Abstract:
A combustion engine including a combustion chamber for combusting a fuel in an explosion cycle, and a separate pump chamber, connected with the combustion chamber and having a liquid inlet opening through which pump liquid flows into the pump chamber, and a liquid outlet opening, through which the pump liquid is expelled from the pump chamber under the action of combustion gas formed in an explosion cycle, wit the separate pump chamber being divided by at least one flexible diaphragm into a gas space and a liquid space so that the combustion gas, with flows out of the combustion chamber into the separate pump chamber, displaces the flexible membrane against the pump liquid.

Description:
RELATED APPLICATION 
     This application is a continuation of International Application PCT/AT99/00052, filed Mar. 1, 1999 and designating the United States. 
    
    
     BACKGROUND OF THE INVENTION 
     1. Field of Invention 
     The invention relates to an internal combustion engine including a combustion chamber for combusting a fuel in an explosion cycle, and a pump chamber which is connected with the combustion chamber and which is filled with a pump liquid through a liquid inlet opening, with the pump liquid being expelled from the liquid outlet opening under the action of the combustion gas formed in the explosion cycle. 
     2. Description of the Prior Art 
     A combustion engine of the type discussed above is known, for example, from the WO 98/01338. In the known internal combustion engine, a plurality of pump chambers, from which the pump liquid is expelled under the direct action of the inflowing combustion gas, is assigned to a single combustion chamber. 
     An object of the present invention is to improve the efficiency of the internal combustion engine of the type discussed above. 
     SUMMARY OF THE INVENTION 
     This and other objects of the present invention which will become apparent hereinafter, are achieved by dividing the pump chamber by a flexible diaphragm into a gas chamber and a liquid chamber. 
     Because of the division of the pump chamber with a flexible diaphragm into a gas space and a liquid space, there can be no mixing between the combustion gas and the pump liquid, which would have lead to a decrease in efficiency. Furthermore, the combustion gas is not divided among several pump chambers, as a result of which the overall construction can be simplified. 
     Under the action of the combustion gas flowing out of the combustion space, the diaphragm is displaced from its first operational position, in which the liquid chamber takes up essentially the whole volume of the pump chamber, into its second operational position, in which the gas space occupies essentially the whole volume of the pump chamber, with the pump liquid being forced out of the outlet opening of the space chamber. In a subsequent implosion cycle, a cooling liquid can be sprayed with a spraying device into the gas space of the pump chamber, as a result of which, because of the cooling of the hot combustion gas, a reduced pressure is produced in the pump chamber, whereby the diaphragm is pushed in the direction of its first operational position, and a new charge of pump liquid can be pumped into the liquid space of the pump chamber. Due to the spraying of cooling liquid into the pump chamber, the surface of the diaphragm, facing the gas space, can furthermore advantageously be wetted with cooling liquid, and a film, which protects the diaphragm against the high temperature of the combustion gas, can be formed. 
     The division of a pump chamber into the gas space and the liquid space can be accomplished by a single elastic diaphragm or by several elastic diaphragms, which are formed, for example, in the form of a tube. 
     Advantageously, the combustion chamber forms part of a circuit for the pump liquid and which also includes a turbine. In a particularly preferred embodiment, this turbine is a radial turbine. 
     Advantageously, an interim reservoir, which can be filled with pump liquid and emptied in the implosion cycle, is connected with the outlet of the turbine. Due to the use of such an interim reservoir, which in timed fashion can be filled with liquid or emptied of liquid, the total volume of pump liquid can be decreased significantly in contrast to the known oscillating liquid circuit disclosed in the WO 98/01338 and, accordingly, a significantly smaller, lighter and more rapidly reacting combustion engine can be produced. 
