EP3015660B1 - Procédé pour le fonctionnement d'un cycle thermodynamique - Google Patents

Procédé pour le fonctionnement d'un cycle thermodynamique Download PDF

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Publication number
EP3015660B1
EP3015660B1 EP14191245.1A EP14191245A EP3015660B1 EP 3015660 B1 EP3015660 B1 EP 3015660B1 EP 14191245 A EP14191245 A EP 14191245A EP 3015660 B1 EP3015660 B1 EP 3015660B1
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EP
European Patent Office
Prior art keywords
condenser
working medium
pump
liquid
pressure
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EP14191245.1A
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German (de)
English (en)
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EP3015660A1 (fr
Inventor
Richard Aumann
Daniela Walter
Roy Langer
Jens-Patrick Springer
Nicolas Restrepo
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Orcan Energy AG
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Orcan Energy AG
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Publication date
Application filed by Orcan Energy AG filed Critical Orcan Energy AG
Priority to EP14191245.1A priority Critical patent/EP3015660B1/fr
Priority to PCT/EP2015/071873 priority patent/WO2016066338A1/fr
Priority to US15/523,265 priority patent/US10378392B2/en
Publication of EP3015660A1 publication Critical patent/EP3015660A1/fr
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Publication of EP3015660B1 publication Critical patent/EP3015660B1/fr
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    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B7/00—Combinations of two or more condensers, e.g. provision of reserve condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/06—Control arrangements therefor

