EP4180625A1 - Moteur à combustion interne - Google Patents

Moteur à combustion interne Download PDF

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Publication number
EP4180625A1
EP4180625A1 EP22203181.7A EP22203181A EP4180625A1 EP 4180625 A1 EP4180625 A1 EP 4180625A1 EP 22203181 A EP22203181 A EP 22203181A EP 4180625 A1 EP4180625 A1 EP 4180625A1
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EP
European Patent Office
Prior art keywords
internal combustion
cylinder
flywheel
combustion engine
flywheels
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Application number
EP22203181.7A
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German (de)
English (en)
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EP4180625B1 (fr
EP4180625C0 (fr
Inventor
Michael-Alexander Müller
Alexander Alhaier
Germina Alhaier
Wladimir Alhaier
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Individual
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Individual
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Publication of EP4180625B1 publication Critical patent/EP4180625B1/fr
Publication of EP4180625C0 publication Critical patent/EP4180625C0/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/026—Rigid connections between piston and rod; Oscillating pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F02B75/282—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders the pistons having equal strokes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups

Definitions

  • the invention relates to an internal combustion engine according to the preamble of claim 1.
  • a first aspect of the invention is an internal combustion engine which is designed as a four-stroke reciprocating piston engine and has the following: a crankshaft, the two crankshaft stubs and two crank arms, the first end of which is fixedly connected to the crankshaft stubs and the second end of which is fixedly connected to a crank pin is connected, has a connecting rod which is connected at a first end to the crank pin and at a second end to a first piston, and a cylinder housing, the inside of which is shaped as a vertical circular cylinder, characterized in that between the first piston and a first circular end surface of the circular cylinder, a combustion chamber is arranged, that in the cylinder housing on the side of the crankshaft stubs facing away from the first piston, a second piston is arranged, which is connected to the first piston by means of at least two spacer rods, that between the second piston and a second combustion chamber is arranged on a second of the circular end surfaces of the circular cylinder.
  • Such an engine which is called Müller's interchangeable chamber engine, is characterized by the advantage that the manufacture of the engine can be considerably simplified in the design as a double-piston engine. It is particularly advantageous here that only one connecting rod has to be used for two pistons. This is made possible by the fact that the two pistons are connected to one another by means of spacer rods. Another advantage is that two pistons can be housed in a single cylinder. In contrast to previous designs of internal combustion engines, however, it is not necessary here to deviate from the shape of the vertical circular cylinder for the crankcase and/or for the combustion chambers.
  • a first tailshaft is fixedly connected to a first receiving gear outside of the cylinder housing and is arranged such that the tailshaft drives the first receiving gear which is arranged to drive first and second flywheels such that the second flywheel is on the direction of the first flywheel facing away from the receiving wheel is arranged.
  • first and the second flywheel are set up in such a way that an axis of rotation of the respective flywheel runs parallel to the axis of rotation of the crankshaft and perpendicular to an axis of symmetry of the circular cylinder and that an intersection point of the axis of rotation of the respective flywheel and the axis of symmetry of the circular cylinder is further away from the crankshaft as the circular end face of the circular cylinder facing the combustion chamber, and that the first and second flywheels balance the internal combustion engine.
  • crankshaft arms are no longer designed as balance weights.
  • a locating wheel is attached to the crankshaft outside of the cylinder and crankshaft housing.
  • On each side of the recording wheel is. provided a flywheel. Accordingly, at least one flywheel is used as a counterweight for the torques applied by the respective piston.
  • These flywheels are driven by the crankshaft via the take-up wheel.
  • the flywheels are mounted outside the motor housing. By using such flywheels, the bearings of the crankshaft are less stressed.
  • the design of the crankshaft arms without counterweights makes it possible to accommodate the combustion chamber, pistons and crankshaft completely in a single cylinder housing.
  • This cylinder housing has the shape of a vertical circular cylinder on its inside. This structure simplifies the manufacture of the motor considerably. In addition, the space required can be reduced with such a design.
  • a third and fourth flywheel are attached to the internal combustion engine, with the third flywheel being disposed on substantially the same axis of rotation as the first flywheel and the fourth flywheel being disposed on substantially the same axis of rotation as the second flywheel.
