Tangential combustion engine with turbine hydraulic system

Abstract

The present invention relates to an internal combustion engine comprising: a first cylinder for fuel combustion with a first drive piston movably arranged therein; a second cylinder for fuel combustion with a second drive piston movably arranged therein; and a shaft, wherein: the internal combustion engine is arranged such that the drive pistons in the two cylinders move back and forth in opposite directions; the first drive piston is mechanically coupled to a first pressure piston; the second drive piston is mechanically coupled to a second pressure piston; and wherein the internal combustion engine is characterized in that: the drive pistons are coupled to each other such that a forward stroke movement of the first drive piston in the first cylinder causes a return stroke movement of the second drive piston in the second cylinder; and it further comprises a first hydraulic unit in which the first pressure piston is movably arranged.and comprising a first impeller arranged in the first hydraulic unit and, separately, a second hydraulic unit in which the second pressure piston is movably arranged, as well as a second impeller arranged in the second hydraulic unit, - wherein the internal combustion engine is further arranged such that the first and the second drive pistons are coupled to each other in such a way that a forward stroke movement of the first drive piston in the first cylinder causes a return stroke movement of the first pressure piston in the first hydraulic unit, and a return stroke movement of the second drive piston in the second cylinder causes a forward stroke movement of the second pressure piston in the second hydraulic unit, so that the two pressure pistons move in opposite directions in their respective hydraulic units - wherein the hydraulic fluid located in the respective hydraulic unit, preferably a liquid,is set in motion by the movement of the pressure pistons and the moving hydraulic fluid causes a rotary back-and-forth movement of the axis of the impeller located in the respective hydraulic unit, - and the rotary back-and-forth movement of the impeller axes is transmitted by means of a transmission device into a continuous rotational movement of the shaft, as well as a method for operating this internal combustion engine, the use of this internal combustion engine for powering a motor vehicle, aircraft or ship and a motor vehicle, aircraft or ship that includes this internal combustion engine.

Description

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

[0002] When developing internal combustion engines, one of the main objectives is to use the energy obtained from the fuel used 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 art. The work performed by the expansion of the gases generated by fuel combustion in a cylinder is transmitted to a piston and then to a crankshaft via a connecting rod. The connecting rod has a joint connection to both the piston and the crankshaft (crank drive). This converts the oscillating motion of the piston into a rotary motion, i.e., generates torque.

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

[0005] The present invention therefore provides an internal combustion engine which a first cylinder for fuel combustion with a first drive piston movably arranged therein, a second cylinder for fuel combustion with a second drive piston movably arranged therein, and a shaft, where the internal combustion engine is designed so that the drive pistons in the two cylinders move back and forth in opposite directions, the first drive piston is mechanically coupled to a first pressure piston, the second drive piston is mechanically coupled to a second pressure piston, and wherein the internal combustion engine is characterized in that the drive pistons are coupled to one another in such a way that a forward stroke movement of the first drive piston in the first cylinder causes a return stroke movement of the second drive piston in the second cylinder, it further comprises a first hydraulic unit in which the first pressure piston is movably arranged, as well as a first impeller arranged in the first hydraulic unit and, separately therefrom, a second hydraulic unit in which the second pressure piston is movably arranged, as well as a second impeller arranged in the second hydraulic unit, wherein the internal combustion engine is further configured such that the first and the second drive piston are coupled to one another in such a way that a forward stroke movement of the first drive piston in the first cylinder causes a return stroke movement of the first pressure piston in the first hydraulic unit,and a return stroke movement of the second drive piston in the second cylinder causes a forward stroke movement of the second pressure piston in the second hydraulic unit, so that the two pressure pistons move in opposite directions in their respective hydraulic units, wherein the hydraulic fluid, preferably a liquid, located in the respective hydraulic unit is set in motion by the movement of the pressure pistons and the moving hydraulic fluid causes a rotary back and forth movement of the axis of the impeller located in the respective hydraulic unit, and the rotary back and forth movement of the axes of the impellers is transmitted by means of a transmission device into a continuous rotary movement of the shaft.

[0006] The internal combustion engine according to the invention can be of any size, from relatively small versions such as a motorcycle engine, to car, boat, and aircraft engines, to very large versions such as marine engines. Its compact design allows for space-saving installation options.

[0007] The working principle of the engine according to the invention is similar to that of conventional internal combustion engines: the power is generated by the explosive combustion of a fuel in the combustion chambers of the cylinders and transferred into a torque of a shaft.

[0008] To do this, an ignitable fuel-oxygen, usually fuel-air, mixture is introduced into the combustion chambers of the cylinders, compressed there, and then ignited near the piston position with the minimum distance from the cylinder head (P min ). The resulting gases expand explosively, causing the piston to move toward the position with the maximum distance from the cylinder head (P max ).