     Advantageously, the liquid flows essentially radially not only in the turbine, but also in the pump chamber and/or in the interim reservoir, as result of which a low overall height and, with that, a high, maximum attainable number of cycles of the engine can be obtained. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     Further advantages and details of the present invention will be explained in detail below with reference to the attached drawings, wherein 
     FIG. 1 shows a diagrammatic longitudinal sectional view of an inventive combustion engine; 
     FIG. 2 shows a cross-sectional view through the pump chamber along the line A—A in FIG. 1; 
     FIG. 3 shows an enlarged cross-sectional view of a portion of FIG. 1; 
     FIG. 4 shows a diagrammatic view of an inventive combustion engine as the driving mechanism for a boat; 
     FIG. 5 shows a diagrammatic cross-sectional view along the line C—C of FIG. 9 of an embodiment of an inventive combustion engine, for which a closed cycle is provided, during the explosion cycle; 
     FIG. 6 shows a diagrammatic view of the combustion engine shown in FIG. 5 during the implosion cycle; 
     FIG. 7 shows a diagrammatic view of the combustion engine shown in FIG. 5 in an idling condition; 
     FIG. 8 shows a diagrammatic view of the combustion engine of FIG. 5 when used as an engine brake; 
     FIG. 9 shows a cross-sectional view along line B—B in FIG. 5; 
     FIG. 10 shows a diagrammatic longitudinal cross-sectional view along line D—D of FIG.  11  through the central longitudinal axis of a second embodiment of an inventive combustion engine; 
     FIG. 11 shows a cross-sectional view along line E—E of FIG. 10; 
     FIG. 12 shows a cross-sectional view along line F—F of FIG. 10; 
     FIG. 13 shows a view illustrating the state of the combustion engine during the explosion cycle; 
     FIG. 14 shows a view illustrating the state of combustion engine during the implosion cycle; and 
     FIG. 15 shows a schematic view illustrating separation of gas and liquid spaces. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     A combustion engine according to the present invention, which shown in FIGS. 1 to  3 , includes a combustion chamber  2  which is filled with a working gas, which is formed in a carburetor  20  and is under atmospheric pressure in the combustion chamber  2 , to start the engine. For this purpose, a starting air pump  21 , which is activated only in the starting phase of the combustion engine, and a fuel pump  22 , which pumps fuel from a fuel tank  23 , are started up. For many carburetors, the fuel pump may be omitted, and the fuel is fed into the carburetor by creating an underpressure in the carburetor. 
     The working gas is ignited by an ignition rod  19 , which has several ignition points along its length, and an explosion cycle of the combustion engine is initiated. Such an ignition rod is formed as a central electrode surrounded by an insulation body and provided at its end projecting from the combustion chamber with a connector for connection with an ignition cable. The combustion gas, which is formed by the explosion and is under an initial overpressure of theoretically not more than 9 bar, closes the check valve  24  and flows into the pump chamber  1  and acts on a flexible diaphragm  3  which, at the start of the explosion cycle, is in the first operational position shown by a continuous line in FIG.  1 . The diaphragm  3  divides the interior space of the pump chamber into a gas space  30 , which is connected with the combustion chamber  2 , and a liquid space  31  (reference symbol  30  in FIG. 1 for the gas space refers to the position of the diaphragm  3  shown by the broken line). The diaphragm  3  is prestressed in the first operational position, which is drawn by a solid line in FIG.  1  and in which the liquid space  31  occupies essentially the whole volume of the pump chamber  1 . The diaphragm  3  is stretched by the combustion gas under pressure, is blown up in a balloon-like manner, and is displaced into the second operational position, which is shown by a broken line in FIG.  1  and in which the gas space  30  occupies the bulk of the volume of the pump chamber  1 . When the diaphragm  3  is displaced from the first operational position into the second operational position, the pump liquid, which fills the liquid space  31  of the pump chamber  1 , is forced out through the liquid outlet opening  36 , with the check valve  6 , which is disposed in the liquid outlet opening  36 , being opened and the check valve  8 , which is disposed in the liquid inlet opening  38 , being closed. 
     Advantageously, the volume of the combustion chamber  2  and the pump chamber  1  are dimensioned so that the pressure of the combustion gas, when it has pushed the diaphragm  3  into the second operational position, is reduced approximately to atmospheric pressure. The average pressure for the duration of the explosion cycle is, for example, 2 bar. 
