TANGENTIAL COMBUSTION ENGINE WITH HYDRAULIC DEVICE

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] US 8 104 436 B2 relates to a quasi-free-piston engine with an additional crankshaft for connecting piston assemblies of the free-piston engine to a flywheel. The power delivered by the combustion pistons of the free-piston engine is converted into hydraulic power via pump pistons, with the additional crankshaft and flywheel setting the TDC position of the combustion pistons.

[0005] DE 35 31 862 A1 relates to a reciprocating piston internal combustion engine having at least one piston with at least one piston surface guided in a cylinder and having at least one toothed rack associated with the piston surface, which rack drives a gear wheel which is connected to an output shaft via a freewheel which locks in one direction of rotation, and having a device which returns the piston via at least one passive stroke.

[0006] DE 10 2006 003026 A1 relates to a transmission in which an oscillating force is transmitted either via a shaft or a rack to a spur gear in a variable speed transmission equipped with five spur gears. The conversion of the oscillating movement into a rotating movement is performed by two pairs of spur gears, each of which has a freewheel in the same direction of rotation.

[0007] The present invention aims to further increase the efficiency of conventional internal combustion engines in order to enable more fuel-efficient operation.

[0008] The present invention therefore provides an internal combustion engine comprising a shaft on which a drive element is arranged, a first cylinder for fuel combustion with a first drive piston movably arranged therein, and a second cylinder for fuel combustion with a second drive piston movably arranged therein, wherein the internal combustion engine is configured such that the drive pistons in the two cylinders move back and forth in opposite directions, which is characterized in that the first drive piston is mechanically coupled to a first pressure piston, the second drive piston is mechanically coupled to a second pressure piston, the first and second drive pistons are operatively connected to the drive element, and the internal combustion engine has a hydraulic unit in which the first pressure piston and the second pressure piston are movably arranged and which contains a fluid, preferably a liquid, in a space between the pressure pistons, wherein the internal combustion engine is further configured such that a return stroke movement of the first pressure piston is induced in the hydraulic unit by means of a forward stroke movement of the first drive piston, whereby a forward stroke movement of the second pressure piston is induced in the hydraulic unit and thus a return stroke movement of the second drive piston is induced, and wherein the operative connection between the drive pistons and the drive element is configured such that the force generated by the reciprocating movement of the drive pistons is transmitted tangentially to the drive means and the drive element sets the shaft in a continuous rotational movement.

[0009] 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.

[0010] 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.

[0011] 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 ).

[0012] The hydraulic unit provided according to the invention enables the transmission of the force acting on the pressure pistons to the drive pistons in the cylinders by means of the hydraulic fluid contained in the hydraulic unit. The hydraulic unit can thus be considered a pressure booster unit and, by providing additional force, can support the movement of the drive pistons, thereby reducing fuel consumption and enabling a piston thrust movement that is improved in terms of fuel consumption and efficiency. This can consequently enable an increase in combustion efficiency and thus in the efficiency of the internal combustion engine.

[0013] The hydraulic fluid is located in an interior space of the hydraulic unit between the pressure pistons. This interior space of the hydraulic unit can also be referred to as the volume that the hydraulic unit creates between the pressure pistons, which are movably arranged within the hydraulic unit.

[0014] The hydraulic fluid used is preferably a liquid such as a mineral oil or water-based fluid.

[0015] 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.

[0016] 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 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 .

[0017] The transmission of the force generated by the thrust movement of the respective drive pistons to the drive element takes place in such a way that the force is always transmitted tangentially, i.e. at a sine angle of 90°, to the shaft.

[0018] The internal combustion engine according to the present invention can also be referred to as a "tangential internal combustion engine" or simply "tangential engine" due to the special design and arrangement of the cylinders and the special transmission of the forces generated during fuel combustion into a torque.

[0019] The design of the tangential motor ensures that the tangential forces always act or are transmitted at the maximum possible sinusoidal angle of 90°, i.e., throughout the entire working process. Thus, the motor 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 motor 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.

