Tangential combustion engine with hydraulic turbine

Abstract

The present invention relates to an internal combustion engine comprising a first cylinder (6) with a first piston (1) movably arranged therein, and a second cylinder (37) with a second piston (33) movably arranged therein. The first and second cylinders (6, 37) each contain a first chamber (5, 39) and a second chamber (7, 36), wherein the first chamber (5, 39) is arranged on one side of the first / second piston (1, 33) and is configured as a combustion chamber (5, 39), and the second chamber (7, 36) is arranged on an opposite side of the first / second piston (1, 33) and contains a fluid, in particular a hydraulic fluid. The first piston (1) and the second piston (33) are fluidically coupled and move back and forth in opposite directions within the first and second cylinders (6, 37).Furthermore, the internal combustion engine has a turbine (23) with a rotor (23) connected to a shaft (18), the turbine (23) being fluidically connected to the second chamber (7, 36) of the first and second cylinders (6, 37). The internal combustion engine is configured to induce a rotation of the rotor (22) of the turbine (23) and a return stroke of the second piston (33) by a forward stroke of the first piston (1), and vice versa, to induce a rotation of the rotor (22) of the turbine and a return stroke of the first piston (1) by a forward stroke of the second piston (33).

Description

[0001] The present invention relates to a novel internal combustion engine.

[0002] In the development of internal combustion engines, one of the main goals is to use the energy obtained from the fuel as effectively as possible, i.e., to achieve the highest possible efficiency in order to save fuel.

[0003] Reciprocating piston engines are known in the prior art, in which the work performed by the expansion of the gases produced by fuel combustion in a cylinder is transmitted to a piston and further to a crankshaft via a connecting rod, the connecting rod having a articulated connection to both the piston and the crankshaft (crankshaft drive). In this way, the oscillating motion of the piston is converted into a rotary motion, i.e., a torque is generated.

[0004] The present invention aims to further increase the efficiency of conventional combustion engines in order to enable more fuel-efficient operation.

[0005] The present invention therefore provides an internal combustion engine that combines an internal combustion drive with a hydraulic turbine. The drive elements of the engine can be designed / scaled in such a way that different performance classes can be covered.

[0006] The operating principle of the internal combustion engine according to the invention is similar to that of conventional internal combustion engines: Through an explosive combustion of a fuel in a combustion chamber of a cylinder of the internal combustion engine, a force is generated on a piston located in the cylinder and transmitted into a torque of a shaft, which can be connected, for example, to a drive shaft of a motor vehicle.

[0007] For this purpose, an ignitable fuel-oxygen mixture, normally a fuel-air mixture, is introduced into the combustion chamber of the cylinder, compressed there, and then ignited near a piston position with minimal distance to the cylinder head. The resulting heat release leads to a steep pressure increase in the combustion chamber, which causes the piston to move towards a position with maximum distance to the cylinder head. In the internal combustion engine according to the invention, unlike conventional engines with a crankshaft drive, the force acting on the piston is transmitted to the shaft by means of the hydraulic turbine. This allows a significant reduction in the number of mechanical components, thereby reducing mechanical friction and wear.

[0008] The internal combustion engine comprises a first cylinder with a first piston movably arranged therein, and a second cylinder with a second piston movably arranged therein. The first and second cylinders each contain a first chamber and a second chamber. The first chamber is located on one side of the first and second pistons, respectively, and is configured as a combustion chamber. The second chamber is located on the opposite side of the first and second pistons, respectively, and contains a fluid, which may be, in particular, a hydraulic fluid. The hydraulic fluid may, for example, be a hydraulic fluid such as a mineral oil-based or water-based fluid.

[0009] The first and second pistons are fluidically coupled and move back and forth in opposite directions within the first and second cylinders. The first and second cylinders, as well as the first and second pistons, can be identical in design, in particular having the same diameter and length or stroke.

[0010] Preferably, the first chamber (combustion chamber) adjoins the top of the first and second pistons, respectively, and the second chamber adjoins the bottom of the first and second pistons, respectively. The pistons can have suitable sealing means, e.g., piston rings, which seal the first and second chambers of the cylinders against each other. In particular, the sealing means can make the combustion chambers gas-tight and the second chambers liquid-tight. Each combustion chamber can contain at least one intake valve for supplying fresh gas (e.g., air or a fuel-air mixture) and at least one exhaust valve for removing combustion gases. The intake and exhaust valves (gas exchange valves) can, for example, be designed as poppet or slide valves and be actuated, for example, by means of at least one camshaft.

