EP3798413B1 - 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 - Google Patents

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 Download PDF

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Publication number
EP3798413B1
EP3798413B1 EP19200418.2A EP19200418A EP3798413B1 EP 3798413 B1 EP3798413 B1 EP 3798413B1 EP 19200418 A EP19200418 A EP 19200418A EP 3798413 B1 EP3798413 B1 EP 3798413B1
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EP
European Patent Office
Prior art keywords
valve
valve seat
valve body
control valve
steam
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
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EP19200418.2A
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German (de)
English (en)
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EP3798413A1 (fr
Inventor
Robert Duschl
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RD Estate GmbH and Co KG
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RD Estate GmbH and Co KG
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Priority to EP19200418.2A priority Critical patent/EP3798413B1/fr
Publication of EP3798413A1 publication Critical patent/EP3798413A1/fr
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Publication of EP3798413B1 publication Critical patent/EP3798413B1/fr
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Classifications

    • 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
    • F01B29/00—Machines or engines with pertinent characteristics other than those provided for in preceding main groups
    • F01B29/08—Reciprocating-piston machines or engines not otherwise provided for
    • F01B29/10—Engines
    • F01B29/12—Steam engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L23/00—Valves controlled by impact by piston, e.g. in free-piston machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/08—Valves guides; Sealing of valve stem, e.g. sealing by lubricant
    • F01L3/085—Valve cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/22—Valve-seats not provided for in preceding subgroups of this group; Fixing of valve-seats