[0020] The hydraulic unit operates in such a way that the force resulting from the forward stroke of the first drive piston acts on the first pressure piston via the mechanical coupling, causing it to move in the reverse direction, i.e., move in such a way that hydraulic fluid in the hydraulic unit is forced into the chamber of the hydraulic unit toward the second pressure piston. As a result, the second pressure piston moves in the opposite direction, i.e., in the forward direction, out of the chamber of the hydraulic unit.

[0021] 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.

[0022] For example, the movement of the drive piston after ignition of the gas mixture in the direction out of the cylinder is referred to as "propulsion" or "pre-stroke". The "front of a piston" is understood to be the side of the piston facing the respective unit (e.g. the cylinder), and the back of a piston is understood to be the side of the piston facing away from the respective unit (e.g. cylinder).

[0023] Due to a movement of the first pressure piston in the forward direction and the resulting movement of the hydraulic fluid located in the interior of the hydraulic unit, the second pressure piston in the hydraulic unit moves in the reverse direction, i.e. in the opposite direction to the first pressure piston.

[0024] "Opposite movement" means a movement of the pressure pistons in the hydraulic unit such that, for example, the first pressure piston moves in the forward direction and thus induces a movement in the reverse direction of the second pressure piston, and vice versa.

[0025] The opposing movement of the pressure pistons in the hydraulic unit 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.

[0026] 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.

[0027] 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.

[0028] 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.

[0029] Preferably, the rigid connection between the respective drive pistons and the respective pressure pistons is made by a rigid, linear rod, for example a connecting rod.

[0030] 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 enables increased stability and simplified, compact manufacturing.

[0031] 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.

[0032] 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.

[0033] In addition, the hydraulic unit is preferably configured such that the pressure pistons move 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.

[0034] Preferably, the drive element comprises a first freewheel and a second freewheel.

[0035] Freewheels usually 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).

[0036] Usually, the freewheels of the drive element are identical in design.

[0037] In this embodiment, the drive pistons are operatively connected to an outer side of the freewheels, wherein the operative connection is such that the back and forth movement of the drive pistons is transmitted tangentially to the outer side of the freewheel(s).

[0038] The reciprocating motion of the drive pistons is translated into a rotary reciprocating motion on the outer side of the first freewheel and an opposing rotary reciprocating motion on the second freewheel. This enables the shaft to rotate in one direction.

[0039] The inner sides of the freewheels are usually connected to the shaft in such a way that they run freely or lock in the same direction.

[0040] Typically, the outer sides of the freewheels are coupled together so that they move in opposite directions.

[0041] Preferably, the outer sides of the freewheels are coupled by a gear connection, wherein the gear located between the freewheels engages in the toothings present on the lateral outer surfaces of the freewheels.

[0042] Further preferably, both drive pistons are operatively connected to the outside of one of the freewheels, for example the first freewheel.

[0043] An advantageous further development of the internal combustion engine can provide that the operative connection of the drive pistons with the freewheels / one of the freewheels is formed by means of a toothing.

[0044] In a further development of the invention, it can be provided that the outer face of the freewheels / one of the freewheels has a toothing into which toothed racks, each connected to a drive piston, engage. For example, both toothed racks connected to the drive pistons can engage the toothing on the outer face of the first freewheel.

[0045] The racks are usually connected to the back of the drive pistons, preferably rigidly.

[0046] The force is transferred tangentially via the racks to the outside of the freewheel associated with the cylinder, which in turn converts the force into torque on its inside. The torque is then transferred to the shaft via the inside of the locking freewheel, which is connected to the shaft.

[0047] In the case of the preferred embodiment, in which both racks connected to the drive pistons engage the outside of the first freewheel, the force is transmitted to the shaft once via the inside of the first freewheel, and during the rotational countermovement through the inside of the second freewheel coupled to the first freewheel. Toothing and corresponding racks can be designed easily and offer high operational reliability as well as reliable power transmission.

[0048] 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.