[0011] The internal combustion engine typically includes an intake manifold with known components for providing an ignitable fuel-air mixture, located adjacent to or upstream of the intake valve. Alternatively, the fuel-air mixture may be formed within the combustion chamber, with only fresh air supplied via the intake manifold. In this case, at least one fuel injector may be located in the combustion chamber. Furthermore, the internal combustion engine typically includes an exhaust manifold with known components for exhaust aftertreatment, located adjacent to or downstream of the exhaust valve. The engine may also incorporate an exhaust gas turbocharger or a mechanical and / or electric compressor in the intake manifold.

[0012] The internal combustion engine can be, for example, a two-stroke or a four-stroke engine. It can be of any size and used to power a motor vehicle, an aircraft, a ship, or a drone.

[0013] When designed as a 2-stroke engine, the scavenging, i.e. the expulsion of the combustion gases and the supply of fresh gas in the cylinder, can be carried out in a known manner, e.g. by cross-flow scavenging, parallel flow scavenging e.g. with a poppet valve, or reverse scavenging.

[0014] Both spark-ignition and diesel combustion processes can be used in the combustion chambers. In the case of a spark-ignition combustion process, at least one spark plug can be present in each combustion chamber. Conventional liquid and gaseous fuels can be used.

[0015] The first and second cylinders can be designed as separate units, for example, as tubes bolted together. It is also possible for the two cylinders to be integrated into a single cylinder block as bores. The internal combustion engine can have multiple first and multiple second cylinders, each with a first and second piston. For example, the engine can have two, four, six, eight, ten, etc., cylinders.

[0016] According to one embodiment, the two pistons can move in opposite directions such that the second piston is in a position with maximum distance to the upper end of the second cylinder when the first piston is in a position with minimum distance to the upper end of the first cylinder. A cylinder head of the internal combustion engine can be located at the upper end of the first and second cylinders. In particular, the first and second pistons can be designed as free pistons and have no mechanical connection to the crankshaft of the internal combustion engine. Instead, the second chamber of each of the first and second cylinders is fluidically connected to the turbine.

[0017] The turbine can be, in particular, a vane turbine, which may include a housing in which the turbine inlet and outlet are located. The turbine housing can preferably be made of two parts, the two parts of which can be, for example, bolted together. Any other suitable connection between the two housing parts is also possible. The turbine contains a rotor that is connected to the shaft. The rotor can, in particular, be rigidly connected to the shaft, for example, by means of a conventional shaft-hub connection. It is also possible that the rotor is pressed onto the shaft or that the shaft and rotor are made as a single piece. The shaft connected to the turbine rotor can be supported in the turbine housing by means of suitable bearings.

[0018] According to one embodiment, the second chamber of the first and second cylinders can each be connected to a turbine inlet via an inlet port and to a turbine outlet via an outlet port. In other words, a first inlet port (inlet port of the first cylinder) can be arranged between the second chamber of the first cylinder and the turbine inlet, and a first outlet port (exhaust port of the first cylinder) can be arranged between the turbine outlet and the second chamber of the first cylinder. Similarly, a second inlet port (inlet port of the second cylinder) can be arranged between the second chamber of the second cylinder and the turbine inlet, and a second outlet port (exhaust port of the second cylinder) can be arranged between the turbine outlet and the second chamber of the second cylinder.

[0019] The internal combustion engine is designed to induce rotation of the turbine rotor and a return stroke of the second piston through a forward stroke of the first piston, and conversely, to induce rotation of the turbine rotor and a return stroke of the first piston through a forward stroke of the second piston. A forward stroke of a piston is defined as a piston movement from the position of minimum distance to the cylinder head to the position of maximum distance to the cylinder head. Similarly, a return stroke is defined as a piston movement from the position of maximum distance to the cylinder head to the position of minimum distance to the cylinder head.