[0009] The hydraulic units provided according to the invention enable, on the one hand, the transmission of the force acting on the pressure pistons to the impellers located in the respective hydraulic unit by means of the hydraulic fluid contained in the hydraulic unit. On the other hand, by selecting the ratios of the cross-sections of the cylinders and the hydraulic unit, the pressure generated by the reciprocating movement of the drive pistons can be increased.

[0010] This can reduce fuel consumption and enable improved piston thrust motion in terms of fuel consumption and efficiency. This can consequently increase combustion efficiency and thus the efficiency of the internal combustion engine.

[0011] The hydraulic fluid is located in an interior of the hydraulic units.

[0012] The hydraulic fluid used is preferably a liquid such as a mineral oil or water-based fluid.

[0013] The hydraulic unit is usually designed in the area of ​​the stroke of the pressure pistons so that the pressure pistons seal with the inner walls of the hydraulic unit.

[0014] The movement of the drive pistons in the first cylinder and in the second cylinder is in opposite directions in the internal combustion engine according to the present invention, ie, for example, when the first drive piston in the first cylinder moves from a position P min,1 to P max,1, the second drive piston moves simultaneously in the other cylinder from the position P max,2 to P min,2.

[0015] The impeller present in each hydraulic unit creates a turbine in the respective hydraulic unit, which transfers the force transmitted to the blades of the impeller by the movement of the hydraulic fluid into a rotary back and forth movement of the impeller axes.

[0016] The transmission of the force generated by the thrust movement of the respective drive pistons to the pressure pistons, which is further transmitted by means of the hydraulic fluid to the blades of the impellers, preferably takes place in such a way that the hydraulic fluid flows at least partially, preferably completely, tangentially through the turbines formed.

[0017] The blades of the impeller are at least partially, preferably completely, exposed to air flow perpendicular to their direction of movement.

[0018] The design of the resulting turbines ensures that the tangential forces act or are transmitted at the maximum possible sinusoidal angle of 90° at all times, i.e., throughout the entire working process. Thus, the engine according to the invention offers the advantages of achieving the highest possible torque even at low speeds, as well as the most constant torque possible at different speeds. This enables the engine according to the invention to be more efficient than conventionally designed reciprocating piston engines, thus also saving fuel. This can also have beneficial environmental benefits.

[0019] The forward and reverse directions, or forward stroke and return stroke, refer to the movement of a piston within its respective unit (cylinder or hydraulic unit). "Forward" or "forward stroke" refers to the movement of the piston outward from the unit, and "reverse" or "return stroke" refers to the movement of the piston into the unit.

[0020] For example, the movement of the drive piston after ignition of the gas mixture in the direction out of the cylinder is called "propulsion" or "pre-stroke"

[0021] The "front side of a piston" is understood to mean the side of the piston facing the respective unit (e.g. the cylinder), and the back or underside of a piston is understood to mean the side of the piston facing away from the respective unit (e.g. cylinder).

[0022] The opposing movement of the pressure pistons in the hydraulic units is supported by the mechanical coupling of the pressure pistons with the respective drive pistons in the cylinders, which are arranged to be equally movable in opposite directions, and the coupling of the drive pistons with each other.

[0023] In the internal combustion engine according to the invention, the pressure pistons are each mechanically coupled to the drive pistons, ie the first drive piston is mechanically coupled to the first pressure piston and the second drive piston is mechanically coupled to the second pressure piston.

[0024] Preferably, the drive pistons in the cylinders are movable such that when the first drive piston of the first cylinder is at a position with a minimum distance to an upper end of the first cylinder, the second drive piston in the second cylinder is at a position with a maximum distance to an upper end of the second cylinder, and / or the movements of the pressure pistons in their respective hydraulic unit are such that when the first pressure piston is at a position with a minimum distance to an upper end of the first hydraulic unit, the second pressure piston is at a position with a maximum distance to an upper end of the hydraulic unit.

[0025] Further preferably, the first pressure piston has a smaller effective surface than the first drive piston and / or the second pressure piston has a smaller effective surface than the second drive piston.

[0026] The "effective surface area" is the area of ​​the front of a piston that is obtained by projecting the actual surface of the piston front onto a surface perpendicular to the stroke direction.

[0027] In this embodiment, the pressure acting on the hydraulic fluid is increased.

[0028] Preferably, the first drive piston and the first pressure piston run in the same longitudinal direction and thus synchronously in one direction and / or the second drive piston and the second pressure piston run in the same longitudinal direction and thus synchronously.

[0029] In an advantageous development, it can be provided that the rear side of the first drive piston is rigidly connected to the rear side of the first pressure piston and / or the rear side of the second drive piston is rigidly connected to the rear side of the second pressure piston. This can achieve improved stability and efficient power transmission from the respective drive piston to the respective pressure piston and vice versa.

[0030] Preferably, the rigid connection between the respective drive pistons and the respective pressure pistons is provided by a rigid, linear rod, for example a connecting rod.

