EP4245969A1 - Moteur à vapeur - Google Patents

Moteur à vapeur Download PDF

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Publication number
EP4245969A1
EP4245969A1 EP22162444.8A EP22162444A EP4245969A1 EP 4245969 A1 EP4245969 A1 EP 4245969A1 EP 22162444 A EP22162444 A EP 22162444A EP 4245969 A1 EP4245969 A1 EP 4245969A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
steam
valve member
steam engine
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.)
Granted
Application number
EP22162444.8A
Other languages
German (de)
English (en)
Other versions
EP4245969B1 (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 EP4245969B1 publication Critical patent/EP4245969B1/fr
Publication of EP4245969C0 publication Critical patent/EP4245969C0/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 the valve train of a steam engine.
  • CHP systems Decentralized combined heat and power systems
  • CHP systems have long been established as an advantageous alternative to the traditional combination of local heating and a central power plant.
  • CHP systems are used to generate electrical energy and useful heat; in particular, CHP systems are preferably operated on site or near the useful heat sink.
  • internal combustion engines such as diesel or gasoline engines, Stirling engines, steam engines, internal combustion turbines or steam engines can be used as a drive for the power generator.
  • Such inlet valves for controlling and/or regulating a fluid flow generally include 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.
  • the valve member in particular its valve body, can be lifted from the valve seat to open the valve and a flow through a valve opening can be made possible.
  • the valve member or the valve body is brought back into contact with the valve seat and thus blocks fluid flow through the valve opening.
  • Valves for controlling or regulating a fluid flow are known in the prior art, in which a closing force is applied to the valve body in the closing direction of the valve, ie in the direction of the valve seat, in order to automatically close the valve in the unactuated state (see e.g. WO 2016/146459 A1 or EP 3 798 413 ).
  • the spring force or tension force can decrease and the valve body can therefore be pressed into the valve seat with too little force.
  • wear can result in bypass flows in the valve and disruptions in the overall system in which the valve is used to control and/or regulate a fluid flow.
  • valve drive is formed by a tappet on the reciprocating piston, which interacts with the valve member at top dead center in order 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 and precise timing (opening time and/or opening speed) of the inlet valve can be ensured over a long period of operation.
  • 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 lift or opening as well as speed) of the inlet valve via the hydraulic pressure.
  • the stroke curve (incline, compression, etc.) can be adjusted largely as desired.
  • the pneumatics in the stroke curve can achieve a steep closing edge, meaning the inlet valve closes very quickly (especially compared to a spring). This allows the expansion phase of the steam in the working space of the reciprocating piston to be extended and greater efficiency to be achieved.
  • pneumatics are not subject to the above-mentioned disadvantages of a spring, in particular a steel spring. The tightness of the inlet valve can therefore be ensured over a very long period of time.
  • pneumatics enable relatively 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 movably guided in the cylinder between a top dead center and a bottom dead center, and a working space in the cylinder which is delimited by the reciprocating piston.
  • the working space is not necessarily to be understood as the maximum total volume that is limited by the reciprocating piston, but rather as the space in which the supplied live steam is expanded.
  • the steam engine further comprises a steam space for providing live 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 cooperates with the valve seat to close and release 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. Furthermore, a valve control for moving the valve member is provided.
  • the valve control includes 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 serves to close the valve opening, with the valve member or its valve body being pressed into the valve seat by the pneumatic pressure in the pneumatic chamber.
  • the hydraulic chamber can be supplied with hydraulic fluid in order to lift the valve member from the valve seat and open the valve opening.
  • a spring can additionally be provided in the pneumatic chamber for safety reasons, this spring is preferably not active during the normal closing process of the inlet valve or valve member. According to a preferred embodiment, the 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 spread evenly across the entire surface of the control piston distributed. This has the advantage that the control piston can be made thinner-walled and therefore lighter.
  • valve member or its valve body is lifted off the valve seat into the steam space.
  • 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 in a linearly movable manner.
  • the valve stem of the valve member can be guided in a linearly movable manner.
  • 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 with 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 air pressure. It can be referred to as compressed air.
  • other gaseous media can also be used, such as nitrogen.
  • the pressure in the pneumatic chamber variable.
