EP4303407A1 - Dispositif et procédé de conversion de chaleur à basse température en énergie mécanique techniquement utilisable - Google Patents

Dispositif et procédé de conversion de chaleur à basse température en énergie mécanique techniquement utilisable Download PDF

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Publication number
EP4303407A1
EP4303407A1 EP22183988.9A EP22183988A EP4303407A1 EP 4303407 A1 EP4303407 A1 EP 4303407A1 EP 22183988 A EP22183988 A EP 22183988A EP 4303407 A1 EP4303407 A1 EP 4303407A1
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EP
European Patent Office
Prior art keywords
energy
working fluid
working
energy converter
liquid
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Pending
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EP22183988.9A
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German (de)
English (en)
Inventor
Kristian Roßberg
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Individual
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Individual
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Priority to EP22183988.9A priority Critical patent/EP4303407A1/fr
Publication of EP4303407A1 publication Critical patent/EP4303407A1/fr
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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
    • 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
    • F01K25/06—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 mixtures of different fluids
    • F01K25/065—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 mixtures of different fluids with an absorption fluid remaining at least partly in the liquid state, e.g. water for ammonia
    • 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
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/0435—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines the engine being of the free piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B27/00—Instantaneous or flash steam boilers

Definitions

  • the invention relates to devices and methods for converting low-temperature heat with a maximum temperature of 200 ° C into technically usable mechanical energy and subsequently electrical energy.
  • TLC trilateral cycle
  • a working fluid is put under working pressure by a pressure pump, external heat is supplied in a heat exchanger, and this is converted into a rotational movement by partial evaporation of the working fluid in a heat engine, which drives a generator.
  • the resulting working medium vapor is condensed after it leaves the heat engine and the cycle begins again.
  • the technical challenge of the TLC process lies in the implementation of partial evaporation as forced flash evaporation with a vertically falling evaporation curve (see Fig. 1 , TS diagram, course from point 3 to point 5) through the wet steam area of the working fluid with a high proportion of liquid.
  • the aim of the present invention is a technical solution for converting low-temperature heat into technically usable energy by implementing flash evaporation according to the TLC process ( Fig. 1 ) while at the same time eliminating the disadvantages of the previously known devices.
  • first energy conversion device For better differentiation, the first energy conversion device is hereinafter referred to as “first energy converter” .
  • the device with double energy conversion is hereinafter referred to as the “ overall system .”
  • the thermodynamic process with double energy conversion implemented in the overall system is hereinafter referred to as the “ TLC2 process ” due to its similarity to the known TLC process and for better differentiation from the prior art.
  • Core component of the overall system 11 Fig. 4 is the first energy converter 21.
  • thermodynamic details of the TLC2 process for the entire system 11 as well as the associated TS and pV diagram are shown.
  • the working medium under pressure at point 2 is heated in a heat exchanger 31 by externally supplied thermal energy and fed to the first energy converter 21.
  • the step of flash evaporation (see Fig.3 , TS diagram) from working point 3 with the maximum temperature to working point 5 with the minimum temperature. This achieves a maximum in exergetic efficiency.
  • the working medium raised and partially evaporated by the first energy converter 21 is collected after exiting the first energy converter 21, the working medium vapor 54 condenses, collected together with the working medium 51 that remains liquid and returned to the lower level while performing mechanical work in a second energy converter 34 .
  • the product of the pressure difference and the volume of the working medium corresponds to the thermal energy converted into potential energy in the first energy converter 21.
  • the first energy converter The first energy converter
  • the physical and technical basis for the first energy converter 21 are work areas AB delimited by two pistons 170 and filled with warm working fluid AM.
  • a plurality of these work areas, separated by pistons 170, are arranged one above the other in an upwardly directed tube (see FIG. 5b).
  • Each work area is under a local working pressure pA, which is generated by the other work areas located in the pipe above the respective work area.