  • the third and the fourth flywheel are arranged on that side of the cylinder on which a second crankshaft stub can be guided out of the cylinder housing.
  • the third and fourth flywheels are set up to balance the internal combustion engine.
  • crankshaft bearings can be further reduced by extending the axes of the first and second flywheels beyond the axis of symmetry of the cylinder housing. Then a third and a fourth flywheel can be mounted on the side where the second tailshaft can be taken out of the cylinder housing.
  • in the internal combustion engine there is at least one opening in each of the circular end faces of the circular cylinder facing a combustion chamber. Furthermore, a number of slides corresponding to the number of openings is arranged on each of the circular end faces of the circular cylinder facing a combustion chamber and is/are designed to close and open the respective opening.
  • the internal combustion engine has the second tailshaft fixedly connected to a second receiving gear outside of the cylinder housing and arranged such that the second tailshaft drives the second receiving gear which is arranged to drive the third and fourth flywheels.
  • the imbalance of the engine can be further reduced by providing both crankshaft stubs with a receiving wheel for driving the flywheels.
  • the axes of rotation of the first and third flywheels and of the second and fourth flywheels are two separate half-shafts in the internal combustion engine, which are each firmly connected to a first bevel gear at the ends facing away from the flywheels in such a way that the first and rotating the second flywheel in the opposite direction to the third and fourth flywheels.
  • flywheels With a suitable design of the flywheels, it is possible to run the shafts between the two flywheels from two half-waves. Both half-shafts are each provided with a first bevel gear at the end facing away from the flywheel. A second bevel gear meshes with both of the first bevel gears. The shaft of this second bevel gear runs essentially on the axis of symmetry of the cylinder housing. By means of this construction of three bevel gears, it is possible to cause the two flywheels to run in opposite directions. By running the two flywheels in opposite directions, the balancing effect of the flywheels can be further improved.
  • the receiving wheel or the receiving wheels drive the flywheel or the flywheels by means of a traction device, in particular a chain or a belt.
  • traction means in particular belts such as toothed belts or chains such as roller chains, can be used to drive the flywheel drive wheels.
  • belts such as toothed belts or chains such as roller chains
  • Particularly common and readily available parts can be used here.
  • the take-up wheel or take-up wheels on the internal combustion engine drive the flywheel drive wheels by means of coupling rods.
  • the first and/or the second receiving wheel is designed as a third bevel gear wheel on the internal combustion engine.
  • a fourth and a fifth bevel gear are arranged for each receiving wheel in such a way that at least one shaft which is coaxial with the crankshaft and is fixedly connected to the fifth bevel gear can be driven by the internal combustion engine.
  • the coupling rod or coupling rods are bridged by means of the fourth and fifth bevel gears.
  • receiving wheels are provided on both sides of the crankshaft, each of which is provided with a coupling rod, it may become necessary to realize the output of the engine in this way.
  • a second aspect of the invention is a two-cylinder internal combustion engine composed of two two-piston internal combustion engines described above, in which two cylinder housings are arranged in a V-shape in such a way that one flywheel for each cylinder housing is provided with bevel gearing in such a way that the two flywheels are arranged in mesh and serve to synchronize the two single-cylinder internal combustion engines, and in the output shafts of the two internal combustion engines at their from the end facing away from the cylinder housing of the respective motor are each provided with a bevel gear and are arranged in such a way that the two bevel gears can engage in a further bevel gear which is arranged on a shaft running perpendicular to the plane spanned by the axes of symmetry of the two cylinder housings, the output shaft of the two-cylinder combustion engine is.
  • two of the single-cylinder internal combustion engines described above can be combined to form a V-engine.
  • a third aspect of the invention is a four-cylinder internal combustion engine composed of two two-cylinder internal combustion engines described above, in which axes of symmetry of cylinder housings of the four single-cylinder internal combustion engines are arranged in one plane and in which output shafts of the four single-cylinder internal combustion engines are connected at their ends separated from the cylinder housing of the each end facing away from the respective engine, are each provided with a conical gearing and are arranged in such a way that the four bevel gearings can engage in a common bevel gear wheel, which is arranged on a shaft running perpendicular to the plane spanned by the symmetry axes of the four cylinder housings, which is the output shaft of the four-cylinder internal combustion engine .
