WO2014016498A1

WO2014016498A1 - Internal and/or external combustion turbine engine

Info

Publication number: WO2014016498A1
Application number: PCT/FR2013/051734
Authority: WO
Inventors: Vianney Rabhi
Original assignee: Vianney Rabhi
Priority date: 2012-07-24
Filing date: 2013-07-18
Publication date: 2014-01-30
Also published as: FR2993929A1; FR2993928A1; FR2993926A1

Abstract

The turbine engine (1) comprises a turbo compressor (2) of which the centrifugal compressor (61) and the turbo compressor turbine (62) are connected by a regeneration - combustion canal (34) which comprises a continuous combustion chamber (35) in which a fuel is burnt, and a post-combustion vapour conveying duct (94) connected to a counter current vapour condenser - regenerator (88), said canal (34) also being connected to the inlet of an expansion power turbine (3) by a duct (66), whereas said canal (34) comprises a regeneration counter current mixture/air exchanger (30) which heats up atmospheric air expelled into said canal (34) by the centrifugal compressor (61) with a mixture of gas and vapour expelled via an expansion power turbine exhaust gas - vapour duct (70) via said turbine (62) and said expansion power turbine (3).

Description

TURBO INTERNAL AND / OR EXTERNAL COMBUSTION ENGINE

The present invention relates to a low pressure internal combustion turbine engine and / or external water vaporization and / or regeneration.

Gas or liquid fuel turbines are commonly used in high power applications to propel heavy land vehicles, aircraft, ships, or to generate electricity.

In some applications, the exhaust gas heat of gas turbines is used to produce steam which is then expanded in a steam turbine. This gas turbine and steam turbine unit is a combined cycle power unit with a heat conversion efficiency of up to 50 to 60 percent mechanical work. This type of configuration is usually reserved for heavy and expensive stationary power generation installations.

In the field of low power such as ^automotive, trucking in general or of production ^stations' light electricity, the most common machines used to convert the heat supplied by the combustion of a fuel into mechanical work are the engines alternating internal combustion engines, mainly diesel or spark ignition, and two or four times,

Many attempts have been made to propel automobiles or light land vehicles using turbo engines comprising one or more turbines and operating with a liquid or gaseous fuel. Various automobiles have been built holding this principle as the model "It" of the company "Rover", the "Socema-Grégoire" or the "Turbine Car" of the company "Chrysler", Note also the attempts remained to the prototype state made in this field by the company "Volkswagen" with turbines of type "GT 70" and "GT 150", Unfortunately, the strong power variations that characterize the automobile use are poor for turbines whose performance is optimal at rated power, but insufficient from said power turbine so that lesdifes n ^'has hitherto not been possible to replace the thermal internal combustion engine alternatives which continue to equip one hundred per cent of thermal propulsion motor vehicles.

It should be noted that the turboshaft engines intended for automotive propulsion were mainly based on a single axial fin power turbine operating at relatively high temperature and pressure and therefore made of high-strength steel or ceramic. These axial finned turbines had the defect of being noisy and cooperating with one or more heat regenerators or recuperators also operating at relatively high temperature and pressure and thus being complex and expensive. These regenerators or recuperators were most often rotating as was the case for example for the turbine of the system "KIT" intended for automotive propulsion and developed by the Swedish professor Sven-Olof Kronogard and the company "United Turbine", these regenerators or rotary recuperators - in addition to their high cost ~ generated pressurized gas leaks detrimental to the overall efficiency of the turbo-engine that was equipped with them.

Today, several companies are still developing turbines for automotive use either to directly drive the wheels of the vehicles, but to produce electricity on board said vehicles while the latter are powered by one or more electric motors. This is the case, for example, of the American company Capstone ⁽ Φ) or the English company Bladon Jets (which develops micro turbines driving an on-board electric generator in vehicles propelled by electric motors. Is particularly known for its concept of hybrid vehicle "C T380 Biaekbird", while the company "Bladon Jets" was noted for having equipped the concept car "Plninfarina Cambiano" or the prototype "Jaguar C-X75" of its device of power generation by micro axial turbine In the same field, we also note the hybrid vehicle demonstrator "GREEN", acronym for Electric Vehicle Road Turbine, made in the nineties by the car manufacturer "Renault" The problem with these micro-turbine concepts is that their cost and noise level remain high, so that Alternative internal combustion is ultimately preferred to produce mass produced and marketed vehicles. Despite these failures, convert f onboard primary energy aboard automotive vehicles into mechanical work by means ^of one or the more turbines would décislvement advantageous since said turbines potentially offer a high power density, it feels compact and lightweight, and they present low friction and pumping losses. In addition, the turbines are by definition pol-fueled because, unlike alternative internal combustion engines, the combustion is sequential, their combustion is continuous so that they are not subject to the constraints imposed by the self-inflamation limit. fuels and the undesirable clatter that may result.

In return for these benefits, unlike reciprocating engines generally cooled Others and offering little contact surface with the hot gases from the combustion of fuel, the turbines have the disadvantage ^to operate at a temperature substantially to that enlivens gases leaving the combustion chamber placed upstream. Said turbines therefore can not operate at a temperature higher than that set by ^¬ their thermomechanical strength limit. However, operating at high temperature is crucial for the thermodynamic efficiency of the compressor-turbine assembly. Thus, turbogenerators, turboshaft engines or turboprops with the highest energy efficiency are also the most expensive because their manufacture uses expensive materials and complex manufacturing processes.

A compromise was finally found by equipping alternative combustion internal combustion engines with a turbocharger whose compressor and turbine have radial fins. Reciprocating engines made in this configuration provide an acceptable performance at low power while ^that: at high powers, the turbocharger turbine recovers part of the calorific energy lost in the exhaust of said engine for supercharging the latter via a centrifugal compressor that said turbine drives in rotation.

Considerable progress has been made in the field of turbochargers in particular through the adoption of variable geometry turbines that accommodate large variations in gas flow while producing the mechanical work necessary to drive the centrifugal compressor to which they are connected. Turbochargers are now mass produced products at competitive costs. According to certain configurations, it is even provided several turbochargers mounted in series or in parallel on the same automobile engine.

Thus, it would be advantageous to benefit from the technological and economic advances of turbochargers and the advantages inherent in turbines in general for driving motor vehicles at a lower cost, while conferring on these turbines a yield less equal to that of alternative internal combustion engines. .

It is for this reason that the low-pressure internal combustion engine and / or external water vaporization and / or regeneration provides, according to a particular embodiment:

* To offer a high energy efficiency over a wide range of power including through the use of several turbochargers as usually used in the automotive industry and several expansion turbines, said turbochargers and turbines that can be simultaneously put in operating in various combinations, this particular strategy making economically viable and technologically feasible the use of turbines for propelling motor vehicles with a high energy efficiency;

* Use of expansion turbines operating at moderate temperature and pressure while offering a high efficiency, and this, so that the manufacture of said turbines does not involve expensive materials at high temperature, and that the turbines can possibly be at variable geometry whatever the type;

»Use single-stage radial expansion turbines that are less expensive and quieter than multi-stage axial expansion turbines;

Integrating one or more high-efficiency temperature exchangers operating at sufficiently low pressure and temperature to remain inexpensive, said exchangers requiring no mechanical drive; Significantly reducing the mass, bulk, vibration and acoustic level, and the cost of the motor-based power units based on said turbo-motor compared to those based on an alternative internal combustion engine;

Significantly increasing the durability and reliability of the automotive power units based on said turbine engine, relative to those of said groups based on an alternative internal combustion engine:

To reduce the size of the cooling sludge (s) piee (s) in taoe before motor vehicles or even to suppress the oudiies or boucbe (s), and significantly reduce the resistance to the penetration into the air of said vehicles ;

To allow the consumption of any liquid or gaseous fuels without any constraint being imposed by the propensity or resistance to ignition of said fuels, and without penalty for the thermal-mechanical conversion efficiency of the turbine engine irrespective of the nature and the quality of the said fuels;

To allow combustion in excess of air at a sufficiently low temperature to avoid the use of any post-treatment apparatus for the oxides of nitrogen, said combustion also operating at a temperature high enough not to produce significant amounts soot and fine particles;

Eliminate the water cooling system ordinarily provided for alternative internal combustion engines;

Significantly reduce the temperature rise time during cold start of said turbine engine compared to that required for internal combustion engines with alternative combustion, with a drastic reduction of fuel overconsumption specific to said reciprocating engines operated under these conditions; The low-pressure internal combustion turbine engine and / or external water vaporization and / or regeneration according to the invention thus allows ei particular according to the embodiment of ύκιύϊί turbine engine:

* To produce clean, quiet, economical, economical and light-weight motor vehicles, which are in this respect efficient and attractive for the end consumers;

* To enhance the knowledge and know-how relating to the design, manufacture and industrialization turbochargers applied to automobile engines â alternative internal combustion, the latter are equipped with ^a variable geometry turbine or fixed geometry turbine;

* Significantly reduce the fuel consumption of motor vehicles on prescribed driving cycles and in ordinary driving conditions, even when these vehicles are used at a highly variable power and thus signifcantly increase the autonomy of such vehicles for the same quantity fuel on board said vehicles;

* Optionally, remove the gearbox from motor vehicles and replace it with a fully electric, flexible and compact transmission;

* Possibly, to supply electrical power to motor vehicles with exclusively electric traction so that they do not suffer from a too limited autonomy or excessive recharge time, and this so that these vehicles become more competitive and more attractive for end consumers;

"To replace the hydrogen fuel cells as provided for generating ^the electricity for some electric vehicles with potentially comparable yields, signlficativernent a lower cost and without the various constraints related to the use of hydrogen as a source of energy or without those related to the least reactivltè in power variation of said stacks; * Drastically reduce the weight and cost of on-board batteries in electric vehicles;

»Facilitate the aerodynamic and aesthetic design of the bodywork of motor vehicles by reducing the cooling and housing constraints of the motor-driven unit of these vehicles, or the size of their batteries for storing electricity;

* Enhance the safety of motor vehicle passengers and pedestrians who may collide with vehicles, in particular by reducing the incompressible volume of the engine power unit housed in the engine compartment of such vehicles;

^*> To improve passenger comfort including motor vehicles with quick reheating i 'passenger compartment of such vehicles in cold weather;

* Simplify maintenance and servicing of motor vehicles;

* To achieve low-cost high-efficiency electricity generation stations for domestic or industrial use, iesclites stations offering the possibility of recovering the fraction of heat non-transf rmée in work by the turbine engine according to the invention, thereby achieving a cogeneration;

It is understood that the low-pressure internal combustion and / or external water vaporization and / or regeneration turbine engine according to the invention can be provided in the context of any application including non-automotive, requiring the production of mechanical work. and / or electricity and / or heat from a liquid or gaseous fuel, or from any heat source.

The turbine engine according to the present invention comprises: * At least one turbocompressor that cooperates with at least one regenerative-combustion duct which connects directly or indirectly the release of a centrifugal turbocharger compressor that includes said turbocharger with ^the inlet of a turbocharger turbine that includes said turbocharger, said compressor expelling atmospheric air in said channel after receiving sucked via a turbine engine air inlet and via an intake duct of the turbine engine, while said channel comprises at least one continuous combustion chamber internal or external to said channel in which fuel can be burned after being injected by at least one continuous combustion fuel injector:

at least one expansion drive turbine which is mounted on a drive turbine shaft of relaxation, the inlet of said turbine being connected directly or indirectly to the regeneration-combustion channel by at least one turbine gas-steam inlet duct relaxing motor;

at least one regenerative countercurrent air / mixture exchanger which is part of the regeneration-combustion channel and in which circulates on the one hand a gas-vapor mixture expelled by the turbocharger turbine and / or the driving turbine of defends the output of said turbines being connected to said cycler by a gas-steam exhaust gasoline engine exhaust duct and secondly, the atmospheric air expelled by the centrifugal compressor turbocharger said mixture heating said air inside to eli exchanger before exiting through an exhaust line through an exhaust line;

* At least one EMS turbine engine management calculator.

Furthermore, the turbine engine according to the present invention comprises:

at least one turbocharger which cooperates with at least one regeneration-combustion channel which directly or indirectly connects the outlet of a turbocharger centric compressor which comprises said turbocharger with the inlet of a turbocharger turbine which comprises said turbocharger, said compressor expelling atmospheric air into said channel after sucking it through a mouth turbine engine air intake and via a turbine engine intake duct, while said duct comprises at least one continuous internal or external combustion chamber duct in which a fuel can be burned after being injected by at least one Continuous combustion fuel injector;

at least one expansion drive turbine which is mounted on an expansion turbine drive shaft, the inlet of said turbine being connected directly or indirectly to the regeneration-combustion channel by at least one turbine gas-steam inlet duct; relaxing motor;

at least one counter-current steam condenser-regenerator in which circulates a gas-vapor mixture expelled by the turbocharger turbine and / or the expansion turbine in a gas-steam mixing circuit; condenser-regenerator and in which circulates on the other hand, a liquid water in a condenser-regenerative water circuit connected to the regeneration-combustion channel, said mixture heating said water inside said condenser-regenerator before emerging by an exhaust line outlet via an exhaust line while the inlet of said condenser-regenerator is connected to a gas-steam exhaust pipe of the driving turbine in which the gas-vapor mixture expelled by the turbine circulates; turbocharger and / or the driving turbine of relaxation;

* At least one EMS turbine engine management calculator.

The turbine engine according to the present invention comprises a regeneration-combustion channel which comprises at least one internal water vaporization chamber to said channel in which a liquid water can be injected by a soda water after-jet injector to form a gas-to-water mixture. steam.

The turbine engine according to the present invention comprises an outlet of the regeneration countercurrent air / mixture exchanger which comprises a regenerator regenerator outlet conduit in which circulates the gas-vapor mixture expelled by the turbocharger turbine and / or the expansion turbine engine, said duct connecting said exchanger with the inlet of a condenser-regenerator countercurrent steam in which flows on the one hand, said a gas-vapor mixture expelled by said turbocharger turbine and / or said driving lurfolne in a condenser-regenerator gas-steam mixture circuit and, on the other hand, a liquid water in a condenser-regenerator water circuit which is connected to the regeneration-combustion channel, said mixture heating said water inside said condenser-regenerator through the inner walls of the latter.

The turbine engine according to the present invention comprises a condenser-regenerator water circuit which consists of at least one internal condenser-regenerator duct in which the liquid water circulates, while the condenser-gas-vapor mixture circuit. regenerator is constituted by at least one external casing of condenser-generator which surrounds and / or adjoins said Internal duct, said casing leaving a space between itself and said internal duct which it contains and / or adjoins while the gas mixture -vapor expelled by the turbocharger turbine and / or the drive turbine of expansion circulates in said space, the direction of circulation of said mixture in said space being opposite to that of the circulation of said water in said conduit;

The turbojet according to the present invention comprises a condenser-regenerator water circuit which is connected to the regeneration-combustion channel via a postcombustion steam supply duct which opens into said channel after the continuous combustion chamber. relative to the flow direction of the steam-gas mixture and / or ^atmospheric air into said channel.

The turbine engine according to the present invention comprises a postcombustion steam supply duct which comprises a post-combustion vapor inlet flap which can close or open said duct.

The turbine engine according to the present invention comprises a condenser-regenerator water circuit which is connected to the regeneration-combustion channel via a precombustion steam supply duct which opens into said channel before the combustion chamber. continuous with respect to the direction of flow of the gas-vapor mixture and / or atmospheric air in said channel. The turbine engine according to the present invention comprises a precombustion steam supply duct which comprises a pre-combustion vapor inlet flap which can close or open said duct. The turbine engine according to the present invention comprises an outlet duct ^of regeneration exchanger which comprises a préehauffage pane and / or vaporization of liquid water upstream of the steam regenerator-condenser against the current relative to the flow direction a gas-vapor mixture in said duct, said shutter enabling the engine management computer EMS to direct all or part of said mixture first to said condenser-regenerator then to the exhaust line outlet or directly to said outlet .

The turbocharger according to the present invention comprises a turbocharger turbine which comprises vanes with variable geometry which can guide a flow of gas-vapor mixture passing through said turbine during operation of the turbine engine.

The turbine engine according to the present invention comprises a drive turbine for expansion which comprises vanes with variable geometry which can guide a flow of gas-vapor mixture passing through said turbine during operation of the turbine engine.

The turbine engine according to the present invention comprises a regenerative countercurrent air / mixture exchanger which comprises at least one internal countercurrent regeneration heat exchanger duct in which circulates the atmospheric air expelled by the centrifugal turbocharger compressor, and at least one outer casing of échangeu regeneration against the current envelope and / or adjacent to said inner conduit, said housing leaving a gap between itself and said inner tubing which ^contains and / or adjoins while the gas mixture steam expelled by the turbocharger turbine and / or the expansion turbine driver circulates in said space, the direction of circulation of said mixture in said space being inverse to that of the circulation of said air in said conduit.

The turbine engine according to the present invention comprises a countercurrent regeneration exchanger internal duct which has fins or daisy section which provide a large contact surface simultaneously with the gas-vapor mixture circulating in the space between the countercurrent regeneration exchanger outer casing and said duct, and with the atmospheric air circulating at inside said duct.