[0020] The pre-stroke movement can be initiated, in particular, by combustion in the first chamber of the first or second cylinder, which is designed as a combustion chamber. For example, combustion in the first chamber of the first cylinder can result in a pre-stroke movement of the first piston, which draws hydraulic fluid from the second chamber of the first cylinder through the corresponding inlet port to the turbine inlet, causing it to rotate. Subsequently, the hydraulic fluid flows from the turbine outlet through the corresponding outlet port into the second chamber of the second cylinder, causing it to perform a return stroke. This compresses the fuel-air mixture in the first chamber of the second cylinder, which is then ignited.The combustion in the first chamber of the second cylinder in turn initiates a pre-stroke movement of the second piston, whereby hydraulic fluid from the second chamber of the second cylinder is conveyed via the associated inlet channel to the turbine inlet and causes it to rotate.

[0021] The hydraulic fluid then flows from the turbine outlet through the associated outlet channel into the second chamber of the first cylinder, causing it to perform a return stroke. This establishes a closed fluid circuit between the second chamber of the first cylinder, the turbine, and the second chamber of the second cylinder, and vice versa.

[0022] It becomes clear that the hydraulic fluid is conveyed from the second chamber of the first and second cylinders to the turbine inlet, so that a forward stroke of the first and second pistons results in a rotation of the turbine in the same direction. Specifically, each forward stroke of the pistons can cause a 180° rotation of the turbine rotor, thereby continuously driving the shaft connected to the rotor. From the turbine outlet, the hydraulic fluid alternately flows to the second chamber of the first cylinder and the second chamber of the second cylinder to cause a return stroke of the respective piston.

[0023] According to one embodiment, at least one inlet valve can be arranged in each inlet channel and at least one outlet valve in each outlet channel to guide the hydraulic fluid through the closed fluid circuit as described above. In particular, the inlet valves can be configured to control a fluid supply from the second chamber of the first or second cylinder to the turbine, and the outlet valves can be configured to control a fluid discharge from the turbine into the second chamber of the first or second cylinder. The inlet and outlet valves can, for example, be actuated by at least one additional camshaft, which can be synchronized, for example, with the camshaft of the gas exchange valves in the combustion chambers of the first and second cylinders. For example, the two camshafts can be arranged offset from each other by a certain angle, such that, for example,An intake valve in the first intake port is open when an intake valve of the combustion chamber of the first cylinder is closed during combustion. Alternatively, a common camshaft can be used for the gas exchange valves and the intake and exhaust valves of the turbine's intake and exhaust ports, with the cams offset from each other by a specific angle. It is also possible for the intake and exhaust valves to be electrically or electronically controlled, e.g., solenoid valves, which can be controlled, for example, by an engine control unit.

[0024] To direct the hydraulic fluid from the second chamber of the first cylinder to the turbine and subsequently into the second chamber of the second cylinder, the inlet valve of the first inlet port and the outlet valve of the second outlet port can be open when the piston in the first cylinder performs a pre-stroke movement. Similarly, the inlet valve of the second inlet port and the outlet valve of the first outlet port can be open when the piston in the second cylinder performs a pre-stroke movement, in order to direct the hydraulic fluid from the second chamber of the second cylinder to the turbine and subsequently into the second chamber of the first cylinder.

[0025] According to one embodiment, two turbine blades, preferably designed as impellers, can be mounted on the outer surface of the rotor. The two turbine blades can cause the rotor to rotate 180° with each forward stroke of the pistons. In particular, a rear (upstream) side of each turbine blade can extend radially outward perpendicular to the outer surface of the rotor, and a front (downstream) side of each turbine blade can extend at an angle from the outer surface of the rotor to an outer edge of the rear side. This allows each turbine blade to have the shape of a right-angled triangle in a longitudinal section through the turbine.

[0026] According to one embodiment, the turbine can have a bypass channel concentric to the shaft, connecting the turbine's inlet and outlet. Furthermore, the turbine can have a shut-off channel located between the inlet and outlet and closed by means of a shut-off valve. Advantageously, the bypass channel and the shut-off channel can be arranged within the turbine housing.

[0027] The bypass channel can have a circular arc shape and be configured such that the central angle of one of the circular arcs underlying the shape of the bypass channel between the turbine inlet and outlet lies in a range between 30° and 180°, with this central angle typically being 180°. In particular, the bypass channel can be arranged parallel to a plane perpendicular to an axis of the shaft in the turbine casing. A diameter of the bypass channel can advantageously be equal to or greater than the length of the trailing edge of the turbine blade, allowing it to extend radially outward from the outside of the rotor to convey the hydraulic fluid through the turbine.