     To provide for implosion cycle, the spray device  37 , which is fed with cooling liquid from the pump  16 , is activated by the control device  13 , and the cooling liquid is sprayed from the spray nozzles  7  into the gas space  30  of the pump chamber  1 . As a result of the spraying of the cooling liquid, the temperature and, with that, the pressure of the combustion gas are lowered suddenly, and a reduced pressure is established in the gas space  30  (the average pressure in the implosion cycle is approximately 0.6 bar, that is, an underpressure of 0.4 bar exists on average). This pressure difference provides for two processes. On one hand, the combustion chamber  2  is filled with fresh working gas, with a very good flushing of the spent combustion gas being achieved by the elongated shape of the combustion chamber. On the other hand, a pressure force is applied to the diaphragm  3  causing its movement from the second operational position in the direction of its first operational position. At the same time, the check valve  8 , which is located in the liquid inlet opening  38 , opens up, and the pump liquid is fed into the enlarged liquid space  31  of the pump chamber  1 . While the diaphragm  3  is moving from its second operational position in the direction of its first operational position, the pressure in the gas space  30  increases, until atmospheric pressure is reached once again. Since the check valve  9  was opened at the end of the explosion cycle, the check valve  49  opens up as soon as the pressure in the gas space  30  exceeds atmospheric pressure, and the combustion gas, together with the cooling liquid, can flow into the exhaust pipe  25 . The displacement of the diaphragm  3  by the still remaining distance to the first operational position takes place, on one hand, as a result of the already acquired kinetic energy of the inflowing pump liquid and, on the other hand, due to the inherent prestress of the diaphragm  3 , with the remaining combustion gas, as well as the cooling liquid being conveyed into the exhaust pipe  25 . In the exhaust pipe  25 , a cooler  18  is provided, which acts as a trap for the cooling liquid, which is accumulated in the reservoir  15  mounted at the bottom of the cooler  18 , while the combustion gas flows out of the exhaust  35 . 
     Consequently, the shut-off valve  9  is closed by the control device  13  over a hydraulic line  34 , and an ignition pulse is communicated by the control device  13  to the ignition rod  19  for initiation of a further explosion cycle. Instead of being controlled hydraulically, the shut-off valve  9  can also be controlled in a different manner, for example, pneumatically. 
     The check valve  8  in the liquid inlet opening  38  is formed by a series of rubber-like, flexible tapes  11 , which overlap in shingle fashion, are stretched transversely over the inlet opening, and are connected at their narrow lateral ends firmly with the pump chamber  1 . During the explosion cycle, the tapes  11  are pressed against one another and against the external collection grid  12 . On the other hand, during the implosion cycle, the tapes rise up scale-like in the direction of the interior of the pump chamber  1 , as shown by the broken line in FIG.  3  and open the liquid inlet opening  38 . As a result of their elastic properties, the tapes  11  are pretensioned in the closed position of the check valve  8 . 
     The check valve  6  in the liquid opening outlet  36  is constructed in an analogous manner. In this case, the collection grid is disposed internally and the flexible tapes straighten up in the direction of the outside of the pump chamber when the valve  6  is opened. 
     Because of the wedge-like shape of the pump chamber  1 , which enlarges from the region, at which the combustion chamber  2  is disposed, up to the outlet opening  6 , the pump liquid is displaced from the liquid space  31  by being squeezed through the outlet opening  36 , starting from the tip of the wedge, with liquid inclusions being avoided. Likewise, in the implosion cycle, gas inclusions in the gas space  30  of the pump chamber  1  are avoided because of a similar squeezing from the wedge tip. 
     The diaphragm  3  is formed of a rubber-elastic material with sufficient resistance to mechanical and thermal stresses. For example, temperature-resistant silicone mixtures are suitable for this purpose. The cooling liquid, sprayed in during the implosion cycle, preferably sprays the entire surface of the diaphragm  3 , facing the gas space. By these means, a moisture film is formed as protection against high temperatures of the combustion gases flowing in during the next explosion cycle. 
