EP2354475B1 - Verfahren zum Betrieb eines Kolbenexpanders eines Dampfmotors - Google Patents

Verfahren zum Betrieb eines Kolbenexpanders eines Dampfmotors Download PDF

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Publication number
EP2354475B1
EP2354475B1 EP10015706.4A EP10015706A EP2354475B1 EP 2354475 B1 EP2354475 B1 EP 2354475B1 EP 10015706 A EP10015706 A EP 10015706A EP 2354475 B1 EP2354475 B1 EP 2354475B1
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EP
European Patent Office
Prior art keywords
steam
piston
dead centre
bottom dead
outlet opening
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
EP10015706.4A
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German (de)
English (en)
French (fr)
Other versions
EP2354475A3 (de
EP2354475A2 (de
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
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MAN Truck and Bus SE
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Publication date
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Publication of EP2354475A2 publication Critical patent/EP2354475A2/de
Publication of EP2354475A3 publication Critical patent/EP2354475A3/de
Application granted granted Critical
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    • 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
    • F01K7/00—Steam 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • 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
    • F01B17/00—Reciprocating-piston machines or engines characterised by use of uniflow principle
    • F01B17/02—Engines
    • F01B17/04—Steam engines
    • 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
    • F01K7/00—Steam 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
    • F01K7/34—Steam 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
    • F01K7/36—Steam 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
    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants 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
    • F01K23/06—Plants 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
    • F01K23/065—Plants 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 from a steam supply is fed through an inlet valve into a cylinder chamber, the live steam introduced into the cylinder chamber is expanded in the power stroke due to a movement of a piston from top to bottom dead center, and the expanded steam is released Reaching the bottom dead center is directed from a closable outlet into a vapor discharge.
  • waste heat occurring in the area of the internal combustion engine and/or in the exhaust gas discharge is at least partially transferred to a secondary heat circuit.
  • a heat transfer fluid is circulated in the secondary heat circuit and is usually at least partially evaporated in an evaporator, the vapor is expanded in an expansion unit, for example in a piston expander, and finally liquefied again in a condenser.
  • the mechanical work generated by the expansion unit is supplied to the drive system, in particular a vehicle drive system, as additional work. It is also conceivable to use the mechanical work gained by using waste heat to drive other components, such as a fan or a compressor, or to generate electrical energy.
  • a heat recovery system for an internal combustion engine is known.
  • the vehicle is provided with additional drive energy from the waste heat from the internal combustion engine and/or the exhaust system.
  • the working medium of the secondary heat cycle is pumped into a condenser, in which it is liquefied with the release of heat, so that the corresponding steam cycle process is closed.
  • a piston of a reciprocating piston expander in which an outer diameter of the piston neck is smaller than an outer diameter of the piston head and/or the piston skirt and at the same time the length of the piston neck almost corresponds to the stroke of the piston when installed.
  • the steam piston expanders known from the prior art are usually operated in the two-stroke process.
  • the live steam is fed into a cylinder of the expander unit via an inlet valve, and in the following power stroke, the steam is expanded while releasing work.
  • the exhaust valve is opened at bottom dead center and the expanded vapor is pushed out of the cylinder during the exhaust stroke by moving the piston from bottom to top dead center.
  • the exhaust valve closes and the corresponding cycle process begins again.
  • the compression ratio must be designed in such a way that the working medium is expanded to a suitable level in the power cycle.
  • the compression ratio is too low, when the exhaust valve opens, the working medium will have an overpressure compared to the back pressure in the exhaust line, which has a negative effect due to the potential possibility of achieving greater relaxation affects the efficiency of the cycle.
  • the compression ratio is designed too high, the working medium is expanded to a pressure below the back pressure in the outlet line, which makes it more difficult to expel the expanded vapor and in turn has a negative effect on the efficiency of the cycle process.
  • the U.S. 2009/0056331 A1 discloses a highly efficient integrated heat engine consisting of a double compound cylinder structure, where the first cylinder is the primary combustion and/or expansion cylinder and the second cylinder is the secondary combustion and/or expansion cylinder. Power strokes driven by expansions of various working fluids such as air-fuel combustion products, steam, and compressed air are integrated into an engine block. There is, among other things, an exhaust air duct in the lower area of the cylinder.