[0028] In one embodiment, the turbine inlet (turbine inlet) can be configured to introduce the hydraulic fluid into the circulating channel in a tangential direction, forming a circle concentric with the shaft. Similarly, the turbine outlet (turbine outlet) can be configured to discharge the hydraulic fluid from the circulating channel in a tangential direction, forming a circle concentric with the shaft. Hydraulic fluid entering the circulating channel tangentially through the turbine inlet can exert pressure on the rear faces of the turbine blades located within the circulating channel, thus causing rotation of the rotor or shaft in the direction of flow of the hydraulic fluid. After circulating in the circulating channel, the hydraulic fluid can exit the turbine tangentially through the turbine outlet. This can occur, in particular, with a constant torque and with a tangential effect.The flow direction of the hydraulic fluid can be tangential to its circular arc shape at any point in the circulating channel. In other words, the tangential effect can exist at any point during the entire circulation of the hydraulic fluid in the circulating channel, thereby achieving a high turbine efficiency.

[0029] Preferably, the bypass channel is part of an annular, concentric channel formed around the rotor or shaft, which has openings for the turbine inlet and outlet as well as the shut-off channel. The shut-off valve in the shut-off channel prevents hydraulic fluid located in the area of ​​the turbine outlet from flowing back to the turbine inlet. This prevents a "short circuit" with respect to the hydraulic fluid circulating in the turbine. For this purpose, the shut-off valve can have a closing element that closes a cross-section of the shut-off channel. The closing element can, for example, be a closing cylinder.

[0030] The entire channel can have the same diameter around its entire circumference, so that the turbine blades can extend outwards in the same way in the barrier channel as in the bypass channel.

[0031] In one embodiment, each of the turbine blades, configured as impellers, can be arranged to open the shut-off valve when a turbine blade passes through the shut-off channel. In particular, in this case, the closing element of the shut-off valve can be pushed from a closed position to an open position by the inclined leading edge of the turbine blade. When the shut-off valve is open, the turbine blade can close the shut-off channel, as it extends over a diameter of the channel. The shut-off valve can include a compression spring, against whose spring force the turbine blade opens the shut-off valve and which closes the shut-off valve again as soon as the turbine blade has passed through it. Instead of a compression spring, the shut-off valve can contain a solenoid for closing the shut-off valve.In particular, the compression spring or the magnet can act on the locking element, pushing it into a position where it closes the locking channel.

[0032] According to one embodiment, a section of the sealing channel located between the shut-off valve and the turbine outlet can be connected to the turbine outlet by means of a bypass channel. This allows hydraulic fluid located between the leading edge of a turbine blade entering the sealing channel and the closing element of the shut-off valve to be directed to the turbine outlet. In this way, it is possible to prevent hydraulic fluid from accumulating in the sealing channel upstream of the shut-off valve and thereby hindering or even completely preventing rotor rotation.

[0033] The present invention further relates to the use of an internal combustion engine according to the invention for powering a motor vehicle, an aircraft, a ship or a drone.

[0034] The invention also relates to a motor vehicle, aircraft, ship or drone, comprising at least one internal combustion engine according to the invention. Brief description of the drawings

[0035] Figure 1 Figure 1 shows a simplified schematic sectional view of a front view of an embodiment of the internal combustion engine according to the invention. Figure 2 shows a simplified schematic cross-sectional view of a turbine of the in Figure 1 shown internal combustion engine. Figure 3 shows a simplified spatial representation of a turbine blade of the in Figure 2 turbine shown. Example

[0036] One embodiment of the internal combustion engine according to the invention is described below with reference to the Figures 1 to 3 described in more detail.

[0037] In the figures, identical or similar elements are marked with the same reference symbols. Therefore, a repetitive description of individual elements is omitted.

[0038] The internal combustion engine shown has a first cylinder 6 and a second cylinder 37, each containing a first piston 1 and a second piston 33. Adjacent to the upper surface of the pistons 1, 33, each cylinder 6, 37 has a combustion chamber 5, 39. Each combustion chamber 5, 39 has an intake port 2, 40 and an exhaust port 4, 42, each of which can contain at least one intake and one exhaust valve (not shown). A fuel-air mixture can enter the combustion chambers 5, 39 via the intake ports 2, 40, while combustion gases can be expelled from the combustion chambers 5, 39 via the exhaust ports 4, 42. Each combustion chamber 5, 39 contains a spark plug 3, 41, which ignites the fuel-air mixture.

