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] 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., torque is generated. An alternative type of reciprocating piston engine is known from US 2010 / 275884 A1.

[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 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, 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, 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, and a second impeller arranged in the second hydraulic unit, wherein the internal combustion engine is further arranged such that the first and 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,The movement of the pressure pistons sets the hydraulic fluid in motion, causing a rotary back-and-forth motion of the impeller axis located in the respective hydraulic unit. This rotary back-and-forth motion of the impeller axis is then transmitted into a continuous rotational motion of the shaft by means of a transmission device.

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

[0007] The operating 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] For this purpose, an ignitable fuel-oxygen, normally fuel-air, mixture is introduced into the combustion chambers of the cylinders, compressed there, and then ignited near the piston position at minimum distance to the cylinder head (P min ). The resulting gases expand explosively and cause the piston to move towards the position at maximum distance to the cylinder head (P max ).

[0009] The hydraulic units provided according to the invention enable, firstly, 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. Secondly, the pressure generated by the reciprocating movement of the drive pistons can be increased by selecting the ratios of the cross-sectional areas of the cylinders and the hydraulic unit.

[0010] This can reduce fuel consumption and enable an improved piston thrust motion in terms of fuel consumption and efficiency. Consequently, this can lead to an increase in combustion efficiency and thus the overall efficiency of the internal combustion engine.

[0011] The hydraulic fluid is located inside the hydraulic units.

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

[0013] The hydraulic unit is usually designed in the area of ​​the stroke of the pressure pistons in such a way that the pressure pistons seal against the inner walls of the hydraulic unit.

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

[0015] The impeller in each hydraulic unit forms a turbine, which converts the force transmitted by the movement of the hydraulic fluid onto the impeller blades 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 to the blades of the impeller wheels by means of the hydraulic fluid, 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 paddle wheels are at least partially, preferably completely, subjected to a flow perpendicular to their direction of movement.

[0018] The design of the turbines ensures that the tangential forces are always present, i.e., throughout the entire operating process, at the maximum possible sinusoidal angle of 90°. Thus, the engine according to the invention offers the advantages of achieving both the highest possible torque at low speeds and a relatively constant torque across various speeds. This results in higher efficiency compared to conventionally designed piston engines, and consequently, fuel savings. This can also have a beneficial impact on the environment.

[0019] 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" describes a movement of the piston out of the unit, and "reverse" or "return stroke" describes a movement of the piston into the unit.

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

[0021] The "front of a piston" refers to the side of the piston facing the respective unit (e.g., the cylinder), and the "back or underside of a piston" refers to the side of the piston facing away from the respective unit (e.g., the 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 move in opposite directions, and by the coupling of the drive pistons to each other.

[0023] In the combustion engine according to the invention, the pressure pistons are mechanically coupled to the drive pistons, i.e. the first drive piston is mechanically coupled to the first pressure piston and the second drive piston 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 in a position with minimum distance to an upper end of the first cylinder, the second drive piston in the second cylinder is in a position with 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 in a position with minimum distance to an upper end of the first hydraulic unit, the second pressure piston is in a position with maximum distance to an upper end of the hydraulic unit.

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

[0026] The "effective surface" refers to 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 further development, the rear side of the first drive piston can be rigidly connected to the rear side of the first pressure piston, and / or the rear side of the second drive piston can be rigidly connected to the rear side of the second pressure piston. This allows for improved stability and efficient force 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 consists of a rigid, linear rod, for example a connecting rod.

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

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

[0033] Typically, the driving pistons in the cylinders are movable in such a way that when the first driving piston of the first cylinder is in a position with minimal distance to the upper end of the first cylinder, the second driving piston in the second cylinder is in a position with 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 in a position with minimum distance to an upper end of the hydraulic unit, the second pressure piston in the hydraulic unit is in a position with 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] Preferably, the first and / or second hydraulic unit comprises, from one end to the other, a first area defined by the stroke of the respective pressure piston, a second area defined by the presence of the respective impeller, and a third area 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 area than in the second area.

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

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

[0040] 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, i.e., usually that the turbine inlet and outlet are opposite each other by 180°.

