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EP2354475A2 - Procédé de fonctionnement d'un piston à expansion d'un moteur à vapeur - Google Patents

Procédé de fonctionnement d'un piston à expansion d'un moteur à vapeur Download PDF

Info

Publication number
EP2354475A2
EP2354475A2 EP10015706A EP10015706A EP2354475A2 EP 2354475 A2 EP2354475 A2 EP 2354475A2 EP 10015706 A EP10015706 A EP 10015706A EP 10015706 A EP10015706 A EP 10015706A EP 2354475 A2 EP2354475 A2 EP 2354475A2
Authority
EP
European Patent Office
Prior art keywords
steam
dead center
piston
outlet opening
cylinder
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
EP10015706A
Other languages
German (de)
English (en)
Other versions
EP2354475A3 (fr
EP2354475B1 (fr
Inventor
Raimund Prof.Dr. Almbauer
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.)
MAN Truck and Bus SE
Original Assignee
MAN Nutzfahrzeuge Oesterreich AG
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 MAN Nutzfahrzeuge Oesterreich AG filed Critical MAN Nutzfahrzeuge Oesterreich AG
Publication of EP2354475A2 publication Critical patent/EP2354475A2/fr
Publication of EP2354475A3 publication Critical patent/EP2354475A3/fr
Application granted granted Critical
Publication of EP2354475B1 publication Critical patent/EP2354475B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B17/00Reciprocating-piston machines or engines characterised by use of uniflow principle
    • F01B17/02Engines
    • F01B17/04Steam engines
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/36Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of positive-displacement type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine

Definitions

  • the invention relates to a method for operating a piston expander, in which live steam is passed from a steam supply through an inlet valve into a cylinder space, which is released into the cylinder chamber live steam in the power stroke due to a movement of a piston from the upper to the lower dead center and the relaxed steam after Reaching the bottom dead center is passed from a closable outlet opening in a steam discharge.
  • the waste heat arising in the region of the internal combustion engine and / or in the exhaust gas discharge is at least partially transferred to a secondary heat cycle.
  • a heat transfer fluid is circulated and this usually at least partially evaporated in an evaporator, the steam in an expansion unit, for example in a piston expander, relaxed and finally liquefied in a condenser.
  • the mechanical work generated by the expansion unit is supplied as additional work to the drive system, in particular a vehicle drive system.
  • the known from the prior art steam piston expander are usually operated in two-stroke process.
  • the live steam is introduced via an inlet valve into a cylinder of the expander unit, and in the following work cycle, the steam is released while releasing work.
  • the exhaust valve is opened and pushed out during the Ausschiebetaktes by moving the piston from the lower to the upper dead center of the expanded steam from the cylinder.
  • the exhaust valve closes and the corresponding cycle begins again.
  • the compression ratio must be designed so that the working medium is relaxed in the working cycle to a suitable level.
  • the compression ratio is too low, the working fluid will have an overpressure with respect to the backpressure in the outlet duct when opening the outlet valve The potential for greater relaxation has a negative impact on the efficiency of the cycle.
  • the compression ratio is made too large, the working fluid is expanded to a pressure below the counter-pressure in the outlet conduit, which makes it more difficult to expel the expanded vapor and in turn adversely affects the efficiency of the cyclic process.
  • the invention has for its object to provide a method for operating a steam piston expander unit, which is operable with a relatively high efficiency.
  • the method to be specified is intended in particular to reduce the amount of fresh steam required for filling the piston, without this significantly reducing the efficiency of the cycle.
  • a method for operating a piston expander in which live steam is passed from a steam supply through an inlet valve into a cylinder space, the fresh steam introduced into the cylinder chamber is relaxed in the power stroke due to movement of a piston from the upper to the lower dead center and the relaxed steam at least partially is passed from a closable outlet opening in a steam discharge, has been developed such that the outlet opening is opened at or after reaching the bottom dead center and then closed before the piston reaches the top dead center in the exhaust stroke.
  • the exhaust port only during a relatively short period, for example, in the lower dead center, or over a longer period of time, especially until about a crankshaft angle of about 30 ° before top dead center is reached to open.
  • the reduction of the steam quantity per cycle of the working process is possible in two ways.
  • the inlet valve throttles the live steam to a lower pressure than the live steam pressure.
  • this reduction in pressure leads to a decisive reduction in the efficiency.
  • the method according to the invention makes use of a second possibility for reducing the amount of live steam per cycle.
  • the outlet opening is not open during the entire Ausschubtaktes, ie during the time in which the piston moves from the lower to upper dead center, but the outlet is closed well before the piston reaches the top dead center.
  • This residual steam remaining in the cylinder is advantageously compressed in the exhaust stroke by the movement of the piston to the top dead center.
  • the inlet valve is opened, there is already a markedly increased pressure in comparison to the counter-pressure which otherwise prevails in the cylinder without compression of the residual steam.
  • Due to the relative to the usual back pressure increased pressure within the cylinder also only a relatively small amount of fresh steam is introduced into the cylinder. Nevertheless, due to the injection of the live steam, the mixing steam forming in the damaged volume of the cylinder is brought to a pressure which corresponds to the live steam pressure.
  • the live steam pressure is achieved here by a further compression of the already biased residual steam within the Schadvolumens of the cylinder, wherein the state of the mixed steam adjusts after injection of the live steam in dependence on the states of the precompressed residual steam and the live steam.
  • This mixed vapor pressure can be achieved independently of the choice of a suitable compression ratio.
  • the inventive method for operating a piston expander is achieved in an advantageous manner that the efficiency of the expander is comparatively high and at the same time a moderate increase in pressure within the cylinder is achieved.
  • the moderate increase in pressure is due to the fact that this is realized over a longer period of time, since initially the residual steam is biased and compressed only after this by injecting live steam to the live steam pressure level.
  • the outlet opening is closed as soon as the piston is in a region between the lower and upper dead center.
  • the outlet opening is closed at a crankshaft angle of 20 ° to 60 ° before the top dead center.
  • a closing of the outlet opening in a range of about 45 ° crankshaft angle before the top dead center.
  • the second alternative embodiment represents, as it were, a limiting case for the method according to the invention.
  • the outlet opening is exclusively opened or kept open as and as long as the piston is in the area of the lower dead center.
  • the opening is made in a crankshaft angle range of 20 ° before to 20 ° after the bottom dead center.
  • a very specific development of the invention provides for a piston stroke of 75 to 85 mm, in particular of 80 mm, a crankshaft angle range of 30 ° for an opening of the exhaust valve. If the piston moves towards the upper dead center again following the opening of the outlet valves, the outlet openings are closed again.
  • the inventive method can be realized with relatively simple structural means.
  • a use of an additional exhaust valve is dispensed with.
  • the opening of the outlet valve takes place in the previously described embodiment of the method according to the invention in the lower dead center. If the piston moves from the bottom dead center toward the top dead center the outlet opening is closed again, so that the mixing steam remaining in the cylinder is compressed.
  • the inlet valve is preferably opened as soon as the piston reaches the top dead center and is kept open up to a crankshaft angle of about 30 ° after top dead center.
  • a mixed steam is generated by the supply of the live steam into the cylinder space, in particular the Schadvolumen the cylinder space, the mixed steam pressure at least approximately corresponds to the live steam pressure.