  • Two of the V-type engines of the second aspect can be assembled into an engine in which four cylinders are arranged along the edges of a quadrilateral.
  • Such an engine is suitable for replacing the radial engines known from aircraft.
  • a fourth aspect of the invention is a multi-cylinder internal combustion engine, consisting of at least two double-piston internal combustion engines as described above, in which the shafts of the flywheels consist of half-shafts, which are connected by means of a second bevel gear, in which engine two single-cylinder internal combustion engines are each so arranged are that the axes of symmetry of their cylinder housings essentially coincide and that second bevel gears of two single-cylinder internal combustion engines are connected to one another by means of a common shaft.
  • the cylinders are lined up along their axis of symmetry. In this way, a separate output shaft can be attached to the crankshaft of each cylinder. This is recommended, for example, to drive several wheels of a vehicle. This can be used on tracked vehicles.
  • a fifth aspect of the invention is a four-cylinder internal combustion engine, composed of four single-cylinder internal combustion engines described above, characterized in that axes of symmetry of the cylinder housings of the four single-cylinder internal combustion engines are arranged parallel to one another, that axes of rotation of the crankshafts of the four single-cylinder internal combustion engines in a plane so are arranged such that the output shafts of the four single-cylinder internal combustion engines are each provided with a bevel gear at their end facing away from the cylinder housing of the respective engine and are arranged running towards one another along the diagonals of a square in such a way that the four bevel gears can be engaged in at least one common bevel gear, which is arranged on a shaft running parallel to the axes of symmetry of the four cylinder housings, which is the output shaft of the four-cylinder internal combustion engine.
  • Tetra engine is particularly suitable for aircraft engines, since the output shaft is located centrally at the intersection of the axes of the crankshaft.
  • the crankshafts form the diagonals of a square.
  • a pusher propeller and a puller propeller can be driven in this way. It is also possible to provide two common bevel gears and two output half shafts so that they extend in opposite directions and rotate in opposite directions.
  • a sixth aspect of the invention is an internal combustion engine composed of at least two single-cylinder internal combustion engines described above, in which the axes of symmetry of the cylinder housings of the at least two single-cylinder internal combustion engines are arranged parallel to one another and in one plane, and in which the receiving wheels of two adjacent single-cylinder internal combustion engines are connected to each other are connected and / or the connecting wheels of two adjacent internal combustion engines are connected to each other.
  • in-line engines with two or more cylinders can be implemented to increase the engine output.
  • a first receiving wheel and first and second flywheels are provided on a first cylinder housing, and a second receiving wheel and third and fourth flywheels are provided on a last cylinder housing.
  • these two recording wheels are the only recording wheels and these four flywheels are the only flywheels of the internal combustion engine.
  • an in-line engine can be implemented in a particularly compact manner.
  • the required distance between the individual cylinder housings and the overall length of the crankshaft are significantly reduced because there is no need to provide space for receiving gears and flywheels.
  • the inside 1 shown internal combustion engine is housed in a circular-cylindrical cylinder housing 1 .
  • the axis of symmetry of the circular cylinder is denoted by 59 .
  • a combustion chamber 29 is located on each of the two circular end surfaces of the cylinder.
  • ignition (external or natural ignition) takes place alternately at one or the other end of the cylinder.
  • Flywheels 2 at the ends of the cylinder are used to balance the flywheel masses of the pistons. They balance the engine.
  • the flywheels 2 are synchronized via coupling rods 14 in this example.
  • a so-called receiving wheel 9 between the two flywheels 2 on one side takes up the movement of the flywheels via the two coupling rods 14 of the two flywheels, which are seated on a common pin.
  • the receiving wheel 9 can be designed as a three-disk flywheel with a centrifugal clutch. Since the coupling rods stand in the way of direct power transmission, a bevel gear set with bridging gears 10 is fitted to the receiving wheel for bridging over the coupling rods, with the power transmission wheel 11 as the outer element. The receiving wheel 9 serves as the inner element.
