Abstract:
An object of the present invention is to provide a method and a system for implementing the method so as to alleviate the disadvantages of a reciprocating combustion engine and gas turbine in electric energy production. The invention is based on the idea of arranging a combustion chamber outside a gas turbine and providing compressed air to the combustion chamber in order to carry out a combustion process supplemented with high pressure steam pulses.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This is a national stage application filed under 35 USC 371 based on International Application No. PCT/FI2015/050007 filed Jan. 7, 2015 and claims priority under 35 USC 119 of Finnish Patent Application No. 20145010 filed Jan. 8, 2014. 
     STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT 
     Not Applicable. 
     THE NAMES OF THE PARTIES TO A JOINT RESEARCH AGREEMENT 
     Not Applicable. 
     INCORPORATION-BY-REFERENCE OF MATERIAL SUBMITTED ON A COMPACT DISC OR AS A TEXT FILE VIA THE OFFICE ELECTRONIC FILING SYSTEM (EFS-WEB) 
     Not Applicable 
     STATEMENT REGARDING PRIOR DISCLOSURES BY THE INVENTOR OR A JOINT INVENTOR 
     Not Applicable. 
     FIELD OF THE INVENTION 
     The present invention relates to a method of generating electricity and to electric generator system. 
     BACKGROUND OF THE INVENTION 
     A typical electric generator system of the prior art consists of a combustion engine, a fuel tank and a generator The combustion engine comprises a set of cylinders with a corresponding set of reciprocating pistons. One of the problems associated with the above arrangement is that the moving pistons and other moving parts have to be constantly lubricated with oil which has a significant impact on running temperature of the combustion engine. Consecutively, the running temperature is a significant factor when considering the coefficient of efficiency. The above mentioned engine withstands running temperature of less than 100 degrees Celsius without a significant deterioration of durability. The temperature is too low for vaporizing water and therefore it cannot be efficiently used for generating electricity i.e. it is just waste heat. 
     U.S. Pat. No. 2,095,984 (H. Holzwarth) discloses an explosion turbine plant. The explosion turbine plant is based on Humphrey process and it comprises an impulse rotor, pistonless explosion chambers for generating explosion gases and nozzles for expanding and directing the gases to a rotor being driven exclusively by intermittent puffs of said gases. 
     US patent application 2005/210879 (Murayama Motohide) discloses a pulse detonation engine system for driving a turbine. 
     Another typical generator system of the prior art consists of a gas turbine and a generator driven by a shaft of the gas turbine. The problem with gas turbines is that the combustor is in relatively low pressure because the gas turbine&#39;s combustor is practically an open space. The low pressure of the combustor significantly drops the coefficient of efficiency. In Holzwarth turbine plant the intermittent low pressure significantly drops the coefficient of efficiency. 
     BRIEF SUMMARY OF THE INVENTION 
     An object of the present invention is thus to provide a method and a system for implementing the method so as to alleviate the above disadvantages. 
     The invention is based on the idea of arranging a combustion chamber outside a gas turbine and providing compressed air to the combustion chamber in order to carry out a combustion process in controlled and optimal conditions and use residue heat from the process to produce steam which is then injected into the process in time-dependent manner. 
     An advantage of the method and system of the invention is that the conditions in the combustion chamber may be optimized for the combustion process which significantly increases overall efficiency of the system. The combustion chamber may have running temperature of hundreds of degrees Celsius and the pressure inside the compression chamber may be similar to the pressure in the end of compression stroke in a diesel cycle of a reciprocating combustion engines. Such a temperature increases the efficiency of the combustion process and the heat may be easily converted to electricity due to the high temperature. Time-dependent injection of the steam optimizes the use of steam and increases the overall efficiency. 