Definitions

  • the invention relates to a method for operating a thermodynamic cycle, in particular an ORC process.
  • An exemplary system for recovering electrical energy from thermal energy consists of the following main components: a feed pump, which conveys liquid working fluid under pressure to an evaporator, the evaporator itself, in which the working fluid is preheated with the supply of heat, evaporated and optionally additionally superheated, an expansion machine in which the highly pressurized vaporized working fluid is expanded, thereby generating mechanical energy, which can be converted, for example via a generator into electrical energy, and a condenser in which the low-pressure steam (relaxed working medium) from the expansion machine and desiccated liquefied becomes. From the condenser, the liquid working medium returns to the feed pump of the system, whereby the thermodynamic cycle is closed. If the working medium is an organic working medium, it is an Organic Rankine Cycle as a thermodynamic cycle (ORC system).
  • ORC system Organic Rankine Cycle
  • the liquid working medium is subcooled, that is cooled to a temperature below the condensation temperature (equivalent to the boiling temperature) at the condensation pressure. In this way, the NPSH value required for the pump (Net Positive Suction Head) is achieved.
  • thermodynamic cycle in particular an ORC system
  • the condensation of the working medium against liquid for example water
  • the condensation can take place against air.
  • Condensation against water has the advantage that the heat of condensation can be fed into a heating circuit and is thus available to heat consumers (for example a stable, a building heater, a fermenter, etc.).
  • heat consumers for example a stable, a building heater, a fermenter, etc.
  • two capacitors can be connected together (according to the applicant's internal, unpublished state of the art) in order to enable both modes of operation (cooling against air and cooling against a liquid, in particular water).
  • the difficulties here are to regulate the distribution of the mass flows of the working medium in the respective capacitors and thus the heat output.
  • the aim is to allow the largest possible or defined usable amount of heat in a condenser, which is integrated into a heating circuit.
  • shut-off valves could be used to control the mass flows. However, this involves the problem that different pressure levels are present in both capacitors. This can lead to the return flow of condensed fluid into the condenser with the lower pressure, to the point of full running of this condenser.
  • the valves to be installed however, the complexity of the system and the susceptibility to errors is increased because the correct valve positions must be maintained for the correct operating modes.
  • FR 2935737 A1 discloses a heat engine with an evaporator powered by a heat source. Water evaporates in the evaporator. The exit of the evaporator is coupled to an inlet of a turbine in which the water expands. The turbine generates electrical energy via the generator. At the exit of the turbine, a first condenser and a second condenser are positioned separately in a parallel arrangement.
  • FR 2984400 A1 discloses a similar heat engine having two separate capacitors positioned in parallel.
  • WO2005 / 119014 A1 discloses a cogeneration plant comprising a water cooled condenser and a parallel air condenser arranged thereover.
  • An exemplary apparatus for operating a thermodynamic cycle in particular an ORC process, comprises: a feed pump for conveying liquid working fluid under pressure increase to an evaporator; the evaporator for preheating, evaporation and optionally additional overheating of the working medium under the supply of heat; an expansion machine for generating mechanical energy by relaxing the vaporized working medium; and at least two capacitors connected in parallel between the expander and the feed pump for defrosting, condensing and optionally additional subcooling of the expanded working medium.
  • the device can be further developed such that the at least two capacitors comprise a liquid condenser and an air condenser.
  • liquid condenser is meant that a liquid flows through the condenser, which can absorb heat from the working medium also flowing through the condenser.
  • air condenser the air flowing through the condenser (or along its contact surfaces) is the heat-absorbing fluid.
  • liquid condenser is provided in a liquid circuit, in particular a heating circuit, with a pump and / or wherein the air condenser comprises a fan.
  • the pump and / or the fan With the pump and / or the fan, a heat loss can be regulated in the liquid circuit, in particular switched on or off and the fan cooling of the working medium can be controlled against air, especially switched on or off.
  • the fan and / or the pump can be regulated, in particular the speed of the fan or the pumped by the pump mass flow of the liquid.
  • the mass flow, which is conveyed by the pump can be done for example via a speed control of the pump or via a balancing valve.
  • each capacitor can be connected via a siphon to the feed pump, wherein a minimum filling level of the condensed working medium is determined in the condenser by the vertex of the siphon.
  • a siphon in the condensate line the liquid level in the condenser is always as high as the height of the siphon. This also ensures a defined minimum subcooling.
  • a pressure-tight container may further be provided between the capacitors and the feed pump, a pressure-tight container.
  • a container between the condensers and the pump ensures that always liquid working fluid flows to the pump. Does it come to operating states in which one of the capacitors runs empty and thus gaseous working fluid flows in the direction of the pump, this is deposited in the container. Even with the liquid working fluid flowing gas bubbles, which could cause (partial) cavitation on the feed pump, are deposited in the container. If the container is not completely filled and a liquid level is established, the working fluid in the container tends to saturate. This results in two possible cases: If the working medium is colder than the environment, it evaporates and an equilibrium state between the liquid phase and the vapor phase sets in.