[0039] Adjacent to the underside of each piston 1, 33 is a second chamber 7, 36 containing hydraulic fluid (indicated by the dotted area). The pistons 1, 33 are designed as free pistons and are fitted with piston rings (not specified) that seal the first chamber 5, 39 against the second chamber 7, 36. In this case, the first piston 1 is in piston position 8a with a minimum distance to the upper end of the first cylinder 6, while the second piston 33 is in piston position 38a with a maximum distance to the upper end of the second cylinder 37. A cylinder head (not shown) may be adjacent to the upper ends of the first and second cylinders 6, 37. This cylinder head may contain the intake and exhaust ports 2, 40, 4, 42 and may house the spark plugs 3, 41.The two pistons 1, 33 move in opposite directions to each other between the piston positions with minimum distance 8a, 38 and maximum distance 8, 38a to the cylinder head in the cylinders 6, 37, back and forth or up and down.

[0040] A turbine 23 is fluidically connected to the second chambers 7, 36 of the first and second cylinders 6, 37. To illustrate the fluidic connection, all areas of the internal combustion engine containing hydraulic fluid are shown in Figure 1 The areas are marked by dotted lines. The flow direction of the hydraulic fluid is indicated by arrows.

[0041] The turbine 23 can convert the counter-rotating motion of the pistons 1, 33 in the cylinders 6, 37 into a rotary motion of a shaft 18 of the turbine 23 (indicated by a rotation arrow on the turbine 23). The shaft 18 can, for example, be connected to a drive shaft of a motor vehicle (not shown).

[0042] The turbine 23 comprises a rotor 22 and a housing 44 in which the rotor 22 is arranged (see Figure 2 The rotor 22 is sealed against the turbine housing 44 at each of its end faces by a sealing ring 20 and is rigidly connected to the shaft 18, e.g., by means of a conventional shaft-hub connection (not shown). It is also possible that the rotor 22 is pressed onto the shaft 18 or that the shaft 18 and the rotor 22 are manufactured as a single piece. The shaft 18 is supported in the turbine housing 44 by means of two bearings 45, 50. In this case, the turbine housing 44 is made in two parts and has two screw connections 43 on an outer circumference (see figure). Figure 2 ).

[0043] On one outer side of the rotor 22, two turbine blades 19 designed as impellers are arranged, which are in the Figure 1The sectional view shown has the shape of a right-angled triangle. A back side 54 of the turbine blade 19 extends perpendicularly to an outer surface of the rotor 22 to the outer circumference of the casing 44, and a front side 53 of the turbine blades 19 extends at an angle of inclination from the outer surface of the rotor 22 to an outer edge of the back side from a lowest point 25 to a highest point 24 of the turbine blade 44 (see also Figure 3 ).

[0044] In the turbine housing 44, a bypass channel 21 and a barrier channel 26 are formed, which together form an annular, concentrically arranged total channel 21, 26 around the rotor 22 or the shaft 18 (see Figure 1Furthermore, the turbine housing 44 has an inlet 15 and an outlet 26, which are connected to each other by means of the bypass channel 21. The bypass channel 26 is arranged between the inlet 15 and the outlet 28 of the turbine 23 and is closed by means of a bypass valve 12. For this purpose, the bypass valve 12 has a closing element 16, which in this case is designed as a closing cylinder 16 that closes a cross-section of the bypass channel 26. The bypass channel 21 has a circular arc shape with a central angle of 180°. In particular, the bypass channel 21 is arranged in this case parallel to a plane perpendicular to an axis of the shaft 18 in the turbine housing 44.