[0031] Preferably, the pressure pistons are attached to the rods of the drive pistons, especially to the connecting rods of the drive pistons. This advantageously enables increased stability and simplified, compact manufacturing.

[0032] In particular, it can also be provided that the first drive piston and the first pressure piston are designed as a one-piece or one-part first piston unit via a rod, in particular a connecting rod. This first piston unit can alternatively also be designed in multiple parts. Accordingly, it can be provided that the second drive piston and the second pressure piston are designed as a one-piece or one-part second piston unit via a rod. This second piston unit can alternatively also be designed in multiple parts.

[0033] Typically, the drive pistons in the cylinders are movable in such a way that when the first drive piston of the first cylinder is at a position with a minimum distance to an upper end of the first cylinder, the second drive piston in the second cylinder is at a position with a maximum distance to the upper end of the second cylinder.

[0034] In addition, the hydraulic units are preferably arranged such that the pressure pistons move in their respective hydraulic unit such that when the first pressure piston is at a position with a minimum distance to an upper end of the hydraulic unit, the second pressure piston in the hydraulic unit is at a position with a maximum distance to an upper end of the hydraulic unit.

[0035] Preferably, the first and / or the second hydraulic unit is closed at the end opposite the end defined by the first or second pressure piston by a first or second closing piston movable in the respective hydraulic unit.

[0036] More preferably, the first and / or the second hydraulic unit comprises, from one end to the other, a first region defined by the stroke of the respective pressure piston, a second region defined by the presence of the respective impeller, and a third region after the impeller up to the respective end piston.

[0037] Preferably, the cross section of the first and / or the second hydraulic unit is smaller in the first region than in the second region.

[0038] Preferably, the impeller axis in the first and / or second turbine formed is arranged perpendicular to the direction of movement of the first and / or second drive piston.

[0039] Preferably, the impeller axis in the first and / or second turbine formed is arranged perpendicular to the direction of movement of the first and / or second pressure piston.

[0040] Further preferably, the impeller axis in the first and / or the second turbine formed is arranged perpendicular to the direction of movement of the respective hydraulic fluid.

[0041] In a preferred embodiment, the first and / or the second turbine is designed such that the hydraulic fluid flows out of the turbine in the same direction in which it flows into the turbine, ie usually that the turbine inlet and outlet are 180° opposite each other.

[0042] In the area of ​​the impeller of the first and / or second hydraulic unit, there is preferably a circular arc-shaped extension of the respective hydraulic unit wall, which also forms this turbine and in which the blades of the impeller rotate as the hydraulic fluid moves. This circular arc-shaped extension of the respective hydraulic unit wall is preferably designed such that almost no, or even no, hydraulic fluid can flow past the outside of the blades.

[0043] The circular arc of the extension preferably covers an angular range of 180°.

[0044] The axis of the impeller preferably lies on an imaginary extended line of the hydraulic unit wall without the circular arc-shaped extension.

[0045] The shaft is preferably arranged perpendicular to the axis of the first and / or second impeller.

[0046] The transmission device preferably comprises a first freewheel and a second freewheel.

[0047] Freewheels typically have an outer and an inner side, which can be designed, for example, as an outer and inner ring, which can lock against each other (drive mode) or run freely (freewheel mode). The freewheels of the transmission device are usually identical in design.

[0048] Preferably, the outer side of the first freewheel is operatively connected to the axis of the first impeller and / or the outer side of the second freewheel is operatively connected to the axis of the second impeller, wherein the operative connection is such that the reciprocating movement of the impeller axis(es) is transmitted to the outer side of the freewheel(s).

[0049] The inner sides of the freewheels are typically connected to the shaft in such a way that the freewheels rotate and lock in the same direction. Thus, the reciprocating motion of the hydraulic fluid in the respective hydraulic unit is transferred into a rotary reciprocating motion on the outer side of the first freewheel and an opposing rotary reciprocating motion on the second freewheel. The arrangement of the freewheels on the shaft enables continuous rotation of the shaft in one direction.

[0050] The outer sides of the freewheels can be coupled together in such a way that they support an opposing movement of the outer sides of the two freewheels.

[0051] Preferably, the operative connection of the axis of the first and / or second impeller with the outer sides of the first and / or second freewheel is effected by a gear connection, wherein the gear located on the axis of the first and / or second impeller usually engages in toothings present on the lateral outer surfaces of the first and / or second freewheel.

[0052] Typically, the rotary reciprocating movement of the first impeller and / or the second impeller takes place over an angular range of at least 60°, preferably of at least 90°, particularly preferably of at least 120°, and most particularly preferably of at least 150° or more.

[0053] It can be provided that the rotary back and forth movement of the first impeller and / or the second impeller takes place over an angular range between 60° and 270°, preferably between 120° and 240°, particularly preferably between 150° and 210°.

