WO2010009839A2 - Dispositif à cycle à vapeur et procédé de commande de ce dispositif - Google Patents

Dispositif à cycle à vapeur et procédé de commande de ce dispositif Download PDF

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Publication number
WO2010009839A2
WO2010009839A2 PCT/EP2009/005194 EP2009005194W WO2010009839A2 WO 2010009839 A2 WO2010009839 A2 WO 2010009839A2 EP 2009005194 W EP2009005194 W EP 2009005194W WO 2010009839 A2 WO2010009839 A2 WO 2010009839A2
Authority
WO
WIPO (PCT)
Prior art keywords
working fluid
expander
evaporator
liquid
flow
Prior art date
Application number
PCT/EP2009/005194
Other languages
German (de)
English (en)
Other versions
WO2010009839A3 (fr
Inventor
Jürgen Berger
Michael Bucher
Christian Bausch
Original Assignee
Voith Patent Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Voith Patent Gmbh filed Critical Voith Patent Gmbh
Priority to EP09777252A priority Critical patent/EP2432973A2/fr
Priority to US12/737,420 priority patent/US20110167823A1/en
Publication of WO2010009839A2 publication Critical patent/WO2010009839A2/fr
Publication of WO2010009839A3 publication Critical patent/WO2010009839A3/fr

Links

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
    • 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
    • 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
    • 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
    • F01K9/04—Plants characterised by condensers arranged or modified to co-operate with the engines with dump valves to by-pass stages