  • the U.S. 1,227,836 discloses a single acting steam engine.
  • the connection between the cylinder and the condenser can be drilled wholly or partially perpendicular to the cylinder axis immediately above the piston in its lowest position.
  • the DE 198 47 742 C1 discloses a steam engine with a device for generating steam and a piston-cylinder unit for generating torque with the help of the steam. Only in the area of bottom dead center is an exhaust valve opened and the cooled vapor expelled.
  • the invention is based on the object of specifying a method for operating a steam piston expander unit which can be operated with a comparatively high level of efficiency.
  • the method to be specified is intended in particular to reduce the amount of live steam required to fill the piston without the efficiency of the cycle process being significantly reduced as a result.
  • According to the invention is a method for operating a piston expander, in which live steam from a steam supply is conducted through an inlet valve into a cylinder chamber, the live steam introduced into the cylinder chamber is expanded in the power stroke due to a movement of a piston from top to bottom dead center, and the expanded steam is at least partially expanded is conducted from a closable outlet opening into a vapor discharge, has been developed in such a way that the outlet opening is opened when or after reaching bottom dead center and then closed before the piston reaches top dead center in the exhaust stroke.
  • the outlet opening is closed in the exhaust stroke in a range of a crankshaft angle of 70° to 100° after bottom dead center.
  • the amount of live steam per cycle of the work process can be reduced 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 efficiency.
  • the method according to the invention makes use of a second option for reducing the amount of live steam per cycle.
  • the outlet opening is not open during the entire exhaust stroke, i.e. during the time in which the piston moves from bottom to top dead center, but the outlet opening is closed well before the piston reaches top dead center. Through this measure ensures that a significant amount of already expanded steam remains in the cylinder and is not discharged into the steam outlet.
  • This residual steam remaining in the cylinder is advantageously compressed in the exhaust stroke by the movement of the piston to top dead center.
  • the pressure is already significantly higher than the back pressure that otherwise prevails in the cylinder without compression of the residual steam.
  • the live-steam pressure is achieved by further compression of the already pre-stressed residual steam within the dead volume of the cylinder, with the state of the mixed steam being adjusted after injection of the live steam as a function of the states of the precompressed residual steam and the live steam.
  • This mixed vapor pressure can be achieved independently of the selection of a suitable compression ratio.
  • the method according to the invention for operating a piston expander advantageously achieves 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 the residual steam is initially pre-stressed and only then is it compressed to the live-steam pressure level by injecting live steam.
  • the intake valve is preferably opened as soon as the piston reaches 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 supplying the live steam into the cylinder chamber, in particular the dead volume of the cylinder chamber, the mixed steam pressure of which corresponds at least approximately to the live steam pressure.
  • the comparatively high mixed-steam pressure The live-steam pressure is achieved by further compression of the already pre-stressed residual steam within the dead volume of the cylinder, with the condition of the mixed-steam being adjusted after injection of the live steam as a function of the states of the pre-compressed residual steam and the live steam.
  • Mixing the live steam with the pressurized residual steam thus produces a mixed steam with an enthalpy that is higher than the usual ratios. This measure increases the efficiency of the cyclic process in a relatively simple manner.
  • figure 1 shows the lift of a valve in an outlet port of the cylinder of a vapor expander.
  • the function curves a, b, c of the valve lift over the crankshaft angle are given in relation to three different valve controls. Reaching the bottom dead center and the top dead center is indicated by a vertical line at approximately 182° or 361° crankshaft angle.
  • the continuous thin function curve a and the dotted curve b each show the lift 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. 1 An embodiment not according to the invention is given in figure 1 illustrated by the function curve d.
  • a special design of the outlet opening is used.
  • slots are provided in the cylinder wall, which create a connection between the cylinder interior and a vapor discharge as soon as the piston edge sweeps over the slot in the expansion stroke.
  • the at least one slot is closed again as soon as the piston edge has once again passed over the slot due to the opposite movement of the piston.
  • the at least one slot is opened at a crankshaft angle of approximately 20° before bottom dead center is reached and closed again at a crankshaft angle of approximately 20° after bottom dead center.
