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WO2011066964A2 - Dispositif d'exploitation de la chaleur, alimenté par la chaleur dissipée - Google Patents

Dispositif d'exploitation de la chaleur, alimenté par la chaleur dissipée Download PDF

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Publication number
WO2011066964A2
WO2011066964A2 PCT/EP2010/007310 EP2010007310W WO2011066964A2 WO 2011066964 A2 WO2011066964 A2 WO 2011066964A2 EP 2010007310 W EP2010007310 W EP 2010007310W WO 2011066964 A2 WO2011066964 A2 WO 2011066964A2
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WIPO (PCT)
Prior art keywords
wnv
exhaust gas
steam
pressure
heat
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PCT/EP2010/007310
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German (de)
English (en)
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WO2011066964A3 (fr
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Erhard Weber
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
    • F01C11/008—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/24—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves
    • 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
    • F01K15/00—Adaptations of plants for special use
    • F01K15/02—Adaptations of plants for special use for driving vehicles, e.g. locomotives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas
    • F01K21/042—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas pure steam being expanded in a motor somewhere in the plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas
    • F01K21/045—Introducing gas and steam separately into the motor, e.g. admission to a single rotor through separate nozzles
    • 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
    • F01K23/065—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 the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • 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
    • 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
    • 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
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • 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
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the aim of the invention is, as efficiently as possible, the total waste heat of cooling and / or the exhaust gas of a primary source e / machine (PM),
  • VM lifting or rotary piston
  • DK lifting or rotary piston
  • VM internal combustion engine
  • GT + DT gas + steam turbine
  • III a burner
  • Heat utilization device in a single resource supply circuit use.
  • the WNV consists of one of the resources (BM) promoting and compressing compression device, a compressor or a heat pump (WP), and a subsequent expansion device, a steam / gas engine (DM).
  • BM resources
  • WP heat pump
  • DM steam / gas engine
  • the WNV delivery / compression device consumes practically nothing up to a maximum of 30% (as heat pump WP) of the total additional power PWNZ of the WNZ system,
  • the serious disadvantage of a DT is that it requires a large mass mass flow at high pressure.
  • the high pressure can be built up energetically favorable only in the liquid state of the BM, and thus in the BM circulation after the DT chain a liquefaction of the entire BM ' s is necessary. This is usually done with external cooling and performs the high condensation as useless or lower-grade waste heat.
  • the WNV here for example is designed as a rotary piston machine (DKM), however, depending on the BM mixture, only a quarter to one third of the BM must be in a liquid state, which is acted upon by a high pressure pump with the high, supercritical pressure, while the main body of BM directly as Steam is recirculated to be mixed with the high pressure steam in two of the four BM versions provided in the first stage of the WNV.
  • DKM rotary piston machine
  • the DKM is equipped here with two inlets and outlets per DKM disc and then delivers three cylinder chamber volumes full of BM per one revolution of the respective rotary piston.
  • the WNZ plant presented here then carries in a circulatory system, solely by utilizing the waste heat of a PM, e.g. for a VM or a (GT + DT) plant, a relative additional power to the PM at
  • a VM as a PM is a great advantage is that in a circuit system, the waste heat of the cooling water in the low temperature range (NT) for the evaporation of the BM we used, and the entire exhaust heat of the VM for further heating of the BM then to higher temperatures Available.
  • NT low temperature range
  • the respective additional services PWNZ with a VM or a GT + DT system or the increase in efficiency with a burner can take into account and including several relevant, realistic loss factors ⁇ between
  • WNV should and can be used in principle three other functions:
  • LV and exhaust gas compressor for recuperation of kinetic energy during thrust and braking operations of the VM operated vehicle, or under load operation of a stationary VM, a burner or a GT + DT system
  • the combined heat and power plant can achieve an effective efficiency of:
  • Taking advantage of the WNV booster function can be for the VM in the car under charging with the stored compressed air the short term, e.g. for a few minutes, retrievable, maximum power of the combined plant, PvM + wNV, max, the maximum rated power of the VM, PvM.max, more than doubled PvM + wNv, max> 2.3 pvM, max, see below.
  • the WNV plant can be used behind and with the following primary aggregates:
  • VM unit e.g. in combined heat and power plants (CHP) for schools, swimming pools and hospitals, but also for single and multi-family houses,
  • CHP combined heat and power plants
  • the VM in a motor vehicle or in a stationary unit can also preferably be operated with (natural) gas, the pressure vessels of which can then be used as DLS after the partial consumption of the gas.