[0045] The diameter of the bypass channel 21 and the shut-off channel 26 is essentially equal to the length of the trailing edge of the turbine blade 19, allowing them to extend radially outwards from the outside of the rotor 22 to convey the hydraulic fluid through the turbine 23. The shut-off valve 12 is opened by means of a turbine blade 19 as it passes through the shut-off channel 26. The closing cylinder 16 of the shut-off valve 12 is pushed from a closed position to an open position by the inclined leading edge 53 of the turbine blade 19, thereby performing a stroke 13. Based on Figure 3It becomes clear that the locking cylinder 16 can be securely guided on the flat front surface 53 of the turbine blade 19. While the shut-off valve 12 is open, the shut-off channel 26 is closed by the turbine blade 19, as it extends over a diameter of the shut-off channel 26. The shut-off valve 12 can include a compression spring (not shown), against whose spring force the turbine blade 19 opens the shut-off valve 12 and which closes the shut-off valve 12 again as soon as the turbine blade 19 has passed over the shut-off valve 12. Instead of a compression spring, the shut-off valve 12 can contain a solenoid for closing the shut-off valve 12. In particular, the compression spring or the solenoid can act on the locking cylinder 16, pushing it into a position in which it closes the shut-off channel 26.

[0046] The turbine inlet 15 is configured to introduce hydraulic fluid, which enters the turbine housing 44 from the second chamber 7, 36 of the first or second cylinder 6, 37 via the associated inlet channel 14, 30, into the bypass channel 21 in a tangential direction to a circle concentric with the shaft 18. Likewise, the turbine outlet 28 is configured to discharge the hydraulic fluid from the bypass channel 21 in a tangential direction to the circle concentric with the shaft 18.

[0047] Hydraulic fluid entering the bypass channel 21 tangentially through the turbine inlet 15 can press against the rear faces of the turbine blade 19 located in the bypass channel 21, thus causing rotation of the rotor 22 or the shaft 18 in the direction of flow of the hydraulic fluid. After circulating in the bypass channel 21, the hydraulic fluid can exit the turbine 23 tangentially through the turbine outlet 28. This can occur, in particular, with a constant torque and with tangential action; that is, the flow direction of the hydraulic fluid can be tangential to its circular arc shape at any point in the bypass channel 21. In other words, the tangential action can exist at every point during the entire circulation of the hydraulic fluid in the bypass channel 21, thereby achieving a high efficiency of the turbine 23.

[0048] The shut-off valve 12 in the shut-off channel 26 prevents hydraulic fluid located in the area of ​​the turbine outlet 28 from flowing back to the turbine inlet 15. This prevents a "short circuit" of the hydraulic fluid circulating in the turbine 23. A section of the shut-off channel 26, located between the shut-off valve 12 and the turbine outlet 28, is connected to the turbine outlet 28 by means of a bypass channel 27. This allows hydraulic fluid located between the leading edge of a turbine blade 19 entering the shut-off channel 26 and the closing element 16 of the shut-off valve 12 to be directed to the turbine outlet 28. In this way, it is prevented that hydraulic fluid accumulates in the shut-off channel 26 upstream of the shut-off valve 12, thereby hindering or even completely preventing the rotation of the rotor 22.

[0049] To provide the fluidic connection between cylinders 6, 37 and the turbine 23, a first inlet channel 14 is arranged between the second chamber 7 of the first cylinder 6 and the turbine inlet 15, and a second inlet channel 30 is arranged between the second chamber 36 of the second cylinder 37 and the turbine inlet 15. The first inlet channel 14 is vertically oriented, while the second inlet channel 30 runs at an angle from the second chamber 36 of the second cylinder 37 to the turbine inlet 15. An inlet valve 9, 34 is arranged at each inlet to the two inlet channels 14, 30. Furthermore, a first outlet channel 11 is arranged between the turbine outlet 28 and the second chamber 7 of the first cylinder 6, and a second outlet channel 29 is arranged between the turbine outlet 28 and the second chamber 36 of the second cylinder 37.The first exhaust port 11 runs at an angle from the turbine outlet 28 to the second chamber 7 of the first cylinder 6, while the second exhaust port 29 extends vertically from the turbine outlet 28 to the second chamber 36 of the second cylinder. An exhaust valve 35, 32 is arranged at each outlet of the two exhaust ports 11, 29. The inlet and exhaust valves 9, 34, 35, 32 are designed as poppet valves, with a poppet 10 of the inlet valve 9 closing the inlet port 14 and a poppet 31 of the exhaust valve 32 closing the exhaust port 29.

[0050] The intake and exhaust valves 9, 34, 35, 32 can be actuated, for example, by means of at least one camshaft (not shown). It is also possible that the intake and exhaust valves 9, 34, 35, 32 are electrically or electronically controlled valves, e.g., solenoid valves, which can be controlled, for example, by a control unit (not shown) of the internal combustion engine.