    
    
     
       BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS 
       In the following the invention will be described in greater detail by means of preferred embodiments with reference to the attached drawings, in which 
         FIG. 1  illustrates a first electric generator system according to an embodiment of the invention; 
         FIG. 2  illustrates a second electric generator system with steam circulation system according to an embodiment of the invention; 
         FIG. 3  illustrates a third electric generator system with an injector or ejector system according to an embodiment of the invention; 
         FIG. 4  illustrates a detail of a system having two combustion chambers; and 
         FIG. 5  illustrates the changes in pressure over time in a system according to an embodiment. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Referring to a simple example of  FIG. 1 , the electric generator system comprises a turbine  22  which is connection with a generator  26  and a compressor  24  axially or via a transmission  20 , The generator may also be axially connected to the turbine  22 . A rotor of the turbine  22  rotates when energy is fed to the turbine by means of fluid flowing through the turbine. Rotation of the turbine rotor drives the transmission  20  and the generator  26  and the compressor  24  which both are connected to the transmission. The turbine, the generator and the compressor may be connected to the transmission by means of drive shafts, axles or other suitable power transmission means. The arrangement converts the energy fed to the turbine  22  into electric energy output  99  with the generator  26  and into air pressure with the compressor  24  which compresses air for the combustion chamber  10 . In an embodiment the compressor  24  accumulates compressed air into an air tank  32  which then feeds the combustion chamber  10  with the compressed air accumulated in the air tank  32 . The compressor  24  is preferably a screw compressor which is highly efficient and able to provide high pressure to the combustion chamber  10  and to the air tank  32 . In an embodiment, the system comprises a second screw compressor connected in series with the first screw compressor  24  to provide even higher pressure to the air tank. In an embodiment, the system comprises a combination of an axial compressor  24 , such as a radial compressor and a screw compressor connected in series with the axial compressor  24  to provide air to the air tank. The compressor or the compressors are preferably arranged to build up pressure of over 2 MPa to the air tank. In an embodiment, the compressor or the compressors are arranged to build up pressure of over 3 MPa, 3.5 MPa or 4 MPa to the air tank. In an embodiment the compressor  24  may be driven with an electric motor. In an embodiment an intercooler can be provided between the series-connected first compressor and the second compressor to cool down the air between the compressors. The intercooler can then be used to generate steam which can be injected into the combustion chamber in a form of short, high pressure steam pulses between expansion phases of the combustion cycle. 
     The electric generator system also comprises a combustion chamber  10  which is arranged to receive compressed air from the compressor  24  or from the air tank  32  and fuel from a fuel tank  30  to initiate a combustion process. The compressed air is released from the air tank into the combustion chamber  10  by means of a controllable valve. The compressed air is preheated before entering the combustion chamber with a heat recovery unit  40  which conveys heat from the combustion chamber to the compressed air. The compressed air may also be preheated with other means, for example electrically with a resistor, when the system is started and the combustion chamber is at room temperature. Fuel is released or pumped from the fuel tank and injected into the combustion chamber. The fuel is preferably diesel or liquid natural gas (LNG). In an embodiment, the fuel is gasoline, natural gas, ethanol, biodiesel or a mixture of two or more the preceding fuels. In an embodiment, the fuel comprises hydrogen and carbon monoxide mixture which is a by-product of a soda recovery unit. In an embodiment water or steam may be injected with fuel into the combustion chamber. In an embodiment the fuel comprises coal dust or brown coal dust as such or mixed to natural gas, diesel or some other suitable fuel. 
     The fuel injected into the combustion chamber ignites due to high pressure and temperature inside the combustion chamber. The high pressure in the combustion chamber is arranged by releasing air from the air tank to the combustion chamber. In addition to the preheating, the heat of the combustion chamber heats up the released air inside the combustion chamber and builds up even higher pressure. The ignition may be triggered with an ignition coil, a glow plug, a pre-glow arrangement or a heater arrangement when the system is started and the combustion chamber has not yet reached its running temperature. The combustion process produces heat which heats up the combustion chamber and keeps the combustion process running by heating the fuel and the compressed air which are introduced into the combustion chamber. In an embodiment the ignition is also used during the combustion cycle after the system is started. In an embodiment the heat recovery unit  40  or other means of heat extraction is used to convey heat from the combustion chamber or combustion process to water or steam and generate high pressure steam. The high pressure steam is injected into the combustion chamber between the expansion phases of the combustion process. The steam is injected in short, high pressure pulses and the amount of pulses between two expansion phases may be for example 1 to 10, 2 to 8, 3 to 6 or some other amount, such as 4, 5, 7 or 8. 
