• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Reciprocating internal combustion engine (1) having a cylinder (3), a crank mechanism (2), a piston (4) which is movably mounted in the cylinder (3) acting on the crank mechanism (2) and the one through it and the cylinder (3) formed chamber (6) gas-tight, an inlet valve (5a, 5b), which regulates a supply of fresh gas to the chamber (6), an outlet valve (7) which controls a gas discharge from the chamber (6), a control unit which controls the opening and closing of the at least one inlet valve (5a, 5b) and the at least one outlet valve (7), and an ignition unit for igniting the fresh gas. The piston (4) carries out a working stroke in a movement expanding the chamber (6) and an ejection stroke in a movement compressing the chamber (6), the inlet valve (5a, 5b) being at least partially opened during the working stroke, and wherein Exhaust valve (7) is at least partially open during the exhaust stroke.
    公开号:AT518788A4
    申请号:T50540/2016
    申请日:2016-06-14
    公开日:2018-01-15
    发明作者:Hans-Georg Panzirsch Mmag；Johann Panzirsch Ing
    申请人:Hans-Georg Panzirsch Mmag；Johann Panzirsch Ing；
    IPC主号:
    专利说明:

    P19884
    Reciprocating combustion engine
    The invention relates to a reciprocating combustion engine according to the preamble of claim 1.
    Reciprocating internal combustion engines are generally known in which four cycles are required in the operation for converting chemically bound energy into mechanical power:
    intake;
    Compression stroke;
    Stroke; and exhaust stroke.
    In each of the cycles, the crank drive makes half a turn, with the clocks repeating every two turns as a result of the clocks. Such reciprocating internal combustion engines are also referred to as four-stroke engines.
    Furthermore, reciprocating combustion engines are known in which only two cycles are required in the operation for the conversion of chemically bound energy into mechanical power:
    Intake and compression stroke; and work and pre-compression stroke.
    Also in this embodiment of the Hubkolbenverbrennungsmotors the crank mechanism completes half a turn per clock, with the clocks repeat as a result of each revolution. Such reciprocating internal combustion engines are also referred to as two-stroke engines.
    Since the two-stroke each revolution of the crank mechanism includes a power stroke and the four-stroke only every second revolution of the crank mechanism includes a power stroke, the two-stroke engine has a better power to weight ratio and also a theoretically better efficiency. Further, in a two-stroke engine, a flywheel for ensuring a constant running of the reciprocating internal combustion engine can be made smaller, and less energy is required to start the engine.
    Both operating variants have in common that a high efficiency of the. By high compression of the air-fuel mixture in the compression stroke
    Reciprocating internal combustion engine can be achieved. However, the type of fuel is to be considered, as it can lead to unwanted auto-ignition of fuels with a low anti-knocking, which permanently destroy the engine. The energy for compression of the air-fuel mixture in the compression stroke is diverted from the rotational energy of the crank mechanism, whereby the disadvantage is obtained that the crank mechanism of the known from the prior art Zweitakters at each revolution and the crank mechanism of the known from the prior art four-stroke every second revolution, at least in some cases significantly slowed down. This results in a very restless running of reciprocating internal combustion engines. Although this can be partially compensated by the size of the flywheel, but a large flywheel leads to a poorer efficiency of the reciprocating internal combustion engine.
    It is the object of the present invention to avoid the above-described disadvantage of the prior art and to form a reciprocating internal combustion engine with a smooth running with small flywheel mass.
    According to the present invention, the present object is achieved by a reciprocating internal combustion engine according to the characterizing part of claim 1.
    The reciprocating internal combustion engine according to the invention is operated by the control of the at least one inlet valve, the at least one exhaust valve and the ignition as a two-stroke, wherein the control of the at least one inlet valve and the at least one exhaust valve has the advantage that the reciprocating internal combustion engine has no compression stroke and no intake stroke , As a result, a partial braking of the crank mechanism is avoided and as a result there is a smoother running of the reciprocating internal combustion engine than in the known from the prior art reciprocating internal combustion engines. The smooth running of the flywheel of the reciprocating internal combustion engine can be reduced.