  • Another development consists in that, for each of the capacitors connected in parallel, a check valve is provided between the respective capacitor and the feed pump and / or between the expander and the respective condenser, each check valve allowing only a flow in the direction of the feed pump. In this way, an undesirable natural circulation between the capacitors can be prevented.
  • the device may further comprise: a temperature sensor for measuring the temperature of a liquid / heating circuit return, and / or a temperature sensor for measuring the temperature of a liquid / heating circuit flow and / or a temperature sensor for measuring the ambient temperature; and a control device for setting a rotational speed of the fan and / or for adjusting a pumped through the pump mass flow of the liquid based on the measured temperature or the measured temperatures, in particular for limiting the return temperature to a maximum value and / or for setting a constant flow temperature ,
  • CHP combined heat and power plant
  • heating networks can be operated, which require a constant flow temperature at different Wäredarfen.
  • thermodynamic cycle in particular an ORC process
  • the method according to the invention for operating a thermodynamic cycle, in particular an ORC process comprises during normal operation the following steps: conveying liquid working medium under pressure increase to an evaporator with a feed pump; Preheating, vaporizing and optionally additional overheating of the working medium with the supply of heat in the evaporator; Relaxing the vaporized working medium in an expansion machine; De-icing, condensing and optionally additional subcooling of the relaxed working medium with at least two capacitors connected in parallel between the expander and the feed pump.
  • the method according to the invention is characterized in that the following further steps are carried out during a start-up operation carried out before normal operation: provision of a sufficient flow height of liquid working medium in front of the feed pump in order to avoid cavitation in the feed pump; Starting the thermodynamic cycle with the condenser in which the lowest condensation pressure is present; and connecting the further capacitors in the order of increasing condensation pressure. Therefore, at the beginning of the starting process, a minimum feed-forward height NPSH r is ensured. Furthermore, a start without cavitation is ensured at the feed pump, since the pressure in front of the pump increases monotonically during the starting process.
  • a mass flow of the expanded working medium from the expansion machine self-regulating by an adjusting between the capacitors Pressure balance in mass flows of the relaxed working medium are divided into the respective capacitors.
  • the at least two capacitors comprise an air condenser with a fan and / or a liquid condenser in a liquid circuit with a pump
  • the method comprises the following further step: setting a speed of the fan and / or adjusting a through the pump pumped mass flow of the liquid.
  • Another development is that the step of starting with the fan running of the air condenser and shut off pump of the liquid circuit is carried out, and wherein the step of connecting the liquid condenser by switching on or increasing the delivered mass flow of the pump.
  • the operating states to be considered are: start-up, stationary operation, load change between heating condenser and air condenser operation, and parallel operation of heating condenser and air condenser.
  • the operating parameters to be ensured are: Suitable fluid distribution in each case for the load cases 100% air condenser operation, 100% condenser operation and parallel operation, as well as a sufficient flow height for the feed pump in the various operating modes.
  • the necessary operating parameters can be achieved in all different operating modes via control engineering methods as well as a suitable arrangement of components and a corresponding filling quantity with working medium. Additional components, such as valves, etc. are not required.
  • the devices and methods are described with which the operating parameters can be met in the simplest embodiment.
  • Fig. 1 shows simplified the standard connection of the system.
  • the liquid working medium is preheated in the heat exchanger (evaporator) 1 under heat, evaporated and then expanded in an expansion machine 2 (eg screw expander, turbine). Downstream of the expansion machine, the distribution of the working medium mass flow to the liquid condenser (heating condenser) 3 and the air condenser 4 (with a fan 7) takes place.
  • the heating water is circulated by a pump 6.
  • the circuit is closed by a feed pump 5 increases the pressure of the working fluid to the evaporation pressure and promotes it again in the evaporator 1.
  • the flow of the working medium or the distribution of the working medium is not controlled by valves, but is purely driven by thermal.
  • the regulation can ensure that the condensation pressure increases monotonically during the starting process. This can be achieved by starting the system in air condenser mode. Thus, the plant starts its operation at low pressure. Subsequently, the system flows smoothly into the heating condenser operation. If the temperature of the heating condenser is higher than the ambient temperature (which is almost always true), the condensation pressure will slowly increase monotonically.
  • Table 1 startup process: phase Heating capacitor Air condenser condensing pressure Location of working medium 1st plant turned off warm, because of heating water to temperature cold, since cooled by ambient air low (saturation at ambient temperature) in the air condenser 2. Plant start (start) warm cold, gets warmer increases still in the air condenser, since heating condenser temp.
  • Table 1 shows the procedure of the boot process.
  • phase 1 the system is shut down.
  • the condensate temperature and thus the condensation pressure are low (see Fig. 2 ).
  • the condensate temperature T kond is equal to the temperature of the ambient air T L.
  • phase two the system is started, the condensation pressure rises slowly. Fluid begins to move into the heating condenser (see Fig. 3 ).
  • the filling level L HK in the heating condenser increases.
  • the condensate temperature rises up to the temperature T VL of the flow in the heating circuit. From the condensate temperature, which allows condensation in the heating condenser (phase 3) is significantly condensed in the heating condenser.
  • the filling level L LK in the air condenser reduces in this phase.