  • the stub shaft 12 is attached to the outside of the power dissipation wheel, which transmits the power of the motor to a gearbox.
  • Each flywheel 2 is designed as a circular disc-shaped hollow body. Near the outer edge of the wheel there is a spigot on which the coupling rod attaches. On the opposite side of the pin 22 serving to anchor the coupling rod, the disc-shaped hollow body is filled with a flywheel mass which has the task of balancing the flywheel mass of the two pistons 3 .
  • the construction has a total of four such flywheel masses. However, these flywheel masses must also balance the flywheel masses of two pistons instead of just one piston.
  • the flywheels are connected by a simple shaft with no bevel gear set. In this way, two flywheels rotate in parallel, which is comparable to the crankshaft cheeks of the conventional engine, which work in pairs to balance the flywheel mass of the piston.
  • the two pistons 3 are kept at a distance by four spacer rods 16 .
  • This construction is called a piston cage. It is also possible to use only two or six appropriately arranged spacer rods instead of four.
  • the crankshaft 4 is constructed as follows:
  • the connecting rod 5 is attached to the underside of one of the two pistons. This is connected by a piston pin 65 to the side of the piston facing away from the combustion chamber.
  • the connecting rod 5 ends at the short transverse segment shaft 50 between two simple crankshaft cheeks 52. Since both pistons are rigidly connected to one another, it is sufficient to attach an internal connecting rod 5 and an internal crankshaft to only one of the two pistons 3.
  • An external stub shaft 53 transfers the combined force of both pistons through the cylinder housing 1 to the receiving wheel 9 .
  • a separate crankshaft housing from the cylinder i.e. the housing of the pistons, is no longer necessary thanks to this design.
  • the cylinder head 24 is a hollow body having the shape of a flat, circular sleeve. It consists of a cover 26, a base 27 and a border 28.
  • the cavity 25 is cooled with water.
  • a closed cooling circuit is created via inlet and outlet lines (not shown) and a water pump (also not shown).
  • the cylinder head of the invention not only has one intake and/or exhaust port, but at least two. At least one opening for the inlet and one opening for the outlet is usually provided. Since both openings open or close according to the same functional principle, only one opening is shown for better clarity, which in this example functions as both an inlet and an outlet.
  • the control of the inlet and outlet openings extends over three levels.
  • the first, outer level is above the cylinder head 24, the second level is inside the cylinder head, i.e. in the cylinder head cavity 25 and the third level is just below the cylinder head at the lower edge (bottom) of the cylinder head 27 or at the upper edge of the combustion chamber 29 .
  • the first level above the cylinder head, contains the control mechanism for the slide 37.
  • the second, middle level is the water-filled interior of the cylinder head cavity 25.
  • the actuator 78 is coupled to the upper end of the connecting shaft 33 and moves it. This is almost entirely on the second, middle level.
  • the connecting shaft 33 passes through the water jacket of the cylinder head within its guide tube 35 and extends into the combustion chamber.
  • the third, lower level is the upper edge of the combustion chamber or the bottom 27 of the cylinder head.
  • a slide 37 moves back and forth at a 60° angle, without direct material contact, at a short distance from the base of the cylinder head.
  • the slider opens and closes the inlet or outlet opening.
  • the pressure of the explosion causes the system to seal itself.
  • the slide is moved via the connecting shaft 33, which in turn is moved via an actuator 78.
  • Guide tubes 35 run between the cover and the base of the cylinder head, inside which the connecting axle 33 is located. These axes start above the cylinder head cover 26, pass through the cylinder head and end in the combustion chamber 29 at the pivot points of the slides 37.
  • the slider control mechanism consists of three nested tubes, the outer guide tube 35, the inner connecting shaft 33 and a spring pin 77 in a recess within the connecting shaft.
  • a control device (not shown) sits on the actuator 78 and controls the rotary movements of the actuator 78 electronically.
  • the connecting shaft is fixed in the interior of the guide tube 35 by two circumferential elevations 79 in circumferential grooves 80 .
