sättigungsdruck des Arbeitsmediums bei aktueller Kondensattemperatur, insbesondere mit einer zusätzlichen Sollunterkühlung des Kondensats, bestimmt werden kann.This can be further developed to the effect that the last condensation nominal pressure during the last operation of the thermodynamic cycle device or the saturation pressure of the working medium at the current condensate temperature, in particular with an additional desired subcooling of the condensate, can be determined as the departure value.
Gemäß einer anderen Weiterbildung erfolgt das Ersetzen beim Abfahren mittels Steuern oder Regeln des Kondensationsdrucks vom während des Betriebs der thermodynamischen Kreisprozessvorrichtung ermittelten Kondensationssolldruck zum Abfahrwert für den Kondensationssolldruck. Beim Abfahren kann der optimale Kondensationsdruck zu schnell abnehmen, so dass an der Pumpe ein zu geringer Druck im Vergleich zur Fluidtemperatur anliegt, so dass die Pumpe kavitiert. Durch die Begrenzung der maximalen Änderungsgeschwindigkeit des Kondensationssolldrucks kann dieses Problem umgangen werden.According to another development, 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. When driving off the optimal condensation pressure can decrease too fast, so that at the pump too low Pressure compared to the fluid temperature is applied, so that the pump kavitiert. By limiting the maximum rate of change of the nominal condensing pressure this problem can be avoided.
Gemäß einer weiteren Weiterbildung wird auch im Regelbetrieb (nach dem Startbetrieb) die Änderungsgeschwindigkeit des Kondensationssolldrucks auf eine maximale Druckänderungsgeschwindigkeit limitiert. Dabei kann dieser Wert für positive und negative Druckänderungen vom Betrag her unterschiedlich sein.According to a further development, 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.
Die obengenannte Aufgabe wird weiterhin gelöst durch eine thermische Kreisprozessvorrichtung nach Anspruch 9.The above object is further achieved by a thermal cycle device according to
Die erfindungsgemäße thermische Kreisprozessvorrichtung, insbesondere eine ORC Vorrichtung, umfasst: eine Speisepumpe zum Fördern von flüssigem Arbeitsmedium unter Druckerhöhung zu einem Verdampfer; den Verdampfer zum Verdampfen und optional zusätzlichen Überhitzen des Arbeitsmediums unter Zuführung von Wärme; eine Expansionsmaschine zum Erzeugen von mechanischer Energie durch Entspannen des verdampften Arbeitsmediums; einen Generator zum zumindest teilweisen Wandeln der mechanischen Energie in elektrischer Energie; dem Kondensator zum Kondensieren des entspannten Arbeitsmediums; und einer Steuer- oder Regeleinrichtung zum temperatursensorlosen Ermitteln einer Temperatur von dem Kondensator zugeführter Kühlluft aus einer ermittelten Drehzahl des Generators oder der Expansionsmaschine, einer ermittelten Drehzahl des Kondensatorlüfters und einem ermittelten Kondensationsdruck; Ermitteln eines Kondensationssolldrucks, bei welchem die elektrische Nettoleistung der thermischen Kreisprozessvorrichtung maximal ist, aus einer ermittelten oder gemessenen Generator- oder Expansionsmaschinendrehzahl und der ermittelten Kühllufttemperatur; und Steuern oder Regeln des Kondensationsdrucks mit dem Kondensationssolldruck als Zielwert, insbesondere mittels Einstellen einer Kondensatorlüfterdrehzahl. Die im Zusammenhang mit dem erfindungsgemäßen Verfahren genannten Vorteile gelten hier gleichermaßen.The thermal cycle device according to the invention, 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 from a determined speed of the generator or the expansion machine, a determined speed of the condenser fan and a determined condensation pressure; Determining a nominal condensation 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 advantages mentioned in connection with the method according to the invention apply equally here.
Die erfindungsgemäße Vorrichtung ist gekennzeichnet durch einen Drehzahlsensor zum Messen einer Drehzahl des Generators oder der Expansionsmaschine; einen weiteren Drehzahlsensor zum Messen einer Kondensatorlüfterdrehzahl; und einen Drucksensor zum Messen des Kondensationsdrucks.The device according to the invention is characterized by a speed sensor for measuring a rotational speed of the generator or the expansion machine; one another speed sensor for measuring a condenser fan speed; and a pressure sensor for measuring the condensation pressure.
Die genannten Weiterbildungen können einzeln eingesetzt oder geeignet miteinander kombiniert werden.The said developments can be used individually or combined with each other.
