US20090229265A1 - Method and Device for Converting Thermal Energy Into Mechanical Work - Google Patents

Method and Device for Converting Thermal Energy Into Mechanical Work Download PDF

Info

Publication number
US20090229265A1
US20090229265A1 US12/227,856 US22785607A US2009229265A1 US 20090229265 A1 US20090229265 A1 US 20090229265A1 US 22785607 A US22785607 A US 22785607A US 2009229265 A1 US2009229265 A1 US 2009229265A1
Authority
US
United States
Prior art keywords
hydraulic
working fluid
pneumatic
set forth
work
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
US12/227,856
Other languages
English (en)
Inventor
Michael Mayer
Bernd Peter Pfeifer
Franz Peter Jegel
Steve Hargreaves
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.)
INTERNATIONAL INNOVATIONS Ltd
International Innovatons Ltd
Original Assignee
International Innovatons Ltd
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 International Innovatons Ltd filed Critical International Innovatons Ltd
Assigned to INTERNATIONAL INNOVATIONS LIMITED reassignment INTERNATIONAL INNOVATIONS LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JEGEL, FRANZ P., PFEIFER, BERND P., HARGREAVES, STEVE, MAYER, MICHAEL
Publication of US20090229265A1 publication Critical patent/US20090229265A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • 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
    • F01K25/02—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for the fluid remaining in the liquid phase
    • 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
    • F01K23/10—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 with exhaust fluid of one cycle heating the fluid in another cycle
    • 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
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • 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
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • F01K27/005—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for by means of hydraulic motors