  • It may be a one-component liquid / vapor BM 1 1 " , 1 1 or a mixture of high pressure steam 1 1 ', for example H20H_, and superheated steam 1 1, H20d, and / or variable proportions of the exhaust gas 13, whose temperature is still (far ) in the high temperature range can be used.
  • the mixture formation of the H-OHd takes place with the FhOd and / or the exhaust gas, with the production of mixing enthalpy, and
  • Heat exchangers are required for all these WNV systems.
  • a WT in the high-temperature region of the exhaust gas flow can simultaneously be considered as
  • Catalyst can be used, by a corresponding dimensioning and exhaust gas side coating with catalyst - precious metals, and possibly a second, also exhaust side coated WT as an oxidation catalyst with regulated air supply, especially for a diesel engine as PM.
  • the good old steam engine (HbOd) operated steam engine is in the smell of low efficiency.
  • the exhaust steam has flue gas by a negative pressure effect, e.g. with Giesl ejectors, extracted and thus more fresh air into the boiler, for more complete combustion of the heating coal.
  • a negative pressure effect e.g. with Giesl ejectors
  • AI "heat engine” is for a VM using the waste heat in two separate, closed equipment (BM) circuits, a low-temperature and a high-temperature circuit, each with a relaxation device an improvement in the efficiency of a VM of each assumes an initial liquid BM, which is demanded by a pump and brought to operating pressure, evaporated in heat exchangers and heated.
  • BM closed equipment
  • BM vaporized and preheated via evaporator VD and heat exchanger WT in a low temperature (NT) range, the cooling of the VM or the end of the Waste gas burner BR9 or GT, and further heated by WT's in the high temperature range of the exhaust gas of all PM 's .
  • the equipment consists of either BM steam or a mixture of high pressure steam plus steam and / or exhaust gas and is conveyed in separate stage components of the WNV, compressed and / or decompressed under operating power, one component also being used as a clocked mixing chamber for the BM mixtures ,
  • a solution for this is in an intermediate heating of the H20D and as a second stage one or more medium pressure (MD) DT 's and as a third stage (s) low pressure (LP) DT' s use.
  • MD medium pressure
  • LP low pressure
  • the ND DT in this application is also successful for larger units with a total GT + DT power of PGUD ⁇ 300MW
  • the delivery and compression e.g. the EhCro high-pressure steam or steam EhOd
  • the high-pressure pump a fraction and for the WP to just under a third of the WNV total output.
  • Fig. 1 Schematic diagram of a waste heat-charged heat recovery device WNV, for three uses: I. behind a burner, II. Behind a GT + DT system and III. behind an internal combustion engine VM.
  • Fig. 2 a to c T-S diagrams for waste heat fed WNV cycles for a VM with the resources BM versions
  • FIG. 3 a a diagram of an internal combustion engine VM 2 plus heat utilization device WNV system, here a double-disc rotary piston machine (DKM), used as conveyor (DM0) and / or compression (WP5) and expansion device (DM1, DM2, DM3) operated with the BM mixtures
  • DKM double-disc rotary piston machine
  • DM0 conveyor
  • WP5 compression
  • DM1, DM2, DM3 expansion device
  • Fig. 5 Diagram of a WNV plant as DKM behind a gas plus steam turbines
  • Enthalpy is supplied via the evaporator / heat exchanger VD / WT, which is used in the cooling circuit of the VM2 or at the end in the hot exhaust gas flow 13 of the burner BR9, the GT4 and the VM2 to the initially liquid, then vaporous operating medium BM 1 1 " are:
  • VD / WT0 in the low temperature range (75 ° C ⁇ T ⁇ 130 ° C to 250 ° C) for evaporating / preheating the BM
  • the low temperature (90 ° C.-130 ° C.) reservoir of the cooling water of the VM2 and / or the DKM via WT0 or VD / WT0 ' is used for evaporation and preheating of the then present steam BM 1 1.
  • H2O coolant of the VM2 directly as BM 11 ", 1, 1 1 in a closed loop system for the WNV plant.
  • the antifreeze can be released by a simultaneous antifreeze lubricating the DKM.