  • FIG 3 the structure of a steam expander is shown schematically. Since a corresponding vapor expander is usually operated in the two-stroke process, the crankshaft and camshaft speed are the same, so that the intake and exhaust valves are actuated by means of a corresponding crank web provided on the crankshaft. Such a design offers the advantage that neither an additional camshaft nor a corresponding drive is required. Of course, it is fundamentally conceivable to provide an additional camshaft in addition to the crankshaft, even in the case of a steam piston expander operated in the two-stroke process.
  • the invention relates to a method for suitably actuating inlet and outlet valves of a piston machine for vapor expansion.
  • FIG 3 schematically shown three technical options with which the actuation of the valves 4, 5 can be realized.
  • the method according to the invention which mainly relates to the point in time at which the valves 4, 5 are opened and closed, can be carried out with each of the three possible valve actuations.
  • FIG 3 The components of a steam piston expander shown that are essential for the implementation of the method according to the invention are the crankshaft 1, the camshaft 2 with the molded cams 3, the inlet valve 4, the outlet valve 5, the position sensor 6 and an actuation unit 7.
  • the valves are actuated via the crankshaft 1 ( Figure 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 primarily characterized by the fact that there is no mechanical connection between the crankshaft 1 and the intake or exhaust valve, a position sensor 6 on the crankshaft and a control unit 10 are also provided.
  • the instantaneous position of the crankshaft 1 is determined with the aid of the position sensor 6 and a corresponding value is sent to the control unit as an input variable.
  • This value is processed in the control unit 10 and an output variable is generated, on the basis of which the actuation of the inlet or outlet valve 4, 5 by the actuation unit 7 takes place.
  • the mixed steam forming in the cylinder has a pressure which at least almost corresponds to the live steam pressure in the steam supply 8 .
  • the live-steam pressure is achieved by further compression of the already pre-stressed residual steam within the dead volume of the cylinder, with the state of the mixed steam being adjusted after injection of the live steam as a function of the states of the precompressed residual steam and the live steam.
  • the outlet opening 5 is closed. If the outlet opening does not have an outlet valve but rather the already described non-inventive slot, which is released at about 20° before bottom dead center is reached, this is closed again due to the movement of the piston in the exhaust stroke and the resulting sweeping over of the piston edge .
  • the outlet opening 5 or the outlet slot 11 By closing the outlet opening 5 or the outlet slot 11 the residual steam is compressed in such a way that the residual steam pressure is only slightly lower than the live steam pressure when the top dead center is reached.
  • the small difference in pressure between residual and live steam offers the main advantage that when the live steam is injected into the dead volume of the cylinder, vapors that are exergetically very similar are mixed with one another.
  • the components of the cylinder in particular the intake valve, are subjected to comparatively little stress due to the compression of the residual steam and the associated small difference between the residual steam pressure and the live steam pressure.
  • no valve is required in addition to the inlet valve 4 .
  • 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 outlet valve is opened as soon as the piston has reached bottom dead center and is closed at a crankshaft angle of approximately 70° to 100° after bottom dead center. After the outlet valve 5 has been closed, the residual vapor remaining in the cylinder is again compressed by the movement of the piston, so that the advantages already mentioned are achieved in this way.
  • valves can be suitably closed with the aid of a crank web ( Figure 3a ) can be pressed.
  • the main advantage of this design is that there is no need for 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 Verfahren zum Betrieb eines Kolbenexpanders eines Dampfmotors Active EP2354475B1 (de)

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 EP2354475A2 (de) 2011-08-10
EP2354475A3 EP2354475A3 (de) 2017-11-15
EP2354475B1 true EP2354475B1 (de) 2023-02-01

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Country Status (7)

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

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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
CN104763472B (zh) * 2012-05-25 2017-05-10 周登荣 用于气动汽车的多缸空气动力发动机总成
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
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
CN110892135B (zh) * 2017-07-10 2022-04-05 伯克哈特压缩机股份公司 利用往复活塞式机器进行气体膨胀的方法和装置
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Also Published As

Publication number Publication date
CN102146808B (zh) 2017-04-12
BRPI1100214B1 (pt) 2020-08-25
US9038388B2 (en) 2015-05-26
BRPI1100214A2 (pt) 2012-07-24
RU2466278C2 (ru) 2012-11-10
AT509394A1 (de) 2011-08-15
MX2011001102A (es) 2011-08-31
AT509394B1 (de) 2012-01-15
EP2354475A3 (de) 2017-11-15
US20110192162A1 (en) 2011-08-11
EP2354475A2 (de) 2011-08-10
CN102146808A (zh) 2011-08-10
RU2011104049A (ru) 2012-08-10

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