Definitions

  • the present invention relates to a method and to an apparatus for converting thermal energy into mechanical work.
  • a discontinuously operated method capable of generating work through heat conversion at moderate efficiency is further known from U.S. Pat. No. 3,803,847 A.
  • such a method consists of the following steps, which are performed as a cyclic process:
  • a working fluid having an appropriate vapor pressure curve such as for example R 134 a, that is 1,1,1,2-tetrafluoroethane
  • the working fluid in this storage reservoir is in an equilibrium state between a liquid phase and a gaseous phase.
  • the pressure is hereby chosen such that this equilibrium is maintained. In the case of R 134 a and of an ambient temperature of about 20° C., this first-pressure will be about 6 bar.
  • the working fluid is transferred to a work tank in which it is preferred that a second, higher pressure prevails.
  • the second pressure is for example 40 bar. The energy expense for the transfer can be minimized if, in a preferred manner, only liquid working fluid is transferred to the work tank by pumping.
  • the working fluid is heated in the work tank. Heating causes the pressure to increase even more and the working fluid evaporates partially. Heating preferably occurs through waste heat, for example from an internal combustion engine. If the working fluid is heated to a temperature of 100° C., the waste heat can be optimally utilized.
  • the working fluid is allowed to overflow into a pneumatic-hydraulic converter.
  • This can occur after the second step, i.e., the heat is completely supplied first and the connection between the work tank and the pneumatic-hydraulic converter is established thereafter.
  • These steps may however also be performed in part or in whole simultaneously, i.e., the fluid in the work tank is heated while it is flowing into the pneumatic-hydraulic converter. In this way, the efficiency can be optimized since the cooling effected by the expansion of the working fluid is immediately accommodated. Moreover, the cycle time is shortened.
  • the inflowing working fluid displaces a hydraulic fluid that is present in the hydraulic chamber and is being worked off in a suited working machine, for example a hydraulic motor, in order to produce mechanical work that may in turn be used to produce electrical energy.
  • the pneumatic-hydraulic converter is re-filled with hydraulic fluid through a small pump, with the working fluid being displaced and recirculated into the storage reservoir.
  • the working fluid is thereby directed through a second heat exchanger, this making it possible to adapt the temperature to the ambient temperature.
  • the efficiency and the performance of the system can be optimized if the possible phase transitions are made use of accordingly. More specifically, in the first step, the working fluid should be moved in the liquid state only, whereas in the third step, only the gaseous phase will be transferred to the pneumatic-hydraulic converter.
  • connection between the work tank and the pneumatic-hydraulic converter is interrupted. This permits to minimize overflow losses.
  • the efficiency may be optimized if the working fluid is cooled while being supplied from the storage reservoir to the work tank. Cooling can occur through an ambient heat exchanger, meaning through a current cooler, but it is also possible to use cold produced by the second heat exchanger provided it is not needed for some other purpose, for example for an air conditioning system or a cooling aggregate.
  • a particular effect of benefit is achieved if the hydraulic fluid is kept at a temperature that corresponds to the mean temperature of the working fluid in the pneumatic-hydraulic converter. This way, undesirable temperature compensating effects can be avoided.
  • the working fluid be directed from the pneumatic-hydraulic converter through a second heat exchanger.
  • low temperatures occasioned by the expansion of the working fluid may be generated in the second heat exchanger. These low temperatures can be used for cooling in order to economize the energy needed there.
  • Another improvement of the production of low temperatures can be achieved by causing the working fluid from the pneumatic-hydraulic converter to expand to an expansion pressure that is lower than the first pressure in the storage reservoir and is next compressed to the first pressure.
  • the invention further relates to an apparatus for converting thermal energy to mechanical work, said apparatus having a storage reservoir, a work tank and a working machine for converting hydraulic work into mechanical work.
  • the work tank is connected to a first heat exchanger for heating the working fluid, that the work tank is further connected to a pneumatic-hydraulic converter that transfers the pressure of the working fluid to a hydraulic fluid and that there is provided a recirculation line for recirculating the working fluid from the pneumatic-hydraulic converter into the storage reservoir.
  • five of the apparatus illustrated in FIG. 1 are for example arranged parallel to each other in a side-by-side relationship and operated in a time-staggered fashion as this is for example the case in a five-cylinder internal combustion engine. This permits to achieve continuous operation without noteworthy cyclic fluctuations.
  • FIG. 1 illustrates the major component parts of the system.
  • FIG. 2 shows a typical vapor pressure curve of a working fluid.
  • a storage reservoir 1 holds a working fluid; a coolant such as R 134 a can be utilized for example.
  • the working fluid in the storage reservoir 1 is in phase equilibrium at ambient temperature and at a pressure of about 6 bar.
  • the storage reservoir 1 is connected to a work tank 3 through a feed pump 2 , this connection being switchable through a valve 4 .
  • a first heat exchanger 5 that serves to heat the working fluid in the work tank 3 .
  • Heat exchanger 5 is supplied with waste heat from an internal combustion engine that has not been illustrated herein via a booster pump 6 , with water at 100° C. being directed through the first heat exchanger 5 for example.
  • the work tank 5 communicates with a first working chamber 8 a of a pneumatic-hydraulic converter 8 that is configured to be a bladder accumulator.
  • the first working chamber 8 a is separated from a second working chamber 8 b by a flexible membrane 8 c that separates the two working chambers 8 a, 8 b while allowing for pressure compensation.
  • the second working chamber 8 b of the pneumatic-hydraulic converter 8 communicates with a hydraulic circuit consisting of a working machine 9 having a generator 10 flanged thereon, an oil tank 20 , a recirculating pump 17 and a third heat exchanger 11 .
  • the third heat exchanger 11 is supplied from a pump 12 .
  • Another work line 19 connects the first working chamber 8 a of the pneumatic-hydraulic converter 8 to a second heat exchanger 16 that communicates through a booster pump 14 with the storage reservoir 1 .
  • the lines 7 , 19 may be closed selectively by valves 7 a, 19 a.
  • liquid working fluid is transferred from the storage reservoir 1 into the work tank 3 via the feed pump 2 , with the pressure being increased from 6 bar to 40 bar.
  • the valve 4 is closed and heating through the first heat exchanger 5 occurs. This heating constitutes the second step. Waste heat from another process can be used therefor.
  • the working fluid By heating the working fluid to 100° C., part of said fluid evaporates in the work tank 3 and this vapor is transferred in a third step, through the line 7 with the valve 7 a being open, into the first working chamber 8 a of the pneumatic-hydraulic converter 8 .
  • the pressure drop is compensated by further heating through the first heat exchanger 5 .
  • the membrane 8 c of the pneumatic-hydraulic converter 8 is displaced toward the second working chamber 8 b so that hydraulic fluid is urged through the working machine 9 driving the generator 10 .
  • the third step ends as soon as the second working chamber 8 b of the pneumatic-hydraulic converter 8 has largely emptied.
  • hydraulic fluid is recirculated via the pump 17 from the tank 20 into the second working chamber 8 b of the pneumatic-hydraulic converter 8 and the working fluid is directed from the first working chamber 8 a, through the valve 19 a in the line 19 , which has opened in the meantime, through the second heat exchanger 16 and is expanded.
  • a booster pump 14 recirculates the working fluid back into the storage reservoir 1 .
  • the heat absorbed by the working fluid in the second heat exchanger 16 can be evacuated as cooling capacity for operating a cooling system or an air conditioning system.
  • a partial flow through a heat exchanger 15 may also be used for cooling the working fluid during compression, though.
  • FIG. 2 illustrates a typical vapor pressure curve of a working fluid adapted for use in the cyclic process described herein above.
  • Said working fluid is R 134 a, which is known to be a coolant, meaning 1,1,1,2-tetrafluoroethane.
  • R 134 a which is known to be a coolant, meaning 1,1,1,2-tetrafluoroethane.
  • the present invention allows for optimal use of waste heat from other processes, like for example from the operation of an internal combustion engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Turning (AREA)
  • Heat Treatment Of Articles (AREA)
  • Pressure Welding/Diffusion-Bonding (AREA)
US12/227,856 2006-06-01 2007-05-24 Method and Device for Converting Thermal Energy Into Mechanical Work Abandoned US20090229265A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ATA950/2006 2006-06-01
AT0095006A AT503734B1 (de) 2006-06-01 2006-06-01 Verfahren zur umwandlung thermischer energie in mechanische arbeit
PCT/AT2007/000249 WO2007137315A2 (de) 2006-06-01 2007-05-24 Verfahren und eine vorrichtung zur umwandlung thermischer energie in mechanische arbeit