Weitere Merkmale und beispielhafte Ausführungsformen sowie Vorteile der vorliegenden Erfindung werden nachfolgend anhand der Zeichnungen näher erläutert. Es versteht sich, dass die Ausführungsformen nicht den Bereich der vorliegenden Erfindung erschöpfen. Es versteht sich weiterhin, dass einige oder sämtliche der im Weiteren beschriebenen Merkmale auch auf andere Weise miteinander kombiniert werden können.Further features and exemplary embodiments and advantages of the present invention will be explained in more detail with reference to the drawings. It is understood that the embodiments do not exhaust the scope of the present invention. It is further understood that some or all of the features described below may be combined with each other in other ways.
Zeichnungen
- Figur 1
- zeigt eine erfindungsgemäße Vorrichtung
- FIG. 1
- shows a device according to the invention
Die thermische Kreisprozessvorrichtung umfasst eine Speisepumpe 1 zum Fördern von flüssigem Arbeitsmedium unter Druckerhöhung zu einem Verdampfer 2, den Verdampfer 2 zum Verdampfen und optional zusätzlichen Überhitzen des Arbeitsmediums unter Zuführung von Wärme, eine Expansionsmaschine 3 zum Erzeugen von mechanischer Energie durch Entspannen des verdampften Arbeitsmediums, einen Generator 4 zum zumindest teilweisen Wandeln der mechanischen Energie in elektrischer Energie, und den Kondensator 5 zum Kondensieren des entspannten Arbeitsmediums. Weiterhin kann ein Drehzahlsensor 6 zum Messen der Drehzahl des Generators 4 vorgesehen sein. Die Generatordrehzahl kann jedoch auch aus elektrischen Signalen vom oder zum Generator 4 ermittelt werden. Zudem ist eine Regeleinrichtung 7 zum temperatursensorlosen Ermitteln einer effektiven Temperatur der Kühlluft, die dem Kondensator zugeführt wird; zum Ermitteln eines Kondensationssolldrucks, bei welchem die elektrische Nettoleistung der thermischen Kreisprozessvorrichtung maximal ist, aus der ermittelten oder gemessenen Generatordrehzahl und der ermittelten Kühllufttemperatur; und zum Regeln des Kondensationsdrucks mit dem Kondensationssolldruck als Zielwert mittels Einstellen einer Kondensatorlüfterdrehzahl bereitgestellt. Weiterhin können ein Drehzahlsensor 8 zu Messen der Drehzahl des Kondensatorlüfters und ein Drucksensor 9 zum Messen des Kondensationsdrucks im Kondensator 5 vorgesehen sein.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
Die wesentliche Idee der Erfindung ist, den Kondensationsdruck im Kondensator 5 ohne Verwendung eines Temperatursensors so zu steuern, dass ein möglichst großer Nettoenergieertrag erzielt wird. Dazu wird ein funktionaler Zusammenhang aus wichtigen Anlagenparametern und einem für jeden Lastpunkt optimalen Kondensationssolldruck formuliert. Dieser Zusammenhang leitet sich aus einem Modell der Anlage in seiner Umgebung ab:
Dabei ist sGEN die Drehzahl des Generators und T∞ die Temperatur der zugeführten Luft (Außentemperatur). In einer Ausführungsform der Erfindung kann aus einem Modell der Anlage für jeden Anlagenzustand auf die entsprechende Außentemperatur zurückgeschlossen werden:
Dieser berechnete Wert T∞ * für die Außentemperatur kann in der Gleichung (1) für den optimalen Kondensationssolldruck genutzt werden. Dabei gehen die Generatordrehzahl sGEN, die Kondensatorlüfterdrehzahl sKOND, und der Kondensationsdruck pKOND zur Berechnung ein.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 s KOND , and the condensation pressure p KOND are included in the calculation.
Zur Quantifizierung der durch das System transportierten Leistung (Lastpunkt) wird die Generatordrehzahl sGEN verwendet. Bei höherer Drehzahl wird (bei gegebenem Frischdampfzustand) mehr Medium durch das System gefördert. Die Speisepumpe muss entsprechend mehr fördern. Damit wird auch eine höhere thermische Eintrittsleistung benötigt. Folglich kann die Generatordrehzahl als Maß für die zugeführte Leistung genutzt werden. Insbesondere bei der Verwendung von volumetrischen Expansionsmaschinen und annähernd konstanten Frischdampfparametern ist dies eine einfache Möglichkeit, die thermische Leistung zu quantifizieren, da der Volumenstrom dann in sehr guter Näherung proportional zur Drehzahl der Expansionsmaschine ist. Durch die direkte Ankopplung des Generators ist sGEN äquivalent zu der Expansionsmaschinendrehzahl.To quantify the power (load point) transported by the system, 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.