[0049] Typically, the rotational back and forth movement of the first freewheel takes place over an angular range of at least 60°, preferably of at least 90°, particularly preferably of at least 120°, and most preferably of at least 150° or more.

[0050] It can be provided that the rotary back and forth movement of the first freewheel or both freewheels takes place over an angular range between 60° and 270°, preferably between 120° and 240°, particularly preferably between 150° and 210°.

[0051] In particular, it can be provided that the rotary back and forth movement of the first freewheel or both freewheels takes place over an angular range of 160° to 200°, preferably from 170° to 190°, more preferably from 175° to 185°, most preferably 180°.

[0052] Preferably, the internal combustion engine according to the invention is designed such that the direction of movement of the drive pistons and / or the 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.

[0053] Further preferably, the drive pistons and / or the pressure pistons are arranged mirror-symmetrically around a center plane in the internal combustion engine.

[0054] In In an advantageous development of the invention, the hydraulic unit has at least one bend, preferably two bends, and can be designed accordingly compactly. Particularly preferably, the hydraulic unit can be designed essentially U-shaped.

[0055] The hydraulic unit can each have a cylindrical section in which a pressure piston is movably arranged according to the above embodiments. The respective cylinder sections are fluidically connected to one another, resulting in a one-piece or integral hydraulic unit in which both pressure pistons are arranged in cylinder sections for force-transmitting movement.

[0056] In particular, a substantially U-shaped hydraulic unit can be obtained. The hydraulic unit preferably forms an interior space comprising at least two cylinder sections and a further section connecting the cylinder sections. A hydraulic fluid is located in the interior space between pressure pistons, which are preferably arranged so as to be movable within the cylinder sections.

[0057] Advantageously, the 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 designed as cylinder sections.

[0058] Typically, the hydraulic device 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 device.

[0059] Typically, the cylinders and, consequently, the drive pistons have a circular cross-section. Preferably, the respective drive pistons are of identical design.

[0060] Furthermore, the sections of the hydraulic system in which the pressure pistons move, and thus also the pressure pistons themselves, generally have a circular cross-section. Preferably, the respective pressure pistons are of identical construction.

[0061] 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 area than the front side of the pressure piston respectively connected to the drive piston, more preferably the area 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 area of the front side of the respective drive piston connected thereto.

[0062] In this embodiment, the area of the front sides of the pressure piston(s) is preferably 10% or more, more preferably 20% or more of the area of the front side of the respective drive piston connected thereto.

[0063] Typically, in the internal combustion engine according to the invention, there is at least one intake and one exhaust valve per cylinder.

[0064] There is usually one spark plug per cylinder.

[0065] 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.

[0066] The combustion engine according to the invention can be designed, for example, as a 2-stroke engine or as a 4-stroke engine.

[0067] 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.

[0068] 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.

[0069] In particular, it can be provided that a hydraulic unit with two pressure pistons each is provided for each of the two cylinders, as described above. In a configuration with four cylinders, two hydraulic units with a total of four pressure pistons are provided.

[0070] 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.

[0071] 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.

[0072] The invention also relates to a motor vehicle, aircraft or ship comprising at least one internal combustion engine according to the invention. Example

[0073] 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 view of one side of the shaft, freewheel and cylinder assembly of the embodiment of the internal combustion engine according to the invention.

[0074] The embodiment of the internal combustion engine according to the invention shown in the figures has two identical cylinders 11, 12, in each of which there is a drive piston 9, 10 with a connecting rod 13, 14.

[0075] The internal combustion engine has a first cylinder 11 for fuel combustion with a first drive piston 9 movably arranged therein and a second cylinder 12 for fuel combustion with a second drive piston 10 movably arranged therein.

[0076] The first drive piston 9 is mechanically coupled to a first pressure piston 23. The second drive piston 10 is mechanically coupled to a second pressure piston 24.

[0077] The first drive piston 9 and the second drive piston as well as the cylinders 9, 10 are identical in construction and arranged parallel to each other.