Publications (1)

Publication Number Publication Date
US20090229265A1 true US20090229265A1 (en) 2009-09-17

Family

ID=38777785

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/227,856 Abandoned US20090229265A1 (en) 2006-06-01 2007-05-24 Method and Device for Converting Thermal Energy Into Mechanical Work

Country Status (15)

Country Link
US (1) US20090229265A1 (de)
EP (1) EP2029878B1 (de)
JP (1) JP2009539005A (de)
KR (1) KR20090018619A (de)
CN (1) CN101484683B (de)
AT (2) AT503734B1 (de)
AU (1) AU2007266295A1 (de)
BR (1) BRPI0712746A2 (de)
CA (1) CA2652928A1 (de)
DE (1) DE502007005619D1 (de)
ES (1) ES2356091T3 (de)
MX (1) MX2008015306A (de)
RU (1) RU2429365C2 (de)
WO (1) WO2007137315A2 (de)
ZA (1) ZA200809859B (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017167464A1 (de) * 2016-03-31 2017-10-05 Siemens Aktiengesellschaft Verfahren und vorrichtung zum verdichten eines fluids
US9835071B2 (en) 2015-07-07 2017-12-05 Hyundai Motor Company Apparatus for transferring recovered power of waste heat recovery unit

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBZ20070049A1 (it) * 2007-11-23 2009-05-24 Walu Tec Di Christoph Schwienb Apparecchiatura per il recupero di energia da macchine motorici
CN101676525A (zh) * 2008-09-17 2010-03-24 北京丸石有机肥有限公司 低温气体能量转换方法及其装置
US8800280B2 (en) * 2010-04-15 2014-08-12 Gershon Machine Ltd. Generator
WO2011128898A2 (en) * 2010-04-15 2011-10-20 Gershon Machine Ltd. Generator
US9540963B2 (en) 2011-04-14 2017-01-10 Gershon Machine Ltd. Generator
EP3599440A1 (de) * 2018-07-24 2020-01-29 Siemens Aktiengesellschaft Verfahren und vorrichtung zur verdichtung eines gases
MA51537B1 (fr) * 2020-10-19 2022-10-31 Byah Ahmed Convertisseur d'énergie calorifique stockée dans les eaux des océans et dans l'atmosphère en énergie électrique.

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4031705A (en) * 1974-11-15 1977-06-28 Berg John W Auxiliary power system and apparatus
US4617801A (en) * 1985-12-02 1986-10-21 Clark Robert W Jr Thermally powered engine
US5953917A (en) * 1994-10-04 1999-09-21 Thermal Energy Accumlator Products Pty Ltd Thermo-volumetric motor
US7000389B2 (en) * 2002-03-27 2006-02-21 Richard Laurance Lewellin Engine for converting thermal energy to stored energy

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2900793A (en) * 1954-04-06 1959-08-25 Sulzer Ag Condensing steam heated boiler feed water heating system including a condensate operated turbine
DE2210981A1 (de) * 1971-03-19 1972-09-21 Europ Propulsion Hydraulische Wärmekraftmaschine
US3803847A (en) * 1972-03-10 1974-04-16 Alister R Mc Energy conversion system
GB1536437A (en) * 1975-08-12 1978-12-20 American Solar King Corp Conversion of thermal energy into mechanical energy
JPS55128608A (en) * 1979-03-23 1980-10-04 Ishikawajima Harima Heavy Ind Co Ltd Apparatus in use of heat accumulating material for converting thermal energy into mechanical force
JPS56135705A (en) * 1980-03-28 1981-10-23 Sumitomo Heavy Ind Ltd Energy-collecting method for taking out power continuously from steam fed intermittently
US4393653A (en) * 1980-07-16 1983-07-19 Thermal Systems Limited Reciprocating external combustion engine
JPH0347403A (ja) * 1989-07-13 1991-02-28 Toshiba Corp 蒸気タービンの水滴除去装置
JPH09222003A (ja) * 1996-02-19 1997-08-26 Isao Nihei 熱エネルギーを動力に変換する方法
AU1047000A (en) 1998-11-03 2000-05-22 Francisco Moreno Meco Fluid motor with low evaporation point
JP2002089209A (ja) 2000-09-07 2002-03-27 Hideo Komatsu ガスタービン‐水力コンバインド発電装置
DE102004003694A1 (de) * 2004-01-24 2005-11-24 Gerhard Stock Anordnung zum Umwandeln von thermischer in motorische Energie

