WO2010106130A2 - Procédé, dispositif et système de transformation d'énergie - Google Patents

Procédé, dispositif et système de transformation d'énergie Download PDF

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Publication number
WO2010106130A2
WO2010106130A2 PCT/EP2010/053526 EP2010053526W WO2010106130A2 WO 2010106130 A2 WO2010106130 A2 WO 2010106130A2 EP 2010053526 W EP2010053526 W EP 2010053526W WO 2010106130 A2 WO2010106130 A2 WO 2010106130A2
Authority
WO
WIPO (PCT)
Prior art keywords
energy
gas
propellant
combustion chamber
combustion
Prior art date
Application number
PCT/EP2010/053526
Other languages
German (de)
English (en)
Other versions
WO2010106130A3 (fr
Inventor
Gernot K. Brueck
Original Assignee
Brueck, Alexandra
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 Brueck, Alexandra filed Critical Brueck, Alexandra
Priority to DE112010001190T priority Critical patent/DE112010001190A5/de
Publication of WO2010106130A2 publication Critical patent/WO2010106130A2/fr
Publication of WO2010106130A3 publication Critical patent/WO2010106130A3/fr

Links

Classifications

    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/126—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with elements extending radially from the rotor body not necessarily cooperating with corresponding recesses in the other rotor, e.g. lobes, Roots type
    • 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
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • 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
    • F01C21/06—Heating; Cooling; Heat insulation
    • 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