[0042] In the area of ​​the impeller of the first and / or the second hydraulic unit, a circular arc extension of the respective hydraulic unit wall is preferably present, which forms part of the turbine and in which the impeller blades rotate when the hydraulic fluid moves. Preferably, this circular arc extension of the respective hydraulic unit wall is designed such that virtually no or 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 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 surface, which can be designed, for example, as an outer and inner ring that can lock against each other (drive mode) or spin freely (freewheel mode). The freewheels of the transmission device are usually identical in construction.

[0048] Preferably, the outside of the first freewheel is operatively connected to the axis of the first paddle wheel and / or the outside of the second freewheel is operatively connected to the axis of the second paddle wheel, wherein the operative connection is designed such that the reciprocating movement of the paddle wheel axis(s) is transmitted to the outside of the freewheel(s).

[0049] The inner surfaces of the freewheels are typically connected to the shaft in such a way that the freewheels rotate freely or lock in the same direction. Thus, the back-and-forth movement of the hydraulic fluid in the respective hydraulic unit is converted into a rotary back-and-forth movement of the outer surface of the first freewheel and a counter-rotating back-and-forth movement of the second freewheel. This arrangement of the freewheels on the shaft allows for continuous rotation of the shaft in one direction.

[0050] The outer surfaces of the freewheels can be coupled to each other in such a way that they support an opposing movement of the outer surfaces of the two freewheels.

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

[0052] Typically, the rotary back-and-forth movement of the first paddle wheel and / or the second paddle wheel is performed through an angular range of at least 60°, preferably at least 90°, particularly preferably at least 120°, and most preferably at least 150° or more.

[0053] It can be provided that the rotary back-and-forth movement of the first paddle wheel and / or the second paddle wheel is carried out by 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 paddle wheel and / or the second paddle wheel is carried out by an angular range of 160° to 200°, preferably 170° to 190°, even more preferably 175° to 185°, and most preferably 180°.

[0055] Furthermore, the rotary back-and-forth movement of the first freewheel and / or the second freewheel typically occurs through an angular range of at least 60°, preferably at least 90°, particularly preferably at least 120°, and most preferably 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 is carried out through 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 is carried out by an angular range of 160° to 200°, preferably 170° to 190°, even more preferably 175° to 185°, and most preferably 180°.

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

[0059] Pistons, including drive and pressure pistons, are usually equipped with piston rings.

[0060] In one embodiment, the internal combustion engine according to the invention is designed such that the entire assembly of first cylinder and first hydraulic unit, including all further elements contained therein, is arranged in a mirror-symmetrical manner to the entire assembly of second cylinder and second hydraulic unit, including all further elements contained therein.

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

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

[0063] The chain to be deflected 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 deflection gear can engage in recesses in the chain links.

[0065] Preferably, the combustion engine according to the invention is arranged such that the direction of movement of the two drive pistons and / or the two pressure pistons are oppositely parallel, which allows them to be arranged in a space-saving manner and also enables efficient operation of the combustion engine.

[0066] Preferably, the drive pistons and / or the pressure pistons are arranged in a mirror-symmetrical manner around a central plane in the internal combustion engine.

[0067] In an advantageous embodiment of the invention, the first and / or the second hydraulic unit has at least one bend, preferably two bends, and can be designed to be correspondingly compact. It is particularly preferred that the first and / or the second hydraulic unit be essentially U-shaped.

[0068] Advantageously, the first and / or second hydraulic unit has two longitudinally linear arms. The first arm has an upper end and a lower end. The first pressure piston is movably arranged within the first arm. The second arm also has an upper end and a lower end. The second pressure piston is movably arranged within the second arm. The arms can be designed as cylindrical 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 is arranged in a connecting section of the essentially U-shaped hydraulic unit, preferably closable.

[0070] As a rule, the cylinders and consequently the driving pistons have a circular cross-section. Preferably, the respective driving pistons are identical in design.

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

[0072] In one embodiment of the internal combustion engine of the invention, the front faces of the drive piston(s) have a larger effective surface area than the front face of the respective pressure piston connected to the drive piston; more preferably, the effective surface area of ​​the front faces of the pressure piston(s) is 75% or less, more preferably 50% or less, and more preferably 33% or less of the effective surface area of ​​the front face of the respective drive piston connected to it.

