FR2993929A1 - INTERNAL AND / OR EXTERNAL COMBUSTION LOW PRESSURE TURBOMOTOR - Google Patents

Abstract

The turbine engine (1) according to the present invention comprises a turbocharger (2) whose centrifugal compressor (61) and turbocharger turbine (62) are connected by a regeneration-combustion channel (34) which comprises a continuous combustion chamber ( 35) in which a fuel is burned, and a postcombustion steam supply duct (94) connected to a counterflow steam condenser-condenser (88), said channel (34) also being connected to the inlet of a drive turbine for expansion (3) via a conduit (66), while said channel (34) comprises a regenerative countercurrent air / mixture exchanger (30) which heats atmospheric air expelled into said channel (34) by the centrifugal compressor (61) with a gas-vapor mixture expelled via a gas-steam exhaust pipe of the expansion turbine (70) by said turbine (62) and said expansion turbine (3).

Description

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 produce 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 the automobile, road transport in general or light power stations, the most commonly used machines to convert the heat delivered by the combustion of a fuel into mechanical work are the engines reciprocating internal combustion engines, mainly diesel or spark ignition, and two or four stroke engines.

Many attempts have been made to propel automobiles or light land vehicles by means of turbine engines comprising one or more turbines and operating with a liquid or gaseous fuel. Various automobiles were built, retaining this principle as the "Ti" model of the company "Rover", the "Socéma-Grégoire" or the "Turbine Car" of the company "Chrysler". We also note the attempts remained in the state of prototype made in this area by the company "Volkswagen" with turbines of type "GT 70" and "GT 150". Unfortunately, the strong power variations that characterize the automobile use are not suitable for turbines whose efficiency is optimal at nominal power, but insufficient out of said power so that said turbines have hitherto not been able to replace the heat engines reciprocating internal combustion engines that continue to equip one hundred percent of thermal propulsion vehicles. It should be noted that turbine 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 cooperated with one or more regenerator (s) or recuperator (s) of heat 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 "KTT" for automotive propulsion and developed by the Swedish professor Sven-Olof Kronogard and the company "United Turbine". These revolving regenerators or recuperators - in addition to their high cost - generated pressurized gas leaks detrimental to the overall efficiency of the turbine 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 in said vehicles while the latter are powered by one or more electric motors. This is the case for example of the American company "Capstone" or the English company "Bladon Jets ®" which develop micro turbines driving an electric generator on board vehicles powered by electric motors. The company "Capstone" is particularly known for its concept of hybrid vehicle "CMT380 Blackbird", while the company "Bladon Jets" was noted for having equipped the concept car "Pininfarina Cambiano" or prototype "Jaguar C-X75" of its device for generating electricity by an axial micro-turbine. In the same field, we also note the demonstration hybrid vehicle "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 acoustic level remain high so that alternative internal combustion engines are ultimately preferred to them to produce mass-produced and commercial vehicles.

Despite these failures, converting the primary energy on board motor vehicles into mechanical work by means of one or more turbines would be decisively advantageous because said turbines potentially have a high power density, they are compact and light, and they present low friction and pumping losses. In addition, the turbines are by definition poly-fuel because unlike the internal combustion engines alternative whose combustion is sequential, their combustion is continuous so that they are not subject to the constraints imposed by the limit of auto-ignition fuels and the undesirable clatter that may result. In return for these advantages, in contrast to reciprocating engines generally cooled with water and offering little contact surface with the hot gases resulting from the combustion of the fuel, the turbines have the disadvantage of operating at a temperature substantially equal to that gases leaving the combustion chamber placed upstream. Said turbines can not operate at a temperature higher than that set by their thermomechanical resistance 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 the reciprocating internal combustion engines with a turbocharger whose compressor and turbine have radial vanes. The reciprocating engines produced according to this configuration offer an acceptable efficiency at low power while at high power, the turbine of the turbocharger recovers a part of the heat energy lost to the exhaust of said engine to supercharge 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 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 to turbines in general for driving motor vehicles at a lower cost, while giving these turbines a yield at least equal to that of alternative internal combustion engines. .

It is for this reason that the low-pressure internal combustion and / or external water vaporization and / or regeneration turbine engine provides, according to one particular embodiment: to offer a high energy efficiency over a wide range of power particularly through the use of several turbochargers as usually used in the automotive industry and several expansion turbines, said turbochargers and said turbines can be operated simultaneously in various combinations, this particular strategy making it economically profitable and technologically possible the use of turbines to propel motor vehicles, with a high energy efficiency; - To use 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 so that said turbines may eventually be at variable geometry whatever the type; - To 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 low enough pressure and temperature to remain inexpensive, said exchangers do not require mechanical drive; - - - - - - - Significantly reduce the mass, bulk, vibratory and acoustic level, and the cost of automotive powertrains based on said turbine engine compared to those based on a reciprocating internal combustion engine; Significantly increasing the durability and reliability of the automotive powertrains based on said turbine engine, compared to those of said groups based on an internal combustion engine with alternative combustion; Reduce the size of the cooling mouth (s) placed (s) on the front of motor vehicles or even remove the or said mouth (s), and significantly reduce the resistance to penetration into the air of said vehicles; ; To allow the consumption of all liquid or gaseous fuels without any constraint being imposed by the propensity or resistance to self-ignition of said fuels, and without penalty for the thermal-mechanical conversion efficiency of said turbine engine irrespective of the nature and 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 the cold start of said turbine engine compared to that required for reciprocating internal combustion engines, with a drastic reduction in the fuel consumption of said reciprocating engines operated under these conditions; The low pressure internal combustion engine and / or external water vaporization and / or regeneration according to the invention thus allows, in particular and according to the embodiment of said turbine engine: - - - 20 - 25 - 30 - 35 To produce clean, quiet, economical, economical to produce and light motor vehicles, which are therefore efficient and attractive for the end consumers; To enhance the knowledge and know-how relating to the design, manufacture and industrialization of turbochargers applied to reciprocating internal combustion engines, whether they are equipped with a variable geometry turbine or a turbine fixed geometry; To significantly reduce the fuel consumption of motor vehicles on regulatory driving cycles and in ordinary driving conditions, even when said vehicles are used at a highly variable power and thus significantly increase the autonomy of said vehicles for the same amount of fuel. fuel on board said vehicles; Eventually, remove the gearbox of motor vehicles and replace it with a fully electric, flexible and compact transmission; Possibly, to supply electric 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 said vehicles become more competitive and more attractive for cars. end consumers; Replace hydrogen fuel cells as planned to generate electricity for certain electric vehicles, with potentially comparable efficiencies, significantly lower cost, and without the various constraints of using hydrogen as a source of electricity. energy or without those related to the least responsiveness in power variation of said batteries; - drastically reduce the weight and cost of on-board batteries in electric vehicles; - Facilitate the aerodynamic and aesthetic design of the body of motor vehicles by reducing the constraints of cooling and housing the powertrain of said vehicles, or the size of their batteries for storing electricity; - Reinforce the safety of motor vehicle passengers and pedestrians who may collide with such vehicles, in particular by reducing the incompressible volume of the powertrain housed in the engine compartment of such vehicles; - Improve the comfort of passengers of motor vehicles including rapid warming of the passenger-cabin of said vehicles in cold weather; - Simplify maintenance and servicing of motor vehicles; - Achieving low-cost high-efficiency electricity generating stations for domestic or industrial use, said stations offering the possibility of recovering the fraction of heat not transformed into work by the turbine engine according to the invention, thereby achieving 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 turbocharger which cooperates with at least one regeneration-combustion channel which directly or indirectly connects the outlet of a centrifugal turbocharger compressor which comprises said turbocharger with the inlet of a turbine turbocharger comprising said turbocharger, said compressor expelling atmospheric air in said channel after having sucked via a turbine engine air inlet and via a turbine engine inlet duct, 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 expansion, 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 regeneration counter-current air / mixture exchanger which is part of the regeneration-combustion channel and in which flows, on the one hand, a gas-vapor mixture expelled by the turbocharger turbine and / or the driving turbine of detent the output of said turbines being connected to said exchanger by a gas-steam exhaust gasoline engine expansion duct and secondly, the atmospheric air expelled by the centrifugal compressor turbocharger said mixture heating said air inside said exchanger before exiting through an exhaust line through an exhaust line; - At least one management computer of the EMS turbine engine.

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 centrifugal turbocharger compressor which comprises said turbocharger with the inlet of a turbocharger turbine comprising said turbocharger, said compressor expelling an atmospheric air into said channel after having sucked it via a turbine engine air intake port 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 expansion, 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 countercurrent steam regeneration condenser in which a gas-vapor mixture expelled by the turbocharger turbine and / or the expansion drive turbine flows in a condenser gas-vapor mixing circuit; -regenerator and in which circulates on the other hand, a liquid water in a condenser-regenerator water circuit connected to the regeneration-combustion channel, said mixture heating said water inside said condenser-regenerator before emerging by a exhaust line outlet via an exhaust line while the inlet of said condenser-regenerator is connected to a gas-steam exhaust pipe driving the expansion turbine in which circulates the gas-vapor mixture expelled by the turbine of turbocharger and / or the driving turbine of relaxation; - At least one management computer of the EMS turbine engine. The turbine engine according to the present invention comprises a regeneration-combustion channel which comprises at least one water vaporization chamber internal to said channel in which a liquid water can be injected by a post-combustion water injector so as to produce a gas-air mixture. steam. The turbine engine according to the present invention comprises an outlet of the regeneration countercurrent air / mixture exchanger which comprises a regeneration exchanger outlet duct in which circulates the gas-vapor mixture expelled by the turbocharger turbine and / or the drive turbine for expansion, said duct connecting said exchanger with the inlet of a condenser-regenerator of countercurrent steam in which flows on the one hand, said gas-vapor mixture expelled by said turbocharger turbine and / or said driving turbine for expansion in a condenser-regenerator gas-steam mixing circuit and, secondly, 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 internal 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 condenser-regenerator casing 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 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 opposite to that of the circulation of said water in said conduit.

The turbine engine 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 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 postcombustion steam supply duct which comprises a postcombustion 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 continuous combustion chamber. relative 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 a regeneration exchanger outlet duct which comprises a preheating flap and / or vaporization of liquid water placed upstream of the condenser-regenerator of countercurrent steam with respect to the direction of flow. a gas-vapor mixture in said duct, said shutter enabling the EMS turbine engine management computer to orient all or part of said mixture first to said condenser-regenerator and then to the exhaust line outlet or directly to said outlet . The turbine engine according to the present invention comprises a turbocharger turbine which comprises blades of 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 countercurrent regeneration exchanger internal duct in which circulates the atmospheric air expelled by the centrifugal turbocharger compressor, and at least one outer casing of countercurrent regeneration exchanger which surrounds and / or adjoins said inner 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 expansion in said space, the direction of circulation of said mixture in said space being opposite to that of the circulation of said air in said conduit.

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

The turbine engine according to the present invention comprises an outlet of the regeneration countercurrent air / mixture exchanger which comprises a regeneration exchanger outlet duct in which circulates the gas-vapor mixture expelled by the turbocharger turbine and / or the expansion drive turbine, said duct connecting said exchanger with the inlet of a countercurrent air / gas exhaust cooler-condenser in which flows on the one hand said gas-vapor mixture expelled by said turbocharger turbine and / or said expansion drive turbine and secondly, an atmospheric air expelled by means of cooling-condensing air insufflation after said air has been sucked into the atmosphere by said means via an intake air intake port. cooling-condensing air and via a cooling-condensing air intake duct and then being blown into said cooler-condenser via an air duct. nsufflation and a cooling-condensing air blowing mouth that includes said cooler-condenser, said mixture heating said air inside said cooler-condenser before said air comes out of said cooler-condenser through an exhaust mouth cooling-condensing air via a cooling-condensing air blowing mouth that includes 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 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 driving turbine. expansion, said duct connecting said condenser-regenerator with the inlet of a countercurrent air / gas exhaust cooler-condenser in which flows on the one hand said gas-vapor mixture expelled by said turbocharger turbine and / or said a driving turbine for expansion and, secondly, an atmospheric air expelled by means of cooling-condensing air insufflation after said air has been sucked into the atmosphere by said means via an air intake mouth of cooling-condensation and via a cooling-condensing air intake duct and then being blown into said cooler-condenser via a pipe a blower and a cooling-condensing air blowing mouth that includes said cooler-condenser, said mixture heating said air inside said cooler-condenser before said air comes out of said cooler-condenser through a mouth cooling-condensing air exhaust system via a cooling-condensing air blowing mouthpiece which comprises said condenser-cooler 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 cooler-condenser 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 motor of relaxation, and at least one external casing of countercurrent cooler-condenser 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 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 opposite to that of the circulation of said mixture in said duct. The turbine engine according to the present invention comprises a countercurrent internal cooler-condenser duct which has fins or daisy section which offer a large contact surface simultaneously with the atmospheric air circulating in the space between the outer casing counter-current cooler-condenser and said duct, and with the gas-vapor mixture circulating inside said duct.