     The combustion chamber flow consists of a material having low thermal conductivity, and the walls of the combustion chamber  2  are cooled only to an extent, by the emission of heat to the environment, which prevents the self-ignition temperature of the working gas in the combustion chamber  2  from being reached. Due to this increased temperature of the walls of the combustion chamber, the carbon monoxide emission from the combustion engine is decreased. 
     As fuels, hydrogen, methanol, ethanol, gasoline (without antiknock additives such as octane, etc.), other combustible gases and basically, also diesel fuel (which is pre-heated), can be considered. The control device  13  comprises an ignition coil and a contact breaker, which specify the ignition cycle, which can be adjusted by the power regulator  17 . For example, a cycle number of 50 cycles per second or 100 cycles per second can be specified. 
     In FIG. 4, the attachment of an inventive combustion engine to a boat  44 , as the driving mechanism for the latter, is shown diagrammatically. In this case, water is used as the pump liquid and as the cooling liquid. The cooling liquid cooler and the cooling liquid trap in the exhaust pipe, as well as the reservoir for the cooling liquid can be omitted. The combustion engine is mounted on the boat in such a manner, that the liquid inlet opening  38  into the pump chamber forms an angle 45 of about 90° with the water flowing by, as a result of which a banking-up pressure, harmful to the efficiency, cannot build up at the liquid inlet opening. Advantageously, an injector pump, which is not shown in FIG. 4, is connected downstream from the combustion engine in order to convert the velocity of the water, flowing out of the outlet opening, into driving pressure. 
     A further embodiment of the inventive combustion engine is shown in FIGS. 5 to  9 , in which similar parts have been designated with the same reference numbers. In the embodiment shown in FIGS. 5-9, the pump chamber  1  is disposed in a closed liquid circuit, which drives a multi-step turbine  134 , which comprises rotors  135  stators  136 . The turbine  134 , disposed in the turbine housing  145 , is connected rigidly with a shaft  137 , from which a torque can be tapped. The blade angle of the turbine can be changed in a known manner over a control shaft  138  and a control device  139 . 
     The difference between pump chamber  1  of the embodiment shown in FIGS. 5-9 and that shown in FIGS. 1 to  4  consists in that instead of a check valve, a controllable inlet valve  108  is disposed in the liquid inlet opening and is actuated by the control device  13 , as it will be described below. 
     FIG. 5 shows the state of the combustion engine at the end of the explosion cycle, the flow of pump liquid being shown with arrows  151 . At the beginning of the explosion cycle, the controllable inlet valve  108  is closed by the control device  13 . The combustion gas, flowing out of the combustion chamber  2 , acts on the diaphragm  3  and displaces it from its first operational position in the direction of its second operational position, with pump liquid being forced out of the check valve  6  into the liquid outlet opening of the pump chamber  1 . The pump liquid reaches the turbine  134  through the turbine inlet  150 , drives the turbine  134 , and emerges from the turbine outlet  149 . 
     At the start of the explosion cycle, the inlet valve  131  of the interim reservoir  130  is opened by the control device  13 , so that the pump liquid, which has passed through the turbine  134 , can flow into the interim reservoir  130 . Since the interim reservoir  130 , which is largely empty at the start of the explosion cycle, also has flexible walls  148 , its volume is increased. The check valve  132  at the outlet of the interim reservoir  130  remains closed due to the pressure of the liquid flowing out of the pump chamber  1 . In the state, shown in FIG. 5, the interim reservoir  130  has already expanded approximately to its maximum volume, which is reached at the end of the explosion cycle. 