    Advantageously, the fresh gas is supplied under a gas pressure standing over the at least one inlet valve to the chamber. As a result, the advantage is obtained that the internal combustion engine according to the invention is charged and a degree of filling of the chamber is increased. Furthermore, the charge entails a better power-to-weight ratio of the reciprocating internal combustion engine.
    In order to store the oxygen and, when using a gaseous fuel, the gaseous fuel to a sufficient extent for combustion in the reciprocating internal combustion engine, these are advantageously stored separately from one another in highly compressed form in pressure vessels. As a result, the advantage is obtained that in a very small volume as much oxygen and gaseous fuel are storable, which is particularly suitable for storage, especially for mobile purposes, for example when using the reciprocating internal combustion engine according to the invention in a vehicle.
    Further, the storage of the oxygen and the gaseous fuel under high pressure, by the supply of oxygen and gaseous fuel under the gas pressure to the chamber and by the inventive control of the at least one inlet valve and the at least one outlet valve has the advantage of being stored The energy expended in the gaseous fuel and the oxygen in the pressure vessel is in part traceable back into mechanical energy in the reciprocating engine. Preferably, the storage pressure in the pressure vessel is 800 bar or more.
    Expediently, the reciprocating internal combustion engine has at least one pressure regulating valve, which is coupled to the at least one inlet valve and is designed to regulate the gas pressure with which the fresh gas is supplied to the chamber. About the pressure control valve, the charge or the degree of filling of the chamber of the Hubkolbenverbrennungsmotors is advantageously controlled with fresh gas and thus controlled the speed of the crank mechanism with running reciprocating internal combustion engine.
    Preferably, the control unit is formed by a cam drive, which is driven by the crank mechanism, wherein a transmission ratio between the crank mechanism and cam drive is 1: 1. Advantageously, the reciprocating internal combustion engine is formed by a standard four-stroke engine, in which the transmission ratio between the crank mechanism and cam drive has been changed to 1: 1 and in which the cam gear has been adjusted so that the reciprocating internal combustion engine operates as a two-stroke engine. As a result, the advantage is obtained that the reciprocating internal combustion engine according to the present invention can be formed by small changes from a standard four-stroke engine, whereby a manufacturing effort is kept as low as possible in a production of the reciprocating internal combustion engine.
    In a further embodiment, the control unit is formed by actuators with an electronic control unit. As a result, the advantage is obtained that the valves can be opened and closed arbitrarily independent of the position of the crank mechanism. Advantageously, the electronic control unit also controls an ignition timing for igniting the fresh gas.
    The at least one inlet valve expediently has a valve stem, a valve disk and a valve piston, wherein the valve disk and the valve piston are arranged on the valve stem and wherein the valve piston prevents an independent opening of the inlet valve due to the gas pressure of the fresh gas.
    Advantageously, the inlet valve is formed by a flutter valve, the control unit controls only the opening and closing of the at least one exhaust valve and the ignition unit is formed by an igniter, which igniter an ignition chamber into which an oxygen supply from an oxygen storage and a fuel supply from a fuel storage , a Gemischzuführleitung to reciprocating internal combustion engine, which Gemischzuführleitung connects to the flutter valve and open flutter valve connects the chamber of Hubkolbenverbrennungsmotors with the ignition chamber for communicating a Zündkolben, which ignition piston is movably mounted in the ignition chamber, by means of which ignition piston, a volume of the ignition chamber is variable and by which regulates a supply of oxygen from the oxygen storage and a fuel supply from the fuel storage via the ignition chamber to the chamber of the reciprocating internal combustion engine ar is a Überströmleitung, which overflow line connects an end portion of the ignition chamber to the Gemischzuführleitung for communicating, and a pressure valve which is arranged in the overflow line, wherein the ignition piston in a compression chamber compressing movement towards the end portion of the fuel supply to the ignition chamber on the Kraftstoffzuführleitung, the oxygen supply to the ignition chamber via the oxygen supply and the removal of the mixture via the Gemischzuführleitung from the ignition chamber and heated a mixture located in the ignition chamber over an ignition temperature, wherein a resulting from the ignition of the mixture pressure wave opens the pressure valve and a flame front of ignited in the ignition chamber mixture via the overflow through the flutter valve in the chamber of the Hubkolbenverbrennungsmotors propagates. By mixing the oxygen and the fuel in the ignition chamber, the advantage is obtained that there is a strong swirling of the oxygen and the fuel and thus a homogeneous mixture of oxygen and fuel is achieved. Furthermore, the ignition unit has the advantage that the provision of spark-generating ignition units, such as spark plugs, can be dispensed with.