[0051] If according to Figure 1When the fuel-air mixture is ignited by the spark plug 41 in the combustion chamber 39 of the second cylinder, the exhaust valve 32 of the second exhaust port 29 is closed and the intake valve 34 of the second intake port 30 is opened simultaneously or a certain short time before ignition. Likewise, the intake valve 9 of the first intake port 14 is closed and the exhaust valve 35 of the first exhaust port 11 is opened. Following ignition of the fuel-air mixture, combustion moves the second piston 33 in the second cylinder 37 from piston position 38 to piston position 38a (pre-stroke movement of the second piston 33), thereby conveying hydraulic fluid from the second chamber 36 of the second cylinder 37 via the second intake port 30 to the turbine inlet 15.From there, the hydraulic fluid flows tangentially into the bypass channel 21 of the turbine 23 and strikes the rear face 53 of one of the two turbine blades 19, causing the rotor 22 to rotate 180° and driving the shaft 18. Subsequently, the hydraulic fluid exits the turbine outlet 28 tangentially and enters the first outlet channel 11, from where it enters the second chamber 7 of the first cylinder 6 and moves the first piston 1 from piston position 8 to piston position 8a (return stroke of the first piston 1). Near piston position 8a, a fuel-air mixture is ignited in the combustion chamber 5 of the first cylinder 6, causing a forward stroke of the first piston 1. In this case, hydraulic fluid from the second chamber 7 of the first cylinder 6 is conveyed via the first inlet channel 14 to the turbine inlet 15, from where it enters the circulation channel 21 and causes a further rotation of the rotor 22 by 180°.The hydraulic fluid then exits the turbine outlet 28 and enters the second chamber 36 of the second cylinder 37 via the second outlet channel 29, where it induces a return stroke of the second piston 33. To direct the hydraulic fluid from the second chamber 7 of the first cylinder 6 to the second chamber 36 of the second cylinder 37 as described, the exhaust valve 9 of the first exhaust channel 14 is opened and the inlet valve 35 of the first inlet channel 11 is closed at or shortly before the ignition of the fuel-air mixture in the combustion chamber 5 of the first cylinder 6. Simultaneously, the exhaust valve 32 of the second exhaust channel 29 is opened and the inlet valve 34 of the second inlet channel 30 is closed. In this way, a closed fluid circuit can be provided between the second chambers 7 and 36 of the cylinders 6 and 37 and the turbine 23, and the shaft 18 can be continuously rotated in one direction.Due to the reduced number of mechanical components, mechanical friction and wear in the combustion engine can be significantly reduced. Reference symbol list:

[0052] 1, 33 first and second piston 2, 40 intake port combustion chamber 3, 41 spark plug 4, 42 exhaust port combustion chamber 5, 39 first chamber or combustion chamber 6, 37 first and second cylinder 7, 36 second chamber 8, 8 amax. / min. Distance first piston to cylinder head 9, 34 Inlet valves turbine 10, 44 Valve head inlet and exhaust valve 11 First exhaust port 12 Check valve 13 Stroke closing element of the check valve 14 First intake port 15 Turbine inlet 16 Closing element of the check valve 18 Shaft 19 Turbine blade 20 Sealing ring 21 Turbine bypass channel 22 Turbine rotor 23 Turbine 24 Highest point turbine blade 25 Lowest point turbine blade 26 Check channel turbine 27 Bypass channel 28 Turbine outlet 29 Second exhaust port 30 Second intake port 32, 35 Turbine exhaust valves 38, 38 Am / Max. Distance from second piston to cylinder head 43 Turbine housing bolting 44 Turbine housing 45, 50 Turbine bearing 53 Front of turbine blade 54 Rear of turbine blade

Claims

1. Internal combustion engine comprising a first cylinder (6) with a first piston (1) movably arranged therein, and a second cylinder (37) with a second piston (33) movably arranged therein, wherein the first and the second cylinder (6, 37) each contain a first chamber (5, 39) and a second chamber (7, 36), wherein the first chamber (5, 39) is arranged on one side of the first / second piston (1, 33) and is configured as a combustion chamber (5, 39), and the second chamber (7, 36) is arranged on an opposite side of the first / second piston (1, 33) and contains a fluid, in particular a hydraulic fluid, wherein the first piston (1) and the second piston (33) are fluidically coupled and move back and forth in opposite directions in the first and second cylinder (6, 37);a turbine (23) with a rotor (23) connected to a shaft (18), wherein the turbine (23) is fluidically connected to the second chamber (7, 36) of the first and second cylinders (6, 37), wherein the internal combustion engine is configured to induce a rotation of the rotor (22) of the turbine (23) and a return stroke of the second piston (33) by means of a forward stroke of the first piston (1), and to induce a rotation of the rotor (22) of the turbine and a return stroke of the first piston (1) by means of a forward stroke of the second piston (33).

