WO2000036281A1 - Extracteur d'energie - Google Patents

Extracteur d'energie Download PDF

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Publication number
WO2000036281A1
WO2000036281A1 PCT/NO1999/000382 NO9900382W WO0036281A1 WO 2000036281 A1 WO2000036281 A1 WO 2000036281A1 NO 9900382 W NO9900382 W NO 9900382W WO 0036281 A1 WO0036281 A1 WO 0036281A1
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WO
WIPO (PCT)
Prior art keywords
energy
fluid
heat exchanger
displacement device
heat
Prior art date
Application number
PCT/NO1999/000382
Other languages
English (en)
Inventor
Geir ONSØYEN
Original Assignee
Therm As
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 Therm As filed Critical Therm As
Priority to AU15878/00A priority Critical patent/AU1587800A/en
Priority to EP99958527A priority patent/EP1151182A1/fr
Publication of WO2000036281A1 publication Critical patent/WO2000036281A1/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
    • F01K25/02—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

Definitions

  • the application relates to a form of energy transformer/converter, a kind of "energy-pump” that transforms energy in the form of relatively small temperature differences between the energy source and the cooling medium to energy in the form of mechanical work.
  • This mechanical work can be further transformed to other types of energy, for example electrical energy, hydraulic energy or pneumatic pressure energy, high temperature heat energy, etc.
  • the application relates to a principle that applies at least one warm reservoir, one less warm/colder reservoir, preferrably three heat exchangers, and two displacement devices where one is applied as a motor and one is applied as a pump or as a hydraulic cylinder with the piston rod side working as a pump and the side without piston rod working as a motor, all this along with piping between the different units.
  • the principle takes advantage of thermal expansion of fluids in a way that a small thermal expansion under high pressure is changed to a large movement that can be taken advantage of.
  • the principle can be utilised to take advantage of low-temperature sources to produce or regain energy that at present is classified as waste energy or energy that is not commercially feasible to develop.
  • the area of utilisation is wide. Waste heat from thermal power and nuclear power, waste heat from process industries, geothermal low temperature energy, solar -energy, warm currents etc.
  • the principle is to a certain degree independent of areas of temperature and can also take advantage of small differences in temperature within low temperature areas - also far below the freezing point of water.
  • Heat pumps can take advantage of low-temperature energy sources, but then to provide heat with a higher temperature.
  • the heat pump is per definition a piece of equipment that extracts heat at one or several temperatures and discharge heat with a higher temperature.
  • the heat pump works the same way as a for example a refrigerator, differing by the fact that the warm side is given priority. Thus, heat pumps extract thermal energy from some sort of energy source and discharges this heat at a higher temperature.
  • a "working fluid” evaporates in an evaporator (E) and extracts heat (Qe) from the system being cooled.
  • the steam is compressed, requiring the work (Wc) , to a pressure where the saturation temperature is higher than the discharge temperature (T2), and further condensed when the heat ⁇ Qc) is discharged in a condenser (C) .
  • the design of a heat pump is illustrated in fig. 2.
  • the pressure in the evaporator is maintained low enough for the working fluid' s saturation temperature to be lower than the temperature in the energy source being cooled off.
  • heat is extracted from the energy source and the working fluid evaporates.
  • the steam passes through a counter flow heat exchanger, often called a precooler PC, with the intention of superheating the steam (this to prevent condensing in the compressor K) while simultaneously supercooling the condensed fluid (to prevent exaggerated degassing in the choke valve CV) .
  • the superheated steam is compressed in the compressor K and condensed in the condenser C.
  • the working fluid which is again back in a liquid phase goes back into the precooler PC and heats the low temperature steam and is thereby supercooled.
  • the supercooled working fluid goes through the choke valve CV and into the evaporator E for then again to be evaporated. With that the cycle is complete.
  • Heat Qe is supplied in the boiler B.
  • the working fluid most often water boils and steam is formed with a steam pressure PI and temperature Tl.
  • the steam from the working fluid drives the steam turbine ST.