[0054] In particular, it can be provided that the rotary back and forth movement of the first impeller and / or the second impeller takes place over an angular range of 160° to 200°, preferably from 170° to 190°, more preferably from 175° to 185°, most preferably 180°.

[0055] Furthermore, the rotational back and forth movement of the first freewheel and / or the second freewheel usually takes place over an angular range of at least 60°, preferably of at least 90°, particularly preferably of at least 120°, and very particularly preferably of at least 150° or more.

[0056] It can be provided that the rotary back and forth movement of the first freewheel and / or the second freewheel takes place over an angular range between 60° and 270°, preferably between 120° and 240°, particularly preferably between 150° and 210°.

[0057] In particular, it can be provided that the rotary back and forth movement of the first freewheel and / or the second freewheel takes place over an angular range of 160° to 200°, preferably from 170° to 190°, more preferably from 175° to 185°, most preferably 180°.

[0058] Typically, gears, racks or gears as well as any bearings of the motor according to the invention are supplied with lubricant in a conventional manner.

[0059] Pistons, such as drive and pressure pistons, are usually provided with piston rings.

[0060] In one embodiment, the internal combustion engine according to the invention is designed such that the entirety of the first cylinder and the first hydraulic unit, including all further elements located therein, is arranged mirror-symmetrically to the entirety of the second cylinder and the second hydraulic unit, including all further elements located therein.

[0061] The coupling of the movement of the first and second drive pistons is preferably carried out by means of a chain deflected via a gear wheel.

[0062] There is usually a rigid rod on the bottom (underside) of the first and / or second drive piston, the length of which corresponds approximately to the length of the stroke of the first or second drive piston.

[0063] The chain to be redirected is usually attached to the end of the rigid rods opposite the respective drive piston.

[0064] The chain is usually designed so that the teeth of the idler gear can engage in recesses in the chain links.

[0065] Preferably, the internal combustion engine according to the invention is designed such that the direction of movement of the two drive pistons and / or the two pressure pistons are parallel in opposite directions, whereby they can be arranged in a space-saving manner and also enables efficient operation of the internal combustion engine.

[0066] Further preferably, the drive pistons and / or the pressure pistons are arranged mirror-symmetrically around a center plane in the internal combustion engine.

[0067] In an advantageous development of the invention, the first and / or second hydraulic unit has at least one bend, preferably two bends, and can be designed accordingly compactly. Particularly preferably, the first and / or second hydraulic unit can be designed essentially U-shaped.

[0068] Advantageously, the first and / or second hydraulic unit has two longitudinally linear legs. The first leg has an upper end and a lower end. The first pressure piston is movably arranged in the first leg. The second leg has an upper end and a lower end. The second pressure piston is movably arranged in the second leg. The legs can be configured as cylinder sections.

[0069] Typically, the first and / or the second hydraulic unit has at least one opening for filling and / or emptying fluid, preferably a liquid, in particular an oil, which opening is arranged, preferably closable, in a connecting section of the substantially U-shaped hydraulic unit.

[0070] Typically, the cylinders and, consequently, the drive pistons have a circular cross-section. Preferably, the respective drive pistons are of identical design.

[0071] Furthermore, the sections of the first and / or second hydraulic unit in which the pressure pistons move, and accordingly the pressure pistons themselves, generally have a circular cross-section. Preferably, the respective pressure pistons are of identical construction.

[0072] In one embodiment of the internal combustion engine of the invention, the front sides of the drive piston or the drive pistons have a larger effective surface than the front side of the pressure piston respectively connected to the drive piston, more preferably the effective surface of the front sides of the pressure piston(s) is 75% or less, more preferably 50% or less, and more preferably 33% or less of the effective surface of the front side of the respective drive piston connected thereto.

[0073] In this embodiment, the effective surface area of ​​the front sides of the pressure piston(s) is preferably 10% or more, more preferably 20% or more of the effective surface area of ​​the front side of the respective drive piston connected thereto.

[0074] Typically, in the internal combustion engine according to the invention, there is at least one intake and one exhaust valve per cylinder.

[0075] There is usually one spark plug per cylinder.

[0076] The internal combustion engine according to the invention can comprise exactly two cylinders, but also more than two cylinders. Preferably, the internal combustion engine according to the invention has a multiple of two cylinders, for example, 2, 4, 6 cylinders, etc.

[0077] The combustion engine according to the invention can be designed, for example, as a 2-stroke engine or as a 4-stroke engine.

[0078] In the 2-stroke engine design, the scavenging, ie the expulsion of 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, co-current scavenging, e.g. with a poppet valve, or reverse scavenging.

[0079] In the case of a 4-stroke engine, there are usually at least four cylinders, preferably two pairs of a first and a second cylinder with associated components, in one of the embodiments described here.

[0080] In particular, it can be provided that two hydraulic units, each with two pressure pistons, are provided for each of the two cylinders, as described above. In a configuration with four cylinders, four hydraulic units with a total of four pressure pistons are provided.