The turbine engine according to the present invention comprises a countercurrent regeneration / regeneration cooler outlet which comprises a regeneration exchanger outlet duct in which circulates the gas-vapor mixture expelled by the turbocharger turbine and / or the expansion turbine engine, said duct connecting said exchanger with the inlet of a countercurrent air / gas exhaust cooler in which flows on the one hand said gas-vapor mixture expelled by said turbocharger turbine and / or said driving expansion turbine and, secondly, an atmospheric air expelled by means of cooling-condensation of air blowing after said air has been sucked into ^the atmosphere by means lesdifs via an inlet mouth of cooling-condensing air and via a cooling-condensing air intake duct and then being blown into said cooler-condenser via a duct ^Insufflation and a mouth of cooling-condensation of blowing air that comprises said cooler-condenser, said mixture heats said air inside ëuétî cooler-condenser before said air comes out of said condenser by a refroidisseur- mouth of exhaust ^air from cooling-condensation via an air blowing mouth of cooling-condensation that comprises said cooler-condenser and a blow duct which connects said blower port to said exhaust outlet.

The turhomofeur according to the present invention comprises an outlet of the counter-current steam condenser-regenerator which comprises a condenser-regenerator outlet duct in which circulates the gas-vapor mixture expelled by the turbocharger turbine and or the main driving turbine. said duct connecting said condenser-regenerator with the inlet of a countercurrent air / gas exhaust aftercooler / cooler in which circulates on the one hand: said gas-vapor mixture expelled by said turbocharger turbine and / or said driving expansion turbine and ^the other hand, an atmospheric air expelled by means of cooling-condensation of air blowing after said air has been sucked into the atmosphere through lesdiis means via an air intake opening Cooling-condensation and via a cooling-condensing air intake duct and then blown into said cooler-condenser via an insufflation duct and a cooling-condensing air insufflation mouthpiece which comprises said cooler-condenser, said mixture heating said air inside the cooler-condenser before said air comes out of the cooler-condenser through a cooling-condensing air exhaust mouth via a cooling-condensing air blower port included in said cooler condenser and a blowing duct which connects said blower mouth to said exhaust mouth.

The turbine engine according to the present invention comprises a countercurrent air / gas exhaust aftercooler which comprises at least one internal counter-current cooler-condenser duct in which circulates the gas-vapor mixture expelled by the turbocharger turbine and / or the drive turbine for expansion, ei at least one outer casing of counter-current cooler-condenser which surrounds and / or adjoins said Intome duct, said casing leaving a space between itself and said internal duct it contains and / or adjoins while the atmospheric air expelled by the cooling-condensing air blowing means circulates in said space, the direction of circulation of said air in said space being inverse to that of the circulation of said mixture in said duct.

The turbine engine according to the present invention comprises an internal condenser cooler-condenser duct which has fins or daisy section which offer a large contact surface simultaneously with the atmospheric air flowing in the space between the external chiller-condenser casing against the current and said duct, and with the gas-vapor mixture circulating inside said duct.

The turbine engine according to the present invention comprises means for cooling-condensation of air insufflation which consist ^of a centrifugal compressor condensation-cooling air driven by an electric engine compressor air cooling-condensation.

The turbine engine according to the present invention comprises a counter-regeneration air / mixture exchanger heat exchanger which comprises a regeneration exchanger outlet duct in which the mixture circulates. gas-vapor expelled by the turbocharger turbine and / or the expansion turbine, said duct connecting said exchanger with the return of a liquid / water preheating exchanger / water exchanger in which circulates on the one hand, the gas mixture -vapeur expelled by the turbocharger turbine and / or the driving expansion turbine and ^the other hand, a liquid water before the latter is injected into the regeneration combustion channel, said mixture warming said water within said mixing / water exchanger.

The turbine engine according to the present invention comprises a regeneration exchanger outlet duct which comprises a preheating flap and or vaporization of liquid water placed upstream of the liquid water preheating mixture / water exchanger with respect to the direction of flow. flow of the gas-vapor mixture in said conduit, said shutter enabling the engine management computer of the ErVIS turbine engine to orient all or part of said mixture first to said mixing / water exchanger and then to the exhaust line outlet or directly towards said output.

The following turbine engine, the present invention comprises a liquid water which comes from the gas-vapor mixture expelled by the turbocharger turbine and / or the drive turbine from which it is extracted by means of a condensate separator-recuperator placed on the line exhaust, said separator-recuperator recovering said water having previously condensed on the inner walls of said line for storage in a condensate recovery tank.

The turbine engine according to the present invention comprises a condensate separator-recuperator which comprises an internal condenser separator-recuperator conduit provided with draining condensate orifices through which the liquid water flows by gravity to the condensate recovery tank where said water is temporarily stored.

The turbine engine according to the present invention comprises an internal condensate separator-recuperator duct which contains an iron straw or lab structure which retains or condenses suspended water in the form of droplets and / or vapor in the gas-gas mixture. vapor expelled by the turbocharger turbine and / or the drive turbine for expansion so that said water flows via the draining orifices of the condensates to the tank of recovery of the condensates rather than being carried away by said gases to the exit of the exhaust line,

The turbine engine according to the present invention comprises a liquid water which is conveyed from the condensate separator-recuperator to the regeneration-combustion channel by at least one condensate pump via at least one condensate recirculation duct.

The turbine engine according to the present invention comprises a condensates recirculation duct which may comprise an Intermediate condensates storage tank for temporarily storing the liquid water.

The turbine engine according to the present invention comprises a condensates recovery tank and / or a condensates recirculation pipe which comprises a condensate filter.

The turbine engine according to the present invention includes a regenerative-combustion channel comprising a injeeteur water precombustion anii NOx placed back in the combustion chamber continues to the direction of flow ^of said atmospheric air into said channel being able to inject a injeeteur liquid water in said channel.

The turbine engine according to the present invention comprises a ^duct power turbine inlet steam-gas relaxation which comprises an expansion turbine inlet valve controlled by the EMS turbine engine management computer said valve can seal said conduit.

The turbine engine according to the present invention comprises a drive turbine for expansion which is mounted on the drive turbine shaft by means of a pressure-free expansion turbine link, said link enabling said turbine to drive in rotation said shaft, but not the opposite.

The turbine engine according to the present invention comprises an expansion power turbine which is mounted on the expansion turbine drive shaft by means of a gear coupler and / or a clutch. The turbine engine according to the present invention comprises a drive turbine shaft for expansion which is connected to an electric turbine generator by means of a mechanical generator transmission, said generator being able to produce electricity when it is rotated by said tree.

The turbine engine according to the present invention comprises a mechanical generator transmission which consists of a generator drive epicyclic train.

The turbine engine according to the present invention comprises an electric turbine generator which is electrically connected to an electromagnetic accumulator and / or to an electrostatic accumulator.

The turbine engine according to the present invention comprises a blowing duct which comprises a start-bypass air shutter of the turbine engine which can force all or part of the atmospheric air soding the air-gas exhaust / cooling condenser-counter-current to go to the intake duct of the turbine engine via a start-bypass air channel of the turbine engine while prohibiting access to the condensing cooling air outlet while an air damper turbine engine starting obstruction, said intake duct is prohibited from said air going up towards the turbine engine air inlet while forcing said air towards the inlet of the turbocharger compressor and while prohibiting any or part of the atmospheric air from the turbine engine air intake mouth to join the inlet of said compressor.

The turbine engine according to the present invention comprises a regeneration-combustion channel which comprises a pollutant post-treatment catalyst placed after the continuous combustion chamber with respect to the direction of circulation of the atmospheric air and / or of the gas-vapor mixture in said channel

The turbine engine according to the present invention comprises a gas-steam exhaust gas engine of expansion and / or a gas-steam inlet gas turbine engine expansion which comprises a post-treatment catalyst pollutants. The turbine engine according to the present invention comprises a regeneration-combustion cana and / or a gas-steam induction turbine engine and / or a gas-steam exhaust gasoline engine and / or an exchange air / mixture against the regenerative current which is coated with a material and / or heat insulating structure internal and / or external holding the heat from ^the atmospheric air and / or gas-vapor mixture flowing ê within said bodies .

The turbine engine according to the present invention comprises an ^intake duct of the turbine engine which includes an intake air filter of the turbine engine.

The turbine engine according to the present invention comprises a cooling-condensing air intake duct which comprises an air-cooling-condensing air filter.

The turbine engine according to the present invention is installed in a motor vehicle so as to directly or indirectly provide propulsion to said vehicle, the latter having a fuel tank and a fuel pump which supply fuel to the continuous combustion fuel injector.

The turbine engine according to the present invention comprises a drive turbine shaft expansion which is connected to at least one wheel that comprises the motor vehicle by mechanical transmission means.

The turbine engine according to the present invention comprises an electric turbine generator that supplies electrical power to at least one electric propulsion-regeneration motor-generator connected to at least one wheel that the motor vehicle comprises via a mechanical engine transmission. -generator.

The turbine engine according to the present invention comprises a mechanical engine-generator transmission which consists of an epieyeioidal engine-generator transmission train.

The turbine engine according to the present invention comprises a blowing duct which comprises an air / water heat exchanger heat recovery in which circulates on the one hand, the atmospheric air expelled by the cooling-condensation air blowing means and, on the other hand, a fluid eacoporteun said air heating said fluid inside the air / water exchange, The The turboshaft engine according to the present invention comprises a blowing duct which includes a residual heat recovery flap placed upstream of the heat exchanger air / water for residual heat recovery with respect to the direction of flow of the atmospheric air in said duct. said shutter enabling the EMS turbine engine management computer to orient all or part of the air ddlt first to said air / water exchanger and then to the cooling-condensing air exhaust mouth or directly to said mouth.

The turbine engine according to the present invention comprises an air / water heat exchanger for residual heat recovery which is connected by at least one heating fluid duct to a heating radiator, the heat transfer fluid flowing in said duct.

The turbine engine according to the present invention comprises at least means ^for condensation-cooling air insufflation and at least the centrifugal compressor condensation-cooling and air. the cooling-condensing air compressor electric motor of which said means are constituted and / or a cooling-condensing air-blowing air filter which are commonly housed in a cooling air-blowing casing- condensation while connectors out of said housing that connect at least the cooling-condensing air intake duct and / or the insufflation duct.

The turbine engine according to the present invention comprises a continuous combustion chamber which is a heat exchanger connected directly or indirectly to a heat source.

The turbine engine according to the present invention comprises a heat source that consists of a condenser that includes a heat pump which extracts heat from ^an environment.

The turbine engine according to the present invention comprises a heat pump which is rotated by the drive turbine shaft. The turbine engine according to the present invention comprises an atmospheric air sucked via the turbine engine air inlet by the centrifugal compressor turbocharger which is previously cooled by an evaporator that includes the heat pump.

The turbine engine according to the present invention comprises an atmospheric air sucked via the air intake intake cooling-ondensation by the means of insufflation of cooling air-condensation which is previously cooled by an evaporator that includes the heat pump .

The turbine engine according to the present invention comprises a drive turbine shaft which can be driven in rotation by the expansion turbine, said shaft being able in turn to rotate a turbine driving pinion which drives in rotation a ring of multi-turbine gearbox that can rotate a multi-turbine gearbox output power shaft,

The turbine engine according to the present invention comprises an expansion drive shaft which is connected at one of its ends to the expansion drive turbine and at its other end to the turbine drive pinion via a seal of transmission.

The turbine engine according to the present invention comprises a multi-turbine gear output power shaft which terminates with a power output cyclic cycle train.

The following turbine engine, the present invention comprises a turbine drive pinion which is mounted on the drive turbine shaft by means of a free wheel connection, said link enabling said shaft to rotate said pinion. , but not the other way around.

The turbine engine according to the present invention comprises a multi-turbine gear ring which is mounted on the multi-turbine gearbox output shaft via a gearbox crown gear which enables said gearbox rotate said shaft, but not vice versa. The turbine engine according to the present invention comprises at least two turbochargers, the first being a low-pressure turbocharger whose low-pressure turbocharger centrifugal compressor pre-compresses the atmospheric air that it sucks via the air intake port. turbine engine when said compressor is rotated by the low-pressure turbocharger turbine of said low-pressure turbocharger, while the second is a high-pressure turbocharger whose centrifugal compressor of high-pressure turbocharger overcompacts the air expelled by the centrifugal compressor of low-pressure turbocharger before ^expel in turn in the regenerative-combustion channel when said compressor is driven in rotation by the turbine high-pressure turbocharger that includes said Upper pressure turbocharger, the outlet of the centrifugal compressor Turbocharger Passenger being connected to the inlet of the high-pressure turbocharger centrifugal compressor through an inter-compressor linkage channel while the high-pressure turbocharger turbine pre-separates a gas-vapor mixture from the regeneration-combustion channel before expelling it at the inlet of the low-pressure turbocharger turbine which over-relaxes said mixture before expelling it in turn into the gas-steam exhaust gas turbine engine.

The following turbine engine, the present invention comprises an inter-compressor linkage channel which comprises a turbocharger intercooler which cools the air expelled by the low pressure turbocharger centrifugal compressor before said air is supercharged by the centrifugal turbocharger compressor. high pressure.

The turbine engine according to the present invention comprises a high-pressure turbocharger centrifugal compressor which comprises a high-pressure compressor bypass valve which, when opened by the engine management computer EMS, can direct a part of the air from the centrifugal compressor of low-pressure turbocharger directly to the regeneration-combustion channel without passing through the centrifugal compressor of high-pressure turbocharger. The turbine engine according to the present invention comprises a high-pressure turbocharger which comprises a high-pressure turbine bypass valve which, when it is opened by the engine management computer ES, to direct a portion of a gas mixture vapor from the regeneration-combustion channel directly from said channel to the low pressure turbocharger turbine without passing through the high pressure turbocharger turbine.

The turbine engine according to the present invention comprises a turbine engine intake duct which comprises an electropneumatic starter consisting of a centrifugal compressor of an electropneumatic starter which can be rotated by an electric motor of the electropneumatic starter so that said compressor compresses the atmospheric air. from the turbine engine air intake port to the inlet of the centrifugal turbocharger compressor.

The turbine engine according to the present invention comprises an intake duct of the turbine engine which comprises an electropneumatic starting flap controlled by the engine management computer of the EMS turbine engine, said flap enabling said computer to force the atmospheric air coming from the intake port of the engine. Turbomotor air to be passed through the centrifugal compressor of the electro-pneumatic starter before joining the inlet of the centrifugal compressor of turbocharger when said flap is in a first position, or to pass through an electropneumatlque starter contamina before, to join said inlet when said flap is in a second position.

The turbine engine according to the present invention comprises an exhaust line which comprises an air / water heat exchanger exhaust heat exchanger in which a circulating water circulates also in a heating radiator which heats a solid, liquid or gaseous environment, said exchanger connected to said radiator by heating radiator conduits while said water is forced to flow through said heat exchanger, said radiator and said conduits through an exhaust heat recovery water pump the gas-vapor mixture expelled by the turbocharger turbine and / or the expansion turbine engine heating said water inside or exchanger before said mixture comes out of the outlet of exhaust line while said water is cooled inside the heating radiator by said environment.

The turbine engine according to the present invention comprises an exhaust line which comprises an exhaust heat recovery flap controlled by the EMS turbine engine management computer, said flap enabling said computer to force the gas-vapor mixture expelled by the turbine from the engine. turbocharger and / or the main driving turbine to pass through the air / water heat exchanger exhaust heat recovery before joining the exhaust line exit when said flap is in a first position, or to go through a channel the exhaust heat exchanger is flanked before joining said outlet when said flap is in a second position.

The turbine engine according to the present invention comprises a regenerative counter-current air / mixture exchanger which is arranged in a deformable structure constituting a shock absorber.

The following description with reference to the accompanying drawings, given by way of non-limiting examples, will provide a better understanding of the invention, the characteristics it presents, and the advantages that it is likely to provide:

Figure 1 illustrates the schematic diagram of the turbine engine according to the present invention equipped with a mixture exchanger / water preheating liquid water.

Figures 2 and 3 are schematic views of the turbine engine according to the present invention as it can be provided for propelling a motor vehicle.

4 is a diagrammatic cross-section of the regenerative countercurrent regeneration exchanger of the turbine engine according to the present invention, such that it can be provided when the countercurrent regeneration exchanger internal duct has a daisy section; said duct being constituted of several said ducts.

FIG. 5 is a diagrammatic section of the countercurrent air / gas exhaust gas cooler / condenser of the following turbine engine: the present invention that! may be provided when the countercurrent internal cooler-condenser duct has a daisy section.

FIG. 6 is a diagrammatic section of the separator-recuperator of the condensates of the turbine engine according to the present invention,

FIG. 7 illustrates the schematic diagram of the turbine engine according to the present invention equipped with a condenser-regenerator of steam against the current

FIG. 8 illustrates the schematic diagram of the turbine engine according to the present invention as it can be provided with two turbochargers, a turbocharger intercooler, a turbogenerator, an electro-pneumatic starter and a multi-turbine group, to the exclusion of all liquid water spraying device.