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

The turbine engine according to the present invention comprises an outlet of the regeneration countercurrent air / mixture exchanger which comprises a regeneration exchanger outlet duct in which circulates the gas-vapor mixture expelled by the turbocharger turbine and / or the expansion turbine, said duct connecting said exchanger with the inlet of a liquid water preheating / mixing exchanger in which flows, on the one hand, the gas-vapor mixture expelled by the turbocharger turbine and / or the drive turbine expansion and secondly, a liquid water before the latter is injected into the regeneration-combustion channel, said mixture heating said water inside said exchanger mixture / water. 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 exchanger mixing / water of liquid water preheating with respect to the direction flow of the gas-vapor mixture in said conduit, said shutter enabling the EMS turbine management computer to orient all or part of said mixture first to said mixture / water exchanger and then to the exhaust line outlet; directly to said output. The turbine engine according to the present invention comprises a liquid water which comes from the gas-vapor mixture expelled by the turbocharger turbine and / or the expansion drive turbine from which it is extracted by means of a condensate separator-recuperator placed on the line d 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 duct provided with condensate-draining orifices through which the liquid water flows by gravity to the condensate recovery tank where said condensate separator water is temporarily stored. The turbine engine according to the present invention comprises an internal condensate separator-recuperator conduit which contains an iron straw or labyrinthine structure which retains or condenses suspended water in the form of droplets and / or vapor in the gas-vapor mixture. discharged 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 condensate recovery tank rather than being carried by said gases to the outlet 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 pipe. The turbine engine according to the present invention comprises a condensate recirculation duct which may comprise an intermediate condensate storage tank for temporarily storing the liquid water. The turbine engine according to the present invention comprises a condensate recovery tank and / or a condensate recirculation pipe which comprises a condensate filter. The turbine engine according to the present invention comprises a regeneration-combustion channel which comprises an anti-NOx pre-combustion water injector placed before the continuous combustion chamber with respect to the direction of circulation of atmospheric air in said channel, said injector being able to inject a liquid water in said channel. The turboshaft engine according to the present invention comprises a gas-steam admitting motor turbine intake duct which comprises an expansion turbine inlet valve controlled by the EMS turbine engine management computer, said valve being able to close off said duct. The turbine engine according to the present invention comprises an expansion power turbine which is mounted on the drive turbine shaft by means of a pressure-free expansion turbine link, said link allowing said turbine to drive in rotation said shaft, but not the opposite. The turbine engine according to the present invention comprises a drive turbine for expansion which is mounted on the drive turbine shaft expansion via a gear coupler and / or a clutch.

The turbine engine according to the present invention comprises a drive turbine shaft which is connected to an electric turbine generator by means of a mechanical transmission of generator, 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 an epicyclic generator drive train.

The turbine engine according to the present invention comprises an electric turbine generator which is electrically connected to an electrochemical 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 leaving the air-to-gas exhaust aftercooler. 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 start-up obstruction that includes said intake duct prohibited said air to go towards the turbine engine air inlet while forcing said air to the inlet of the turbocharger compressor and while prohibiting all 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 channel and / or an expansion engine gas-steam admission duct and / or an exhaust gas turbine-engine exhaust duct and / or an exchanger air / countercurrent regeneration mixture which is coated with an internal and / or external heat-insulating material and / or structure which retains the heat of the atmospheric air and / or the gas-vapor mixture circulating inside said organs . The turbine engine according to the present invention comprises an intake duct of the turbine engine which comprises a turbine engine intake air filter. The turbine engine according to the present invention comprises a cooling-condensing air intake duct which comprises a cooling-condensing air insufflation air filter.

The turbine engine according to the present invention is installed in a motor vehicle so as to ensure directly or indirectly the propulsion of 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 a motor-generator epicyclic gear train.

The turbine engine according to the present invention comprises a blowing duct which comprises an air / water heat recovery heat exchanger in which flows on the one hand, the atmospheric air expelled by the cooling-condensing air blowing means and on the other hand, a coolant, said air heating said fluid inside said air / water heat exchanger.

The turbine engine according to the present invention comprises a blowing duct which includes a residual heat recovery flap placed upstream of the air / water heat recovery heat exchanger with respect to the direction of flow of atmospheric air in said duct. , said shutter enabling the EMS turbine engine management computer to orient all or part of said air first to said air / water heat 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 recovery heat exchanger which is connected by at least one heating fluid duct to a heating radiator, the coolant circulating in said duct. The turbine engine according to the present invention comprises at least cooling-condensing air blowing means and at least the centrifugal cooling-condensation air compressor and 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-condensing air insufflation box while connectors come out of said housing which make it possible to connect at least the cooling-condensing air intake duct and / or 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 which consists of a condenser comprising 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 cooling-condensing air intake pipe by the cooling-condensation air insufflation means which is previously cooled by an evaporator that includes the heat pump. . The turbine engine according to the present invention comprises an expansion drive shaft which can be driven in rotation by the expansion drive turbine, said shaft being able in turn to drive in rotation a turbine drive pinion which drives in rotation a ring gear. multi-turbine gearbox capable of rotating 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 an epicyclic output power train. The turbine engine according to 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 opposite. 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 in which the centrifugal compressor of low-pressure turbocharger pre-compresses the atmospheric air that it sucks through the air intake port of the engine. 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 supercharges the air expelled by the centrifugal compressor of low-pressure turbocharger before expelling it in turn into the regeneration-combustion channel when said compressor is rotated by the high-pressure turbocharger turbine of said high-pressure turbocharger, the output of the centrifugal compressor of low pressure turbocharger being connected to the the high-pressure turbocharger centrifugal compressor through an inter-compressor linkage channel while the high-pressure turbocharger turbine pre-expands 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 turbine engine according to 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 high turbocharger compressor. -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 opened by the engine management computer EMS, can direct a part 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 electro-pneumatic starter consisting of a centrifugal compressor of electropneumatic starter that can be rotated by an electric motor of the electropneumatic starter so that said compressor compresses 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. turbine engine air to be passed through the centrifugal compressor of the electro-pneumatic starter before reaching the inlet of the centrifugal compressor of turbocharger when said flap is in a first position, or to pass through a bypass channel of the electro-pneumatic starter before joining 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 being connected to said radiator by heating radiator ducts while said water is forced to circulate in said exchanger, said radiator and said ducts by an exhaust heat recovery water pump, the gas-vapor mixture expelled by the turbine turbocharger and / or the expansion turbine engine heating said water inside said exchanger before said mixture comes out of the exhaust line outlet 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 includes 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 bypassing the exhaust heat recovery exchanger before joining said outlet when said flap is in a second position.

The turbine engine according to the present invention comprises a regeneration counter-current air / mixture exchanger which is arranged in deformable structure constituting a shock absorber. The following description with reference to the accompanying drawings, given by way of non-limiting examples, will make it possible to better understand the invention, the characteristics it presents, and the advantages that it is likely to provide: FIG. of the principle 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.

FIG. 4 is a diagrammatic section of the countercurrent regeneration air / mixture 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 gas / air exhaust gas cooler / condenser according to the present invention as it can be provided when the counter-current cooler-condenser inner duct has a daisy section; . Figure 6 is a schematic section of the separator-recuperator of the condensates of the turbine engine according to the present invention. Figure 7 illustrates the schematic diagram of the turbine engine according to the present invention equipped with a condenser-regenerator of countercurrent steam.

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 electropneumatic starter and a multi-turbine group, to the exclusion of any device liquid water vaporization.

FIGS. 9 and 10 are three-dimensional views of a multi-turbine group 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 drive turbine shaft which is terminated by a driving pinion cooperating with a multi-turbine gear ring gear so as to rotate a multi-turbine gearbox output power shaft. Figure 11 is a schematic sectional view of a gearwheel freewheel as it can be provided on a ring gear of multi-turbines that can comprise the turbine engine according to the present invention. DESCRIPTION OF THE INVENTION in FIGS. 1 to 3, the low-pressure internal combustion and / or external water vaporization and / or regeneration turbine engine 1. The turbine engine 1 according to the invention comprises at least one turbocharger 2 cooperating with at least one regeneration channel. combustion 34 which directly or indirectly connects the output of a centrifugal compressor turbocharger 61 that includes said turbocharger 2 with the inlet of a turbocharger turbine 62 that includes said turbocharger 2, said compressor 61 expelling atmospheric air in said channel 34 after having sucked through a turbine engine air intake port 60 and via an intake duct of the turbine engine 58. It can be seen in FIG. al 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. The centrifugal turbocharger compressor 61 and / or said turbocharger turbine 62 may be integrally mounted on the same shaft or be interconnected by transmission means fixed ratio or discrete or continuous variable ratio, said means being able to be mechanical, electrical, hydraulic or pneumatic while said compressor 61 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 inside and / or outside of the continuous combustion chamber 35 can be made of or coated with a refractory material and / or heat insulating with high temperature resistance and include a spark plug 63 comparable to those found in the internal combustion engines spark ignition, said spark plug 63 may optionally cooperate with a not shown glow plug.

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 of the drive turbine 66 while said drive turbine 3 expansion may comprise several stages mounted or not in series on the same shaft. Note that, according to a particular embodiment of the turbine engine 1 according to the invention, the drive turbine 3 expansion can be turbocharger turbine 62 itself.

FIG. 1 shows that the turbine engine 1 comprises at least one regenerative countercurrent air / mixture exchanger 30 forming part of the regeneration-combustion channel 34 and in which circulates a gas-vapor mixture expelled by the turbine turbocharger 62 and / or the driving turbine expansion 3 the output of said turbines being connected to said heat exchanger 30 by a gas-steam exhaust gasoline engine exhaust fan 70 and secondly, the atmospheric air expelled by the centrifugal compressor turbocharger 61 said mixture heating said air inside said exchanger 30 before emerging through an exhaust line 55 via an exhaust line 54. As shown in Figure 7, as an alternative to the air exchanger In addition to or in addition to the latter, the turbine engine 1 may comprise a countercurrent steam regeneration condenser 87 in which circulates from one to the other. t, the gas-vapor mixture expelled by said turbocharger turbine 62 and / or the expansion turbine 3 in a condenser-regenerator gas-vapor mixture circuit 88 and in which a liquid water 45 flows in the other a condenser-regenerator water circuit 89 which is connected to the regeneration-combustion channel 34, said mixture heating said water 45 inside said condenser-regenerator 87 through the inner walls of the latter while a fraction significant amount of water vapor contained in said mixture condenses inside said condenser-regenerator 87 by yielding its heat to the liquid water 45 so that the latter is vaporized in all or part, the inlet of said condenser- regenerator 87 being connected either with the outlet of the regeneration counter-current air / mixture heat exchanger 30 via a regeneration exchanger outlet duct 84 which comprises said exchanger and in a heat exchanger l circulates the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the expansion drive turbine 3, either directly to the gas-steam exhaust gasoline engine exhaust pipe 70. Note that the exhaust line 54 and / or the regeneration-combustion channel 34 and / or the gas-steam induction turbine driving duct 66 and / or the inlet 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 flowmeter, said sensors and said flowmeter giving the management computer of the turbine engine EMS 57. In addition, the turbine engine 1 comprises at least one management engine of the turbine engine EMS 57. 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 IDE 45 can be injected by a post-combustion water injector 38 so as to produce a gas-vapor mixture. The liquid water 45 is injected by the post-combustion water injector 38 so that said water 45 vaporizes in the water vaporization chamber 37 so as to produce superheated steam during operation of the turbine engine 1 in order to to increase the overall efficiency of the latter, and to protect the various mechanical work production members of any excessive temperature that is likely to compromise the thermomechanical behavior of said bodies and / or the manufacture at moderate cost of said organs.