[0078] The first pressure piston 23 and the second pressure piston 24 are identical in construction. The pressure pistons 23, 24 are smaller than the drive pistons 9, 10. Apart from their different sizes, the drive pistons 9, 10 and the pressure pistons 23, 24 have the same geometric shape.

[0079] The drive pistons 9, 10 each have piston pins 7, 8. The first drive piston 9 has two piston pins 7, the second drive piston 10 has two piston pins 8.

[0080] The first drive piston 9 has a connecting rod 13. The second drive piston has a connecting rod 14. The connecting rod 13 is connected to one of the piston pins 7. The connecting rod 14 is connected to one of the piston pins 8.

[0081] The connecting rod 13 of the first drive piston 9 is connected to the first pressure piston 23 at an end facing away from the piston pin 7. The first drive piston 9 is mechanically coupled to the first pressure piston 23 at its piston pin 21 by means of the connecting rod 13.

[0082] The connecting rod 14 of the second drive piston 10 is connected to the second pressure piston 24 at an end facing away from the piston pin 8. The second drive piston 10 is mechanically coupled to the second pressure piston 24 at its piston pin 22 by means of the connecting rod 14.

[0083] A first structural unit, comprising the first drive piston 9, piston pin 7, first pressure piston 23, piston pin 21, and connecting rod 13, is preferably rigid. A second structural unit, comprising the second drive piston 10, piston pin 8, second pressure piston 24, piston pin 22, and connecting rod 14, is preferably rigid. The first and second structural units are therefore structurally identical.

[0084] The internal combustion engine further comprises a shaft 30 on which the drive element 31 is arranged. In the exemplary embodiment, the drive element comprises two annular freewheels 37, 38 operatively connected to one another via a gear 42, which have toothings on their outer rings, respectively on the front side 39, 40 and on the side.

[0085] The first drive piston 9 and the second drive piston 10 are operatively connected to the drive element 31.

[0086] In the exemplary embodiment, this operative connection is achieved via toothings in the form of racks 15, 16. The racks 15 and 16 engage with the toothing 39 on the side of the outer ring of the first freewheel 37 for power transmission.

[0087] The racks 15, 16 are connected to the rear side of the respective drive piston by means of piston pins 7, 8. The connection between the racks 15, 16 and the piston pins 7, 8 is designed as a rigid connection.

[0088] The internal combustion engine has a hydraulic unit 26. The hydraulic unit 26 contains a fluid 25. The fluid 25 is located in the interior of the hydraulic unit 26 between the pressure pistons 23, 24.

[0089] In the hydraulic unit 26, the first pressure piston 23 and the second pressure piston 24 are each arranged to be movable in cylindrical, straight longitudinal sections.

[0090] An opening 28 is provided for filling the hydraulic unit 26 and / or for emptying the hydraulic unit 26.

[0091] By means of a forward stroke movement of the first drive piston 9, a return stroke movement of the first pressure piston 23 can be induced in the hydraulic unit 26. This induces a forward stroke movement of the second pressure piston 24 in the hydraulic unit 26 and thus a return stroke movement of the second drive piston 10. The internal combustion engine is thus configured such that the drive pistons 9, 10 move in opposite directions. This movement refers to a movement in the respective cylinders 11, 12.

[0092] The drive element 31, which is operatively connected to the drive pistons 9, 10, is designed such that it sets the shaft 30 into a continuous rotational movement through the movement of the drive pistons 9, 10.

[0093] During engine operation, a fuel-air mixture is fed into the combustion chamber 5, 6 of the cylinders 11, 12 through an intake valve 3, 4. Combustion gases discharged from the respective cylinder 11, 12 are discharged from the cylinders 11, 12 through an exhaust valve 27.

[0094] Optionally, an exhaust pump 19, 20 can be provided for each cylinder 11, 12. Optionally, a valve 17, 18 can be provided for each cylinder.

[0095] The fuel-air mixture is ignited by means of a spark plug 1, 2 located in the combustion chamber 5, 6 of the cylinder 11, 12.