  • Pressure and temperature in the steam decreases to P2 and T2 over the turbine ST and the energy Wt is released as mechanical work.
  • the working fluid is thereafter pumped by the water feed pump FP back to the boiler B, and the cycle is complete.
  • Typical values for a steam turbine ST are shown in fig. 4.
  • UK Patent Application GB 2 049 058 A describes a method for developing energy from low temperature sources.
  • the phase transition from gas to liquid is utilised to drive a turbine.
  • a working fluid with a boiling point below 0 °C is utilised.
  • the working fluid boils heat is extracted from water (the energy source) with low temperature.
  • UK Patent Application GB 2 062 111 A describes a method for producing energy from LNG (liquefied natural gas) .
  • LNG liquefied natural gas
  • the phase transition from gas to liquid is utilised to drive a turbine.
  • a working fluid that has a low boiling point is used.
  • LNG transforms from liquid phase to gas phase at a very low temperature. This temperature is utilised in the condenser so that the working fluid is condensed and then driven back to the evaporator - which extracts heat from for example water with low temperature.
  • Offenlegungsschrift DE 3445785 Al describes a method for developing energy by utilizing the difference in temperature between a heat emitting and a heat absorbing medium, this by a using a working medium moving in a circuit between an evaporator and a condenser.
  • the phase transition from gas to liquid is utilised to drive a inverted rotating vane pump.
  • This vane pump rotates because the pressure in the gas decreases when the gas passes through.
  • the vane pump probably needs a lower pressure than a turbine to function.
  • the principle is built upon the usual principle of boiling in an evaporator and condensing in a condenser.
  • US Patent 5.327.745 describes a method that utilises a liquid with very special characteristics in the liquid phase (liquid carbon dioxide) in either a heat pump or opposite, in a construction made for developing mechanical energy and transforming this to electrical energy.
  • Liquid carbon dioxide has special characteristics with relation to thermal expansion and compressibility making it suitable to be used as a liquid in a heat pump because of the increase in temperature taking place during pressure buildup and compression.
  • the compression heat is positively utilized when the system is used as a heat pump.
  • the energy loss due to the compression heat lowers the efficiency when the system is utilised to develop electrical energy because of the heat loss that occurs. This reduces the efficiency of such a system with C02.
  • the known system uses gear pumps or vane pumps as displacement devices.
  • liquid carbon dioxide has a thermal expansion that is larger than the displacement device's internal leakage.
  • These types of pumps that are used in this US-patent cannot be used for approximately ideal liquids because these liquids have a thermal expansion that is less than the internal leakage in gear- or vane-pumps.
  • Approximately ideal liquids have characteristics that are suitable in a system designed for developing electrical energy because the compression heat is very low and the heat loss is small and the efficiency high, but liquids like this have thermal expansions so low that any kind of internal leakage in the displacement devices is hardly acceptable, even though there will always be a unavoidable micro-leakage.
  • US Patent 5.327.745 is suitable as a heat pump, but not as a system for developing electrical energy because the efficiency is too low.
  • the US-patent actually describes a KFK-free. heat pump that may be operable, but where development of energy is brought along as a modification which is not feasible because of the mentioned disadvantages of compressible fluids and internal leakage.
  • the example below illustrates which potentials of energy that is present in low energy sources.
  • the present invention seeks to utilize parts of this illustrated energy potential residing in low temperature energy sources.
  • Liquid flow 1 litre per second
  • Fig. 5 shows: the arrangement with a heat exchanger VI is arranged to remove heat from a source C of a relatively warmer liquid, gas or radiation - called LI, and transmit the energy to a secondary liquid L2 on the other side of the heat exchanger VI which has a secondary outlet connected to a displacement device G with relatively higher volumetric capacity which again has an outlet connected to the heat exchanger V2 which further on has a free outlet to a reservoir J that is cooled by a liquid or gas L3.