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

As shown in FIG. 7, the condenser-regenerator water circuit 89 consists of at least one internal condenser-regenerator duct 90 in which the liquid water circulates 45, whereas the condenser gas-vapor mixing circuit -regenerator 88 is constituted by at least one external casing of condenser-regenerator 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 3 circulates in said space, the direction of circulation of said mixture 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 turbine engine 1 according to the invention, the condenser-regenerator water circuit 89 is connected to the regeneration-combustion channel 34 via a postcombustion steam supply duct 94 which opens in said channel 34 after the continuous combustion chamber 35 with respect to the direction of flow of the gas-vapor mixture and / or atmospheric air in said channel 34.

In the latter context, the postcombustion steam supply duct 94 may comprise a post-combustion vapor inlet flap 95 which can close or open said duct 94, said flap 95 possibly consisting of a valve, a rotary valve , a valve or any other means known to those skilled in the art for closing a pipe, said shutter 95 can be controlled opening or closing by the management computer of the turbine engine EMS 57 including by means of a pneumatic, electropneumatic, electric, hydraulic or electro-hydraulic actuator.

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 precombustion vapor supply pipe 92 may comprise a steam inlet flap pre-combustion 93 which can close or open said duct 92, said flap 93 may consist of a valve, a rotary valve, a valve or any other means known to those skilled in the art for sealing a duct, said flap 93 can be controlled opening or closing by the engine management computer EMS 57 including by means of a pneumatic actuator, electropneumatic, electrical, hydraulic or electro-hydraulic We noticed e that the regeneration exchanger outlet duct 84 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 mixture gas-vapor 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 87 and then to the exhaust line outlet 55 or directly towards said exit 55.

As represented in FIG. 1, the turbocharger turbine 62 comprises vanes with a variable geometry 76 which can guide a flow of gas-vapor mixture passing through said turbine 62 during the operation of the turbine engine 1, the angular orientation of said vanes 76 being able to be modified by the engine management computer of the EMS turbine engine 57 by means of a pneumatic, electropneumatic, electric, hydraulic or electro-hydraulic actuator so as to regulate the power of said turbocharger turbine 62.

Alternatively, said turbine 62 may be of the "slidevane" type or of any other type known to those skilled in the art that makes it possible to adjust the passage section of the gas-vapor mixture stream 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 regeneration countercurrent air / mixture exchanger 30 comprises at least one internal countercurrent regeneration heat exchanger duct 31 in which the atmospheric air circulates. discharged by the turbocharger centrifugal compressor 61, and at least one countercurrent regenerative heat exchanger outer casing 33 which surrounds and / or adjoins said inner conduit 31, said casing 33 leaving a space between itself and said inner conduit 31 that it contains and / or adjoins while the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the drive turbine 3 relaxation circulates in said space, the direction of circulation of said mixture in said space being opposite to that the circulation of said air in said duct 31.

In FIG. 4, it has been shown that the counter-current regeneration heat exchanger internal duct 31 has fins or daisy-section 32 which offer a large surface of contact simultaneously with the gas-vapor mixture which circulates in the space included. between the outer casing of countercurrent regeneration exchanger 33 and said duct 31, and with the atmospheric air circulating inside said duct 31 so as to promote the heating of the atmospheric air by the gas-gas mixture. steam, while the daisy section 32 may for example be obtained by hydroforming 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 expansion turbine engine 3, said duct 129 connecting said exchanger 30 with the inlet of a countercurrent air / gas exhaust cooler-condenser 16 in which flows on the one hand said gas-vapor mixture expelled by said turbine turbocharger 62 and / or said driving expansion turbine 3 and secondly, atmospheric air expelled by means of cooling-condensing air blowing 26 after said air has been sucked into the atmosphere by said means 26 via a cooling-condensing air intake port 22 and via a cooling-condensing air inlet duct 64 and then blown into said condenser-cooler 16 via an air duct. insufflation 24 and a cooling-condensing air blowing mouth 20 which includes said cooler-condenser 16, said mixture heating said air inside said cooler-condenser 16 before said air comes out of said cooler-condenser 16 by a cooling-condensing air outlet 23 via a cooling-condensing air blower 21 which comprises said cooler-condenser 16 and a blowing duct 25 which connects said blower mouth 21 to said mouth 23. The air-to-gas exhaust air-cooled cooler / condenser 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 drive turbine 3, and at least one external casing of countercurrent cooler-condenser 19 which surrounds and / or adjoins said internal duct 17 said housing 19 leaving a space between itself and said inner conduit 17 that it contains and / or adjoins while the atmospheric air expelled by the cooling-condensing air blowing means 26 circulates in said space, the flow direction of said air in said space being opposite to that of the circulation of said mixture in said duct 17. As illustrated in FIG. 5, the internal duct of the counter-current cooler-condenser 17 has fins or daisy section 18 which provide a large contact surface simultaneously with the atmospheric air flowing in the space between the outer casing of countercurrent cooler-condenser 19 and said duct 17, and with the gas-vapor mixture circulating inside said duct 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 a tub e of stainless steel or not. In FIG. 1, it has been shown that the cooling-condensation air insufflation means 26 consist of a centrifugal compressor of cooling-condensation air 27 driven by an electric motor of a cooling-condensing air compressor. 28 said compressor 27 may in particular be of similar design to the turbo-supercharger compressors or comprise a blower wheel paddle or blades arranged helically.

Whatever the type of said compressor 27, the electric motor 28 can be regulated in power and / or in rotational mode by the management computer of the turbine engine EMS 57 as a function of the flow of atmospheric air that it is necessary to inject in the air-to-gas exhaust after-cooler-condenser 16. FIG. 1 illustrates that according to a particular embodiment of the turbine engine 1 according to the invention, the outlet of the regeneration counter-current air / mixture exchanger 30 comprises a regeneration exchanger outlet duct 84 in which circulates the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the expansion drive turbine 3, said duct 84 connecting said exchanger 30 with the inlet of a liquid water preheating / mixing exchanger 79 in which the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the expansion turbine 3 flows 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 said mixing / water exchanger 79. In addition, the regeneration exchanger outlet conduit 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 of the gas-vapor mixture in said duct 84, said flap 78 allowing the management computer of the turbine engine EMS 57 to orient all or part of said mixture first to said mixing / water exchanger 79 and then to the exhaust line outlet 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 62 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 centrifugation created for example by a helical shape or by tangential ducts that includes the interior of the separator-recuperator 40 said centrifugation generating a cyclone which projects said water 45 on the inner walls of said separator-recuperator which are connected to said tray 43 by one or more channels or orifices, while the gas-vapor mixture mainly freed from its liquid water 45 escapes through the center of said cyclone towards the exhaust line outlet 55. The condensate separator-recuperator 40 further comprises an internal separator-recuperator conduit of the condensates 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.

FIG. 6 illustrates the condensate separator-recuperator inner conduit 41 which contains an iron straw or labyrinthine structure 44 which retains or condenses suspended water in the form of droplets and / or vapor in the expelled gas-vapor mixture. by the turbocharger turbine 62 and / or the expansion drive turbine 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 up to the 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 able to be driven by an electric motor and consist of a hydraulic turbine, pistons, a membrane, or any other means of pumping known to those skilled in the art. It can be seen in FIG. 1 that the condensate recirculation duct 47 may comprise an intermediate condensate storage tank 48 for temporarily storing the liquid water 45, said intermediate reservoir 48 being able for example to consist of a plastic bladder that can not be removed. to be destroyed by the possible freezing of the liquid water 45 and allowing if necessary the addition of liquid water by an operator. The condensate drain pan 43 and / or the condensate recirculation duct 47 comprises a condensate filter 49 which can be static and consists of a filter element made of cloth, paper, foam or any other material known to the water. skilled in the art for its filtering properties and / or can be dynamic and operate a filtration by centrifugation or electrostatic, said filter 49 retaining in particular the particles that convey liquid water 45.

The regeneration-combustion channel 34 shown in FIG. 1 comprises an anti-NOx pre-combustion water injector 39 placed before the continuous combustion chamber 35 with respect to the direction of circulation of atmospheric air in said channel 34, said injector 39 being able to 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 carried out in the continuous combustion chamber 35 so that said combustion does not produce or few oxides d nitrogen, while said water 45 may in particular come from the condensate recovery tank 43. It can be seen in FIG. 1 that the gas-steam induction turbine driving duct 66 comprises an expansion turbine inlet valve 4 driven by the engine management computer of the turbine engine EMS 57 said valve 4 being able to close off said duct 66 and said valve 4 which can allow or prohibit the gas-vapor mixture to go from the regulating channel. combustion-nération 34 to the expansion turbine 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 closing an orifice or conduit 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, electropneumatic, electric, hydraulic or electro-hydraulic actuator. The expansion drive turbine 3 is mounted on the expansion drive turbine shaft 67 via a free-wheeling expansion turbine connection 5, said link 5 allowing said turbine 3 to rotate said shaft. 67, but not vice versa, said link being ratchet (s), ball (s), roller (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 permitting said turbine 3 to rotate at a pressure speed different from that of the shaft 67, said coupler being able to be an epicyclic gear while the clutch can in particular be driven by the management computer of the turbine engine EMS 57 by means of an electromechanical actuator, electro hydraulic or electropneumatic. FIG. 1 shows that the expansion turbine drive shaft 67 is connected to an electric turbine generator 11 by means of a mechanical transmission of generator 6, said generator 11 being able to produce electricity when it is driven in rotation 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 or continuous variable ratio, and can be hydraulic, electrical, pneumatic, and possibly consisting of a chain, a belt, rollers, a gear system, or any type 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 making it possible to prevent a radial force being exerted on the drive turbine shaft 67 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 secured to the planet carrier of said epicyclic train 7 while the crown of said train 7 is fixed and that the sun gear is integral with the drive turbine shaft expansion 67. Note that the electric turbine generator 11 is electrically connected to an electrochemical accumulator 10 and / or an electrostatic accumulator 69. Figure 1 shows that the conduit of blowing 25 comprises a start bypass air flap of the turbine engine 8 which can force all or part of the outgoing atmospheric air the air-to-gas exhaust cooler-condenser 16 to go towards the intake duct of the turbine engine 58 via a start bypass air channel of the turbine engine 65 while prohibiting access to the mouth of condensing cooling air exhaust 23 while a turbine engine starting obstruction 9 air shutter that includes said intake duct 58 prohibits said air to go up towards the turbine engine air inlet mouth 60 while forcing said air towards the inlet of the turbocharger compressor 61 and while preventing all or part of the atmospheric air from the turbine engine air intake mouth 60 from reaching the inlet of said compressor 61.

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 the gas-vapor mixture in said channel 34, said catalyst 53 completing the combustion of the fuel operated in the continuous combustion chamber 35 so as to avoid introducing gaseous pollutants at the inlet of the turbocharger turbine 62 and / or in the gas-steam intake duct 62. According to a variant not shown, the exhaust gas-steam exhaust gas exhaust duct 70 and / or the turbine engine gas-steam inlet duct The detent 66 may comprise a catalyst for post-treatment of the pollutants, the said catalyst completing - as previously - the combustion of the fuel previously operated in the combustion chamber. naked 35 so as to avoid expelling gaseous pollutants at the exit of the exhaust line 55. It will be noted, particularly in FIGS. 1, 4 and 5, that the regeneration-combustion channel 34 and / or the admission duct gas turbine engine of expansion turbine 66 and / or the gas-steam exhaust duct of driving turbine 70 and / or the air exchanger / regeneration countercurrent mixture 30 is coated with a material and / or internal and / or external heat-insulating structure 51 which retains the heat of atmospheric air and / or of the gas-vapor mixture circulating inside said members 34, 66, 70, 30.

The heat-insulating material and / or structure 51 can consist of rockwool, a double or multiple skin (s) metal (s) or not and said material 51 can create a space possibly filled with a weakly thermally conductive gas or partial or total vacuum, or thermal screen (s), these components possibly being kept at a distance from said members 34, 66, 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 turbine engine 1 according to the invention and be made of any other material and / or arrangement known to those skilled in the art and to retain heat.