[0096] For example, ignition in the first cylinder 11 of the engine occurs at a position close to P min of the first drive piston 9. As a result, the first drive piston 9 in the first cylinder 11 moves "into the cylinder" due to the force generated by the explosive combustion process, thus performing a so-called "pre-stroke." This pre-stroke movement induces a return stroke movement of the first pressure piston 23 in the hydraulic unit 26, which induces a forward stroke movement of the second pressure piston 24 and thus a return stroke movement of the second drive piston 10, which is mechanically coupled to it.

[0097] The drive pistons 9, 10, which move back and forth in the cylinders 11, 12 between the positions P min (i.e. the position of the drive piston with minimum distance to the cylinder head) and P max (i.e. the position of the drive piston with maximum distance to the cylinder head), are sealed in the usual way against the combustion chamber 5, 6, e.g. by piston rings.

[0098] The drive element 31 comprises a first freewheel 37 and a second freewheel 38. The drive pistons 9, 10 are operatively connected to the outer ring of the first freewheel 37 by means of toothed racks. The toothed racks 15 and 16 engage at engagement points 32, 33 with the toothing 29 of the drive element 31 for power transmission.

[0099] The inner rings of the freewheels 37, 38 are each connected to the shaft 30 in such a way that they run freely or lock in the same direction.

[0100] The force is transmitted tangentially to the outer ring of the first freewheel via the toothed racks 15, 16, which in turn transmits the force into a torque on its inner side and thus into a torque on the shaft 30 connected to the inner side of the freewheel, i.e. in this direction the freewheel is in driving mode (locking direction). The second freewheel is in idling mode (freewheeling direction). As soon as the first drive piston 9 has reached or just exceeded a position P max and the second drive piston has reached or just exceeded a position P min, the ignitable mixture in the second cylinder is ignited. This causes the second drive piston to move in the forward direction. The force is then transmitted tangentially to the outer side of the first freewheel via the toothed rack 16. This is in idling mode; the force is transmitted via the gear 42 to the outer side of the second freewheel, which is in locking mode and transmits the force to the shaft 30.

[0101] Overall, the force generated by the respective forward stroke movement of the drive pistons is transferred tangentially to the drive element, which then transfers it to the torque acting in the same direction.

[0102] The cylinders 11, 12 and hydraulic unit 26 are attached to one of the fastening devices 44.

[0103] The drive element has a support device in which the shaft 30 is mounted in bearings 35 and 36. The shaft 30 can be connected to a working machine at its end 34.

[0104] Optionally, a stabilizing unit (not shown in detail) with a toothing can be provided, which is mechanically coupled to the drive element, preferably a toothed drive element, for stabilization, for example via a chain or a belt or the like. In particular, it can also be provided that a drive piston is operatively connected to the drive element and a drive piston is operatively connected to the stabilizing unit, which is mechanically coupled to the drive element. This operative connection can be achieved by a toothing, in particular by a rack. List of reference symbols:

[0105] 1, 2 Spark plug 3, 4 Intake valve 5, 6 Combustion chamber 7, 8 Piston pin 9, 10 Drive piston 11, 12 Cylinder 13, 14 Connecting rod 15, 16 Rack 17, 18 Valve 19, 20 Exhaust port 21, 22 Piston pin 23, 24 Pressure piston 25 Fluid 26 Hydraulic unit 27 Exhaust valve 28 Port 29 Gearing 30 Shaft 31 Drive element 32, 33 Engagement point 34 Gear shaft 35, 36 Bearing 37 First freewheel 38 Second freewheel 39, 40 Gearing 41 Gearing (sideways gears) 42 Connecting gear 43 Fastening device 44Carrier device