  • One third to two thirds of the cooling of the VM2 and the DM0 / WP 5 is dissipated by the evaporation of preheating of the BM 1 1, ie a mixture of water and steam cooling used for the VM2 and the DKM.
  • the H20d superheated steam is either after the medium pressure MD
  • the VM2 a 0.6 liter to 1 liter petrol (or rotary) engine with e.g. used two to four cylinders, each with four valves per cylinder, with one
  • PvM.max 50 kW assumed. Due to the higher exhaust gas temperatures required for the WNV plant, operation of the VM2 without exhaust gas turbocharger ATL15 or a DKM as VM2 is to be preferred.
  • PWNV 4.2 kW will be the total power of VM2 + WNV
  • Fig. 3a and b is schematically a combination plant VM2 plus WNV for the two
  • the BM mixture version (3) is calculated in detail, wherein the calculations for the other BM versions (1), ((2)) and ((4)) can be carried out analogously, and the results also in the Tab. 1 are registered.
  • a double-disc rotary piston engine (DKM) is advantageously used, the DK have no piston recesses, and the cylinder surfaces are refined, for example, chrome-plated.
  • This DKM works as a nearly perfect "two-stroke” without valves and allows a very good separation of suction and compression processes.
  • the lower and the upper cylinder chamber of the DKM which are formed alternately with each 120 ° rotation of the rotary piston, can have different functions each with two separate inlets (18 to 18 ") and outlets (19 to 19 "' ).
  • These DKMs can achieve compression factors of ⁇ > 23: 1 without piston recess and are at high speeds of U> 18,000 / min in the situation.
  • the chamber volume of the DKM was 80 cm 3 (90 cm 3 for the BM version (1))
  • Cylinder chamber height A 130 mm and for the first disc 1 a width of
  • the factor 1.5 comes about because per one revolution of the rotary pistons 25, 25 ' in the lower and the upper cylinder chamber 22, 22 ' each 1.5 VT volumes are promoted.
  • Tx ( ⁇ WÜ Va Cp, a Ta + Vd / Hd Cv Tx-1) / ( ⁇ WÜ Va Cp, a + Vd / Hd Cv, d / Hd), where Tx is the temperature of the BM (1 1 ", 1 1 ' , 1 1) after and Tx-i for which stands before the respective WTx
  • Tx is the temperature of the BM (1 1 ", 1 1 ' , 1 1) after and Tx-i for which stands before the respective WTx
  • Tm 350 ° C.
  • the upper chamber of the first DKM disk 1 is filled as the first expansion stage with a ratio of 1: 2, as DM1, via a volume-wise small, short connection 34, whereby the reciprocal density of
  • the HbOa steam relaxes under work performance and partial condensation in the ratio 1: 4.5 on
  • the two chambers 22, 22 'of the second DKM disc are separated as DM2 and DM3 and fed in succession.
  • the WT1 returned, and then only the exhaust gas 13 in the upper chamber 22 ', the third WNV relaxation stage DM 3, the remaining HbOd added steam, said BM wiring is not shown in Fig. 3.
  • FIGS. 2 a to c show the BM versions (1), (3) and ((4)) as T-S diagrams, for the WNV system with the VM 2 and in FIG. 2 d with the GT 4 + DT 3,3 '.
  • BM mixture versions ((2)), (3), and ((4)) are that a low entropy BM state (FbOHd) is mixed with such high entropy (PkOd or exhaust 13) increases the usable exergy.
  • the common density pm and temperature Tm of the BM mixture is so far in the HbOd steam range that the relaxation in the three stages of the WNV does not lead, or only slightly, into the wet steam range of the H2Od.f1.
  • the pressure charging of the HbOHd vapor is done with a high pressure liquid pump 27 and requires much less power than e.g. the heat pump WP5 or a turbine compressor 52 for the H2Üd steam or a gas, e.g. Air.
  • This allows the heat energy to be transferred per unit of time, AQ / At, lighter, ie with smaller ⁇ - and relative ⁇ / ⁇ - losses are transferred from the exhaust gas to this part of the BM 11 ', resulting in a higher end temperature T2 of HbOHd, see the calculations of Fig. 4, or a larger amount of HbOHd can be prepared.
  • the same heat energy in the form of heat of condensation is dissipated by the condensation cooler 41 in relation to the work done and is lost or used as inferior heating energy, and then has to be re-applied as vaporization heat in the cycle from here the GT4 exhaust become.