Definitions

  • the invention relates to a steam cycle device and a method for controlling the same, wherein the steam cycle device in particular forms part of a vehicle drive or auxiliary drive in a vehicle.
  • Steam cycle processes for example a Clausius-Rankine process, for generating mechanical power from a heat flow are known and can be driven, for example, by a separate burner unit in a combined heat and power device.
  • steam cycle processing devices are preferably used to use waste heat of an internal combustion engine, depending on the choice of the working fluid and the temperature control of the steam cycle as heat sources of the cooling water flow of the internal combustion engine or preferably their exhaust gas flow serve.
  • the CH 171813 describes a steam power plant with a steam cycle, in which, viewed in the flow direction of the working fluid, the following components are arranged one behind the other: a feed pump, an evaporator, a
  • a shut-off valve is arranged, by means of which the influx of vaporized working fluid to the steam turbine can be completely interrupted.
  • a first bypass is provided downstream of the feed pump.
  • a second bypass is provided by means of which vaporous working fluid can be conducted past the steam turbine. Both bypasses can be connected to one another in a flow-conducting manner via corresponding control valves.
  • the second bypass is always opened when the shut-off valve is closed in the supply line to the steam turbine and the steam turbine is to be stopped or when pressure peaks occur in the steam cycle as a result of closing the shut-off valve. Since in the case of closing the shut-off valve evaporated working fluid would rest in the supply line, the superheater would be destroyed due to the ever increasing heat input - because the heat energy to overheat the steam is not transmitted to the flowing working fluid and discharged from this. For this reason, when closing the shut-off valve, the control valves in the first and second
  • the vaporized, bypassed working medium thereby collapses in the connecting line and is then fed via the second bypass to the condenser for further removal of heat.
  • the two bypasses thus provide only a safety device to prevent the destruction of the superheater and continue to serve to reduce pressure peaks in the circuit due to the closing of the valve in the live steam supply to the expander. With this arrangement, no power control of the expander is expressly provided.
  • Bypass lines restrictor to maintain the pressure drop across the pump. Due to the design of the disclosed bypass lines in the case of the opening of the bypass line, only a pressure peak degraded, so that the disclosed device does not allow control of the volume flow and / or pressure of the working fluid in the supply line to the evaporator along a setpoint curve, instead, the measures described above are taken only in the case of overpressure. The same applies to the pump device in the supply line to the burner.
  • the published patent application DE 195 24 171 A1 describes a low-temperature engine (refrigerating machine) for driving working machines with a gas as working fluid.
  • liquid gas is conveyed by means of a pump and fed to an evaporator.
  • the vaporized gas performs work in a flash machine and is subsequently cooled and liquefied in a flash (condenser).
  • the liquefied working fluid is then fed to a fluid collector (tank) and conveyed from there via the pump again.
  • a bypass is provided, seen in the flow direction of the working fluid behind the pump, branches off a part of the liquid working fluid and this the already relaxed, cooled and thus liquid working fluid flowing from the condenser, supplies.
  • a portion of the working fluid flowing out of the pump is supplied directly to the fluid collector.
  • the working fluid pump rotatably from the
  • the working fluid pump runs in response to the internal combustion engine speed, so that the funded working fluid flow is proportional to the speed of the internal combustion engine.
  • the working fluid pump runs in response to the internal combustion engine speed, so that the funded working fluid flow is proportional to the speed of the internal combustion engine.
  • correspondingly larger-sized pumps are used.
  • this also means that due to the torsionally rigid coupling at maximum speeds of the engine, a correspondingly high working medium volume flow to the evaporator is generated.
  • the subsidized by the working fluid pump Working medium volume flow is thus significantly greater than the required volume flow for the evaporator or the expander.
  • the invention has for its object to provide a Dampf Vietnamese remedies and a method for controlling the same, which make it possible, especially for applications in a motor vehicle or its drive train, the capacitor smaller and lighter than previously run.
  • a separate, variable-speed adjustable drive machine for the working fluid pump and yet the delivery volume of the evaporator or expander supplied working fluid for the purpose of power adjustment made variable, or the pressure of the working fluid in the supply line to the evaporator can be adjusted according to a target specification ,
  • a structurally and production-technically simple solution is sought, which takes up a small space and also works energy-efficient.
  • the inventors have recognized that by branching off at least part of the working medium volume flow upstream of the working medium pump and feeding the diverted part to the working fluid leaving the expander downstream, reduces the abriosfiguration and the capacitor can be structurally made smaller.
  • a steam cycle device comprises a reservoir for a liquid working fluid and an evaporator in which the working fluid is vaporized by supplying heat, the vaporous working fluid being fed to an expander for relaxation and mechanical work and subsequently liquefied in a condenser communicating with the reservoir stands.
  • a working fluid pump for supplying working fluid from the reservoir to the evaporator is provided. In this case, in the working fluid flow direction before or in the region of the condenser, liquid working fluid is supplied to the working fluid emerging from the expander.
  • the invention can be used particularly advantageously in motor vehicles, especially rail, truck or passenger cars, it is also conceivable to use the steam cycle apparatus according to the invention or the control method according to the invention in other mobile devices or stationary systems, in particular for exhaust gas energy recovery in industrial plants.
  • the expander could then be used to drive aggregates.
  • bypass line for supplying the liquid working fluid is provided, which establishes a connection between an output side of the working fluid pump and an input side of the capacitor.
  • the bypass line for example, open directly in the pressure chamber of the working fluid pump, so be disposed within the working fluid pump or in a connecting line to the evaporator.
  • the other end of the bypass line may open directly in the condenser or in a line in the working direction before the condenser.
  • bypass line opens with its one end in a line between the expander and the condenser.
  • an orifice may for example be designed as a T-shaped connecting pipe. But other forms are conceivable.
  • bypass line opens with its one end directly in the expander.
  • the mouth can, for example, in
  • Outlet area so be provided downstream of the expansion space of the expander, so that the supply of liquid, passed by the evaporator working fluid takes place in the expander.
  • the working medium supplied via the bypass line to the outlet of the expander or to the inlet of the condenser is essentially in a (single) physical state, namely the liquid state.
  • a single state of aggregation means that it is assumed that the state variables of the working medium can not change suddenly, as described e.g. in the case of cavity.
