EP2499343B1 - Thermodynamische maschine sowie verfahren zu deren betrieb - Google Patents

Thermodynamische maschine sowie verfahren zu deren betrieb Download PDF

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Publication number
EP2499343B1
EP2499343B1 EP10782537.4A EP10782537A EP2499343B1 EP 2499343 B1 EP2499343 B1 EP 2499343B1 EP 10782537 A EP10782537 A EP 10782537A EP 2499343 B1 EP2499343 B1 EP 2499343B1
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EP
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Prior art keywords
working fluid
machine
auxiliary gas
liquid
pump
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EP10782537.4A
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German (de)
English (en)
French (fr)
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EP2499343A2 (de
Inventor
Andreas Schuster
Andreas Sichert
Richard Aumann
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Orcan Energy AG
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Orcan Energy AG
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Priority to PL10782537T priority Critical patent/PL2499343T3/pl
Publication of EP2499343A2 publication Critical patent/EP2499343A2/de
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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
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas
    • 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
    • F01K15/00—Adaptations of plants for special use
    • F01K15/02—Adaptations of plants for special use for driving vehicles, e.g. locomotives
    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • 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 thermodynamic machine with a circulation system in which a particularly low-boiling working fluid circulates alternately in gas and liquid phase.
  • the machine comprises a heat exchanger, a relaxation machine, a condenser and a liquid pump.
  • the invention further relates to a method for operating such a thermodynamic machine, wherein the working fluid is heated in a circuit, relaxed, condensed and conveyed by pumping the liquid working fluid.
  • thermodynamic machine Under such a thermodynamic machine is particularly understood a machine that operates on the thermodynamic Rankine cycle.
  • the Rankine cycle is characterized by pumping the liquid working medium, evaporating the working medium at high pressure, depressurizing the gaseous working fluid to perform mechanical work, and condensing the gaseous working fluid at low pressure.
  • today's conventional steam power plants operate according to the Rankine cycle.
  • fossil-fired steam power plants produce water vapor at temperatures above 500 ° C at a pressure of over 200 bar.
  • the condensation of the relaxed water vapor takes place at about 25 ° C and a pressure of about 30 mbar.
  • thermodynamic machine A working according to the Rankine cycle thermodynamic machine and a method for their operation is for example from the WO 2005/021936 A2 known.
  • the working fluid is water.
  • ORC machines in which instead of the working fluid water, a low-boiling, in particular organic fluid is used.
  • low-boiling is understood to mean that such a fluid boils at lower pressures relative to water or has a higher vapor pressure compared to water.
  • An ORC machine operates according to the so-called Organic Rankine Cycle (ORC) cycle, ie essentially with a different, especially organic, low-boiling working fluid from water.
  • ORC Organic Rankine Cycle
  • working fluids for an ORC machine for example, hydrocarbons, aromatic hydrocarbons, fluorinated hydrocarbons, carbon compounds, especially alkanes, fluoroether, fluoroethane or synthesized silicone oils are known.
  • ORC machines or systems for example, the heat sources available in geothermal or solar power plants can be used economically to generate electricity. Also, with an ORC engine so far unused waste heat of an internal combustion engine from exhaust air, cooling circuit, exhaust gas, etc. can be used to perform work or to generate electricity.
  • the vapor pressure of a liquid which belongs to a particular temperature, evaporates.
  • the undershooting of the vapor pressure can take place in quiescent or in moving liquids. For example, in a flowing liquid due to a sharp deflection or acceleration of the flow locally below the vapor pressure, so that a local evaporation takes place.
  • the locally produced vapor bubbles condense at points of higher pressure and collapse. The whole process is called cavitation.
  • cavitation occurring in the liquid phase of the working fluid represents a not inconsiderable problem. Because of the small size of the vapor bubbles, the condensation takes place very quickly. A sudden implosion of the vapor bubbles may form a microbeam. Is this directed to a surrounding wall, local pressure peaks of up to 10,000 bar can be achieved. In addition, due to the high pressures, local temperatures of well over 1000 ° C can be reached, which can lead to melting processes in the wall material. Destruction effects from cavitation can occur within hours.
  • the occurrence of cavitation undesirably reduces the flow rate of fluid. Since the density of the vapor bubbles is generally clearly different from that of the liquid, even with a small mass fraction of the working fluid, the mass flow which can be conveyed is reduced as steam at a given volume flow. With a strong formation of steam, the mass flow possibly even breaks down. For example, if the work machine is used as a pump in an ORC system, the entire cycle process may possibly come to a standstill. Due to the lack of pump power it comes to the backflow of the liquid working fluid in the condenser, whereby its effect is significantly reduced. As a result, the heat dissipation comes to a standstill. This state of the overall system is difficult to leave. It is necessary to wait until the working fluid undercooled itself by cooling. Next breaks the flow in the evaporator together, so that no heat can be dissipated. If necessary, the working fluid used can then be damaged by exceeding its stability limit.