  • the working medium AM has partially evaporated in a flash evaporation with a simultaneous increase in volume and has cooled down as a result of the flash evaporation (see Fig. 5b).
  • the weight medium In contrast to the working medium, the weight medium is not heated by the heat source.
  • the working medium and the weight medium can - but do not have to - be identical, i.e. non-heated work medium is used as the weight medium.
  • the weight medium has the effect - with otherwise the same processes as before Fig 5 described - due to its own weight, an increase in the working pressure on each working area AB located in the upward pipe. This makes it possible - as will be shown later - to significantly reduce the height of the upward pipe required to build up the working pressure pA.
  • the in Fig. 7 The structure of the overall system 12 shown with a further developed first energy converter 22 is largely identical to the overall system 11 Fig. 4 .
  • thermodynamic processes of the TLC2 process Fig. 3 also apply to the entire system 12 with the further developed first energy converter 22.
  • the entire system can be easily regulated. It is particularly advantageous that the further developed first energy converter can also be operated in an operating mode without a weight medium, thus extending the usable temperature range to lower temperatures and temperature differences.
  • first energy converter and the further developed first energy converter for converting thermal energy into potential energy allow any number of upward pipes to be built in parallel for energy conversion (see Fig.8 ).
  • thermodynamic steps follows the course of the TLC2 process Fig.3 .
  • the starting point of the energy conversion process is point 2 of the TLC2 process (see Fig.3 , TS and pV diagram) in the lower area of the overall systems 11 and 12 (see Fig. 4 and 7 ).
  • the cold liquid working medium 51 is under pressure and is fed through feeds 40 to the heat exchanger 31 to absorb thermal energy from the low-temperature heat source and is heated therein without evaporating.
  • geothermal heat In addition to geothermal heat, ocean heat, solar heat, waste heat from technical processes (e.g. steel and plastics industries), heat from cooling processes (e.g. cold storages, data centers), heat from combustion processes (e.g. waste incineration, biogas) or residual heat from other processes (e.g. chemical industry) can be used as low-temperature heat sources ) be used.
  • technical processes e.g. steel and plastics industries
  • cooling processes e.g. cold storages, data centers
  • heat from combustion processes e.g. waste incineration, biogas
  • residual heat from other processes e.g. chemical industry
  • all organic and inorganic substances as well as mixtures of substances can be used as working materials that cover the temperature range from the maximum temperature of the low-temperature heat source to the minimum temperature of the vapor liquefaction as a liquid without thermal decomposition and cover without freezing.
  • the heated working medium 52 emerging from the heat exchanger 31 then flows through thermally insulated feeds 40 to the first energy converter 21 ( Fig.4 , overall system 11) or the further developed first energy converter 22 ( Fig.7 , overall system 12).
  • the thermal energy absorbed by the warm liquid working fluid 52 is corresponding to the TLC2 process (see Fig.3 , points 4' and 4") converted into potential energy by performing volume change work in the form of lifting work.
  • the work equipment and the weight medium are raised from the lower to the upper area.
  • the working equipment is in accordance with the TLC2 process (see Fig.3 : Course points 4' and 4") partially evaporated and cooled overall.
  • the still liquid portion of the cold working fluid 51 leaves at the upper level (point 5) in the overall system 11 ( Fig.4 ) or overall system 12 ( Fig.7 ) the first energy converter 21 or 22 and flows to the collecting container 33.
  • the weight medium 60 also flows directly to the collecting container 33 and increases the volume of the liquid cold working medium 51.
  • the evaporated and cooled portion of the working fluid 54 also leaves the first energy converter 21 and 22 in both overall systems 11 and 12, flows to the steam liquefaction device 32 and is liquefied again here with a reduction in entropy (point 6). Any non-condensable gases that may arise are sucked out here.
  • the cold working medium 51 which is liquid again, also flows into the collecting container 33.
  • the cold working medium 51 (including the former weight medium 60) now has potential energy.
  • the cold working medium 51 - in the overall system 12 also the weight medium 60 - flows through pressure-stable feeds 42 to the second energy converter 34 while pressure builds up.
  • the liquid column At the inlet of the second energy converter 34, the liquid column generates a high pressure (point 7). This pressure is partially converted into mechanical energy in the second energy converter 34, which is subsequently converted into electrical energy in a generator, for example, but can also be used as mechanical energy to drive machines.
  • the cold working medium 51 leaves the second energy converter 34 under a remaining residual pressure, hereinafter referred to as metering pressure pD.