  • the BM version (1) has the great advantage of the simplest structure.
  • the BM versions (3) and ((4)) yield the highest additional power PWNV, see discussion above, mainly due to the large contribution of the implied enthalpy of mixing Hm and the direct AHm contributions, values with * in Tab. 1 and 2.
  • the primary source / machine PM is deprived of the largest amount of heat energy AQ / h, both the NT range by evaporation of the liquid BM 1 1 " and preheating of the gaseous BM 1 1 or of the liquid BM 1 1 "for the H2Üd or the H20Hd, as well as the HT range, the exhaust gas 13 of the PM, here the VM2, but also in the case of the GT4 or the burner BR9.
  • the optimum mixing ratio H2ÜHd to H2Üd can be calculated by the control computer in each operating state, depending on the number of revolutions rpm, the offered temperatures of the VM2 cooling water, the DM0 / WP5 and possibly also the DM1, and in particular of the temperature of the exhaust gas 13, in order then to be adjusted via the metering valve 7 'and / or the delivery rate of the high pressure pump 27 EhOfi.Hd.
  • the water vapor FhOd cleans in the version ((2)) and ((4)) the exhaust gas further to the exhaust gas catalyst, here in the combination WT2 / KAT, further from SOx, NOx, and other pollutants, and these can End of the cycle in the then condensed FhOfl, before returning to the BM circuit cycle, through filters and / or with chemicals, eg be precipitated with calcium hydroxide, CaOH, as gypsum, similar to the washout in cooling towers at combined cycle power plants.
  • the BM H2O is exchanged after a set number of cycles, depending on the effectiveness of the built-in filters. With the BM versions ((2)) and ((4)) also the exhaust gas cleaning of a rotary piston machine DKM becomes much easier.
  • Ts 100 ° C of H2O at atmospheric pressure shuts down
  • the BM versions (3) and ((4)) can be used in an analogous manner for the cases II and I of the primary sources, the GT4 + GT3 system and the burner BR9, with similarly good results, see description to FIG. 5 and Tab. 2, and the advantages listed above and the, in stationary systems, easier to control disadvantages.
  • Fig. 3b is another advantageous example of the combination plant VM2 + WNV for the BM version (1): pure FhOd steam, with the placement of the WT2 between the WP5 and the DM1 drawn schematically. Small changes that result in the Bergsbowungen before the WP5, see FIG. 1, are not shown in Fig.3 here.
  • the double disc DKM is used here as a conveying heat pump plus working steam engine, WP + DM, the lower cylinder chamber 22 of the first disc 1 of the DKM acting as WP5, the upper as DM1 stage, which more than compensates the power consumption of the upstream WP5, see Tab. 1, the entire second DKM disc 1 ' is again used as DM2 stage.
  • the main part of the cooling water 21 with a pump 27 ' through the cylinder head of the VM2, or through the first disc 1 of DKM (not shown in Fig. 3) in channels or tube coils (26 ' ) is circulated.
  • This main flow of the cooling water 21 can be regulated by a valve 7 "in such a way that the heat dissipation is just compensated by the evaporation and / or preheating of the fuel 1 BM" 1 1 " .
  • the evaporator / heat exchangers VD / WT0 and VD / WT0 ' can be used here in the NT range, for example, cast of AI all tube blocks, which are in good thermal contact with the cylinder block of the VM 2 and the DKM compressor.
  • the cooling water mixed with a lubricating antifreeze
  • hollow cone or ultrasonic nozzles (24) in droplets with a diameter of about 0 20 to 70 ⁇ sprayed into the duct / tube system of the WTC, see FIG. 1, Case III, or ultrasonically sprayed surfaces.
  • the two WT1 and WT2 / KAT in the exhaust gas stream 13 flows inside the stainless steel tube 26, the BM 1 1 and outside they are flowed around by the VM2 exhaust gas 13.
  • the inputs 18, 18 ', 18 “, 18”' and outlets 19, 19 ' , 19 “ , 19 “' are arranged on the DKM cylinder disks 1, 1 'in such a way that, during rotation, the rotary pistons 25, 25 ' No or little overlap of the intake and exhaust stroke results.
  • a flutter check valve 37 is installed to prevent backflow of the BM 1 1 in the lower WP5, DKM chamber.
