US20130205783A1 - Steam turbine - Google Patents

Steam turbine Download PDF

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Publication number
US20130205783A1
US20130205783A1 US13/879,564 US201113879564A US2013205783A1 US 20130205783 A1 US20130205783 A1 US 20130205783A1 US 201113879564 A US201113879564 A US 201113879564A US 2013205783 A1 US2013205783 A1 US 2013205783A1
Authority
US
United States
Prior art keywords
nozzles
steam turbine
rotor
steam
stator
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.)
Abandoned
Application number
US13/879,564
Other languages
English (en)
Inventor
Ilona Krinn
Juergen Stegmaier
Manfred Schmitt
Bernd Banzhaf
Nadja Eisenmenger
Juergen Hilzinger
Patrick Glaser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: EISENMENGER, NADJA, STEGMAIER, JUERGEN, SCHMITT, MANFRED, KRINN, ILONA, BANZHAF, BERND, HILZINGER, JUERGEN, GLASER, PATRICK
Publication of US20130205783A1 publication Critical patent/US20130205783A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00—Steam engine plants not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/18—Final actuators arranged in stator parts varying effective number of nozzles or guide conduits, e.g. sequentially operable valves for steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/60—Application making use of surplus or waste energy
    • F05D2220/62—Application making use of surplus or waste energy with energy recovery turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/01—Purpose of the control system
    • F05D2270/16—Purpose of the control system to control water or steam injection