  • the novelty about the invention comprises that the displacement device G with a relatively higher volumetric capacity is connected to the displacement device H with a relatively lower volumetric capacity, which has an inlet from the relatively colder reservoir J with the secondary liquid L2, which displacement device H having an outlet connected to the intake of the secondary side of the heat exchanger V2 which has an outlet to the heat exchanger VI which is connected to the displacement device G with relatively higher volumetric capacity, simultaneously connected to a energy transformer W arranged to transform mechanical energy to other forms of energy - preferably electrical energy.
  • the arrangement is completely different from a heat pump through the fact that it converts heat energy to mechanical work, while the heat pump transforms heat with low temperature to heat with a higher temperature.
  • the arrangement is different from other energy transformers in that a small thermal expansion with approximately ideal fluids under high pressure and with a high level of efficiency is transformed to mechanical power as opposed to other energy transformers that take advantage of the large increase in volume taking place by phase transition liquid / gas in the evaporator or the relatively large thermal expansion taking place in fluids with unique characteristics in the liquid phase.
  • the thermal expansion occurring with increasing temperature in an approximately ideal fluid is very small compared to the increase in volume taking place during phase transition liquid / gas or fluids with unique characteristics in the liquid phase.
  • the force or the pressure build up that arises from the thermal expansion taking place by an increase in temperature with approximately ideal fluids can, on the other hand, be very large compared to the force or pressure build up that takes place in the phase transition liquid / gas or by the relatively large thermal expansion within some selected fluids with especially unique characteristics in the liquid phase. This is taken advantage of in the invention. While not using the phase transition liquid/gas, the condensing heat in the condenser is not lost. If one in addition use approximately ideal fluids that are only slightly compressible, a minimal rise in temperature will occur during the increase in pressure, and thereby a reduced heat loss in V3.
  • the plant can therefore obtain a substantially higher degree of efficiency compared to what can be obtained by taking advantage of the phase transition liquid / gas due to the fact that heat energy is transferred back from the low pressure side to the high pressure side by heat exchanger V2 in fig. 5.
  • This heat recovery thus becomes larger when a approximately ideal fluid is used than if a more compressible fluid is used because one will never get a lower temperature on the low pressure side out of V2 than the temperature on the high pressure side into V2. I.e. a smaller amount of heat has to be removed in V3 when approximately ideal fluids are taken in use as working fluids, this again giving a higher degree of efficiency.
  • Figures 5 and 6 show schematically the main elements that make up a preferred embodiment of the invention.
  • a preferrably differentially connected double-acting hydraulic device HA as a combined pump and motor is used.
  • the hydraulic device HA moves in two strokes: induction stroke when the piston PI moves in the direction of a preferrably inductive sensor IU and pump stroke when the piston PI moves in the direction of the preferrably inductive sensor IT. That the sensors IU and IT are given as inductive is meant as a non-limiting example.
  • the point with this arrangement with a fluid on both sides of the piston PI together with induction stroke and pump stroke is that one obtains approximately the same pressure on both sides of the piston PI in the cylinder resulting in the internal leakage essentially being eliminated.
  • the piston PI can be magnetically detectable or detectable in some other way, and it' s position detected on the outside be the preferentially inductive sensors IT and IU, that on detection send signals to the controller X, that can consist of for example a PLS or relays.
  • the controller will control the valves L and M.
  • the valve M When the piston reaches the position where the inductive sensor IU is situated the valve M is closed and the valve G is thereafter opened.
  • the pressure in the system will act on a smaller area on the piston rod side and thereby force the piston towards the inductive sensor IT, in such a way that the volume in the "H-side" (see fig. 5) of the hydraulic device is forced into the pressure side of the system via the check valve 0.
  • the valve L will close and thereafter the valve M will open.
  • the piston PI is forced towards the inductive sensor IU when valve M is open and valve L is closed.
