CN101415908B - Large-sized turbo-charging diesel motor with energy recovery apparatus - Google Patents
Large-sized turbo-charging diesel motor with energy recovery apparatus Download PDFInfo
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- CN101415908B CN101415908B CN2006800541824A CN200680054182A CN101415908B CN 101415908 B CN101415908 B CN 101415908B CN 2006800541824 A CN2006800541824 A CN 2006800541824A CN 200680054182 A CN200680054182 A CN 200680054182A CN 101415908 B CN101415908 B CN 101415908B
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
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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
- 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
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
- F02G5/02—Profiting from waste heat of exhaust gases
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
- F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
- F28D7/1669—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having an annular shape; the conduits being assembled around a central distribution tube
- F28D7/1676—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having an annular shape; the conduits being assembled around a central distribution tube with particular pattern of flow of the heat exchange media, e.g. change of flow direction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G2280/00—Output delivery
- F02G2280/20—Rotary generators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/30—Technologies for a more efficient combustion or heat usage
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Combustion & Propulsion (AREA)
- Chemical & Material Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Geometry (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Supercharger (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
- Exhaust-Gas Circulating Devices (AREA)
Abstract
A large turbocharged diesel engine provided with exhaust gas boilers and a power turbine for recovering energy in the exhaust gases. One of the boilers can be an integral part of the exhaust gases receivers. A part of the exhaust gas flow upstreams of the turbocharger turbine is branched off to the power turbine. The engine comprises a preheating boiler at the low-pressure side of the turbocharger of turbine whilst a superheating boiler is arranged at the high pressure side of the turbocharger turbine. The engine can be operated with highly humidified scavenging air to thereby increase the amount of energy in the exhaust gases that can be recovered. The engine can also be operated as a heat pump, i.e. the exhaust gas leaving the engine to have a temperature below ambient.
Description
Technical field
The present invention relates to a kind of large-sized turbo-charging diesel motor with one or more exhaust heating boiler, be particularly related to a kind of large-sized turbo-charging diesel motor that is provided with power turbine, the exhaust gas drive that this power turbine is distributed by the upstream from the turbine of turbosupercharger.
Background technique
EP0434419 has disclosed a kind of large two-stroke turbo-charging diesel motor, and wherein the heat energy in the exhaust is recycled by the boiler that is positioned at the turbosupercharger low voltage side and the combination that is positioned at the on high-tension side boiler of turbosupercharger.When low engine load, by a certain proportion of exhaust is directly imported the turbosupercharger of walking around the upstream boiler reduced before exhaust is imported turbosupercharger exhaust in the recovery of heat energy.But, by between the turbine of exhaust receiver and turbosupercharger, placing a boiler, cause overall structure to become relatively huge and complicated.In addition, the increase of the flow-path-length between exhaust valve and the turbosupercharger can reduce the response of turbosupercharger to accelerating.In addition, this motor only reclaims heat energy, and the energy of form that can not the transformation of energy one-tenth that reclaim is more useful, such as rotation energy or electric energy.
Summary of the invention
Under this background, the purpose of this invention is to provide the turbo-charging diesel motor of type that a kind of front is carried, the compacter and easy structure of this turbo-charging diesel motor.This purpose realizes by the turbo-charging diesel motor that a kind of described type is provided that according to claim 1 this motor comprises: a plurality of cylinders, and each cylinder is connected to exhaust receiver by corresponding manifold; Upstream exhaust pipe, this upstream exhaust pipe is used for exhaust is guided to from described exhaust receiver the entrance of the turbine of turbosupercharger; Downstream row tracheae, this downstream exhaust gas pipe are used for exhaust is guided to atmosphere from the outlet of the turbine of described turbosupercharger; Be used for reclaiming from exhaust one or more exhaust heating boilers or the heat exchanger of heat energy, wherein, at least one boiler in described boiler or the heat exchanger or heat exchanger be arranged in the described exhaust receiver.
By one in the described boiler is placed in the exhaust receiver, effectively make the compact area of parts at the large-sized turbo-charging diesel motor top of system no longer need any space.This measure has produced more spaces around motor, has reduced simultaneously the stringing amount.In addition, saved the housing of boiler, because the housing of exhaust receiver has two functions now: the first is provided for receiving and collects from the cavity of the exhaust of each cylinder; It two provides be used to the cavity that holds boiler.Another advantage is that to allow pressure drop through boiler be three times in the conventional construction and can not cause the decline of engine performance.The pressure drop that increases then makes gas velocity increase, thereby so that heat exchange area significantly reduces (every other parameter too), thereby cause boiler much smaller.