FIG. 1 illustrates that the regeneration exchanger outlet duct 84 comprises a liquid water preheating / mixing exchanger 79 in which the gas-vapor mixture expelled by the turbocharger turbine 62 and / is circulated on the one hand; or the drive turbine 3 relaxation and secondly, the liquid water 45 before the latter is injected into the regeneration-combustion channel 34, said mixture heating said water 45 inside said exchanger / water 79 .

The direction of circulation of said mixture inside the exchanger 79 may be the opposite of that of the circulation of said water 45 in said exchanger 79 so that said mixture can yield to said water 45 as much heat as possible. 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 of the mixture. gas-vapor 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 exchanger / water mixture 79 and to the air-cooled air-cooled condenser / countercurrent gas 16 is directly to said cooler-condenser 16, said flap 78 may 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 number of impurities expelled into the condenser cooler. The air / gas exhaust against countercurrent 16 by means of cooling-condensation air blowing means 26, said impurities having been previously sucked by said means 26 at the same time as atmospheric air.

Figures 2 and 3 show the turbine engine 1 according to the invention which is installed in a motor vehicle 56 so as to ensure directly or indirectly the propulsion of said vehicle 56, the latter having a fuel tank 71 and a fuel pump 72 which feed fueling the continuous combustion fuel injector 36.

According to a particular embodiment, the turbine engine 1 according to the invention can also ensure the supply of electricity and / or heat of the accessories and equipment for safety, comfort, driving and management of said vehicle 56, while the vehicle automobile 56 may include external intakes of gas, fuel oil or any other fuel outlet and outlets of electricity output and hot air produced by said turbine engine 1 so that said vehicle 56 can serve as an autonomous group of production of electricity and heat for all domestic and / or industrial use.

Depending on the configuration chosen for producing the turbine engine 1 according to the invention, the drive turbine shaft 67 is connected to at least one wheel 73 that includes the motor vehicle 56 by mechanical transmission means, said means being a gearbox cooperating or not with a clutch and / or a differential gear, said gearbox 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 FIGS. 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 that the motor vehicle 56 comprises by means of a motor. In this context and according to this example, the engine-generator mechanical transmission 74 consists of a motor-generator epicyclic transmission gear train 75.

FIG. 1 shows that the blowing duct 25 comprises an air / water heat recovery heat exchanger 81 in which circulates, on the one hand, the atmospheric air expelled by the cooling-condensing air blowing means 26 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 of said 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 flap 80 placed upstream of the air / water heat exchanger 81 for residual heat recovery with respect to the direction of flow of the atmospheric air in said duct 25, said shutter 80 allowing the management computer of the turbine engine EMS 57 to direct all or part of said air first to said air / water heat exchanger 81 and then to the exhaust air outlet cooling-condensation 23 or 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 FIGS. 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 to transport heat from said heat exchanger 81 to 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 cooling 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 are coming out of said housing 50 which make it possible to connect at least the cooling-condensation air intake duct 64 and / or the blowing duct 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 turbine engine 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. regeneration-combustion 34 by the centrifugal compressor turbocharger 61. The heat source consists of a condenser that includes a heat pump that extracts heat from an environment, said heat pump extracting said heat from the ambient air , a stream or a soil and being known per se to those skilled in the art, being commonly used in various domestic or industrial heating systems.

The heat pump is rotated by the drive turbine shaft 67 directly or indirectly by means of any mechanical, electrical, hydraulic or pneumatic transmission device, variable or not and generally, known to the man of art.

The atmospheric air sucked via the turbine engine air intake port 60 by the centrifugal turbocharger compressor 61 is pre-cooled by an evaporator included in the heat pump. The atmospheric air sucked via the cooling-condensing air intake pipe 22 by the cooling-condensing air blowing means 26 is pre-cooled by an evaporator included in the heat pump. According to a particular configuration of the turbine engine 1 according to the invention, the drive turbine shaft 67 is driven in rotation by the drive turbine 3, said shaft can in turn rotate a turbine drive pinion 115 which drives in rotation a ring gear of multi-turbines 114 which can rotate a power output shaft of multi-turbines gear reducer 118. According to this principle, a single ring of multi-turbines gearbox 114 can be rotated by several turbines expansion motors 3 each driving said ring gear 114 via its turbine drive gear 115. According to another variant of this principle illustrated in FIGS. 8, 9 and 10, a plurality of multi-turbine gear reducers 114 may be mounted on the same shaft multi-turbine gear reducer power output 118 each ring 114 being then rotated by a single drive turbine drive FIG. 3 cooperates with its drive turbine shaft 67 and its turbine drive gear 115 so as to constitute, in these two cases, a multi-turbine group 126.

Whatever the configuration adopted, the different rotating elements that make up the multi-turbine group 126 - that is to say said turbines 3, said turbine shafts 67, said drive gears 115, said rings 114 or said output shaft of power 118 - may be carried by hydrodynamic, aerodynamic or magnetic bearings axial and / or radial, by roller or ball bearings of any type, or by any device known to those skilled in the art to ensure rotating and guiding said rotating elements with lower friction. It should 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 115 by means of a gasket. transmission that can be homokinetic or not, with concurrent or parallel axes, flexible or rigid, with or without slide, with gimbal, ball, tripod, based on a flexible intermediate piece of "Flector" type, or any other type known to those skilled in the art. The multi-turbine gear reducer output shaft 118 terminates with a power output epicyclic gear train 125.

In addition, the turbine drive pinion 115 is mounted on the expansion drive shaft 67 via a freewheel connection, said link enabling said shaft 67 to rotate said pinion gear 115, but not the opposite while according to an alternative not shown, said connection may consist of an electrically controlled clutch, said clutch being of any type known to those skilled in the art. As seen in FIG. 11, the multi-turbine gear ring 114 is mounted on the multi-turbine gearbox output shaft 118 via a gearbox crown gear 117 which allows said ring gear 114 to rotate said shaft 118, but not vice versa, whereas according to an alternative not shown, said free wheel 117 can be replaced by an electrically controlled clutch, said clutch being of any type known to man art. The turbine engine 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 that it sucks via the intake port of the engine. turbine engine air 60 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 whose centrifugal compressor turbocharger high-pressure The pressure 123 overcompresses the air expelled by the low pressure turbocharger centrifugal compressor 121 before expelling it in turn into the regeneration-combustion channel 34 when said compressor 123 is rotated by the high pressure turbocharger turbine 124 that comprises said high-pressure turbocharger 104, the output of the centrifugal compressor of tur low-pressure bocompressor 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 channel regeneration-combustion device 34 before expelling it at the inlet of the low-pressure turbocharger turbine 122 which over-relaxes said mixture before it is in turn expelled into the turbine-engine exhaust gas-steam exhaust pipe. relaxation 70.

Note that this configuration with two turbochargers 2 is available in three turbochargers 2 or more, the centrifugal compressors and turbines of each of the turbochargers 2 being interconnected in a similar manner, that is to say in this case that the output of each compressor is connected to the input of the next compressor in ascending order of absolute pressure except the last compressor whose output is connected with the regeneration-combustion channel 34 while the output of each turbine is connected with 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.

It will be noted that the inter-compressor linkage channel 116 comprises a turbocharger intercooler 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. 123. As shown in FIG. 8, the high-pressure turbocharger centrifugal compressor 123 comprises a high-pressure compressor bypass valve 105 which, when it is opened by the turbine engine management computer EMS 57, can direct a part of the air from the low pressure turbocharger centrifugal compressor 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 it is opened by the turbine engine management computer EMS 57, can direct part of a mixture vapor gas 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. 8 also illustrates that the intake duct of the turbine engine 58 comprises an electro-pneumatic starter 108 consisting of an electro-pneumatic starter centrifugal compressor 110 rotatable by an electro-pneumatic starter motor 109 so that said compressor 110 compresses atmospheric air from the air intake port of the turbine engine 60 at the inlet of the centrifugal turbocharger compressor 61.

In this context, the admission duct of the turbine engine 58 comprises an electropneumatic starting flap 111 controlled by the engine management computer EMS 57, said flap 111 enabling said computer 57 to force atmospheric air from the intake port of turbine engine air 60 to pass through the centrifugal compressor of electro-pneumatic starter 110 before joining the inlet of the centrifugal compressor of turbocharger 61 when said flap 111 is in a first position, or to pass through a bypass channel of the electropneumatic starter 120 before joining said input when said flap 111 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 expelled by the turbocharger turbine 62 and / or the expansion turbine engine 3 heating said water inside said exchanger 100 before said mixture exits through the exhaust line outlet 55 while said water is cooled inside the heating radiator 83 by said environment. In the latter context, the exhaust line 54 comprises an exhaust heat recovery flap 101 controlled by the engine management computer EMS 57, said flap 101 allowing said computer 57 to force the gas-vapor mixture expelled by the turbocharger turbine 62 and / or the expansion turbine engine 3 to pass through the air / water exhaust heat recovery 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. If the turbine engine 1 according to the invention is mounted on a motor vehicle 56, the regeneration countercurrent air / mixture exchanger 30 is arranged in a deformable structure constituting a shock absorber. OPERATION OF THE INVENTION: From the foregoing description, it will be understood - with reference to FIGS. 1 to 11 - the operation of the low-pressure internal combustion and / or external turbine engine with water vaporization and / or regeneration 1 according to the present invention which, according to a particular embodiment, is the following: In relation with FIG. 8, the turbine engine 1 according to the invention being mounted on a motor vehicle 56 (FIGS. 2 and 3) so as to ensure propulsion of said vehicle while said turbine engine 1 is stopped, the management computer of the turbine engine EMS 57 orients the electropneumatic starting flap 111 in order to put the intake duct of the turbine engine 58 in relation with the air intake port of the turbine engine 60 via the centrifugal compressor of the electro-pneumatic starter 110 and not via the bypass channel of the electro-pneumatic starter 120.

Then, the engine management computer of the EMS turbine 57 orders the electrical power supply of the electro-pneumatic starter motor 109 which rotates the centrifugal compressor of the electro-pneumatic starter 110, said current being supplied by the electrochemical accumulator 10. Thus driven, the electro-pneumatic starter centrifugal compressor 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 the air duct; admission 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 that comprises the high-pressure turbocharger 104 while that the bypass valve of high pressure compressor ion 105 is kept closed by the engine management computer of the EMS turbine engine 57. Then, said air rises in the regeneration countercurrent air / mixture heat exchanger 30 through the countercurrent regeneration heat exchanger internal conduit 31 and then opens in the regeneration-combustion channel 34 and then in the continuous combustion chamber 35 that comprises said channel 34. The management computer of the turbine engine EMS 57 then orders the injection of fuel into the continuous combustion chamber 35 by the fuel injector continuous combustion 36 said fuel from the fuel tank 71 and being fed toadjector 36 by the fuel pump 72. Simultaneously, said computer 57 orders the formation of one or more spark (s) between the electrodes of the spark plug 63 by applying a high voltage current to the terminals of said spark plug 63. Said sparks ignite the air / fuel mixture formed in the continuous combustion chamber 35, while the heat resulting from this ignition 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 turbine of Low-pressure turbocharger 122 of the low-pressure turbocharger 103 as shown in FIG. 8 then begin to relax the hot pressurized gases leaving the continuous combustion chamber 35. As a result, said turbines 124 and 122 respectively drive the centrifugal compressor in rotation. high-pressure turbocharger 123 of said turbocharger 104 and the low-pressure turbocharger centrifugal compressor 121 of said turbocharger 103, the high-pressure turbine bypass valve 106 and the high-pressure compressor bypass valve 105 being maintained closed by the EMS 57 turboshaft management computer. The work produced by the Said turbines 124 and 122 thus gradually increases the mass flow rate of fresh atmospheric air admitted into the continuous combustion chamber 35 and this, until the pressure in said chamber 35 has reached a value sufficient for the management calculator the turbine engine EMS 57 can stop supplying electrical power to the electro-pneumatic starter electric motor 109, and can orient the electropneumatic starting flap 111 so as to put the inlet duct of the turbine engine 58 directly in relation with the intake mouth of turbine engine air 60 via the bypass channel of the electro-pneumatic starter 120 and not via the centrifugal compressor of the electro-pneumatic 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 temperature it is necessary to complete the fuel combustion, the latter then becoming almost complete. Since the combustion temperature operated inside the continuous combustion chamber remains lower than that required for the massive production of the nitrogen oxides, the catalyst 53 remains a simple oxidation catalyst intended to post-treat only the hydrocarbons. unburned and carbon monoxide, excluding oxides of nitrogen. Thus, the thermodynamic cycle of the turbine engine 1 according to the invention exploits all the heat energy of the fuel since the pollutant post-treatment catalyst 53 is positioned upstream of any expansion turbine. As the combustion carried out in the continuous combustion chamber 35 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 liquid or gaseous fuel irrespective of the sensitivity to auto-ignition and the knocking propensity of said fuel.