    Preferably, the ignition chamber in the form of a blind bore and the ignition piston is cylindrical. As a result, the advantage is obtained that the production engineering effort in the manufacture of the ignition unit is kept low.
    Suitably, the ignition piston is driven by the crank mechanism. As a result, the advantage is obtained that can be dispensed with additional drives and a simple precise control is achieved.
    In a further advantageous embodiment, the ignition unit is formed by an electronic ignition with spark plug.
    The fresh gas is preferably formed by oxygen and hydrogen. Suitably, the hydrogen and oxygen are obtained by water electrolysis with the aid of solar power. The combustion of hydrogen and oxygen in the reciprocating internal combustion engine has the advantage that only water or water vapor is produced as exhaust gas and not carbon monoxide (CO), carbon dioxide (CO2) and nitrogen oxides (ΝΟχ), as in the combustion of carbonaceous fuels with air , Thus, can be dispensed with a complex exhaust aftertreatment or exhaust gas recirculation.
    In another embodiment, the fresh gas is formed by air and atomized diesel, atomized biodiesel, atomized gasoline, atomized ethanol, methane or a mixture of the stated fuels. The air is advantageously compressed by coupled with the crank mechanism ancillaries such as compressors.
    Further advantageous embodiments of the reciprocating internal combustion engine according to the invention are explained in more detail below in the figures.
    Figure 1 shows a variant of the invention Hubkolbenverbrennungsmotors in a schematic view.
    Figure 2 shows a valve arrangement of the reciprocating internal combustion engine according to the invention according to Figure 1 in a schematic view.
    Figure 3 shows a variant of an inlet valve of the reciprocating internal combustion engine according to the invention according to Figure 1 in a sectional view.
    Figures 4 to 11 show the embodiment of the reciprocating internal combustion engine according to the invention according to Figure 1 during a revolution of a crank mechanism of the reciprocating internal combustion engine in a schematic view.
    Figures 12 and 13 show a variant of an ignition unit of the reciprocating internal combustion engine according to the invention according to Figure 1 in a schematic view.
    Figure 1 shows a variant of the invention Hubkolbenverbrennungsmotors 1 in a schematic view. The reciprocating internal combustion engine 1 comprises a crank mechanism 2, a cylinder 3 sealed on one side, a piston 4, a chamber 6 bounded by the cylinder 3 and the piston 4, an exhaust valve 7 and two intake valves, an intake valve 5a comprising a supply of hydrogen and the other inlet valve 5b regulates a supply of oxygen into the chamber 6. The outlet valve 7 is shown in FIGS. 2 and 8 to 11. The crank mechanism 2 consists of a crankshaft 8 and a connecting rod 9, which connecting rod 9 is coupled by means of a piston pin 10 with the piston 4. Both the intake valves 5a and 5b and the exhaust valve 7 are formed by poppet valves. Further, the reciprocating internal combustion engine 1 has a control unit constituted by a cam gear (not shown), the cam gear being driven by the crank gear 2, and the cam gear controlling the opening and closing of the intake valves 5a and 5b and the exhaust valve 7.