[0081] Unless explicitly stated, where applicable, all embodiments described as "usual," "customary," or "preferred" that refer to a cylinder and / or its associated or assigned components are also considered "usual," "customary," or "preferred" for all other cylinders of the internal combustion engine. This also applies to described cylinder pairs. This applies accordingly to the embodiments that refer to a piston, whereby this applies in particular to drive pistons and pressure pistons, unless exclusive.

[0082] The present invention further relates to a method for operating an internal combustion engine in one of the embodiments described here and to the use of an internal combustion engine in one of the embodiments described here for driving a motor vehicle, aircraft or ship.

[0083] The invention also relates to a motor vehicle, aircraft or ship comprising at least one internal combustion engine according to the invention. Example

[0084] An embodiment of the internal combustion engine according to the invention is described in more detail below with reference to the figures. Fig. 1 shows a simplified schematic sectional view of a front view of an embodiment of the internal combustion engine according to the invention. Fig. 2 shows a detailed view of the transmission device 44 of the embodiment of the internal combustion engine according to the invention. Fig. 3 shows a partial detailed view of a hydraulic unit of the embodiment of the internal combustion engine according to the invention.

[0085] The embodiment of the internal combustion engine according to the invention shown in the figures has, as in Fig. 1shown, two identical cylinders 14, 15, in each of which there is a drive piston 8, 9 with a connecting rod 10, 11.

[0086] The internal combustion engine has a first cylinder 14 for fuel combustion with a first drive piston 8 movably arranged therein and a second cylinder 15 for fuel combustion with a second drive piston 9 movably arranged therein.

[0087] The first drive piston 8 is mechanically coupled to a first pressure piston 20. The second drive piston 9 is mechanically coupled to a second pressure piston 21.

[0088] The drive pistons 8, 9 and pressure pistons 20, 21 are each provided with piston rings 24.

[0089] The first drive piston 8 and the second drive piston 9 as well as the cylinders 14 and 15 are identical in construction and arranged parallel to each other.

[0090] The first pressure piston 20 and the second pressure piston 21 are identical in design. The pressure pistons 20 and 21 are smaller than the drive pistons 8 and 9 and therefore have a smaller effective surface area.

[0091] The first drive piston 8 has a connecting rod 10. The second drive piston 9 has a connecting rod 11.

[0092] The connecting rod 10 of the first drive piston 8 is connected to the first pressure piston 20 at the end facing away from the drive piston 8. This connection is preferably rigid.

[0093] The connecting rod 11 of the second drive piston 9 is connected to the second pressure piston 21 at the end facing away from the drive piston 9. This connection is preferably rigid.

[0094] The first structural unit, comprising the first drive piston 8, the first pressure piston 20, and the connecting rod 10, is preferably rigid. A second structural unit, comprising the second drive piston 9, the second pressure piston 21, and the connecting rod 11, is also preferably rigid.

[0095] The first and second structural units are therefore identical in design.

[0096] The drive pistons 8, 9 are movable in the cylinders 14 and 15, respectively, such that when the first drive piston 8 of the first cylinder 14 is at a position with a minimum distance to an upper end of the first cylinder 14, the second drive piston 9 in the second cylinder 15 is at a position with a maximum distance to the upper end of the second cylinder 15.

[0097] The internal combustion engine further comprises two separate hydraulic units 27, 28, each of which movably houses a pressure piston 20, 21. The hydraulic units 27, 28 are configured such that the pressure pistons 20, 21 move within their respective hydraulic units 27, 28 such that, when the first pressure piston 20 is at a position with a minimum distance from an upper end of the hydraulic unit 27, the second pressure piston 21 in the hydraulic unit 28 is at a position with a maximum distance from an upper end of the hydraulic unit 28.

[0098] The first 27 and the second hydraulic unit 28 are closed at the end opposite the end defined by the first and second pressure pistons 20, 21, respectively, by a first 22 and a second closing piston 23 movable in the respective hydraulic unit 27, 28.

[0099] The first 27 and the second hydraulic unit 28 have, seen from one end to the other, a first region defined by the stroke of the respective pressure piston, a second region defined by the presence of the respective impeller, and a third region after the impeller up to the respective end piston.

[0100] The cross section of the first 27 and the second hydraulic unit 28 is smaller in the first area than in the second area.

[0101] The first 27 and the second hydraulic unit 28 have two 90° bends located between the second and the third region of the hydraulic units 27, 28, so that the end region of the third region of the hydraulic units 27, 28 is arranged parallel to the first region of the hydraulic unit 27, 28.

[0102] Thus, the first and second hydraulic units 27, 28 are essentially U-shaped and two longitudinally linear legs 25, 29 and 26, 30 are formed per hydraulic unit.

[0103] The linear legs 29 and 30 can also be regarded as storage cylinders for the hydraulic fluid.