  • the comparatively high mixed vapor pressure The live steam pressure is achieved here by further compression of the already biased residual steam within the damaged volume of the cylinder, wherein the state of the mixed steam is adjusted after injection of the live steam as a function of the states of the precompressed residual steam and the live steam.
  • FIG. 1 the stroke of a valve is shown in an outlet opening of the cylinder of a steam expander.
  • the function curves a, b, c of the valve lift over the crankshaft angle with respect to three different valve controls are given.
  • the reaching of the lower as well as the upper dead center is in each case by a vertically running Line indicated at about 182 ° or 361 ° crankshaft angle.
  • the solid thin functional curve a and the dotted curve b respectively show the stroke of the exhaust valve in known standard methods.
  • the third function curve c which is designed as a thick line, shows the valve lift of the exhaust valve when using the method according to the invention for opening and closing the exhaust valve.
  • FIG. 2 In addition to the in FIG. 1 illustrated course of the stroke of the exhaust valve during the movement of a piston, are in FIG. 2 the pressure gradients for the three in FIG. 1 shown illustrated method for closing the outlet opening. It can be clearly seen that in the standard methods a, b a very rapid increase in pressure takes place shortly before reaching the upper dead center. In comparison, the pressure increase is at an early closing of the exhaust valve, so well before the piston reaches the top dead center, very soft. This is due to the fact that with an early closing of the exhaust valve, the pressure in the cylinder increases continuously by the compression of the residual steam, while using the standard methods a, b, the pressure only very close to reaching the top dead center, in particular about 10 ° crankshaft angle before reaching of the upper dead center, rises.
  • FIG. 3 is schematically the structure of a steam expander, with which the inventive method can be ⁇ -executed, shown. Since a corresponding steam expander is usually operated in the two-stroke cycle, crankshaft and camshaft speed are the same, so that the intake and exhaust valves are actuated by means of a corresponding, provided on the crankshaft crank arm. Such an embodiment offers above all the advantage that neither an additional camshaft nor a corresponding drive is required. Of course, it is conceivable in principle to provide an additional camshaft in addition to the crankshaft even with a steam piston expander operated in a two-stroke process.
  • the invention relates to a method for the suitable actuation of intake and exhaust valves of a piston engine for steam release.
  • FIG. 3 schematically illustrated three technical possibilities with which the actuation of the valves 4, 5 can be realized.
  • the method according to the invention which relates in the main to the time of opening and closing of the valves 4, 5, can be carried out.
  • the crankshaft 1, the camshaft 2 with the molded-on cams 3, the inlet valve 4, the outlet valve 5, the position sensor 6 are illustrated, components of a steam piston expander which are essential for realizing the method according to the invention and an actuating unit 7.
  • the actuation of the valves takes place via the crankshaft 1 (FIG. Fig. 3a ), via the camshaft 2 (3b) or the further actuating unit (7), which can be driven electrically, hydraulically or pneumatically.
  • a further actuating unit 7 which is characterized in particular by the fact that there is no mechanical connection between the crankshaft 1 and the inlet or outlet valve, a position sensor 6 on the crankshaft and a control unit 10 are also provided. With the help of the position sensor 6, the current position of the crankshaft 1 is determined and fed a corresponding value as an input to the control unit. In the control unit 10, this value is processed and an output variable is generated, on the basis of which the actuation of the inlet or outlet valve 4, 5 takes place by the actuating unit 7.
  • the mixed steam forming in the cylinder has a pressure which corresponds at least almost to the live steam pressure in the steam feed 8.
  • the live steam pressure is achieved here by a further compression of the already biased residual steam within the Schadvolumens of the cylinder, wherein the state of the mixed steam adjusts after injection of the live steam in dependence on the states of the precompressed residual steam and the live steam.
  • the inlet valve 4 is closed again. Due to the compressed mixed steam in the cylinder, the piston 9 is now moved in the working cycle in the direction of the lower dead center, so that the steam is released. Upon reaching the bottom dead center, an outlet opening 5 is opened. In a first alternative, this is designed as a slot 11 in the cylinder wall, which is released as soon as the piston 9 is in the area of the lower dead center. Preferably, the exhaust port is released by sweeping the piston edge at a crankshaft angle of about 20 ° before reaching the bottom dead center. By the released outlet opening 5 and the outlet slot 11 escapes now relaxed mixed steam.
  • the outlet opening 5 is closed. If the outlet opening does not have an outlet valve but has the slot already described, this is closed again due to the movement of the piston in Ausschiebetakt and the consequent sweeping the piston edge.
  • the residual steam is compressed in such a way that the residual vapor pressure is only slightly lower than the live steam pressure when the upper dead center is reached.
  • the low pressure difference between residual steam and live steam offers the advantage that when the live steam is injected into the damaged volume of the cylinder, vapors which are very similar to exergetically are mixed with one another.
  • the components of the cylinder in particular the inlet valve due to the compression of the residual steam and the associated small difference between residual steam and live steam pressure comparatively little stress.
  • no valve is required in addition to the inlet valve 4. After reaching the top dead center again the inlet valve 4 is opened and the described cycle begins again.
  • a valve is also provided in the outlet opening 5, which is actuated via a crank web of the crankshaft 1, a cam 3 of the camshaft 2 or a further actuating unit 7.
  • the exhaust valve is opened as soon as the piston has reached the bottom dead center and closed at a crankshaft angle of about 45 ° before the top dead center. After the exhaust valve 5 has been closed, the residual vapor remaining in the cylinder is in turn compressed by the movement of the piston, thereby achieving the advantages already mentioned in connection with the description of the first alternative.
  • valves are suitably secured by means of a crank arm ( Fig. 3a ).
  • An advantage of this structural design is especially that it can be dispensed with the use of an additional camshaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Hydraulic Motors (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP10015706.4A 2010-02-05 2010-12-16 Procédé de fonctionnement d'un piston à expansion d'un moteur à vapeur Active EP2354475B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT0016010A AT509394B1 (de) 2010-02-05 2010-02-05 Verfahren zum betrieb eines kolbenexpanders eines dampfmotors