  • the connecting shaft 33 becomes immovable in the axial direction, but remains rotatable in the radial direction by the actuator 78 . Therefore, the spring pin has four axially extending elevations 75 which engage in axially extending grooves 76 of the connecting shaft 33. This gives the spring pin 77 a short amount of axial spring travel to allow it to hold the slide off the bottom edge of the cylinder head, but also to allow the explosive pressure to push it up a short distance. Actuator control of connecting shaft rotation removes the limitations of rigid camshaft curves and provides complete timing flexibility.
  • an actuator 78 Located above the cylinder head cover 26 is an actuator 78 connected to the connecting shaft 33 for direct control of the connecting shaft.
  • An electronic control device (it may also be the car's black box) is connected to the actuator and electronically controls the rotary movements of the actuator 78 . This means that the limits of the rigid camshaft curves fall. This causes a complete flexibility of the control times. Because the sliders are electronically controlled by a control device are controlled, the opening and closing times can be freely varied as required. Thus, the opening or closing of the inlet and outlet ports can be advanced or delayed relative to the position of the piston.
  • the slide 37 open and close the lower junction of the inlet or outlet channel 43 and 44, which protrudes into the combustion chamber.
  • Each port opening is provided with a riser ring 74 which protrudes above the bottom edge of the cylinder head by exactly the amount corresponding to the distance between the top of the slide and the bottom edge of the cylinder head. Since the slides close the opening coming from the side and floating completely flat close to the bottom of the cylinder head, the slides are pressed against the raising ring by the compression of the gas mixture or the explosion pressure of the combustion chamber and thus seal the opening completely tight.
  • There is a self-energizing type of port closure that corresponds to the operation of the valve head of a conventional internal combustion engine. Therefore, maximum compression and maximum power output are secured.
  • each inlet or outlet port opening must be provided with a raised ring 74 rounded on the outside, on which the slide can run flat in order to reliably close the port.
  • the raising ring is raised above the cylinder head base to the same extent as the slide is raised above the lower end of the connecting axle above the cylinder head base.
  • the actuator is well protected against the heat of the combustion chamber in an air space above the cylinder head and is not restricted in its movement by the water jacket of the cylinder head.
  • the control axis 33 runs in the guide tube 35 from the cover 26 through the water-filled Cylinder head cavity 25 extends to the bottom 27 of the cylinder head. This means that the control axis does not run in the water but in the guide tube and can therefore be lubricated with oil inside the guide tube.
  • Thermal bridges arise because the guide tube 35 and the control axis 33 are guided through the cylinder head 24 .
  • the thermal energy that these thermal bridges dissipate from the combustion chamber is dissipated by the water cooling of the cylinder head.
  • a cylinder head with four pairs of slides is shown, among other things.
  • Each slide closes or opens an inlet channel 43 or an outlet channel 44.
  • the inlet and outlet channels 43 and 44 are adjacent to one another. They are opened and closed by the slides described, which work horizontally within the combustion chamber on the underside of the cylinder head base.
  • the inlet channels that are adjacent to one another are connected to one another via pressure rings 7 .
  • the pressure rings 7 correspond to the injection bar in the conventional common rail system.
  • FIG 5 shows another embodiment of the internal combustion engine of FIG 1 .
  • the flywheels 2 drive a bevel gear 19 via two half-shafts 6 .
  • These bevel gears 19 are connected via another bevel gear 20 .
  • This allows the rotational movement of the flywheel drive wheels 2 to run in opposite directions.
  • FIG. 6 shows a possible variation of the internal combustion engine 1 .
  • the coupling rods attached on both sides between the flywheel drive wheels are replaced by a traction device 18 such as a chain or a corresponding toothed belt.
  • the omitted coupling rods no longer stand in the way of a crankshaft that extends directly from the inside of the respective cylinder through the cylinder wall to the outside. Since the advantages that make it possible to keep the crankshaft simple, i.e. the flywheel mass compensation outsourced to the flywheel drive wheels and the supporting effect of the rigid spacer rods, are still effective, there is still no need for a crankshaft housing.
  • FIG. 7 shows another possible variation of the internal combustion engine according to the invention with variable compression.
  • each of the in 1 shown spacer bars 16 divided into three segments.
  • the lower and the upper segment 60 are designed as immersion tubes.
  • the middle segment 61 is designed as a standpipe.