  • the total internal volume of the WT2 is then equal to the transport volume VT a DKM chamber 22, 22 ' selected, see Fig. 4, so that the compression or expansion ratio of the WP 5 or the DM1 is advantageously 2: 1 or 1: 2.
  • the second DKM disc 1 ' with double chamber width 2B follows as steam engine DM2 as another expansion device, which provides the main additional performance.
  • the H20d BM 11 is introduced into both cylinder chambers 22, 22 'of the second DKM disk as DM2 in parallel and further relaxed under working power.
  • the DKM disc 1 also have the width B, then translated by a gear 16 at twice the speed or by two gears (not shown) and then run in the opposite direction of rotation to the first DKM disc 1, then interchanged with 18 and Outlets 19.
  • the VM2 cooler 40 has to pay for the BM 1 1 version (1): Od, here about 1/3 to 1/2 of the VM2 (DKM) cooling, and for the entire VM2 (DKM) cooling below the VM 2 transition speed Uü ⁇ 2500 / min, for which the WNV works as LV for charging the VM2, and generally when operating the WNV system as LV / AV or as a booster.
  • stage of the DKM H20fl share with the main BM FbOd portion of the DKM can be operated lying and advantageously with side inlets.
  • the two DKM disks are then fed through the inlet 29 in the reverse flow direction to the WNZ / DM + WP operation with atmospheric air and operated as a three-stage air compressor, LV1 to LV3, and a 1: 3 to 4 Reduction of the transmission 16 selected.
  • Circuit system is discharged with the exhaust gas 13, or the small amount of remaining in the WNV plant BM 1 1, HbOd, when switching to LV / AV for charging the VM2 or for storing the compressed air in the DLS 20 / DAS 50 is not significant, or in the exhaust 13 storage due to the 14% FbOd share in the exhaust 13 is negligible, and in the BM (1 1, 1 ⁇ , 13) cycle this proportion in the partially open BM circulatory system lost HbOd at replaced.
  • a compressed air (exhaust) storage DLS 20 (DAS 50) is charged during LV (AV) operation.
  • Compressed air 10 ' (pressure exhaust gas 13 ' ) is then fed via controllable pressure reducer 17, 17 ' :
  • DLS 50 DLS 20
  • compressed air 10 ' stored in a DLS 20 of 100 l contents at a pressure of approx. P ⁇ 100 bar and approx. T ⁇ 500 ° C is sufficient for operating the VM 2 without fuel for approx. 6 min, ie for one driving distance of about 12 km at a mean speed of 120 km / h.
  • the increased temperature of the compressed air 10 ' (of the pressure exhaust gas 13 ' ) is energetically meaningful, since with the expansive decompression of the stored compressed air by means of the variable pressure reducer 17, 17 ' , to about p ⁇ 2 bar for charging the VM2 or to about a medium pressure from p m ⁇ 6 bar for the operation of the VM 2 without fuel or the WNV as a booster, a significant cooling of the air takes place.
  • a good thermal insulation 53 of the DLS 20 (DAS 50) and all leads (not shown) is provided.
  • a drain tap for H2O residues at the lowest point of the storage container is provided.
  • the DLS 20 and DAS 50 containers are internally protected by a protective layer of plastic or a durable metal coating
  • the switching times are mainly determined by the approximately ten revolutions of the WNV, the DKM, which are necessary for the flushing of the cylinder chambers 22, 22 ' and the lines in the BM version (1) and (3), and amount to eg Transition speed of
  • the WNV can be switched between the various functions with virtually no noticeable delay, which is essential for the energy recuperation during braking and coasting of the car and for activating the LV function for charging the VM2 and the booster function at strong acceleration processes.
  • DLS 50 a minimum pressure in the DLS 20
  • a higher power of the VM2 is required by downshifting to a lower gear (in manual transmissions eg by an electrically on and off overdrive) and the LV / AV function and simultaneously the charging of the VM2 from the DLS 20 via a variable pressure reducer 17 is activated.
  • the performance of the WNV Booster can reach or exceed the maximum rated power of the VM 2 or DT 3 and thus acts similar to the KERS (Kinetic Energy Recovery System) facility at Formula 1 Engines, only with significantly higher power delivery, see introduction.
  • KERS Kinetic Energy Recovery System
  • this compressed air motor function of the WNV possibly saves a second GT4 'for peak load times, see description for FIG. 5.