[0104] The first and second hydraulic units 27, 28 each have a closable opening (not shown in the figures) for filling and / or emptying hydraulic fluid, which is usually arranged in the transverse section 56, 57 of the respective hydraulic unit 27, 28.

[0105] As a rule, cylinders 14, 15 and, accordingly, drive pistons 8, 9 have a circular cross-section. Preferably, the respective drive pistons 8, 9 are of identical design.

[0106] Furthermore, the sections of the first and / or second hydraulic unit 27, 28 in which the pressure pistons 20, 21 move, and accordingly also the pressure pistons 20, 21, generally have a circular cross-section. Preferably, the respective pressure pistons 20, 21 are of identical construction.

[0107] As in Fig. 3 As shown, in the area of ​​the impeller 39, 40 of the first and second hydraulic units 27, 28, there is a circular arc-shaped extension 55 of the respective hydraulic unit wall, in which the blades 54 rotate when the hydraulic fluid moves. This circular arc-shaped extension 55 of the respective hydraulic unit wall is designed such that almost no hydraulic fluid, or none at all, can flow past the blades 54 on the outside.

[0108] The blade wheel 39, 40 present in the second area of ​​the respective hydraulic unit 27, 28, together with the circular arc-shaped extension 55, constructively results in a turbine around the respective blade wheel 39, 40, which transmits the force transmitted by the movement of the hydraulic fluid to the blades 54 of the blade wheels 39, 40 into a rotary back and forth movement of the blade wheel axes 41, 42.

[0109] The blade wheel axis 41, 42 in the first and second turbines formed is arranged perpendicular to the direction of movement of the first and second drive pistons 8, 9 and thus also to the direction of movement of the first and second pressure pistons 20, 21.

[0110] The impeller axis 41, 42 is arranged in the first and second turbines formed perpendicular to the direction of movement of the respective hydraulic fluid.

[0111] Furthermore, the first and second turbines are designed such that the hydraulic fluid flows out of the turbine in the same direction in which it flows into the turbine, ie that the turbine inlet and outlet are 180° opposite each other.

[0112] The circular arc of the extension preferably covers an angular range of 180°.

[0113] The axes 41, 42 of the paddle wheels 39, 40 lie on an imaginary extended line of the hydraulic unit wall without the circular arc-shaped extension.

[0114] Furthermore, the axes 41, 42 of the paddle wheels 39, 40 are mounted in the respective wall sections 37, 38 of the hydraulic unit 27, 28.

[0115] How to continue in Fig. 3As shown, the drive piston 8 has an effective surface area A 1 , and after ignition of the fuel / air mixture in cylinder 14, the piston is subjected to a pressure p 1 . The pressure piston 20 has an effective surface area A 2 , which is smaller than A 1 , and a pressure p 2 is generated that is greater than p 1 . A 3 denotes the surface area of ​​the blades of the impeller.

[0116] The internal combustion engine further comprises a shaft 43 on which a transmission unit 44 is arranged. As shown in Fig. 2 As shown, the transmission element 44 comprises two annular freewheels 46, 47, which have toothings 52, 53 on the side of their outer rings.

[0117] By means of the transmission device 44, the rotary back-and-forth movement of the bucket wheel axes 41, 42 is transferred into a continuous rotational movement of the shaft 43, to which, for example, a working machine is connected.

[0118] The freewheels 46, 47 each have an outer and an inner side, designed as an outer and inner ring, which can lock against each other (drive mode) or run freely (freewheel mode). The freewheels 46, 47 of the transmission device 44 are structurally identical.

[0119] The outer side of the first freewheel 46 is operatively connected to the axis of the first impeller 39 and the outer side of the second freewheel 47 is operatively connected to the axis of the second impeller 40 by means of a gear connection, so that the reciprocating movement of the impeller axes 41, 42 is transmitted to the outer side of the freewheels 46, 47.

[0120] For this purpose, a gear 50, 51 is located at the end of each of the paddle wheel axles 41, 42, which engages in toothings 52, 53 present on the lateral outer surfaces of the first and second freewheels 46, 47.

[0121] The inner sides of the freewheels 46, 47 are connected to the shaft 43 in such a way that they rotate freely or lock in the same direction, i.e., they are mounted mirror-inverted on the shaft 43. Thus, the reciprocating motion of the hydraulic fluid in the respective hydraulic unit 27, 28 is translated into a rotary reciprocating motion of the outer side of the first freewheel 46 and an opposing rotary reciprocating motion of the second freewheel 47. The arrangement of the freewheels 46, 47 on the shaft 43 enables the continuous rotation of the shaft 43 in one direction.

[0122] The rotary back and forth movement of the first impeller 39 and the second impeller 40, and of the first freewheel 46 and the second freewheel 47 each takes place over an angular range of 180°.

[0123] Gears and any bearings of the motor according to the invention are supplied with lubricant in a conventional manner.