[0073] In this embodiment, the effective surface area of ​​the front faces of the pressure piston(s) is preferably 10% or more, more preferably 20% or more of the effective surface area of ​​the front face of the respective drive piston associated therewith.

[0074] Typically, in the internal combustion engine according to the invention, at least one inlet and one exhaust valve are provided 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, i.e., for example, 2, 4, 6 cylinders, etc.

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

[0078] 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.

[0079] In the version as 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 for every two cylinders, two hydraulic units, each with two pressure pistons as described above, are provided. In a configuration with four cylinders, therefore, four hydraulic units with a total of four pressure pistons are provided.

[0081] Unless explicitly stated otherwise, where applicable, all embodiments described as "customary," "ordinary," or "preferable" that relate to a cylinder and / or its associated or related components shall also be considered "customary," "ordinary," or "preferable" for all other cylinders of the internal combustion engine. This also applies to described cylinder pairs. This applies accordingly to embodiments relating to a piston, in particular to the drive piston and the pressure piston, unless explicitly excluded.

[0082] The present invention further relates to a method for operating an internal combustion engine in one of the embodiments described herein and to the use of an internal combustion engine in one of the embodiments described herein for powering 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] One embodiment of the internal combustion engine according to the invention is described in more detail below with reference to the figures. Fig. 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. 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 detail 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 features, as shown in Fig. 1shown are two identical cylinders 14, 15, each containing a driving 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 driving piston 8 movably arranged therein and a second cylinder 15 for fuel combustion with a second driving 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 equipped with piston rings 24.

[0089] The first driving piston 8 and the second driving 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 construction. 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 piston 8 has a connecting rod 10. The second 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 opposite the drive piston 9. This connection is preferably rigid.

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

[0095] The first and second building units are therefore identical in construction.

[0096] The driving pistons 8, 9 are movable in the cylinders 14 and 15 respectively such that when the first driving piston 8 of the first cylinder 14 is in a position with minimum distance to an upper end of the first cylinder 14, the second driving piston 9 in the second cylinder 15 is in a position with 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 containing a movable pressure piston 20, 21. The hydraulic units 27, 28 are arranged such that the pressure pistons 20, 21 move within their respective hydraulic units 27, 28 such that when the first pressure piston 20 is in a position with minimum distance to an upper end of hydraulic unit 27, the second pressure piston 21 in hydraulic unit 28 is in a position with maximum distance to an upper end of 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 and 21, respectively, by a first 22 and second closing piston 23 movable in the respective hydraulic unit 27 and 28.

[0099] The first 27 and the second hydraulic unit 28, viewed from one end to the other, have a first area defined by the stroke of the respective pressure piston, a second area defined by the presence of the respective impeller, and a third area 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 third sections of the hydraulic units 27, 28, such that the end section of the third section of the hydraulic units 27, 28 is arranged parallel to the first section of the hydraulic unit 27, 28.

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

[0103] The linear legs 29 and 30 can also be considered as reservoir 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 and 15, and consequently also the driving pistons 8 and 9, have a circular cross-section. Preferably, the respective driving pistons 8 and 9 are identical in design.

[0106] Furthermore, as a rule, the sections of the first and / or the second hydraulic unit 27, 28, in which the pressure pistons 20, 21 move, and accordingly also the pressure pistons 20, 21, have a circular cross-section. Preferably, the respective pressure pistons 20, 21 are identical in 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, a circular arc extension 55 of the respective hydraulic unit wall is present in each of the hydraulic units, in which the impellers 54 rotate when the hydraulic fluid moves. This circular arc extension 55 of the respective hydraulic unit wall is designed such that virtually no or no hydraulic fluid can flow past the outside of the impellers 54.

[0108] The impeller 39, 40, located in the second area of ​​each hydraulic unit 27, 28, together with the arc-shaped extension 55, constructively forms a turbine around the respective impeller 39, 40, which transmits the force transmitted by the movement of the hydraulic fluid onto the blades 54 of the impellers 39, 40 into a rotary back-and-forth movement of the impeller axes 41, 42.

