EP1691039A1 - Methode und Vorrichtung zur Erzeugung von Arbeit - Google Patents

Methode und Vorrichtung zur Erzeugung von Arbeit Download PDF

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Publication number
EP1691039A1
EP1691039A1 EP05101039A EP05101039A EP1691039A1 EP 1691039 A1 EP1691039 A1 EP 1691039A1 EP 05101039 A EP05101039 A EP 05101039A EP 05101039 A EP05101039 A EP 05101039A EP 1691039 A1 EP1691039 A1 EP 1691039A1
Authority
EP
European Patent Office
Prior art keywords
gas
temperature
liquid
process according
medium
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.)
Withdrawn
Application number
EP05101039A
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English (en)
French (fr)
Inventor
Frank Hoos
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.)
Blue Sky Energy NV
Original Assignee
Blue Sky Energy NV
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 Blue Sky Energy NV filed Critical Blue Sky Energy NV
Priority to EP05101039A priority Critical patent/EP1691039A1/de
Priority to ARP060100479A priority patent/AR052480A1/es
Priority to PCT/NL2006/050024 priority patent/WO2006085770A2/en
Publication of EP1691039A1 publication Critical patent/EP1691039A1/de
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F01K25/04—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 being in different phases, e.g. foamed
    • 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
    • F01K25/10—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 the vapours being cold, e.g. ammonia, carbon dioxide, ether