  • the pressure of the gas fed in (gas pressure) 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 performance of the steam engine. For this purpose, for example, the maximum vapor pressure prevailing in the working space before expansion can be used as a parameter.
  • the stroke (valve lift) of the valve member when the valve member is lifted off the valve seat can be in a range between 1 mm and 5 mm.
  • the valve member including the cylinder piston connected to it 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 which 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, especially because the pressure in the pneumatic chamber counteracts the penetration of hydraulic fluid from the hydraulic chamber.
  • the seal can be attached to the piston. In one embodiment, however, the seal is mounted in the inner wall of the control cylinder. For example, a so-called rod seal can be used. This means the seal is 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 projecting into the pneumatic chamber.
  • a clearance between the control cylinder or the wall of the control cylinder and the control piston wall can be chosen to be small, for example in the range of 0.01 mm to 0.02 mm.
  • This configuration means that the control piston is guided in the control cylinder. Forces on any seals are thereby further reduced because the seal does not have to take on a guiding function.
  • an adequate seal can be achieved even without a seal if the play is only a few ⁇ m.
  • this design requires small manufacturing tolerances and can lead to problems during operation due to thermal expansion.
  • the control piston wall can have a length or height starting from the control piston base, which is at least twice and at most four times 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 relative to the valve member, in particular the valve stem of the valve member.
  • a rod seal is preferably used here, which seals in opposite directions.
  • control piston on the side of the hydraulic chamber can have a diameter in a range between 20mm and 30mm, preferably 20mm to 25mm. Due to the small diameter, the opening speed of the valve member can be reduced and brought to less than 1ms (e.g. 0.7ms or 0.8ms). With a diameter below 20mm, 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 above 30mm, the opening time becomes too long.
  • the hydraulic chamber can have a hydraulic opening connected to a hydraulic line for the supply and removal 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 a supply line and a discharge line on the other can be opened and closed alternately by a common valve member.
  • Cylinder assembly shown schematically includes a cylinder 10.
  • a reciprocating piston 12 is guided to move 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 space 18 is formed in the cylinder 10.
  • the working space 18 is limited at the bottom by the top 20 of the reciprocating piston 12.
  • the working space 18 is delimited by the cylinder head 22 or its underside/floor 24.
  • the volume of the working space is minimal. This volume is also called the compression volume or residual volume. If the reciprocating piston 12 is at bottom dead center, the volume of the working space 18 is maximum. This volume is also called the expansion volume.
  • the inlet valve 26 includes a valve opening 28, which is formed in the bottom 24 of the valve head 22 in the illustrated embodiment.
  • the inlet valve 26 comprises a valve seat 30 surrounding the valve opening 28 and a valve member 32 which interacts with the valve seat 30.
  • the valve member 32 includes a valve body 34 and a valve stem 36.
  • the valve body 34 includes a surface 38 which cooperates 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 be complementary to 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 therefore 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 accommodated in the guide 40 and guided in a linearly movable manner.
  • the cylinder head 22 further comprises a steam space 76, to which live steam can be supplied via a steam supply opening 78.
  • the live 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 in order to move the valve member 32 axially and to lift it from the valve seat 30 or bring it into contact with it in order to close and release the valve opening 28.
  • the valve control 42 includes 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. This requires an integral design, i.e. H. a one-piece, material-uniform design is conceivable.
  • fastening means e.g. screws
  • a cohesive connection e.g. by welding
  • the control piston 46 divides the control cylinder 44 into a pneumatic chamber 48 and a hydraulic chamber 50.
  • the control piston 50 also 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 an underside 62 of the control piston 46 and a lower end 64 (an underside) of the control cylinder 44.
  • the control piston has, in particular on its underside 62, a diameter in a range between 20mm and 30mm, preferably 20mm to 25mm.
  • a gas pressure opening 68 is also provided in the control cylinder 44, to which a gas pressure line 70 is connected. Via the gas pressure line 70 and the Gas pressure opening 68 can be supplied with gas to the pneumatic chamber 48.
  • a control valve 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 performance of the steam engine, for example the maximum pressure prevailing in the working space 18 before the 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 and removed 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 also has a supply opening 104 which opens into a supply chamber 112.
  • the supply opening 104 is surrounded and thereby 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 also has 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 Are defined.