FIGS. 9 and 10 are three-dimensional views of a group of multi-turbines that may comprise the turbine engine according to the present invention, said group Including, according to this example, four expansion turbines each mounted on a driving turbine shaft of expansion which ends with a driving pinion co-operating with a multi-threaded gear ring gear so as to rotate a power output shaft of a multi-turbine gearbox

Figure 1 1 is a schematic sectional view of a gearwheel crown freewheel such that it can be provided on a ring gear of niulti-turbines that can comprise the turbine engine according to the present invention

DESCRIPTION OF THE NVENTION ..,,

FIGS. 1 to 3 show the low pressure internal combustion and / or external water vaporization and / or regeneration turbine 1.

The turbine engine 1 according to the invention comprises at least one turbocharger 2 cooperating with at least one regeneration-combustion channel 34 which directly or indirectly connects the outlet of a centrifugal compressor of turbocharger 81 that comprises said turbocharger 2 with the inlet of a turbocharger turbine 82 comprising said turbocharger 2, said compressor 61 expelling atmospheric air in said channel 34 after vacuum sucked via a turbine engine air intake port 80 and via an intake duct of the turbine engine 58.

FIG. 1 shows that the channel 34 comprises at least one continuous combustion chamber 35 internal or external to said channel 34 in which a fuel can be burned after having been injected by at least one continuous combustion fuel injector 36.

The centrifugal turbocharger compressor 61 and / or said turbocharger turbine 62 may be integrally mounted on the same shaft or be interconnected by means of transmission gear ratio, fixed or discrete or continuous variable ratio, said means being able to be mechanical, electrical, hydraulic or pneumatic while said compressor 81 and / or said turbine 62 may comprise several stages mounted or not in series on the same shaft.

Also, the turbocharger 2 can cooperate with other turbochargers with which it is mounted in series or in parallel while the interior and / or exterior of the continuous combustion chamber 35 may be made of or coated with a refractory material and / or or heat-resistant to high temperature resistance and have a spark plug 63 comparable to those found in internal combustion engines with spark ignition, said spark plug 63 possibly cooperating with a not shown preheating brew.

The turbine engine 1 according to the invention comprises at least one driving pressure turbine 3 mounted on a drive turbine shaft 67, the inlet of said turbine 3 being connected directly or indirectly to the regeneration-combustion channel 34 by at least one gas-steam intake duct for driving the expansion turbine 66 while said drive turbine 3 relaxation may comprise several stages mounted or not in series on the same arh.

It should be noted that, according to a particular embodiment of the turbine engine 1 according to the invention, the drive turbine 3 may be the turbine turbocharger 82 itself. It can be seen in FIG. 1 that the turbulator 1 comprises at least one regenerative counter-current air / mixture exchanger 30 forming part of the regeneration-combustion channel 34 and in which flows, on the one hand, a gas-vapor mixture expelled by the turbocharger turbine 62 and / or the driving expansion turbine 3 the output of said turbine being connected to said heat exchanger 30 through a conduit ^exhaust gas-steam driving expansion turbine 70 and on the other hand, the atmospheric air expelled by the turbocharger centrifugal compressor 61 said mixture heating said air inside said exchanger 30 before exiting through an exhaust line 55 via an exhaust line 54.

As shown in FIG. 2, as an alternative to or in addition to the regeneration / regeneration air / mixture exchanger 30, the turbine engine 1 may comprise a countercurrent steam regeneration condenser 8. wherein circulates ^a graze the mixture g & z ~ steam exhausted from said turbocharger turbine 62 and / or the driving expansion turbine 3 in a gas-vapor mixture circuit regenerator-condenser 88 and in which circulates the other hand a liquid water 45 in a condenser-regenerator water circuit 89 which is connected to the regeneration-combustion channel 34, said mixture heating said water 45 to the failure of the condenser-regenerator bed 87 through the internal walls of this last while a significant fraction of the water vapor contained in said mixture condenses inside said condenser-regenerator 87 by yielding its heat to the liquid water 46 so that the latter is vaporized in whole or part, the condenser-regenerator inlet 87 being connected either with the outlet of the regeneration countercurrent air / mixture exchanger 30 via a regeneration exchanger outlet conduit 84 which is said exchanger and in which circulates the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the expansion drive turbine 3, either directly to the exhaust gas-steam exhaust gas engine 70.

It will be noted that the exhaust line 54 and / or the regeneration-combustion channel 34 and / or the gas-steam induction turbine driving duct 86 and / or the intake duct of the turbine engine 58 and / or any other member of the turbine engine 1 containing a liquid or a gas may comprise at least one temperature sensor and / or at least one pressure sensor and / or at least one key, said sensors and said flow meter informing the ES 57 turbocontrol management calculator,

In addition, the uremometer 1 comprises at least one management computer EMS 57 turbocharger.

According to a particular embodiment, the regeneration-combustion channel 34 comprises at least one water vaporization chamber 37 internal to said channel 34 in which a liquid water 45 may be injected by a post-combustion water injector 38 so as to realize a gas-vapor mixture.

^The liquid water 45 is injected llnjecteur water afterburner 38 so that said water 45 vaporizes water in the vaporization chamber 37 in order to produce superheated steam during operation of the iurbomoieur 1 in order to to increase the overall efficiency of the latter, and to protect the various mechanical work production members from any excessive temperature which is likely to compromise the thermomechanical behavior of said organs and / or the manufacture at moderate cost of said organs.

According to a particular embodiment of the turbomolder 1, the liquid water 45 may be a fluid that boils at low temperature when it is subjected to atmospheric pressure.

As shown in Figure 7, the first regenerator condenser water circuit 89 is comprised ^of at least one internal duct condenser-regenerator 90 in which circulates the liquid water 45, while the gas-steam condenser mixing circuit -regenerator 88 consists of at least one external condenser-regenerator casing 91 which surrounds and / or adjoins said inner duct 90, said casing 91 leaving a space between itself and said internal duct 90 that it contains and / or adjacent while the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the expansion turbine driver 3 circulates in said space, the flow direction άυύιί mixing in said space being opposite to that of the circulation of said water 45 in said conduit 90.

According to a particular embodiment of the turbomolder 1 according to the invention, the condenser-regenerator water circuit 89 is connected to the cooling channel. regeneration -combustion 34 via a conduit steam supply afterburner 94 which opens into said channel 34 after the combustion chamber 35 continues in the direction of flow of the steam-gas mixture and / or ^air in said channel 34.

In the latter context, the postcombustion steam supply duct 94 little! comprise a steam inlet flap afterburner 95 which may close or open said conduit 94, said pane 95 may consist of a valve, a rotary valve, a valve or any other means known to ^the man of art for closing a conduit, said shutter 95 can be controlled in opening or closing by the engine management computer EMS 57 including su using a pneumatic actuator, electro-pneumatic, electric, hydraulic or electro-hydraulic.

Alternatively or additionally, the condenser-regenerator water circuit 89 may be connected to the regeneration-combustion channel 34 via a precombustion steam supply conduit 92 which opens into said channel 34 before the chamber continuous combustion 35 with respect to the direction of flow of the gas-vapor mixture and / or atmospheric air in said channel 34.

According to this variant, the precooling steam supply duct 92 may comprise a precombustion vapor inlet flap 93 which can seal or open said duct 92, said flap 93 possibly consisting of a valve, a bushel rotary, a valve or any other means known to those skilled in the art for closing a conduit, said flap 83 can be controlled opening or closing by the engine management computer EMS 5? in particular by means of a pneumatic, electropneumatic, electric, hydraulic or electro-hydraulic actuator

It will be noted that the regeneration exchanger outlet duct 34 may comprise a preheating flap and / or vaporization of liquid water 78 placed upstream of the countercurrent vapor regeneration condenser 87 with respect to the direction of flow of the gas-vapor mixture in said duct 84, said flap 78 allowing the management computer of the turbine engine EMS 57 to direct all or part of said mixture is first to said condenser-regenerator 37 and then to the exhaust line outlet 55 is directly to said set 55, As represented in FIG. 1, the turbocharger turbine 62 comprises vanes with a variable geometry 78 which can guide a stream of gas-vapor mixture passing through said turbine 62 during the operation of the turbine engine 1, the angular orientation of said vanes 78 being able to be modified by the ES 57 turbine engine management computer by means of a pneumatic actuator ,. electropneumatic, electric, hydraulic or electro-hydraulic so as to adjust the power of said turbocharger turbine 62.

Alternatively, said turbine 62 may be of "slidevane" type or any other type known to man Tari, which allows to adjust the passage section of gas-vapor mixture flow passing between said turbine 62 and its housing.

Similarly, the expansion drive turbine 3 comprises vanes with a variable geometry 77 which can guide a flow of gas-vapor mixture passing through said turbine 3 during operation of the turbine engine 1, the angular orientation of said vanes 77 being able to be modified by the management computer of the turbine engine EMS 57 by means of a pneumatic, electropneumatic, electric, hydraulic or electro-hydraulic actuator so as to regulate the power of said driving expansion turbine 3, while alternatively, said turbine 3 may be of type "slidevane" or any other type known to those skilled in the art that allows to adjust the passage section of the gas-vapor mixture flow passing between said turbine 3 and its housing.

According to a particular embodiment of the turbine engine 1 according to the invention, the air exchanger / countercurrent regeneration mixture 30 comprises at least one internal conduit countercurrent regeneration heat exchanger 31 in which circulates the atmospheric air expelled by the centrifugal compressor of turbocharger 61, and at least one external rack of countercurrent regeneration exchanger 33 which surrounds and / or adjoins said Internal conduit 31, said casing 33 leaving a space between itself and said internal duct 31 that it contains and / or adjoins while the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the expansion turbine 3 circulates in said space, the direction of circulation dudii mixture in said space being opposite to that of the circulation άυάιϊ air in said duct 31, In FIG. 4, it has been shown that the counter-current regeneration exhaust internal duct 31 has ducts or daisal section 32 that offer a large contact surface simultaneously with the gas-vapor mixture that circulates in space. comprised between the countercurrent regeneration heat exchanger outer casing 33 and said duct 31 and with the atmospheric air circulating inside the duct duct 31 so as to favor the heating of the atmospheric air by the gas-vapor mixture, while the daisy section 32 may for example be obtained by hydroferming of a stainless steel tube or not.

FIG. 1 shows that the outlet of the regeneration countercurrent air / mixture exchanger 30 comprises a condenser-regenerator outlet duct 129 in which circulates the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the drive turbine 3, said duct 129 connecting said exchanger 30 with the inlet of a countercurrent air / gas exhaust cooler-condenser 18 in which flows on the one hand said gas-vapor mixture expelled by said turbine turbocharger 82 and / or said expansion turbine 3 and ^{on the} other hand, an atmospheric air expelled by means of cooling-condensing air blowing 28 after said air has been sucked into the atmosphere by! esd! Average means 28 via a cooling-condensing air inlet 22 and via a cooling-condensing air inlet duct 64 and then blown into said condenser-cooler 18 via a duct. blowing mouth 24 and a condensation-cooling air blowing 20 comprises that said cooler-condenser 18, said mixture heats said air to ^the lower dudlt cooler-condenser 16 before said air dudlt comes refroidlsseur- condenser 18 by an exhaust mouth; cooling-condensing air-outlet 23 via a cooling-condensing air-blowing outlet 21 included in said cooler-condenser 18 and a blowing duct 25 which connects said blower outlet 21 to said exhaust port 23.

The air-to-gas exhaust cooler-condenser. against counter current 16 comprises at least one internal counter-current cooler-condenser duct 17 in which circulates the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the defensive driving turbine 3, and at least one outer casing counter-current cooler-condenser 19 which envelope and / or adjacent to said inner conduit 17, said casing 19 leaving a space between itself and said inner conduit 17 that contains and / or pl e while atmospheric air expelled by means ^of air insufflation cooling-condensation circuit 26 circulates in said space, the direction of circulation ofdii air in said space being opposite to that of the circulation ûuéit mix in said conduit 17,

As illustrated in FIG. 5, the counter-current internal combustion-convector duct 17 has fins or daisy-section 18 which offer a large contact surface simultaneously with the atmospheric air circulating in the space between the outer casing countercurrent cooler-condenser unit 19 and said duct 17, and with the gas-vapor mixture circulating inside the interior where it conducts 17 so as to promote the heating of atmospheric air by the gas-vapor mixture, while the daisy section 18 may for example be obtained by hydroforming of a tube of ^stainless steel or not.

In Figure 1 _s showed that the means for condensation-cooling air insufflation 26 consist of a centrifugal compressor condensation-cooling air 27 driven by an electric motor condensation-cooling air compressor 28 said compressor 27 may in particular be of similar design to turbo-supercharger compressors or include a blower wheel paddle or propeller blades.

Whatever the type of said compressor 27, the electric motor 28 can be regulated in power and / eu in rotation by the management engine of the turboshaft engine BUS 57 as a function of the atmospheric air flow rate that is necessary to insufflate in the countercurrent air / gas exhaust cooler-condenser 18,

FIG. 1 illustrates that according to a particular embodiment of the turbine engine 1 according to the invention, the outlet of the mixed air exchanger with regeneration countercurrent 30 compodes a regeneration regeneration outlet pipe 84 in which the expired gas-vapor mixture circulates. by the turbocharger turbine 62 and / or the driving expansion turbine 3, said conduit 84 connecting said heat exchanger 30 with the inlet ^of a mixing / water exchanger of preheating of liquid water 79 in which circulates on the one hand, the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the drive turbine 3 and on the other hand, a liquid water 45 before the latter is injected into the regeneration-combustion channel 34, said mixture heating said water 45 inside the mixing exchanger / water 79.

In addition, the regeneration exchanger outlet duct 84 comprises a preheating flap and / or vaporization of liquid water 78 placed upstream of the liquid water preheating mixture / water exchanger 79 with respect to the direction of flow. flow of the gas-vapor mixture in said duct 84, said flap 78 enabling the management computer of the turbomixer EUS 57 to direct all or part of said mixture first to said mixing exchanger / water 79 and then to the line exit of exhaust 55 or directly to said outlet 55.

FIG. 1 also shows that the liquid water 45 comes from the gas-vapor mixture expelled by the turbocharger turbine 82 and / or the expansion turbine 3 from which it is extracted by means of a condensate separator-recuperator 40 placed on the exhaust line 54, said separator-recuperator 40 recovering said water 45 having previously condensed on the internal walls of said line 54 to store it in a condensate recovery tank 43, said separator-recuperator 40 may in particular force said liquid water 45 to flow into said tank 43 by gravity, or by a centrifugationlon created by a free spiral shape or tangentl conduits that includes the interior of the separator-recuperator 40 said hundred generating a cyclone that projects said water 45 on the inner walls cudii separator-recuperator which are connected to said tray 43 by one or more channels or orifices, while the gas-vapor mixture mainly freed of its liquid water 45 escapes through the center of the cyclone towards the exit of the exhaust line 55.

The separator-recuperator of the condensates 40 further comprises an internal condenser separator-recuperator duct 41 provided with condenser orifices 42 through which the liquid water 45 flows by gravity to the condensate recovery tank 43 where said water 45 is temporarily stored. FIG. 6 illustrates the condenser separator-recuperator inner conduit 41 which contains an iron straw or honeycomb structure 44 which retains or condenses suspended water in the form of droplets and / or vapor in the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the expansion turbine engine 3 so that said water flows via the draining orifices of the condensates 42 to the condensate recovery tank 43 rather than being carried by said gases to the set with exhaust line 55,

The liquid water 45 is then conveyed from the separator-recuperator of the condensates 40 to the regeneration-combustion channel 34 by at least one condensate pump 46 via at least one condensate recirculation duct 47, said pump 46 being drivable by an electric motor and consist of a hydraulic turbine, pistons, a membrane, or any other means of pumping known to the man of Pari,

It can be seen in FIG. 1 that the condensates recirculation duct 4? may comprise an intermediate reservoir for storing condensates 43 for temporarily storing liquid water 45, said intermediate reservoir 48 being able for example to consist of a plastic bladder that can not be destroyed by the possible freezing of liquid water 45 and allowing if necessary the addition of liquid water by an operator.

The condensate recovery tank 43 and / or the condensate recirculation pipe 47 comprises a condensate filter 49 which can be static and constituted by a filtering element made of cloth, paper, foam or any other material known to the skilled in the art for its filtering properties and / or can be dynamic and operate a filtratlon by centrifugation or electrostatic, said filter 49 retaining in particular the particles that convey liquid water 45.

The combustion-regeneration of channel 34 shown in Figure 1 comprises a water-precombustion anii NGX injector 39 positioned before the continuous combustion chamber 33 relative to the direction of flow ^of atmospheric air into said channel 34 said injector 39 can inject a liquid water 45 in said channel 34, said water 45 allowing in particular and in this context, to reduce the temperature of the combustion operated in the continuous combustion chamber 35 so that said combustion does not produce or ^few nitrogen oxides, while said water noiamrnent 45 may come from the recovery tank 43 of the condensate.

It can be seen in FIG. 1 that the gas-steam induction turbine driving duct 86 comprises an expansion turbine inlet valve 4 controlled by the ES 57 turbocharger management computer, said valve 4 being able to close off and conducting 66 and said valve 4 being able to allow or prohibit the gas-vapor mixture to go from the regeneration-combustion channel 34 to the booster driving urbine 3.