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

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

[0111] Furthermore, the first and second turbines are designed such that the hydraulic fluid flows out of the turbine in the same direction as it flows into the turbine, i.e., 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 arc-shaped extension.

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

[0115] What's next in Fig. 3As shown, the drive piston 8 has an effective surface area A1 and is subjected to a pressure p1 after ignition of the fuel / air mixture in cylinder 14. The pressure piston 20 has an effective surface area A2, which is smaller than A1, and generates a pressure p2, which is greater than p1. A3 denotes the surface area of ​​the impeller blades.

[0116] The internal combustion engine also has a shaft 43 on which a transmission unit 44 is arranged. As in Fig. 2 As shown, the transmission element 44 comprises two ring-shaped freewheels 46, 47, each of which has teeth 52, 53 on the side of its outer rings.

[0117] The transmission device 44 transmits the rotary back-and-forth movement of the paddle wheel axes 41, 42 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 surface, designed as an outer and inner ring, which can lock against each other (drive mode) or spin freely (freewheel mode). The freewheels 46, 47 of the transmission device 44 are identical in construction.

[0119] The outside of the first freewheel 46 is operatively connected to the axis of the first paddle wheel 39 and the outside of the second freewheel 47 to the axis of the second paddle wheel 40 by means of a gear connection, so that the reciprocating movement of the paddle wheel axes 41, 42 is transmitted to the outside 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 teeth 52, 53 located on the lateral outer surfaces of the first and second freewheel 46, 47.

[0121] The inner surfaces of the freewheels 46, 47 are connected to the shaft 43 such that they rotate and lock in the same direction, i.e., they are mounted on the shaft 43 in a mirror-image configuration. Thus, the reciprocating motion of the hydraulic fluid in the respective hydraulic unit 27, 28 is converted into a rotary reciprocating motion of the outer surface of the first freewheel 46 and a counter-rotating reciprocating motion of the second freewheel 47. This 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 paddle wheel 39 and the second paddle wheel 40, and of the first freewheel 46 and the second freewheel 47 each takes place through 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 combustion engine according to the invention is designed in the exemplary embodiment such that the entire assembly of first cylinder 14 and first hydraulic unit 27, including all further elements contained therein, is arranged in a mirror-symmetrical manner to the entire assembly of second cylinder 15 and second hydraulic unit 28, including all further elements contained therein.

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

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

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

[0128] The ignition of the fuel-air mixture is effected 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 near P min of the first drive piston 8. This causes the first drive piston 8 in the first cylinder 14 to move "out of the cylinder" due to the force generated by the explosive combustion process, i.e., it causes a forward stroke of the drive piston 8. This forward stroke induces a return stroke of the first pressure piston 20 in the first hydraulic unit 27. This, in turn, forces the hydraulic fluid 31 towards the turbine and sets the impeller 39 in motion.

[0131] The rotational movement of the impeller shaft 41 is transmitted by means of the transmission device 44 through the gear connection of gear 50 at the end of the impeller shaft to the outer surface of the first freewheel 46, which has a toothed section 52 on this outer surface into which the gear 50 engages. This freewheel 46 is in the locked position and consequently 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 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 ignition occurs in the second cylinder 15, the corresponding opposite movements are effected in an analogous manner.

[0135] Overall, the force generated by the respective combustion of fuel in cylinders 14, 15 is thus transferred to the shaft 43 in such a way that it is set into a continuous rotational movement always in the same direction. Reference symbol list:

[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 Hydraulic unit longitudinal leg 27, 28 Hydraulic unit 29, 30 Hydraulic unit longitudinal leg 31, 58 Hydraulic fluid 32, 36 Chain ends 33 Chain 34 Idler gear 35 Idler gear teeth 37, 38 Bearing 39, 40 Impeller 41, 42 Impeller shaft 43 Shaft 44 Transmission device 46, 47 Freewheel 50, 51 Gears 52, 53 Toothing (sideways gears) 54 Blade 55 Arc-shaped extension 56, 57 Transverse sections of the hydraulic unit