  • the inside diameter of this standpipe 61 is slightly larger than the outside diameter of the dip tubes 60.
  • the dip tubes 60 can dip into the standpipe 61.
  • Four control legs 62 are spread or folded in their crossing element 63 by a variable-length control body 64 inside the standpipe 61 . This allows the length of the spacer bars to be varied. This in turn varies the compression because the length of the spacer rods influences the distance between the pistons 3 .
  • This spacing of the pistons 3 is in turn a fixed part of the total inner length of the cylinder housing.
  • the two-cylinder internal combustion engine shown is a so-called V-engine according to the second aspect. It is created by assembling two combustion engines described above. It can be implemented by arranging two cylinder housings 1 in a V-shape in such a way that one flywheel 23 per cylinder housing is provided with conical teeth in such a way that the flywheels 23 provided with the conical teeth are arranged in an intermeshing manner and are used to synchronize the two internal combustion engines, and that the output shafts 84 of the two internal combustion engines are each provided with a bevel gear 86 at their end facing away from the cylinder housing 1 of the respective engine and are arranged in such a way that the two bevel gears 86 can engage in a further bevel gear 82, which is arranged on a plane perpendicular to that of the axes of symmetry 59 of the two cylinder housing spanned plane running shaft 83 is arranged, which is the output shaft of the two-cylinder internal combustion engine.
  • In 9 is one of two V engines 8 composite four-cylinder engine shown.
  • a power connection of four interchangeable chamber motors lying in a square to each other is possible via a gearing of corresponding flywheel drive wheels.
  • the power output of the output shafts 84 of the individual cylinders is derived along the diagonals of the square and summarizes it via a set of four bevel gears 86 arranged at the ends of the output shafts 84 and a central bevel gear 82, one can obtain a high, perpendicular to the plane of the Square on the output shaft 83 z.
  • B. generate on a propeller 89 deriving power. This design is suitable for replacing radial engines.
  • a so-called chain motor in which several, in this case four, cylinder housings 1 are lined up along their axis of symmetry. In all cases, these are motors in which the shaft of the flywheel drive wheels 2 is divided.
  • Such an engine is in figure 5 shown.
  • the half-shafts 6 carry bevel gears 19 at their end remote from the flywheel drive wheels. Because the shaft of the flywheels 2 consists of two half-shafts 6, the direction of rotation of the flywheels 2 is opposite on both sides of the cylinder. Accordingly, the output shafts on both sides of the cylinders are in opposite directions. If, for example, synchronization of the shafts on both sides of the cylinders is required in a tracked vehicle, a corresponding gear must be provided on at least one side.
  • the in the 11 and 12 Tetra engine shown consists of four cylinder housings 1 with eight combustion chambers.
  • the cylinder housings 1 are arranged in such a way that they are arranged similarly to the four "cylinders" of a tall skyscraper in Kunststoff.
  • the rotary motion of the output shafts 84 of the four cylinders is dissipated into the space between the cylinders through the belt drive of the flywheels.
  • These four output shafts 84 run along the diagonals of a square.
  • Each of these four output shafts carries a bevel gear 86. All four bevel gears meet itself in the middle of the gap.
  • All four bevel gears 86 mesh with two central gears 82, each of which has a split output shaft 83 that protrudes beyond the front and rear limits of the Tetra engine.
  • This output shaft 83 runs parallel to the axes of symmetry 59 of the four cylinder housings.
  • the two half-shafts of the output shaft are in opposite directions here.
  • a set of flywheels 2 is provided on both sides of the crankshaft of each cylinder housing 1 .
  • an in-line engine is shown, which is composed of four cylinder housings 1 in this example.
  • the crankshafts of the two cylinders shown on the left in the picture are connected to one another by connecting the receiving wheels 9 by means of a bridging wheel 10 .
  • the crankshafts of the two cylinders shown in the picture on the right are also connected to one another.
  • Both pairs of cylinders are connected to one another in that the connecting wheels 13 of adjacent cylinders arranged between two flywheels 2 are connected to one another via a bridging wheel 10 .
  • the receiving wheels 9 and the two connecting wheels 13 facing one another, like the gear wheels 10, are designed as bevel gear wheels.