     The combustion chamber  10  is preferably a hollow container with input means for fuel and compressed air and an output for combustion products i.e. exhaust gas. The inputs and the output are controllable and may be closed and opened in specific phases of a combustion cycle in order to build up pressure into the combustion chamber before the ignition of the fuel and to expel combustion products after the ignition. The combustion process in the combustion chamber is a cycle process which at least resembles Diesel cycle. Preheated compressed air from the air tank is introduced into the combustion chamber and fuel is injected into the combustion chamber until the air-fuel mixture ignites. The combustion of the air-fuel mixture expands its volume so the combustion products and the compressed air are expelled through the output when output valve is opened. Running speed of the combustion cycle is controlled by controlling the input and output valves. The running speed may be chosen freely within certain limits which are defined by the properties of the system. Such properties that may limit the running speed may be for example operation speed of the valves, the air pressure in the air tank, fuel type, etc. However, the running speed may be adjusted for optimal performance in each system because it is not restricted by moving pistons or similar physical limitations of moving mass. 
     The combustion chamber has preferably a simple form, most preferably a sphere or a cylinder, for enabling a quick, clean and complete combustion process. The simple form enables higher running temperatures which increases efficiency and decreases the amount of harmful particles and gases produced during the combustion process. The combustion chamber is arranged to function in high temperatures. In addition to the simple form, also the material of the combustion chamber has to withstand high temperatures without significant deterioration of performance or durability. The material of the combustion chamber may be ceramic, metal, alloy or preferably a combination of two or more materials. For example, the combustion chamber may comprise an alloy encasing with a ceramic inner coating. The alloy encasing withstands high pressure and strong forces while the ceramic inner coating withstands high surface temperatures. The construction of the combustion chamber is preferably arranged to withstand running temperature of 400 degrees of Celsius. In an embodiment the combustion chamber is arranged to withstand running temperature of 500, 600, 700 or 800 degrees of Celsius. The combustion chamber itself does not comprise any moving parts so it is relatively simple task to design the combustion chamber to withstand high temperatures. The moving parts that experience the highest thermal stress are the valves at the input and output ports of the combustion chamber. However, there are valves readily available that are designed to operate in these temperatures and therefore it should be relatively easy task to design and realize a durable valve system. 
     The output of the combustion chamber  10  leads a stream consisting of the combustion products and the compressed air from the combustion chamber into the turbine  22 . Due to the high pressure in the combustion chamber, the stream is expelled with high velocity when the output is opened. The expelling of the combustion products may be enhanced by having the output and the air input open simultaneously for a certain period of time. The turbine  22  comprises a rotor which rotates when the stream flows through the turbine. The rotating rotor drives the transmission  20  which in turn drives the generator  26  and the compressor  24  as stated earlier. The stream is guided to exhaust pipe  90  after the turbine and the exhaust gas  98  is released from the system. 
     The combustion chamber  10  is preferably a separate unit outside the turbine  22 . The combustion products expelled from the combustion chamber  10  are guided to the turbine  22  with a pipe, tube or some other channel connecting the combustion chamber  10  and the turbine  22 . In an embodiment the system comprises multiple combustion chambers. In that case each combustion chamber has a pipe, tube or some other channel connecting that combustion chamber to the turbine  22 . Preferably the multiple combustion chambers are arranged to expel their combustion products sequentially, i.e. not all at the same time, to provide a steadier flow of combustion products to the turbine  22 . In an embodiment, the steadier flow to turbine  22  is accomplished with short, high pressure steam pulses which are injected into the combustion chamber between the expansion phases of the combustion process. 
     In an embodiment the generator  26  feeds an electric storage system which comprises one or more capacitors, super capacitors or batteries for storing the electrical energy produced by the generator. This type of system can be used in vehicular applications for producing and storing electrical energy for electrical motors of a vehicle. 
     Now referring to  FIG. 2 , in an embodiment the electric generator system further comprises a steam circulation system. The steam circulation system comprises a steam tank  34 , a heat recovery unit  40 , a heat exchanger  42 , a condenser  50  and a water tank  36 . In an embodiment, the steam circulation system further comprises a second turbine. Water and steam circulates in the steam circulation system wherein the water is accumulated into the water tank  36  and the steam is accumulated into the steam tank  34 . In an embodiment the steam tank and the water tank is a single tank wherein the water is accumulated in the bottom of the tank and steam is accumulated on the top of the tank. The flowing of the steam is based on pressure differences within the system but it might be assisted with pumps or similar arrangement if necessary. The flowing is controlled by means of a number of valves which may be operated in controlled manner. 