As previously discussed, the high pressure turbocharger turbines 124 and low pressure turbocharger turbines 122 have begun to relax the pressurized hot gases that exit the continuous combustion chamber 35 from the pollutant aftertreatment catalyst 53. being produced in sufficient quantity, the management computer of the turbine engine EMS 57 orders the opening of the expansion turbine inlet valve 4 positioned at the inlet of the smallest expansion turbine 3 that includes the multi-turbine group 126, shown in FIGS. 8, 9 and 10. Said turbine 3 immediately starts rotating and produces mechanical work that it communicates with the multi-turbine gear reducer output shaft 118 as represented in FIGS. 8, 9, 10 and 11 successively via the expansion drive turbine shaft 67, the turbine drive gear 115, the turbine output gear ring 114, and the drive crown free wheel. reducing gear 117 with which said turbine 3 cooperates, said shaft 118 being mechanically connected to the wheels of the motor vehicle 56 via a continuously variable gearbox, not shown, via the power output epicyclic gear train 125 illustrated in FIGS. 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.

In parallel, it should be noted that the management computer of the turbine engine EMS 57 has opened the bypass valve of turbine generator 107 (FIG. 8) in order to supply hot gases under pressure to the turbine generator turbine 98 that the turbine generator 97 comprises, hot gases having previously been produced in the continuous combustion chamber 35. This has resulted in said turbine 98 rotating. The latter being integral with the turbine generator generator 99, said generator has also rotated and produced electricity to recharge the electrochemical accumulator 10, in addition to power accessories and safety equipment, comfort , driving and management that includes the motor vehicle 56. Having been relaxed by the smallest expansion turbine 3 that includes the multi-turbine group 126, the hot gases produced by the combustion of the fuel operated in the combustion chamber continues 35 have lost some of their heat and are expelled by said turbine 3. Said gas is then conveyed by the exhaust gas turbine exhaust gas exhaust pipe 70 from said turbine 3 to the air / mixture exchanger against regeneration stream 30 in which they enter and pass into the space between the outer casing regeneration exchanger against current 33 and the internal ducts of countercurrent regeneration exchanger 31 envelops said housing 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.

At the same time, the centrifugal high-pressure turbocharger compressor 123 and the low-pressure turbocharger centrifugal compressor 121 continue to circulate compressed atmospheric air within the counter-current regeneration heat exchanger internal ducts 31; the direction of flow of said air in said ducts 31 being opposite 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 ducts 31 in which it circulates, said hot gases progressively yielding a large part of their heat by circulating in the opposite direction between the countercurrent regeneration heat exchanger outer casing 33 and said internal ducts 31, and between them, this heat transfer constituting a thermal regeneration which improves very significantly makes it of the turbine engine 1 according to the invention. Note that according to this exemplary embodiment, the regeneration counterflow air / mixture exchanger 30 comprises a plurality of countercurrent regeneration exchanger internal conduits 31 which commonly offer a large contact surface with, on the one hand, atmospheric air expelled by the centrifugal compressor of high-pressure turbocharger 123 and the centrifugal compressor of low-pressure turbocharger 121 and with the other hand, the hot gases from the continuous combustion chamber 35. Said wide contact surface makes it possible to better warming said air and better cooling said gases during their journey inside the regeneration countercurrent air / mixture exchanger 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 the multiturbine group 126 while when said gases emerge from the exchanger air / mixture against regenerating current 30, their temperature is approximately equivalent to that of atmospheric air immediately after the latter has been expelled by the centrifugal compressor High-pressure turbocharger 123. It can also be noted that, mounted on a motor vehicle 56, the turbine engine 1 according to the invention has the advantage over an internal reciprocating engine of not requiring cooling radiators in front. front of said vehicle 56, which improves the coefficient of penetration into the air of the latter, the engine compartment can be completely closed. In addition, all the elements constituting said turbine engine 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 expansion turbines 3, the low-pressure turbocharger turbine 122 or the high-pressure turbocharger turbine 124 is released into the atmosphere via the exhaust line outlet 55 located at the rear of said vehicle 56. This release of heat creates a slight thrust that tends to significantly improve the coefficient of penetration into the air of said vehicle 56.

It is 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 intercooler Turbocharger 96 commonly constitutes a two-stage intermediate cooling compression system which also contributes to maximizing the energy efficiency of said turbine engine 1. According to this configuration, the atmospheric air is cooled in the turbocharger intercooler 96 after being pre-conditioned. compressed by means of the low-pressure turbocharger centrifugal compressor 121 and is supercharged by the centrifugal compressor of high-pressure turbocharger 123. This gives the compression system thus constituted a very high isentropic efficiency. In this context, it is noted that the heat dissipated by the turbocharger cooler 96 is not a net loss in that it is compensated by an increase in the heat fraction recovered by the air / mixture heat exchanger. Thus, the total energy balance of the system constituted by the turbine engine 1 according to the invention is greatly improved by the compression system of two stages with intermediate cooling and this, all the more important that said turbine engine is used at high power. It is also noted that, depending on the power to be delivered by the turbine engine 1 according to the invention, the management computer of the turbine engine EMS 57 can open or open the high-pressure turbine bypass valve 106 and / or the valve high-pressure compressor by-pass 105 so as to modify the compression ratio of the low-pressure turbocharger centrifugal compressor 121 relative to that of the high-pressure turbocharger centrifugal compressor 123. This additional adjustment also makes it possible to optimize the operation of the turbine engine 1 according to the invention, so as to maximize the efficiency of the latter. When the motor vehicle 56 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-turbine group 126 and which was used until then can be replaced by a drive turbine expansion 3 medium size or large (Figures 8, 9 and 1 0). To perform this replacement, the EMS 57 turbine engine management computer 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 turbine engine. medium or large expansion valve 3 to be used, so that 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 mechanical work that it produces to the multi-turbine gear reducer output shaft 118 as represented in FIGS. 8, 9, 10 and 11 successively via the transmission shaft. expansion turbine engine 67, the turbine drive pinion 115, the turbine output gear ring 114, and the gearbox crown gearwheel 117 with which cooperates said turbine 3.

Depending on the power demanded by the motor vehicle 56, several combinations of expansion turbine (s) 3 are possible. With regard to the configuration with 4 expansion turbines 3 as represented in FIGS. 8, 9 and 10, it will be noted that ten combinations of expansion turbines 3 are possible to produce work on the multi-reduction power output shaft. - Turbines 118. An additional combination consists in having no active expansion turbine 3, in which case only the turbines of the low-pressure turbocharger 103 and the high-pressure turbocharger 104 relax the hot gases leaving the continuous combustion chamber. 35, possibly in addition to the turbine generator turbine 98.

It should be noted that the unused expansion turbines 3 have their expansion turbine inlet valve 4 kept closed by the engine management computer EMS 57 and do not rotate because said turbines 3 are not rotated by the shaft multi-turbine gear reducer power output 118 because their multi-turbine gear ring 114 is equipped with a gear ring gear 117, or by the hot gases exiting the continuous combustion chamber 35 because the latter can not access said turbines 3, their expansion turbine inlet valve 4 being kept closed. Thus, unused expansion turbines 3 do not generate friction losses or pump losses that are unfavorable to the final energy efficiency of the turbine engine 1 according to the invention.

It is noted that, still with the objective of maximizing the efficiency of the turbine engine 1 according to the invention, the management computer of the turbine engine EMS 57 does not select the expansion turbine (s) 3 to relax the hot gases coming from the engine. continuous combustion chamber 35 on the sole criterion of the power that must produce the turbine engine 1 to move the motor vehicle 56. In fact, said computer 57 also selects the turbine (s) 3 on a criterion of better performance of said turbines 3 , by operating this or these latter (s) on its operating point (s) offering the highest energy efficiency.

Thus, for the same power available on the multi-turbine gear output shaft 118, several combinations of expansion turbine (s) 3 are possible, as well as several pressure levels and mass and volume flow rates of the gases leaving the the combustion chamber continues 35. Due to the different reduction ratio for each expansion turbine 3 that presents their torque crown of multi-turbine gear 114 / turbine driver pinion 115, said turbines 3 can operate simultaneously under the same differential pressure each retaining 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 power output epicyclic gear train 125 (FIG. Figures 9 and 10). Indeed, said box makes it possible to meet the power and speed requirements of the motor vehicle 56 regardless of the torque and the rotational speed printed on the multi-turbine gearbox output shaft 118 by the turbine or turbines ( 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. 35 by means of the continuous combustion fuel injector 36, in particular by regulating the fuel flow pumped by the fuel pump 72.

It will be noted that the pressure in the continuous combustion chamber 35 depends directly on the combination of expansion turbine (s) 3 on the one hand and the quantity of fuel injected into the continuous combustion chamber 35 on the other hand. in relation to the amount of atmospheric air introduced into said chamber 35 by the centrifugal low-pressure turbocharger compressor 121 and the high-pressure turbocharger compressor 123.

As seen previously, it is noted that the management computer of the turbine engine EMS 57 can act on the high-pressure compressor bypass valve 105 and / or the high-pressure turbine bypass valve 106 to maximize the efficiency of the engine. intermediate-stage two-stage compression system commonly constituted by the low-pressure turbocharger 103, the high-pressure turbocharger 104 and the turbocharger intercooler 96. As can easily be deduced from FIG. 8, in winter period or in cold weather, at the start of the turbine engine 1 according to the invention, the management computer of the EMS turbine engine 57 can derive the exhaust gas expelled at the outlet of the regeneration countercurrent air / mixture exchanger 30 by the low pressure turbocharger turbine 122 and / or the expansion turbine (s) 3 so as to direct said gases towards the air / water exhaust heat recovery heat exchanger 100 that comprises 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 computer 57 can direct the exhaust heat recovery flap 101 so that said gases can not go directly to the exhaust line exit 55 via the bypass channel of the exhaust heat recovery exchanger 127, but are forced to pass through said air / water exchanger 100. Thus, said exhaust gases can transfer their heat to the water circulated in said exchanger 100 by the exhaust heat recovery water pump 102, said heat then being again transferred to the air of the passenger compartment of the passengers of said vehicle 56 via the heating radiator 83. Once the desired temperature is reached for said passenger compartment, the management computer of the turbine engine EMS 57 can maintain said temperature by varying the amount of exhaust gas that passes through the exhaust heat recovery air / water heat exchanger 100 by means of the exhaust heat recovery flap 101, and / or by controlling the flow rate of the exhaust heat recovery water pump 102.

As an alternative to the operation that has just been described, the low-pressure internal combustion and / or external water vaporization and / or regeneration turbine engine 1 according to the invention may 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 turbine intake valves 4 and simultaneously directs the start bypass air flap of the turbine engine 8 and the starter air shutter of the turbine engine 9 so that the first flap 8 directs the atmospheric air from the centrifugal compressor of cooling-condensing air 27 to the intake duct of the turbine engine 58 via the start bypass air channel of the turbine engine 65 while preventing access to the exhaust air outlet of the engine oidissement-condensation 23, while the second component 9 prohibits said air back in the direction of the turbine engine air intake port 60, forcing said air to go to the turbocharger compressor 61. Then, the management computer of the EMS turbine engine 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 27 as shown in FIGS. 1, 2, 3 and 7 draws atmospheric air at room temperature respectively via the cooling-condensing air intake pipe 22, the intake duct of cooling-regeneration air 64 and the cooling-condensing air-blowing air filter 29 and then compressing said air in the counter-current cooler-condenser outer casing 19 via the insufflation duct 24 and the air intake port. cooling-regenerating air insufflation 20 so that said air rises inside said housing 19 to exit through the cooling-condensing air blower 21 and reaches the turbocharger compressor 61 via said blowing mouth 21, the blowing duct 25, the start bypass air channel of the turbine engine 65 and the intake duct of the turbine engine 58. Then, said air passes through the centrifugal compressor turbocharger 61 so as to lead into the regeneration-combustion channel 34 and then into the continuous combustion chamber 35 that includes said channel 34, after having passed through the regeneration countercurrent air / mixture exchanger 30 which also comprises said channel 34 from the inside of the countercurrent regeneration exchanger internal pipe 31 that comprises said exchanger 30. The engine management computer of the EMS turbine 57 then orders the injection of fuel into the continuous combustion chamber 35 by the injector fuel 36 from said fuel tank 71 and being conveyed to said injector 36 by the fuel pump 72, while said calculator 57 also orders the formation of one or more spark (s) between electrodes of the spark plug 63 by application of a high-voltage current to the terminals of said spark plug 63. The air / fuel mixture formed in the continuous combustion chamber 35 is thus fired by the one or more spark (s) while the heat emission which results from said firing causes the pressure of the gases contained in said chamber 35 to increase.