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4031705A (en) * 1974-11-15 1977-06-28 Berg John W Auxiliary power system and apparatus
US4617801A (en) * 1985-12-02 1986-10-21 Clark Robert W Jr Thermally powered engine
US5953917A (en) * 1994-10-04 1999-09-21 Thermal Energy Accumlator Products Pty Ltd Thermo-volumetric motor
US7000389B2 (en) * 2002-03-27 2006-02-21 Richard Laurance Lewellin Engine for converting thermal energy to stored energy

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9835071B2 (en) 2015-07-07 2017-12-05 Hyundai Motor Company Apparatus for transferring recovered power of waste heat recovery unit
WO2017167464A1 (de) * 2016-03-31 2017-10-05 Siemens Aktiengesellschaft Verfahren und vorrichtung zum verdichten eines fluids

Also Published As

Publication number Publication date
ES2356091T3 (es) 2011-04-04
RU2429365C2 (ru) 2011-09-20
EP2029878B1 (de) 2010-11-10
RU2008152408A (ru) 2010-07-20
CN101484683A (zh) 2009-07-15
AT503734B1 (de) 2008-11-15
AT503734A1 (de) 2007-12-15
JP2009539005A (ja) 2009-11-12
MX2008015306A (es) 2009-03-06
BRPI0712746A2 (pt) 2012-09-11
ZA200809859B (en) 2009-11-25
CN101484683B (zh) 2012-02-22
AU2007266295A1 (en) 2007-12-06
DE502007005619D1 (de) 2010-12-23
CA2652928A1 (en) 2007-12-06
WO2007137315A3 (de) 2008-12-04
ATE487868T1 (de) 2010-11-15
EP2029878A2 (de) 2009-03-04
WO2007137315A2 (de) 2007-12-06
KR20090018619A (ko) 2009-02-20

Similar Documents

Publication Publication Date Title
US20090229265A1 (en) Method and Device for Converting Thermal Energy Into Mechanical Work
US20070163260A1 (en) Method for converting thermal energy into mechanical work
US10550765B2 (en) Energy storage device and method for storing energy
CA2874473C (en) Device and method for utilizing the waste heat of an internal combustion engine, in particular for utilizing the waste heat of a vehicle engine
US20050262842A1 (en) Process and device for the recovery of energy
RU2673959C2 (ru) Система и способ регенерации энергии отходящего тепла
US11047302B2 (en) Compressed air energy storage power generation apparatus
JP7434158B2 (ja) 燃料電池及び可逆熱力学を結合する、エネルギーを生産するアセンブリ
CN114198170A (zh) 一种基于双蓄热回路的二氧化碳储能系统及其工作方法
CN104279542A (zh) 锅炉系统
WO2009118342A1 (en) Method for converting thermal energy into mechanical work
EP3701135A1 (de) Energiespeichervorrichtung und -verfahren
CN108087069B (zh) 一种基于双相变储热器的朗肯循环余热回收系统及控制方法
CN104279543A (zh) 锅炉系统
CN115163459A (zh) 一种冷热罐混合式绝热压缩空气储能系统
CN114483231A (zh) 一种压缩空气储能系统及其控制方法
CN111472889A (zh) 一种将热能转化为机械能的新装置
CN101749206B (zh) 低温液化能量回收动力供应系统
CN115013094B (zh) 带直接膨胀的中低温热源回收动力循环系统及循环方法
CN102588021A (zh) 一种动力生成系统
CN113756874A (zh) 蒸汽活塞驱动直线发电机
KR101912988B1 (ko) 복합 사이클의 내연 피스톤 엔진 파워 플랜트를 위한 냉각 배열체
CN113062846A (zh) 多源紧凑型蓄热式压缩空气储能综合利用系统及方法
CN113062849A (zh) 组合式蓄热的紧凑型压缩空气储能系统及方法
NZ552469A (en) Method for converting thermal energy into mechanical work, with two heat exchangers each having first and second working chambers, one chamber connected to a pneumo-hydraulic converter

Legal Events

Date Code Title Description
AS Assignment

Owner name: INTERNATIONAL INNOVATIONS LIMITED, AUSTRALIA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MAYER, MICHAEL;PFEIFER, BERND P.;JEGEL, FRANZ P.;AND OTHERS;REEL/FRAME:022360/0268;SIGNING DATES FROM 20090120 TO 20090211

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION