EP4245969B1 - Moteur à vapeur - Google Patents

Moteur à vapeur Download PDF

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Publication number
EP4245969B1
EP4245969B1 EP22162444.8A EP22162444A EP4245969B1 EP 4245969 B1 EP4245969 B1 EP 4245969B1 EP 22162444 A EP22162444 A EP 22162444A EP 4245969 B1 EP4245969 B1 EP 4245969B1
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EP
European Patent Office
Prior art keywords
valve
chamber
steam
control
motor according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP22162444.8A
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German (de)
English (en)
Other versions
EP4245969A1 (fr
EP4245969C0 (fr
Inventor
Robert Duschl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
RD Estate GmbH and Co KG
Original Assignee
RD Estate GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by RD Estate GmbH and Co KG filed Critical RD Estate GmbH and Co KG
Priority to EP22162444.8A priority Critical patent/EP4245969B1/fr
Priority to PCT/EP2023/056161 priority patent/WO2023174816A1/fr
Publication of EP4245969A1 publication Critical patent/EP4245969A1/fr
Application granted granted Critical
Publication of EP4245969C0 publication Critical patent/EP4245969C0/fr
Publication of EP4245969B1 publication Critical patent/EP4245969B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/02—Steam engine plants not otherwise provided for with steam-generation in engine-cylinders