Definitions

  • the invention relates to a steam turbine, in particular for using the waste heat of an internal combustion engine.
  • a steam turbine is known from the German patent application DE 42 14 775 A1, which can be operated at different load conditions.
  • Said steam turbine is characterized by a plurality of nozzle groups of the same design in the stator.
  • the steam inflow to each nozzle group is adjusted with a control valve.
  • a control valve In the case of a low load demand, only one nozzle or one nozzle group is activated.
  • steam is applied to one nozzle group after the other.
  • the control of the steam supply takes place thereby by means of the control slots of a rotary slide valve. It is also common to employ automatic regulators.
  • the steam turbine according to the invention has the advantage that a particularly large power spectrum can be covered by the steam turbine through the use of nozzles, which are designed for different load points and can be switched on and off independently from each other.
  • the different designs of the nozzles can be simply and advantageously predefined by the geometry thereof, the area ratio between the narrowest nozzle cross section and the outlet cross section, the amount of unblocked flow cross section and/or the angle of inclination of the nozzle with respect to the rotor.
  • the requirement for a large power spectrum occurs especially in steam turbines which are employed for using the waste heat of an internal combustion engine that is operated in a motor vehicle. It is thus particularly advantageous for the different operating points of the internal combustion engine to correspond to the different load points of the rotor.
  • the boundary conditions steam quantity, temperature, pressure
  • An optimal utilization of the energy provided by the internal combustion engine can be achieved by switching differently designed nozzles on and off because said nozzles are adapted to the respective boundary conditions.
  • Laval nozzles are expediently employed for the acceleration of the steam in the stator.
  • the steam can thereby be accelerated from ultrasonic velocity to supersonic velocity.
  • a particularly high power output of the steam turbine can be achieved.
  • partially impinged turbines is advantageous because the diameter of the rotor can be increased by means of the partial impingement, and design sizes of turbines which are small and difficult to implement can thereby be avoided.
  • a further advantage results if the nozzles of the steam turbine are switched on and off via switching equipment consisting of control valves or aperture plates. Such switching equipment makes a plurality of possible nozzle combinations available.
  • Switching equipment which is controlled via a pressure difference present at the stator, is particularly advantageous because the switching of the nozzles on and off can be optimally adapted to the prevailing boundary conditions. It is useful for the switching equipment to be actuated via a servomotor, in particular a multiphase motor, as this allows for a simple and cost effective implementation option.
  • the nozzle which serves as the nozzle bypass, changes the direction of the steam jet in such a manner that a resulting torque is not produced at the rotor. In so doing, a power output of the steam turbine during deceleration is prevented.
  • a steam turbine having the previously mentioned features is particularly advantageous if said turbine is disposed in a circuit comprising a feed pump, heat exchanger and condenser and the heat exchanger serves the purpose of using the waste heat of an internal combustion engine and produces the steam which is supplied to the nozzles of the stator. This is the case because a particularly broad power spectrum results from this disposal.
  • FIG. 1 shows a steam turbine in a schematic depiction according to a first exemplary embodiment.
  • FIG. 2 shows a Laval nozzle in perspective depiction.
  • FIG. 3 shows a steam turbine in schematic depiction according to a second exemplary embodiment
  • FIG. 4 shows a steam turbine comprising a circuit in a schematic depiction.
  • FIGS. 1 and 3 show a steam turbine 10 in a schematic depiction comprising a rotor 26 , a stator 20 and switching equipment 28 . At least two nozzles 22 are disposed in the stator 20 , which convert the potential energy of the steam into kinetic energy in said stator 20 .
  • the nozzles 22 are disposed in parallel in relation to each another in the stator 20 ; and therefore the steam enters in a plane which is the same for all nozzles 22 and is perpendicular to the main flow direction and leaves said nozzles 22 in another plane which is perpendicular to the main flow direction.
  • the nozzles 22 are circularly disposed in the stator 20 This can relate to a fully impinged steam turbine 10 , in which said nozzles are disposed around the entire stator 20 or to a partially impinged steam turbine 10 , in which said nozzles 22 occupy only parts or a sector of the circle of the said stator 20 .
  • the nozzles 22 are designed for different load points of the rotor 26 , wherein at least one of the nozzles 22 is designed for a high load point of the rotor 26 and at least one of the nozzles 22 is designed for a low load point of said rotor 26 .
  • the nozzles 22 are preferably Laval nozzles 24 , as they are depicted in FIG. 2 , and guide the steam in an accelerated manner onto the rotor 26 of the steam turbine 10 .
  • the Laval nozzles 24 are configured as rectangular channels having a convergent and divergent cross-sectional profile. Due to their special design, Laval nozzles 24 are capable of accelerating gas flows from subsonic to supersonic velocities.
  • the nozzles 22 can be disposed in nozzle groups or individually in the stator 20 .
  • Switching equipment 28 is disposed upstream of the stator 20 , said switching equipment switching the nozzles 22 in said stator 20 independently from each other.
  • each nozzle 22 can be opened alone while the other nozzles 22 are closed, or a plurality of nozzles 22 can be opened simultaneously. If the nozzles 22 are disposed in nozzle groups, entire nozzle groups can also be opened or closed via the switching equipment 28 .
  • the switching equipment 28 can consist of control valves or of an aperture plate and can be disposed in front of or behind the stator 20 .
  • the switching equipment 28 can be controlled via a pressure difference prevailing at the stator 28 .