     At the very end of the explosion cycle, when the diaphragm  3  has reached its second working position, in which the gas space  30  essentially occupies the whole volume of the pump chamber, the inlet valve  131  of the interim reservoir  130  is closed, and the inlet valve  108  of the pump chamber  1  is open. Cooling liquid is sprayed into the gas space  30  by the spraying device  37 , as a result of which the implosion cycle is initiated. Because of the reduced pressure developing in the pump chamber  1 , initially the check valve  6  in the liquid outlet opening of the pump chamber  1  is closed. Furthermore, the check valve  132  in the outlet of the interim reservoir  130  is opened and the pump liquid, stored in the interim reservoir  130 , can flow preferably completely out of this interim reservoir  130  and, through the turbine inlet  150 , the turbine  134 , the turbine outlet  149 , the turbine discharge chamber  140 , and the inlet valve  108 , into the liquid space  31  of the pump chamber  1 . 
     In FIG. 6, the state of the combustion engine at the end of the implosion cycle is shown. The interim reservoir  130  has already been emptied and the diaphragm  3  has been pushed back by a substantial amount in the direction of its first operational position. When the pressure in the gas space  30  increases above atmospheric pressure, the check valve  47  opens up and the remainder of the combustion gas can flow out of the gas space  30  of the pump chamber  1  (the check valve  9  has been open since the start of the implosion cycle). 
     Since the average pressure difference resulting from the explosion pressure in the explosion phase is larger than the pressure difference due to the implosion pressure in the implosion phase (for example, 2.5 bar average overpressure in the explosion phase, 0.4 bar average underpressure in the implosion phase), the liquid outlet opening of the pump chamber is larger and, for the pressure ratio given, preferably almost twice as large as the outlet opening of the interim reservoir, as a result of which the discharging rates are matched to one another. 
     In FIG. 7, the idling state of the combustion engine is shown. The idling state is a state when there is no further explosion cycle at the end of the implosion cycle, the inlet valve  108  remains open and the inlet valve  131  remains closed. The check valve  106  opens up and the pump liquid flows through the turbine  134  and the pump chamber  1  as if they were a bypass. 
     Furthermore, the blade angle of the turbine  134  can be changed so far that the direction of rotation of the turbine  134  is reversed while the direction of flow of the liquid remains the same. A reversing gear can be realized in this manner without an additional transmission. 
     In order to provide an engine brake, the function of which is explained with reference to FIG. 8, the liquid circuit has a further branch  143 , which connects the turbine outlet  149  with the turbine inlet  150  and which lies parallel to the branch in which the pump chamber  1  is disposed. For starting the engine brake, the inlet valves  131  and  108  are closed. The pump liquid flows from the turbine outlet  149  to the check valve  141  and is throttled in the throttle  142 , becoming hotter in the process. Over the cooler  144 , it returns to the main circuit and to the turbine inlet  150 . Instead of or in addition to the throttle  142 , a generator could also be provided for generating electrical energy. 
     It can be seen from the view shown in FIG. 9 that, in the case of the embodiment shown, several pump chambers and several interim reservoirs are connected parallel to one another, the explosion cycles and the implosion cycles of the pump chambers as well as the inlet valves of the pump chambers and the interim reservoirs being synchronized. 
     In the case of a practical realization of the invention, it was possible to attain an output of 30 horsepower in the case of a pump chamber volume of 1 L, with the real efficiency η-eff being 0.46. 
     Another, particularly preferred embodiment of the present invention is shown in FIGS. 10 to  14 . 
     In order to start this combustion engine, a combustion chamber  202  is filled once again with a working gas which is formed in a carburetor  220  and is essentially at atmospheric pressure in the combustion chamber  202 . For this purpose, a starting air pump  221 , which is activated only in the starting phase of the combustion engine, is actuated. Most fuels do not require their own fuel pump for pumping the fuel contained in the fuel tank  223 . Either the fuel is a gas, which is anyhow under pressure, or the fuel is pumped as a result of the underpressure in the carburetor  220 . 
     The working gas is ignited over an ignition rod  209 , which has several ignition points along its length, and an explosion cycle is initiated in the combustion engine. The combustion gas, formed by the explosion and under pressure, closes the check valve  224  and flows into the pump chamber  201 . 