  • the mixture of the liquid phase of the branched off via the bypass line working fluid with the vaporous phase of the exhaust steam of the expander takes place only in the exhaust steam of the expander leading line or in the condenser.
  • the supply of liquid, diverted from the evaporator working fluid to the expander leaving, usually completely vaporous working fluid has the advantage that the steam is condensed or at least partially liquefied.
  • the collapse of the vapor at the point of supply of the liquid working fluid results in an improved heat transfer and a reduced volume of working fluid flowing from the expander into the condenser, so that the heat transfer surface can be made smaller to dissipate the waste heat in the condenser.
  • at least the same amount of heat as in conventional larger capacitors without supply of liquid working fluid can be dissipated in the capacitor despite smaller dimensions.
  • the liquid surface of the liquid working medium is increased.
  • An enlargement of the liquid surface can be done for example by atomizing the branched liquid working medium.
  • air can be supplied to the liquid working medium in the manner of an aerosol, so that a spray mist is formed.
  • Such atomization can be done for example by means of a Venturi nozzle.
  • the liquid working fluid can be transferred through a suitable nozzle in a kind of spray.
  • the advantage of atomization also lies in the fact that the working fluid leaving the expander is better mixed with the supplied liquid working fluid.
  • a controllable valve may be provided, by means of which the pressure and / or flow rate of the working medium in the supply line to the evaporator (indirectly) is controlled / controlled.
  • the amount of working fluid, ie, the volume flow of the (liquid) working medium flowing into the evaporator is varied as a function of the temperature of the (vaporous) working medium leaving the evaporator, by diverting a certain partial volume flow of liquid working fluid, bypassing the evaporator and bypassing the evaporator, the outlet of the expander or the inlet of the capacitor is supplied.
  • the diverted volume flow can be adjusted, for example, by changing the opening cross-section of the controllable valve.
  • the opening cross section of the valve in the bypass line is varied as a function of the temperature of the working fluid leaving the evaporator in order to evaporate more or less liquid working fluid.
  • an inflow control ie an indirect Adjustment of the pressure or volume flow of the vaporized working fluid as a function of the liquid working medium achieved.
  • these sensors can be in the evaporator, expander or the corresponding
  • the pressure and / or volume flow of the vaporous working medium produced in the evaporator can be adjusted or varied to the expander depending on the power requirement on the expander.
  • the volume flow and / or pressure profile of the working fluid in the supply line to the evaporator (and thus the flow and / or pressure profile of the vaporized working medium to the expander) follow a predetermined setpoint curve, which can be adjusted via the control / regulating device.
  • Internal combustion engine can be optimally used. For example, at an operating point of the internal combustion engine in which relatively much heat is obtained (high engine load, high engine speed) of bypassed via the bypass liquid working fluid flow to the expander emerging from the working medium (steam) are supplied, whereby the vapor collapses and liquefied.
  • Such a regulation / control can preferably always, ie during operation of the internal combustion engine and especially when relatively particularly much waste heat, take place.
  • the working medium volume flow conveyed by the working medium pump varies independently of a desired value for the pressure and / or the volume flow of the working medium to the evaporator, and the working medium volume flow supplied to the evaporator and / or expander is regulated and / or controlled by a part of the working medium volume flow from the working fluid pump is supplied to the emerging from the expander working fluid and thus does not enter the evaporator.
  • FIG. 1 schematically simplifies an embodiment of a steam cycle device according to the invention.
  • Figure 2 shows a further embodiment of an inventive
  • FIG. 1 shows schematically the basic components of a steam cycle device.
  • a working fluid pump 1 to the evaporator 2.
  • the evaporator 2 the evaporation of the working fluid, wherein the necessary for this thermal energy is supplied from a burner unit, not shown in detail.
  • the steam cycle device is part of a vehicle drive with an internal combustion engine whose waste heat heats the working fluid in the evaporator 2.
  • the exhaust gases of an internal combustion engine come into consideration, wherein the components necessary for the simplification of the representation are not shown in detail in Figure 1.
  • the evaporator 2 can be constructed in several stages, in particular, a superheating unit for the vapor phase can be provided.
  • the working fluid is supplied in the vapor state from the evaporator 2 to the expander 3 via a line 8 in which this performs mechanical work under relaxation. Following the expander 3, the working fluid in the condenser 4 is liquefied and returned to the reservoir 5.
  • the expander 3 which can also be generally referred to as a steam-driven engine, is designed, for example, as a piston engine, steam turbine or centrifugal machine.
  • an internal gear pump is used, the speed of which is set independently of the volume flow specification in the supply line to the evaporator 2.
  • a bypass line 7 which opens with its one end in the condenser 4 and thus mixes liquid working fluid with the flowing from the expander 3 in the condenser 4 vaporous working fluid.
  • the bypass line 7 comprises a valve 6, which may be designed, for example, as a controlled overflow valve or pressure relief valve. It may also be an electrically, electromagnetically, pneumatically or mechanically operable Proportional valve act.
  • the valve 6 can be actuated, for example, by a central control unit, such as an on-board computer.
  • suitable sensors may be arranged for receiving pressure in the valve 6 and / or in the bypass line 7, which send signals for control or control to a central control unit.
  • FIG. 2 shows a further exemplary embodiment of a steam cycle device according to the invention, wherein the same reference numerals as in FIG. 1 are used for matching components.
  • FIG. 2 shows a further exemplary embodiment of a steam cycle device according to the invention, wherein the same reference numerals as in FIG. 1 are used for matching components.
  • Embodiment empties the bypass line 7 in a line 8, which expander 3 and capacitor 4 connects working medium conducting each other.
  • the bypass line 7 discharges directly into the line 8 leading from the expander 3, where the liquid phase from the bypass line 7 mixes with the substantially vaporous phase of the working medium (exhaust steam from the expander 3).
  • the connection point can be designed, for example, as a T-shaped connecting tube.
  • a nozzle may be provided which atomizes the liquid working fluid from the bypass line 7.
  • the nozzle may also be arranged in the bypass line 7. Through the nozzle should a
  • Atomization can be carried out, for example, by sucking in or supplying air, such as ambient air. It is of course also conceivable to apply the branched liquid working fluid from the bypass line 7 in the connecting pipe or in the feed line by wetting on the inner sides of the line 8 or the connecting pipe.
  • the working fluid is at the outlet of the working fluid pump 1 or downstream of the working fluid pump 1, before or in the area branched off the evaporator 2 and fed to the vaporous working fluid of the expander 3 for cooling.