2. Internal combustion engine according to claim 1, wherein the second space (7, 36) of the first and second cylinder (6, 37) is each connected via an inlet channel (14, 30) to an inlet (15) of the turbine (23) and via an outlet channel (11, 29) to an outlet (28) of the turbine (23). 3.Internal combustion engine according to claim 2, wherein at least one inlet valve (9, 34) is arranged in each inlet channel (14, 30) and at least one exhaust valve (35, 32) is arranged in each outlet channel (11, 29).

4. Internal combustion engine according to claim 3, wherein the inlet valves (9, 34) are configured to control a fluid supply from the second chamber (7, 36) of the first or second cylinder (6, 37) to the turbine (23), and the exhaust valves (35, 32) are configured to control a fluid discharge from the turbine (23) into the second chamber (7, 36) of the first or second cylinder (6, 37). 5.Internal combustion engine according to claim 3 or 4, wherein an inlet valve (9) of an inlet port (14) of the first cylinder (6) and an exhaust valve (32) of an exhaust port (29) of the second cylinder (37) are open when the piston (1) in the first cylinder (6) performs a pre-stroke movement, and an inlet valve (34) of an inlet port (30) of the second cylinder (37) and an exhaust valve (35) of an exhaust port (11) of the first cylinder (6) are open when the piston (33) in the second cylinder (37) performs a pre-stroke movement.

6. Internal combustion engine according to at least one of claims 2 to 5, wherein the turbine (23) has a circulation channel (21) concentric to the shaft (18) which connects the inlet (15) and the outlet (28) of the turbine (23), and a sealing channel (26) which is arranged between the inlet (15) and the outlet (28) of the turbine (23) and is closed by means of a sealing valve (12). 7.Internal combustion engine according to at least one of claims 2 to 6, wherein the inlet (15) of the turbine (23) is configured to introduce the fluid in a tangential direction to a circle concentric with the shaft (18) into the circulation channel (21), and the outlet (28) of the turbine (23) is configured to direct the fluid out of the circulation channel (21) in a tangential direction to the circle concentric with the shaft (18).

6. Internal combustion engine according to at least one of the preceding claims, wherein the rotor (22) of the turbine (23) is configured to perform a rotation by 180° during each forward stroke movement of the pistons (1, 33).

7. Internal combustion engine according to at least one of the preceding claims, wherein two turbine blades (19) are mounted on an outside of the rotor (22). 8.Internal combustion engine according to claim 7, wherein a rear side (54) of each turbine blade (19) extends radially outwards perpendicular to the outside of the rotor (22) and a front side (53) of each turbine blade (19) extends at an angle of inclination from the outside of the rotor (22) to an outer edge of the rear side (54).

9. Internal combustion engine according to claim 7 or 8, wherein each turbine blade (19) is configured to open the shut-off valve (12) when a turbine blade (19) passes through the shut-off channel (26).

10. Internal combustion engine according to at least one of claims 6 to 9, wherein a section of the blocking channel (26) which is arranged between the blocking valve (12) and the outlet (28) of the turbine (23) is connected to the outlet (28) of the turbine (23) by means of a bypass channel (27). 11.Internal combustion engine according to at least one of the preceding claims, wherein when the first piston (1) is located at a piston position (8a) with minimum distance to an upper end of the first cylinder (6), the second piston (43, 29) is located at a piston position (38a) with maximum distance to the upper end of the second cylinder (37).

12. Use of the internal combustion engine according to any one of claims 1 to 13 for powering a motor vehicle, an aircraft, a ship or a drone.

13. Motor vehicle, aircraft, ship or drone comprising at least one internal combustion engine according to one or more of claims 1 to 11.

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