In any event, the valve 4 may consist of a shutter, a rotary plug, a valve or any other means known to those skilled in the art for sealing an orifice or a duct, said valve 4 can be driven in opening or closing by the EMS 57 turbine engine management computer, in particular by means of a pneumatic, pneumatic, electric, hydraulic or electro-hydraulic actuator.

The gas turbine engine défente 3 is mounted on ^the power turbine shaft of trigger 87 via a free wheel connection expansion turbine of said connecting S. 5 allowing said turbine 3 to rotate said shaft 87, but not the Inverse, said link 5 being cliqyet (s), billets), roll (x) or any other type known to those skilled in the art

Also, the expansion drive turbine 3 is mounted on the expansion drive shaft 67 via a gear coupler and / or a clutch, said gear coupler allowing said turbine 3 to rotate at a different speed. that of the shaft 87, said coupler may be an plcydoïdai train while the clutch can in particular be driven by the ECM management ECM 57 controller by means of an electroméeanique, electro-hydraulic or electro-pneumatic engine.

FIG. 1 shows that the expansion turbine drive shaft 67 is connected to an electric turbine generator 1 1 by means of a mechanical transmission of generator 8, said generator 1 1 being able to produce electricity when it is rotated by said shaft 67, said electricity being produced in the form of a direct or alternating current, at high or low voltage, while said transmission 6 can be fixed ratio or discrete variable ratio or continuous, and. Petu be hydraulic, electric, pneumatic, el possibly be constituted by a chain, ^a belt, rollers, a system en§ Tenage _s or any kind of transmission known to those skilled in the art.

The mechanical transmission of generator 6 consists of an epicyclic generator drive train 7, said train 7 also makes it possible to prevent a radial force from being exerted on the drive turbine shaft 87 by the torque generated by the drive turbine 3, and to achieve a high gear ratio between said shaft 67 and said generator 11, the output shaft of said generator being integral with the planet carrier epicyclic train 7 while the crown of said train 7 is ftm and that the sun gear is integral with the drive turbine shaft 87,

Note that the electric turbine generator 1 1 is electrically connected to an electrochemical accumulator 10 and / or to an electrostatic accumulator 89.

FIG. 1 shows that the blowing duct 25 comprises a starting bypass air shutter of the turbine engine 8 which can force all or part of the atmospheric air leaving the countercurrent air / gas exhaust cooling / cooler 16 to go to the inlet duct of the turbine engine 58 via a start bypass air channel of the turbine engine 85 while denying access to the condensing cooling air outlet 23 while a flap of air turbocharger start obstruction air 9 that includes said intake duct 58 prevents said air from rising towards the turbine engine air intake port 60 while forcing said air to the inlet of the turbocharger compressor 81 and prohibiting all or part of the atmospheric air from the turbine engine air intake port 60 from reaching the compressor inlet 81.

According to a particular embodiment of the turbine engine according to the invention, the regeneration-combustion channel 34 comprises a pollutant post-treatment catalyst 53 placed after the continuous combustion chamber 35 with respect to the direction of circulation of the atmospheric air and / or of the gas-vapor mixture in said channel 34, said catalyst 53 completing the combustion of the fuel operated in the combustion chamber continues 35 so as to avoid introducing gaseous pollutants at the inlet of the turbocharger turbine 62 and / or in the gas-steam induction turbine driving duct 68.

According to a variant not shown, the gas-vapw exhaust gas duct expansion 70 and or the gas-steam inlet gas turbine engine 68 may comprise a catalyst for post-treatment pollutants, said catalyst completion ^■ ·· · as before fuel combustion previously operated in the continuous combustion chamber 35 so as to prevent expelling of pollutants in exhaust gas output line 55.

It will be noted, particularly in FIGS. 1, 4 and 5, that the regeneration-combustion channel 34 and / or the gas-steam induction turbine driving duct 66 and / or the gas-vapor exhaust duct motive expansion turbine 70 and / or the air / mixture against the regenerative current 30 is coated ^with a material and / or internal heat insulating structure 51 and / or outer holding the heat from the atmospheric air and / or the gas-vapor mixture circulating inside said members 34, 66, 70, 30.

The heat-insulating material and / or structure 51 may consist of rockwool, a double or multiple skin (s) metal (s) or not and said material 51 may create a space possibly filled with a weakly thermo-thermal gas. conductor even partial or total vacuum, or screen (s} t ermique (s), these components being possibly kept at a distance from said bodies 34, 68 <70, 30 by thermal insulation pads, while said material and or structure 51 may also coat the air / gas exhaust air-cooled cooler / condenser 16 or any other member of the turbojet 1 according to the invention and be made of any other material and / or arrangement known to the man of the art and to retain heat.

Figure 1 illustrates that the output cf conduit do regeneration exchanger 84 comprises a mixture exchanger / liquid water preheater 79 wherein water flows on ^the one hand, the gas-vapor mixture exhausted from the turbocharger turbine 62 and / or the drive turbine 3 relaxation and secondly, the liquid water 45 before the latter is thirsty injected into the regeneration-combustion channel 34, said mixture heating said water 45 inside the ddlt exchanger mixture / water 79. 35

The flow direction eucilt mixture inside the heat exchanger 79 can be reversed to that of the circulation of said water 45 in said heat exchanger 79 so that this mixture can yield to said water 45 as much heat as possible.

The outlet pipe of the regeneration exchanger 84 comprises a preheating flap and / or vaporization of liquid water 78 placed upstream of the exchanger mixture / liquid water preheating water 79 with respect to the direction of flow of the mixture gas-vapor in said duct 84, said flap 78 enabling the management computer of the turbine engine ES 5 to direct all or part of the mixture to be first to said mixing / water exchanger 79 and then to the air cooler-condenser exhaust air counter-current gas 18 or directly to said cooler-condenser 16, said flap 78 being able to be an inlet valve and two outlets of any type known to those skilled in the art,

In addition, the intake duct of the turbine engine 58 comprises a turbine engine intake air filter 59 which reduces the size and the number of impurities expelled into the regeneration-combustion channel 34 by the centrifugal turbocharger compressor 61. said impurities having been previously sucked by said compressor 61 at the same time as the atmospheric air.

Similarly, the cooling-condensing air intake duct 64 includes a cooling-condensing air insufflation air filter 29 which reduces the size and the number of impurities expelled into the condenser cooler. exhaust air / gas against the stream 16 by the means for blowing ^air-cooling condensation 26. said impurities having been previously sucked by said means 26 together with the atmospheric air.

FIGS. 2 and 3 show the turbine engine i according to the invention which is installed in a motor vehicle 66 so as to ensure directly or indirectly the propulsion of the vehicle 56, the latter having a fuel tank 71 and a fuel pump 72 which supply fuel injection fuel continuous combustion 36, According to a particular embodiment, the turbojet 1 according to the invention can also ensure the supply of electricity and / or heat accessories and equipment safety, comfort, driving and managementdidii vehicle 56, while the motor vehicle 56 may include outlets for the intake of gas, fuel oil or any other fuel and outlets external output of electricity and hot air produced by said turbojet 1 so that said vehicle 56 can serve as a group autonomous production of electricity and heat for all domestic and / or industrial use.

Depending on the configuration chosen for producing the turbojet 1 according to the invention, the drive turbine shaft 87 is connected to at least one wheel 73 that the motor vehicle 56 comprises by means of mechanical transmission means, the means being able to be a gearbox cooperating or not with a clutch and / or a differential train, said box being manual or automatic with discrete or continuously variable ratios, based on at least one gear system, or at least one roller, a chain, a belt, hydraulic transceiver motors, or any other mechanical transmission means known to those skilled in the art.

In Figures 2 and. 3, it has been shown that the electric turbine generator 11 supplies electrical power to at least one electric propulsion-regeneration motor-generator 68 connected to at least one wheel 73 which the motor vehicle 56 comprises by means of a mechanical transmission of motor-generator 74.

In this context and according to this example, the engine-generator mechanical transmission 74 consists of a motor-generator transmission pulse train 75.

FIG. 1 shows that the blowing duct 25 comprises an air / water heat exchanger for residual heat recovery SI in which circulates, on the one hand, the atmospheric air expelled by the cooling-condensing air insufflation means 2.8 and on the other hand, a heat transfer fluid, said air heating said fluid inside said air / water exchanger 81 while the direction of circulation ddi air inside said exchanger 81 can be reversed to that of the circulation of said fluid in said exchanger 81 so that said mixture can yield to said fluid as much heat as possible.

Also, the blowing duct 25 comprises a residual heat recovery duct 80 placed upstream of the air / water heat recovery heat exchanger 81 relative to the direction of flow of atmospheric air in said duct 25 _s said voiet 80 allowing the iurfeomoteur EUS management computer 57 to direct all or part àuëû ^air is first to said air / water heat exchanger 81 and then to the air outlet mouth refroidissoment-condensaiion 23 either directly to said mouth 23, said flap 80 may be an inlet valve and two outputs of any type known to those skilled in the art.

In Figures 1, 2 and 3, it has been shown that the air / water heat recovery heat exchanger 81 is connected by at least one heating fluid duct 85 to a heating radiator 83, the coolant circulating in said duct 85 so as to transport heat from said exchanger 81 up radiator 83, the latter for example to heat the passenger compartment of a motor vehicle 56.

FIGS. 1 _< 2 and 3 also illustrate that at least the cooling-condensing air blowing means 26 and at least the centrifugal cooling-condensation air compressor 27 and the air compressor electric motor condensing coolant 28 of which said means are constituted and / or the cooling-condensation air blowing air filter 29 are commonly housed in a cooling-condensing air blowing box 50 while connectors 86 extend dud housing 50, for connecting at least the inlet ^duct condensation-cooling air 64 and / or conduit insufflation 24,

Thus, said insufflation box 50 is an autonomous subassembly that can be produced - for example - by an automotive supplier.

According to a particular configuration of the iurbo no 1 according to the invention, the continuous combustion chamber 35 is a heat exchanger connected directly or indirectly to a heat source said exchanger heating the atmospheric air after the latter has been expelled into the channel of regeneration-combustion 34 by the centrifugal compressor of turbocharger 81.

The heat source is constituted by a condenser that includes a heat pump that extracts heat from an environment, said heat pump extracting said heat from the ambient air, a watercourse or a heat pump. and being known per se to those skilled in the art, being commonly used in various home heating or industrial installations.

The heat pump is rotated by the defensive driving turbine shaft 67 directly or indirectly by means of any mechanical, electrical, hydraulic or pneumatic transmission device, variable and not generally known to the person skilled in the art. 't t.

The atmospheric air sucked through the air intake port of the turbocharger centrifugal compressor 61 is pre-cooled by a vaporizer included in the heat pump.

The atmospheric air sucked via the cooling-condensing air intake pipe 22 by the cooling-condensing air insufflation means 26 is pre-cooled by an evaporator included in the heat pump.

According to a particular configuration of the iurhomotor 1 according to the invention, the drive turbine shaft 87 is driven in rotation by the drive turbine 3, said shaft can in turn rotate in a turbine driver pl 1 which drives in rotation a ring of multi-turbine gear 1 14 which can rotate a multi-furbine gear output shaft 1 18, according to this principle, the same multi-turbine gear ring 1 14 can be driven in rotation by a plurality of driving expansion turbines 3 each driving said ring gear 114 via its turbine drive pinion 1 15.

According to another variant of this principle illustrated in FIGS. 8, 9 and 10, a plurality of multi-turbine gear reducers 1 14 can be mounted on the same multi-turbine gearbox output power shaft 1 18, each ring 11 being then driven. in rotation by a single drive turbine 3 cooperating with its drive turbine shaft 67 and its turbine drive pinion 1 15 so as to constitute, in these two cases, a multi-turbine group 126,

Whatever the configuration adopted, the various rotating elements that make up the roll-turbines group 126 ~ ie said turbines 3, said turbine shafts 67, said drive gears 115 ,. Said rings 114 or said power output shaft 1 18 ~ can be carried by hydrodynamic bearings, aerodynamic or axial and / or radial magnetic bearings, by roller or ball bearings of any type, or by any device known to the skilled in the art to ensure the rotation and guidance of said rotating elements with lower friction.

It will be noted that the expansion drive shaft 67 is connected at one of its ends to the expansion drive turbine 3 and at its other end to the turbine drive pinion 16 via a joint transmission which can be home-kinetic or not, with concurrent or parallel axes, flexible or rigid, with or without slide, cardan, ball, at a time, based on a flexible intermediate piece Flector type, or of any other type known to those skilled in the art,

The power output shaft of the multi-turbine gear unit 1 18 terminates with a power output epicyclic gear train 125,

In addition, the turbine drive pinion 15 is mounted on the drive turbo drive shaft 87 via a free wheel connection, said link enabling said shaft 67 to drive said pinion 115 in rotation. , but not vice versa, while in a not shown alternative, said connection may consist of a clutch controlled electrically, said clutch being of any type known to ^those skilled in the art.

As seen in Figure 1 1 the multi-turbines gear ring 114 is mounted on the shaft muiti-reducing turbine power output shaft 118 via ^a freewheeling ring gear 11? which allows said ring gear 114 to rotate said shaft 118, but not the Inversse. while according to an alternative not shown, said freewheel 117 can be replaced by an electrically controlled clutch, said clutch being of any type known to those skilled in the art.

The invention according to the present invention comprises at least two turbochargers 2,. the first being a low-pressure turbocharger 103 whose low-pressure turbocharger centrifugal compressor 121 pre-compresses the atmospheric air which! sucks via the air intake port of the turbocharger 80 when said compressor 121 is rotated by the low pressure turbocharger turbine 122 that includes said low pressure turbocharger 103, while the second is a high pressure turbocharger 104 the high pressure turbocharger centrifugal compressor 123 supercharges the air expelled by the low pressure turbocharger centrifugal compressor 121 to expel it to its in the regeneration-combustion channel 34 when said compressor 123 is rotated by the high-pressure turbocharger turbine 124 included in said high-pressure turbocharger 104, the output of the low-pressure turbocharger centrifugal compressor 121 being connected to the inlet of the centrifugal compressor of the high-pressure turbocharger 123 through an in-line connection channel; 1 16 compressors while the high-pressure turbocharger turbine 124 pre-relaxes a mixture gas-vapor from the combustion-regeneration channel 34 before expelled to ^the input of the low-pressure turbocharger turbine 122 which surdétend said mixture before ejecting in turn in the gas-vapor exhaust conduit of driving turbine 70.

It is drowned that this configuration with two turbochargers 2 is available in three turbochargers 2 or more, the centrifugal compressors and the turbines of each of the turbochargers 2 being connected together in a similar manner, ie in this case that the spell of each compressor is connected to ^the input of the next compressor in ascending order of absolute pressure at the exception of the last compressor whose output is connected with the combustion-regeneration of channel 34 while the output of each turbine is connected to the input of the next turbine in descending order of absolute pressure with the exception of the last turbine which is connected with the exhaust gas motor steam-gas exhaust duct 70. 4?

It will be noted that the channel of the inter-compressor aiso 116 comprises a turbocharger intercooler 98 which cools the air expelled by the low-pressure turbocharger centrifugal compressor 121 before said air is over-compressed by the centrifugal compressor of the high-pressure turbocharger. pressure 123.

Gum shown in Figure 8, the centrifugal compressor for high pressure turbocharger 123 includes a compressor bypass valve 105, which high-pressure, ^when it is opened by the management computer of furbomoteur EMS 57 may direct a portion of the air coming from the centrifugal compressor of low-pressure turbocharger 121 directly to the regeneration-combustion channel 34 without passing through the centrifugal compressor of high-pressure turbocharger 123.

FIG. 8 also shows that the high-pressure turbocharger 104 comprises a high-pressure turbine bypass valve 106 which, when opened by the EMS 57 management computer, can direct part of a vapor gas mixture from the regeneration-combustion channel 34 directly from said channel 34 to the low-pressure turbocharger turbine 122 without passing through the high-pressure turbocharger turbine 124.

FIG. 5 also illustrates that the intake duct of the turbo-fan 58 comprises an electro-pneumatic starter 108 consisting of a centrifugal compressor of an electro-pneumatic starter 110 that can be rotated by an electro-pneumatic starter motor 109 so that said compressor 1 10 compresses the atmospheric air coming from the muffler air inlet 60 to the inlet of the centrifugal turbocharger compressor 61.

In this context, the intake duct of the furbomoteur 58 comprises an electropneumatic starting flap 11 1 controlled by the management computer of the EMS turbocomputer 57, said flap 11 enabling said computer 5? forcing the atmospheric air from the turhomeer air intake port 60 to pass through the electro-pneumatic starter centrifugal compressor 1 10 before rejoining the inlet of the centrifugal turbocharger compressor 61 when said flap 11 is in a first position, or to go through a channel 1.20 prior to joining said inlet when said flap 1 1 1 is in a second position.