  • a discharge line 92 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 which projects 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 chosen to be small, for example in the range of 0.02 mm to 0.03 mm.
  • This configuration means that the control piston is guided in the control cylinder.
  • the control piston wall 84 can have a length or height starting from the control piston base 86, which 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 regard 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, material-uniform design, is conceivable.
  • fastening means e.g. screws
  • a cohesive connection e.g. by welding
  • the cylinder wall 56 of the control cylinder 44 has a recess 80 into which an O-ring 82 is inserted for sealing against the control piston wall 84.
  • the seals 82 can also be provided.
  • the inlet valve 26 is opened.
  • the electromagnet 116 of the double-seat valve 88 is activated.
  • the valve member 96 is tightened 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 from the first valve seat 108 and releases 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 port 72.
  • the pressure in the hydraulic chamber 50 is again reduced 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 downward 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 from the second valve seat 110 and releases the discharge opening 106.
  • the pressure prevailing in the pneumatic chamber 48 acts on the top 58 of the control piston 46, so that it moves downwards.
  • the valve body 34 or its surface 38 is pressed into the valve seat 30 and the valve opening 28 is closed.
  • the lift curve when opening and closing the inlet valve 26 is in Figure 2 shown.
  • the valve lift is 3 mm. Opening and closing the inlet valve 26 takes approximately 3ms.
  • the time to reach the “valve open” state is approximately 0.7ms to 0.8ms.
  • the valve remains open for approximately 1.6ms, with the maximum valve lift being reached in this range.
  • the time to completely close the valve is again around 0.7ms to 0.8ms.
  • the opening flank (slope and compression) can be adjusted almost arbitrarily via the pressure in the hydraulic chamber 50. Because the hydraulic chamber 50 only works against the air pressure in the pneumatic chamber 48, very rapid opening (steep opening slope) can also be achieved.
  • a constant air pressure can be present in the pneumatic chamber 48, so that the closing edge can only be adjusted via the hydraulic chamber 50.
  • the air pressure can be 50 bar in an exemplary embodiment, but usually depends on the maximum pressure in the working space 18 (full pressure). To ensure reliable closing, the air pressure is always set above full pressure.
  • the air pressure in the pneumatic chamber 48 essentially replaces the function of a conventional spring.
  • the use of gas means that the inlet valve 26 can open significantly faster than with a spring due to the inert mass of the spring. Given the required closing pressures, the spring would also have to be preloaded by approx. 300 kg, which would lead to considerable effort during assembly.
  • the air pressure in the pneumatic chamber 48 can thus be 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 edge (pitch and compression) almost arbitrarily.
  • gas pressure in the pneumatic chamber 48 also has the significant advantage that the gas pressure is also used to seal the control piston 46 from the Hydraulic chamber 50 works.
  • the gas pressure counteracts the inflow of hydraulic fluid from the hydraulic chamber 50 through the space between the outer peripheral 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 prevents both the penetration of live steam into the hydraulic chamber 50 and the escape of hydraulic fluid from the hydraulic chamber 50 seals.
  • the combination of pneumatic and hydraulic control of the intake valve 26 provides 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)
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 true EP4245969A1 (fr) 2023-09-20
EP4245969B1 EP4245969B1 (fr) 2024-04-17
EP4245969C0 EP4245969C0 (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)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080093477A1 (en) * 2004-09-17 2008-04-24 Andrzej Miczyk Working - Fluid Injector for a Piston Steam Engine
WO2016146459A1 (fr) 2015-03-13 2016-09-22 International Business Machines Corporation Fluide de travail pour un dispositif, dispositif et procédé servant à convertir de la chaleur en énergie mécanique
US20190055898A1 (en) * 2015-10-23 2019-02-21 University Of Newcastle Upon Tyne Free Piston Engine Power Plant
EP3594459A1 (fr) * 2018-07-10 2020-01-15 Prosperitos sp. z o.o. Procédé et injecteur de vapeur permettant de fournir de la vapeur ultra-supercritique à des moteurs à piston à vapeur
EP3798413A1 (fr) 2019-09-30 2021-03-31 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

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080093477A1 (en) * 2004-09-17 2008-04-24 Andrzej Miczyk Working - Fluid Injector for a Piston Steam Engine
WO2016146459A1 (fr) 2015-03-13 2016-09-22 International Business Machines Corporation Fluide de travail pour un dispositif, dispositif et procédé servant à convertir de la chaleur en énergie mécanique
US20190055898A1 (en) * 2015-10-23 2019-02-21 University Of Newcastle Upon Tyne Free Piston Engine Power Plant
EP3594459A1 (fr) * 2018-07-10 2020-01-15 Prosperitos sp. z o.o. Procédé et injecteur de vapeur permettant de fournir de la vapeur ultra-supercritique à des moteurs à piston à vapeur
EP3798413A1 (fr) 2019-09-30 2021-03-31 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

Also Published As

Publication number Publication date
EP4245969B1 (fr) 2024-04-17
WO2023174816A1 (fr) 2023-09-21
EP4245969C0 (fr) 2024-04-17

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