  • the crankshaft of this four-cylinder in-line engine is continuous for every two cylinders.
  • the connecting wheels 13 are joined together by means of a bridging wheel 10. These connecting gears 13 are not directly connected to the adjacent tail crankshaft. The connecting gears 13 are driven via the receiving gears 9 on the other side of each cylinder and the flywheel set.
  • any shafts of the bridging gears 10 can be used as the output shaft of this motor, as well as any shafts of those bevel gears that connect the two half-shafts of the flywheel drive wheels 2 to one another.
  • a more compact in-line engine design is in 15 shown. Instead of coupling rods as in 14 traction means 18 such as belts are used here to connect the flywheels 2 to the receiving wheels 9.
  • flywheels 2 are only present on the outside of the two cylinders that are at the ends of the row. The pistons of the inner cylinders are balanced by the flywheels of the cylinders at the ends of the row. If no flywheels are provided on the inner cylinders, a continuous crankshaft extending through a receiving wheel 9 into the output shaft 83 becomes possible.
  • the first condition is that the power transmission from the receiving wheel to the stub shaft is interrupted via a clutch and the stub shaft is temporarily stopped as a result.
  • the second condition is that, over a period of a few cycles, a control command to the actuator brings the slides into a position in which all inlet and outlet channels are open at the same time, so that the old gas mixture can escape completely. This prevents the petrol gas mixture and diesel gas mixture from meeting in the combustion chamber and causing damage.
  • the third condition is that you have two separate fuel tanks and two separate fuel lines. Between the two lines, a switch must ensure that the flow of the fuel type currently required or blocked is appropriately released or blocked.
  • the fourth condition is that the pressure rings are completely emptied before they can be filled with the new type of fuel.
  • the piston causes the pressure rings to be emptied by its emptying downward movements and its gas expulsion through the permanently open outlet openings during its upward movements.
  • the pressure rings are emptied over several revolutions until they are completely emptied. After that, further operation with the new type of fuel is electronically controlled.
  • the single-chamber engine has only one piston, one combustion chamber and only two flywheels. It can be used as a small motor, e.g. B. be built for mopeds. It needs a conventional crankshaft that dissipates the force to the outside. It goes without saying that no complex crankshaft design is required here either, since the flywheel drive wheels compensate for the imbalance of the piston movement. Accordingly, no complex crankshaft housing is necessary.
  • the work cycles of the two combustion chambers support each other.
  • the cycle sequence of one combustion chamber is shifted by exactly one cycle compared to the other combustion chamber.
  • stroke 3 working stroke
  • the piston moves down after ignition.
  • This piston transmits its kinetic energy to the other piston via the rigid spacer rods.
  • stroke 2 compression stroke
  • the combustion energy of the first piston supports the compression movement of the second piston.
  • the second piston then reaches top dead center and is moved in the opposite direction again in cycle 3. This movement occurs on stroke 4 (exhaust stroke) of the first piston and amplifies its ejection movement to remove the old gases.
  • the interchangeable chamber motor does not need valves. He thus avoids valve discs that are in the middle of the gas flow and therefore severely impede it. This increases performance and reduces consumption. Since the gas channels are no longer opened and closed mechanically, the camshafts as well as the valves are no longer required. In addition, there are no longer any rigid opening and closing times that are caused by different cam shapes, but thanks to the control of the slider by an electronic actuator, there are infinitely many. This opens up new scope for coordination with changing load conditions.
  • the pistons are held in place by four spacer rods. This makes it almost impossible for the pistons to tilt in the vicinity of the dead centers. This also makes it easier to achieve large piston diameters.
  • the interchangeable chamber engine also has the same variability capabilities as today's modern four-stroke engine. Through the variable control of intake and exhaust, the timing of injection and exhaust can be adjusted dynamically to the respective Load state of the engine can be adjusted. It is therefore possible to fine-tune the power and torque curve just as carefully as with a conventional four-stroke engine.
  • Dynamos can be attached to one or more flywheels via sprocket connections, which can feed recuperated braking energy back into the motor.
  • the engine is therefore also conceivable as a hybrid engine that can recover kinetic energy and convert it back into electrical energy.