The turbocharger turbine 62 shown in FIGS. 1 and 7 then begins to relax the hot and pressurized gases exiting the continuous combustion chamber 35 so as to drive in rotation the centrifugal turbocharger compressor 61 which in turn increases the mass flow rate. Fresh atmospheric 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 timely manner the combustion of the fuel, the latter then becoming almost complete. The combustion temperature operated within the continuous combustion chamber remaining below the production threshold of the nitrogen oxides, said catalyst 53 is an oxidation catalyst intended to post-treat only the unburned hydrocarbons and the carbon monoxide, excluding oxides of nitrogen. Thus, the thermodynamic cycle of the turbine engine 1 according to the invention involves all the heat energy of the fuel because said catalyst 53 is positioned before the relaxation of the hot gases from 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 the latter also accommodates almost any liquid or gaseous fuel irrespective of the sensitivity to auto-ignition and the knocking propensity of said fuel. As previously discussed, the turbocharger turbine 62 began to relax the pressurized hot gases exiting the continuous combustion chamber 35 via the pollutant aftertreatment catalyst 53. Said gases being produced in sufficient quantity, the EMS calculator 57 can order the opening of the expansion turbine inlet valve 4 of the smallest expansion turbine 3 so that the latter produces mechanical work on the drive turbine shaft 67 relaxation, said shaft being mechanically connected to electric turbine generator 11 via the mechanical transmission of generator 6 constituted according to this example of a motor-generator epicyclic drive train 7. Thus rotated, the electric turbine generator 11 produces electricity which is either directly used to power the electric propulsion-regeneration motor-generator 68 e that the latter propels the motor vehicle 56 (Figures 2 and 3) to which it is connected, is stored in the electrochemical accumulator 10 and / or the electrostatic accumulator 69, or both at the same time. Note that the electricity produced by the turbine electric generator 11 can also be used to supply the cooling-condensing air compressor electric motor 28, as well as the accessories and equipment for safety, comfort, control and management. of the motor vehicle 56.

Note that the electricity stored in the electrochemical accumulator 10 is preferably used to ensure the operation in all-electric mode of the motor vehicle 56 during its movement over distances of a few meters - for example during congestion of traffic - while the electrostatic accumulator 69 is preferably used during the braking of said vehicle 56 to store electricity produced by the electric motor-generator of propulsion-regeneration 68 which operates in generator mode during said braking so as to recover the largest possible share the kinetic energy of said vehicle 56, said electricity being then reused to accelerate said vehicle 56 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 preferably effected via the electrochemical accumulator 10 with low power over long periods of time, whereas said smoothing is preferably effected via the electrostatic accumulator 69 for high powers over short periods. As the turbine engine 1 is sufficiently hot, the management computer of the turbine engine EMS 57 simultaneously orients the start bypass air flap of the turbine engine 8 and the starter air shutter of the turbine engine 9 so that the first flap 8 directs the atmospheric air from the centrifugal condensation-cooling air compressor 27 to the cooling-condensation air outlet 23 while preventing it from accessing the intake duct of the turbine engine 58 via the channel of the bypass air of the turbine engine 65, while the second flap 9 connects the turbine engine air intake port 60 with the turbocharger centrifugal compressor 61 via the turbine engine air intake filter 59 while by closing the bypass air channel 65, so as to allow said compressor 61 to draw atmospheric air via said mouth 60. After being relaxed by the power 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 gas-steam exhaust gasoline engine exhaust fan 70. Said gases then enter the regeneration countercurrent air / mixture exchanger 30 and more precisely are introduced into the space between the countercurrent regeneration exchanger outer casing 33 and the internal exchanger conduit. counter-current regeneration 31 enveloping said housing 33, said housing 33 and said duct 31 constituting said exchanger 30 mainly (Figure 4). At the same time, the turbocharger centrifugal compressor 61 continues to circulate atmospheric air inside the counter-current regeneration exchanger internal duct 31, the direction of circulation of said air in said duct 31 being the opposite of that of the circulation of said hot gases in the casing 33. As a result, the atmospheric air expelled by the centrifugal compressor turbocharger 61 heats up progressively in contact with the inner duct of countercurrent regeneration heat exchanger 31 in which it 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 inner duct 31, this heat transfer constituting a thermal regeneration which improves the efficiency of the turbine engine 1 according to the invention.

Note that according to this exemplary embodiment, the regeneration countercurrent air / mixture exchanger 30 comprises a plurality of countercurrent regeneration exchanger internal ducts 31 which have a daisy section 32 (FIG. wide contact surface simultaneously with the atmospheric air expelled by the centrifugal compressor turbocharger 61 and with the hot gases from the continuous combustion chamber 35 so as to better heat said air and to better cool said gas, 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 drive turbine 3 relaxation while when said gases emerge from the air / mixture heat exchanger against the current regeneration 30, their temperature is approximately equivalent to that of atmospheric air immediately. t after the latter has been expelled by the centrifugal turbocharger compressor 61.

To optimize the efficiency of the turbine engine 1 according to the invention and to make it possible to operate over a wide power range without exceeding the heat resistance limit of its components, the EMS 57 turbine engine management computer can trigger the circulation of liquid water 45 in the condenser-regenerator water circuit 89 that comprises the counter-current steam-regeneration condenser 87 illustrated in FIG. 7. For this, said computer 57 starts the condensate pump 46 so that the latter conveys the liquid water 45 to the condenser-regenerator countercurrent steam 87 via the condensate recirculation duct 47, said water 45 from the condensate recovery tank 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 being relaxed by said turbines 62, 3 flow simultaneously and in the opposite direction in the condenser-regenerator gas-vapor mixing circuit 88 that includes said condenser-regenerator 87 said gas yielding their heat to said water 45 so that 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 generated vapor then mixes with the hot gases from the continuous combustion chamber 35 via said catalyst 53. As a result, the steam is superheated and, by doing so, said vapor cools said hot gases so that the temperature of said gases becomes compatible with the thermomechanical resistance limit, in particular of the turbocharger turbine 62, the drive turbine 3, the gas-steam intake duct 62 and the expansion turbine inlet valve 4. either consecutively to 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 regeneration channel; combustion 34, a large volume flow rate of gas-vapor mixture is produced which is significantly greater than the volume flow rate of atmospheric air admitted p by the turbocharger centrifugal compressor 61 minus the gas-vapor mixture volume-flow rate passing through the turbocharger turbine 62. This differential volume-flow of pressurized gas-steam mixture can be expanded at relatively low temperature by the turbine engine 3, which further increases the amount of work that the latter can produce, without increasing the amount of fuel injected into the continuous combustion chamber 35, while protecting said turbine 3 from any excessive temperature.

It is noted that after being expanded in the expansion turbine 3, the gas-vapor mixture retains a residual heat which is largely recycled in the regeneration countercurrent air / mixture exchanger 30 for heating the expelled atmospheric air. by the centrifugal compressor of turbocharger 61, said mixture yielding a large part of said heat to said air so as to improve the efficiency of the turbine engine 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 counter-current steam condenser-regenerator 87. While passing through said condenser-regenerator 87 via said casing 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 can provide a large part of the heat required for said water 45 to vaporize. Said mixture thus leaves the condenser-regenerator of countercurrent steam 87 at a significantly reduced temperature. As can easily be deduced from FIG. 7, at the outlet of the countercurrent vapor regeneration condenser 87, the gas-vapor mixture is introduced into the countercurrent air / gas exhaust cooler-condenser 16 and above. particularly, inside the inner duct of the counter-current cooler-condenser 17, the schematic section of which is illustrated in FIG. 5. Simultaneously, the centrifugal cooling-condensation air compressor 27 continues to circulate atmospheric air in the external casing of counter-current cooler-condenser 19 and more precisely, between said casing 19 and said duct 17 which envelops said casing, 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 conduit 17. Thus, the gas-vapor mixture progressively gives up a significant portion of its residual heat to said air, so that when said mixture returns t of the air-to-gas exhaust air cooler / condenser 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 through 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 exhaust fan 70 out of the air-gas exhaust cooler / condenser 16 against a temperature close to that of the ambient atmospheric air. 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 condenser-regenerator countercurrent steam 87 condenses on the inner walls of said inner conduit 17. The liquid water 45 that results from this condensation flows along said inner conduit 17 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 turbine engine 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 there, aided by iron straw. or labyrinthine structure 44 that includes the internal condenser separator-recuperator conduit 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 turbine engine 1, so that said water is not carried by said mixture to the exit of the exhaust line 55 but stored in the condensate recovery tank 43. It is noted that besides retaining the residual liquid water droplets contained in the gas-vapor mixture, the iron straw or labyrinthine structure 44 also largely captures the residual particles of soot that can convey the said mixture, by agglutinating said particles around the wet metal fibers or surfaces of the iron straw or labyrinthine structure 44 said soot is then carried by the liquid water which flows by gravity and returns to the condensate recovery tank 43. following, said particles are - according to this particular embodiment of the turbine engine 1 according to the invention - retained by the condensate filter 49 so that it can be eliminated during the replacement of said filter 49 operated during the maintenance of said turbine engine 1. When the motor vehicle 56 (Figures 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 power turbine of trigger 3 previously used by the EMS 57 turbine engine management computer to drive the turbine electric generator 11 p This computer 57 could be replaced by a medium-sized expansion turbine 3 or by a large expansion turbine 3 (FIGS. 1 and 7). For this, said computer 57 can close the expansion turbine inlet valve 4 of the expansion turbine 3 to be no longer used, then open the valve 4 corresponding to the turbine 3 to be used, so that the mixture pressurized gas-vapor exiting the water vaporization chamber 37 is expanded through said turbine 3 to be used. It is noted that the unused expansion motor turbines 3 then rotate freely around the drive turbine shaft 67 on which they are mounted, without being driven by said shaft 67 due to the free-wheel drive of the expansion turbine 5 which connects said turbines 3 to said shaft 67.

Since the power of the expansion drive turbine 3 is greater, the management computer of the turbine engine EMS 57 orders the injection of more fuel into the continuous combustion chamber 35 by means of the continuous combustion fuel injector 36, in particular by adapting consequently, 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 turbocharger compressor 61 into the continuous combustion chamber 35 by modifying the turbocharger turbine power 62 via its variable geometry vanes 76. In addition, said calculator 57 can also increase the flow rate of liquid water 45 introduced into the countercurrent vapor regeneration condenser 87 to be vaporized therein. acting on the flow of the condensate pump 46. It is noted that according to a particular mode of use of the turbine engine 1 according to the inv In addition, several expansion motor turbines 3 can be used simultaneously to add their power, this being achieved by simultaneously opening the corresponding expansion turbine inlet valves 4 to said turbines 3 (FIGS. 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 countercurrent air / gas exhaust cooler / condenser 16 which can be reintroduced at the inlet of the centrifugal compressor of turbocharger 61 via the start bypass air flap of the turbine engine 8 and the flap d air starter obstruction of the turbine engine 9, so that said heat is not lost in the atmosphere. Combined with the low thermal inertia of said turbine engine 1, this allows the rapid rise in temperature of the latter.