     The pump chamber  201  has a shape, which is essentially rotationally symmetrical, and the combustion chamber  202 , which also has a rotationally symmetrically shape, is disposed centrally at the pump chamber  201  so that its longitudinal axis coincides with the longitudinal axis of the pump chamber  201 . Furthermore, combustion chamber  202  is connected with pump chamber  201  over several combustion gas inlet openings  250  of the pump chamber  201 . 
     In the pump character  201 , several flexible, elastic tubular diaphragms  203  are provided. The tubular diaphragm  203  in each case connects a combustion gas inlet opening  250  with one of the combustion gas outlet openings  239 . The tubular diaphragms  203  are disposed radially, in spoke fashion, in the pump chamber  201  and divide the pump chamber  201  into a liquid space  231  and gas space  230 , which is formed by the interior spaces of the tubes; 
     In the embodiment of FIGS. 10-14, the liquid space  231  is separated from the gas space  230  by flexible tubes that form the diaphragm  203 . The tubes extend between the combustion gas inlet  250  and the combustion gas outlets  239 . The inner space of the tubes, forms the gas space  230 , and the space outside of the tubes forms the liquid space  231  (FIG.  15 ). FIG. 11 shows a plan view of inwardly located positions of the radially extending tubes which for the diaphragm  203 . The outwardly extending portions of the tubes are shown with dash lines. FIG. 10 shows a cross-section along line D—D in FIG.  11 . Viewed from below, the tube is cut to form left and right portions. In the rear, viewed from below, part of the FIG. 10, a side view of two tubes is shown. 
     At the beginning of the explosion cycle, the combustion gas outlet valves  209  are closed, and the valve disk  273  is in its lower end position in which it closes off the liquid inlet opening  252  into the pump chamber  201 , as shown in FIG.  13 . Furthermore, at the beginning of the explosion cycle, the tubular elastic diaphragms  203  are emptied, and the liquid space  231 , which is filled with pump liquid, takes up essentially the whole volume of the pump chamber  201 . 
     The combustion gas, expanding from the combustion chamber  202 , fills the tubular elastic diaphragms  203  in the pump chamber  201  and, as a result, forces the pump liquid out of the liquid space  231  through the liquid outlet openings  236  of the pump chamber  201 , which simultaneously form liquid inlet openings  236  for the turbine  260 . Due to the pressure of the liquid flowing in, the lip  206  is pressed upward and, closes the liquid outlet openings  231  from the interim reservoir  230 , which simultaneously form further liquid inlet openings into the turbine  260 . 
     The turbine  260  is a radial turbine (in the form of a Francis turbine), in which the liquid flows radially through the turbine rotor. The turbine housing has disk-shaped, outwardly curved lower and upper housing parts  261 ,  262 . As seen radially from the outside in, the lower and upper parts of the housing  261 ,  262  in each case have a ring of inlet openings  236 ,  237 , an inlet vane ring  263 ,  264 , a free space for the turbine rotors, an outlet vane ring  265 ,  266 , and a central opening. The turbine rotor is formed by a turbine blade ring, which is fastened to an axially centered disk  268 , which is rigidly connected with a squirrel cage rotor  269 . The squirrel cage rotor  269  has a plurality of axially aligned rods  270 , which are disposed circularly about the longitudinal axis of the machine, and is mounted rotatably at the upper and lower parts of the housing  261 ,  262  in radial bearings  271 ,  272 . Within the squirrel cage rotor  269 , a valve disk  273  is disposed, which accommodates the rods  270  in notches  274  at its edge (see FIG.  12 ). By these means, the valve disk  273  is rotationally locked with the squirrel cage rotor  269 , but can be displaced axially with respect to the squirrel cage rotor  269 . In the lower end position in the squirrel cage rotor  269 , the valve disk  273  closes off the central opening in the lower part  261  of the housing of the turbine and, with that, the liquid inlet opening  252  in the pump chamber  201 . In the upper end position of the valve disk  273  in the squirrel cage rotor, the valve disk  273  closes off the central opening in the upper part  262  of the housing of the turbine and, with that, the liquid inlet opening  253  (see FIG. 13) into the interim reservoir  260 . 