  • the problem of the occurrence of cavitation is, for example, in EP 1 624 269 A2 described.
  • a cavitation in the working fluid water within the condenser and the subsequent pump can be prevented by the fact that the condenser, a specific pressure and temperature control is provided.
  • appropriate pressure and temperature sensors are included.
  • the water level in the condenser is maintained at a predetermined level. This is supported by a drain valve, which discharges water or non-condensing gases to the outside.
  • a complex fluid machine which operates according to the Rankine cycle.
  • the fluid machine has a pump for pressurizing and pumping out a liquid-phase working fluid and an expansion device connected in series with the pump for generating a driving force by expanding the working fluid which is heated to become a gas-phase working fluid. It is provided to transfer the heat of the working fluid at an outlet side of the expansion device to the working fluid at an outlet side of the fluid pump.
  • a transportable drive unit for converting heat is known, which is designed as a thermodynamic machine of the type mentioned and operates according to the Rankine cycle.
  • thermodynamic machine of the type mentioned above known.
  • a gas / liquid solution in particular an ammonia / water solution, circulates.
  • the pressure of gas and liquid is lowered.
  • the pressure is increased.
  • the object of the invention is to develop a thermodynamic machine of the type mentioned in that the occurrence of cavitation in the liquid or in the liquid working fluid is avoided as possible. Furthermore, it is an object of the invention to provide a corresponding method for operating such a thermodynamic machine, cavitation in the liquid being avoided as far as possible.
  • thermodynamic machine of the type mentioned that the liquid working fluid in the flow of the liquid pump by adding a non-condensing auxiliary gas, a system pressure-increasing partial pressure is impressed.
  • the invention is based on the recognition that, especially in the design of an ORC machine, the possibility of an occurrence of cavitation in the liquid phase is underestimated. So it happens that in the overall design, for example, a specified for a pump flow height is not met. Such a flow height caused by the fluid column at the intake there is a necessary pressure increase. Because of the upstream condenser namely the fluid is without regard to the flow height of the pump with the saturation or condensation vapor pressure, assuming that no hypothermia takes place. When the pump is switched on, the saturation vapor pressure can then be exceeded without regard to the flow height due to the resulting suction power. It comes to cavitation.
  • the flow height for a pump is typically given by the so-called NPSH value.
  • the NPSH value (Net Positive Suction Head) is understood to mean the necessary minimum inlet height above the saturation vapor pressure. In other words, the necessary NPSH value expresses the suction power of the pump.
  • the NPSH value is given in meters. It is typically a few meters for a pump suitable here. Therefore, if the NPSH value is not met for a given pump in advance, it will happen during the Operation to not insignificant cavitation problems. There is an undesirable formation of vapor bubbles.
  • the pump has to be lowered relative to the system level, especially in the design of a small and compact ORC machine, which leads to an undesirable increase in installation space.
  • the invention now recognizes that the problem of the formation of cavitations in a thermodynamic machine can be solved by the use of a noncondensing gas. While hitherto in the machines operating in the Rankine cycle, the non-condensing gas in circulation has been undesirably removed since the efficiency has been lowered, the invention now deliberately introduces it.
  • the invention recognizes that, in the case of a non-condensing gas in circulation, its partial pressure in the gas phase adds to the condensation pressure.
  • the resulting system pressure which has been raised in the desired manner, is impressed on the liquid working fluid, in particular in the supply line of the fluid pump.
  • the disadvantages associated with the addition of a non-condensing gas to the circuit in particular an increase in the backpressure for the expansion machine, are eliminated in the case of a low-boiling working fluid by the advantages of avoiding cavitation.
  • condensation is made with water at higher pressures. Typically, at room temperature be condensed above atmospheric pressure.
  • the partial pressure necessarily generated by the auxiliary gas has less effect on the overall efficiency in the sense of the overall concept and negligible.
  • the invention makes it possible to choose the added amount of substance of the auxiliary gas so that the flow height for the pump in the sense of the available space can be reduced accordingly.
  • the counterpressure hindering the expansion machine remains at a generally acceptable level.
  • the invention offers the distinct advantage that a compact thermodynamic machine for the utilization of low-temperature heat sources can be designed.