Described large-sized turbo-charging diesel motor also can comprise the preheating/evaporation boiler that is positioned at the turbosupercharger low voltage side.The steam superheating that places this moment the boiler in the exhaust receiver to be used to make the boiler of turbosupercharger low voltage side to produce.So, the quality improvement of steam, particularly consider and in steam turbine, use superheated vapor.
Large-sized turbo-charging diesel motor can also comprise the steam-powered steam turbine that is produced by single boiler or a plurality of boiler.So the energy that reclaims from exhaust is converted into more useful form of energy.Power turbine can drive generator and will rotate and can convert electric energy to.
Exhaust receiver can hold a plurality of boilers, perhaps multistage single boiler.So the energy in the exhaust can more effectively be delivered to steam.
Described a plurality of boiler can form the multistage steam superheated vapor that comprises preheating/evaporation and overheated/evaporation boiler and produce system.
Another object of the present invention provides the large-sized turbo-charging diesel motor that a kind of improved exhaust energy reclaims.According to claim 9, by providing a kind of large-sized turbo-charging diesel motor to realize, this large-sized turbo-charging diesel motor comprises this purpose: turbosupercharger, this turbosupercharger have the exhaust gas drive turbine that is connected to booster air compressor; Be positioned at the on high-tension side first exhaust heating boiler of turbosupercharger; Be positioned at the second exhaust heating boiler of the low voltage side of turbosupercharger; And power turbine, this power turbine is by a part of exhaust gas drive of shunting out from the high pressure side of turbosupercharger.
Be positioned at the on high-tension side boiler of turbocharger turbine and shunt a part of exhaust from the high pressure side of turbocharger turbine by use, quantitatively improved the energy total amount that can from exhaust, reclaim, especially change under the larger condition in operating mode, because with produce more rotation by power turbine and can compare, this system is suitable for producing more heat energy by boiler.So this system also can be as the total fuel efficiency that helps to improve in the propulsion system of ocean boat in the stationary power generation factory.
On the one hand, the first boiler can be by all exhaust stream mistakes, and the discharge portion that is used for simultaneously power turbine is shunted in the downstream of this first exhaust heating boiler.Allow to like this total amount maximization of the energy that reclaims.
On the other hand, the splitter section that the first boiler can only be deflated flows through, and this does not affect the thermal equilibrium of turbosupercharger, has guaranteed by this way the responsiveness of accelerating period turbocharger turbine.
Leave the exhaust of power turbine and can again be introduced main exhaust stream in the low voltage side of turbosupercharger.Can guarantee that so all exhausts for example obtain reprocessing in selective catalytic reactor and/or silencing apparatus.
Preferably, power turbine drives generator.So the energy that is recovered can be used to produce a kind of energy of very attractive flexible form.
But another object of the present invention provide a kind of flexible operating and can be from exhaust the large two-stroke diesel engine of recovered energy well.
This purpose is according to claim 23 by providing a kind of large supercharged two-stroke diesel engine to realize, this large supercharged two-stroke diesel engine comprises: the exhaust gas drive turbine that drives generator, drive the booster air compressor that motor drives by electricity, and heat exchanger, this heat exchanger is positioned at the high pressure side of described turbine, is used for extracting heat energy from exhaust.
Owing to do not connect the axle of turbine and compressor, so the working condition of motor can be controlled with larger degrees of freedom, the simultaneously use of the on high-tension side heat exchanger of turbine has been guaranteed to reclaim well the energy that comprises in the exhaust.
Preferably, this motor does not comprise turbosupercharger.
Heat exchanger can be used for producing steam.
Described motor can also comprise the part of accumulating the electric energy that generator produces, and the electric energy that stores is offered the device that electricity drives motor.
Preferably, described motor comprises the assigned unit of the control electric energy that produces of generator and stored electric energy.
Described motor can also comprise the steam turbine that is driven by the steam that produces under helping at the heat from heat exchanger.
Preferably, described heat exchanger is configured to make the temperature of the exhaust of leaving described heat exchanger to be reduced to make the degree of temperature below ambient temperature of the exhaust of leaving the turbine that is positioned at described heat exchanger downstream.
Another object of the present invention provides a kind ofly can use combustion engine in cogeneration power plant with very high fuel efficiency.
This purpose is according to claim 23 by providing the boosting explosive formula motor of a kind of use in cogeneration power plant to realize, described motor comprises: the gas handling system that is used for the air under the absorbing environmental pressure and temperature, this gas handling system comprises compressor, and this compressor is used for the pressurized air of pressure more than external pressure is transported to the cylinder of described internal combustion engine; Turbine by exhaust gas drive; And heat exchanger, this heat exchanger is positioned at the high pressure side of turbine, is used for extracting heat from exhaust, and described heat exchanger and turbine are configured to obtain to be lower than the turbine low voltage side delivery temperature of ambient temperature.