  • a pressure difference prevailing at the stator 28 As a function of the prevailing pressure difference, one or a plurality of nozzles 22 adapted to this boundary condition are activated while other nozzles 22 are closed.
  • the switching equipment 28 can be actuated via a servomotor, in particular a multiphase motor.
  • the actuation of the switching equipment 28 can then actively take place by means of a servomotor or passively by using the prevailing pressure difference.
  • FIG. 3 A further exemplary embodiment is depicted in FIG. 3 , in which a further nozzle is provided, which serves as a nozzle bypass 32 , beside the nozzles 22 which serve to accelerate the steam onto the rotor 26 .
  • Said nozzle bypass 32 is not embodied as a Laval nozzle 24 because the nozzle bypass 32 is to guide the steam without acceleration onto the rotor 26 .
  • Said nozzle bypass 32 has a large flow cross section in comparison to other nozzles 22 ; and therefore the pressure in the high pressure part upstream of the steam turbine 10 reduces very quickly and the steam achieves only very low flow velocities when entering the rotor 26 . Due to the low flow velocities, no significant power output is achieved in the rotor 26 .
  • the power output of the rotor 26 can be still further reduced if the nozzle bypass 32 changes the direction of the steam jet escaping from the nozzle bypass 32 in such a manner that no resulting torque is produced. This can be brought about by said steam jet flowing against the rotor 26 in the axial direction or in the reverse direction of rotation.
  • the steam turbine 10 can also be embodied as a multistage steam turbine 10 , in which a plurality of stages consisting of stators 20 and rotors 26 is disposed one behind the other.
  • the nozzles 22 of the rotor 20 can be switched on and off via switching equipment 28 and corresponding to the two exemplary embodiments pursuant to FIG. 1 and FIG. 3 .
  • switching equipment 28 for controlling the nozzles 22 can be situated only in the first stage of the steam turbine 10 , which consists of stator 20 and rotor 26 and is situated directly behind the steam source.
  • the nozzles 22 of the downstream stages consisting of stator 20 and rotor 26 can be arranged in such a manner that said nozzles correspond from the positioning thereof to the nozzles 22 of the first stage. In so doing, the steam jet of the nozzle 22 , which is released in the first stage, should only enter into the corresponding nozzle 22 of the second stage.
  • the corresponding nozzles 22 are designed such that they achieve an optimal degree of efficiency at the prevailing boundary conditions.
  • the steam turbine 10 is particularly suited for the recovery of waste heat in applications in motor vehicles.
  • the steam turbine 10 of the invention is however also suited for other applications.
  • FIG. 4 shows a steam turbine 10 according to one of the preceding exemplary embodiments in a circuit 4 for the recovery of waste heat of an internal combustion engine 2 .
  • a heat exchanger 8 , a condenser 12 , a feed pump 6 and the steam turbine 10 are disposed in the circuit 4 containing a circulating working medium.
  • the internal combustion engine 2 burns fuel in order to produce mechanical energy.
  • the exhaust gases ensuing from this process are discharged via an exhaust gas system, in which an exhaust gas catalyst can be disposed.
  • a duct section of the exhaust gas system is led through a heat exchanger 8 . Heat energy from the exhaust gases or the exhaust gas recirculation is given off to the working medium in the heat exchanger 8 so that said working medium can be evaporated and superheated in said heat exchanger 8 .
  • the heat exchanger 8 of the circuit 4 is connected via a line to the steam turbine 10 .
  • the evaporated working medium flows via the line to said steam turbine 10 and drives the same.
  • Said steam turbine 10 has an output shaft 11 , via which said steam turbine 10 is connected to a load. In this way, mechanical energy can, for example, be transferred to a drive train or used to drive an electrical generator, a pump or something similar.
  • the working medium is led via a line to a condenser 12 .
  • the working medium which was expanded via said steam turbine 10 is cooled in the condenser 12 and condenses.
  • Said condenser 12 can be connected to a cooling circuit.
  • the working medium liquefied in said condenser 12 is transported via a line from a feed pump 6 into the line to the heat exchanger 8 .
  • a flow direction of the working medium through the circuit 4 is provided by the feed pump 6 .
  • Heat energy which can be released in the form of mechanical energy to the shaft 11 , can therefore be continuously extracted via the heat exchanger 2 from the exhaust gases and the constituent parts of the exhaust gas recirculation of the internal combustion engine 2 .
  • Water or another liquid, which corresponds to the thermodynamic requirements, can be used as the working medium.
  • the working medium experiences thermodynamic changes in state when flowing through the circuit 4 .
  • said working medium is brought by the feed pump 6 to the pressure level required for evaporation.
  • the heat energy of the exhaust gas is subsequently given off to said working medium via the heat exchanger 8 .
  • said working medium is isobarically evaporated and subsequently superheated.
  • the steam is then adiabatically expanded in the steam turbine 10 . In so doing, mechanical energy is obtained and transferred to the shaft 11 .
  • Said working medium is then cooled in the condenser 12 , liquefied and supplied again to the feed pump 6 .
  • the heat exchanger 8 produces the steam, which is available to the steam turbine 10 .
  • the steam turbine 10 has to work as a function of the operating point of the internal combustion engine 2 with other boundary conditions (amount of steam, temperature, pressure) and adapt accordingly to the load points thereof. This takes place by switching the nozzles 22 in the stator 20 of the steam turbine 10 on and off, which nozzles correspond to the different load points of the internal combustion engine 2 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
US13/879,564 2010-10-13 2011-09-19 Steam turbine Abandoned US20130205783A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010042412.9 2010-10-13
DE102010042412A DE102010042412A1 (de) 2010-10-13 2010-10-13 Dampfturbine
PCT/EP2011/066218 WO2012048987A1 (de) 2010-10-13 2011-09-19 Dampfturbine