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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)

Abstract

L'invention concerne un dispositif à cycle à vapeur comprenant un réservoir destiné à recevoir un fluide de travail liquide; un évaporateur dans lequel le fluide de travail est évaporé par apport de chaleur, le fluide de travail sous forme de vapeur étant acheminé dans un détendeur servant à produire une détente et fournir un travail mécanique, puis condensé dans un condenseur relié au réservoir; ainsi qu'une pompe à fluide de travail servant à acheminer du fluide de travail du réservoir à l'évaporateur. L'invention se caractérise en ce que du fluide de travail liquide est acheminé en amont ou dans la région du condenseur, dans le sens d'écoulement du fluide de travail, dans le fluide de travail sortant du détendeur.
PCT/EP2009/005194 2008-07-25 2009-07-17 Dispositif à cycle à vapeur et procédé de commande de ce dispositif WO2010009839A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP09777252A EP2432973A2 (fr) 2008-07-25 2009-07-17 Dispositif à cycle à vapeur et procédé de commande de ce dispositif
US12/737,420 US20110167823A1 (en) 2008-07-25 2009-07-17 Steam circuit process device and method for controlling the same

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008034977A DE102008034977A1 (de) 2008-07-25 2008-07-25 Dampfkreisprozessvorrichtung und Verfahren zur Steuerung derselben
DE102008034977.1 2008-07-25

Publications (2)

Publication Number Publication Date
WO2010009839A2 true WO2010009839A2 (fr) 2010-01-28
WO2010009839A3 WO2010009839A3 (fr) 2012-03-01

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Application Number Title Priority Date Filing Date
PCT/EP2009/005194 WO2010009839A2 (fr) 2008-07-25 2009-07-17 Dispositif à cycle à vapeur et procédé de commande de ce dispositif