Definitions

  • the present invention relates to a steam engine, in particular the valve control or valve drive of a steam engine.
  • CHP plants Decentralized combined heat and power plants have long been established as an advantageous alternative to the conventional combination of local heating and central power plants.
  • CHP plants are used to generate electrical energy and useful heat; in particular, CHP plants are preferably operated on site or near the useful heat sink.
  • Combustion engines such as diesel or gasoline engines, Stirling engines, steam engines, combustion turbines or steam engines can be used to drive the power generator.
  • Such inlet valves for controlling and/or regulating a fluid flow generally comprise a valve seat and an axially movable valve member.
  • the valve member usually has a valve stem and a valve body at one end thereof.
  • a valve drive or a valve control is also provided, which is directly or indirectly connected to the valve stem in a force-transmitting manner. This allows the valve member, in particular its valve body, to be lifted off the valve seat to open the valve and enable flow through a valve opening.
  • the valve member or the valve body is brought back into contact with the valve seat, thus blocking fluid flow through the valve opening.
  • EP3594459 A , US2019/055898 A1 and US2008/093477 A1 refer to a valve control in a steam engine.
  • valves for controlling or regulating a fluid flow are known in which the valve body is subjected to a closing force in the closing direction of the valve, i.e. in the direction of the valve seat, by means of a spring element in order to automatically close the valve in the non-actuated state (see e.g. WO 2016/146459 A1 or EP3 798 413 ).
  • the spring force or clamping force can decrease and the valve body can be pressed into the valve seat with too little force.
  • wear can result in bypass flows in the valve and malfunctions in the overall system in which the valve is used to control and/or regulate a fluid flow.
  • valve train is formed by a tappet on the piston, which interacts with the valve member at top dead center to lift the valve member or its valve body from the valve seat.
  • the task was therefore to provide a steam engine or a valve control for a steam engine in which both the tightness of the inlet valve can be maintained over a long operating period and precise timing (opening time and/or opening speed) of the inlet valve can be ensured.
  • inlet valves or their valve members can be opened hydraulically and closed pneumatically. This makes it possible to control or regulate the opening flank (valve stroke or opening and speed) of the inlet valve via the hydraulic pressure.
  • the stroke curve slope, compression, etc.
  • the pneumatics can achieve a steep closing flank in the stroke curve, i.e. the inlet valve closes very quickly (particularly compared to a spring). This means that the expansion phase of the steam in the working space of the reciprocating piston can be extended and a higher level of efficiency can be achieved.
  • pneumatics are not subject to the above-mentioned disadvantages of a spring, especially a steel spring. The tightness of the inlet valve can thus be ensured over a very long period of time.
  • pneumatics enable comparatively simple seals compared to hydraulics because the gas pressure provides additional sealing.
  • the steam engine is a piston steam engine and comprises a cylinder, a reciprocating piston that is movably guided in the cylinder between a top dead center and a bottom dead center, and a working space in the cylinder that is delimited by the reciprocating piston.
  • the working space is not necessarily to be understood as the maximum total volume that is delimited by the reciprocating piston, but rather as the space in which the supplied fresh steam is expanded.
  • the steam engine also comprises a steam space for providing fresh steam and an inlet valve with a valve opening that connects the steam space and the working space, a valve seat surrounding the valve opening, and a movable valve member that interacts with the valve seat to close and open the valve opening.
  • the valve member can, as explained later, comprise a valve stem and a valve body, the valve body interacting with the valve seat.
  • a valve control is also provided for moving the valve member.
  • the valve control comprises a control cylinder and a control piston that interacts with the valve member.
  • the control piston divides the control cylinder into a pneumatic chamber (closing chamber) and a hydraulic chamber (actuation chamber).
  • the pneumatic chamber is used to close the valve opening, whereby the valve member or its valve body is pressed into the valve seat by the pneumatic pressure in the pneumatic chamber.
  • the hydraulic chamber can be pressurized with hydraulic fluid to lift the valve member from the valve seat and release the valve opening.
  • valve control does not require such a spring. While a spring would only partially introduce the force into the control piston, the force generated by the gas pressure is distributed evenly across the entire surface of the control piston. This has the advantage that the control piston can be designed with thinner walls and thus lighter.
  • valve member or its valve body is lifted off the valve seat into the steam chamber.
  • the pneumatic chamber is arranged facing away from the valve seat and the hydraulic chamber is arranged facing the valve seat.
  • valve member has an elongated valve stem which is connected, in particular firmly connected, to the control piston.
  • the valve member can be guided to move linearly.
  • the valve stem of the valve member can be guided to move linearly.
  • the pressure in the pneumatic chamber can be constant, wherein the pneumatic chamber can be pressurized with gas pressure from a gas pressure source that supplies gas pressure at a substantially constant pressure.
  • the gas pressure can have a pressure between 30 bar and 100 bar, preferably between 40 bar and 70 bar.
  • air is used as a medium, so that the gas pressure corresponds to an air pressure between 100 and 200 bar. Compressed air can be used.
  • other gaseous media can also be used, such as nitrogen.
  • the pressure in the pneumatic chamber can therefore also be adjustable.
  • a conventional control valve can be used for this. It is also conceivable to regulate or control the gas pressure depending on the power of the steam engine. For example, the maximum steam pressure in the working chamber before expansion can be used as a parameter.
  • the stroke (valve stroke) of the valve member when lifting the valve member from the valve seat can be in a range between 1 mm and 5 mm.
  • the valve element including the connected cylinder piston can have a weight of 100 g to 300 g.
  • control piston is sealed against an inner wall (the cylinder wall) of the control cylinder.
  • a seal is provided that seals between the inner wall (the cylinder wall) of the control cylinder and the control piston or its outer circumference.
  • Conventional piston seals or O-rings can be used here, particularly because the pressure in the pneumatic chamber counteracts the ingress of hydraulic fluid from the hydraulic chamber.
  • the seal can be attached to the piston. In one embodiment, however, the seal is attached to the inner wall of the control cylinder. For example, a so-called rod seal can be used. This makes the seal static and the forces acting on the seal can be reduced. As a result, the stability of the seal is increased and the maintenance interval of the steam engine is extended.
  • the control piston is cup-shaped.
  • the control piston can have a control piston base and a cylindrical control piston wall that protrudes from it into the pneumatic chamber.
  • the clearance between the control cylinder or the wall of the control cylinder and the control piston wall can be small, for example in the range of 0.01 mm to 0.02 mm.
  • This design guides the control piston in the control cylinder. Forces on any seals are thereby further reduced, since the seal does not have to take on a guiding function.
  • the control piston wall can have a length or height starting from the control piston base that is at least twice and at most four or at most three times as large as the diameter of the control piston or control piston base.
  • control cylinder is sealed in opposite directions to the valve member, in particular the valve stem of the valve member.
  • a rod seal that seals in opposite directions is preferably used here.
  • control piston on the side of the hydraulic chamber can have a diameter in a range between 20mm and 30mm, preferably 20mm to 25mm.
  • the small diameter allows the opening speed of the valve element to be reduced to less than 1ms (e.g. 0.7ms or 0.8ms).
  • the gas pressure required to close the valve becomes very high, the sensitivity of the inlet valve increases and control becomes difficult.
  • With a diameter of more than 30mm the opening time becomes too long.
  • the hydraulic chamber can have a hydraulic opening connected to a hydraulic line for the supply and discharge of hydraulic fluid into and out of the hydraulic chamber.
  • a double seat valve can be used, which is connected to the hydraulic line on the one hand and to a supply line and a discharge line on the other hand, which are alternately opened and closed by a common valve element.
  • the cylinder assembly shown schematically comprises a cylinder 10.
  • a reciprocating piston 12 is guided so as to be movable back and forth along the cylinder axis 14.
  • the reciprocating piston 12 has an eye 16 for connection to a connecting rod (not shown), which is connected to an output shaft (also not shown).
  • a working chamber 18 is formed in the cylinder 10.
  • the working chamber 18 is limited at the bottom by the top 20 of the reciprocating piston 12. On the opposite side, the working chamber 18 is limited by the cylinder head 22 or its underside/base 24.
  • the volume of the working chamber is minimal. This volume is also referred to as the compression volume or residual volume. If the piston 12 is at the bottom dead center, the volume of the working chamber 18 is maximum. This volume is also referred to as the expansion volume.
  • the inlet valve 26 comprises a valve opening 28, which in the illustrated embodiment is formed in the base 24 of the valve head 22.
  • the inlet valve 26 comprises a valve seat 30 surrounding the valve opening 28 and a valve member 32 cooperating with the valve seat 30.
  • the valve member 32 comprises a valve body 34 and a valve stem 36.
  • the valve body 34 comprises a surface 38 which interacts with the valve seat 30 or comes into sealing contact.
  • the surface 38 is conical in the embodiment shown.
  • the valve seat 30 is designed to complement the surface 38.
  • the valve stem 36 is elongated and cylindrical.
  • the base area of the conical valve body 34 is not larger in diameter than the diameter of the cylindrical valve stem 36.
  • the valve member 32 of the inlet valve 26 is thus designed in the form of a needle valve.
  • valve member 32 is axially movable.
  • the valve member 32 is guided in a guide 40.
  • the valve stem 36 is received in the guide 40 and guided in a linearly movable manner.
  • the cylinder head 22 further comprises a steam chamber 76, to which fresh steam can be supplied via a steam supply opening 78.
  • the fresh steam can have a pressure of 30 bar to 800 bar, preferably 30 to 500 bar, particularly preferably 30 to 180 bar, and a temperature of 300 °C to 600 °C.
  • valve control 42 is provided to move the valve member 32 axially and to lift it off the valve seat 30 or to bring it into contact with it in order to close and release the valve opening 28.
  • the valve control 42 comprises a control cylinder 44 and a control piston 46.
  • the control piston 46 is firmly connected to an end of the valve stem 36 facing away from the valve body 34.
  • An integral design i.e. a one-piece, uniform material design, is conceivable for this purpose.
  • a material-fitting connection e.g. by welding is also conceivable.
  • the control piston 46 divides the control cylinder 44 into a pneumatic chamber 48 and a hydraulic chamber 50.
  • the control piston 50 further has a piston ring 52 (O-ring) which seals an outer peripheral surface 54 of the control piston 46 against an inner wall 56 of the control cylinder 44.
  • the pneumatic chamber 48 is delimited on the one hand by a surface 58 of the control piston 46 and on the other hand by an upper end 60 (an upper side) of the control cylinder 44.
  • the hydraulic chamber 50 in turn is delimited by a bottom side 62 of the control piston 46 and a lower end 64 (a bottom side) of the control cylinder 44.
  • the control piston has, in particular on its underside 62, a diameter in a range between 20 mm and 30 mm, preferably 20 mm to 25 mm.
  • a gas pressure opening 68 is also provided, to which a gas pressure line 70 is connected. Via the gas pressure line 70 and the Gas can be supplied to the pneumatic chamber 48 via the gas pressure opening 68.
  • a control valve (not shown) can be provided in the gas pressure line 70, which regulates or controls the pressure in the pneumatic chamber 48. This can be done depending on the power of the steam engine, for example the maximum pressure prevailing in the working chamber 18 before expansion.
  • a hydraulic opening 72 is provided in the control cylinder 44, to which a hydraulic line 74 is connected. Hydraulic fluid, in particular hydraulic oil, can be supplied to and discharged from the hydraulic chamber 50 via the hydraulic line 74 and the hydraulic opening 72.
  • a double seat valve 88 can be used.
  • the hydraulic line 74 is connected to the double seat valve 88.
  • the hydraulic line 74 opens into a valve chamber 94.
  • a movable valve member 96 is arranged in the valve chamber 94.
  • the valve member 96 has a valve body 98.
  • the valve body 98 has a first closing surface 100 and a second closing surface 102 at opposite axial ends.
  • the valve chamber 94 further has a supply opening 104 which opens into a supply chamber 112.
  • the supply opening 104 is surrounded by and defined by a first valve seat 108.
  • a supply line 90 opens into the supply chamber 112 and provides the required hydraulic pressure.
  • the valve chamber 94 further comprises a discharge opening 106 which opens into a discharge chamber 114.
  • the discharge opening 106 is surrounded by a second valve seat 110 and thereby defined.
  • a discharge line 91 opens into the discharge chamber 114 in order to ensure rapid pressure relief.
  • An electromagnet 116 is provided for actively moving the valve member 96.
  • a spring 118 acts in the opposite direction to the electromagnet 116.
  • control piston 46 is cup-shaped.
  • the control piston has a control piston base 86 and a cylindrical control piston wall 84 protruding from it into the pneumatic chamber 48.
  • a clearance between the control cylinder 44 or the wall 56 of the control cylinder 44 and the control piston wall 84 can be selected to be small, for example in the range of 0.02 mm to 0.03 mm.
  • This design guides the control piston in the control cylinder.
  • the control piston wall 84 can have a length or height starting from the control piston base 86 that is at least twice and at most four times or at most three times as large as the diameter of the control piston 46 or control piston base 86 (it should be noted that Figure 3 in this respect is only schematic and not to scale).
  • the control piston 46 or the control piston base 86 is firmly connected to an end of the valve stem 36 facing away from the valve body 34.
  • An integral design ie a one-piece, uniform material design, is conceivable for this.
  • a material-fitting connection e.g. by welding is also conceivable.
  • the cylinder wall 56 of the control cylinder 44 has a recess 80 into which an O-ring 82 is inserted to seal against the control piston wall 84.
  • the seals 82 can also be provided.
  • pressures in the steam chamber 76 are in a range between 30 bar and 800 bar, preferably 30 to 500 bar, particularly preferably 30 to 180 bar, and temperatures in a range between 300 °C and 600 °C.
  • the inlet valve 26 is opened.
  • the electromagnet 116 of the double seat valve 88 is activated.
  • the valve member 96 is attracted or raised against the spring force of the spring 118.
  • the second closing surface 102 of the valve member 96 comes into contact with the second valve seat 110 and closes the discharge opening 106.
  • the first closing surface 100 of the valve member 96 lifts off the first valve seat 108 and opens the supply opening 104. This allows the hydraulic fluid to flow into the valve chamber and into the hydraulic chamber 50 via the hydraulic line 74.
  • the pressure in the hydraulic chamber 50 is thus increased by supplying hydraulic fluid via the hydraulic line 74 and the hydraulic opening 72.
  • the pressure in the hydraulic chamber 50 is reduced again by discharging hydraulic fluid from the hydraulic chamber 50 via the hydraulic opening 72 and the hydraulic line 74.
  • the electromagnet 116 of the double seat valve 88 is deactivated.
  • the valve member 96 is returned or moved downwards by the spring force of the spring 118.
  • the first closing surface 100 of the valve member 96 comes into contact with the first valve seat 108 and closes the supply opening 104.
  • the second closing surface 102 of the valve member 96 lifts off the second valve seat 110 and opens the discharge opening 106. This allows the hydraulic fluid to flow out of the hydraulic chamber 50 via the hydraulic line 74 and the valve chamber 94.
  • the pressure prevailing in the pneumatic chamber 48 acts on the upper side 58 of the control piston 46, causing it to move downwards.
  • the valve body 34 or its surface 38 is pressed into the valve seat 30 and the valve opening 28 is closed.
  • the stroke curve when opening and closing the intake valve 26 is in Figure 2
  • the valve lift is 3 mm.
  • the opening and closing of the inlet valve 26 takes about 3 ms.
  • the time to reach the "valve open" state is about 0.7 ms to 0.8 ms.
  • the valve remains open for about 1.6 ms, with the maximum valve lift being reached in this range.
  • the time for the valve to completely close is approximately 0.7ms to 0.8ms.
  • the opening flank (inclination and compression) can be adjusted almost arbitrarily via the pressure in the hydraulic chamber 50. Due to the fact that the hydraulic chamber 50 only works against the air pressure in the pneumatic chamber 48, very fast opening (steep opening flank) is also possible.
  • a constant air pressure can be present in the pneumatic chamber 48, so that the closing flank can only be adjusted via the hydraulic chamber 50.
  • the air pressure can be 50 bar, but usually depends on the maximum pressure in the working chamber 18 (full pressure). To ensure reliable closing, the air pressure is always set above the full pressure.
  • the air pressure in the pneumatic chamber 48 essentially replaces the function of a conventional spring.
  • the use of gas enables the inlet valve 26 to be opened much more quickly than with a spring due to the inert mass of the spring.
  • the required closing pressures would also require a spring preload of around 300 kg, which would result in considerable effort during assembly.
  • the air pressure in the pneumatic chamber 48 can be variably controlled by supplying gas pressure via the air pressure line 70 and the air pressure opening 68. This also makes it possible to adjust the closing flank (slope and compression) almost as desired.
  • gas pressure in the pneumatic chamber 48 also has the considerable advantage that the gas pressure can also be used to seal the control piston 46 against the Hydraulic chamber 50 acts.
  • the gas pressure counteracts the inflow of hydraulic fluid from the hydraulic chamber 50 through the space between the outer circumferential surface 54 of the control piston 46 and the inner wall 56 of the control cylinder 44. Consequently, despite the relatively high pressures, a relatively simple seal in the form of a piston ring 52 or an O-ring is possible.
  • a rod seal 66 is provided around the outer circumference of the valve stem 36, which seals against both the ingress of fresh steam into the hydraulic chamber 50 and the escape of hydraulic fluid from the hydraulic chamber 50.
  • the combination of pneumatic and hydraulic control of the intake valve 26 offers significant advantages in terms of assembly, operation and adjustability of the intake valve lift curve.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)