Publications (1)

Publication Number Publication Date
US20130205783A1 true US20130205783A1 (en) 2013-08-15

Family

ID=44651838

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/879,564 Abandoned US20130205783A1 (en) 2010-10-13 2011-09-19 Steam turbine

Country Status (5)

Country Link
US (1) US20130205783A1 (zh)
EP (1) EP2627869A1 (zh)
CN (1) CN103154439B (zh)
DE (1) DE102010042412A1 (zh)
WO (1) WO2012048987A1 (zh)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3530924A1 (en) * 2018-02-27 2019-08-28 Borgwarner Inc. Waste heat recovery system and turbine expander for the same
US11015489B1 (en) * 2020-03-20 2021-05-25 Borgwarner Inc. Turbine waste heat recovery expander with passive method for system flow control
WO2022023053A1 (fr) 2020-07-29 2022-02-03 IFP Energies Nouvelles Turbine axiale orc a admission variable pilotee

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012208506A1 (de) * 2012-05-22 2013-11-28 Siemens Aktiengesellschaft Steuern der Zufuhr von Arbeitsfluid zu einer Turbine mittels einer ventilindividuellen Ansteuerung von mehreren Ventilen
DE102012211578B4 (de) * 2012-07-04 2015-02-19 Bmw Ag Vorrichtung und Verfahren zur Nutzung von Abwärme eines Verbrennungsmotors insbesondere eines Kraftfahrzeugs sowie Turbine für eine solche Vorrichtung
DE102012222671B4 (de) * 2012-12-10 2014-07-24 Bmw Ag Vorrichtung sowie Verfahren zur Nutzung von Abwärme eines Verbrennungsmotors sowie Turbinenaggregat für eine solche Vorrichtung
DE102013203903A1 (de) 2013-03-07 2014-09-11 Robert Bosch Gmbh Dampfturbine
DE102013218887A1 (de) * 2013-09-20 2015-03-26 Mahle International Gmbh Lavaldüse
DE102014225608A1 (de) * 2014-12-11 2016-06-16 Siemens Aktiengesellschaft Vorrichtung und Verfahren zur Regelung eines Dampfmassenstroms bei einer Dampfturbine
CN114607476B (zh) * 2022-03-04 2023-05-09 暨南大学 一种全负荷工况高效汽轮机组、设计方法及运行方法

Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US811249A (en) * 1905-03-23 1906-01-30 Gen Electric Governing mechanism for elastic-fluid turbines.
US811984A (en) * 1905-05-22 1906-02-06 Wilkinson Turbine Company Elastic-fluid turbine.
US2389074A (en) * 1943-09-27 1945-11-13 Westinghouse Electric Corp Turbine apparatus
US3350061A (en) * 1964-04-15 1967-10-31 Linde Ag Expansion-turbine nozzle ring and apparatus incorporating same
US3879616A (en) * 1973-09-17 1975-04-22 Gen Electric Combined steam turbine and gas turbine power plant control system
US3948054A (en) * 1973-07-27 1976-04-06 Westinghouse Electric Corporation Steam turbine blade protection system and method especially for electric power plants
US4325670A (en) * 1980-08-27 1982-04-20 Westinghouse Electric Corp. Method for admitting steam into a steam turbine
US4563989A (en) * 1982-10-15 1986-01-14 Robert Bosch Gmbh Regulation system for an internal combustion engine
US4780057A (en) * 1987-05-15 1988-10-25 Westinghouse Electric Corp. Partial arc steam turbine
US4850793A (en) * 1987-10-13 1989-07-25 Westinghouse Electric Corp. Steam chest modifications for improved turbine operations
US4979873A (en) * 1988-02-01 1990-12-25 Asea Brown Boveri Ltd. Steam turbine
US5383763A (en) * 1992-05-04 1995-01-24 Abb Patent Gmbh Steam turbine with a rotary slide for controlling steam throughput
US20100189550A1 (en) * 2007-07-10 2010-07-29 Richard Geist Rotary valve for the control of steam throughput in a steam turbine
US20110056203A1 (en) * 2008-03-06 2011-03-10 Gaertner Jan Method for recuperating energy from an exhaust gas flow and motor vehicle
US20110179793A1 (en) * 2010-01-22 2011-07-28 Robert Bosch Gmbh Method for operating an internal combustion engine having a steam power plant
US20120260654A1 (en) * 2009-10-06 2012-10-18 Thomas Proepper Driving device

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE719273C (de) * 1939-04-07 1942-04-02 Gutehoffnungshuette Oberhausen Gruppenventilsteuerung fuer Dampfturbinen
US4604028A (en) * 1985-05-08 1986-08-05 General Electric Company Independently actuated control valves for steam turbine
DE4023900A1 (de) * 1990-07-27 1992-01-30 Borsig Babcock Ag Vorrichtung zum regeln einer turbine
DE4214775A1 (de) 1992-05-04 1993-11-11 Abb Patent Gmbh Dampfturbine mit einem Drehschieber
CN1105418A (zh) * 1994-01-11 1995-07-19 付德隆 改变工作质、内燃机、锅炉、热交换、太阳能四做功能高效获得法
JP3621216B2 (ja) * 1996-12-05 2005-02-16 株式会社東芝 タービンノズル
JP2005344697A (ja) * 2004-05-07 2005-12-15 Toyota Industries Corp 車両用排熱回収システム
JP4869370B2 (ja) * 2009-03-13 2012-02-08 株式会社東芝 軸流タービンの蒸気導入部構造体および軸流タービン