Definitions

  • the present disclosure relates to a control valve for a steam engine, for example a steam engine that performs mechanical work using steam as its working fluid. More specifically, the present disclosure relates to a control valve for a reciprocating steam engine, preferably having application in electric power generation. Furthermore, the present disclosure relates to a steam engine having the aforementioned control valve and a combined heat and power plant having the steam engine.
  • CHP plants Decentralized combined heat and power plants
  • CHP plants have long been established as an advantageous alternative to the conventional combination of local heating and central power plant.
  • CHP plants are used to generate electrical energy and to generate useful heat, in particular CHP plants are preferably operated on site or in the vicinity of the useful heat sink.
  • Combustion engines such as diesel or Otto engines, Stirling engines, steam engines, internal combustion turbines or steam engines can be used, for example, to drive the power generator.
  • Well-known steam engines such as the in WO 2016/146159 A1 described, which are used in particular for power generation, however, have the disadvantage that, for example, a relatively high level of leakage occurs during a cold start. This is due in particular to the fact that the steam injected into the steam engine (superheated steam or live steam) at a pressure of 40 bar to 150 bar is injected into the piston chamber in a relatively short time and acts there for a long time, which places high demands on the piston ring seal, which separates the water vapor from the lubricating oil in the crankshaft space or in the oil pan.
  • Such valves for controlling and/or regulating a fluid flow generally include a valve seat and a valve member that is mounted so that it can move axially.
  • the valve member typically includes a valve stem and a valve body at one end thereof.
  • a valve drive is also provided, which is directly or indirectly connected to the valve stem in a force-transmitting manner.
  • the valve body can be lifted off the valve seat to open the valve and flow through the pipeline or the valve can be made possible.
  • the valve body is brought back into contact with the valve seat, thus blocking fluid flow through the tubing.
  • Valves for controlling or regulating a fluid flow are known in the prior art, which are intended to enable simplified interaction of the valve body and the valve seat by means of a conical valve seat. In particular, this guides the valve body into the valve seat, which should lead to reliable and low-wear closing even with high forces. Nevertheless, even these valves do not provide a satisfactory result at high temperatures and pressures.
  • the object of the invention is to provide a control valve for controlling and/or regulating a steam flow in a steam engine, which is capable of reliably and permanently closing or shutting off the steam engine, despite the high temperatures and pressures present in the working cycle of a steam engine to ensure the valve while realizing ease of manufacture and easy maintenance.
  • One of the basic ideas of the present disclosure is to create a defined contact surface, in particular an annular contact surface between the valve body and the valve seat, with which a reliable and permanent closing or shutting off of the valve is ensured despite the high temperatures and pressures present in the working cycle of a steam engine can be performed while realizing ease of manufacture and maintenance.
  • the present disclosure provides a control valve in which an easily definable and manufacturable annular surface is realized between a conical component and a flat component.
  • a control valve for controlling and/or regulating a steam flow in a steam engine has: a valve seat, a valve body, which is guided in translation along a central axis CA of the control valve and is preferably subjected to a force against the valve seat by means of an elastic element , with a the valve seat axial end of the valve body facing toward the central axis of the valve body has a surface tapered toward the center axis of the valve body, thereby forming an annular contact surface with the valve seat, or an axial end of the valve seat facing the valve body has a surface tapered toward the central axis of the valve seat, thereby forming an annular contact surface with the Valve body is formed.
  • axial can be understood here as along the main axis of the valve member or the valve train or along the central axis of the control valve itself and corresponds to the longitudinal direction of said elements.
  • a slanted surface of the valve seat or that of the valve body is slanted inward toward the central axis, whereby the annular contact surface is formed in the region of the outer circumference of the slanted surface, the central axis of the valve seat and/or the central axis of the valve body runs parallel to the central axis CA, in particular approximately aligned with it.
  • the term "inwards” can be understood in such a way that the surface is beveled in the direction of the material of the respective element, e.g. the valve body, which forms a depression in the middle of the valve body.
  • the surface of the valve body, the facing the valve seat, funnel-shaped, ie has a conical shape.
  • an angle of inclination ⁇ of the slanted surface of the valve seat or of the valve body to a plane that is defined by the contact surface between the valve body and the valve seat and runs perpendicular to the central axis is between 0.5° and 1.5° 1°, is.
  • the conical surface produced in this way and the contact surface connected thereto can easily be brought back to size after an optional heat treatment, in particular hardening, which can be achieved, for example, by grinding.
  • the contact surface created in this way can also be easily repaired by grinding after a long period of use and the associated wear and tear.
  • valve seat is formed by a valve seat disk, which has a flat surface, at least in the region of the contact surface with the valve body, which is preferably aligned perpendicularly to the central axis CA.
  • valve seat from a valve seat disc also brings with it the advantage that it is easy to produce and to repair. Furthermore, the valve seat can be easily replaced in this way.
  • valve body has a projection on the axial end facing the valve seat, which is set up to interact with a valve drive in a force-transmitting manner in order to lift the valve body from the valve seat and thereby open the control valve, the valve drive and the Valve body are preferably formed decoupled.
  • a decoupling is to be understood here as meaning that the valve train and the valve body can move relative to one another and independently of one another.
  • valve body is made of a tough material, for example HSS steel (high-speed steel or high-alloy tool steel), which preferably has an elongation at break of at least 5%, more preferably at least 10%. It is also advantageous if at least one of the contact surfaces is plated.
  • the contact surfaces are the upper surface of the valve body which comes into contact with the elastic element, the lower surface of the valve body which comes into contact with the valve train, and the contact surface with the valve seat.
  • the plating is carried out using a build-up welding process such as, for example, plasma powder build-up welding, also known as the PTA process.
  • a build-up welding process such as, for example, plasma powder build-up welding, also known as the PTA process.
  • nickel martensite, tungsten carbide or stellite or a cobalt-chromium hard alloy can be used as the coating material.
  • the contact surfaces which are thus provided with an anti-wear coating, are preferably ground.
  • a wear ring made of nickel martensite, tungsten carbide, stellite or a cobalt-chromium hard alloy or a composite of ceramic and metal onto a base body of the valve body made of HSS steel, for example.
  • the shrunk-on ring can then be provided with the beveled surface described above to form the annular contact surface between valve seat and valve body.
  • valve seat or valve seat disc is preferably made of a very hard, wear-resistant material that is impact-resistant. There is no need for a tough core, as there is no bending stress (fracture stress).
  • the valve seat or the valve seat disc can also be made from a composite of ceramic and metal.
  • valve seat disc has an inner diameter that is at least large enough for the projection of the valve body and/or the valve drive to extend/protrude at least partially into the inner bore of the valve seat disc in the axial direction, i.e. in the direction of the central axis CA. preferably reach/stand through them, can/can.
  • the valve body is biased against the valve seat by steam pressure and the elastic member functions only as a damper.
  • the spring force of the elastic element which presses the valve body against the valve seat, is adjusted so that the valve only opens when a certain force is applied by the valve drive, which means that the valve can be prevented from opening too early. A targeted opening of the valve can thus be achieved.
  • the closing force of the control valve regulates itself in this way independently or automatically.
  • the necessary closing forces of the control valve which can be used to ensure adequate tightness/sealing of the control valve, increase.
  • the vapor pressure of the working fluid is used directly to provide the necessary closing force of the control valve, the available closing force also increases with higher working pressure.
  • live steam is to be understood in the present disclosure as steam/superheated steam which for example, from a steam generator to a steam engine for operating the steam engine.
  • the live steam usually has pressures in the range from 40 to 140 bar and temperatures above 500°C.
  • the contact surface of the valve seat and/or the valve body is hardened, and preferably the hardness of the valve body is greater than the hardness of the valve seat. In this way, a sufficiently high hardness/strength of the contact surface can be ensured, which is necessary to be able to withstand the high surface pressure.
  • the annular contact surface between the valve body and the valve seat has an annular width of 0.2 mm to 3 mm, preferably 0.5 mm to 2 mm, more preferably 1 mm.
  • the present disclosure relates to a steam engine, in particular a piston steam engine, which is preferably used for generating electric power, having: at least one cylinder which encloses a working space, one in the working space between a top dead center OT and a bottom dead center UT along a central axis CA of the cylinder reciprocating piston, and the control valve described above, wherein the control valve serves to control and/or regulate a fluid flow, in particular a steam flow, which acts as the working fluid (flow) of the steam engine.
  • valve drive of the control valve is designed as a projection of the piston, which is arranged on an upper end of the piston that faces the control valve, the projection lifting the valve body from the valve seat when the piston moves in the area / near the top dead center to open the control valve.
  • the projection has a conical shape, which has a flat contact surface, in particular aligned perpendicularly to the central axis CA, in particular on the side facing the valve body. In this way it is possible to form a circular contact surface between the valve body and the valve train and thus to reduce the surface pressure that occurs and the associated wear.
  • the contact surface of the valve train is plated, in particular using a build-up welding process such as plasma powder build-up welding, also known as the PTA process.
  • the piston is provided with a concave recess on its upper side, into which the coating material is introduced by means of build-up welding and is then ground to form a flat contact surface.
  • nickel martensite, tungsten carbide or stellite or a cobalt-chromium hard alloy can be used as the coating material.
  • the steam engine has an antechamber that can be supplied with fresh steam from the outside, wherein the antechamber has an opening for introducing the live steam into the working space, and the opening can be opened and closed by the control valve.
  • valve body is designed in the form of a cylindrical plunger, which can be moved in translation by an axial guide along the central axis CA of the control valve, which is preferably approximately aligned with a central axis CA of the cylinder 10, and preferably by pressure of the live steam that is applied to a side of the valve body facing away from the valve seat, a force is applied against the valve seat.
  • the present disclosure relates to a combined heat and power plant that has a steam generator and the steam engine described above, wherein the steam engine is coupled to a generator for generating electrical power.