  • the condensate temperature approaches the temperature T RL of the return in the heating circuit.
  • phase 4 the start is completed and a pure condenser operation is active.
  • the colder capacitor is the one in which condensing is to take place.
  • air condenser operation the air condenser is flowed through with cold outside air, while the heating condenser assumes the temperature of the exhaust steam in the stationary state.
  • a lower pressure is established in the air condenser and the fluid (working medium) flows through the air condenser for condensation.
  • the condensation heat is released to the ambient air.
  • heating condenser operation the heating condenser is flowed through by the return of the heating water. This is colder than the evaporation temperature. Since the air condenser with the fans off a temperature (due to heat loss only) close to the Assumes the temperature of the exhaust steam, the condensation takes place in the colder heating condenser.
  • 100% Condenser or 100% Air Condenser operation The 100% operating cases are each achieved by switching off or reducing the power of the fans, or the heating water circulating pump, so that in one of the capacitors no heat can be dissipated. Since the condensers on the side of the working medium are not separated from each other by valves, always a small part of the exhaust steam flows through the unused capacitor and is cooled by natural convection or heat conduction.
  • the sufficient flow height of the working medium in front of the feed pump is adjusted by the capacity and the geodetic height of the liquid column above the pump.
  • the geometric relationships between the heating condenser and the air condenser are chosen so that with the same capacity and operation of one capacitor so much working fluid in the condenser is that a sufficient supercooling is achieved. On the required flow height in parallel operation of both capacitors will be discussed in more detail in the following section.
  • the process described here stabilizes itself. This means that always the condenser with the larger heat output also has the highest level. This is due to the fluidic distribution of the fluids. There is always a state of equilibrium where there are no pressure differences between the two capacitors.
  • the total pressure p ges to be considered is composed of the respectively prevailing condensation pressure p kond and the geodetic pressure ⁇ p geod which is established via the filling level ⁇ h.
  • the process parameters V_dot denote the volume flow, p_kond the condensation pressure, p_geod. the geodetic pressure, h the filling level and Q_dot the heat flow.
  • the positions 1 to 5 correspond to the respective condenser a and b: after the expansion machine and before dividing the total mass flow V_dot, p (position 1), after splitting and before entering the condenser (position 2), in the condenser (FIG. Position 3), after the condenser and before the merging of the partial mass flows (position 4), after the merging and before the feed pump (position 5).
  • the comparison relates to the respective process parameters with respect to the two capacitors a and b.
  • the capacity of the system must be such that none of the two capacitors runs idle during operation.
  • the filling quantity and the constructive height of the capacitors interact with one another in such a way that there is currently no or only minimal fluid in the respectively unused capacitor (100% heating capacitor or 100% air condenser). This reduces heat loss and helps to save fluid.
  • the load change is achieved by a sliding control of the condensation components in the air condenser or in the liquid condenser is carried out by adjusting the speed of the fan and / or the pumped by the pump mass flow, in particular by each fan or heating pump are turned off. This increases the pressure in the unused capacitor and the condensation takes place in the other condenser in which a lower pressure prevails.
  • Control parameters can be, for example, a maximum temperature of the heating circuit return. If too much heat is introduced into the heating network by the ORC, the temperature of the return to the combined heat and power plant (CHP) can increase. If this exceeds a certain maximum value, the emergency cooler switches on to dissipate the excess heat from the system. To avoid this, the ORC system has to reduce the coupled thermal power at an early stage.
  • Another control parameter may be the desired flow temperature for the heating network. Reducing fan speed reduces heat discharged in the air condenser. As a result, the condensation pressure of p 1 to p 2 increases and a part of the exhaust steam flows into the heating condenser, where it increases the heat dissipation in the heating network.
  • the heating water circulating pump can be regulated, which allows a constant flow temperature T VL in the heating network (see Fig. 6 ).
  • heating networks can be operated, which require a constant flow temperature at different heat demands (for example, for temperature-sensitive processes, or for a sanitation, etc.).
  • the power of the pump can be adapted to the actual heat requirement and thus the efficiency of the system can be increased.
  • the simple ORC system with two capacitors can be improved by various variations of the interconnection, so that the required operating parameters can be maintained more safely (see Fig. 7 ).
  • a defined minimum filling level can be defined in the condenser 3, 4, since the liquid level in the condenser must always be as high as the height of the siphon. This also ensures a defined minimum subcooling.
  • a container 9 between the capacitors 3, 4 and the feed pump 5 ensures that always liquid working fluid flows to the pump. If it comes to operating conditions in which one of the capacitors runs empty and thus gaseous working fluid flows in the direction of the pump, this is deposited in the container. Even with the liquid working fluid flowing gas bubbles, which could cause (partial) cavitation on the feed pump, are deposited in the container. If the container is not completely filled and a liquid level is established, the working fluid in the container tends to saturate. This results in two possible cases: If the working medium is colder than the environment, it evaporates and an equilibrium state between the liquid phase and the vapor phase is established.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Claims (4)