  • the valves N, 0, P, and Q are check valves.
  • R and S indicate hydraulic accumulators that mute pulsing and maintain the pressure locally.
  • a warm reservoir C is the source for heating the fluid LI.
  • the working fluid L2 is heat exchanged with LI in the heat exchanger VI.
  • the heated working fluid L2 that is let out by the "G-part" of the hydraulic device via the valve M in the induction stroke is lead into the heat exchanger V2 and counter flow heat exchanged with the cold working fluid L2 in the heat exchanger V2.
  • the working fluid L2 is directed to the heat exchanger V3 and there cooled down by the cold fluid L3, thereafter going to the reservoir J.
  • Energy is released as mechanical work on the generator W via the hydraulic motor K and transformed to electrical energy with the piston rod in the hydraulic device working as a piston in a smaller cylinder that together with the piston rod functions as a pump in a hydraulic circuit that drives the hydraulic motor K.
  • the "G-side" of the hydraulic device (see fig. 5 and fig. 6) has a volumetric capacity that is slightly higher than the "H-side" of the hydraulic device.
  • the ratio between the two sides H and G is calculated from the coefficient of thermal expansion of the working fluid L2, the temperature of the working fluid L2 out of VI and the temperature of the working fluid L2 into the induction side of the "H-side" of the hydraulic device.
  • the density of pentane at 20 °C is 0,6262g/cm 3 .
  • the volumetric capacity in the inpumping hydraulic device H is set as 1000 cm 3 per stroke to simplify and make the explanation more understandable.
  • the volumetric capacity of the hydraulic device G shall thus be calculated.
  • Mass in is equal to mass out.
  • the table and calculation shows that when 1000 cm 3 at 20 °C enters that equals a mass of 626,2 g. When 1024 cm 3 is let out at a temperature of 35 °C, that is equivalent of the same mass, i.e. 626,2 g.
  • the ratio of volumetric capacity between inpumping hydraulic device and outletting hydraulic device is thereby that 1000 cm 3 pumped in relates to 1024 cm 3 let out because the mass let in equals the mass let out when temperature in is 20 °C and temperature out is 35 °C.
  • the curves in figure 8 show the effects of some selected fluids.
  • the curves show that in the area 1/1,035 to 1/1,04 the largest output effect can be obtained for the actual range of temperature.
  • the curves in figure 8 are calculated as follows:
  • the formula for thermal expansion of fluids is:
  • V2 VI (1+ ⁇ . ⁇ T)
  • VI volume prior to heating given in dm3
  • VI the initial volume prior to increasing or decreasing the pressure, dm 3 .
  • the formula for hydraulic power is:
  • Trans-1, 2-dichlorethylene as a liquid, in a closed system when the temperature rises above 50 °C.
  • the compressibility factor for trans-1, 2- dichloroethylene is 1,1210 "3 MPa "1 .
  • the calculation example below shows the change in volume taking place when heating up 1000 cm 3 of trans-1, 2- dichloroethylene in an open system at atmospheric pressure.
  • the coefficient of thermal expansion for trans-1, 2- dichloroethylene is 1, 3610 "3o C _1 .
  • the increase in temperature is from 10 °C to 60 °C, i.e.
  • V2 VI . (1 + ⁇ . ⁇ T) .
  • V2 1000 cm 3 • (1 + 1,36" 10 "3 C "1 • 50 C) .
  • V2 1068 cm 3 .
  • VI 1040 cm 3 . (the volume increases by 4 %)
  • V2 1068 cm 3 . (the volume would increase by 6,8 % in an open system)
  • V2 1068 cm 3 (the volume would increase by 6,8 % in an open system)
  • M the mass of the medium to be heated or cooled, given in the unit kg sec "1
  • V2 Flow into the high pressure side of V2 is 100 dm 3 min "1 with a temperature of 10 °C.
  • E ⁇ ost V3 2 , 13 kg ' sec "x • 1 , 2 kWs kg "1 C "1 • 2 °C .
  • E lo3t V3 5 , 12 kW .
  • E tot E liberated + E lostV3.
  • E tot 1, 6kW + 5, 12 kW.
  • E tot 6,72 kW.
  • E tot 1 , 6kW + 2 , 56 kW .
  • E tot 4 , 1 6 kW .
  • the efficiency is highly influenced by the temperature increase in the fluids with pressure build up. The lower this rise in temperature is, the higher the potential of increasing the efficiency. This because the temperature in L2 on the low pressure side of V2 cannot become lower than the temperature of L2 into the high pressure side of V2. For example, if one has a temperature in L2 out of V3 at 10 °C and this temperature rises to 20 °C during the pressure build up the temperature of L2 on the low pressure side of V2 will never become lower than 20 °C. With that L2 must be cooled down to 10 °C in V3 and ElostV3 will be disproportionately high in proportion to E liberated so that the efficiency will be low. This is the reason that liquid carbon dioxide is not suitable as a fluid in a layout constructed to develop energy. The heat loss in V3 becomes too large.