  • the CHP system 100 shown consists of a steam generator 110, which is connected via a valve 180 to an inlet of a steam engine 1, 120, which drives a generator 130 to generate electricity.
  • a steam generator 110 which is connected via a valve 180 to an inlet of a steam engine 1, 120, which drives a generator 130 to generate electricity.
  • oil which, however, mixes with the expanded water vapor during the operation of the steam engine 1, 120 and is discharged with it.
  • the expanded steam discharged from the steam engine 1, 120 has a relatively large amount of oil.
  • the steam engine 1, 120 is followed by a condenser 150 for condensing the expanded steam, which has a pressure of approximately 0.15 bar and a temperature of approximately 55° C. when it leaves the steam engine 120.
  • the condensed water vapor which also contains a large proportion of oil, is fed to a condensate suction pump (or circulation pump) 170, in particular a piston pump, via a water column 190, which increases the pressure of the condensed water vapor to approx. 0.25 bar .sucked in by this one.
  • the condensate suction pump increases the pressure of the condensed water vapor or the oil-water mixture that is now present to approximately 1.50 bar and conveys the oil-water mixture to a device 140 for separating oil and water.
  • the separated or separated oil is routed back to a crankshaft chamber of the steam engine or injected into the steam engine for fine sealing and the cleaned water is routed to a feed water tank 160, which feeds the treated or cleaned water to the steam generator 110 again for steam generation Provides, so the cycle is closed.
  • FIG 2 1 shows a schematic sectional view of a steam engine 1 equipped with a control valve 50 according to an embodiment of the present invention.
  • the steam engine 1 shown has a cylinder 10 which has an upper end 11 and a lower end 12 .
  • the cylinder 10 is connected to a crankcase 20 at the lower end 12 .
  • a plurality of outlet openings 13 are provided in the circumferential direction in the cylinder wall/working space wall 14 of the cylinder 10 .
  • the outlet openings 13 connect a cylinder chamber or a working space 15 with an annular chamber 16 in order to discharge or discharge used steam from the working space 15 .
  • the outlet openings 13 are arranged close to a bottom dead center UT of a piston 30, which is located at bottom dead center UT in the view shown.
  • the piston 30 is translationally movable along a central axis CA of the cylinder 10 between the bottom dead center UT and a top dead center OT.
  • the piston 30 is connected to a crankshaft (not shown) housed in the crankcase 20 via a piston connecting rod or piston control rod (not shown).
  • the piston 30 has a sealing ring 31 at its lower end 32 and a plurality of sealing rings 31 at its upper end 33 .
  • the engine further includes a cylinder head unit 40 .
  • the cylinder head unit 40 has a first case body 41 and a second case body 42 . Furthermore, in the first housing body 41 is provided with an antechamber (vapor chamber) 44 which communicates with the working space 15 via an opening 43 .
  • the opening can be opened and closed by means of the control valve 50, which has a valve seat 51 and a valve body 52, with which the inflow of live steam (superheated steam that is under high pressure) into the working chamber can be controlled.
  • the control valve 50 is in the closed state, ie the valve body 52 is pressed against the valve seat 51 in order to prevent the flow of live steam into the working chamber 15 .
  • the valve body 52 is guided in translation along the central axis CA by means of an axial guide 55 and is subjected to a force or pressed against the valve seat 51 by an elastic element 54, which is implemented by a compression spring in the illustrated embodiment. Furthermore, the second housing body 42 contains fluid channels, not shown, with which the valve body 52 can be acted upon on its side facing away from the valve seat 51 with the working fluid, i.e. the superheated steam, in order to increase the closing force between the valve seat 51 and the valve body 52 and thus a tight Complete the opening 43 to ensure.
  • the working fluid i.e. the superheated steam
  • valve body 52 has, on an end facing valve seat 51, a surface 52A that is beveled inward toward a central axis of valve seat 51 or toward central axis CA, as a result of which the surface of valve body 52 facing valve seat 51 is funnel-shaped. In this way it is possible to realize a defined annular contact surface between the valve seat 51 and the valve body 52 .
  • FIG figure 3 shows an enlarged partial view of the schematic sectional view of FIG figure 2 , to the training of Control valve, in particular the valve seat 51 and the valve body 52 further to clarify.
  • the valve seat 51 is formed of a simple valve seat disk which is inserted into the first housing body 41. This makes it possible to easily replace the valve seat 41 after a long period of use and the associated wear. In this case, the valve seat 51 can be repaired for reuse by simply grinding it again.
  • the inwardly tapered surface 52A forms with the plane defined by the contact area between valve body 52 and valve seat 51 and in which figure 3 is oriented horizontally, an inclination angle ⁇ , which is actually extremely flat, in a range of 0.5 ° to 1.5 °. However, to better illustrate the invention, the angle is shown much larger.
  • the valve body 52 has a projection 52B which is provided on the slanted surface 52A facing the valve seat 51 and projects into the opening 43. As shown in FIG.
  • the projection 52B makes it possible for the piston 30 to move the valve body 52 against the applied steam pressure and against the applied spring force of the Valve seat 52 is lifted and thus the opening 43 is released, whereby live steam can flow from the antechamber 44 into the working chamber 15 and thus the piston 30 can cause a downward movement from top dead center OT to bottom dead center UT.
  • the projection (valve drive 53) of the piston 30 has a spherical or curved surface/shape, whereby between the projection 52B of the valve body 52 and the projection of the Piston 30 a point contact point is realized and thus only forces in the axial direction, ie along the central axis CA, can be transmitted from the piston 30 to the valve body 52, but no transverse forces can be introduced into the valve body 52.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Lift Valve (AREA)