     The valve disk  273  furthermore is connected with a drive shaft  290  for joint rotation therewith. The rotation of the drive shaft  290  can be transferred, for example, to the rear axle  291  of a motor vehicle. The rotation of the vane ring  267  is thus formlockingly transferred over the disk  268 , the squirrel cage rotor  269  and the valve disk  273  to the driving axle  290 . In order to be able to adjust the valve disk  273  between the first lower end position and the second upper end position in the squirrel cage rotor, the valve disk  273  is connected axially displaceably with the drive shaft  290 , the axial displacement being effected with an actuating piston  274 , which is disposed in a cylindrical recess  275  in the drive shaft  290 . 
     The pump liquid, flowing out of the pump chamber  201  into the turbine, is directed by the inlet vane rings  263 ,  264  onto the turbine blade ring  267 , subsequently radially by the outlet vane rings  265 ,  266 , and flows through the liquid inlet opening  253  into the interim reservoir  280 . The volume of the latter can be changed by a flexible diaphragm or wall  281 , with the inflowing liquid, as shown in FIG. 13, pressing the wall  281  upward (commencing on the inside and continuing towards the outside) whereby the volume of the interim reservoir  280  is increased. 
     In order to avoid contact between the valve disk  273  and the flexible wall  281  of the interim reservoir  280  or the diaphragm  203  of the pump chamber  201 , covering disks  276 ,  277  are provided above and below the valve disk  273  and are mounted rotatably over bearings  278 ,  279  with respect to valve disk  273 . 
     The explosion cycle ends when essentially all pump liquid has been displaced from the pump chamber  201 . The tubular diaphragms  203  lie tightly next to one another, and the gas space  230  of the pump chamber  201  occupies essentially all of the volume of the pump chamber  201 . Thus, as far as possible, all of the pressure energy of the combustion gas can be utilized, with the pressure of the combustion gas having at this time been reduced approximately to atmospheric pressure. This is achieved due to the fact that the ratio of the volume of the combustion chamber  202  to that of the pump chamber  201 , which always remains constant, is selected, depending on the fuel used and on the burner charge, with the volume of the pump chamber  201  being significantly larger, for example, approximately five times as large as the volume of the combustion chamber  202 . If the burner charges remain constant, the time, which is required for an explosion cycle, is also constant and, at the end of this time, the control device  213  displaces the valve disk  273  from its lower end position into the upper end position. For this purpose, there are provided a hydraulic fluid pressure tank  283  to which pressure is communicated by a pump  284  from a tank  285 , and a valve  282 , which is controlled by a control device  213  and over which pressure is communicated to the piston  274 . 
     Furthermore, towards the end of the explosion cycle, a cooling medium, preferably a cooling liquid, is sprayed by spray nozzles  207  into the gas chamber  230  of the pump chamber  201 , in order to initiate the implosion cycle. For this purpose, a valve  286  is opened by the control device  213  and connects a cooling liquid pressure tank, to which the cooling liquid is fed by a pump  288 , with the spray nozzles. By spraying in the cooling liquid, the volume of the hot combustion gas is reduced suddenly, and an underpressure is developed in the gas space  230  of the pump chamber  201 . This underpressure has a twofold effect. On one hand, it provides for aspiration of spent combustion gases out of the combustion chamber  202  (which, at the same time, also implodes), so that the valve  224  opens and a new mixture is fed through the inlet  225  and over the fuel line  226  into the combustion chamber  202 . The flow rate of the mixture is adjusted by throttles, which are not shown in the Figures. Furthermore, the pump liquid is aspirated, as a result of the underpressure in the gas space  230  of the pump chamber  201 , out of the interim reservoir  280  through the turbine  260 . The pump liquid flows through the liquid outlet openings  237  of the interim reservoir  280 , which at the same time form the liquid inlet openings  237  of the turbine, through the inlet vane rings  263 ,  264  onto the turbine blade ring  267 , through the outlet vane rings  265 ,  266 , and the turbine outlet opening  252 , which at the same time forms the liquid inlet opening into the pump chamber  201 . In this way, the thermal energy of the combustion gas is also utilized to drive the turbine  260 . The pump liquid, flowing into the liquid space  231  of the pump chamber  201 , squeezes the tubular diaphragms  203 , from inside out (that is, reduces their volume starting from the inside and continuing to the outside) and, in so doing, initially closes off the outlet openings  250  of the combustion chamber  202 , with the check valve  224  also being closed. At this time, the rinsing process of the combustion chamber  202  has just been concluded. 