[0124] As in Fig. 1As can be seen, the internal combustion engine according to the invention is designed in the exemplary embodiment such that the entirety of the first cylinder 14 and the first hydraulic unit 27, including all further elements located therein, is arranged mirror-symmetrically to the entirety of the second cylinder 15 and the second hydraulic unit 28, including all further elements located therein.

[0125] The movement of the first 8 and the second drive piston 9 is coupled to each other and this coupling is effected by means of a chain 33 deflected via a gear 34. The chain 33 is connected at its two ends 32, 36 to a rigid rod 12, 13, which is attached to the bottom (underside) of the first and second drive pistons 8, 9, respectively.

[0126] The chain 33 is designed so that the teeth 35 of the idler gear 34 can engage in recesses in the chain links.

[0127] During engine operation, a fuel-air mixture is fed into the combustion chambers 6, 7 of cylinders 14, 15 through an intake valve 1, 2. Combustion gases discharged from each cylinder 14, 15 are discharged from each cylinder 11, 12 through an exhaust valve 5.

[0128] The fuel-air mixture is ignited by means of a spark plug 3, 4 located in the combustion chamber 6, 7 of the cylinder 14, 15.

[0129] The resulting exhaust gases can be discharged via the exhaust openings 18, 19 with valves 16, 17.

[0130] For example, ignition in the first cylinder 14 of the engine occurs at a position close to P min of the first drive piston 8. As a result, the first drive piston 8 in the first cylinder 14 moves in the "out of the cylinder" direction due to the force created by the explosive combustion process, i.e., causes a forward stroke of the drive piston 8. This forward stroke movement induces a return stroke movement of the first pressure piston 20 in the first hydraulic unit 27. This in turn pushes the hydraulic fluid 31 towards the turbine and sets the impeller 39 in motion.

[0131] The rotational movement of the impeller axle 41 is transmitted by means of the transmission device 44 through the gear connection of gear 50 at the impeller axle end to the outer side of the first freewheel 46, which has a toothing 52 on this outer side into which the gear 50 engages. This freewheel 46 is in locking mode and thus transmits the rotational movement to the shaft 43 via its inner ring.

[0132] Furthermore, the coupling of the two drive pistons 8, 9 via the chain connection causes a return stroke movement of the second drive piston 9, which in turn results in a forward stroke movement of the second pressure piston 21 and causes a movement of the hydraulic fluid in the second hydraulic unit 28 following the pressure piston.

[0133] The rotational movement thus generated at the second impeller 40 is not transmitted to the shaft 43 by the second freewheel 47 of the transmission device 44, which then runs freely.

[0134] When the second cylinder 15 is ignited, the corresponding opposite movements are effected in an analogous manner.

[0135] Overall, the force generated by the respective combustion of fuel in the cylinders 14, 15 is transmitted to the shaft 43 in such a way that it is set in a continuous rotational movement always in the same direction. List of reference symbols:

[0136] 1, 2 Inlet valve 3, 4 Spark plug 5 Exhaust valve 6, 7 Combustion chamber 8, 9 Drive piston 10, 11 Connecting rod 12, 13 Rigid connecting rod 14, 15 Cylinder 16, 17 Exhaust valves 18, 19 Exhaust port 20, 21 Pressure piston 22, 23 End piston 24 Piston rings 25, 26 Longitudinal leg of the hydraulic unit 27, 28 Hydraulic unit 29, 30 Longitudinal leg of the hydraulic unit 31, 5 8 Hydraulic fluid 32, 36 Chain ends 33 Chain 34 Deflection gear 35 Teeth of the deflection gear 37, 38 Bearing 39, 40 Paddle wheel 41, 42 Paddle wheel axle 43 Shaft 44Transmission device 46, 47Freewheel 50, 51Gears 52, 53Toothing (side gears) 54Blade 55Circular extension 56, 57Cross sections of the hydraulic unit

Claims

1. Internal combustion engine, which comprises - a first cylinder 14 for fuel combustion with a first drive piston 8 movably arranged therein, - a second cylinder 15 for fuel combustion with a second drive piston 9 movably arranged therein, and - a shaft 43, wherein - the internal combustion engine is designed such that the drive pistons 8, 9 move back and forth in opposite directions in the two cylinders 14, 15, - the first drive piston 8 is mechanically coupled to a first pressure piston 20, - the second drive piston 9 is mechanically coupled to a second pressure piston 21, and wherein the internal combustion engine is characterized by- the drive pistons 8, 9 are coupled to one another in such a way that a forward stroke movement of the first drive piston 8 in the first cylinder 14 causes a return stroke movement of the second drive piston 9 in the second cylinder 15, - it further comprises a first hydraulic unit 27, in which the first pressure piston 20 is movably arranged, as well as a first impeller 39 arranged in the first hydraulic unit 27 and, separately therefrom, a second hydraulic unit 28, in which the second pressure piston 21 is movably arranged, as well as a second impeller 40 arranged in the second hydraulic unit 28, - wherein the internal combustion engine is further configured such that the first 8 and the second drive piston 9 are coupled to one another in such a way that a forward stroke movement of the first drive piston 8 in the first cylinder 14 causes a return stroke movement of the first pressure piston 20 in the first hydraulic unit 27,and a return stroke movement of the second drive piston 9 in the second cylinder 15 causes a forward stroke movement of the second pressure piston 21 in the second hydraulic unit 28, so that the two pressure pistons 20, 21 move in opposite directions in their respective hydraulic units 27, 28 - whereby the hydraulic fluid 31, 58 located in the respective hydraulic unit 27, 28, preferably a liquid, is set in motion by the movement of the pressure pistons 20, 21 and the moving hydraulic fluid 31, 58 causes a rotary back-and-forth movement of the axis of the impeller 39, 40 located in the respective hydraulic unit 27, 28 - and the rotary back-and-forth movement of the axes 41, 42 of the impellers 39, 40 are transmitted by means of a transmission device 44 into a continuous rotary movement of the shaft 43.