  • a drive belt 34 which runs over a respective conical wheel 32 on the crankshaft of the VM 2 and on the shaft of the WNV / DKM, advantageously couples the VM 2 to the WNV via a CVT transmission 16 (continuously variable transmission) or a planetary transmission (not shown).
  • This gear 16 can be varied by an electro-magnetic or pneumatic control advantageously continuously between reduction ratios 1: 1 to 4: 1, for optimized operation of the DKM as WNV plant, as WNV booster or as LV / AV or as a mechanical charger for the VM2.
  • Fig. 4 a and b the construction of a high-temperature heat exchanger is shown using the example of WT2 / KAT, consisting of 12 stainless steel tubes 26 with outer diameter
  • a flap-check valve 37 is inserted in the connecting flange 35, which in the rhythm of the intake and compression stroke of the DKM
  • Component WP5 opens or closes the inlet to the 12 tubes 26.
  • This valve 34 is designed so thin-walled and smooth that it copes with the here maximum clock frequency of the discs 1 and 1 'of the DKM of about U ⁇ 9,000 / min.
  • a stainless steel hood 39 is slipped, which is sealed in a groove of the flange 35.
  • two exhaust 13 pipe connections 33 and 33 ' respectively in the lower part of the hood 39, the tube bundles 26 are flowed transversely, and the exhaust gas flow 13 is through a centrally between the tube bundles 26th arranged partition 44 then led to below the upper flange 36 and back to the outlet 33.
  • the tubes 26 are externally coated with Pd or Pt (40), so that the heat exchanger WT2 can simultaneously take over the function of the catalytic converter KAT.
  • the dimensioning of the WT2 KAT is then limited except for the BM version (1) and can be optimized for the catalyst function.
  • the tubes 26 particularly in the WT2 (and the WT1) are designed so that the temperature difference ⁇ necessary to transfer the heat quantity AQ / h by convection from the exhaust gas 13 to the FbOd vapor (the high-pressure H2OH vapor) only is up to ⁇ ⁇ 30 (20) ° C, and the corresponding pressure loss in the WT ' s does not become greater than ⁇ ⁇ 0.2 (5) bar.
  • the total amount of heat transferred to all WTs / hour AQ / h see Tab. 1.
  • Prandtl number Pr ⁇ Cp / ⁇ , dimensionless characteristics, with
  • the values ⁇ for the WNV operated with the BM version (1) can still be reduced below higher ⁇ values, in particular by reducing the pipe radius r and by simultaneously increasing the total length L and, if necessary, by increasing n, wherein the volume content of the heat exchanger in question is kept constant.
  • the dimensioning is much freer to design and optimize, especially with regard to the simultaneous use of the WT2 as a catalyst KAT or the optimal utilization of the exhaust gas (13) heat for the BM mixtures ( (2)), (3) and ((4)).
  • the conditions are completely uncritical, since both the small ⁇ and the ⁇ are well within the specified range of ⁇ ⁇ 5 bar and ⁇ ⁇ 30 ° C and here in particular the high pressure of p ⁇ 190 bar through the high pressure Liquid pump is constructed.
  • a WNV is coupled, here as an example consisting of
  • heat exchanger / evaporator WT0 "VD, WTl, WT2, WT3 and WT4, and a compressed air reservoir DLS 20 (a pressure exhaust gas storage DAS is not shown) with heat insulation 53 for storing the compressed air 10 'is provided so that the WNV by atmospheric air 10 (or exhaust 13) through the port 29 (via a three-way valve 6) in the reverse direction can be operated as air compressor LV1, LV2 and LV3.
  • a condensation cooler 41 ' on which as a foreign cooling waste heat recovery 42, z. B. a district heating, is connected, the BM (11, 1 1 ' ) H20d, Hd after passing through the DT3 and DT3 ' and the three DKM components for the BM version (3) liquefied in its entirety.
  • Three three-way valves 6 allow the electromagnetic switching between the various functions of the WNV.
  • both the WNV as booster and the firing system 51 and thus the GT4 can be operated or charged from the DLS 20 by disconnecting the turbine compressor 52 via a coupling 57 with the compressed air 10'.
  • the WNV with the circuit, as shown in Fig. 5 a operated, which also results for the GT + DT system, the largest additional power in normal mode WNV.