Country Status (4)

Country Link
US (1) US20110167823A1 (fr)
EP (1) EP2432973A2 (fr)
DE (1) DE102008034977A1 (fr)
WO (1) WO2010009839A2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130133328A1 (en) * 2010-08-26 2013-05-30 Michael Joseph Timlin, III The Timlin Cycle - A Binary Condensing Thermal Power Cycle
FR2985767A1 (fr) * 2012-01-18 2013-07-19 IFP Energies Nouvelles Dispositif de controle d'un fluide de travail dans un circuit ferme fonctionnant selon un cycle de rankine et procede utilisant un tel dispositif

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Publication number Priority date Publication date Assignee Title
DE102010027068A1 (de) * 2010-07-13 2012-01-19 Behr Gmbh & Co. Kg System zur Nutzung von Abwärme eines Verbrennungsmotors
US10195561B2 (en) * 2012-09-20 2019-02-05 Mitsubishi Heavy Industries Engineering, Ltd. Steam supply system and CO2 recovery unit including the same
NO335230B1 (no) * 2013-02-19 2014-10-27 Viking Heat Engines As Anordning og framgangsmåte for drifts- og sikkerhetsregulering ved en varmekraftmaskin
JP6044529B2 (ja) * 2013-12-05 2016-12-14 トヨタ自動車株式会社 廃熱回収装置

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FR1253121A (fr) * 1960-04-05 1961-02-03 Licentia Gmbh Dispositif pour la commande d'installation de turbines à vapeur
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US4020637A (en) * 1975-01-27 1977-05-03 Nissan Motor Co., Ltd. Vehicle steam engine using on-off valves for controlling steam temperature and pressure
US4391101A (en) * 1981-04-01 1983-07-05 General Electric Company Attemperator-deaerator condenser
DE19524171A1 (de) * 1995-07-03 1997-01-09 Rauscher Georg Niedertemperaturmotor (NTM), Tieftemperaturmotor (TTM) bzw. Kältekraftmaschine (KKM)

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Publication number Priority date Publication date Assignee Title
US3174288A (en) * 1959-10-16 1965-03-23 Sulzer Ag Steam power plant
FR1253121A (fr) * 1960-04-05 1961-02-03 Licentia Gmbh Dispositif pour la commande d'installation de turbines à vapeur
US4020637A (en) * 1975-01-27 1977-05-03 Nissan Motor Co., Ltd. Vehicle steam engine using on-off valves for controlling steam temperature and pressure
US4391101A (en) * 1981-04-01 1983-07-05 General Electric Company Attemperator-deaerator condenser
DE19524171A1 (de) * 1995-07-03 1997-01-09 Rauscher Georg Niedertemperaturmotor (NTM), Tieftemperaturmotor (TTM) bzw. Kältekraftmaschine (KKM)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130133328A1 (en) * 2010-08-26 2013-05-30 Michael Joseph Timlin, III The Timlin Cycle - A Binary Condensing Thermal Power Cycle
FR2985767A1 (fr) * 2012-01-18 2013-07-19 IFP Energies Nouvelles Dispositif de controle d'un fluide de travail dans un circuit ferme fonctionnant selon un cycle de rankine et procede utilisant un tel dispositif
WO2013107949A3 (fr) * 2012-01-18 2014-12-24 IFP Energies Nouvelles Dispositif de contrôle d'un fluide de travail dans un circuit fermé fonctionnant selon un cycle de rankine et procédé utilisant un tel dispositif
CN105593477A (zh) * 2012-01-18 2016-05-18 Ifp新能源公司 用于控制在根据兰金循环运行的闭合环路内工作流体的装置及使用所述装置的方法

Also Published As

Publication number Publication date
WO2010009839A3 (fr) 2012-03-01
DE102008034977A1 (de) 2010-03-25
EP2432973A2 (fr) 2012-03-28
US20110167823A1 (en) 2011-07-14

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