    The hydrogen is stored in a hydrogen pressure vessel 11 and is fed via a hydrogen feed line 12 via a first pressure regulating valve 13 to the inlet valve 5a. The hydrogen in the hydrogen pressure vessel 11 has a gas pressure of about 800 bar. The oxygen is stored in an oxygen pressure vessel 14 and is regulated via an oxygen supply line 15 via a second pressure control valve 16 to the inlet valve 5b. The oxygen in the oxygen pressure vessel 14 has a gas pressure of about 800 bar. The hydrogen supply line 12 and the Sauerstoffzuführleitung 15 are shown for ease of illustration only as lines in Figure 1. The hydrogen supply line 12 and the oxygen supply line 15 are advantageously formed by tubes which connect in a gas-tight manner to the inlet valves 5a and 5b, wherein the tubes are advantageously formed of steel or stainless steel.
    FIG. 2 shows a valve arrangement of the two inlet valves 5a and 5b and of the outlet valve 7 of the reciprocating internal combustion engine 1 according to the invention according to FIG. 1 in a schematic view.
    FIG. 3 shows a variant embodiment of an inlet valve 5a of the reciprocating internal combustion engine 1 according to the invention according to FIG. 1 installed in the cylinder 3 in one
    Sectional view. The inlet valve 5a has a valve stem 17, a valve disk 18, a valve spring 32 and a valve piston 19. An arrow 20 indicates the hydrogen supply to the inlet valve 5a via the hydrogen supply line 12, wherein the hydrogen supply line 12 advantageously connects directly to an opening 29. A gas engagement surface 30 of the valve piston 19 is the same size as a gas attack surface 31 of the valve disk 18, whereby the valve piston 19 prevents inadvertent opening of the inlet valve 5a due to the gas pressure of the hydrogen in the hydrogen supply 12 against a spring force of the valve spring 32. The spring force of the valve spring 32 presses from the cylinder 3 supporting the inlet valve 5a in its closed position. In the cylinder 3, a compensation channel 21 is formed, which produces a pressure equalization between a space formed by the valve piston 19 and the cylinder 3 and an exterior.
    Advantageously, the inlet valve 5b in the mechanical structure is the same as the inlet valve 5a.
    Figures 4 to 11 show the embodiment of the reciprocating internal combustion engine 1 according to the invention according to Figure 1 during one revolution of the crank mechanism 2 in a schematic view. With the aid of FIGS. 4 to 11, a mode of operation of the reciprocating internal combustion engine 1 will be described in more detail below with reference to one revolution of the crankshaft 8, wherein the revolution starts as an example in a top dead center OT of the piston 4. See FIG. 4. At the top dead center OT of the piston 4, both inlet valves 5a and 5b and the outlet valve 7 are closed. A rotation angle of the crank shaft 8 is zero in the top dead center TDC of the piston 4. If the crank shaft 8 is now rotated further, the piston 4 is displaced from the position at top dead center TDC in the direction of the crankshaft 8. See Figure 2. Now open both inlet valves 5a and 5b, wherein by the first pressure regulating valve 13 and the second pressure regulating valve 16, a gas pressure of the inflowing into the chamber 6 hydrogen and oxygen is controlled. The first pressure control valve 13 and the second pressure control valve 16 are advantageously formed by proportional pressure control valves. A mixture of hydrogen and oxygen takes place in the chamber 6. By the opening duration of the inlet valve 5a and 5b and / or by means of the first pressure regulating valve 13 set gas pressure and the valve 16 set at the second pressure control gas pressure is a charge or a degree of filling the chamber 6, whereby a torque output and a rotational speed of the reciprocating internal combustion engine 1 is controlled. For the efficient control of the reciprocating internal combustion engine 1, it is possible to open the inlet valves 5a and 5b for different lengths of time or to let the hydrogen and the oxygen flow into the chamber at different gas pressures. Advantageously, the inlet valves 5a and 5b and the first pressure control valve 13 and the second pressure control valve 16 are driven so that a Mas sen ratio of oxygen to hydrogen of a charge of the cylinder 3 is eight to one. Since a pressure in the cylinder 3 during charging of the cylinder 3 is lower than the pressure with which the hydrogen and the oxygen flow into the cylinder 3, the cylinder 3 is cooled by the strong expansion of the oxygen and the hydrogen during charging of the cylinder 3 , As a result, the advantage is obtained that can be dispensed with an external cooling device, such as an air-water heat exchanger, or a small external cooling device for cooling the Hubkolbenverbrennungsmotors 1 is sufficient.