Betrachtet man den optimalen Kondensationsdruck über einen relevanten Bereich von Umgebungstemperatur und Generatordrehzahlen, so lässt sich ein mathematischer Zusammenhang dieser drei Größen ermitteln. Diese formale Beschreibung kann in die Regelung des Kondensationsdrucks über die Steuerung der Kondensatordrehzahl einfließen.Considering the optimal condensation pressure over a relevant range of ambient temperature and generator speeds, a mathematical relationship of these three quantities can be determined. This formal description can be incorporated in the regulation of the condensation pressure via the control of the condenser speed.
Trägt man diesen mathematischen Zusammenhang grafisch auf, so sieht man, dass sich zu jeder Umgebungstemperatur und Generatordrehzahl ein eindeutiger optimaler Kondensationssolldruck zuordnen lässt, siehe Gleichung (1). Mit zunehmender Außentemperatur bei konstanter Drehzahl ergibt sich ein höherer optimaler Kondensatorsolldruck. Bei konstanter Außentemperatur ergibt sich mit zunehmender Generator- und damit Expansionsmaschinendrehzahl ein höherer optimaler Kondensatorsolldruck.If one plots this mathematical relationship graphically, one sees that a definite optimum condensation nominal pressure can be assigned to each ambient temperature and generator speed, see equation (1). With increasing outside temperature at a constant speed results in a higher optimal condensator target pressure. At constant outside temperature results with increasing generator and thus expansion engine speed, a higher optimal condensator target pressure.
Außentemperaturbestimmung ohne Messung: Ziel ist es nun, eine quantitative Aussage über die Umgebungsbedingungen (Temperatur der zugeführten Luft) aus anlageninternen Größen zu bestimmen.Outside temperature determination without measurement: The aim now is to determine a quantitative statement about the ambient conditions (temperature of the supplied air) from plant-internal variables.
Der im Kondensator während des Betriebs vorherrschende Kondensationsdruck wird durch die im Kondensator abgeführte Wärme beeinflusst. Es kann gezeigt werden, dass sich die Wärmeabfuhr des Kondensators auf verschiedene Weise anhand von 4 Variablen beschreiben lässt, nämlich T∞, sKOND, sGEN, und pKOND. Aufgrund dieser Zusammenhänge kann dann durch Eliminieren der Wärmeabfuhr in den Gleichungen ein Zusammenhang zwischen den 4 Variablen abgeleitet werden. Durch Ermittlung dieses mathematischen Zusammenhangs kann somit eine quantitative Aussage über die aktuellen, die Kondensation beeinflussenden, Umgebungsbedingungen dargestellt werden. Aus diesem Zusammenhang kann dann die Temperatur der zugeführten Luft T∞ (also die effektive Temperatur T∞ *) aus den anderen drei Größen ermittelt werden. Die nur aus anlageninternen Größen berechenbare Größe kann somit in die beschriebene Kondensatorregelung einfließen.The condensation pressure prevailing in the condenser during operation is influenced by the heat dissipated in the condenser. It can be shown that the heat dissipation of the capacitor can be described in various ways by means of 4 variables, namely T ∞ , s KOND , s GEN , and p KOND . Based on these Connections can then be derived by eliminating the heat dissipation in the equations a correlation between the 4 variables. 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.
Erfindungsgemäß wird ein Verfahren zur Regelung eines Kondensators in der thermischen Kreisprozessvorrichtung, insbesondere in einer ORC Vorrichtung, bereitgestellt, wobei das Verfahren die folgenden Schritte umfasst: Ermitteln, insbesondere Messen einer Drehzahl des Generators 4 oder der Expansionsmaschine 3; temperatursensorloses Ermitteln einer Temperatur T∞ * von dem Kondensator 5 zugeführter Kühlluft; Ermitteln eines Kondensationssolldrucks, bei welchem die elektrische Nettoleistung der thermischen Kreisprozessvorrichtung maximal ist, aus der gemessenen Generator- oder Expansionsmaschinendrehzahl und der ermittelten Kühllufttemperatur; und Steuern oder Regeln des Kondensationsdrucks mit dem Kondensationssolldruck als Zielwert mittels Einstellen einer Kondensatorlüfterdrehzahl.According to the invention, a method for controlling a capacitor in the thermal cycle device, in particular in an ORC device, is provided, the method comprising the following steps: determining, in particular measuring a rotational speed of the
Die dargestellten Ausführungsformen sind lediglich beispielhaft und der vollständige Umfang der vorliegenden Erfindung wird durch die Ansprüche definiert.The illustrated embodiments are merely exemplary and the full scope of the present invention is defined by the claims.