Claims (14)

  1. Moteur à vapeur comprenant
    un cylindre (10),
    un piston alternatif (12) guidé de manière mobile entre un point mort supérieur et un point mort inférieur dans le cylindre (10),
    un espace de travail (18) dans le cylindre (10), qui est délimité par le piston alternatif (12),
    un espace à vapeur (76) destiné à fournir de la vapeur vive,
    une soupape d'entrée (26) avec une ouverture (28) de soupape, qui relie l'espace à vapeur (76) et l'espace de travail (18), un siège (30) de soupape entourant l'ouverture (28) de soupape et un organe (32) de soupape mobile coopérant avec le siège (30) de soupape pour fermer et dégager l'ouverture (28) de soupape,
    une commande (42) de soupape destinée à déplacer l'organe (32) de soupape,
    caractérisé en ce que
    la commande (42) de soupape présente :
    un cylindre de commande (44) et
    un piston de commande (46), qui coopère avec l'organe (32) de soupape et divise le cylindre de commande (44) en une chambre pneumatique (48) et une chambre hydraulique (50), la chambre hydraulique (50) étant apte à être soumise à une action de fluide hydraulique pour retirer l'organe (32) de soupape du siège (30) de soupape et pour dégager l'ouverture (28) de soupape.
  2. Moteur à vapeur selon la revendication 1, dans lequel, pour retirer l'organe (32) de soupape du siège (30) de soupape dans l'espace à vapeur (76), la chambre pneumatique (48) est opposée au siège (30) de soupape et la chambre hydraulique (50) est tournée vers le siège (30) de soupape.
  3. Moteur à vapeur selon la revendication 1 ou la revendication 2, dans lequel l'organe (32) de soupape présente une tige (36) de soupape allongée et le piston de commande (46) est relié, en particulier est relié de manière solidaire, à la tige (36) de soupape.
  4. Moteur à vapeur selon l'une quelconque des revendications précédentes, dans lequel l'organe (32) de soupape est guidé de manière mobile linéairement.
  5. Moteur à vapeur selon l'une quelconque des revendications précédentes, dans lequel la chambre pneumatique (48) est soumise à l'action d'une pression de gaz avec une pression sensiblement constante.
  6. Moteur à vapeur selon l'une quelconque des revendications 1 à 4, dans lequel la chambre pneumatique (48) peut être soumise à l'action d'une pression de gaz avec une pression variable.
  7. Moteur à vapeur selon l'une quelconque des revendications précédentes, dans lequel la course de l'organe (32) de soupape se situe, lors du retrait de l'organe (32) de soupape du siège (30) de soupape, dans une plage entre 1 mm et 5 mm.
  8. Moteur à vapeur selon l'une quelconque des revendications précédentes, dans lequel l'organe (32) de soupape présente un poids de 100 g à 300 g.
  9. Moteur à vapeur selon l'une quelconque des revendications précédentes, dans lequel le piston de commande (46) est étanchéifié par rapport à une paroi intérieure (56) du cylindre de commande (44).
  10. Moteur à vapeur selon la revendication 9, dans lequel un joint d'étanchéité (82) est installé dans la paroi intérieure (56) du cylindre de commande (44).
  11. Moteur à vapeur selon l'une quelconque des revendications précédentes, dans lequel le piston de commande (46) est configuré en forme de coupelle.
  12. Moteur à vapeur selon l'une quelconque des revendications précédentes, dans lequel le cylindre de commande (44) est étanchéifié par rapport à l'organe (32) de soupape, en particulier à la tige (36) de soupape de l'organe (32) de soupape.
  13. Moteur à vapeur selon l'une quelconque des revendications précédentes, dans lequel le piston de commande (46) a un diamètre dans une plage entre 20 et 30 mm, de manière préférée de 20 à 25 mm.
  14. Moteur à vapeur selon l'une quelconque des revendications précédentes, dans lequel la chambre hydraulique (50) présente une ouverture hydraulique (72) reliée à une conduite hydraulique (74) pour l'amenée de fluide hydraulique dans la chambre hydraulique et pour son évacuation hors de celle-ci, laquelle est reliée à une soupape à double siège (88), dans lequel la soupape à double siège (88) est reliée à une conduite d'amenée (90) et à une conduite d'évacuation (91), qui sont ouvertes et fermées en alternance par un organe (96) de soupape commun.
EP22162444.8A 2022-03-16 2022-03-16 Moteur à vapeur Active EP4245969B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP22162444.8A EP4245969B1 (fr) 2022-03-16 2022-03-16 Moteur à vapeur
PCT/EP2023/056161 WO2023174816A1 (fr) 2022-03-16 2023-03-10 Moteur à vapeur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP22162444.8A EP4245969B1 (fr) 2022-03-16 2022-03-16 Moteur à vapeur