Claims (14)

  1. Vanne de commande (50) permettant de commander et/ou réguler une circulation de vapeur dans un moteur à vapeur (1), comprenant :
    un siège de vanne (51),
    un corps de vanne (52) guidé en translation le long d'un axe central (CA) de la vanne de commande (50) et soumis à une force s'exerçant à rencontre du siège de vanne (51) au moyen d'un élément élastique (54),
    caractérisée en ce que
    une extrémité axiale, tournée vers le siège de vanne (51), du corps de vanne (52) présente une surface (52A) inclinée par rapport à l'axe central du corps de vanne (52) et formant une surface de contact annulaire avec le siège de vanne (51), ou
    une extrémité axiale, tournée vers le corps de vanne (52), du siège de vanne (51) présente une surface (51A) inclinée par rapport à l'axe central du siège de vanne (51) et formant une
    surface de contact annulaire avec le corps de vanne (52).
  2. Vanne de commande (50) selon la revendication 1, dans laquelle une surface inclinée (51A, 52A) du siège de vanne (51), ou celle
    du corps de vanne (52), est inclinée vers l'intérieur par rapport à l'axe central, de sorte que la surface de contact annulaire est réalisée dans l'étendue de la périphérie extérieure de la surface inclinée (51A, 52A), dans laquelle l'axe central du siège de vanne (51) et/ou l'axe central du corps de vanne (52) s'étend parallèlement à l'axe central (CA), en particulier de manière approximativement alignée avec celui-ci.
  3. Vanne de commande (50) selon la revendication 1 ou 2, dans laquelle un angle d'inclinaison α de la surface inclinée (51A, 52A) du siège de vanne (51) ou du corps de vanne (52) par rapport à un plan, qui est défini par la surface de contact entre le corps de vanne (52) et le siège de vanne (51) et s'étend de manière perpendiculaire à l'axe central (CA), est compris entre 0,5° et 1,5°, de préférence est égal à 1°.
  4. Vanne de commande (50) selon l'une quelconque des revendications précédentes, dans laquelle le siège de vanne (51) est réalisé sous la forme d'un disque de siège de vanne présentant de préférence, au moins dans l'étendue de la surface de contact avec le corps de vanne (52), une surface plane orientée de préférence perpendiculairement à l'axe central (CA).
  5. Vanne de commande (50) selon l'une quelconque des revendications précédentes, dans laquelle le corps de vanne (52) présente, sur l'extrémité axiale tournée vers le siège de vanne (51), une saillie (52B) conçue pour collaborer avec un entraînement de vanne (53) de manière à transmettre une force afin de décoller le corps de vanne (52) du siège de vanne (51) et ainsi ouvrir la vanne de commande (50), dans laquelle l'entraînement de vanne (53) et le corps de vanne (22) sont de préférence réalisés de manière découplée.
  6. Vanne de commande (50) selon la revendication 5, qui dépend de la revendication 4, dans laquelle le disque de siège de vanne présente un diamètre intérieur (Di) au moins suffisamment grand pour que la saillie (52B) du corps de vanne (52) et/ou l'entraînement de vanne (53) puisse/puissent rentrer/demeurer, de préférence s'enfoncer/loger, au moins partiellement dans l'alésage intérieur du disque de siège de vanne dans la direction axiale.
  7. Vanne de commande (50) selon l'une quelconque des revendications précédentes, dans laquelle le corps de vanne (52) est soumis à une force s'exerçant à rencontre du siège de vanne (51) du fait de la pression de vapeur, et l'élément élastique (54) fait office d'amortisseur.
  8. Vanne de commande (50) selon l'une quelconque des revendications précédentes, dans laquelle au moins la surface de contact du siège de vanne (51) et/ou du corps de vanne (52) est durcie, et la dureté du corps de vanne (52) est de préférence supérieure à la dureté du siège de vanne (51).
  9. Vanne de commande (50) selon l'une quelconque des revendications précédentes, dans laquelle la surface de contact annulaire présente une largeur annulaire comprise entre 0,2 mm et 3 mm, de préférence comprise entre 0,5 mm et 2 mm, de préférence est égale à 1 mm.
  10. Moteur à vapeur (1), en particulier moteur à vapeur à piston, qui est utilisé de préférence pour la production de courant électrique, comprenant :
    au moins un cylindre (10), qui renferme une chambre de travail (15),
    un piston (30) mobile en va-et-vient dans l'espace de travail (15) entre un point mort haut (OT) et un point mort bas (UT) le long d'un axe central (CA) du cylindre (10), et
    une vanne de commande (50) selon l'une quelconque des revendications 1 à 9, dans lequel la vanne de commande (50) sert à commander et/ou réguler une circulation de vapeur faisant office de fluide de travail du moteur à vapeur.
  11. Moteur à vapeur (1) selon la revendication 10, dans lequel l'entraînement de vanne (53) de la vanne de commande (50) est réalisé sous la forme d'une saillie du piston (30) agencée à une extrémité supérieure (33), tournée vers la vanne de commande (50), du piston, dans lequel la saillie décolle le corps de vanne (52) du siège de vanne (51) lorsque le piston (30) se trouve dans l'étendue du point mort haut (OT), ou à proximité de celui-ci, afin d'ouvrir la vanne de commande (50).
  12. Moteur à vapeur (1) selon la revendication 10 ou 11, comprenant en outre :
    une préchambre (44) pouvant être alimentée en vapeur vive depuis l'extérieur, dans lequel la préchambre (44) présente un orifice (43) permettant d'introduire la vapeur vive dans l'espace de travail (15), dans lequel l'orifice (43) peut être ouvert et fermé grâce à la vanne de commande (50).
  13. Moteur à vapeur (1) selon l'une quelconque des revendications 10 à 12, dans lequel le corps de vanne (52) est réalisé sous la forme d'un piston-chasse cylindrique qui est mobile en translation le long de l'axe central (CA), préférence approximativement aligné avec un axe central (CA) du cylindre (10), de la vanne de commande grâce à un guide axial (55) et qui est soumis de préférence à une force s'exerçant à rencontre du siège de vanne (51) grâce à la pression de la vapeur vive s'exerçant sur un côté, opposé au siège de vanne (51), du corps de vanne (52).
  14. Installation de cogénération, comprenant :
    un générateur de vapeur (110), et
    un moteur à vapeur (1, 120) selon l'une quelconque des revendications précédentes 10 à 13, dans lequel le moteur à vapeur est couplé à un générateur (130) permettant de produire de l'électricité.
EP19200418.2A 2019-09-30 2019-09-30 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 Active EP3798413B1 (fr)