Claims (9)
- Method for regulating a condenser (5) in a thermal cycle apparatus, in particular in an ORC apparatus, wherein the thermal cycle apparatus comprises a feed pump (1) for conveying liquid working medium with an increase in pressure to an evaporator, the evaporator (2) for evaporating and optionally additionally superheating the working medium with a supply of heat, an expansion machine (3) for generating mechanical energy by expansion of the evaporated working medium, a generator (4) for at least partially converting the mechanical energy into electrical energy, and the condenser (5) for condensing the expanded working medium, and wherein the method comprises the following steps:determining, in particular measuring, a rotational speed of the generator or of the expansion machine;determining, without the use of a temperature sensor, a temperature of cooling air supplied from the condenser;determining from the determined generator or expansion machine rotational speed and the determined cooling air temperature, a condensation setpoint pressure at which the net electrical power of the thermal cycle apparatus is at a maximum; andcontrolling or regulating the condensation pressure, with the condensation setpoint pressure as target value, in particular by adjusting a condenser fan rotational speed;characterized in thatthe determining of the cooling air temperature without using temperature sensors comprises a calculation of the temperature from a determined rotational speed of the generator or the expansion machine, a determined rotational speed of the condenser fan and a determined condensation pressure; or wherein determining the cooling air temperature without using temperature sensors comprises sampling the temperature from a predetermined table depending on a determined rotational speed of the generator or the expansion machine, a determined rotational speed of the condenser fan, and a determined condensation pressure.
- Method according to claim 1, wherein the determined rotational speed of the generator or the expansion machine is a measured rotational speed of the generator or the expansion machine, and/or the determined rotational speed of the condenser fan is a measured rotational speed of the condenser fan and/or the determined condensation pressure is a measured condensation pressure.
- Method according to claim 1 or 2, wherein during starting the thermo-dynamic cycle apparatus, initially, the following steps are carried out:determining a start value for the condensation setpoint pressure;starting the thermo-dynamic cycle apparatus and controlling or regulating the condensation pressure with the start value of the condensation setpoint pressure as target value by means of adjusting the condenser fan rotational speed; andreplacing the start value for the condensation setpoint value with the condensation setpoint value determined during the operation of the thermo-dynamic cycle apparatus.
- Method according to claim 3, wherein a start value for the condensation setpoint value the saturation pressure of the working medium at the current condensate temperature or the saturation pressure at the temperature of the working medium at an inlet of the feed pump, in particular with additional setpoint sub-cooling of the working medium, the actual pressure in standstill of the thermo-dynamic cycle apparatus, or the last condensation setpoint pressure during the last operation of the thermo-dynamic cycle apparatus can be determined.
- Method according to one of the claims 3 or 4, wherein replacing comprises controlling or regulating the condensation pressure from the start value of the condensation pressure to the setpoint condensation pressure determined during the operation of the thermo-dynamic cycle apparatus.
- Method according to one of the claims 1 to 5, wherein subsequent to a shut-down of the thermo-dynamic cycle apparatus, the following steps may be carried out:determining a shut-down value for the setpoint condensation pressure;replacing the setpoint condensation pressure determined during operation of the thermo-dynamic cycle apparatus with the shut-down value for the setpoint condensation pressure; andcontrolling or regulating the condensation pressure with the shut-down value as target value by means of adjusting the condenser fan rotational speed and stopping the operation of the thermo-dynamic cycle apparatus.
- Method according to claim 6, wherein as shut-down value the last setpoint condensation pressure during the last operation of the thermo-dynamic cycle apparatus or the saturation pressure of the working medium at current condensate temperature, in particular with an additional setpoint sub-cooling of the condensate, is specified.
- Method according to one of the claims 6 or 7, wherein replacing comprises a controlling and regulating the condensation pressure of the setpoint condensation pressure determined during operation of the thermo-dynamic cycle apparatus to the shut-down value for the setpoint condensation pressure.