Definitions

  • the invention relates to a method for converting the energy of a primary energy carrier, such as a gas or a liquid fuel, into mechanical secondary energy, the primary energy source being combusted in a combustion chamber and the energy of the combustion gases determined by gas pressure and / or gas temperature being used to generate kinetic secondary energy becomes.
  • a primary energy carrier such as a gas or a liquid fuel
  • the invention relates to a device for carrying out this method, with a housing in which at least one rotationally driven shaft is mounted in a working space.
  • the invention also relates to a system for carrying out this method with a combustion chamber for combustion of a primary energy source.
  • the rotary motor known from EP 0 432 287 A1 is a technical solution close to the turbine in that there are no defined cycles, but continuous operation is provided instead of four-stroke operation.
  • the rotary motor is divided into two separate areas. First, a combustion chamber area is provided, which is not directly connected to the turbine, but via heat exchangers performs an energy transfer to water as a heat transfer medium. This is followed by the actual turbine, which is to be operated with water vapor in the temperature range of up to 560 0 C and more. In this process, a significant amount of energy is lost in the evaporation of water. Assuming a steam temperature of 560 0 C, no less than 74% of the previously obtained energy is used solely to generate the steam, with only 26% being available for conversion into mechanical energy.
  • the invention has for its object to provide in a structurally less complex manner, a method of the type mentioned above, as well as a device suitable for carrying out the method and a corresponding system, whereby the efficiency in energy conversion to mechanical energy can be increased. According to the invention, this is achieved for the method by using at least one quasi-dense turbine-type device to generate the kinetic secondary energy.
  • a labyrinth seal is a non-contact shaft seal in which the sealing effect is based on the extension of the sealing path, wherein for example on the shaft and the stationary housing part alternately rings are arranged. Due to the high flow resistance in the resulting extended gap only a small, tolerable amount of fluid can escape through the labyrinth seal. Absolute tightness is not possible with this noncontact design, but leakage currents can be expected to be on the order of less than 5%, preferably less than 3% and optimally less than 1% of a fluid flow through the device to be sealed.
  • Turbine-like is understood to mean that the device is a fluid energy machine which, like a turbine (latin: turnable turbo), converts the energy inherent in a fluid into rotational or rotational energy.
  • the object underlying the invention is achieved in that the working space via the housing quasi-tight, in particular via a labyrinth seal, is sealed from the environment. It can be provided with advantage in particular that for driving the shaft drive units on the shaft, such as teeth, pistons or rotor blades, are arranged, which form the delivery units in a gear pump, rotary pump or rotary piston pump. In the system according to the invention, this device according to the invention is connected downstream of the combustion chamber.
  • T n is the lowest and T h is the highest temperature in Kelvin that occurs in the process.
  • the ratio of the mechanical power obtained in the process according to the invention to the supplied heat flow or to the energy of the primary energy carrier is much higher in comparison with a process using steam at the same Carnot efficiency because the energy of the combustion gases is used directly and not for steam generation , According to the invention, it is advantageous to achieve a power conversion efficiency of 50 to 70%, which is understood as meaning the proportion convertible from the primary carrier via the intermediate stage of the mechanical energy into electrical energy.
  • the gases or fuels are provided with sufficient atmospheric oxygen and then burned.
  • the internal temperature of this combustion chamber can be largely regulated by the supply air.
  • air and gas are pumped into the combustion chamber as primary energy carriers via corresponding blowers or pumps. These may be valves provided with quasi-locked pumps or other volume conveyors. If pressure is to be produced by expanding flue gases in the combustion chamber, only locked pumps, such. B. gear pumps, rotary lobe pumps or rotary piston pumps can be used.
  • the fluid media - air and gas - are forced through such conveyor locks in the combustion chamber, ignited there, and the now in a closed space developing pressure is used to use preferably acting as an "inverse" pump device according to the invention as a drive and to move.
  • the cross-sectional area of the air-gas feeds is to make much smaller than the exit surface over which a drive is to be set in motion.
  • the rotors of such pumps or drives must be closely interlocked with each other, to prevent in this way any kind of friction or reduce to the minimum possible , This leads to a certain extent leaks, which can be neglected in comparison to the volume flow rate and which are minimized again at optimum operating temperature.
  • the resulting mechanical work results directly from the temperature and pressure drop of the flue gases or exhaust gases.
  • the invention is also based on the finding that using the inventive device, compared to the prior art fundamentally simplified device achievable level of efficiency of energy conversion, in particular waiving the use of water or water vapor as an energy source, significantly increased and therefore not only in a first stage of energy Conversion, but also in optionally existing further stages, a higher efficiency can be achieved.
  • the boiling point should be well above the normal ambient temperature in addition to the low heat of evaporation compared to water and the stability should also be given at the operating temperature.
  • the secondary side of the heat exchanger should on the one hand be able to withstand high operating pressures and, on the other hand, to ensure the most complete possible transfer of the heat from the primary circuit of the smoke or combustion gases.
  • the gas is liquefied anew each time after it has greatly cooled off from the evaporation of the selected propellant due to expansion in a suitably large space, in an additional cooler, and is then available again for further regasification.
  • a large selection of liquids is suitable.
  • silicon-based compounds such as silanes, siloxanes or silicone oils, and halogenated carbon or hydrocarbon compounds are particularly well suited.
  • either multi-leaf rotors can be used or several drives can be connected in series.
  • FIG. 1 in a schematic representation, a first embodiment of a system for
  • FIG. 2 in a schematic representation, a second embodiment of a system for
  • FIG. 3 is a perspective view, omitting the representation of a front side wall, a first embodiment of an apparatus for performing a method according to the invention
  • FIG. 4 in a longitudinal sectional view, a second embodiment of a
  • FIG. 1 shows a first embodiment 100 of a system for carrying out a method according to the invention.
  • a combustible gas is supplied by means of a first pump 2 as a primary energy carrier and by means of a second pump 3 fresh air.
  • the size of an inlet opening 5 of the combustion chamber 1 for the fresh air and the size of an inlet opening 6 of the combustion chamber 1 for the gas are adapted to the respective volume flows.
  • the gas is combusted in the interior 4 of the combustion chamber 1, and the hot exhaust gases escape through a larger outlet opening 7 in comparison with the inlet openings 5, 6.
  • the temperature in the combustion chamber 1 can be controlled with advantage by the amount of air supplied, in particular reduced over a spontaneously adjusting by the heat of combustion of the primary energy carrier temperature.
  • Optimal is the setting of a temperature in the range of 450 0 C to 800 0 C, preferably in the range of 580 0 C to 620 0 C, more preferably at 600 0 C.
  • the pressure optimally in the range of 3 bar to 10 bar, especially at a temperature of 600 0 C at exactly 10 bar lie.
  • the pressurized exhaust gases flow into a high-temperature turbine 8 arranged downstream of the combustion chamber 1, which is embodied by way of example as a gearwheel turbine. After the exhaust gases have given off part of their energy by the movement of the high-temperature turbine 8, they expand via an outlet opening 9 of the High-temperature turbine 8 in a non-pressurized space, which forms the primary side 11 of a heat exchanger 10.
  • a propellant liquid is injected, vaporized and heated via a small opening 21 to a high-temperature gas also with a high pressure - also preferably in the range of 3 bar to 10 bar - via an outlet 13 in another, a low temperature turbine 14, to arrive.
  • gears are driven in the working space, sitting on shafts, which are held on the housing exterior mounted, meshing with each other closely meshed gears 15.
  • this expansion space 17 should advantageously be so large that, when the propellant gases expand, the final pressure setting is equal to the ambient pressure , Thereafter, the highly cooled gas is condensed by a condenser 18 again, wherein the condensate drips into a collecting container 19 and from there via a third pump 20 is returned to the circulation.
  • FIG. 2 shows a system embodiment 200 with a drain without a high temperature turbine.
  • a combustion chamber 24 - together with fresh air - via a first pump 23 combustible gas out the air is conveyed through a second pump 22.
  • the gas is burned without pressure.
  • the temperature in the combustion chamber 24 can be advantageously controlled by the amount of air supplied, in particular reduced with respect to the combustion temperature of the primary energy carrier.
  • the exhaust gases pass through an outlet 25 in the primary side 26 of a heat exchanger 27 and flow through it.
  • On the secondary side 28 of the heat exchanger 27 is - as in the first embodiment 100 of the system - a propellant injected through an injection port 36, evaporated and heated to then hit with high pressure via an outlet 29 to a turbine 30. After passing through the gas expands through an outlet opening 31 in an expansion space 32. Thereafter, it is condensed via a cooler 33, and the condensate drips into a collecting container 34, from where a third pump 35 receives the liquid again and the injection port 36 feeds.
  • a turbine which also works as a quasi-locked gas delivery unit.
  • the gas passes through an inlet opening 37 in the housing 41, flows into the one working space 38 forming interdental spaces and exerts pressure on the as drive units in a housing 41 exemplified gears 39, which terminate sufficiently close to the inside of the housing , So as turbine wheels, acting gears 39 from.
  • the profile of each individual tooth 43 is calculated in such a way that the highest possible sealing closure always results in the joint 44, where the gears 39 meet, but there is minimal play to avoid energy losses due to friction should. From this point of view, it is particularly important to set a constant temperature of the combustion gases over the operating time. After the gas has been guided by the rotation of the gears 39 through the working space 38, it can then flow out at an outlet opening 40.
  • FIG. 4 illustrates, by way of example, a solution for achieving lateral sealing on a further embodiment 500 of a device according to the invention. This is done by structuring the shaft 48 with the corresponding shape-adapted structure in the housing 46. The gear structure as a rotor 49 is thereby sufficiently close to the housing 46.
  • a labyrinth seal 50 forming a zigzag structure in both the shaft 48, as well as provided in the housing 46, so that the bearing 47 is no longer subjected to propellant gases.
  • a similar structure could also be mounted vertically if the shaft were designed to be slimmer.
  • the present invention is not limited to the illustrated embodiments, but includes all the same means and measures in the context of the invention. Furthermore, the invention is not limited to the feature combinations defined in the independent claims but may be defined by any other combination of particular features of all the individual features disclosed overall. This means that in principle virtually every individual feature of the independent claims can be omitted or replaced by at least one individual feature disclosed elsewhere in the application. In this respect, the claims are to be understood merely as a first formulation attempt for an invention.