     The steam is arranged to flow from the steam tank  34  to the heat recovery unit  40 . The heat recovery unit  40  is in thermal connection with the combustion chamber  10  so that the combustion chamber heats up the heat recovery unit in which the heat is conveyed to the steam flowing through the heat recovery unit. The heat recovery unit may be a separate unit having a thermal connection to the combustion chamber or it may be a fixed part of the combustion chamber. In an embodiment the heat recovery unit may even a pipework inside the combustion chamber or tubing on the surface of the combustion chamber. When the heat from the combustion chamber is conveyed to the steam flowing through the heat recovery unit, the steam rapidly heats up and expands. The steam flow is then directed to the turbine  22  wherein the steam flow rotates the rotor of the turbine  22  simultaneously with the combustion products and compressed air which are expelled from the combustion chamber  10  into the turbine  22 . 
     In an embodiment the heat recovery unit  40  is replaced with heat insulating material and time-dependent steam injections to the combustion chamber  10  maintain a stable running temperature of the combustion chamber. The time-dependent steam injections are preferably short, high pressure steam pulses injected into the combustion chamber between expansion phases of the combustion process. Said expansion phases may or may not be two consecutive expansion phases and steam may also be injected during the expansion phases. Time-dependence in connection with the combustion cycle and the flow of steam injection is adjusted within a combustion cycle. The injected high pressure steam pulses need only a reduced amount of steam due to their short pulse type length. After injection the steam exits the combustion chamber and enters into the turbine  22 . In an embodiment the pulses are 1-100 milliseconds long. In another embodiment the pulses are shorter than 100 ms, 50 ms, 20 ms or 10 ms. 
     In an embodiment the system comprises an additional burner for increasing the amount and/or the temperature of the steam in the system. The burner preferably uses the same type of fuel as the rest of the system. The fuel is burned in the burner for producing heat which then heats steam and/or the burning fuel heats water to produce steam. The additional burner can be used in systems which do not produce enough “waste heat” to produce an adequate amount of steam. The use of the additional burner ensures that a desired amount of steam in a desired temperature and pressure can be achieved. 
     In an embodiment, the steam is not directed into the same turbine  22  as the combustion products. In that embodiment the system comprises a second turbine which is dedicated to the steam stream while the (first) turbine  22  is dedicated to the stream of combustion products and compressed air. The stream of combustion products and compressed air may even be arranged to flow through an additional heat exchanger after the turbine  22  to heat up the steam stream before that stream enters the second turbine. The arrangement of the second turbine may be similar to known combined cycle power plants. 
     From the turbine a stream of steam, compressed air and combustion products flows through the heat exchanger  42  to the condenser  50  wherein the steam is condensed into water and the compressed air and the combustion products are guided out of the system through exhaust pipe  90 . In the embodiment of the second turbine the stream of combustion products and compressed air is arranged to flow through heat exchanger  42  directly to exhaust pipe and the steam stream is arranged to flow through the heat exchanger  42  and the condenser  50  to the water tank  36 . 
     The water condensed from the steam flows into the water tank  36  or is pumped in there. An ion exchanger  52  may be arranged between the condenser  50  and the water tank  36  for purifying the water before it enters the cycle again. The water tank  36  accumulates water which is then guided or pumped to the heat exchanger  42 . The heat exchanger conveys the heat from the stream of steam, compressed air and combustion products to the water flowing through the heat exchanger. The heat of the heat exchanger vaporizes the water into steam which is then guided to flow back into the steam tank  34 . From the steam tank  34  the high pressure steam can be released in short bursts to create short, high pressure pulses to the combustion chamber. 
       FIG. 3  illustrates an electric generator system which is otherwise similar to the system of  FIG. 2  except that the system further comprises a pump having a converging-diverging nozzle, for example an injector or ejector  12  for combining the stream of combustion products from the combustion chamber  10  and the steam from the heat recovery unit  40  or from the heat exchanger  42  wherein the ejector  12  guides the steam and combustion products into the turbine  22  for rotating the rotor of the turbine. The pump having a converging-diverging nozzle is called an ejector within the description but in an embodiment the pump can also be for example an injector, steam injector or steam ejector. The ejector  12  is between the turbine and the combustion chamber and its heat recovery unit. The combustion products and the compressed air are expelled into the ejector wherein the steam from the heat recovery unit is superheated by the hot matter from the combustion chamber. The superheating of the steam causes rapid expansion of the steam. The ejector  12  guides the stream of superheated steam, combustion products and compressed air into the turbine  22  wherein the stream rotates the rotor of the turbine. In an embodiment, short, high pressure steam pulses are injected into the ejector  12  from where the steam flows to the turbine and rotates the rotor or the turbine. 