- Thermal cycle apparatus, in particular an ORC apparatus, comprising:a feed pump (1) for conveying liquid working medium with an increase in pressure to an evaporator,the evaporator (2) for evaporating and optionally additionally superheating the working medium with a supply of heat;an expansion machine (3) for generating mechanical energy by expansion of the evaporated working medium;a generator (4) for at least partially converting the mechanical energy into electrical energy;a condenser (5) for condensing the expanded working medium; anda control and regulation device (7) for determining a temperature of cooling air supplied from the condenser without using temperature sensors from a determined rotational speed of the generator or the expansion machine, a determined rotational speed of the condenser fan and a determined condensation pressure; determining a condensation setpoint pressure at which the net electrical power of the thermal cycle apparatus is at a maximum from a determined or measured generator or expansion machine rotational speed and the determined cooling air temperature, and for controlling or regulating the condensation pressure with the setpoint condensation pressure as target value, in particular by adjusting a condenser fan rotational speed;characterized bya rotational speed sensor (6) for measuring the rotational speed of the generator or the expansion machine;a pressure sensor (9) for measuring the condensation pressure; anda further rotational speed sensor (8) for measuring the condenser fan rotational speed.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP13198793.5A EP2886811B1 (en) | 2013-12-20 | 2013-12-20 | Method for condenser control in a thermal cycle arrangement and thermal cycle arrangement |
PCT/EP2014/068740 WO2015090648A1 (en) | 2013-12-20 | 2014-09-03 | Sensorless condenser regulation for power optimization for orc systems |
US15/106,709 US10329961B2 (en) | 2013-12-20 | 2014-09-03 | Sensorless condenser regulation for power optimization for ORC systems |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP13198793.5A EP2886811B1 (en) | 2013-12-20 | 2013-12-20 | Method for condenser control in a thermal cycle arrangement and thermal cycle arrangement |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2886811A1 EP2886811A1 (en) | 2015-06-24 |
EP2886811B1 true EP2886811B1 (en) | 2017-08-09 |
Family
ID=49882877
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13198793.5A Active EP2886811B1 (en) | 2013-12-20 | 2013-12-20 | Method for condenser control in a thermal cycle arrangement and thermal cycle arrangement |
Country Status (3)
Country | Link |
---|---|
US (1) | US10329961B2 (en) |
EP (1) | EP2886811B1 (en) |
WO (1) | WO2015090648A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105756731A (en) * | 2016-03-01 | 2016-07-13 | 合肥通用机械研究院 | Organic Rankine cycle system capable of effectively improving efficiency of expansion machine |
CN105673106A (en) * | 2016-04-01 | 2016-06-15 | 上海开山能源装备有限公司 | Organic Rankine cycle expansion machine system with combined condenser |
EP3682701A4 (en) | 2017-09-13 | 2021-05-19 | Ethertronics, Inc. | Adaptive antenna for channel selection management in communication systems |
JP7034759B2 (en) * | 2018-02-23 | 2022-03-14 | 三菱重工マリンマシナリ株式会社 | Condensation system control method and condensate system and ships equipped with it |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4926230B1 (en) * | 1968-02-09 | 1974-07-06 | ||
US3723018A (en) * | 1970-12-16 | 1973-03-27 | Hitachi Ltd | Automatic valve changeover apparatus for a turbine |
JPS5831602B2 (en) * | 1976-02-04 | 1983-07-07 | 株式会社日立製作所 | Dual system control device |
JPS54111871A (en) * | 1978-02-22 | 1979-09-01 | Hitachi Ltd | Frequency detecting method |
US6128905A (en) * | 1998-11-13 | 2000-10-10 | Pacificorp | Back pressure optimizer |
ES2561829T3 (en) * | 2002-10-15 | 2016-03-01 | Danfoss A/S | A procedure to detect a heat exchanger anomaly |
US7329478B2 (en) * | 2003-05-22 | 2008-02-12 | Tokyo Ohka Kogyo Co., Ltd. | Chemical amplified positive photo resist composition and method for forming resist pattern |
JP3930462B2 (en) * | 2003-08-01 | 2007-06-13 | 株式会社日立製作所 | Single-shaft combined cycle power generation facility and operation method thereof |
EP1624269A3 (en) * | 2003-10-02 | 2006-03-08 | HONDA MOTOR CO., Ltd. | Cooling control device for condenser |
US8433450B2 (en) * | 2009-09-11 | 2013-04-30 | Emerson Process Management Power & Water Solutions, Inc. | Optimized control of power plants having air cooled condensers |
US9556747B2 (en) * | 2012-12-04 | 2017-01-31 | Dresser-Rand Company | Methods for retrofitting a turbomachine |
-
2013
- 2013-12-20 EP EP13198793.5A patent/EP2886811B1/en active Active
-
2014
- 2014-09-03 WO PCT/EP2014/068740 patent/WO2015090648A1/en active Application Filing
- 2014-09-03 US US15/106,709 patent/US10329961B2/en active Active
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
US20170002693A1 (en) | 2017-01-05 |
WO2015090648A1 (en) | 2015-06-25 |
US10329961B2 (en) | 2019-06-25 |
EP2886811A1 (en) | 2015-06-24 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2933442B1 (en) | Device and method for detecting leaks in closed cycle processes | |