Definitions

  • the invention relates to a process and an apparatus for generating work.
  • a Carnot cycle also referred to as "steam cycle”
  • a high temperature medium typically superheated steam
  • a turbine which generates work, and is subsequently condensed, (super)heated and once more fed to the turbine. I.e., the difference between the amount of heat contained in the high temperature medium and the amount of heat sunk to the low temperature source is converted into work, in accordance with the first law of thermodynamics.
  • the environment serves as the low temperature source (heat sink) and the high temperature medium is generated by burning fossil fuels or by nuclear fission.
  • the process according to the present invention comprises the steps of expanding a gas, preferably substantially adiabatically and/or at the critical pressure and temperature of the gas, causing part of the gas to condensate and form a liquid phase, and separating, during or after expansion, at least part of the liquid phase from the gas phase.
  • a temperature difference and a substantial difference in heat content between the liquid and the gas phase can be generated with little work, preferably by subsequently compressing the gas phase, causing the temperature of the gas phase to increase to a temperature higher, preferably at least 20°C higher, than that of the liquid phase.
  • a preferred process further comprises the step of raising the pressure of the separated liquid.
  • the process comprises the steps of heating a further medium by means of the gas phase and generating work by expanding the further medium, preferably in a Carnot or steam cycle.
  • the invention further pertains to an apparatus for producing work comprising at least one cylinder of turbine for expanding a gas, preferably substantially adiabatically and/or at the critical pressure and temperature of the gas, thus causing part of the gas to condensate and form a liquid phase, and means for separating, during or after expansion, at least part of the liquid phase from the gas phase.
  • the apparatus further comprises a compressor for compressing the gas phase, preferably substantially adiabatically or cooled, causing the temperature of the gas phase to increase to a temperature higher, preferably at least 20°C higher, than that of the liquid phase. Consequently, a substantial difference in heat content between the liquid and the gas phase can be generated with little work.
  • a compressor for compressing the gas phase preferably substantially adiabatically or cooled, causing the temperature of the gas phase to increase to a temperature higher, preferably at least 20°C higher, than that of the liquid phase. Consequently, a substantial difference in heat content between the liquid and the gas phase can be generated with little work.
  • the said components form a main cycle for generating a relatively low temperature liquid and a relatively high temperature gas and that the cycle is coupled to a further cycle for generating work.
  • Figure 1 is a schematic layout of a power plant in accordance with the present invention.
  • Figures 2A to 2C show cross-sections of a preferred cylinder and piston assembly suitable for use in the power plant of Figure 1.
  • Figure 3 shows a side view and a cross-section of a preferred centrifuge for separating liquid and gas at the outlet of the assembly of Figures 2A to 2C.
  • Figure 1 shows a layout of a power plant 1 including two systems, a first system operated in accordance with the present invention and referred to as "heat swing cycle" and a second system operated in accordance with a Carnot or steam cycle.
  • the first system comprises twelve pairs of cylinders 2 1 - 2 24 , each cylinder 2 containing a piston 3 connected, via a rod 4, to a common crankshaft 5.
  • This particular crankshaft 5 is modular, i.e. it comprises a crank section for each pair of cylinders 2 interconnected by means of e.g. pre-tensioned splines (not shown).
  • the total power of the plant 1 can be de- or increased by respectively removing or adding (pairs of) cylinders 2.
  • Each cylinder 2 comprises a non-return valve 6, connected to a gas pressure line 7 and allowing gas to be expelled from the cylinder 2, and a control valve 8, connected to a suction line 9 and allowing fluid to be drawn into the cylinder 2.
  • a further control valve 10 is provided to remove liquid from the cylinder 2.
  • the further control valves 10 of each pair of cylinders 2 are connected to a pump 11.
  • the gas pressure lines 7 are mutually interconnected and in communication with compensators 12 to reduce pulsations in the lines 7.
  • the compensators 12 in turn are connected to a common pressure vessel 14 and serve to equalise pulsations generated by the cylinders 2.
  • the gas pressure lines 7 and liquid pressure lines 13 are connected to respectively first and second reverse current heat exchangers 15, 16, and, downstream from the heat exchangers 15, 16, connected to a central (collecting) duct 17, which in turn is connected to the suction lines 9.
  • the second system referred to as "steam cycle"
  • steam cycle comprises an evaporator, i.e. the first heat exchanger 15, a condenser, i.e. the second heat exchanger 16, an additional heater 18, and a heat engine, known in itself and comprising, in this example, a plurality of piston generators 19, and a pump 20, which serves as a boiler feed pump.
  • the system further comprises, downstream from both the heat engine 19 and the pump 20, compensators 21, which are connected to common pressure vessels 22.
  • the heat swing system is filled, for example, with Argon
  • the Carnot cycle is filled, for example, with CF 4 .
  • Both systems are cooled to a temperature preferably at least 50 °C lower than ambient temperature, e.g. to 150 K, and the pressure and temperature in the heat swing system are controlled to be substantially equal to the critical pressure (P c ) and temperature (T c ) of the medium, in this example, Argon.
  • P c critical pressure
  • T c temperature
  • each of the cylinders goes through a cycle comprising the following steps:
  • the gas expelled from the cylinders is fed to the first reverse current heat exchanger, i.e. heat of the gas is used to heat condensate in the steam cycle. Further, the temperature of the gas is decreased to T c or near T c .
  • the liquid pressure is increased to P c by use of the pumps.
  • the compressibility of the liquid is very low, an increase in pressure will substantially not result in an increase of the liquid temperature.
  • the liquid is fed to the second heat exchanger, i.e. the heat content of the (relatively cold) liquid is used to convert gas in the condensers of the steam cycle to liquid. Further, the temperature of the liquid in the heat swing cycle is increased to T c or near T c .
  • the heated liquid and cooled gas in the heat swing cycle are subsequently mixed to obtain a mixture having a pressure and temperature substantially equal to the pressure and temperature of the mixture that was present in the cylinder at the start of the expansion stroke (shown in uneven cylinder 2 1 ; and even cylinder 2 12 ).
  • the steam cycle is operated thus:
  • the medium, e.g. CF 4 , in the steam cycle is pre-heated in the evaporator 15 and, since the amount of heat is not sufficient to completely evaporate the medium, subsequently heated in the additional heater 18, which preferably comprises a heat exchanger that absorbs heat from the environment, such as a river or the atmosphere.
  • the heated medium is fed to the heat engine, where it generates work, and discharged to the condenser 16, where the medium is cooled and condensed by means of the liquid in the heat swing cycle. Finally, the medium is pumped to the evaporator 15 and the cycle is complete.
  • the gas in the heat swing cycle is cooled during compression. Such cooling can be achieved e.g. with the cold condensate after it has been used for gas to liquid conversion in the condenser of the steam cycle.
  • Figures 2A to 3 show a preferred cylinder and piston assembly 25 suitable for use in the power plant 1 of Figure 1 and a preferred centrifuge 26 for separating liquid and gas at the outlet of this assembly 25.
  • the assembly 25 comprises two pistons 3, rigidly interconnected by means of a rod 4 and received inside corresponding cylinders 2.
  • the rod 27 is provided with a slot 28 extending in a direction substantially perpendicular to the direction of reciprocating movement of the pistons 3 and allowing a crank of a crankshaft 5 to pass.
  • the pistons 3 are connected to the crankshaft 5 by means of respective pairs of rods 29A, 29B.
  • the cylinders 2 each comprise a spiral cylinder head 30 having a tangential outlet 31 and an axial inlet duct 32.
  • the inlet duct 32 is fixed with respect to the cylinder head 30 and slidingly received in a central bore 33 in the piston 3.
  • the piston 3 itself comprises a plurality of return ducts 34 that extend substantially parallel to the central bore 33 and open, via vanes 35, into the spiral cylinder head 30.
  • Figure 3 shows an active cyclone 26 for separating the gas and the liquid and comprising an inlet 40, connected to the tangential outlet 31 of the cylinder 2, a central rotor 41 having a plurality of U-shaped ducts 42, an annular filter 43 surrounding the outlets of the ducts 42 and providing an annular outlet duct 44 for the liquid, and, beneath the filter 43, an annular outlet duct 45 for collecting the gas.
  • a gas preferably at its critical pressure and temperature, is continuously fed, via the inlet duct 32 to one of the cylinders 2 and allowed to expand, causing the piston to move towards the crankshaft and causing part of the medium to condensate, forming a liquid phase.
  • the piston will cause the piston in the other (opposite) cylinder, which is in a different stage of the cycle, to compress the medium contained in that cylinder.
  • the medium containing the condensate subsequently flows through the return ducts 34 and passed the vanes 35, which impart a centrifugal force on the condensate and entrain droplets.
  • the flow is then fed to the inlet 41 of the cyclone 26 and separated into a liquid (outlet 44) and a gas (outlet 45).
  • the invention will now be illustrated by way of a numerical example.
  • the calculations below are based on the following assumptions and conditions: the pistons move without friction, the process is considered to be adiabatic and reversible (isentropic), heat can be transferred at negligible differential temperatures, and the flow of the media is constant (no pulsations).
  • the starting temperature (T h ) of the medium in the heat swing cycle, Argon is 150 K (-123°C) and the temperature after expansion (T l ) is 110 K (-163°C).
  • Work inputted (W inp ) in the heat swing cycle to compress the medium amounts to 1000 kJ.
  • the energy of the total system will be much higher if environmental heat is used as a high temperature source in the steam cycle.
  • the amount of heat available in the high temperature source is 4750 kJ.
  • the heat swing cycle can be operated using rotary converters.
  • the gas and the liquid can be separated by means of a filter or electrostatically.