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EP19200418.2A EP3798413B1 (fr) 2019-09-30 2019-09-30 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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EP19200418.2A EP3798413B1 (fr) 2019-09-30 2019-09-30 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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EP3798413A1 EP3798413A1 (fr) 2021-03-31
EP3798413B1 true EP3798413B1 (fr) 2022-08-10

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EP4245969B1 (fr) 2022-03-16 2024-04-17 RD Estate GmbH & Co. KG Moteur à vapeur
CN115110999A (zh) * 2022-06-24 2022-09-27 何致远 蒸汽发动机

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US1630750A (en) * 1925-06-15 1927-05-31 Krasno Philip Internal-combustion-engine valve
GB1163211A (en) * 1967-01-19 1969-09-04 Chadburns Res & Dev Ltd Improvements in or relating to Apparatus for Dispensing Liquids Incorporating a Reciprocating Pump
US4050357A (en) * 1974-06-25 1977-09-27 Carter Sr J Warne Steam admission valve and variable clearance volume steam cylinder
JPS5999016A (ja) * 1982-11-29 1984-06-07 Komatsu Ltd 蒸気エンジンのインパルス弁
US4766924A (en) * 1986-12-08 1988-08-30 The Lee Company Pressure relief valve
DE3913351A1 (de) * 1989-04-22 1990-10-25 Teves Gmbh Alfred Vorrichtung zur hilfsdruckerzeugung
WO2016146159A1 (fr) 2015-03-16 2016-09-22 Aross 3D Gmbh Moteur à vapeur

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