  • the DT3 is only operated with the third of the H20Hd high-pressure steam, while the DT3 ' with the second third, then a 1: 1 mixture of H2ÜHd and H20d and the WNV with the last third of H2ÜHd, ie a 1: 2 mixture of H2ÜHd and HbOd by forwarding each of the resulting H20d superheated steam to the next stage of the chain.
  • Injection into the DM0 can be done by hollow cone or ultrasonic nozzles (not shown in Fig. 5) for strong expansion, so that it by the high-pressure steam jet
  • the first advantage - even in comparison to a pure DT3, 3 ', 3 "combination - is that not every part of the BM must be condensed and liquefied after each decompression stage, but only once at the end of the whole chain saves heat energy from the exhaust stream 13, which is then available for heating the BM to higher temperatures or preparation of a larger BM amount available.
  • the second advantage is the possibility of using the WNV as an air / exhaust compressor and as a booster.
  • the respective proportions of the quantity ⁇ 2 ⁇ TM available after the WT3, which are branched off at the branching points 14 to the three consumers, can be varied by the nominal values, one-third, and optimized by electronic control for the respective power requirement to the combined plant.
  • nwü 0.8 was included.
  • FIG. 5 b the circuit for operation of the WNV with the single-component BM according to version (1): FkOd is shown schematically by dashed lines with dashed lines. This version corresponds to that for the VM2, which was shown in Fig. 3 b and described there in more detail. In this case, the temperature T and thus the FteOd vapor pressure pd in the condensation cooler 41 'can be varied and adapted to the output of the DT3 ' .
  • the DKN combi-plant is not as sensitive to the formation of droplets during the expansion of the FhOd as the steam turbines DT 3, 3 '(3 "). Therefore, the expansion of the FL-Od BM 11 can be (until) far into the Two-phase range, HbOd + FfeOfi, would occur in a DT with an FhOfi fraction of (1 - x)> 0.12. Damage to the turbine blades would result from erosion.
  • the other great advantage of the WNV combination is that it is used in low-consumption times by switching three three-way valves 6 as a multi-stage air compressor LV (or exhaust compressor AV), which sucks via an inlet 29 atmospheric air 10 (or exhaust gas 13), see Fig. 1 and Fig. 3, for charging a here mecanicvolurnigen compressed air reservoir DLS 20 (Druckabgas Eats DAS 50) of (which) is surrounded with a heat insulation 53 (are).
  • LV multi-stage air compressor LV
  • AV exhaust compressor
  • AV exhaust compressor
  • WT2 the exhaust gas 13 heat exchanger WT2
  • WT1 heat exchanger WT1
  • heated compressed air 10 ' (the pressure exhaust gas 13 ' ) can then be operated via an adjustable pressure reducer 17, the WNV system itself and / or the GT4 without or with reduced.
  • the DKM also has the three functions described above.
  • the WMV system booster function can be coupled with charging the GT4 with the stored compressed air 10 'from the DLS (20) via a second pressure reducer 17 ' .
  • the turbine compressor 52 of the GT4 is decoupled, eliminating the 40% power consumption, and charging the fuel 55 charged furnace 52 and the GT4 solely by the compressed air 10 'from the DLS 20, the performance of the GT4 + DT3,3 ' plant even increased by almost two thirds with the WNV booster function for peak load times,
  • the compressed air storage is already used in areas where no water storage pumping station is possible with high efficiencies.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

<span lang=FR style='font-family:"Courier New"'>L'invention concerne un dispositif d'exploitation de la chaleur WNV qui, en exploitant la chaleur de refroidissement et/ou d'échappement d'une machine primaire PM, atteint sur un circuit de fluide de fonctionnement BM un degré de rendement élevé de 0,45 < </span>ηPM + WNV < 0,69. La machine primaire PM peut être un moteur à combustion interne VM, stationnaire ou installé dans un véhicule (automobile), une centrale à turbines à gaz ou à vapeur, une installation de cogénération ou un brûleur (de biogaz) et le fluide de fonctionnement BM peut être de la vapeur surchauffée ou un mélange d'une vapeur surcritique à haute pression et d'une vapeur surchauffée et/ou des parties des gaz d'échappement en exploitant l'enthalpie de mélange. Par ailleurs, il est prévu d'utiliser le dispositif WNV comme compresseur d'air ou de gaz d'échappement avec stockage comme chargeur mécanique de la machine primaire qui, tout comme le dispositif WNV, peut être exploitée comme machine à air comprimé/à gaz d'échappement ou comme booster en exploitant la pression d'air/de gaz d'échappement accumulé, ce qui permet d'atteindre une puissance totale relative de l'installation combinée PM + WNV de 1,6 < PPM+WNV/PPM < 2,3.