2. Internal combustion engine according to claim 1, characterized in that- the drive pistons 8, 9 in the cylinders 14, 15 are movable in such a way that, when the first drive piston 8 of the first cylinder 14 is at a position with a minimum distance to an upper end of the first cylinder 14, the second drive piston 9 in the second cylinder 15 is at a position with a maximum distance to an upper end of the second cylinder 15 and / or - the movements of the pressure pistons 20, 21 in their respective hydraulic unit 27, 28 are such that, when the first pressure piston 20 is at a position with a minimum distance to an upper end of the first hydraulic unit 27, the second pressure piston 21 is at a position with a maximum distance to an upper end of the hydraulic unit 28.

3. Internal combustion engine according to claim 1 or 2, characterized in thatthe first pressure piston 20 has a smaller effective surface than the first drive piston 8 and / or the second pressure piston 21 has a smaller effective surface than the second drive piston 9.

4. Internal combustion engine according to one of the preceding claims, characterized in that the first 27 and / or the second hydraulic unit 28 is closed at the end opposite the end defined by the first or second pressure piston by a first 22 or second closing piston 23 movable in the respective hydraulic unit 27, 28.

5. Internal combustion engine according to one of the preceding claims, characterized in thatthe first 27 and / or the second hydraulic unit 28 comprises, from one end to the other, a first region defined by the stroke of the respective pressure piston, a second region defined by the presence of the respective impeller, and a third region after the impeller up to the respective end piston, wherein preferably the cross section of the first and / or the second hydraulic unit 27, 28 is smaller in the first region than in the second region.

6. Internal combustion engine according to one of the preceding claims, characterized in thatby means of the impeller 39, 40 present in the hydraulic units 27, 28, a turbine is constructed in the respective hydraulic unit 27, 28, which turbine transmits the force transmitted to the blades 54 of the impeller 39, 40 by the movement of the hydraulic fluid 31, 58 into a rotary back and forth movement of the impeller axes 41, 42, wherein the hydraulic fluid 31, 58 flows through the formed turbines preferably at least partially tangentially.

7. Internal combustion engine according to one of the preceding claims, characterized in that the transmission device 44 comprises a first freewheel 46 and a second freewheel 47, wherein the outer side of the first freewheel 46 is operatively connected to the axis 41 of the first impeller 39 and / or the outer side of the second freewheel 47 is operatively connected to the axis 42 of the second impeller 40.

8. Internal combustion engine according to claim 7, characterized in thatthe operative connection between the outer side of the first freewheel 46 and the axis 41 of the first impeller 39 and / or the operative connection of the outer side of the second freewheel 47 and the axis 42 of the second impeller 40 is effected by means of a gear connection.

9. Internal combustion engine according to claim 7 or 8, characterized in that the inner sides of the freewheels 46, 47 are each connected to the shaft 43 in such a way that they run freely or lock in the same direction, so that the shaft 43 is set into continuous rotation by a rotary back and forth movement of the outer sides of the freewheels 46, 47.

10. Internal combustion engine according to one of the preceding claims, characterized in that the entirety of the first cylinder 14 and the first hydraulic unit 27 is arranged mirror-symmetrically to the entirety of the second cylinder 15 and the second hydraulic unit 28.

11. Internal combustion engine according to one of the preceding claims, characterized in thatthe coupling of the movement of the first 8 and second drive piston 9 is effected by means of a chain 33 deflected via a gear wheel 34.

12. Internal combustion engine according to one of the preceding claims, characterized in that the drive pistons 9, 10 and / or the pressure pistons 23, 24 are arranged parallel to each other.

13. A method for operating an internal combustion engine according to any one of the preceding claims.

14. Use of an internal combustion engine according to one of claims 1 to 12 for driving a motor vehicle, aircraft or ship.

15. Motor vehicle, aircraft or ship, comprising at least one internal combustion engine according to one or more of claims 1 to 12.

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