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

Abstract

L'invention concerne un procédé de transformation de l'énergie d'un porteur d'énergie primaire tel qu'un gaz ou un carburant liquide, en énergie secondaire mécanique, le porteur d'énergie primaire étant brûlé dans une chambre de combustion (1), et l'énergie des gaz de combustion définie par la pression des gaz et/ou la température des gaz étant utilisée pour produire de l'énergie secondaire cinétique. L'invention vise à améliorer le rendement du procédé avec des moyens de construction peu élevés. A cet effet, un dispositif de type turbine quasi-étanche (8, 14) est employé pour produire l'énergie secondaire cinétique.
PCT/EP2010/053526 2009-03-18 2010-03-18 Procédé, dispositif et système de transformation d'énergie WO2010106130A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112010001190T DE112010001190A5 (de) 2009-03-18 2010-03-18 Verfahren, Vorrichtung und System zur Energiewandlung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910013632 DE102009013632A1 (de) 2009-03-18 2009-03-18 Verfahren und Vorrichtung zur Verstromung von Energieprodukten wie Gas und Treibstoffe
DE102009013632.0 2009-03-18

Publications (2)

Publication Number Publication Date
WO2010106130A2 true WO2010106130A2 (fr) 2010-09-23
WO2010106130A3 WO2010106130A3 (fr) 2011-09-22

Family

ID=42628796

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Application Number Title Priority Date Filing Date
PCT/EP2010/053526 WO2010106130A2 (fr) 2009-03-18 2010-03-18 Procédé, dispositif et système de transformation d'énergie

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DE (2) DE102009013632A1 (fr)
WO (1) WO2010106130A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016212777A1 (de) * 2016-07-13 2018-01-18 KAE Kraftwerks- & Anlagen-Engineering GmbH Passiv-aktiver Wärmeübertrager

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2218380A1 (de) 1972-04-15 1973-11-08 Gernot Klaus Brueck Rotationsverbrennungsmotor
EP0432287A1 (fr) 1989-11-28 1991-06-19 Waldemar H. Kurherr Moteur rotatif

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE481609A (fr) * 1947-04-03
US4357800A (en) * 1979-12-17 1982-11-09 Hecker Walter G Rotary heat engine
DE3333421A1 (de) * 1983-09-16 1985-04-11 Motos Motor GmbH, 4512 Wallenhorst Rotationskolbenmaschine
DE10226244A1 (de) * 2002-06-13 2003-12-24 Gerhard Bihler Triebwerke

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2218380A1 (de) 1972-04-15 1973-11-08 Gernot Klaus Brueck Rotationsverbrennungsmotor
EP0432287A1 (fr) 1989-11-28 1991-06-19 Waldemar H. Kurherr Moteur rotatif

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016212777A1 (de) * 2016-07-13 2018-01-18 KAE Kraftwerks- & Anlagen-Engineering GmbH Passiv-aktiver Wärmeübertrager

Also Published As

Publication number Publication date
WO2010106130A3 (fr) 2011-09-22
DE112010001190A5 (de) 2012-04-26
DE102009013632A1 (de) 2010-09-23

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