Claims

1. An internal combustion engine having - a shaft (30), on which a drive element (31) is arranged, - a first cylinder (11) for combusting fuel, said first cylinder having a first driving piston (9) movably arranged therein, and - a second cylinder (12) for combusting fuel, said second cylinder having a second driving piston (10) movably arranged therein, - wherein the internal combustion engine is configured such that the driving pistons (9, 10) reciprocate in opposite directions in the two cylinders (11, 12), characterised in that - the first driving piston (9) is mechanically coupled to a first pressure piston (23), - the second driving piston (10) is mechanically coupled to a second pressure piston (24), - the first and second driving pistons (9, 10) are operatively connected to the drive element (31), and - the internal combustion engine has a hydraulic unit (26) in which the first pressure piston (23) and the second pressure piston (24) are movably arranged and which contains a fluid, preferably a liquid, in an interior space (25) between the pressure pistons (23, 24), wherein the internal combustion engine is also configured such that a forward stroke movement of the first driving piston (9) induces a return stroke movement of the first pressure piston (23) in the hydraulic unit (26), thereby inducing a forward stroke movement of the second pressure piston (24) in the hydraulic unit and thus inducing a return stroke movement of the second driving piston (10), and wherein the operative connection between the driving pistons (9, 10) and the drive element (31) is configured such that the force generated by the reciprocating movement of the driving pistons (9, 10) is transmitted tangentially to the drive means (31), and the drive element (31) causes the shaft (30) to rotate in a continuous rotational movement.

2. The internal combustion engine according to claim 1, characterised in that - the driving pistons (9, 10) are movable in the cylinders (11, 12) in such a way that when the first driving piston (9) of the first cylinder (11) is located at a position with minimal distance from an upper end of the first cylinder (11), the second piston (10) in the second cylinder (12) is located at a position with maximal distance from an upper end of the second cylinder (12) and / or - the movements of the pressure pistons (23, 24) in the hydraulic direction (26) are such that, when the first pressure piston (23) is located at a position with minimal distance from an upper end of the hydraulic unit (26), the second pressure piston (24) in the hydraulic unit (26) is located at a position with maximal distance from an upper end of the hydraulic unit (26).

3. The internal combustion engine according to claim 1 or 2, characterised in that the drive element (31) comprises a first freewheel (37) and a second freewheel (38), wherein the driving pistons (9, 10) are operatively connected to an outer side of the freewheels (37, 38), preferably of the first freewheel (37).

4. The internal combustion engine according to any one of the preceding claims, characterised in that the drive element (31) comprises a first (37) and a second freewheel (38), wherein inner sides of the freewheels are each connected to the shaft (30) so that they run freely or lock in the same direction, and outer sides of the freewheels (37, 38) are coupled to one another such that they perform a movement in opposite directions.

5. The internal combustion engine according to claim 3 or 4, characterised in that the operative connection of the driving pistons (9, 10) to the outer side of the first freewheel (37) is configured such that the back-and-forth movement of the driving pistons (9, 10) causes a rotary back-and-forth movement of the first freewheel (37) and thus causes a rotary back-and-forth movement of the second freewheel (38) in the opposite direction.

6. The internal combustion engine according to claim 3, 4 or 5, characterised in that the operative connection of the driving pistons (9, 10) to the first freewheel (37) is formed by means of a toothing.

7. The internal combustion engine according to claim 6, characterised in that the outer side of the first freewheel (37) has, on its end face, a toothing (39), with which toothed racks (15, 16) each connected to a driving piston (9, 10) intermesh.

8. The internal combustion engine according to any one of claims 3 to 7, characterised in that the rotary back-and-forth movement of the first freewheel (37) is performed through 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.

9. The internal combustion engine according to claim 8, characterised in that the rotary back-and-forth movement of the first freewheel (37) is performed through an angular range between 60° and 270°, preferably between 120° and 240°, particularly preferably between 150° and 210°.

10. An internal combustion engine according to claim 9, characterised in that the rotary back-and-forth movement of the first freewheel (37) is performed through an angular range of from 160° to 200°, preferably from 170° to 190°, even more preferably from 175° to 185°, very particularly preferably 180°.

11. The internal combustion engine according to any one of claims 3 to 10, characterised in that the outer sides of the freewheels are coupled by a gearwheel connection.

12. The internal combustion engine according to any one of the preceding claims, characterised in that the driving pistons (9, 10) and / or the pressure pistons (23, 24) are arranged parallel to one another.

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