  • This metering pressure pD corresponds to point 2 of the TLC2 process and is so high that the working fluid 51 does not subsequently begin to evaporate when thermal energy is absorbed again in the heat exchanger 31.
  • the entire working fluid 51 is fed to the heat exchanger 31 again.
  • part of the cold heat medium 51 is separated as a weight medium 60 and fed directly to the first energy converter 22.
  • the remaining working fluid 51 is fed to the heat exchanger 31 again.
  • first energy converters 21 or further developed first energy converters 22 can be used in parallel (see Fig. 6 - shown using the example of the entire system 11).
  • the number of the first energy converters can be as high as desired.
  • a corresponding adjustment of the performance of the shared components heat exchanger 31, steam condenser 32, collecting container 33 and the second energy converter 34 is assumed.
  • the operation of the overall systems 11 and 12 is based only on the pressure difference between the vapor pressure at maximum working temperature and the vapor pressure at vapor liquefaction temperature.
  • the condensation heat can heat heating water.
  • the amount of energy generated by the entire system decreases accordingly.
  • the exergetic efficiency of the entire system changes according to the degree of use of the condensation heat.
  • Fig. 10 overall system 13
  • Fig. 11 shows a preferred arrangement for using low-temperature heat from solar thermal heating, but also from flue gases or coolant vapors.
  • the common feature of the overall systems 13 and 14 is that the heat exchanger 31 for introducing the low-temperature heat is arranged between the collecting container 33 and the second energy converter 34 and extends over the head H.
  • the working medium 51 to be heated passes through the heat exchanger 31 while pressure builds up at the same time and is fed to the second energy converter 34 as already heated working medium 52. After the warm working fluid exits the second energy converter 34, there is no evaporation due to the remaining high metering pressure pD. The heated working fluid is then fed directly to the first energy converter 21 or 22.
  • thermodynamic sequence of the M-TLC2 process is visually similar in the p-V diagram; compared to the TLC2 process, little changes.
  • the starting point for the conversion of thermal energy into potential energy is in the lower area of the pipe system, - shown as an example - in the lower pipe bend 110.
  • pistons 170 which are under the pressure pK of the subsequent piston stack 171, are introduced into the introduction devices 121 ( Fig.12 ) or 122 ( Fig.13 ) pushed.
  • the pressure pK of the piston stack 171 from the descent pipe 160 is greater than the maximum working pressure pA.
  • the introduction device 121 or 122 is supplied from the outside with the heated working medium 52, which is under a metering pressure pD - which is greater than the maximum working pressure pA.
  • the heated working fluid 52 is then introduced between two pistons 170 in the introduction device 121 or 122. This area becomes a work area AB.
  • cold working medium can be introduced as a weight medium 60 between two work areas AB.
  • An area filled with weight medium 60 thus becomes a weight area GB.
  • the amount of media supplied and the time of introduction are controlled by metering devices 126.
  • individual pistons 170 can be briefly stopped in the introduction devices 121 and 122 by a piston stop device 125. After the stopped pistons 170 are released, the introduced areas are pushed into the riser pipe 130 by the pressure of the subsequent pistons 170 or the next introduced areas.
  • the pistons 170 create a spatial and thermally insulated boundary for the heated working medium or the weight medium from the preceding or following areas.
  • any area between two pistons can be a working area or a weight area.
  • Step 2 Conversion of thermal energy into potential energy
  • the preferred embodiment of the riser pipe 130 according to the invention is vertical without a change in direction.
  • the general basic principle of pressure build-up also allows an oblique, helical or other upward design of the rise pipe 130.
  • the working fluid 52 After falling below a working pressure pA which is dependent on the temperature and the vapor pressure curve of the warm working fluid, the working fluid 52 begins to evaporate in a flash evaporation, so that warm working fluid vapor 53 is formed. This results in an increase in the volume of the work area while at the same time cooling down the work equipment.
  • the working pressure pA which rests on the work and weight areas remaining in the riser pipe 130 (the latter only in the further developed first energy converter 22), is reduced.
  • the working fluid 52 has partially evaporated and cooled down to the condensation temperature.
  • the resulting working medium vapor 54 is expanded with an increase in volume and cooling down to condensation pressure.
  • the p-V characteristic of the first energy converters is variable and, due to the self-regulating working pressure pA of each individual work area and the resulting forced expansion evaporation of the work fluid, automatically adapts to the p-V evaporation characteristic of the work fluid in the temperature range used.