  • the space is no longer mandatory given by the necessary flow height of the pump. Since, in principle, the non-condensing auxiliary gas can be introduced once during filling of the system, if necessary even no additional structural measures are required.
  • the invention offers an extremely cost-effective option for further compaction of a thermodynamic machine.
  • the invention is thus outstanding, to design small mobile machines that are used for example on motor vehicles for the use of engine, coolant or exhaust heat.
  • auxiliary gas partial pressure is sufficiently large, so that the saturation vapor pressure is not exceeded in the flow during operation of the liquid pump.
  • this is the case, for example, when the resulting partial pressure is at least equal to the NPSH value of the liquid pump.
  • a flow height of the pump may possibly even be omitted altogether.
  • the amount of auxiliary gas supplied must be such that the resulting partial pressure exceeds the suction pressure or the converted NPSH value.
  • thermodynamic machine operating on the Rankine cycle.
  • a machine which does not comprise any evaporation of the working fluid upstream of the expansion machine but in which a flash evaporation of the working fluid takes place in the expansion machine through a continuously increasing working space.
  • continuous phase conversions can be made.
  • mixtures of different working media can also be used as the working fluid so as to achieve an ideal mode of operation of the machine adapted to the given conditions.
  • auxiliary gas By an added non-condensing auxiliary gas (right part of the image FIG. 2 ) results in a system pressure at the pump, which is added from the saturation vapor pressure p S and the partial pressure p part of the auxiliary gas. After switching on the pump, this system pressure is again reduced by the suction pressure p NPSH specified by the NPSH value. If the partial pressure p part of this noncondensing gas resulting from the introduced auxiliary gas is greater than or at least equal to the suction pressure p NPSH at the intake manifold of the pump, then the inlet pressure p E is at least equal to or greater than the saturation vapor pressure p s . Cavitation is thus prevented.
  • the amount of substance x i of the auxiliary gas is then dimensioned such that sufficient auxiliary gas is present even under unfavorable conditions, that is to say with reduced condensation temperatures and thus reduced saturation vapor pressures. It should also be noted that part of the auxiliary gas goes into solution and thus is no longer available for generating a pressure difference. Also, different operating phases of the machine (partial load, full load) can be taken into account in the dimensioning of the supplied amount of material of the auxiliary gas.
  • the height can be correspondingly reduced by the fact that the actual flow height of the liquid pump with respect to a necessary flow height, which takes into account the NPSH value and optionally a supercooling of the liquid working fluid is reduced.
  • the necessary flow height will decrease due to the reduced vapor pressure.
  • further reduction of the actual flow height is given by the partial pressure of the introduced auxiliary gas. In this case, to maintain certain reserves even a low flow height can be maintained despite appropriate supply of the auxiliary gas.
  • a reduction of the flow height is compensated insofar by a corresponding amount of substance of the auxiliary gas.
  • the introduction point for the auxiliary gas can in principle be provided at any point in the circulation system of the machine.
  • the introduction point can be designed here for a single introduction or for a repeated introduction of the auxiliary gas.
  • a preferred embodiment is a Einbringstelle provided for the auxiliary gas between the expansion machine and the liquid pump.
  • the auxiliary gas is available directly at the required point in the circulation.
  • the auxiliary gas is introduced into the liquid phase on the cold side of the cyclic process.
  • the auxiliary gas can also be easily removed there, since it can be collected in the condenser.
  • the machine can be "cold run", whereby the auxiliary gas flows slowly into the condenser.
  • a compressor may be used to add the auxiliary gas.
  • a pressure bottle can be connected.
  • An addition of the auxiliary gas on the hot side of the cycle is associated with additional expense.
  • the non-condensing auxiliary gas is such a gas which does not condense under the conditions prevailing or prevailing in the cycle of the thermodynamic machine.
  • auxiliary gas for example, noble gases or nitrogen are suitable as such an auxiliary gas.
  • suitable organic gases come into question.
  • the non-condensing auxiliary gas will move to some extent with the working fluid in the cycle of the thermodynamic machine.
  • water is provided for the condenser, so-called tube bundle heat exchangers.
  • the tubes are flowed through by a cooling liquid inside.
  • the gaseous working fluid flows along the outside of the tubes, condenses on their surface and drips off as condensate or liquid phase.
  • the non-condensing auxiliary gas optionally accumulates in such a condenser depending on its orientation.
  • the auxiliary gas remains as an insulating layer around the tubes, thereby reducing the efficiency of the condenser.
  • the non-condensing auxiliary gas can only be reduced by a withdrawal against the flow direction of the condensate or by diffusion.