PCT/EP2010/007310 2009-12-04 2010-12-02 Dispositif d'exploitation de la chaleur, alimenté par la chaleur dissipée Ceased WO2011066964A2 (fr)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8844291B2 (en) 2010-12-10 2014-09-30 Vaporgenics Inc. Universal heat engine
US10428713B2 (en) 2017-09-07 2019-10-01 Denso International America, Inc. Systems and methods for exhaust heat recovery and heat storage
US11137177B1 (en) 2019-03-16 2021-10-05 Vaporgemics, Inc Internal return pump
CN115059552A (zh) * 2022-05-30 2022-09-16 上汽通用汽车有限公司 一种发动机热能回收系统和热能回收发电方法
CN115186612A (zh) * 2022-07-27 2022-10-14 大连海事大学 一种轮机模拟器中的柴油机涡轮增压器压气机体积流量模型
CN115370428A (zh) * 2022-08-09 2022-11-22 中国能源建设集团江苏省电力设计院有限公司 一种多能耦合压缩空气储能发电系统及运行方法

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012223818A1 (de) * 2012-12-19 2014-06-26 Siemens Aktiengesellschaft Einsatz eines Hilfsaggregates zur Bereitstellung von Abgaswärme für den Abhitzedampferzeuger eines GuD-Kraftwerks
DE102022100696A1 (de) 2022-01-13 2023-07-13 Bayerische Motoren Werke Aktiengesellschaft Verfahren und Steuergerät zum Betreiben eines Dieselkraftfahrzeugs zur Emissionsreduzierung und Kraftfahrzeug
AT527889A1 (de) * 2024-04-19 2025-06-15 Avl List Gmbh Verfahren zum betreiben einer brennkraftmaschine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10259488A1 (de) 2002-12-19 2004-07-01 Bayerische Motoren Werke Ag Wärmekraftmaschine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0076885A1 (fr) * 1981-10-09 1983-04-20 Bernd-Michael Messinger Procédé à rendement élevé pour convertir des combustibles en énergie de propulsion et moteur à combustion interne et à vapeur combiné y adapté
US5896740A (en) * 1996-09-12 1999-04-27 Shouman; Ahmad R. Dual cycle turbine engine having increased efficiency and heat recovery system for use therein
US20030005696A1 (en) * 2000-10-18 2003-01-09 Wilson Benjamin Raymond Internal combustion engine energy extraction devices
DE102007049366A1 (de) * 2007-10-07 2009-04-09 Bernd Hille Vorrichtung und Verfahren zur Gewinnung von mechanischer Energie aus heißen Gasströmen insbesondere eines Verbrennungsmotors
EP2334602B1 (fr) * 2008-10-02 2014-12-10 BAUDINO, Etienne Systeme hybride motorise

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10259488A1 (de) 2002-12-19 2004-07-01 Bayerische Motoren Werke Ag Wärmekraftmaschine

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8844291B2 (en) 2010-12-10 2014-09-30 Vaporgenics Inc. Universal heat engine
US10428713B2 (en) 2017-09-07 2019-10-01 Denso International America, Inc. Systems and methods for exhaust heat recovery and heat storage
US11137177B1 (en) 2019-03-16 2021-10-05 Vaporgemics, Inc Internal return pump
CN115059552A (zh) * 2022-05-30 2022-09-16 上汽通用汽车有限公司 一种发动机热能回收系统和热能回收发电方法
CN115186612A (zh) * 2022-07-27 2022-10-14 大连海事大学 一种轮机模拟器中的柴油机涡轮增压器压气机体积流量模型
CN115186612B (zh) * 2022-07-27 2025-07-18 大连海事大学 一种轮机模拟器中的柴油机涡轮增压器压气机体积流量模型
CN115370428A (zh) * 2022-08-09 2022-11-22 中国能源建设集团江苏省电力设计院有限公司 一种多能耦合压缩空气储能发电系统及运行方法

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