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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)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)

Abstract

L'invention concerne un échangeur de chaleur (V1) qui peut extraire l'énergie thermique d'une source (C) de fluide primaire relativement plus chaud (L1) et transférer cette énergie à un fluide secondaire relativement plus froid (L2) du côté opposé de l'échangeur (V1). Une sortie secondaire est reliée à un dispositif de déplacement (G) de capacité volumétrique relativement supérieure, lequel comporte une sortie vers un réservoir (J) après refroidissement dans un échangeur de chaleur (V3) par un fluide (L3). Le dispositif de déplacement (G) est relié à un dispositif de déplacement (H) de capacité volumétrique relativement inférieure, qui comporte une admission depuis le réservoir (J) contenant le fluide secondaire relativement plus froid (L2). Le dispositif de déplacement (H) a une sortie reliée à l'admission de l'échangeur (V2), lequel comporte une sortie reliée à l'échangeur (V1), lui-même relié au dispositif de déplacement (G), à son tour relié à un convertisseur d'énergie (W) qui transforme l'énergie mécanique en une autre forme d'énergie, de préférence électrique.
PCT/NO1999/000382 1998-12-16 1999-12-15 Extracteur d'energie WO2000036281A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU15878/00A AU1587800A (en) 1998-12-16 1999-12-15 Energy extractor
EP99958527A EP1151182A1 (fr) 1998-12-16 1999-12-15 Extracteur d'energie

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO19985914 1998-12-16
NO19985914A NO310583B1 (no) 1998-12-16 1998-12-16 Energi-ekstraktor

Publications (1)

Publication Number Publication Date
WO2000036281A1 true WO2000036281A1 (fr) 2000-06-22

Family

ID=19902747

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NO1999/000382 WO2000036281A1 (fr) 1998-12-16 1999-12-15 Extracteur d'energie

Country Status (4)

Country Link
EP (1) EP1151182A1 (fr)
AU (1) AU1587800A (fr)
NO (1) NO310583B1 (fr)
WO (1) WO2000036281A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU775136B2 (en) * 1999-07-19 2004-07-15 Stephen Lanyi Composite heat engine

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4637211A (en) * 1985-08-01 1987-01-20 Dowell White Apparatus and method for converting thermal energy to mechanical energy
US5327745A (en) * 1993-09-28 1994-07-12 The United States Of America As Represented By The Secretary Of The Navy Malone-Brayton cycle engine/heat pump

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4637211A (en) * 1985-08-01 1987-01-20 Dowell White Apparatus and method for converting thermal energy to mechanical energy
US5327745A (en) * 1993-09-28 1994-07-12 The United States Of America As Represented By The Secretary Of The Navy Malone-Brayton cycle engine/heat pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU775136B2 (en) * 1999-07-19 2004-07-15 Stephen Lanyi Composite heat engine

Also Published As

Publication number Publication date
NO985914L (no) 2000-06-19
NO985914D0 (no) 1998-12-16
AU1587800A (en) 2000-07-03
EP1151182A1 (fr) 2001-11-07
NO310583B1 (no) 2001-07-23

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