  • Step 3 Separation and removal of media
  • the media are separated in the separation device 150.
  • the remaining liquid working fluid 51 is collected, collected and fed to the collecting container 33.
  • the remaining liquid working medium 51 is collected together with the weight medium 60.
  • the working fluid vapor 54 is supplied to the vapor liquefaction device 32 through appropriate feeds 40. Any droplets of working fluid that may have been entrained by the working fluid vapor are separated in the separation device 150 and fed to the collecting container 33.
  • the pistons 170 which are inoperative after the media exits the pipe system, are guided further to the descent pipe 160. There, due to the weight of the pistons, the remaining working medium vapor 54 is pressed out of the pipe system into the separation device 150 through outlet openings provided for this purpose.
  • the pistons 170 are brought together as a piston stack 171 and, due to their own weight, generate the piston pressure pK required in the insertion devices 121 and 122.
  • the inventive structure of the first energy converters 21 and 22 as a closed pipe system with free-running pistons opens up the possibility of energy conversion from thermal to potential energy with a very large and variable working range in terms of the possible increase in volume and the working pressure to be reduced.
  • stepless and variable flash evaporation of a working medium which can be achieved using the principle of individual small working areas, can only be compared with a very finely stepped turbine.
  • the flash evaporation curve can be shown in the TS diagram Fig. 3 and Fig. 9 from point 3 to point 5 pass through safely and completely and the thermal energy absorbed can be fully converted.
  • the tubes for guiding the pistons are provided with a well-sliding thermal internal insulation such as PTFE or polyamide (PA).
  • the pistons themselves are provided on the sealing surfaces with a sealing and sliding material that matches the material of the inner insulation of the pipe, which ensures both sealing of the areas and thermal insulation.
  • the contact of the working fluid with the pipe wall and the stripping of the working fluid from the pipe wall by the piston leads to turbulence and intensive mixing of the working fluid. This promotes the evaporation of the working fluid.
  • This turbulence can be further promoted through a suitable design of the piston and the piston seal.
  • the pistons also preferably have a roughened, porous surface, which promotes the formation of bubbles when the working fluid evaporates (comparable to the effect of boiling stones).
  • the main task of the piston seal is to provide a support function in order to prevent the pistons from tipping in the pipe system. This is possible through a suitable piston design.
  • Corresponding piston designs are known to those skilled in the art.
  • the pipe cross section supports the piston design.
  • non-circular pipe cross sections e.g. ellipse or oval
  • advantages for example in the design of the insertion device or the outlet openings and other tasks.
  • a design of the lower and upper sections of the circumferential pipe system as a horizontal zone with constant pressure (see examples Fig. 15 ) in combination with a non-circular pipe cross section facilitates the technical design of the introduction device 120 and the separation device 150.
  • the overall system 11 can be used Fig.4 Even small temperature differences of 10°K can be used.
  • the small pressure difference of only 0.033 MPa (0.33 bar), which is thermodynamically given due to the temperature difference, between the maximum working pressure and the vapor liquefaction pressure in the first energy converter 21 according to the invention is converted into a technically usable pressure difference of 0.25 MPa (2.5 bar) for the second energy converter 34 implemented.
  • Table 2 shows an example of a comparison of the overall systems 11 (without weight medium) and 12 (with weight medium) with otherwise identical input parameters.
  • Table 3 shows examples of the working parameters of an overall system 12 with a further developed first energy converter 22 at different working temperatures.
  • the temperature scenario shown (increase in the maximum working temperature from 40 to 100 °C) corresponds to the daily course of an energy converter with solar thermal heat supply and liquefaction of the working fluid vapor by ambient air as the ambient temperature increases (increase in the condensation temperature from 20 to 40 °C).
  • the changing operating parameters depending on the change in the maximum working temperature and the condensation temperature are clearly visible.
  • the last column shows an example of the influence of the condensation temperature on the achievable performance.
  • the number of working areas used corresponds to the number of seconds in which the working fluid passes through the flash evaporation curve from thermodynamic point 3 to point 5 of the TLC2 process.
  • Table 1 ⁇ /b> Process example for the implementation of the TLC2 process in the overall system 11 with a temperature difference of 10° between the inlet and condensation temperature Input parameters Unit