As the turbine engine 1 is hot and the starting bypass air flaps of the turbine engine 8 and the starting obstruction of the turbine engine 9 are no longer in the starting position but in the operating position of said turbine engine 1, the residual heat of the engine air expelled from the cooling-condensation air outlet 23 is used to warm the passenger compartment of the motor vehicle 56 via the air / water heat recovery heat exchanger 81 shown in FIGS. 1, 2, 3 and 7 This is obtained by forcing the atmospheric air leaving the blowing duct 25 to pass into said exchanger 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 coolant circulating in said exchanger 81, said fluid then serving to heat the passenger compartment of said vehicle. hicule 56 by means of the heating radiator 83 shown in FIGS. 2 and 3. It will be noted that in FIG. 7 there is shown the counter-current vapor condenser-regenerator 87, whose operation has just been described, whereas in FIG. FIG. 1, the latter is replaced by a liquid water preheating mixture / water exchanger 79 which makes it possible to heat the liquid water 45 to a temperature just below its vaporization temperature before its injection in liquid form into a vaporization chamber water 37 by a post-combustion water injector 38. That the configuration adopted is that illustrated in Figure 1 or that illustrated in Figure 7, it is noted that the adjustment of the amount of heat transferred to the liquid water 45 by the mixture gas-steam can be set by the management computer of the turbine engine EMS 57 by means of the preheating flap and / or vaporization of liquid water 78 said flap for deriving all or part of said mixture outgoing of the regeneration countercurrent air / mixture exchanger 30 via the regeneration exchanger outlet duct 84 to either the liquid water preheating mixing / heating exchanger 79 or the countercurrent vapor regeneration condenser current 87 according to the configuration selected, said mixture then continuing its way via the countercurrent air / gas exhaust cooler-condenser 16 and the condensate separator-recuperator 40 to the exhaust line exit 55, or directly to said cooler-condenser 16 without passing through said exchanger 79 or condenser-regenerator 87. To optimize the efficiency of the turbine engine 1 as a function of the power required by the motor vehicle 56, the management computer of the turbine engine EMS 57 can thus act on several parameters among which the driving turbine (s) relaxation (s) 3 used (s) or said turbine (s) being selectable (s) via its (their) admission 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 notably regulated by the variable geometry vanes 76 that the turbine of turbocharger 62, the mass flow rate of fuel injected into the combustion chamber continues 35 by the continuous combustion fuel injector 36, the flow of liquid water 45 introduced into the internal condenser-regenerator pipe 90 said flow rate can be adjusted by the condensate pump 46, the amount of heat transferred to said water 45 in the condenser-regenerator countercurrent steam 87 said amount being adjustable by means of the preheating flap and / or vaporization of liquid water 78, the flow rate of air introduced into the outer casing of countercurrent cooler-condenser 19 by the centrifugal compressor of cooling-condensing air 27, said flow rate being adjusted by said computer 57 by modulating the power supply power of the electric motor of the cooling-condensation air compressor 28, or the storage or the removal of electricity in the electrochemical accumulator 10 and / or the electrostatic accumulator 69, in particular via an electrical and / or electronic power unit 82. It is also 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 regulate the quantity of fuel. atmospheric air at ambient temperature from the turbine engine air intake opening 60 introduced into the intake duct of the turbine engine 58, relative to the quantity of atmospheric air at higher temperature coming from the air blowing mouth; cooling-condensing air 21 introduced into said duct 58, said quantities being regulated by said computer 57 by means of the starter bypass air shutter of the turbine engine 8 and the shutter air shutter of the turbine engine 9. In particular, it can be observed that by thus adjusting the temperature of the air admitted by the centrifugal compressor of turbocharger 61, the EMS turbine engine management calculator 57 can adjust the mass of air expelled by the centrifugal turbocharger compressor 61 in the regeneration-combustion channel 34 for the same volume flow rate of air entering said compressor 61.

Given the silent nature of the turbine engine 1 according to the invention with respect to an internal combustion engine with alternative combustion, it is also possible - without damage to the comfort of the passengers of the motor vehicle 56 - to operate said turbine engine 1 by alternating sequences of operating at high power of a few seconds with others at very low power by storing-destocking at the same frequency of the energy in the electrostatic accumulator 69 so as to operate the various driving turbines 3 and / or the centrifugal compressor turbocharger 61 to the nearest of their best performance and reduce the amount of fuel converted 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 EMS 57 can optimize the choice of the turbocharger (s) 2 parallel to that of the driving turbine (s) of relaxation 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 again, it can drive the mechanical transmission of engine-generator 74 if the latter is variable so as to optimize the rotational speed of the electric motor-generator propulsion-regeneration 68 on a criterion of better performance of said motor-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 foregoing description has been given only by way of example and which in no way limits the scope of the invention which would not be overcome by replacing the details of execution described by any other equivalent.30

Claims (66)