Still in FIG. 8, it can be seen that the exhaust line 54 comprises an exhaust heat / air heat exchanger 100 in which water circulates also in a heating radiator 83 that heats a solid, liquid or gaseous environment. said exchanger 100 being connected to said radiator 83 by heating radiator conduits 128 while said water is forced to flow in said exchanger 100, said radiator 83 and said conduits 128 by an exhaust heat recovery water pump 102 the gas-vapor mixture ejected pa turfeina the turbocharger 62 and / ου the driving expansion turbine 3 warming said water inside MH exchanger 100 before said mixture comes out through the outlet ^exhaust line 55 while said water is cooled inside the heating radiator 83 by said environment

In the latter context, the ^exhaust line 54 has an exhaust heat recovery part 101 controlled by the management computer of turhomoteur EMS 57, said shutter 101 allowing said computer 5? to force the gas-vapor mixture exhausted from the turbocharger turbine 62 and / or the gas turbine engine défente 3 to pass through ^the air / exhaust heat recovery water 100 before re anoint the output line exhaust 55 when said flap 101 is in a first position, or to pass through a bypass channel of the heat exchanger exhaust heat recovery 127 before joining said outlet 55 when said flap 101 is in a second position.

If the turbojet 1 according to [Invention is mounted on a motor vehicle 56, the air exchanger / countercurrent regeneration mixture 30 is arranged in a deformable structure constituting a shock absorber. i mmM i i MMBmi.

From the foregoing description, it will be understood - with reference to FIGS. 1 to 1 1 - the operation of the low-pressure internal combustion and / or external water vaporization and / or regeneration turbo-engine 1 according to the present invention which according to a particular embodiment, is the following: In relation with FIG. 8, ie the turbine engine 1 according to the invention being mounted on a motor vehicle 56 (FIGS. 2 and 3) so as to ensure the propulsion of the vehicle while said turbine engine 1 is at a standstill, the engine of FIG. management of the turbine engine EMS 57 orients the electropneumafiqoe starting shutter 111 to put the inlet duct of the turbine engine 58 in relation with the turbine engine air intake port 80 via the centrifugal compressor of the electropneumatic starter 110 and not via electropneumatic starter bypass channel 120.

Then, the management computer of the turbine engine EMS 5? the electrical power supply of the electric motor of the electro-magnetic actuator 109 is controlled which rotates the electromagnetic energy starter compressor 10, said current being supplied by the electrochemical accumulator 10.

Thus driven, the centrifugal compressor of the eleetropneumetique starter 110 draws atmospheric air at ambient temperature respectively via the turbine engine air intake port 60 and the turbine engine intake air filter 59, and then compresses said air in ie intake duct of the turbine engine 58. Said air then passes through the low-pressure turbocharger centrifugal compressor 121, through the turbocharger intercooler 96, then reaches the high-pressure turbocharger centrifugal compressor 123 which the high-pressure turbocharger comprises. pressure 104 while the high-pressure compressor bypass valve 105 is kept closed by the engine management computer EMS 57. Then, said air goes up in the air exchanger / regeneration countercurrent mixture 30 via the Internal conduit countercurrent regeneration exchanger 31 and then opens into the regeneration-combustion channel 34 p uis in the continuous combustion chamber 35 that includes said channel 34.

The engine management computer EMS 57 then orders the injection of fuel into the continuous combustion chamber 35 by the continuous combustion fuel injector 38, said fuel coming from the fuel tank 71 and being conveyed to said injector 38 by the fuel pump 72. Simultaneously, said computer 57 orders the formation of one or several spools (s) between the electrodes of the spark plug 63 by applying a high voltage current to the terminals of said spark plug 63, Lesdi.es Sparks ignite the air / fuel mixture formed in the continuous combustion chamber 35, while that the heat resulting from this inflammation of said mixture causes the increase of the pressure of the gases contained in said chamber 35,

The high pressure turbocharger turbine 124 of the high pressure turbocharger 104 and the low pressure turbocharger turbocharger 122 of the low pressure turbocharger 103 as shown in FIG. 8 then begin to relax the hot pressurized gases exiting the combustion chamber. Continuously 35, Accordingly, said turbines 124 and 122 respectively drive in rotation the centrifugal compressor of high-pressure turbocharger 123 of said turbocharger 104 and the centrifugal compressor of low-pressure turbocharger 121 of said turbocharger 103, the high turbine bypass valve. -pressure 108 and the bypass valve of high-pressure compressor 105 being kept closed by the management computer of the turbine engine EMS 57. The work produced by said turbines 124 and 122 thus gradually increases the mass flow rate of fresh air admitted air in the continuous combustion chamber 35 and this, until the pressure r in said chamber 35 has reached a value sufficient for the management computer of the turbine engine Efv S 57 can stop supplying electrical power to the electric motor electric starter 1G9 _S and can orient the electropneumatic starting flap 11 1 so that putting the intake duct of the turbine engine 58 directly in relation with the turbine engine air intake port 60 via the eontournemen channel of the electro-pneumatic starter 120 and not via the centrifugal compressor of the éeetropneumaiique starter 110.

It can be seen in figs 1, 7 and 8 that the pollutant post-treatment catalyst 53 is placed in the regeneration-combustion channel 34, immediately after the continuous combustion chamber 35. As such, said catalyst 53 rapidly reaches the the temperature which is necessary for it to complete the combustion of the fuel, the latter then becoming almost complete, the combustion temperature operated inside the continuous combustion chamber 35 remaining lower than that required for the production. In the case of nitrogen oxides, said catalyst 53 remains a simple oxidation catalyst designed to adsorb only unbound hydrocarbons and carbon monoxide, with the exception of nitrogen oxides. Thus, the thermodynamic cycle of the turbine engine 1 according to the invention exploits all the heat energy of the fuel because the pollutant post-treatment catalyst 53 is positioned upstream of any expansion turbine. Since the combustion carried out in the continuous combustion chamber takes place at a sufficient temperature, this produces only a small amount of soot so that it is not necessary to provide a particulate filter on the exhaust line 54 of the turbine engine 1 As said combustion is continuous, the turbine engine 1 can consume virtually any gaseous liquid fuel whatever the sensitivity to self-ignition and propensity to rattle said fuel.

As previously discussed, the high pressure turbocharger turbocharger 124 and the low pressure turbocharger turbines 122 have begun to relax the hot pressurized gases exiting the continuous combustion chamber 35 via the pollutant aftertreatment catalyst 53. being produced in sufficient quantity, the turbine engine management computer EIV1S 57 orders the opening of the expansion turbine inlet valve 4 positioned at ^the entrance to the smaller driving expansion turbine 3 that comprises the group 126 shown muitMurblnes in Figures 8, 9 and 10. Said turbine 3 immediately starts rotating and produces mechanical work that it communicates to the multi-turbine gear output power output shaft 1 18 as shown in Figures 8,. 9, 10 and 11 successively via the drive turbine shaft 67, the turbine drive gear 1 15, the turbine gear ring 114, and the gear ring gear 1 17 with which said gear cooperates turbine 3, said shaft 118 being mechanically connected to the wheels of the motor vehicle 56 by means of a continuously variable gearbox, not shown, via the power output e-cycloidal train 125 illustrated in FIGS. 9 and 10,

The continuously variable gearbox thus Indirectly transmits the work produced by said smaller expansion drive turbine 3 to the wheels of the motor vehicle 56 (FIGS. 2 and 3), so as to propel the latter. At the same time, we note that the ES 5? has opened the turbo-generator bypass valve 107 (FIG. 8) in order to supply hot gas to the turbogenerator turbine 98 that comprises the turbine generator 97, said hot gases having previously been produced in the continuous combustion chamber 35, This has resulted in turning said turbine 98 into rotation. The latter being integral with the generator of turbine generator 99, said generator has also rotated and produced electricity to recharge the electroehimlque accumulator 10, in addition to power accessories and safety equipment, comfort , driving and management of the motor vehicle 56.

Having been relaxed by the smallest expansion turbine 3 of the multi-turbine group 126, the hot gases produced by the combustion of the fuel operated in the continuous combustion chamber 35 have lost some of their heat and are expelled by said turbine 3. Said gases are then conveyed by the exhaust gas turbine exhaust gas exhaust pipe 70 from said turbine 3 to the regeneration air / mixture regeneration exchanger 30 in which lilies penetrate and pass into the the space between the outer casing of counter-current regeneration exchanger 33 and the internal ducts of countercurrent regeneration exchanger 31 envelops said frame 33, the latter constituting said exchanger 30 with said ducts 31 (Figure 8). In addition, said gases pass between said ducts 31 themselves so as to better give them their heat.

Simultaneously, the centrifugal compressor of high-pressure turbocharger 123 and the centrifugal compressor of low-pressure turbocharger 121 continue to circulate compressed atmospheric air ^inside the ducts regeneration exchanger internals against the current 31, the the flow direction of the air flow in said ducts 31 being inverse to that of the circulation of said hot gases in said casing 33 and between said ducts 31. As a result, the atmospheric air expelled by said compressors 123 and 121 gradually heats up in contact with said conduits 31 in which II circulates, said hot gases progressively yielding a large part of their heat by circulating in the opposite direction between the outer casing of counter-current regeneration exchanger 33 and said internal ducts 31, and between these, this heat transfer constituting a thermal regeneration which very significantly improves; the efficiency of the lurbomotor 1 according to the invention.

Note that according to this exemplary embodiment, the regeneration counterflow air / mixture exchanger 30 comprises several counter-current regeneration exchanger internal conduits 31 which commonly offer a contact surface largo on the one hand, ^atmospheric air expelled by the centrifugal compressor for high pressure turbocharger 123 and the centrifugal compressor of low-pressure turbocharger 121 and with the other hand, the hot gases from the combustion chamber 35. Said continuous large contact surface enables better warming said air and m me cooling said gas during their journey inside the exchanger air / mixture against counter current regeneration 30, to the point that when said air reaches the continuous combustion chamber 35 its temperature is approximately equivalent to that of said gases when they have just been expelled by the smallest expansion turbine 3 that includes whereas, when said gases emerge from the air / mixture regeneration counter-current exchanger 30, their temperature is approximately equivalent to that of atmospheric air immediately after this latter has been expelled by the centrifugal compressor of high-pressure turbocharger 123.

One can also note that, mounted on a motor vehicle 58, the iurbomoteur 1 according llnvention has ^the advantage relative to a reciprocating Internal Combustion Engine of not requiring do cooling radiators front éudlï vehicle 58, which improves the coefficient of penetration into the air of the latter, its engine compartment can be completely closed. In addition, all the elements constituting said turhomoeureur 1 are insulated. Thus, most of the heat released into the combustion chamber continues through combustion of the fuel and is not converted to work by the detent turbines 3, the low-pressure turbocharger turbine 122 or the high pressure turbocharger turbine. 124 is released into the atmosphere via the exhaust line 55 located at the rear of said vehicle 55. This release of heat creates a slight thrust that tends to significantly improve the coefficient of penetration into the air of said vehicle 58. It should be noted that in addition to the regeneration counter-current air / mixture exchanger 30 which significantly increases the efficiency of the turbine engine 1 according to the invention, the low-pressure turbocharger 103, the high-pressure turbocharger 104 and the turbocharger intermediate cooler 98 commonly form a compression system bbétagè intercooled which also helps to maximize ^energy efficiency duélt turbine engine 1. According to this configuration, the atmospheric air is cooled in the intermediate refroldisseur turbocharger 98 after being pre-compressed by means of centrifugal compressor of low pressure turbocharger 121 and is then compressed by the centrifugal compressor of high-pressure turbocharger 123. This gives the compression system thus constituted a very high isenfropic efficiency. In this context, it should be noted that the heat dissipated by the turbocharger intermediate cooler 98 is not a clear pearl in that it is compensated by an increase in the heat fraction recovered by the counter-current air / mixture heat exchanger. regeneration 30. therefore, the total energy balance of the system that constitutes the turbine 1 according to the invention is greatly improved by the bf-stage compression system with intermediate cooling and this, so all the ^more important that said gas turbine engine is used at high power.

It should also be noted that, depending on the power that the turbine engine 1 according to the invention must deliver, the engine management computer of the turbine engine EMS 5? can open or open the high-pressure turbine bypass valve 106 and / or the high-pressure compressor bypass valve 105 so as to modify the compression ratio of the low-pressure turbocharger centrifugal compressor 121 relative to to that of the centrifugal compressor of high-pressure turbocharger 123. This additional adjustment also optimizes the operation of the turbine engine 1 according to the invention, so as to maximize the efficiency of the latter.

When the motor vehicle 58 shown in FIGS. 2 and 3 needs more power to move, according to the particular embodiment chosen here to illustrate the operation of the turbine engine 1 according to the invention, the smallest expansion turbine 3 that comprises the multi-turin group 126 and which was used until then can be replaced by a motor turbine defensive 3 of medium size or large (Figures 8, 9 and 10). perform this replacement, the management calculator of the turbine engine ES 5? closes the expansion turbine inlet valve 4 of the smallest expansion turbine 3 and then opens the corresponding expansion turbine inlet valve 4 to the medium or large expansion turbine 3 to be used; whereby the hot gases leaving the continuous combustion chamber 35 via the pollutant post-treatment catalyst 53 are expanded through said medium or large turbine 3, the latter then providing the propulsion of the vehicle, in particular by communicating the work It is produced mechanically from the power output shaft of the multi-turbine gearbox 1 18 as shown in FIGS. 8, 10 and 11 successively via the drive turbine shaft 67, the drive pinion of FIG. turbine 115, the impeller crown 1 14, and the crown gear reducer 1 1? with which said turbine 3 cooperates.

Depending on the power required by the motor vehicle 58, several combinations of turbines) relaxation 3 are possible. Regarding the configuration with 4 expansion turbines 3 as shown in FIGS. 8, 9 and 10, it should be noted that ten combinations of expansion turbines 3 are possible to produce work on the multi-reduction power output shaft. - Turbines 1 18. An additional combination consists in having no active expansion turbine 3, in this case only the turbines of the low pressure turbocharger 103 and the high pressure turbocharger 104 relax the hot gases leaving the combustion chamber. continuous 35, possibly in addition to the turbine generator turbine 98.

It will be noted that the unused expansion motor turbines 3 have their expansion turbine inlet valve 4 kept closed by the engine management computer EMS 57 and do not rotate because the turbine turbines 3 are not rotated by the engine shaft. multi-turbine gear reducer power output 113 because their multitrane gear ring 114 is equipped with a gear ring gear 17, or with hot gases exiting the continuous combustion chamber 35 because The latter can not access said turbines 3, their expansion turbine admission valve 4 being kept closed. Thus, the turbines this relaxing 3-ncn utllisées doors do not generate frictional losses or adverse final pumping efficiency of the turbine engine 1 according to ^the invention. It should be noted that, still with the aim of maximizing the efficiency of the turbine engine 1 according to the invention, the management computer of the turbine engine ES 57 does not select the expansion turbine (s) 3 to relax the hot gases coming from the combustion chamber. continuous combustion 35 on the sole criterion of the power that must produce the turbine engine 1 to move the motor vehicle 56, Indeed, said calculator 5? also selects the turbine (s) 3 on a criterion of better performance of said turbines 3, by operating the latter (s) on its (their) operating point with the highest energy efficiency.

Thus, for the same power available on the muifi-furbine reducer power output shaft 113, several combinations of thrust ring (s) 3 are possible as well as several pressure levels and mass and volume flow rates of the gases leaving the pipe. Continuous combustion chamber 35, Thanks to the different reduction ratio for each expansion turbine 3 that their torque ring gear muitidurblnes 1 14 / turbine driver pinion 115 presents, said turbines 3 can operate simultaneously under the same pressure differential each maintaining the rotation regime corresponding to their best performance.

With the aim of optimizing the efficiency of the turbine engine 1 according to the invention, the important role of the continuously variable gearbox (not shown), whose input shaft is connected to the plcyclofdal power output train 125 (FIG. Figures S) and 10). In effect, said box makes it possible to meet the power and speed requirements of the motor vehicle 58 irrespective of the torque and the rotational speed printed at the output shaft of the melting motor gear 113 by the urine (s) } of relaxation 3, said torque and said speed being chosen by the management computer of the turbine engine EMS 57 on a criterion of better performance of the turbine engine 1 taking into account the power required.