  • the engine is easier to repair than the conventional four-stroke engine. Since it burns very cleanly and the pistons are broadly supported by the spacer rods, wear and tear should also be lower and the service life longer.
  • An advantage of the invention is that multi-cylinder engines can be manufactured according to the modular principle.
  • the sizes of the cylinder and the piston are determined on the basis of the piston stroke and the piston diameter.
  • the balancing masses of the flywheels are derived from these dimensions.
  • Multi-cylinder engines can be made by simply assembling these elements together. Only the flywheels connecting the individual cylinders and the elements of the crankshaft or output shaft connecting the individual cylinders are variable.
  • a separate block housing the crankshaft and cylinder on the one hand and a cylinder head adapted to the number of cylinders on the other are not required. In conventional engines, these elements are adapted to the respective engine.
  • Multi-cylinder engines of various types are possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP22203181.7A 2021-11-11 2022-10-24 Moteur à combustion interne Active EP4180625B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102021129350.2A DE102021129350A1 (de) 2021-11-11 2021-11-11 Verbrennungsmotor

Publications (3)

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EP4180625A1 true EP4180625A1 (fr) 2023-05-17
EP4180625B1 EP4180625B1 (fr) 2024-04-17
EP4180625C0 EP4180625C0 (fr) 2024-04-17

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DE (1) DE102021129350A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2310733A (en) * 1942-03-25 1943-02-09 Duke Charles Austin Internal combustion engine
FR2067119A1 (fr) * 1969-11-07 1971-08-20 Guillon Marcel
DE2656391A1 (de) * 1976-12-13 1978-06-15 Horst Ing Grad Hendel Zentralhubkolben-brennkraftmaschine
DE3600657A1 (de) * 1986-01-11 1987-07-16 Bongers Hermann Gegenzylinder-zweitakt-brennkraftmotor
NL9000464A (nl) * 1990-02-27 1991-09-16 Pieter Frans Van Rij Zuigermotor en in- en uitlaatsysteem daarvoor.
WO2014011122A1 (fr) * 2012-07-13 2014-01-16 Just Ladislav Soudure solidaire de deux pistons opposés sur un seul un axe par double pontage

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB791223A (en) 1956-04-24 1958-02-26 Michal Rubel Improvements in or relating to internal combustion engines
DE2514068A1 (de) 1975-03-29 1976-10-07 Heinrich Euler Verbrennungsmotor
DE3118452A1 (de) 1981-05-09 1982-12-02 E.D. Dr. 7562 Gernsbach Voigt Verbrennungsmotor
IT1278531B1 (it) 1995-12-13 1997-11-24 Giuseppe Raoul Piccinini Macchina alternativa
WO2004111411A1 (fr) 2003-06-17 2004-12-23 Rafaranirina, Herimalala, Lucia Moteur thermique a combustion interne semi-rotatif a cycle superposes
DE102013000253A1 (de) 2013-01-09 2014-07-10 Wilfried von Ammon Verfahren zur Umsetzung einer oszillierenden Hubbewegung in eine Drehbewegung und eine nach diesem Verfahren arbeitende Kolbenmaschine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2310733A (en) * 1942-03-25 1943-02-09 Duke Charles Austin Internal combustion engine
FR2067119A1 (fr) * 1969-11-07 1971-08-20 Guillon Marcel
DE2656391A1 (de) * 1976-12-13 1978-06-15 Horst Ing Grad Hendel Zentralhubkolben-brennkraftmaschine
DE3600657A1 (de) * 1986-01-11 1987-07-16 Bongers Hermann Gegenzylinder-zweitakt-brennkraftmotor
NL9000464A (nl) * 1990-02-27 1991-09-16 Pieter Frans Van Rij Zuigermotor en in- en uitlaatsysteem daarvoor.
WO2014011122A1 (fr) * 2012-07-13 2014-01-16 Just Ladislav Soudure solidaire de deux pistons opposés sur un seul un axe par double pontage

Also Published As

Publication number Publication date
EP4180625B1 (fr) 2024-04-17
EP4180625C0 (fr) 2024-04-17
DE102021129350A1 (de) 2023-05-11

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