    Has the crank shaft 8 reaches the rotation angle φ close the intake valves 5 a and 5 b and there is the ignition of the mixture. See Figure 6. In a mechanical control of the intake valves 5a and 5b via the cam drive, the rotational angle φ at which close the intake valves 5a and 5b, advantageously about 30 °. Ignition takes place in this embodiment of the reciprocating engine 1 via a spark plug, not shown, and a commercially available contactless electronic ignition. The ignition timing is coupled to the closing of the intake valves 5a and 5b.
    The piston 4 moves through the ignited mixture in the direction of its bottom dead center UT and in the process releases mechanical energy to the crank drive 2. The previous movement from top dead center OT to bottom dead center OT, which corresponds to a rotation of the crank shaft 8 of 180 °, is also referred to as a working stroke. In bottom dead center UT, the opening of the exhaust valve 7 begins, being pushed by a further movement of the crank shaft 8 and thus the piston 4 in the direction of top dead center OT, the exhaust gas, here pure water vapor through the outlet valve 7. The exhaust valve 7 closes at the top dead center OT. The movement from the bottom dead center UT to the top dead center OT is also referred to as the exhaust stroke. See Figures 8-10. When the piston 4 reaches top dead center TDC, the crankshaft 8 has completed one revolution and the cycle begins again.
    In a further embodiment variant, the reciprocating internal combustion engine 1 has a plurality of cylinders 3.
    In a further embodiment, the control unit of
    Hubkolbenverbrennungsmotors 1 formed by electronically controllable actuators. As a result, the advantage is obtained that the intake valves 5a and 5b and the exhaust valve 7 can be opened and closed arbitrarily independent of the position of the crankshaft 8. The rotational angle φ at which the intake valves 5a and 5b close becomes at this
    Embodiment advantageously changed depending on a speed of the crankshaft 8 and is preferably between 15 ° and 30 °.
    Figures 12 and 13 show a variant of an ignition of the reciprocating internal combustion engine 1 according to the invention according to Figure 1 in a schematic view. The ignition unit is formed by an ignition device 22. Advantageously, in a reciprocating internal combustion engine 1 equipped with a Zündeinvorrichtung 22 only one inlet valve is provided and the inlet valve is formed by a flutter valve, not shown. The cam drive controls only the opening and closing of the exhaust valve 7. Further, the hydrogen supply pipe 12 and the oxygen supply pipe 15 directly open into a housing 23 of the ignition device 22.
    The ignition device 22 further includes a firing piston 24 which is slidably mounted in the housing 23 and a gas-tight in the housing 23 formed ignition chamber 25 to the outside, a Gemischzuführleitung 26, an overflow 27 and a pressure valve 28. The Gemischzuführleitung 26 is connected to the Flutter valve coupled to the reciprocating internal combustion engine 1 and connects in the open state of the fluttering valve, the chamber 6 of the reciprocating internal combustion engine 1 with the ignition chamber 25. The overflow 27 connects an end portion 33 of the ignition chamber 25 with the Gemischzuführleitung 26th
    The pressure valve 28 is arranged in the overflow 27 and is formed by a check valve which is spring-loaded and in which a release pressure at which the pressure valve 28 opens, is adjustable.