It should also be noted that, depending on the power demanded by the motor vehicle 56 and the configuration of expansion turbines 3 resulting from said power, the engine management computer of the EMS 57 turbine engine adapts the quantity of fuel injected into the continuous combustion chamber. By means of the continuous combustion fuel injector 36, in particular by regulating the fuel flow pumped by the fuel pump 72, Note that the pressure in the continuous combustion chamber 35 depends directly on the combination of restrainer furbine (s) 3 ^{on the} one hand, and the amount of fuel injected into a continuous combustion chamber 36 on the other hand in relation to the amount of atmospheric air introduced into said chamber 35 by the low pressure turbocharger centrifugal compressor 121 and the high pressure turbocharger centrifugal compressor 123,

As seen previously, it is noted that the EsVIS 57 turbine engine management computer can act on the high-pressure compressor hy-pass valve 105 and / or the high-pressure turbine bypass valve 106 to maximize the efficiency of the engine. a two-stage compression system with intermediate cooling that is commonly constituted by the low-pressure turbocharger 103, the high-pressure turbocharger 104 and the turbocharger intermediate cooler 98

As can easily be deduced from FIG. 8, during the winter period or in cold weather, when starting the turbine engine 1 according to the invention, the engine management computer of the turbine engine ES 5? The exhaust gas expelled at the outlet of the regeneration countercurrent air / mixture exchanger 30 can be exhausted by the low pressure turbocharger turbine 122 and / or the expansion turbine (s) 3 so as to direct the gases towards Exhaust air / water heat exchanger exhaust 100 that includes the exhaust line 54 and this to warm the passenger compartment of the motor vehicle 56 by means of the heating radiator 83. For this, said calculator 57 can guide the exhaust heat recovery flap 101 so that the gases can not go directly to the exhaust line outlet 55 via the bypass channel of the exhaust heat recovery exchanger 127, but forced to pass through said air / water heat exchanger 100, Thus, said exhaust gases can transfer their heat to the water circulated in said heat exchanger 100 by the recovery water pump exhaust heat 102, said heat being then again transferred to the air of the passenger compartment of said vehicle 56 via the heating radiator 83. Once the desired temperature is reached for said passenger compartment, the management computer the EMS 57 turbine engine can maintain the said temperature by varying the amount of gas Exhaust passing through the exchanger air / exhaust heat recovery water 100 through the heat recovery component ^exhaust 101, and / or controlling the flow of the water pump recovery exhaust heat 102,

As an alternative to the operation just described, the low-pressure internal combustion turbine and / or external water vaporization and / or regeneration 1 according to the invention can be provided to operate as follows:

The turbine engine 1 according to the invention being mounted on a motor vehicle 56 (FIGS. 2 and 3) so as to ensure the propulsion of said vehicle and said turbine engine 1 being stopped the management computer of the turbine engine EMS 57 closes the valves of expansion turbine inlet 4 and simultaneously directs the start bypass air flap of the turbine engine 8 and the starter obstruction air flap of the turbine engine 9 so that the first flap 8 directs the atmospheric air from the compressor centrifugal flow of cooling-condensing air 27 to the intake duct of the turbine engine 58 via the start bypass air channel of the turbine engine 85 while at the same time preventing access to the cooling air exhaust port- condensing 23, while the second flap 9 prevents said air from going up towards the turbine engine air intake opening 60, forcing said air to go towards the turbocharger compressor 81.

Then, the turbine engine management computer EMS 57 orders the electric power supply of the cooling-condensing air compressor electric motor 28 which rotates the centrifugal cooling-condensation air compressor 27 while said current is supplied by the electrochemical accumulator 10 and / or the electrostatic accumulator 69.

Thus driven, said compressor 2.7 as shown in FIGS. 1, 2, 3 and 7 draws atmospheric air at room temperature respectively through the cooling-condensing air intake port 22, the intake duct of FIG. cooling-regeneration air 64 and the cooling-condensing air insufflation air filter 29 and then compressing said air into the countercurrent condenser-condenser external casing 19 via the insufflation duct 24 and the mouth of Air insufflation of cooling-regeneration 20 so that said air rises to {Interior udit casing 19 to come out through the air-cooling-condensing air blower 21 and that it arrives until the turbocharger compressor 61 screws said blowing mouth 21 the blowing duct 25, the turbo-motor starting duct 65 and the turbomaker inlet duct 58. Next, said air passes through the centrifugal turbocharger compressor 81 so as to open into the regeneration-air channel. combustion 34 and then in the continuous combustion chamber 35 that comprises said channel 34, after having passed through the air / mixture regeneration counter-current exchanger 30 that also comprises said channel 34 by the lower internal regeneration exchanger conduit against the current 31 that includes said ecgger 30.

The turbocharger management computer E1V1S 57 then orders the injection of fuel into the continuous combustion chamber 35 by the continuous combustion fuel injector 36, said fuel coming from the fuel tank 71 and being conveyed to the injector injector 36 by the fuel pump. fuel 72, while said computer 57 also orders the formation of one or more spark (s) between the electrodes of the spark plug 83 by applying a high voltage current to the terminals of said spark plug 63. The mixture The air / fuel formed in the continuous combustion chamber 35 is thus ignited by said one or more electrons while the heat emission which results from said firing causes the pressure of the gases contained in said gas to increase. room 35.

The turbocharger turbine 62 shown in FIGS. 1 and 7 then starts to defend the hot and pressurized gases exiting the continuous combustion chamber 35 so as to drive in rotation the turbocharger centrifugal compressor 81 which in turn increases the mass flow rate. atmospheric fresh air admitted into said chamber 35 and this, until the pressure in said chamber 35 has reached a sufficient value ..

It will be noted in FIGS. 1, 7 and 8 that the pollutant post-treatment catalyst 53 is placed immediately after the continuous combustion chamber 35. As such, said catalyst 53 quickly finds its operating temperature so as to complete in a short time. burns the fuel, this latter becoming substantially complete, the temperature of combustion carried out within the continuous combustion chamber 35 remaining below the nitrogen oxide production threshold, said catalyseu 53 is an ^oxidation catalyst designed to do For example, unburnt hydrocarbons and carbon monoxide, excluding nitrogen oxides. Thus, the thermodynamic cycle of the gas turbine engine 1 according to ^the invention t ^'has Intervening the full heat energy of the fuel for said catalyst 53 is positioned prior to operates the expansion of the hot gases from the combustion. Said combustion being continuous and operated at a sufficient temperature, it is noted that said combustion produces little soot so that it is not necessary to provide a particulate filter on the exhaust line 54 of the turbine engine 1, the operation of this Lastly, they are also suitable for practically any liquid or gaseous fuel whatever the sensitivity to auto-ignition and the propensity to rattle the fuel.

As previously discussed, the turbocharger turbine 62 has begun to relax the pressurized hot gases exiting the continuous combustion chamber 35 via the pollutant aftertreatment catalyst 53. As the gases are produced in sufficient quantity, the EMS calculator 57 may order the opening of the expansion turbine inlet valve 4 of the smaller driving expansion turbine 3 so that the latter produces mechanical work on ^the power turbine shaft of trigger 87, said shaft being connected mechanically to the electric turbine generator 1 1 via the mechanical generator transmission 6 formed according to this example of an epicyclic motor-generator drive train 7.

Thus rotated, the electric generator turbine 11 produces ^the lectricity which is either directly used louse power the electric motor-generator propulsion refresh 68 of soda that it propels the motor vehicle 56 (Figures 2 and 3} which it is connected, either stored in the electroclimate accumulator 10 and / or the electrostatic accumulator 69, or both at the same time It should be noted that the electricity produced by the electric turbine generator 1 1 can also be used to power the motor condenser cooling compressor 28, as well as accessories and equipment for safety, comfort, driving and management of the motor vehicle 56. 58

It is noted that the electricity stored in ^the battery 10 is éleetroehlrnlque prèférentieliement used to provide operation in all-electric mode of the motor vehicle 56 during its movement over distances of a few meters - for example, when traffic congestion - while electrostatic accumulator 89 is used during braking préférentiellernent dudlt vehicle 56 for storing ^electricity generated by the electric motor-generator-drive regeneration 68 which operates in generator mode when said brake so that recovers the largest possible share the kinetic energy of said vehicle 58, said electricity being then reused to accelerate said vehicle 66 when it returns to the desired driving speed. It is also noted that the smoothing of the need for electricity consumption or storage of the motor vehicle 56 is operated prèférentieliement via electrochemical accumulator 10 will act low power over long periods while said smoothing ^s' operates prèférentieliement via electrostatic accumulator 69 are high powers over short periods of time,

Since the turbine engine 1 is sufficiently hot, the turbofan management computer EMS 5? simultaneously orients the start bypass air flap of the turbine engine 8 and the starter obstruction air flap of the turbine engine 9 so that the first flap 8 directs the atmospheric air from the centrifugal air compressor -condensation 27 to the exhaust air-cooling-condensation mouth 23 while denying access to the intake duct of the turbine engine 58 via the start bypass air channel of the turbine engine 65, while the second shutter 9 connects the turbine engine intake port 80 with the turbocharger centrifugal compressor 61 via the turbine engine intake air filter 59 while closing the bypass air channel 65, so as to allow audil compressor 61 aspirate atmospheric air via said mouth 60.

After having been relaxed by the expansion turbine 3, the hot gases produced by the combustion of the fuel operated in the continuous combustion chamber 35 have lost some of their heat and are expelled by said turbine 3 via the exhaust gas duct The exhaust gas turbine 70. The gases then enter the heat exchanger at the same time. countercurrent regeneration 30 and more precisely; are introduced into the space between the countercurrent regeneration exchanger external card 33 and the internal conduit <countercurrent regeneration exchanger 31 enveloping said casing 33, said casing 33 and said duct 31 constituting mainly said exchanger 30 (Figure 4).

At the same time, the centrifugal compressor of turbocharger 61 continues to circulate atmospheric air inside the Internal conduit to exchange counter-current regeneration 31, the direction of circulation of said air in said conduit 31 being opposite to that the circulation of said hot gases in the casing 33. As a result, the atmospheric air expelled by the centrifugal compressor turbocharger 81 gradually warms in contact with the inner duct of the countercurrent regeneration exchanger 31 in which it circulates, lesdlts hot gases progressively yielding a large part of their heat by circulating in the opposite direction between the external counter-current regeneration exchanger 33 and said Internal duct 31, this heat transfer constituting a thermal regeneration which improves the efficiency of the turbine engine 1 according to the invention.

It will be noted that according to this exemplary embodiment, the regenerated counter-current regeneration exchanger 30 comprises a number of internal conduits c counter-current regeneration exchanger 31 which have a daisy section 32 (FIG. 4) which offers a large contact area simultaneously with the atmospheric air expelled by the centrifugal compressor of turbocharger 81 and with the hot gases from the continuous combustion chamber 35 so as to better heat said air and to better cool said gases, to the point that when said air reaches the chamber continuous combustion 35 its temperature is approximately equivalent to that of said gases when they have just been expelled by the drive turbine 3 relaxation while when dalt gas supply air exchanger / regenerative countercurrent mixture 30, their temperature is approximately equivalent to that of atmospheric air immediately after the latter has been expelled by the centrifugal compressor of turbocharger 61,

To optimize the efficiency of the turbine engine 1 according to the invention and to make it possible to operate over a wide range of power without exceeding the limit of heat resistance of its components, the ES 57 turbocharger management computer can trigger the circulation of liquid water 45 in the condenser-regenerator water circuit 89 that comprises the counter-current steam condenser-regenerator 87 illustrated in FIG. 7. For this, said calculator 57 starts the condensate pump 48 so that the latter conveys the liquid water 45 to the condenser-countercurrent regenerator 87 via the condensate recirculation duct 47, said water 45 from the recovery tank condensais 43 which can be seen in detail in Figure 6.

By passing through the counter-current vapor condenser-regenerator 87, the liquid water 45 gradually rises in temperature because the hot gases produced in the combustion chamber continue and then expelled by the turbocharger turbine 62 and / or the turbine engine. 3, after having been relaxed by the turbines 62, 3, flow simultaneously and without the reverse in the condenser-regenerator gas-vapor mixing circuit 88 that includes said condenser-regenerator 87 said gases yielding their heat to said water 45 of sode to vaporizing the latter before it comes out of said condenser-regenerator 87 via the postcombustion steam supply duct 94, the steam thus produced then emerging via said duct 94 into the regeneration-combustion channel 34 at the outlet of the catalyst post-treatment of pollutants 53 (Figure 7).

Said produced vapor then mixes with the hot gases from the continuous combustion chamber 36 via said catalyst 53. As a result, the steam is superheated and in doing so, said steam cools said hot gases so that the temperature of said gases becomes compatible with the thermomechanical resistance limit, in particular of the turbocharger turbine 82, of the expansion turbine 3, of the gas-steam admitting turbine engine 66 and the expansion turbine intake valve 4,

Whether as a result of the combustion carried out in the continuous combustion chamber 35 and the vaporization of the liquid water 45 in the condenser-regenerator water circuit 89, or following the overheating of the resulting vapor in the cooling channel. regeneration-combustion 34, a large volume-flow of gas-vapor mixture is produced which is signlflcafivement greater than the flow rate of atmospheric air admitted by the compressor As a result of the turbocharger centrifugal flow rate 61 minus the volume flow rate of gas-vapor mixture passing through the turbocharger turbine 62, this differential volume flow rate of pressurized gas-vapor mixture can be expanded at relatively low temperature by the expansion turbine 3 _S which further increases the amount of work that the latter can produce, without increasing the amount of fuel injected into the combustion chamber 35 continues, while protecting said turbine 3 drive overtemperature,

It is noted that after being expanded in the expansion turbine 3 the gas-vapor mixture retains a residual heat which is largely recycled to the regeneration countercurrent air / mixture exchanger 30 for heating the expelled atmospheric air. centrifugal compressor turbocharger 81 said mixture yielding a large part of said heat to said air so as to improve the efficiency of the turbojet 1 according to the invention.

At the exit of the regeneration countercurrent air / mixture exchanger 30, the gas-vapor mixture is introduced inside the external condenser-regenerator casing 91 (FIG. 7) of the countercurrent steam regeneration condenser 87 Passing through said condenser-regenerator 87 via said housing 91, said mixture transfers a large part of its heat to the liquid water 45 circulating in the opposite direction in the internal condenser-regenerator duct 90, in particular, the heat energy released. By condensation of the water vapor contained in said mixture, it is possible to supply a large part of the heat required for said water 45 to vaporize, said mixture thus leaving the condenser-regenerator of countercurrent vapor 87 at a temperature advantageously scaled down.

As can easily be deduced from FIG. 7, at the outlet of the countercurrent steam regeneration condenser 37, the gas-vapor mixture is introduced into the countercurrent air / gas exhaust cooler-condenser 18 and more. particularly, inside the inner duct of condenser cooler-condenser 17 whose schematic section is illustrated in Figure 5. Simultaneously, the centrifugal compressor cooling-condensation air 27 continues to circulate atmospheric air in the outer casing of countercurrent condenser-condenser 19 and more precisely between said rack 1 and said duct 17 when said casing surrounds, the direction of circulation of said air in said casing 19 being opposite to that of the circulation of the gas-vapor mixture in said duct 17, Thus, the gas-vapor mixture progressively yields a large part of its residual heat. air audit, so that when said mixture leaves the exhaust cooler-condenser, air / gas against the current 16, its temperature is substantially equal to that of the ambient air. According to the same principle, the atmospheric air leaving said cooler-condenser 16 via the cooling-condensing air blowing outlet 21 has a temperature substantially equal to that of said mixture just before entering said cooler-condenser 16.

Thus, the gas-vapor mixture initially expelled from the gas-steam exhaust gas engine of expansion turbine 70 leaves the chiller-condenser exhaust air / gas against the current 16 at a temperature close to that of atmospheric air ambient. The significant drop in temperature experienced by said mixture between the moment it entered the countercurrent internal cooler-condenser conduit 17 and the moment it exited said conduit 17 implies that a major portion of the steam of residual water that still contains said mixture after passing through the steam-regenerator condenser-current against 87 condenses on the inner walls âuàïi inner conduit 17, ^the liquid water 45 which résuite that condensation runs down said inner conduit 1 and then joins the internal condenser separator-recuperator duct 41 (FIG. 6) that comprises the condensate separator-recuperator 40 placed on the same exhaust line 54 as the said internal duct 17, the said liquid water 45 being assisted in this by the continuous stream of gas-vapor mixture expelled by the turbomoieur 1 according to the invention.

The liquid water 45 thus formed then flows by gravity via the draining orifices of the condensates 42 (particularly visible in FIG. 6) to the condensate recovery tank 43 for temporary storage, aided by iron straw. or structure lah nnthiguo 44 that includes the internal duct separator-recuperator condensate 41 said straw 44 retaining or condensing water still remaining in suspension in the form of droplets and / or steam in the gas-vapor mixture expelled by the turbojet 1, so that said water is not carried by said mixture to the exit of the exhaust line 55 but stored in the tank of recovery of the condensates 43. It is noted that besides retaining the residual liquid water droplets contained in the gas-vapor mixture, the iron straw or lahyrinthic structure 44 also largely captures any residual soot particles that can convey said mixture, by agglutinating said particles around the wet metal fibers or surfaces of the iron straw or labyrinth structure 44, said soot being then washed away by the liquid water which flows by gravity and returns to the condensate recovery tank 43, thereafter Said particles are ~ according to this particular embodiment of the turbine engine 1 according to the invention - retained by the condenser filter 49 so that it can be eliminated during the replacement of the filter 49 operated during the maintenance of said turbine engine 1

When the motor vehicle 58 (FIGS. 2 and 3) needs more power to move, according to the particular embodiment chosen here to illustrate the operation of the turbine engine 1 according to the invention, the smallest expansion turbine 3 previously used by the management computer of the turbine engine EMS 57 for driving the turbine generator 11 can be replaced by said computer 5? by means of a medium-sized expansion turbine 3 or a large expansion turbine 3 (FIGS. 1 and 2), for which purpose said calculator 57 can close the inlet valve 4 of the driving turbine 3 to be used, then open the valve 4 corresponding to the turbine 3 to be used, so that the pressurized gas-steam mixture leaving the water vaporization chamber 37 is expanded through said turbine 3 It should be noted that the unused driving turbines 3 are then freely rotatable around the regenerative drive turbine art 6 on which they are mounted, without being driven by the said shaft 67 because of the wheel-drive connection. free of expansion turbine 5 which connects said turbines 3 to said shaft 67,

Since the power of the expansion drive turbine 3 is greater, the engine management computer of the EMS turbine 57 orders the injection of more fuel into the continuous combustion chamber 35 by means of a continuous combustion fuel injector 36, in particular by adapting it accordingly. the flow of fuel pumped by the fuel pump 72. In parallel, said computer 57 can also increase if necessary the mass flow rate of atmospheric air introduced by the centrifugal compressor turbocharger 81 in the continuous combustion chamber 35 by changing the power of the turbocharger turbine 62 via its vanes with variable geometry 76, In addition, said calculator 57 little! also increase the liquid water flow rate 45 Introduced into the countercurrent steam regeneration condenser 87 for vaporization, by acting on the flow rate of the condensate pump 46.