  • the condenser is advantageously configured to entrain the auxiliary gas in the flow direction of the condensate or of the liquid working fluid.
  • a capacitor is designed, for example, as an air condenser or by means of plate heat exchange elements.
  • the gaseous working fluid flows through the interior of pipes, which are flowed around outside, for example, by air, but also by another coolant.
  • the auxiliary gas is at least partially pushed by subsequent gaseous working fluid through the tubes in the flow direction.
  • capacitors which are formed by means of plate heat exchange elements. Again, the gaseous working fluid flows through the interstices of the plate heat exchange elements and will take part of the auxiliary gas from the condenser. The given for a tube bundle heat exchanger undesirable effect of forming an insulating layer is thereby reduced.
  • a sensor for detecting the auxiliary gas concentration is arranged in the reservoir.
  • a sensor for detecting the auxiliary gas concentration is arranged in the reservoir.
  • substance amount of the auxiliary gas can be measured and when falling below or exceeding a predetermined limit, a warning signal can be output. According to the warning signal then a certain amount of substance of the auxiliary gas can be supplied or withdrawn.
  • thermodynamic machine is particularly suitable for a mobile system in a motor vehicle, wherein the heat exchanger is thermally coupled to a waste heat source of the vehicle.
  • a waste heat source constitutes, for example, the coolant, other equipment such as e.g. Oil, the engine block itself or the exhaust gas.
  • the expansion machine coupled to generate electricity with a corresponding generator is preferably designed as a positive displacement machine.
  • a displacement machine is for example a screw or piston expansion machine or a scroll expansion machine.
  • a vane machine can be used.
  • the object directed to a method according to the invention is achieved by the feature combination according to claim 9. Accordingly, it is provided for a method for operating a thermodynamic machine that the fluid pressure in a pump flow by adding a non-condensing auxiliary gas, a system pressure-increasing partial pressure is impressed.
  • FIG. 1 is schematically shown an ORC machine 1, as it is particularly suitable as a mobile system for utilizing the waste heat of internal combustion engines.
  • the ORC machine 1 comprises, in a circulation system 2 as a heat exchanger 3, an evaporator, an expansion machine 5, a condenser 6 and a liquid pump 8.
  • the illustrated ORC machine 1 operates according to the Rankine cycle, wherein the expansion machine 5 Work to drive a generator 9 is performed.
  • the generator 9 is designed in particular for feeding in the recovered current into the vehicle's on-board electrical system or connected thereto.
  • the working fluid 10 a hydrocarbon is used, which has a significantly higher vapor pressure compared to water.
  • the working fluid 10 is in a closed circuit.
  • liquid working fluid 10 is evaporated in the evaporator 3 at a high pressure.
  • the expansion machine 5 which is designed as a positive displacement machine, the gaseous working fluid 10 relaxes while performing the work.
  • the expanded gaseous working fluid 10 is condensed in the condenser 6 at low pressure.
  • the saturation vapor pressure in the condenser 6 is about 1.2 bar.
  • the condensate or the liquid working fluid 10 is collected in a storage tank 11 before it is again pumped by the pump 8 for evaporation.
  • a waste heat removal 14 is provided for cooling the condenser 6, .
  • this may be circulating air of a motor vehicle, wherein the heat of condensation of the working fluid of the circulating air is supplied for heating the passenger compartment, for example.
  • the condenser 6 is designed as an air condenser in which the working fluid 10 to be cooled flows in the interior of flow-around tubes.
  • the heat is supplied to the evaporator 3 via a waste heat supply 16.
  • the evaporator 3 is supplied via a suitable heat exchange heat from the exhaust gas of the vehicle engine.
  • heat can be supplied from the cooling circuit of the internal combustion engine.
  • the waste heat of the internal combustion engine and the exhaust gas generated can be supplied to the evaporator 3 in total via a corresponding third medium.
  • a supply point 18 for introducing a non-condensing auxiliary gas 20 into the circuit of the ORC machine 1 is provided on the condenser 6.
  • a specific amount of substance x i of the auxiliary gas 20 can be introduced into the circulation of the ORC machine.
  • the amount of substance x i is dimensioned so that in the flow of the pump 8, the partial pressure of the auxiliary gas 20 and the saturation vapor pressure of the working fluid 10 (resulting from the condensation in the condenser 6) added to a system pressure such that after switching on the pump, the saturation vapor pressure of Working fluid is not fallen below.
  • the amount of substance x i is dimensioned such that the resulting partial pressure of the auxiliary gas is greater than the suction pressure corresponding to the NPSH value of the pump. In this respect, cavitation is prevented in the flow and in particular at the suction nozzle of the liquid pump. Since the saturation vapor pressure of the working fluid 10 does not fall below during operation, there are no vapor bubbles formed there.
  • the flow height 21 (shown schematically here) is clearly lowered compared to the NPSH value of the liquid pump 8 to only a few tens of centimeters.
  • a sensor 22 for measuring the concentration of the auxiliary gas 20 is arranged in the storage tank 11.