     In an embodiment the system also comprises an adjustable nozzle and a valve in connection with the ejector  12  and the output of the combustion chamber  10  for adjusting the expelling of combustion products from the combustion chamber  10 . The nozzle has a certain design and a form which may be altered. The nozzle is within the ejector in a by-pass flow of the steam flowing from the heat recovery unit  40  to the turbine  22 . The form of the nozzle has a significant impact to the expelling of the combustion products from the combustion chamber when the valve in the output is open. By altering the form of the nozzle the expelling of the combustion products may be increased with help of the by-pass flow of the steam. 
     In an embodiment a portion of the combustion products, i.e. the exhaust gas, is guided to a low temperature/pressure region of the turbine  22  or to a low pressure turbine when the exhaust gas is exhaust from the combustion chamber. An ejector or ejectors ( 14   a ,  14   b ) can be omitted in this embodiment since the pressure in suction side is higher than the pressure in low temperature/pressure region. 
       FIG. 4  illustrates a detail of an embodiment of a combustion system having two combustion chambers  10   a  and  10   b  and an ejector  12 . The number of combustion chambers and ejectors is not limited to this example. Two combustion chambers and one ejector were chosen for this embodiment to give an example and represent the capabilities of the system. In an embodiment the electric combustion system has one, two, three, four or more combustion chambers and zero, one, two, three, four or more ejectors. In an embodiment the ejectors are not essential and the system can operate without a single ejector. 
     Each combustion chamber  10   a ,  10   b  comprises one or more inputs  101 ,  102  which can be controlled with or without input valves and one or more outputs  111 ,  112  which can be open or controlled with output valves. The inputs and the outputs may be controlled without valves by controlling the pressure of the inputs and outputs because gases tend to flow from a higher pressure region to a lower pressure region. In an embodiment at least some of the inputs and outputs are controlled with gas vibrations or oscillations instead of valves. In an embodiment each combustion chamber comprises an output controlled by a main exhaust valve  111 . In an embodiment each combustion chamber comprises two outputs, one output being controlled by a main exhaust valve  111  and one output being controlled by an auxiliary exhaust valve  112 . In an embodiment each combustion chamber comprises an open output which is not controlled by valve. In an embodiment each combustion chamber comprises an input  101  for fuel. In an embodiment each combustion chamber comprises inputs  101 ,  102  for fuel and pressurized air. In an embodiment each combustion chamber comprises inputs for fuel, pressurized air and steam. In an embodiment each combustion chamber comprises inputs for one or more of the following: fuel, pressurized air, steam and water. The steam may be produced at least partially using waste heat of the combustion process of the system. In an embodiment, the steam is injected in the form of short, high pressure steam pulses which are injected into the combustion chamber between the expansion phases of the combustion process. In this embodiment, the exhaust valves may be omitted as the pressure and temperature conditions of the combustion chamber are controlled with the steam pulse injections. In an embodiment, an ORC turbine or a Stirling engine can be used after the heat exchanger for cooling the exhaust gas and steam in a temperature range of about 200 degrees Celsius. 