It is drowning that according to a particular mode of use of the turbine engine 1 according to the invention, several driving turbines 3 can be used simultaneously to add their power, this being achieved by opening simultaneously the expansion turbine inlet valves 4 corresponding to said turbines 3 (Figures 1 and 7).

As can be deduced from FIGS. 1 and 7, in the starting phase of the turbine engine 1 according to the invention, almost all the energy released by the combustion carried out in the continuous combustion chamber 35 serves to heat the turbine engine 1, the heat recovered by the air / gas exhaust cooler-condenser. against the current 16 can be reintroduced at the inlet of the centrifugal compressor turbocharger 61 by means of the flow of air bypass start of the turbine engine 8 and the shutter air flap start of the turbine engine 9, so that said heat is not lost in the atmosphere. Combined with the low thermal inertia dudlt turbine engine 1, this allows the rapid rise in temperature of the latter.

With the turbine engine 1 being hot and the starting bypass air flaps of the turbine engine S and starting obstruction of the turbine engine 9 no longer in the starting position but in the operating position of the turbine engine 1 the residual heat of the air expelled from the exhaust air-cooling-condensation outlet 23 is used to warm the passenger compartment of the motor vehicle 58 via the air / water heat exchanger waste heat exchanger 81 shown in Figures 1, 2, 3 and? This is achieved by forcing the atmospheric air exiting the blowing duct 25 to pass into said scrubber 81 by means of the residual heat recovery flap 80 before releasing said air into the atmosphere via the air exhaust mouth In this case, said air gives up all or part of its heat to the carrier fluid circulating in said écangeur 81, said fluid thereafter for heating the passenger compartment of the vehicle 56 by means of the heating radiator 83 shown in FIGS. 2 and 3,

Note that in Figure 7, there is shown the condenser-regenerator countercurrent steam 87 whose operation has just been described while in Figure 1, the latter is replaced by a preheating mixture / water heat exchanger. liquid water 79 for heating the liquid water 45 to a temperature just below its vaporization temperature before its injection in liquid form in a water vaporization chamber 37 by a post-combustion water injector 38,

Whether the configuration adopted is that illustrated in FIG. 1 or that illustrated in FIG. 7, it will be noted that the adjustment of the quantity of heat transferred to the liquid water 45 by the gas-vapor mixture can be regulated by the turbine engine management calculator. EMS 57 by means of the preheating part and / or vaporization ^of liquid water 78 said flap for deriving all or part of said mixture exiting féehangeur air / mixture against the regenerative current 30 via the outlet conduit regeneration exchanger 84 either to the liquid water preheating mixture / water exchanger 79 or the countercurrent vapor regeneration condenser 87 according to the selected configuration, said mixture then continuing its path via the air / gas exhaust cooler / condenser against the current 18 and the separator-recuperator of the condensates 40 to the exit of the exhaust line 55, thirst directly to said cooler-condenser 16 without passing through said exchanger 79 or condenser-regenerator 87.

In order to optimize the efficiency of the turbine engine 1 as a function of the power demanded by the motor vehicle 58, the engine management computer of the EMS 57 turbine engine can thus act on several parameters among which the turbine engine (s) releasing the vehicle (s) 3 where the one or more turbines) is selected via its expansion turbine inlet valve (4), the mass flow rate and the atmospheric air pressure introduced by the centrifugal turbocharger compressor 61 into the continuous combustion chamber 35 said flow being in particular adjusted by the variable geometry vanes 76 that includes the turbocharger turbine 62, the mass flow rate of fuel injected into the continuous combustion chamber 35 by the continuous combustion fuel jet engine 36, the flow rate d liquid water 45 introduced into the internal condenser-regenerator duct 90, which flow rate can be regulated by the condensate pump 46, the amount of heat transferred to the said water 45 in the counter-current vapor condenser-regenerator 87, the said quantity being adjustable by means of the preheating flap and / or vaporization of liquid water 78, the air flow introduced into the counter-current cooling-condenser outer casing 19 by the centrifugal cooling-condensation air compressor 27, said flow being regulated by said calculator 57 by modulating the power of the electrical supply of the motor of compressor condensation-cooling air 28, or the storage or the electricity storage at ^the storage cell 10 and / or electrostatic accumulator 69 notably via an electrical and / or electronic power unit 82,

It should also be noted that, in order to optimize the efficiency of the turbine engine 1 according to the invention, the engine management computer of the EMS turbine 57 can adjust the quantity of atmospheric air at ambient temperature coming from the turbine engine air intake port 60 introduced in the intake duct of the turbine engine 58, with respect to the amount of atmospheric air at higher temperature coming from the cooling-condensing air blower 21 introduced into said duct 58, the quantities being regulated by said calculator 57 by means of the starter bypass air flap of the turbine engine 8 and the starter air shutter of the turbine engine 9, it is notably noted that by thus adjusting the temperature of the air admitted by the centrifugal compressor turbocharger 81 _; the engine management computer EMS 57 can adjust the mass of air expelled by the centrifugal compressor turbocharger 81 in the regeneration-combustion channel 34 for the same volume flow rate of air entering said compressor 81,

Given the silent nature of the turbine engine 1 according to the invention with respect to an internal combustion engine alternative combustion, it is also possible - without damage to the comfort of the passengers of the motor vehicle 58 - to operate said turbine engine 1 by alternating sequences of high power operation of a few seconds with others at very low power stookant-destocking at the same frequency of energy in the electrostatic accumulator 89 so as to operate the various driving turbines 3 and / or the centrifugal compressor of turbocharger 61 at the closest to their best performance and reduce the amount of fuel processed by the turbine 1 low power, where it is potentially less energy efficient,

It should also be noted that the turbine engine 1 according to the invention may comprise several turbochargers 2 and that, as such, the management computer of the turbine engine ES 57 can optimize the choice of turbocharger (s) 2 parallel to that of the turbine engine (s) ( s) relaxation (s) 3 on a criterion of efficiency and / or power.

If necessary, the management computer of the turbine engine EMS 57 can also control the mechanical transmission of generator 6 if the latter is variable so as to optimize the rotational speed of the electric turbine generator 11 on a criterion of better efficiency of said generator 11, or it may control the mechanical transmission of the engine-generator 74 if the latter is variable so as to optimize the rotational speed of the electric-propulsion-regeneration motor-generator 68 on a criterion of better efficiency of said engine-generator 68,

In general, the good management of the electrical functions directly or indirectly connected to the turbine engine 1 according to the invention can benefit from the know-how and general knowledge of those skilled in the art relating to the energy optimization of the electrical systems of average and high power, it must also be understood that the above description n ^'was given as an example and which in no way limits the scope of the invention which is not exceeded by replacing the details of described by any other equivalent.

Claims

Ρδ

Low-pressure internal combustion and / or external water vaporization and / or regeneration turbine engine (1), characterized in that it comprises:

At least one turbocharger (2) cooperating with at least one regeneration-combustion channel (34) connects directly or indirectly the outlet of a centrifugal turbocharger compressor (61) that comprises said turbocharger (2) with the inlet of a turbocharger turbine (62) comprising said turbocharger (2), said compressor (61) expelling atmospheric air into said channel (34) after sucking it through a turbine engine air intake port (60) and via an intake duct of the turbine engine (58), while said channel (34) comprises at least one continuous combustion chamber (35) internal or external to said channel (34) in which fuel can be burned after being injected by at least one continuous combustion fuel injector (36);

at least one expansion drive turbine (3) mounted on an expansion turbine drive shaft (67), the inlet of said turbine (3) being connected directly or indirectly to the regeneration-combustion channel (34) by at least a gas-steam induction motor driving duct (66);

at least one regenerative counter-current air / mixture exchanger (36) forming part of the regeneration-combustion channel (34) and in which circulates ^{on the} one hand, a gas-vapor mixture expelled by the turbocharger turbine (62); ) and / or the expansion turbine (3) the output of said turbines being connected to said exchanger (30) by a gas-steam exhaust gas engine (70) and on the other hand, the ai expelled by the centrifugal turbocharger compressor (61) said mixture heats said air inside dodit exchanger (30) before exiting through an exhaust outlet (55) via an ^exhaust line (54):

"At least one engine management calculator EUS (57).

2. Low pressure internal combustion engine and / or external water vaporization and / or regeneration (1) characterized in that it comprises:

At least one turbocharger (2) cooperating with at least one regeneration-combustion nozzle (34) which directly or indirectly connects the outlet of a centrifugal turbocharger compressor (81) which comprises said turbocharger (2) with the inlet of a turbocharger turbine (82) comprising said turbocharger (2), said compressor (61) expelling atmospheric air in said channel (34) after sucking through a turbine engine air inlet (80) and via an intake duct of the turbine engine (58), while said channel (34) comprises at least one continuous combustion chamber (35) Internal or external to said channel (34) in which a fuel can be burned after being injected by at least one continuous combustion fuel injector (36);

At least one expansion drive turbine (3) mounted on an expansion turbine drive shaft (67), the inlet of said turbine (3) being connected directly or indirectly to the regeneration-combustion channel (34) by at least a gas-steam induction motor driving duct (86);

at least one countercurrent steam regeneration condenser (87) in which a gas-vapor mixture expelled by the turbocharger turbine (82) and / or the expansion turbine (3) flows in a condenser-regenerator gas-vapor mixing circuit (88) and in which a liquid water (45) flows in a condenser-regenerator water circuit (89) connected to the regeneration-combustion channel ( 34) _? warming said mixture said water (45) within éuéîi condenser-regenerator (87) before exiting through an exhaust outlet (55) via an ^exhaust line (54) while the inlet of said condenser- regenerator (87) is connected to a gas-steam exhaust pipe of the expansion turbine (70) in which circulates the gas-vapor mixture expelled by the turbocharger turbine (62) and / or the expansion turbine (3). );

"At least one engine management calculator EMS (57), 88

3. The turbomotor according to any one of claims 1 and 2, characterized in that the regeneration-combustion channel (34) comprises at least one water vaporization chamber (37) internal to said channel (34) in which a liquid water (45) can be injected by a post-combustion water injector (38) so as to produce a gas-vapor mixture.

4. A motorcycle according to claim 1, characterized in that the outlet of the regeneration counter-current exchanger (30) comprises a regeneration exchanger outlet (84) in which the gas-vapor mixture expelled by the turbocharger turbine (82) and / or the expansion drive turbine (3), said duct (84) connecting said exchanger (30) with the inlet of a countercurrent steam regeneration condenser (87) in which circulates on the one hand, said gas-vapor mixture expelled by said turbocharger turbine (62) and / or said expansion turbine (3) in a condenser-regenerator gas-vapor mixture circuit (88) and on the other hand, a liquid water (45) in a condenser-regenerator water circuit (89) which is connected to the regeneration-combustion channel (34), said mixture heating said water (45) to the interior of the chamber; condenser-regenerator (87) through the internal walls of c he last.

5. The turboshaft according to any one of claims 2 and 4, characterized in that the condenser-regenerator water circuit (89) is constituted by at least one internal condenser-regenerator duct (90) in which circulates in the atmosphere. liquid water (45), while the condenser-regenerator gas-vapor mixing circuit (88) is constituted by at least one external condenser-regenerator casing (91) which surrounds and / or adjoins said internal duct (90). ), said housing (91) leaving a space between itself and said inner conduit (90) that it contains and / or adjoins while the gas-vapor mixture expelled by the turbocharger turbine (82) and / or the turbine A driving motor (3) circulates in said space, the direction of circulation at mixing in said space being opposite to that of the circulation of said water (45) in said conduit (90).

6. A ïurbomoteur queiconque one of claims 2 and 4, characterized in that the regenerator condenser-water circuit (89) is connected to the regenerative-combustion channel (34) via ^a conduit supply of post-combustion steam (94) which opens into said channel (34) after continuous combustion chamber (35) with respect to the circulating no gas-vapor mixture and / or atmospheric air in said channel (34).

7. A gas turbine engine according to claim 6, characterized an that the conduit ^for supplying steam afterburner (94) comprises a steam inlet flap afterburner (95) which can close or open said conduit (94).

8. Turbomotor according to any one of claims 2 and 4, characterized in that the condenser-regenerator water circuit (89) is connected to the regeneration-combustion channel (34) via a steam supply duct precombustion (92) which opens into said channel (34) before the continuous combustion chamber (35) relative to the direction of flow of the gas-vapor mixture and / or atmospheric air in said channel (34). 8. A gas turbine engine according to claim S, characterized m that the e ^duct precombustion steam supply (92) comprises a steam inlet flap prechamber (93) which can close or open said conduit (92),

10. Turbomotor according to claim 4 _; characterized in that the outlet pipe of the regeneration exchanger (84) comprises a preheating flap and / or vaporization of liquid water (78) placed upstream of the countercurrent vapor condenser-condenser (87) relative to the direction flow of the gas-vapor mixture in said duct (84), said flap (78) allowing the EMS turbine engine management computer (57) to orient all or part of said mixture first to said condenser-regenerator (87); ) then to the exhaust line outlet (55) or directly to said outlet (55).

11. Turbomotor according to any one of claims 1 and 2, characterized n that the turbocharger turbine (82) comprises variable geometry vanes (78) which can guide a flow of gas-vapor mixture passing through said turbine (62). during operation of the turbine engine (1).

12. A gas turbine engine according to ^one of claims 1 and 2, characterized in that the driving expansion turbine (3) has variable geometry vane (77) that can direct a gas-vapor mixture flow through said turbine (3 ) during operation of the turbine engine (1).

A turbocharger according to claim 1, characterized in that the regeneration countercurrent air / heat exchanger (30) comprises at least one countercurrent regeneration heat exchanger inner duct (31) in which the atmospheric air expelled by the centrifugal turbocharger compressor (61), and at least one countercurrent regeneration heat exchanger outer casing (33) which surrounds and / or adjoins said inner conduit (31), said housing (33) leaving a space between itself and said inner duct (31) that it contains and / bu adjoins while the gas-vapor mixture expelled by the turbine turbocharger (62) and or ia the turbina driving relaxation (3) circulates in said space, the direction of circulation or mixture in said space being inverse to that of the circulation dudii air in said conduit (31). A turbotower according to claim 13, characterized in that the countercurrent regeneration exchanger internal conduit (31) has daisy fins or section (32) which provide a large contact surface simultaneously with the gas-mixture. vapor which circulates in the space between the external countercurrent regeneration exchanger casing (33) and said duct (31), and with the atmospheric air circulating inside said duct (31). , Turbomoteu according to claim _1: characterized m that an outlet air / méiange against the flow of regeneration (30) comprises an outlet duct ^of regeneration exchanger (84) in which circulates the gas-vapor mixture exhausted from the turbocharger turbine (62) and / or the expansion drive turbine (3), said duct (84) connecting said exchanger (30) with the inlet of a countercurrent air / gas exhaust aftercooler ( 16) in which circulates on the one hand, said gas-vapor mixture expelled by said turbocharger turbine (62) and or said expansion drive turbine (3) and, on the other hand, an atmospheric air expelled by means of cooling air insufflation- condensation (26) after said air has been sucked into the atmosphere by the medium means (26) via a cooling-condensing air inlet (22) and via a cooling air intake duct- condensation (64) then has been insufflated in said cooler-condenser (16) via an insufflation duct (24) and a cooling-condensing air insufflation mouth (20) that comprises a cooler-condenser (16), said mixture heating said air (interior) to said cooler-condenser (18) before said air comes out of said cooler-condenser (16) through a cooling-condensing air exhaust mouth (23) via a cooling-condensing air blower (21) that includes said cooler-condenser (16) and a blowing duct (25) which connects said blower (21) to said exhaust mouth (23).