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP22183988.9A 2022-07-09 2022-07-09 Dispositif et procédé de conversion de chaleur à basse température en énergie mécanique techniquement utilisable Pending EP4303407A1 (fr)

Priority Applications (1)

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EP22183988.9A EP4303407A1 (fr) 2022-07-09 2022-07-09 Dispositif et procédé de conversion de chaleur à basse température en énergie mécanique techniquement utilisable

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EP22183988.9A EP4303407A1 (fr) 2022-07-09 2022-07-09 Dispositif et procédé de conversion de chaleur à basse température en énergie mécanique techniquement utilisable

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Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3169375A (en) 1963-01-10 1965-02-16 Lucas J Velthuis Rotary engines or pumps
US3953971A (en) 1975-01-02 1976-05-04 Parker Sidney A Power generation arrangement
US4187686A (en) 1978-01-16 1980-02-12 Pommier Lorenzo A Power generator utilizing elevation-temperature differential
DE2943686A1 (de) 1979-10-30 1981-07-02 Erwin 8014 Neubiberg Veldung Industrieabwaermekraftwerk
US4557112A (en) 1981-12-18 1985-12-10 Solmecs Corporation Method and apparatus for converting thermal energy
DE4035870A1 (de) 1990-11-12 1992-05-14 Priebe Klaus Peter Arbeitsverfahren und -vorrichtung
US20010054289A1 (en) * 1999-11-15 2001-12-27 Cover John H. Methods and apparatus for generating hydrodynamic energy and electrical energy generating systems employing the same
US7093503B1 (en) 2004-11-16 2006-08-22 Energent Corporation Variable phase turbine
WO2006126241A1 (fr) * 2005-05-23 2006-11-30 Takahiro Agata Moteur stirling et procede de generation d'une difference de pression du moteur stirling
DE102007041457A1 (de) 2007-08-31 2009-03-05 Siemens Ag Verfahren und Vorrichtung zur Umwandlung der Wärmeenergie einer Niedertemperatur-Wärmequelle in mechanische Energie
US20130341929A1 (en) * 2012-06-26 2013-12-26 The Regents Of The University Of California Organic flash cycles for efficient power production
DE102018130412A1 (de) 2018-11-29 2020-06-04 Carmen Lindner Energieumwandlungssystem
US20220186679A1 (en) * 2019-02-08 2022-06-16 Eaton Intelligent Power Limited Pressure boost system

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3169375A (en) 1963-01-10 1965-02-16 Lucas J Velthuis Rotary engines or pumps
US3953971A (en) 1975-01-02 1976-05-04 Parker Sidney A Power generation arrangement
US4187686A (en) 1978-01-16 1980-02-12 Pommier Lorenzo A Power generator utilizing elevation-temperature differential
DE2943686A1 (de) 1979-10-30 1981-07-02 Erwin 8014 Neubiberg Veldung Industrieabwaermekraftwerk
US4557112A (en) 1981-12-18 1985-12-10 Solmecs Corporation Method and apparatus for converting thermal energy
DE4035870A1 (de) 1990-11-12 1992-05-14 Priebe Klaus Peter Arbeitsverfahren und -vorrichtung
US20010054289A1 (en) * 1999-11-15 2001-12-27 Cover John H. Methods and apparatus for generating hydrodynamic energy and electrical energy generating systems employing the same
US6412281B2 (en) 1999-11-15 2002-07-02 John H. Cover Methods and apparatus for generating hydrodynamic energy and electrical energy generating systems employing the same
US7093503B1 (en) 2004-11-16 2006-08-22 Energent Corporation Variable phase turbine
WO2006126241A1 (fr) * 2005-05-23 2006-11-30 Takahiro Agata Moteur stirling et procede de generation d'une difference de pression du moteur stirling
DE102007041457A1 (de) 2007-08-31 2009-03-05 Siemens Ag Verfahren und Vorrichtung zur Umwandlung der Wärmeenergie einer Niedertemperatur-Wärmequelle in mechanische Energie
US20130341929A1 (en) * 2012-06-26 2013-12-26 The Regents Of The University Of California Organic flash cycles for efficient power production
DE102018130412A1 (de) 2018-11-29 2020-06-04 Carmen Lindner Energieumwandlungssystem
US20220186679A1 (en) * 2019-02-08 2022-06-16 Eaton Intelligent Power Limited Pressure boost system

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