     A combustion cycle in the system of  FIG. 4  could have the following steps. First pressurized air is fed to the combustion chambers  10   a ,  10   b  via air inputs  102  and fuel is fed to the combustion chambers  10   a ,  10   b  via fuel inputs  101 . The pressure in the combustion chambers is built up due to residue heat until the fuel in the combustion chambers ignites, for example at 2 to 3 MPa pressure, and produces combustion products and more pressure. The combustion products and the pressure are released to the ejector  12  by opening the main exhaust valve  111  between a combustion chamber  10   a  and the ejector  12 . In an embodiment the main exhaust valve is omitted and the combustion products move freely to the ejector  12 . In an embodiment a pressure wave supercharger replaces the main exhaust valve. Preferably the combustion cycles in each combustion chamber runs with a phase difference to the other combustion chambers so that the exhaust stream from the combustion chambers is steadier and less pulse-like. The combustion products flow from the combustion chamber to the ejector  12  and from ejector to turbine  22  through an output  113 . At the same time, liquid water and/or water vapour i.e. steam can be injected to the combustion chamber  10   a  via inputs and thus improving the ventilation of the combustion products out of the combustion chamber. Preferably steam is injected into the combustion chamber in short pulses with high steam pressure, for example ranging from several MPa to ten MPa. The injection of steam also helps to keep the pressure in an elevated level for an extended period of time as can be seen from  FIG. 5 . The injection of water and/or steam also lowers the temperature of the combustion chamber and facilitates temperature controlling. The injection also lowers the temperature of the main exhaust valve  111  which can extend the lifetime of the main exhaust valve  111 , When the pressure in the combustion chamber and in the ejector has dropped, for example to 4 to 5 MPa, the main exhaust valve  111  is closed, One or more of the valves may be electronically controlled for example via a control unit. In an embodiment the main exhaust valve  111  can be omitted when steam pulses are injected into the combustion chamber so the main exhaust output is constantly open. 
     In an embodiment including the main exhaust valve, after closing the main exhaust valve  111  the ejector can be sprayed with liquid water and/or water vapour i.e. steam via valve  103  which raise the pressure in the ejector  12 , for example to 6.5 Mpa. At a certain pressure in the ejector  12 , for example 6.5 MPa, the main exhaust valve  111  of the second combustion chamber  10   b  opens and releases combustion products to the ejector  12  and from there to the turbine  22 . At the same time the secondary exhaust valve  112  of the first combustion chamber  10   a  is kept open to ventilate the residue combustion products from the first combustion chamber  10   a . The ventilation can be enhanced by introducing pressurized air or steam via the inputs  101 ,  102  to the combustion chamber. The secondary exhaust valve  112  may lead the residue combustion products to the turbine  22  via one or more second ejectors  14   a ,  14   b . In an embodiment a single second ejector can comprise multiple inputs so that it can be used with two combustion chambers. Once the first combustion chamber  10   a  is ventilated and the pressure has dropped to a sufficiently low level, for example to 10, 2, 1, 0.5 or 0.2 MPa, the secondary exhaust valve  112  is closed and the next cycle of the combustion cycle can begin. 
     In an embodiment the second ejector  14   a ,  14   b  is arranged to receive motive steam or motive gas via input  114 . The motive gas is preferably pressurized water vapour for example in 6, 8 or 10 MPa pressure. The motive gas is directed through the second ejector  14   a ,  14   b  and discharged to the ejector  12  via valve  104 . When the motive gas goes through the second ejector it creates a suction effect drawing residue combustion products from a combustion chamber  10   a ,  10   b  when output valve  112  connecting the combustion chamber to the second ejector is open. The valve  104  is preferably a control valve. The throughput and/or opening direction of the valve  104  can be adjusted. In an embodiment all excess steam produced within the system can be fed to the turbine via the valve  104  and/or the second ejector  14   a ,  14   b.    
     In an embodiment a back flow from the turbine  22  using an intermediate steam tapping can be introduced to a third ejector. The back flow or the intermediate steam from the turbine may comprise steam or combustion products or a mixture of steam and combustion products which are introduce to the third ejector. The pressure of the intermediate steam at the third ejector is raised to a sufficient level by using valves and introducing gas such as water vapour to the third ejector. The steam and the combustion products increase the volume of the gas and decrease the temperature of the gas. The mixture of gases is introduced from the third ejector to the ejector  12  for example via the second ejector  14   a ,  14   b  and valve  104 , or to some other input valve of the system. In an embodiment, an output using an intermediate steam tapping can also be introduced right after the heat exchanger. 
     In an embodiment the turbine is arranged to rotate a by-pass fan in an aviation application for example replacing turbofan engines of commercial airplanes. In an embodiment the system comprises an oxygen tank connected to the combustion chamber and controlled with a valve. The combustion chamber can be used as a combustion chamber of rocket engine using rocket fuel from the fuel tank and oxygen from the atmosphere in the lower atmosphere so that the oxygen from the oxygen tank can be used in the upper atmosphere where the amount of oxygen is not sufficient for the combustion. 