    The function of the ignition device 22 will be explained in more detail below. The ignition piston 24 is coupled via a gear, not shown, with the crank mechanism 2 of the reciprocating internal combustion engine 1. If the crankshaft 8 of the reciprocating internal combustion engine 1 is at zero rotational angle, the piston 4 is at top dead center TDC. In this position, the ignition piston 24 is in the position as shown in Figure 13. The exhaust valve 7 is closed and the flutter valve is in its open starting position. By further rotation of the crankshaft 8, the ignition piston 24 is moved to the position as shown in Figure 12, whereby the ignition piston 24 an opening the hydrogen supply line 12, the oxygen supply 15 and the Gemischzuführleitung 26 releases. Hydrogen and oxygen flow into the ignition chamber 25, mix there and continue to flow through the Gemischzuführleitung 26 through the flutter valve in the chamber 6 of the Hubkolbenverbrennungsmotors 1. Has the crankshaft 8 reaches the rotational angle φ of the firing plunger 24 back into the position as in Figure 13th displaced, wherein the ignition piston 24 while a supply of oxygen and hydrogen to the ignition chamber 25 and a discharge of the mixture via the Gemischzuführleitung 26 from the ignition chamber 25 prevents and heated by the compression of the leftover mixture in the ignition chamber 25, this over an ignition temperature of the mixture , As a result, ignites the mixture, wherein a resulting pressure wave opens the pressure valve 28, whereby a flame front via the overflow 27, parts of the Gemischzuführleitung 26 and the flutter valve in the chamber 6 of the reciprocating internal combustion engine 1 propagates. By an explosion caused by the ignition of the mixture in the chamber 6 explosion pressure, the flutter valve is closed and the piston 4 moves in the direction of bottom dead center UT. An external ignition device and the provision of a spark plug omitted in this embodiment.
    The Gemischzuführleitung is advantageously formed of steel or stainless steel and formed as short as possible.
    Suitably, the housing 23 and the piston 24 are formed by steel, an aluminum alloy or stainless steel.
    Preferably, the piston 4, the cylinder 3, the ignition piston 24 and / or the housing 23 are provided with a coating which protects the components from corrosion.
    Suitably, a raceway of the cylinder 3, the piston 4, the ignition piston 24 and / or a raceway of the housing 23 is provided with a coating having good sliding friction properties.
    In a further embodiment, the ignition piston is driven by an electric drive.
    权利要求:
    Claims (12)
    [1]
    claims:
    1. Reciprocating internal combustion engine (1) with a cylinder closed on one side (3), a crank drive (2), a piston (4) which is movably mounted in the unilaterally closed cylinder (3) which is coupled to the crank mechanism (2) and which gas-tightly seals a chamber (6) formed by it and the cylinder (3) sealed at one end, at least one inlet valve (5a, 5b) which regulates a supply of fresh gas to the chamber (6), at least one outlet valve (7) a discharge of waste gas from the chamber (6) controls, at least one control unit, which regulates opening and closing of the at least one inlet valve (5a, 5b) and the at least one outlet valve (7), and an ignition unit for igniting the fresh gas in the Chamber (6), wherein the fresh gas is formed by oxygen and atomized fuel, in particular gaseous fuel, characterized in that the piston (4) in a chamber (6) expanding movement a and performs a discharge stroke in a movement compressing the chamber (6), wherein the at least one inlet valve (5a, 5b) is at least partially open during the power stroke and wherein the at least one exhaust valve (7) is at least partially opened during the exhaust stroke ,
    [2]
    2. reciprocating internal combustion engine (1) according to claim 1, characterized in that the fresh gas under a gas pressure standing over the at least one inlet valve (5a, 5b) to the chamber (6) can be fed.
    [3]
    3. reciprocating internal combustion engine (1) according to claim 2, characterized in that the reciprocating internal combustion engine (1) at least one pressure control valve (13, 16) which is coupled to the at least one inlet valve (5a, 5b) and for regulating the gas pressure, with the fresh gas is supplied to the chamber (6) is formed.
    [4]
    4. Hubkolbenverbrennungsmotor (1) according to one of claims 1 to 3, characterized in that the control unit is formed by a cam drive, which is driven by the crank mechanism (2), wherein a transmission ratio between the crank mechanism (2) and the cam drive 1: 1 is.
    [5]
    5. Reciprocating internal combustion engine (1) according to one of claims 2 to 4, characterized in that the at least one inlet valve (5a, 5b) has a valve stem (17), a valve disc (18) and a valve piston (19), wherein the valve disc (18) and the valve piston (19) are arranged on the valve stem (17) and wherein the valve piston (19) prevents an independent opening of the inlet valve (5a, 5b) due to the gas pressure of the fresh gas.