  1. Procédé pour assurer le fonctionnement d'un processus à cycle thermodynamique, notamment un processus ORC (processus à cycle organique de Rankine), le procédé comprenant les étapes suivantes pendant un fonctionnement normal :
    refoulement de fluide de travail avec élévation de pression, vers un évaporateur (1), à l'aide d'une pompe d'alimentation (5) ;
    préchauffage, évaporation et optionnellement surchauffe supplémentaire du fluide de travail par amenée de chaleur dans l'évaporateur (1) ;
    détente du fluide de travail vaporisé dans une machine de détente (2) ;
    chauffage, condensation et optionnellement sous-refroidissement du fluide de travail détendu, à l'aide d'au moins deux condenseurs (3, 4) raccordés en parallèle entre la machine de détente et la pompe d'alimentation ;
    caractérisé en ce que
    pendant un fonctionnement de démarrage effectué avant le fonctionnement normal, on effectue les étapes supplémentaires suivantes :
    fourniture d'un niveau primaire suffisant de fluide de travail liquide avant la pompe d'alimentation, pour éviter de la cavitation dans la pompe d'alimentation ;
    démarrage du processus de cycle thermodynamique avec le condenseur dans lequel règne la pression de condensation la plus basse ;
    mise en service complémentaire des condenseurs supplémentaires dans l'ordre correspondant à la pression de condensation devenant plus grande.
  2. Procédé selon la revendication 1, d'après lequel un débit massique du fluide de travail détendu est réparti en débits massiques du fluide de travail détendu dans les condenseurs respectifs, à partir de la machine de détente, par autorégulation, grâce à un équilibre de pression s'établissant entre les condenseurs considérés.
  3. Procédé selon la revendication 1 ou la revendication 2, d'après lequel lesdits au moins deux condenseurs englobent un condenseur à air avec un ventilateur et/ou un condenseur à liquide dans un circuit de liquide avec une pompe, et le procédé comprenant l'étape supplémentaire suivante :
    le réglage d'une vitesse de rotation du ventilateur et/ou le réglage d'un débit massique du liquide refoulé par la pompe,
    procédé d'après lequel notamment en arrêtant le ventilateur il ne se produit pas de condensation du fluide de travail dans le condenseur à air, de préférence avec une pompe en marche, ou d'après lequel en arrêtant la pompe il ne se produit pas de condensation dans le condenseur à liquide, de préférence avec un ventilateur en marche.
  4. Procédé selon la revendication 3, d'après lequel l'étape du démarrage s'effectue avec le ventilateur du condenseur à air en marche et la pompe du circuit de liquide à l'arrêt, et d'après lequel l'étape de la mise en service supplémentaire du condenseur à liquide s'effectue par la mise en marche de la pompe ou l'augmentation du débit massique refoulé par celle-ci.
EP14191245.1A 2014-10-31 2014-10-31 Procédé pour le fonctionnement d'un cycle thermodynamique Active EP3015660B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP14191245.1A EP3015660B1 (fr) 2014-10-31 2014-10-31 Procédé pour le fonctionnement d'un cycle thermodynamique
PCT/EP2015/071873 WO2016066338A1 (fr) 2014-10-31 2015-09-23 Dispositif et procédé permettant de faire fonctionner un processus cyclique thermodynamique
US15/523,265 US10378392B2 (en) 2014-10-31 2015-09-23 Device and method for operating a thermodynamic cycle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14191245.1A EP3015660B1 (fr) 2014-10-31 2014-10-31 Procédé pour le fonctionnement d'un cycle thermodynamique

Publications (2)

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EP3015660A1 EP3015660A1 (fr) 2016-05-04
EP3015660B1 true EP3015660B1 (fr) 2018-12-05

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CN111237021B (zh) * 2020-01-13 2022-06-28 北京工业大学 一种用于有机朗肯循环的小压差蒸气直驱高增压比工质泵
SE547323C2 (en) * 2023-02-10 2025-07-01 Climeon Ab Thermodynamic system comprising a pump assembly

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US10378392B2 (en) 2019-08-13
WO2016066338A1 (fr) 2016-05-06
US20170328242A1 (en) 2017-11-16
EP3015660A1 (fr) 2016-05-04

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