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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)
EP10782537.4A 2009-11-14 2010-10-30 Thermodynamische maschine sowie verfahren zu deren betrieb Active EP2499343B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10782537T PL2499343T3 (pl) 2009-11-14 2010-10-30 Maszyna termodynamiczna oraz sposób jej eksploatacji

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009053390A DE102009053390B3 (de) 2009-11-14 2009-11-14 Thermodynamische Maschine sowie Verfahren zu deren Betrieb
PCT/EP2010/006640 WO2011057724A2 (de) 2009-11-14 2010-10-30 Thermodynamische maschine sowie verfahren zu deren betrieb

Publications (2)

Publication Number Publication Date
EP2499343A2 EP2499343A2 (de) 2012-09-19
EP2499343B1 true EP2499343B1 (de) 2013-12-11

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Country Status (14)

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US (1) US8646273B2 (pl)
EP (1) EP2499343B1 (pl)
JP (1) JP5608755B2 (pl)
KR (1) KR101752160B1 (pl)
CN (1) CN102639818B (pl)
BR (1) BR112012011409B1 (pl)
CA (1) CA2780791C (pl)
DE (1) DE102009053390B3 (pl)
ES (1) ES2447827T3 (pl)
IL (1) IL219426A (pl)
MX (1) MX2012005586A (pl)
PL (1) PL2499343T3 (pl)
RU (1) RU2534330C2 (pl)
WO (1) WO2011057724A2 (pl)

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WO2011057724A2 (de) 2011-05-19
US8646273B2 (en) 2014-02-11
KR101752160B1 (ko) 2017-06-29
RU2534330C2 (ru) 2014-11-27
EP2499343A2 (de) 2012-09-19
KR20120115225A (ko) 2012-10-17
WO2011057724A3 (de) 2011-10-13
CA2780791A1 (en) 2011-05-19
JP2013510984A (ja) 2013-03-28
RU2012124416A (ru) 2013-12-20
CA2780791C (en) 2015-06-02
CN102639818A (zh) 2012-08-15
IL219426A0 (en) 2012-06-28
CN102639818B (zh) 2015-03-25
PL2499343T3 (pl) 2014-05-30
DE102009053390B3 (de) 2011-06-01
IL219426A (en) 2016-10-31
MX2012005586A (es) 2012-05-29
BR112012011409B1 (pt) 2020-02-11
JP5608755B2 (ja) 2014-10-15
BR112012011409A2 (pt) 2016-05-03
ES2447827T3 (es) 2014-03-13

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