16.Turbomoieur according to claim 2, characterized in that the output of the condenser-regenerator countercurrent steam (8?) Comprises a condenser-regenerator outlet duct (129) in which circulates the gas-vapor mixture expelled by the turbocharger turbine (62) and / or the expansion turbine (3), said duct (129) connecting said condenser-regenerator (8?) with the inlet of an air / gas exhaust condenser-condenser against current (16) in which flows on the one hand said gas-vapor mixture expelled by said turbine turbocharger (62) and / or said turfelne driving relaxation (3) and secondly, atmospheric air expelled by means of Insufflation of cooling-condensing air (28) after said air has been sucked into the atmosphere by the medium means (28) via a cooling-condensing air inlet (22) and via an air duct. intake of cooling-condensing air (84) then has been blown into said refroldisseur-condenser (16) via a conduit ^insufflation (24) and a mouth of cooling-condensation of air blowing (20) that includes said refroldisseur-condenser (16), said warming said mixture air inside said cooler-condenser (16) before said air comes out of said condenser-condenser (16) through a cooling-condensing air exhaust port (23) via an air blower mouth; condensation-cooler (21) which comprises said condenser-condenser (16) and a blowing duct (25) which connects said blower mouth (21) to said exhaust mouth (23), the vibomofeur according to one any of claims 15 and 16, characterized in that the countercurrent air / gas exhaust cooler-condenser (16) comprises at least one countercurrent internal condenser / coolant duct (17) in which the mixture circulates. gas-vapor expelled by the turbocharger turbine (62) and / or the drive turbine (3), and at least one outer casing of condenser-condenser against-current: (19) which surrounds and / or adjoins said Internal conduit (17), said carry (19) leaving a space between itself and said inner conduit (17) that it contains and / or adjoins while the atmospheric air expelled by the means of insufflation of cooling-condensing air (26) circulates in said space, the direction of circulation ofdiff air in said space being the same as that of the circulation of said mixture in said conduit (1).

18. Turbo-engine according to claim 17, characterized in that the inner channel of the countercurrent cooler-conoenser (17) has fins or daisy section (18) which provide a large contact surface simultaneously with the air atmospheric circulating in the space between the outer casing of the cooler-condenser against the current (19) and said duct (17), and with the gas-vapor mixture circulating inside said duct (17).

19. Tnrbomoteur according to ^one of claims 15 and 16, characterized in that the means of air cooling-condensation insufflation (26) consist of a centrifugal compressor air cooling-condensation (27) driven by a cooling-condensing air compressor electric motor (28),

20. Turt) omoteur according to claim 1, characterized in that the outlet of the air / regeneration counter-current cooler (30) comprises an outlet duct Regeneration exchanger (84) in which circulates the gas-vapor mixture discharged by the turbocharger turbine (62) and / or the expansion drive turbine (3), said duct (84) connecting said exchanger (30) with return of a liquid water preheating / mixing exchanger (79) wherein flows the one hand the gas-vapor mixture exhausted from the turbocharger turbine (62) and / or the driving expansion turbine (3) and on ^the other hand., a liquid water (45) before this latter is injected into the regeneration-combustion channel (34), said mixture heating said water (45) inside said mixing / water exchanger (79).

21. Turbamofeur according to claim 20 wherein _s qm éehangeur outlet duct of regeneration (84) comprises a liquid water vaporization andlor preheating flap (78) positioned upstream of mixing Téchangeur / preheating water to liquid water (79) in relation to the meaning flow of the gas-vapor mixture in said duct (84), said flap (78) allowing the ElvlS turbo-engine management calculator (57) to orient all or part of said mixture first to said mixing / water stripper ( 79) then to the exhaust line exit (55) or directly to said outlet (55),

22. Turbornoteur according to any one of claims 2 _S 3, 4 and 20, characterized an that the liquid water (45) from the gas-vapor mixture exhausted from the turbocharger turbine (82) and / or the power turbine relaxing (3) of which, it is extracted by means of a collector-separator for condensates (40) placed on the ^line ec appement (54), said recuperator séparateur- (40) recovering said water (45) having previously condensed on the inner walls of said line (54) for storage in a condensate recovery tank (43).

23, turbototor according to claim 22, characterized in that the condensate separator-recuperator (40) comprises an internal condensate separator-recuperator conduit (41) provided with draining orifices condensates (42) through which the liquid water (45) flows by gravity to the condensate recovery tank (43) where said water (45) is temporarily stored.

24. Turbornoteur according to claim 23, characterized in that the internal duct of qm condensate collector-separator (41) contains steel wool or labyrinthine structure (44) which retains or condensed ^water suspension droplet form and / or vapor in the gas-vapor mixture expelled by the turbocharger turbine (62) and / or the expansion turbine (3) so that said water flows via the draining orifices of the condensates (42) to the tank recovering the condensates (43) rather than being carried by said gases to the exit of the exhaust line (55).

25, turbototor according to claim 22, characterized in that the liquid water (45) is conveyed from the condensate separator-recuperator (40) to the regeneration-combustion channel (34) by at least one condensate pump ( 48) via at least one condensate recirculation duct (47).

26. Turbomizer according to claim 25, characterized in that the condensates recirculation duct (4?) Comprises an intermediate condenser storage tank (48) for temporarily storing the liquid water (45).

^■ 5 27. Turbomoieur according to any one of claims 22 and 25, characterized in qm the condensate drain pan (43) and / or the conduit reclrculstlon condensates (4?) Has a condensate filter (49) .. 0 28.Turbornoteur according ^to one of claims 1 and 2, characterized in that the regeneration-combustion channel (34) comprises a water injector precombustion anti-Ox (39) placed before the combustion chamber continues (35) relative to the direction of flow of atmospheric air in said channel (34) said injector (39) being able to inject liquid water (45) into said channel (34),

29. Turbomiereur according to any one of claims 1 and 2, characterized in that the gas-steam inlet gas turbine engine expansion (68) comprises an expansion turbine inlet valve (4) driven by the engine of management of the EUS turbocharger (57) said valve (4) being able to close said duct (68).

30. Turbomizer according to any one of claims 1 and 2, characterized in that the driving turbine expansion (3) is mounted on the drive turbine shaft expansion (6?) Through a molt-free link expansion turbine (5), said link (5) allowing said turbine (3) to rotate said shaft (87), but not vice versa.

31. Turbomizer according to any one of claims 1 and 2, characterized in that the driving turbine expansion (3) is mounted on the drive turbine shaft expansion (67) via a gear coupler and / or a clutch.

32. Turbomizer according to any one of claims 1 and 2, characterized in that the fan drive turbine shaft (67) is connected to an electric turbine generator (11) by means of a mechanical transmission of generator (6), said generator (1 1) being able to produce electricity when it is rotated by said shaft (67), a turbot according to claim 32, characterized in that the mechanical transmission of generator (6) consists of an epicycfoidal generator drive train (7). Turboturbator according to Claim 32, characterized in that the electric turbine generator (11) is electrically connected to an electrochemical accumulator (10) and / or to an electrostatic accumulator (69), a turbot according to one of Claims 15 and 18. , characterized in that the blowing duct (25) comprises a turbot propeller (8) starting bypass air shutter which can force all or part of the atmospheric air exiting the air / gas exhaust cooling-exhaust condenser against the current (18) to go to the intake duct of the turbocharger (58) via a start bypass air channel of the turbot motor (65) while prohibiting access to the exhaust air outlet of condenser cooling (23) while a turbanotor start air shutter air shutter (9) that includes said intake duct (58) prohibits said air to rise towards the air intake opening of urbomoieur (80) while forcing said air towards the inlet of the turbocharger compressor (81) and while prohibiting all or part of the atmospheric air from the turbo engine air inlet (80) to join the dudlt inlet Compressor (61),, a turbotower according to any one of claims 1 and 2, characterized in that the regeneration-combustion channel (34) comprises a pollutant post-treatment catalyst (53) placed after the continuous combustion chamber (35) relative to the direction of circulation of the atmospheric air and / or the gas-vapor mixture in said channel (34). Turboturbator according to one of Claims 1 and 2, characterized in that the gas-steam exhaust gas duct for the expansion turbine (70) and / or the gas-steam induction motor exhaust duct ( 66) comprises a catalyst for post-treatment of the pollutants.

38.Tur omoteur according to any one of claims 1 and 2, characterized in that the regeneration-combustion channel (34) and / or the gas-steam inlet gas turbine engine (66) and / or the exhaust gas turbine-engine exhaust gas duct (70) and / or the regeneration counter-current air / mixture exchanger (30) is coated with an internal {51} heat-insulating material and / or structure; or external which retains the heat of the atmospheric air and / or the gas-vapor mixture circulating inside said organs (34, 68, 70, 30). 39, turbototor according to any one of claims 1 and 2 _f characterized in that the intake duct of the turbo engine (58} _s comprises a turbocharger intake air filter (59),

40. A turbocharger according to any one of claims 15 and 16, characterized in that the cooling-condensing air intake duct (84) comprises an air filter for cooling-condensing air ( 29).

41. A turbot engine according to any one of claims 1 and 2, characterized m that it is installed in a motor vehicle (58) so as to ensure directly or indirectly the propulsion of said vehicle (58), the latter having a reservoir of fuel (71) and a fuel pump (72) that supply fuel to the continuous combustion fuel injector (36). 42. turbototeur according to claim 41, characterized in that the arb e of the driving turbine expansion (87) is connected to at least one wheel (73) that comprises the motor vehicle (56) by mechanical transmission means. 43, turbototor according to claims 32 and 41, characterized in that the electric turbine generator (11) supplies electrical power to at least one electric propulsion-regeneration motor-generator (88) connected to at least one wheel (73) that comprises the motor vehicle (58) via a mechanical motor-generator transmission (74),

44. A turbocharger according to claim 43, characterized in that the engine-generator mechanical transmission (4) consists of a motor-generator epicyclic transmission train (75), 45, a turbine engine according to any one of the preceding claims. 15 and 18, characterized in that the blowing duct (25) comprises an exchanger "air / water heat recovery residual (81) in which circula on the one hand," atmospheric air expelled by the insufflation means of cooling-condensing air (26) and secondly, a heat transfer fluid, said air heating said fluid inside the air / water exchanger (81).

46, turbinator according to claim 45, characterized in that the blowing duct (25) comprises a residual heat recovery flap (80) placed upstream of the heat exchanger air / water heat recovery residual (81) with respect to a sense flow of atmospheric air in said duct (25), said flap (80) allowing the EMS turbine engine management computer (57) to orient all or part of the air dodit first to said air / water exchanger ( 81) then to the cooling-condensing air outlet (23) directly to said mouth (23).

47, Turbomotor according to Claim 45, characterized in that the air exchanger / waste heat recovery water (81) is connected by at least one heating fluid duct (85) to a heating radiator (83), the coolant flowing in said conduit (85). 8, a turbomachine according to any one of claims 18 and 40, characterized in that at least the cooling-condensing air insufflation means (28) and at least the centrifugal compressor of cooling-condensing air ( 27) and the cooling-condensing air compressor electric motor (28) of which said means are constituted and or the cooling-condensing air insufflation air filter (29) are commonly accommodated in a housing of cooling-condensing air insufflation (50) while connectors (86) extend from said casing (50) for connecting at least the cooling-condensing air intake duct (64) and / or the duct insufflation (24),

49. A turbomixer according to any one of claims 1 and 2, characterized in that the continuous combustion chamber (35) is a heat exchanger connected directly or indirectly to a heat source. NaN / Turbocharger according to Claim 49, characterized in that the heat source consists of a condenser comprising a heat pump which extracts heat from an environment.

51, turbine engine according to claim 50, characterized in that the heat pump is rotated by the drive turbine shaft (67).

52, Tu rbon oteur according to claim 50, characterized in that q atmospheric air sucked via the turbine engine air inlet (60) by the centrifugal compressor turbocharger (81) is previously cooled by an evaporator that includes the heat pump.

53. A turbine engine according to any one of claims 15, 16 and 50, characterized in that the atmospheric air sucked via the cooling-condensing air intake pipe (22) by the cooling air insufflation means. -condensation (26) is previously cooled by an evaporator that includes the heat pump.

54. A turbine engine according to any one of claims 1 and 2, characterized in that the drive turbine shaft expansion (67) can be rotated by the drive turbine (3) relaxation, said shaft can in turn lead to rotating a turbine driver pinion (115) which rotates a multithrust reducer ring (114) which can rotate a mufti-turbines reducer power output shaft (118). 55. A turbocharger according to claim 54, characterized in that the expansion turbine drive shaft (67) is connected at one of its ends to the expansion turbine (3) and at its other end to the drive pinion. turbine (115) via a transmission joint. 56.The electric motor according to claim 54, characterized in that the multi-turbine gear reducer output shaft (118) terminates with a power output gear (125), 57 / Turmeric engine according to claim 54, characterized in that the turbine drive pinion (115) is mounted on the expansion drive shaft (67) via a free wheel connection, said a link enabling said shaft (67) to rotate said pinion (115), but not vice versa,

SS. A rotor according to claim 54, characterized in that the multi-rotor ring gear ring (114) is mounted on the mufti-turbines reducer power output shaft (118) through a free-wheeling mechanism. gearbox crown (117) which allows said ring gear (1 14) to rotate said shaft (118), but not vice versa.

59. Turtle motor according to any one of claims 1 and 2, characterized in that it comprises at least two turbochargers (2) _: the first being a low-pressure turbocharger (103) whose centrifugal compressor low-pressure turbocharger (121) pre-compresses the atmospheric air that it sucks through the mylomotor air inlet (βθ) when said compressor (121) is rotated by the low-pressure turbocharger turbine (122) that comprises said low-pressure turbocharger (103), while the second is a high-pressure turbocharger (104) whose high-pressure turbocharger centrifugal compressor (123) overcompensates the air expelled by the centrifugal low-pressure turbocharger compressor ( 121) before it is expelled in turn into the regeneration-combustion channel (34) when said compressor (123) is rotated by the high-pressure turbocharger turbine (124) provided therein high-pressure turbocharger (104), the sodie of the low-pressure turbocharger centrifugal compressor (121) being connected to the inlet of the high-pressure turbocharger centrifugal compressor (123) through an inter-compressor linkage channel (116) while the high-pressure turbocharger turbine (124) pre-expands a gas-vapor mixture from the regeneration-combustion channel (34) prior to expelling it at the inlet of the low-pressure turbocharger turbine (122); overstretching said mixture prior to expelling it in turn into the gas-steam exhaust gas engine (70).

60. The turbocharger according to claim 59, characterized in that the inter-compressor link channel (118) comprises an intermediate cooler of a turbocharger (96) which cools the air expelled by the low pressure turbocharger centrifugal compressor (121) before said air is supercharged by the centrifugal high pressure turbocharger compressor (1 3),

81. A turbocharger according to claim 59, characterized in that the centrifugal compressor of high pressure turbocharger (123) comprises a high-pressure compressor hy-pass valve (105) which, when opened by the management computer of the turbocharger ES (57), can direct part of the air from the centrifugal compressor of low-pressure turbocharger (121) directly to the regeneration-combustion channel (34) without passing through the centrifugal compressor of high-pressure turbocharger ( 123).

62. A turbocharger according to claim 59, characterized in that the high pressure turbocharger (104) comprises a high pressure turbine bypass valve (106) which, when opened by the turbo motor management calculator EMS (57) _s can direct a portion of a vapor gas mixture from the regenerative-combustion channel (34) directly from said channel (34) to the low-pressure turbocharger turbine (22) without passing through the turbocharger turbine high pressure (124).

63. A gas turbine engine according to ^one of Claims 1 and 2 _(wherein er? Ue that the turbomoleur intake duct (58) comprises an electropneumatic starter (108) of a centrifugal compressor electropneumatic starter (110) being rotated by an electric motor starter electropneumatic (109) whereby said compressor (1 10) compresses the atmospheric air from the intake mouth ^of air turbomoleur (60) at the inlet of the centrifugal compressor turbocharger (61),

64. A turbocharger according to claim 83, characterized in that the intake duct of the turbomolor (58) comprises an electropneumatlque starting flap (1 1 1) controlled by the turbomolor management computer EMS (57), said flap (1 ) enabling said calculator (57) to force atmospheric air from the turbine engine air intake port (60) to pass through the electro-centrifugal starter centrifugal compressor (110) before joining the turbocharger centrifugal compressor (81) when said flap (111) is in a first position, or passing through a bypass channel of the electropneumatic starter (120) before joining said inlet when said flap (111) is in a second position.

65. Turbornoteur according to ^one of claims 1 and 2, characterized in that the exhaust line (54) includes an air / water heat recovery of exhaust {100} in which circulates a water also Circulating in a heating radiator (83) which heats a solid, liquid or gaseous environment, said heat exchanger (100) being connected to said radiator (83) by heating radiator conduits (128) while said water is forced to flow in said heat exchanger (100), said radiator (83) and the conduits (128) by an exhaust heat recovery water pump (102), the gas-vapor mixture expelled by the turbocharger turbine (82) and / or the turbine triggering member (3) warming said water inside said exchanger (100) before said mixture exits through the exhaust line outlet (55) while said water is cooled to the bottom of the heating radiator ( 83) by said env ironment.

68. A turbotower according to claim 85, characterized in that the exhaust line (54) comprises an exhaust heat recovery flap (101) controlled by the turbofan management computer EIV1S (57), said flap (101). ) enabling said computer (57) to force the gas-vapor mixture expelled by the turbocharger turbine (62) and / or the expansion turbine (3) to pass through the exhaust air / water heat exchanger (100) before joining the exhaust line exit (55) when said flap (101) is in a first position, or passing through a bypass channel of the exhaust heat recovery exchanger (127) ) before joining said outlet (55) when said flap (101) is in a second position.

87. Turboteroteur according to any one of claims 1 and 2, characterized mce ue the exchanger air / mixture against regenerating current (30) is arranged in a deformable structure constituting a shock absorber.