Claims

1. An internal combustion engine, comprising: - a first cylinder 14 for the combustion of fuel, including a first drive piston 8 arranged movably therein; - a second cylinder 15 for the combustion of fuel, including a second drive piston 9 arranged movably therein; and - a shaft 43; - the internal combustion engine being configured in such a way that the drive pistons 8, 9 move back and forth in opposite directions in the two cylinders 14, 15; - the first drive piston 8 being mechanically coupled to a first pressure piston 20; - the second drive piston 9 being mechanically coupled to a second pressure piston 21; and the internal combustion engine being characterized in that - 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; - the internal combustion engine furthermore comprises a first hydraulic unit 27, in which the first pressure piston 20 is movably arranged, as well as a first impeller 39 which is 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 which is arranged in the second hydraulic unit 28; - the internal combustion engine furthermore being configured so that the first drive piston 8 and 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 the respective hydraulic units 27, 28 thereof; - the hydraulic fluid 31, 58 present in the respective hydraulic unit 27, 28, preferably a liquid, being caused to move as a result of the movement of the pressure pistons 20, 21, and the moving hydraulic fluid 31, 58 causing a rotational back and forth movement of the shaft of the impeller 39, 40 situated in the respective hydraulic unit 27, 28; and - the rotational back and forth movement of the shafts 41, 42 of the impellers 39, 40 being converted by means of a conversion device 44 into a continuous rotational movement of the shaft 43.

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

3. The internal combustion engine according to claim 1 or 2, characterized in that the 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. The internal combustion engine according to any one of the preceding claims, characterized in that the first hydraulic unit 27 and / or the second hydraulic unit 28 are closed at the end located opposite the end that is defined by the first or second pressure piston by a first closing piston 22 or second closing piston 23 that is movable in the respective hydraulic unit 27, 28.

5. The internal combustion engine according to any one of the preceding claims, characterized in that the first hydraulic unit 27 and / or the second hydraulic unit 28, from one end to the other, comprise a first region defined by the length of the stroke of the respective pressure piston, a second region defined by the presence of the respective impeller, and a third region downstream from the impeller to the respective closing piston, the cross-section of the first and / or second hydraulic units 27, 28 in the first region preferably being smaller than in the second region.

6. The internal combustion engine according to any one of the preceding claims, characterized in that the impeller 39, 40 that is present in each case in the hydraulic units 27, 28, from a design perspective, creates a turbine in the respective hydraulic unit 27, 28, which converts the force transmitted by the movement of the hydraulic fluid 31, 58 to the vanes 54 of the impellers 39, 40 into a rotational back and forth movement of the impeller shafts 41, 42, the hydraulic fluid 31, 58 flowing at least partially tangentially through the formed turbines.

7. The internal combustion engine according to any one of the preceding claims, characterized in that the conversion device 44 comprises a first freewheel 46 and a second freewheel 47, the outer side of the first freewheel 46 being operatively connected to the shaft 41 of the first impeller 39 and / or the outer side of the second freewheel 47 being operatively connected to the shaft 42 of the second impeller 40.

8. The internal combustion engine according to claim 7, characterized in that the operative connection between the outer side of the first freewheel 46 to the shaft 41 of the first impeller 39 and / or the operative connection of the second freewheel 47 to the shaft 42 of the second impeller 40 takes place by means of a gear wheel connection.

9. The 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 so as to run freely or block in the same direction, so that the shaft 43 is caused to perform a continuous rotation as a result of a rotational back and forth movement of the outer sides of the freewheels 46, 47.

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

11. The internal combustion engine according to any one of the preceding claims, characterized in that the coupling of the movement of the first drive piston 8 and second drive piston 9 is carried out by means of a chain 33 that is deflected by a gear wheel 34.

12. The combustion engine according to any one of the preceding claims, characterized in that the drive pistons 9, 10 and the pressure pistons 23, 24 are arranged parallel to one another.

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 any one of claims 1 to 12 for driving a motor vehicle, an aircraft or a ship.

15. A motor vehicle, an aircraft or a ship, comprising at least one internal combustion engine according to any one or more of claims 1 to 12.

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