    [6]
    6. Reciprocating internal combustion engine (1) according to one of claims 1 to 4, characterized in that the inlet valve is formed by a flutter valve, that the control unit only controls the opening and closing of the at least one outlet valve (7) and that the ignition unit by a Ignition device (22) is formed, which ignition device (22) an ignition chamber (25) into which an oxygen supply (15) from an oxygen reservoir (14) and a fuel supply line (12) from a fuel reservoir (11) open, a Gemischzuführleitung (26) for reciprocating internal combustion engine (1), which Gemischzuführleitung (26) connects to the flutter valve and open flutter valve, the chamber (6) of the reciprocating internal combustion engine (1) with the ignition chamber (25) for communicating, a priming piston (24), which ignition piston ( 24) is movably mounted in the ignition chamber (25), by means of which ignition piston (24) a volume of the ignition chamber (25) is variable and by means of which an oxygen supply from the oxygen reservoir (14) and a fuel supply from the fuel reservoir (11) via the ignition chamber (25) to the chamber (6) of the reciprocating internal combustion engine (1) is controllable, an overflow line (27), which overflow line (27) having an end portion (33) of the ignition chamber (25) communicating with the mixture supply line (26) for communicating, and a pressure valve (28) disposed in the overflow line (27), the ignition piston (24) communicating with the ignition chamber (25); 25) compressing movement in the direction of the end part (33) the fuel supply to the ignition chamber (25) via the fuel supply (12), the oxygen supply to the ignition chamber (25) via the oxygen supply (15) and the discharge of the mixture via the Gemischzuführleitung (26) from the Ignition chamber (25) and heated in the ignition chamber (25) mixture heated above an ignition temperature, wherein a resulting by the ignition of the mixture Druckw The pressure valve (28) opens and a flame front of the mixture ignited in the ignition chamber (25) flows via the overflow line (27) through the flutter valve into the chamber (6) of the reciprocating internal combustion engine (1).
    [7]
    7. Hubkolbenverbrennungsmotor (1) according to claim 6, characterized in that the ignition chamber (25) has the shape of a blind bore and the firing piston (24) is cylindrical.
    [8]
    8. Hubkolbenverbrennungsmotor (1) according to claim 6 or 7, characterized in that the ignition piston (24) by the crank drive (2) is driven.
    [9]
    9. Hubkolbenverbrennungsmotor (1) according to any one of claims 6 to 8, characterized in that the oxygen reservoir (14) and the fuel reservoir (11) are formed by pressure vessels.
    [10]
    10. reciprocating internal combustion engine (1) according to one of claims 1 to 5, characterized in that the ignition unit is formed by an electronic ignition with spark plug.
    [11]
    11. reciprocating internal combustion engine (1) according to one of claims 1 to 10, characterized in that the working stroke in a top dead center (TDC) of the piston (4) starts and ends in a bottom dead center (UT) of the piston (4), wherein the Crankshaft (8) of the crank mechanism (2) during the power stroke makes a 180 ° rotation, and that the control unit at least one intake valve (5a, 5b) at top dead center (TDC) of the piston (4) at a rotation angle of zero the Crankshaft (8) opens and φ closes at a rotation angle.
    [12]
    12. reciprocating internal combustion engine (1) according to claim 11, characterized in that the rotation angle φ at which the at least one inlet valve (5a, 5b) closes, is variable.
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    同族专利:
    公开号 | 公开日
    AT518788B1|2018-01-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3696795A|1971-01-11|1972-10-10|Combustion Power|Air pollution-free internal combustion engine and method for operating same|
    US20150285135A1|2014-04-04|2015-10-08|Nexovation, Inc.|Combustion engine including an air injector, and power generating system including the combustion engine|DE102018131679A1|2018-12-11|2020-06-18|Florian Köhler|Method for operating a turbo compound system|
    法律状态:
    2022-02-15| MM01| Lapse because of not paying annual fees|Effective date: 20210614 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50540/2016A|AT518788B1|2016-06-14|2016-06-14|reciprocating engine|ATA50540/2016A| AT518788B1|2016-06-14|2016-06-14|reciprocating engine|
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