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US811249A (en) * 1905-03-23 1906-01-30 Gen Electric Governing mechanism for elastic-fluid turbines.
US811984A (en) * 1905-05-22 1906-02-06 Wilkinson Turbine Company Elastic-fluid turbine.
US2389074A (en) * 1943-09-27 1945-11-13 Westinghouse Electric Corp Turbine apparatus
US3350061A (en) * 1964-04-15 1967-10-31 Linde Ag Expansion-turbine nozzle ring and apparatus incorporating same
US3948054A (en) * 1973-07-27 1976-04-06 Westinghouse Electric Corporation Steam turbine blade protection system and method especially for electric power plants
US3879616A (en) * 1973-09-17 1975-04-22 Gen Electric Combined steam turbine and gas turbine power plant control system
US4325670A (en) * 1980-08-27 1982-04-20 Westinghouse Electric Corp. Method for admitting steam into a steam turbine
US4563989A (en) * 1982-10-15 1986-01-14 Robert Bosch Gmbh Regulation system for an internal combustion engine
US4780057A (en) * 1987-05-15 1988-10-25 Westinghouse Electric Corp. Partial arc steam turbine
US4850793A (en) * 1987-10-13 1989-07-25 Westinghouse Electric Corp. Steam chest modifications for improved turbine operations
US4979873A (en) * 1988-02-01 1990-12-25 Asea Brown Boveri Ltd. Steam turbine
US5383763A (en) * 1992-05-04 1995-01-24 Abb Patent Gmbh Steam turbine with a rotary slide for controlling steam throughput
US20100189550A1 (en) * 2007-07-10 2010-07-29 Richard Geist Rotary valve for the control of steam throughput in a steam turbine
US20110056203A1 (en) * 2008-03-06 2011-03-10 Gaertner Jan Method for recuperating energy from an exhaust gas flow and motor vehicle
US20120260654A1 (en) * 2009-10-06 2012-10-18 Thomas Proepper Driving device
US20110179793A1 (en) * 2010-01-22 2011-07-28 Robert Bosch Gmbh Method for operating an internal combustion engine having a steam power plant

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3530924A1 (en) * 2018-02-27 2019-08-28 Borgwarner Inc. Waste heat recovery system and turbine expander for the same
US20190264606A1 (en) * 2018-02-27 2019-08-29 Borgwarner Inc. Waste heat recovery system and turbine expander for the same
CN110195616A (zh) * 2018-02-27 2019-09-03 博格华纳公司 废热回收系统及其涡轮膨胀机
JP2019152206A (ja) * 2018-02-27 2019-09-12 ボーグワーナー インコーポレーテッド 廃熱回収システムおよびそのためのタービン膨張機
US11156152B2 (en) * 2018-02-27 2021-10-26 Borgwarner Inc. Waste heat recovery system with nozzle block including geometrically different nozzles and turbine expander for the same
US11560833B2 (en) 2018-02-27 2023-01-24 Borgwarner Inc. Waste heat recovery system with nozzle block including geometrically different nozzles and turbine expander for the same
US11015489B1 (en) * 2020-03-20 2021-05-25 Borgwarner Inc. Turbine waste heat recovery expander with passive method for system flow control
WO2022023053A1 (fr) 2020-07-29 2022-02-03 IFP Energies Nouvelles Turbine axiale orc a admission variable pilotee
FR3113090A1 (fr) 2020-07-29 2022-02-04 IFP Energies Nouvelles Turbine axiale ORC à admission variable pilotée

Also Published As

Publication number Publication date
CN103154439B (zh) 2016-03-23
WO2012048987A1 (de) 2012-04-19
DE102010042412A1 (de) 2012-04-19
EP2627869A1 (de) 2013-08-21
CN103154439A (zh) 2013-06-12

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Date Code Title Description
AS Assignment

Owner name: ROBERT BOSCH GMBH, GERMANY

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STCB Information on status: application discontinuation

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