REVENDICATIONS1. Low-pressure internal combustion and / or external combustion engine with water vaporization and / or regeneration (1) characterized in that it 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 turbocharger compressor (61) which comprises said turbocharger (2) with the inlet of a turbocharger turbine (62) which comprises 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 a turbine engine intake duct (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 regeneration countercurrent air / mixture exchanger (30) forming part of the regeneration-combustion channel (34) and in which circulates a gas-vapor mixture expelled by the turbocharger turbine (62); ) and / or the expansion turbine (3) the outlet of said turbines being connected to said exchanger (30) by a gas-steam exhaust duct for driving the expansion turbine (70) and on the other hand, atmospheric air discharged by the centrifugal turbocharger compressor (61) said mixture heating said air inside said exchanger (30) before emerging through an exhaust line outlet (55) via an exhaust line (54); At least one EMS turbine engine management calculator (57). 67 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 channel; combustion (34) which directly or indirectly connects the outlet of a turbocharger centrifugal compressor (61) which comprises said turbocharger (2) with the inlet of a turbocharger turbine (62) which comprises 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 a turbine engine intake duct (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 countercurrent steam regeneration condenser (87) in which circulates a gas-vapor mixture expelled by the turbocharger turbine (62) and / or the expansion turbine (3) 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), said mixture heating said water (45) inside said condenser-regenerator (87) before emerging through an exhaust line (55) via an exhaust line (54) while the inlet said condenser-regenerator (87) is connected to a gas-steam exhaust duct of the expansion turbine (70) in which circulates the gas-vapor mixture expelled by the turbocharger turbine (62) and / or the driving turbine of relaxation (3); - At least one management computer of the EMS turbine engine (57). 3. 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 water liquid (45) can be injected by a post-combustion water injector (38) so as to produce a gas-vapor mixture. 4. Turbomotor according to claim 1, characterized in that the outlet of the air / mixture regeneration counter-current exchanger (30) comprises a regeneration exchanger outlet duct (84) in which circulates the gas-gas mixture. vapor expelled by the turbocharger turbine (62) and / or the expansion turbine (3), said duct (84) connecting said exchanger (30) with the inlet of a countercurrent steam regeneration condenser ( 87) in which flows, 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) indoors said condenser-regenerator (87) through the inner walls of this rnier. 5. Turbomotor according to any one of claims 2 and 4, characterized in that the condenser-regenerator water circuit (89) consists of at least one internal condenser-regenerator duct (90) in which circulates in the reactor. 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 (62) and / or the turbine relaxation motor (3) circulates in said space, the direction of circulation of said mixture in said space being opposite to that of the circulation of said water (45) in said conduit (90). 6. 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 conduit d supply of post-combustion steam (94) which opens into said channel (34) after the continuous combustion chamber (35) with respect to the direction of circulation of the gas-vapor mixture and / or atmospheric air in said channel (34). 7. A turbine engine according to claim 6, characterized in that the postcombustion steam supply duct (94) comprises a postcombustion vapor inlet flap (95) which can close or open said duct (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 channel 10 of regeneration-combustion (34) via a conduit precombustion vapor feed (92) which opens into said channel (34) before the continuous combustion chamber (35) with respect to the direction of flow of the gas-vapor mixture and / or atmospheric air in said channel (34); ). 15 9. Turbomotor according to claim 8, characterized in that the precombustion steam supply duct (92) comprises a precombustion vapor inlet flap (93) which can close or open said duct (92). 10. Turbomotor according to claim 4, characterized in that the regeneration exchanger outlet duct (84) comprises a preheating flap and / or vaporization of liquid water (78) placed upstream of the steam condenser-regenerator. countercurrently (87) with respect to the direction of 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 mixing either first to said condenser-regenerator (87) and 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 in that the turbocharger turbine (62) comprises variable geometry vanes (76) which can direct a flow of gas-vapor mixture passing through said turbine (62). ) during operation of the turbine engine (1). 12. Turbomotor according to any one of claims 1 and 2, characterized in that the drive turbine expansion (3) comprises vanes with variable geometry (77) which can guide a flow of gas-vapor mixture passing through said turbine ( 3) during operation of the turbine engine (1). 13. Turbomotor according to claim 1, characterized in that the regeneration countercurrent air / mixture exchanger (30) comprises at least one countercurrent regeneration exchanger internal duct (31) in which the circulator circulates. 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 duct (31), said casing (33) leaving a space between itself and said inner duct (31) that it contains and / or adjoins while the gas-vapor mixture expelled by the turbocharger turbine (62) and / or the drive turbine (3) circulates in said space, the direction of circulation of said mixture in said space being opposite to that of the circulation of said air in said duct (31). A turbojet engine according to claim 13, characterized in that the countercurrent regeneration exchanger internal duct (31) has daisy fins or section (32) which provide a large contact surface simultaneously with the gas-mixture. vapor that circulates in the space between the countercurrent regeneration exchanger outer casing (33) and said duct (31), and with the atmospheric air circulating inside said duct (31). 15. Turbomotor according to claim 1, characterized in that the outlet of the regeneration countercurrent air / mixture exchanger (30) comprises a regeneration exchanger outlet duct (84) in which the gas-gas mixture circulates. vapor expelled by the turbocharger turbine (62) and / or the expansion turbine (3), said duct (84) connecting said exchanger (30) with the inlet of an air / gas exhaust aftercooler against current (16) in which flows on the one hand said gas-vapor mixture expelled by said turbocharger turbine (62) and / or said drive turbine (3) relaxation and on the other hand, atmospheric air expelled by means condensing-cooling air insufflation (26) after said air has been sucked into the atmosphere by said means (26) via a cooling-condensing air inlet (22) and via a conduit of cooling-condensing air intake (64) then has been blown into said cooler-condenser (16) via an insufflation duct (24) and a cooling-condensing air insufflation mouth (20) which comprises said cooler-condenser (16), said mixture heating said air to inside said cooler-condenser (16) before said air comes out of said cooler-condenser (16) through a cooling-condensing air exhaust port (23) via a cooling air blower- condensation (21) included in said cooler-condenser (16) and a blowing duct (25) which connects said blower mouth (21) to said exhaust mouth (23). 16. Turbomotor according to claim 2, characterized in that the outlet of the countercurrent steam regeneration condenser (87) 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 (87) with the inlet of a countercurrent air / gas exhaust aftercooler (16) in which flows on the one hand said gas-vapor mixture expelled by said turbocharger turbine (62) and / or said drive turbine (3) and on the other hand, an atmospheric air expelled by means of cooling-condensing air supply (26) after said air has been sucked into the atmosphere by said means (26) via a cooling-condensing air intake port (22) and via an air duct; cooling-condensing air intake (64) p Uis has been blown into said cooler-condenser (16) via an insufflation duct (24) and a cooling-condensing air insufflation port (20) included in said condenser-cooler (16), said warming-up mixture said air inside said cooler-condenser (16) before said air comes out of said cooler-condenser (16) through a cooling-condensing air exhaust port (23) via an air blower cooling-condensing system (21) comprising said cooler-condenser (16) and a blowing duct (25) which connects said blower (21) to said exhaust port (23). 17. Turbomotor according to any one of claims 15 and 16, characterized in that the countercurrent air / gas exhaust cooler-condenser (16) comprises at least one internal duct cooler-condenser (17). ) in which circulates the gas-vapor mixture expelled by the turbocharger turbine (62) and / or the expansion turbine (3), and at least one outer casing of the countercurrent cooler-condenser (19) which surrounds and / or abuts said inner duct (17), said casing (19) leaving a space between itself and said inner duct (17) that it contains and / or adjoins while the atmospheric air expelled by the blowing means d cooling-condensing air (26) circulates in said space, the direction of circulation of said air in said space being opposite to that of the circulation of said mixture in said duct (17). Turbomotor according to Claim 17, characterized in that the countercurrent internal cooler-condenser duct (17) has fins or daisy section (18) which provide a large contact surface simultaneously with the atmospheric air which circulates in the space between the outer casing of the counter-current cooler-condenser (19) and said duct (17), and with the gas-vapor mixture circulating inside said duct (17). 19.Turbomotor according to any one of claims 15 and 16, characterized in that the cooling-condensing air insufflation means (26) consist of a centrifugal compressor of cooling-condensation air (27) driven by a cooling-condensing air compressor electric motor (28). 20. Turbomotor according to claim 1, characterized in that the outlet of the regeneration countercurrent air / mixture exchanger (30) comprises a regeneration exchanger outlet duct (84) in which the gas-gas mixture circulates. vapor expelled by the turbocharger turbine (62) and / or the expansion turbine (3), said duct (84) connecting said exchanger (30) with the inlet of a liquid water preheating mixture / water exchanger (79) in which circulates on the one hand, the gas-vapor mixture expelled by the turbocharger turbine (62) and / or the expansion 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 said mixing / water exchanger (79). 21. Turbomotor according to claim 20, characterized in that the regeneration exchanger outlet duct (84) comprises a preheating flap and / or vaporization of liquid water (78) placed upstream of the exchanger mixture / water preheating liquid water (79) with respect to the flow direction of the gas-vapor mixture in said duct (84), said flap (78) enabling the EMS turbine engine management calculator (57) to orient all or part of said mixing either first to said mixing / water exchanger (79) and then to the exhaust line outlet (55) or directly to said outlet (55). 22. Turbomotor according to any one of claims 2, 3, 4 and 20, characterized in that the liquid water (45) comes from the gas-vapor mixture expelled by the turbocharger turbine (62) and / or the turbine engine detent (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 inner walls of said line (54) for storing it in a condensate collection tank (43). 23. Turbomotor 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. Turbomotor according to claim 23, characterized in that the internal condensate separator-recuperator duct (41) contains an iron straw or labyrinthine 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 (3) so that said water flows via the draining orifices of the condensates (42) to the tank condensate recovery system (43) rather than being carried by said gases to the exhaust line outlet (55). Turbomotor 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) via at least one condensate pump ( 46) via at least one condensate recirculation duct (47). 26. Turbomotor according to claim 25, characterized in that the condensate recirculation duct (47) comprises an intermediate condensate storage tank (48) for temporarily storing the liquid water (45). 27.Turbomotor according to any one of claims 22 and 25, characterized in that the condensate recovery tank (43) and / or the condensate recirculation duct (47) comprises a condensate filter (49). 28. Turbomotor according to any one of claims 1 and 2, characterized in that the regeneration-combustion channel (34) comprises an anti-NOx pre-combustion water injector (39) placed before the continuous combustion chamber (35). relative to the direction of circulation of atmospheric air in said channel (34) said injector (39) can inject liquid water (45) in said channel (34). 29. Turbomotor according to any one of claims 1 and 2, characterized in that the gas-steam inlet gas turbine engine (66) comprises an expansion turbine inlet valve (4) driven by the EMS turbine engine management calculator (57) said valve (4) being able to close off said duct (66). 30. Turbomotor according to any one of claims 1 and 2, characterized in that the driving motor expansion (3) is mounted on the drive turbine shaft expansion (67) via a link wheel- free of expansion turbine (5), said link (5) allowing said turbine (3) to rotate said shaft (67), but not vice versa. 31. Turbomotor according to any one of claims 1 and 2, characterized in that the drive turbine expansion (3) is mounted on the drive turbine shaft expansion (67) via a gear coupler and / or a clutch. 32. Turbomotor according to any one of claims 1 and 2, characterized in that the drive turbine shaft expansion (67) is connected to an electric turbine generator (11) by means of a mechanical degenerator transmission (6). ), said generator (11) being able to produce electricity when rotated by said shaft (67). 33. Turbomotor according to claim 32, characterized in that the mechanical generator transmission (6) consists of an epicyclic gear train generator (7). 34. A turbine engine according to claim 32, characterized in that the turbine electric generator (11) is electrically connected to an electrochemical accumulator (10) and / or to an electrostatic accumulator (69). 35. Turbomotor according to any one of claims 15 and 16, characterized in that the blowing duct (25) comprises a starting bypass air flap of the turbine engine (8) which can force all or part of the air atmospheric flow exiting the air-to-gas exhaust cooler-condenser (16) to go to the turbine engine intake duct (58) via a turbine engine start bypass air channel (65) while prohibiting it access to the condensing cooling air outlet (23) while a shutter air shutter of the turbine engine (9) that comprises said intake duct (58) prohibits said air from up towards the turbine engine air inlet (60) while forcing said air towards the inlet of the turbocharger compressor (61) and while prohibiting all or part of the atmospheric air from the mouth turbine engine air intake (60) to join the entr e said compressor (61). 36. A turbomachine according to any one of claims 1 and 2, characterized in that the regeneration-combustion channel (34) comprises a pollutant aftertreatment catalyst (53) placed after the continuous combustion chamber (35) by relative to the direction of circulation of the atmospheric air and / or the gas-vapor mixture in said channel (34). 37. A turbine engine according to any one of claims 1 and 2, characterized in that the gas-steam exhaust gas engine exhaust (70) and / or the gas-steam inlet gas turbine engine (66) comprises a catalyst for post-treatment of pollutants. 38. A turbomachine according to claim 1, characterized in that the regeneration-combustion channel (34) and / or the gas-steam induction turbine driving duct (66) and / or the exhaust gas turbine engine exhaust gas-exhaust duct (70) and / or the regeneration counter-current air / mixture heat exchanger (30) is coated with a material and / or heat-insulating structure (51) and / or external which retains the heat of the atmospheric air and / or the gas-vapor mixture circulating inside said organs (34, 66, 70, 30). 39. Turbomotor according to any one of claims 1 and 2, characterized in that the intake duct of the turbine engine (58) comprises a turbine engine intake air filter (59). 40.Turbomotor according to either one of Claims 15 and 16, characterized in that the cooling-condensation air intake duct (64) comprises a cooling-condensing air-blowing air filter ( 29). 41. A turbine engine according to any one of claims 1 and 2, characterized in that it is installed in a motor vehicle (56) so as to ensure directly or indirectly the propulsion of said vehicle (56), the latter having a reservoir of fuel (71) and a fuel pump (72) that supply fuel to the continuous combustion fuel injector (36). 42. Turbomotor according to claim 41, characterized in that the drive propeller shaft (67) is connected to at least one wheel (73) that comprises the motor vehicle (56) by mechanical transmission means. 43. A turbine engine according to claims 32 and 41, characterized in that the electric turbine generator (11) supplies electric power to at least one electric propulsion-regeneration motor-generator (68) connected to at least one wheel (73) that comprises the motor vehicle (56) via a mechanical motor-generator transmission (74). 44.Turbomotor according to claim 43, characterized in that the engine-generator mechanical transmission (74) consists of a motor-generator epicyclic transmission train (75). 45.Turbomotor according to any one of claims 15 and 16, characterized in that the blowing duct (25) comprises an air / water heat recovery heat exchanger (81) in which flows on the one hand, the air atmospheric expelled by the cooling-condensing air blowing means (26) and secondly, a coolant, said air heating said fluid inside said air / water exchanger (81). 46. A turbocharger according to claim 45, characterized in that the blowing duct (25) comprises a residual heat recovery flap (80) p laced in am am of the air / water heat recovery heat exchanger (81). with respect to the direction of 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 said air first to said exchanger air / water (81) then to the cooling-condensing air outlet (23) directly to said mouth (23). 47. A turbocharger according to claim 45, characterized in that the air / water heat recovery heat exchanger (81) is connected by at least one heating fluid duct (85) to a heating radiator (83). coolant circulating in said conduit (85). 48.Turbomotor according to either of Claims 19 and 40, characterized in that at least the cooling-condensing air blowing means (26) and at least the centrifugal cooling-condensing air compressor ( 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 condensing-cooling air insufflation (50) while connectors (86) extend from said housing (50) for connecting at least the cooling-condensing air intake duct (64) and / or the insufflation duct (24). 49. A turbine engine 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. 50. A turbine engine according to claim 49, characterized in that the heat source consists of a condenser that includes a heat pump that extracts heat from an environment. 51.Turbomotor according to claim 50, characterized in that the atmospheric air sucked via the turbine engine air inlet (60) by the centrifugal turbocharger compressor (61) is previously cooled by an evaporator that includes the pump heat. 52.Turbomotor according to any one of claims 15, 16 and 50, characterized in that the atmospheric air sucked via the cooling-condensation air inlet (22) by the air blowing means cooling-condensing system (26) is previously cooled by an evaporator included in the heat pump. 53. A turbocharger 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 expansion (3), said shaft can in turn rotating a turbine driver pinion (115) which rotates a multi-turbine gear ring gear (114) rotatable to a multi-turbine gear output shaft (118). 54.Turbomotor according to claim 53, characterized in that the drive turbine shaft (67) is connected at one of its ends to the drive turbine (3) and at its other end to the pinion gear. turbine attack (115) via a transmission joint. 55.Turbomotor according to claim 53, characterized in that the multi-turbine gear output shaft (118) terminates with a power output epicyclic gear (125). Turromotor according to Claim 53, characterized in that the turbine drive pinion (115) is mounted on the expansion drive shaft (67) via a free wheel connection, said link allowing said shaft (67) to rotate said pinion (115), but not vice versa. A turbine engine according to Claim 53, characterized in that the multi-turbine gear ring gear (114) is mounted on the multi-turbine gearbox output shaft (118) via a free wheel gearbox crown (117) which allows said ring gear (114) to rotate said shaft (118), but not vice versa. 58. A turbine engine 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 turbine engine air inlet (60) 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 (123) supercharger supercharges 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) of said turbo high-pressure compressor (104), the output 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); over-relaxes said mixture prior to expelling it in turn into the gas-steam exhaust gas engine (70). A turbojet engine according to claim 58, characterized in that the inter-compressor link channel (116) comprises a turbocharger intercooler (96) which cools the air expelled by the centrifugal low-pressure turbocharger compressor (121) before that said air is not compressed by the centrifugal compressor of high-pressure turbocharger (123). 60.Turbomotor according to Claim 58, characterized in that the high-pressure turbocharger centrifugal compressor (123) comprises a high-pressure compressor bypass valve (105) which when opened by the management computer of the EMS turbine engine (57), can direct part of the air from the low pressure turbocharger centrifugal compressor (121) directly to the regeneration-combustion channel (34) without passing through the centrifugal compressor of high pressure turbocharger ( 123). 61.Turbomotor according to claim 58, characterized in that the high-pressure turbocharger (104) comprises a high-pressure turbine bypass valve (106) which, when opened by the EMS turbine engine management computer. (57), can direct a portion 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 turbocharger turbine -pressure (124). 62. A turbine engine according to any one of claims 1 and 2, characterized in that the intake duct of the turbine engine (58) comprises an electropneumatic starter (108) consisting of a centrifugal compressor electropneumatic starter (110) can be put in rotation by an electric motor of the electropneumatic starter (109) so that said compressor (110) compresses the atmospheric air from the turbine engine air inlet (60) to the inlet of the centrifugal turbocharger compressor ( 61). 63. A turbine engine according to claim 62, characterized in that the intake duct of the turbine engine (58) comprises an electropneumatic starting flap (111) controlled by the engine management computer EMS turbine (57), said flap (111) allowing said computer (57) forcing atmospheric air from the turbine engine air intake port (60) to pass through the centrifugal electro-pneumatic starter compressor (110) before reaching the inlet of the centrifugal turbocharger compressor ( 61) 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. 64. A turbomachine according to any one of claims 1 and 2, characterized in that the exhaust line (54) comprises an air / water heat exchanger exhaust heat exchanger (100) in which circulates a water flowing also 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 said conduits (128) by an exhaust heat recovery water pump (102), the gas-vapor mixture expelled by the turbocharger turbine (62) and / or the turbine trigger motor (3) heating said water inside said exchanger (100) before said mixture exits through the exhaust line outlet (55) while said water is cooled inside the heating radiator ( 83) by said envi ronment. 65. A turbine engine according to claim 64, characterized in that the exhaust line (54) comprises an exhaust heat recovery flap (101) controlled by the EMS turbine engine management computer (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 air / water heat exchanger for exhaust heat recovery (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 exchanger (127) ) before joining said outlet (55) when said flap (101) is in a second position. 66. A turbine engine according to any one of claims 1 and 2, characterized in that the exchanger air / mixture against regenerating current (30) is arranged in a deformable structure constituting a shock absorber.