Publications (3)

Publication Number Publication Date
EP2354475A2 true EP2354475A2 (fr) 2011-08-10
EP2354475A3 EP2354475A3 (fr) 2017-11-15
EP2354475B1 EP2354475B1 (fr) 2023-02-01

Family

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Application Number Title Priority Date Filing Date
EP10015706.4A Active EP2354475B1 (fr) 2010-02-05 2010-12-16 Procédé de fonctionnement d'un piston à expansion d'un moteur à vapeur

Country Status (7)

Country Link
US (1) US9038388B2 (fr)
EP (1) EP2354475B1 (fr)
CN (1) CN102146808B (fr)
AT (1) AT509394B1 (fr)
BR (1) BRPI1100214B1 (fr)
MX (1) MX2011001102A (fr)
RU (1) RU2466278C2 (fr)

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AT509394B1 (de) * 2010-02-05 2012-01-15 Man Nutzfahrzeuge Oesterreich Verfahren zum betrieb eines kolbenexpanders eines dampfmotors
CN103122773B (zh) * 2011-11-18 2015-03-11 广西玉柴机器股份有限公司 一种蒸汽马达
ITMI20120497A1 (it) * 2012-03-28 2013-09-29 Roberto Rossetti Motore a vapore con valvole di ammissione e scarico dotate di controllo elettromagnetico.
US10475980B2 (en) * 2012-03-29 2019-11-12 Lenr Cars Sa Thermoelectric vehicle system
CN103423443A (zh) * 2012-05-22 2013-12-04 广西玉柴机器股份有限公司 蒸汽马达活塞
CN103422892B (zh) * 2012-05-25 2016-03-30 周登荣 用于气动汽车的空气分配控制器
CN103422893B (zh) * 2012-05-25 2015-07-08 周登荣 用于气动汽车的空气动力发动机总成
CN104329137B (zh) * 2014-10-20 2017-01-25 广西玉柴机器股份有限公司 蒸汽马达的配气机构
CN104806297A (zh) * 2015-03-11 2015-07-29 郭富强 一种余热利用的方法
JP7225196B2 (ja) * 2017-07-10 2023-02-20 ブルクハルト コンプレッション アーゲー 往復動ピストンマシンを用いて気体を膨張させるための方法およびデバイス
CN109944640A (zh) * 2019-04-30 2019-06-28 天津大学 一种活塞式膨胀机的进排气电磁控制系统

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0900945A1 (fr) 1997-09-05 1999-03-10 Emil Jäger GmbH & Co. KG Accouplement d'arbres
DE102006043139A1 (de) 2006-09-14 2008-03-27 Man Nutzfahrzeuge Ag Vorrichtung zur Gewinnung von mechanischer oder elektrischer Energie aus der Abwärme eines Verbrennungsmotors eines Kraftfahrzeugs

Also Published As

Publication number Publication date
AT509394A1 (de) 2011-08-15
RU2011104049A (ru) 2012-08-10
US20110192162A1 (en) 2011-08-11
MX2011001102A (es) 2011-08-31
US9038388B2 (en) 2015-05-26
BRPI1100214B1 (pt) 2020-08-25
RU2466278C2 (ru) 2012-11-10
CN102146808B (zh) 2017-04-12
EP2354475A3 (fr) 2017-11-15
EP2354475B1 (fr) 2023-02-01
AT509394B1 (de) 2012-01-15
BRPI1100214A2 (pt) 2012-07-24
CN102146808A (zh) 2011-08-10

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