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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)
  • Separation Using Semi-Permeable Membranes (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
EP05101039A 2005-02-11 2005-02-11 Methode und Vorrichtung zur Erzeugung von Arbeit Withdrawn EP1691039A1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP05101039A EP1691039A1 (de) 2005-02-11 2005-02-11 Methode und Vorrichtung zur Erzeugung von Arbeit
ARP060100479A AR052480A1 (es) 2005-02-11 2006-02-10 Procedimiento y aparato para generar trabajo
PCT/NL2006/050024 WO2006085770A2 (en) 2005-02-11 2006-02-10 Process and apparatus for generating work

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05101039A EP1691039A1 (de) 2005-02-11 2005-02-11 Methode und Vorrichtung zur Erzeugung von Arbeit

Publications (1)

Publication Number Publication Date
EP1691039A1 true EP1691039A1 (de) 2006-08-16

Family

ID=35124682

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05101039A Withdrawn EP1691039A1 (de) 2005-02-11 2005-02-11 Methode und Vorrichtung zur Erzeugung von Arbeit

Country Status (3)

Country Link
EP (1) EP1691039A1 (de)
AR (1) AR052480A1 (de)
WO (1) WO2006085770A2 (de)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6176707A (ja) * 1984-09-21 1986-04-19 Hisaka Works Ltd 排熱回収装置
EP0485596A1 (de) * 1989-01-31 1992-05-20 Tselevoi Nauchno-Tekhnichesky Kooperativ "Stimer" Verfahren zur umwandlung der wärmeenergie eines mediums in mechanische energie in einer dampfanlage
US5525034A (en) * 1992-05-05 1996-06-11 Biphase Energy Company Hybrid two-phase turbine
US5806316A (en) * 1992-04-29 1998-09-15 New Systems International Limited Apparatus and method for producing working fluid for a power plant
GB2338034A (en) * 1998-09-29 1999-12-08 Lannanet Ltd A non combustible expanding gas motor
US20040144093A1 (en) * 2003-01-28 2004-07-29 Hanna William Thompson Lubrication management of a pump for a micro combined heat and power system
WO2005031123A1 (en) * 2003-09-25 2005-04-07 City University Deriving power from a low temperature heat source

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6176707A (ja) * 1984-09-21 1986-04-19 Hisaka Works Ltd 排熱回収装置
EP0485596A1 (de) * 1989-01-31 1992-05-20 Tselevoi Nauchno-Tekhnichesky Kooperativ "Stimer" Verfahren zur umwandlung der wärmeenergie eines mediums in mechanische energie in einer dampfanlage
US5806316A (en) * 1992-04-29 1998-09-15 New Systems International Limited Apparatus and method for producing working fluid for a power plant
US5525034A (en) * 1992-05-05 1996-06-11 Biphase Energy Company Hybrid two-phase turbine
GB2338034A (en) * 1998-09-29 1999-12-08 Lannanet Ltd A non combustible expanding gas motor
US20040144093A1 (en) * 2003-01-28 2004-07-29 Hanna William Thompson Lubrication management of a pump for a micro combined heat and power system
WO2005031123A1 (en) * 2003-09-25 2005-04-07 City University Deriving power from a low temperature heat source

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 010, no. 246 (M - 510) 23 August 1986 (1986-08-23) *

Also Published As

Publication number Publication date
WO2006085770A3 (en) 2007-01-04
WO2006085770A2 (en) 2006-08-17
AR052480A1 (es) 2007-03-21

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