       FIG. 5  illustrates time dependence of pressure in a system according to an embodiment. As the combustion cycle causes the pressure to change within the system in rather broad range, the turbine  22  does not receive optimal input unless the system in controlled in a time-dependent manner. Preferably all the inputs  101 ,  102 ,  103 ,  104  are controlled in time-dependent manner to keep the output  113  to the turbine in optimal pressure. Without any other time-dependent inputs than fuel and air, the output to the turbine would look like the curve  200  in  FIG. 5 . In the beginning of the combustion cycle the pressure builds up quickly peaking just before the main exhaust valve  111  is opened which quickly lowers the pressure as the combustion products flow through the turbine. Now if the combustion chamber is injected with liquid water and/or water vapour immediately after the main exhaust valve  111  is opened, the pressure would not fall as quickly because the liquid water would evaporate and the vapour would heat up due to residue heat of the combustion chamber and thus the injection would lessen the impact of opening the main exhaust valve  111 . In a similar manner, once the main exhaust valve  111  has been closed, the ejector can be sprayed with liquid water and/or water vapour i.e. steam via valve  103  which raise the pressure in the ejector  12  thus raising the output pressure to the turbine. The amount of liquid water, steam and air is controlled in a time-dependent manner in order to prevent the output to the turbine from dropping too much. Keeping the output to the turbine in an elevated and relatively constant level has a significant impact on the efficiency of the system. The turbine can be driven in optimal operating range most of the time with a relatively constant output whereas the turbine can not make the most out of sparse, short bursts. 
     The output to the turbine can be maintained in an elevated level with the injection of water, steam and air. This elevated level is illustrated with dashed line  201  in  FIG. 5 . However, a lot of steam and air is needed to maintain such a high pressure if the main exhaust valve is omitted or kept constantly open. If the injection of steam is in the form of very short and high pressure pulses, the main exhaust valve can be omitted thus simplifying the system and increasing its reliability. Curve  202  represents the pressure level during a combustion cycle when the injections are in the form of short steam pulses. The short steam pulses can maintain the average pressure at a high enough level that the main exhaust valve is not necessary. The short steam pulses may have peak pressure higher than the pressure pulse caused by the combustion. In an embodiment of e.g. two combustion chambers, short steam pulses can be fed to the system (e.g. to the first combustion chamber) after fuel is ignited and combustion products expelled from the first combustion chamber. The feeding of steam pulses can be continued while an exhaust valve of the second combustion chamber is closed. During that time any residue steam and combustion products are flushed from the second combustion chamber. The second combustion chamber is flushed with an input of compressed air which flows through e.g. a secondary exhaust valve  112  which then conveys the air and the residues to e.g. lower pressure turbine. After the flushing the second combustion chamber is filled with compressed air, fuel is injected to the second combustion chamber and the mixture ignites or is ignited. After the fuel is ignited and combustion products expelled from the second combustion chamber, short steam pulses can be fed to the system (e.g. to the second combustion chamber) while the exhaust valve of the first combustion chamber is closed, the first combustion chamber is flushed, filled and ignited like the second combustion chamber earlier, and so on. This enables high enough pressure for efficient use of the turbine throughout the process. 
     In an embodiment the pressure within the ejector  12  is kept always over for example 2, 3, 4 or 5 MPa. In an embodiment the amount of injected water, steam and air and point of time at which those are injected are determined based on measured quantities of the system, Such measured quantities can be for example temperature, pressure, humidity, gas composition, state of a valve or some other process quantity. Said quantities can be measured with e.g. sensors. In an embodiment the amount of injected water, steam and air and point of time at which those are injected are determined based on the phase of the combustion cycle. The time dependent injection of water and/or steam also increases the reliability of the turbine  22  by controlling the temperature of the gas which is introduced to the turbine  22 . The injection of water and steam lowers the average temperature of the gas introduced to the turbine and therefore it allows for higher pressure (and thus higher temperature) to be used in the combustion chamber. In an embodiment the time-dependent controlling of the inputs comprises creating steam or water pulses into the combustion chamber. 
     It will be obvious to a person skilled in the art that, as the technology advances, the inventive concept can be implemented in various ways. The invention and its embodiments are not limited to the examples described above but may vary within the scope of the claims. 
     SEQUENCE LISTING 
     Not Applicable