Publications (3)

Publication Number Publication Date
EP4245969A1 EP4245969A1 (fr) 2023-09-20
EP4245969C0 EP4245969C0 (fr) 2024-04-17
EP4245969B1 true EP4245969B1 (fr) 2024-04-17

Family

ID=80785005

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22162444.8A Active EP4245969B1 (fr) 2022-03-16 2022-03-16 Moteur à vapeur

Country Status (2)

Country Link
EP (1) EP4245969B1 (fr)
WO (1) WO2023174816A1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL370154A1 (pl) * 2004-09-17 2006-03-20 HUZAR POWER Sp.z o.o. Wtryskiwacz czynnika roboczego do tłokowego silnika parowego
US9739179B2 (en) 2015-03-13 2017-08-22 International Business Machines Corporation Working fluid for a device, device and method for converting heat into mechanical energy
GB201518833D0 (en) * 2015-10-23 2015-12-09 Univ Newcastle Free piston engine power plant
PL426295A1 (pl) * 2018-07-10 2020-01-13 Prosperitos Spółka Z Ograniczoną Odpowiedzialnością Sposób zasilania parą wodną o parametrach ultra-nadkrytycznych tłokowych silników parowych i zawór do zasilania parą wodną o parametrach ultra-nadkrytycznych tłokowych silników parowych
EP3798413B1 (fr) 2019-09-30 2022-08-10 RD Estate GmbH & Co. KG Soupape de commande pour un moteur à vapeur, moteur à vapeur comportant une soupape de commande ainsi qu'installation de production combinée électricité-chaleur comportant le moteur à vapeur

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Publication number Publication date
EP4245969A1 (fr) 2023-09-20
EP4245969C0 (fr) 2024-04-17
WO2023174816A1 (fr) 2023-09-21

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