     Shortly thereafter, the volume of the gas space  230  of the pump chamber  201  decreases to an extent at which the combustion gas in the gas space  230  approximately reaches atmospheric pressure. Approximately at this time, which once again occurs at a certain constant time period after the ignition, the control device  213  opens the combustion gas outlet valves  209  by actuating valve  289 . The remaining combustion gas is now forced by the kinetic energy of the liquid, which flows out of the interim reservoir  280 , out of the combustion gas outlet openings  239  into the exhaust pipe  227 , with the volume of the gas space  230  of the pump chamber  201  being reduced further. Together with the combustion gas, the cooling liquid is also displaced from the gas space  230  into the exhaust pipe  227 , accumulates in the cooler  218 , and is pumped by the pump  288  once again into the pressure tank  287 . 
     The implosion cycle is thus ended, and the control device  231  closes the combustion gas outlet valves  209  and displaces the valve disk  273  into its lower end position. A new explosion cycle is initiated by the ignition of the working gas in the combustion chamber  202 . 
     As it has already been mentioned, the power of the combustion engine, which can be adjusted by the actuator  217 , is controlled not by charging the combustion chamber  202  differently but by omitting individual cycles, when power is not required, that is, there is no ignition of the working gas in the combustion space, the valves  209  remain closed and the valve disk  273  remains in its upper end position. As it has already been described above, the turbine  260  is a radial turbine in the form of a Francis turbine and works with slippage with respect to the liquid flowing through. However, in the case of the inventive closed system, a high liquid slippage in the turbine does not mean an overall deterioration in the efficiency, since kinetic energy or pressure of the pump liquid, which is not converted during the passage through the turbine, can be supplied once again to the inlet of the turbine. In other words, kinetic energy of the pump liquid, which is not converted by the turbine during the primary passage, is incorporated in the closed cycle as hydraulic centrifugal kinetic energy. Thus, the adjustment of the turbine blades and/or the guide vanes can be dispensed with, and the rotational speed and the torque are automatically controlled dynamically by increased or decreased slippage of the pump liquid in the turbine. The speed at which the pump liquid is circulated is once again determined by the burner performance, which results from the frequency of the ignitions carried out. 
     In order to keep internal flow losses (friction and turbulences) as small as possible, the flow segment for the pump fluid was configured so that its cross-section, as far as possible, remains constant. Switching over the pump liquid from the pump chamber into the interim reservoir and the reverse take place in such a way that flows in the opposite directions do not meet (unrestricted hydraulic switching over). 
     The number of cycles of 100 per second is possible with the combustion engine described, and a 50 HP engine can be made available, which has a volume of about 5 liters and a weight of about 10 kg. About 3 liters of pump liquid are being cycled in the engine. 
     The walls of the combustion chamber can take on a relatively high temperature, in order to decrease harmful emissions. For this purpose, the burner is formed of a ceramic material and has cooling liquid pipelines in its walls in order to control the temperature. 
     Though the present invention was shown and described with references to the preferred embodiments, such are merely illustrative of the present invention and are not to be construed as a limitation thereof and various modifications of the present invention will be apparent to those skilled in the art. It is therefore not intended that the present invention be limited to the disclosed embodiments or details thereof, and the present invention includes all variations and/or alternative embodiments within the spirit and scope of the present invention as defined by the appended claims.