EP2865854B1 (en) | Device and method for reliable starting of ORC systems | |
EP2686526B1 (en) | Method for operating a steam cycle process | |
EP2260185A2 (en) | Method for obtaining energy from an exhaust flow and motor vehicle | |
WO2014117914A1 (en) | Method for operating a waste heat utilisation device | |
DE102010019718A1 (en) | Control of a thermal cycle | |
EP2886811B1 (en) | Method for condenser control in a thermal cycle arrangement and thermal cycle arrangement | |
WO2008003571A2 (en) | Method for operating a gas turbine and gas turbine for carrying out said method | |
DE102010042458A1 (en) | Method for operating a combined cycle power plant and for the implementation of the method prepared gas and steam turbine plant and corresponding control device | |
EP2837829A1 (en) | Control of the characteristics of centrifugal pumps | |
EP2526353B1 (en) | Method for controlling and regulating heat pumps and cooling systems | |
WO2015149916A1 (en) | Method for operating a system for a thermodynamic cycle, control device for a system for a thermodynamic cycle, a system, and an arrangement made from an internal combustion engine and a system | |
WO2016071204A1 (en) | Control method for operating a heat recovery steam generator | |
EP2667117B1 (en) | Method for controlling and regulating refrigeration assemblies and heat pumps with an air-cooled evaporator | |
EP1365110B1 (en) | Process and apparatus for operating a steam power plant, especially in a partial load range | |
EP3375990B1 (en) | Model-based monitoring of the operational state of an expansion machine | |
EP1764486A1 (en) | Method for determining the actual peak load of a power plant and device for regulating | |
DE102015208557B3 (en) | Method for determining a lubricant content in a working fluid circuit of a system for carrying out a thermodynamic cycle, system for carrying out a thermodynamic cycle, and arrangement with an internal combustion engine and such a system | |
DE102014206043B4 (en) | Method for operating a system for a thermodynamic cycle with a multi-flow evaporator, control device for a system, system for a thermodynamic cycle with a multi-flow evaporator, and arrangement of an internal combustion engine and a system | |
DE112020002572B4 (en) | GAS TURBINE AND CONTROL METHODS THEREOF AND COMBINED CYCLE POWER PLANT | |
EP3922925A1 (en) | Compression cooling system and method for operating a compression cooling system | |
DE102019122087A1 (en) | Energy recovery system with coupling circuit | |
EP2669480B1 (en) | Method for operating a solar energy system | |
DE102016219633B4 (en) | System for carrying out a thermodynamic cycle process and method for operating such a system | |
DE102019207637B4 (en) | Method for operating a refrigeration system for a vehicle with a refrigerant circuit |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20131220 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: ORCAN ENERGY AG |
|
R17P | Request for examination filed (corrected) |
Effective date: 20151127 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F28B 1/06 20060101ALI20170201BHEP Ipc: F01K 11/00 20060101ALI20170201BHEP Ipc: F01K 13/02 20060101ALI20170201BHEP Ipc: F01K 9/00 20060101AFI20170201BHEP Ipc: F28B 11/00 20060101ALI20170201BHEP Ipc: F01K 25/08 20060101ALI20170201BHEP |
|
INTG | Intention to grant announced |
Effective date: 20170227 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP Ref country code: AT Ref legal event code: REF Ref document number: 917091 Country of ref document: AT Kind code of ref document: T Effective date: 20170815 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502013007996 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20170809 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 5 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20171109 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20171209 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20171110 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20171109 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502013007996 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20180511 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171220 Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20171231 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171220 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171231 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171231 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171231 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20131220 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 917091 Country of ref document: AT Kind code of ref document: T Effective date: 20181220 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20181220 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170809 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20231220 Year of fee payment: 11 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20231220 Year of fee payment: 11 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20231221 Year of fee payment: 11 |