By in the on high-tension side exhaust heating boiler of turbine, extracting a large amount of energy, and the turbine that uses effective turbine area less, the expansion of relatively cold exhaust in turbine can cause significantly being lower than ambient temperature in the temperature of the exhaust of turbine low voltage side.So self changes heat pump into combustion engine, from environment, extract low-grade energy and convert it into high-grade energy.The total fuel efficiency apparently higher than 100% be can obtain, good Economy and environment friendly shown thus.Delivery temperature can be hanged down to extremely-40 ℃.Leave in the exhaust of chimney of the power station that uses this motor and may contain snowy or similar ice crystal.
Preferably the large capacity by be used for increasing the heat exchanger that falls through the temperature of the exhaust of described heat exchanger and being used for increases the delivery temperature that little effective turbine area that exhaust falls in the temperature of described turbine inflation process obtains to be lower than ambient temperature.
Preferably, leave the temperature of exhaust of cylinder between 400 ℃ to 500 ℃, leave the temperature of exhaust of exhaust heating boiler below 110 ℃, and the pressure of exhaust that leaves this boiler is more than 2bar.
Turbine and compression function couple together to form turbosupercharger by axle.At this moment, described motor can also comprise power turbine, and this power turbine is by the exhaust gas drive of the turbocharger turbine that is diverted to described boiler downstream from exhaust stream.
Described motor can comprise steam turbine, the steam driven that the heat that this steam turbine is extracted from exhaust by described heat exchanger utilization produces.
Preferably, described motor can also comprise the on high-tension side pressurized air humidifying unit that is positioned at described compressor.
The pressure that leaves the exhaust of turbine preferably equals or a little more than external pressure.
Leave the temperature of exhaust of turbine preferably between-5 ℃ to-40 ℃.
At least when described engine operation during in maximum continuous rating, the temperature of leaving the exhaust of turbine is lower than ambient temperature.
At least when described engine operation during in maximum continuous rating, leave the temperature of exhaust of turbine in-5 ℃ to-40 ℃ scopes.
A kind of supercharged combustion engine is provided in accordance with a further aspect of the present invention, it is air-breathing under external pressure and temperature that this supercharged combustion engine comprises that a gas handling system is used for, described gas handling system comprises: compressor, and this compressor is used for the pressurized air of pressure more than external pressure is transported to the cylinder of described internal combustion engine; The first turbine by the given effective turbine area of having of exhaust gas drive; The second turbine by the given effective turbine area of having of exhaust gas drive; Heat exchanger, this heat exchanger is positioned at the high pressure side of turbine, is used for extracting heat from exhaust; And be used for optionally using two turbines or two any turbines of turbine so that the device that motor moves with different turbine low voltage side delivery temperatures.
According to a further aspect in the invention, provide a kind of supercharged combustion engine, this supercharged combustion engine comprises: compressor, and this compressor is used for the pressurized air of pressure more than external pressure is transported to the cylinder of described internal combustion engine; Turbine by the given effective turbine area of having of exhaust gas drive; And heat exchanger, this heat exchanger is positioned at the high pressure side of turbine, is used for extracting heat from exhaust.
In accordance with a further aspect of the present invention, a kind of method that operates supercharged combustion engine is provided, described supercharged combustion engine comprises: the system that enters that is used for the air under the absorbing environmental pressure and temperature, this gas handling system comprises compressor, and this compressor is used for the pressurized air of pressure more than external pressure is transported to the cylinder of described internal combustion engine; The first turbine by the given effective turbine area of having of exhaust gas drive; The second turbine by the given effective turbine area of having of exhaust gas drive; And heat exchanger, this heat exchanger is positioned at the high pressure side of turbine, is used for extracting heat from exhaust, and described method comprises optionally uses described turbine to obtain the step of different turbine low voltage side delivery temperatures.
Other purposes, feature, advantage and characteristic according to supercharged combustion engine of the present invention will become apparent in the following detailed description.
Description of drawings
Below this specification in the detailed description, the exemplary embodiment shown in reference to the accompanying drawings is described in more details the present invention, in the accompanying drawings:
Fig. 1 is the partial side view of the large-sized turbo-charging diesel motor of first embodiment of the invention,
Fig. 2 is the longitudinal sectional view of motor among Fig. 1,
Fig. 3 schematically shows the large-sized turbo-charging diesel motor with heat recovery equipment according to second embodiment of the invention,
Fig. 4 schematically shows the large-sized turbo-charging diesel motor with heat recovery equipment according to third embodiment of the invention,
Fig. 4 a is the chart that the Operational Limits of motor among Fig. 4 is shown,
Fig. 5 schematically shows the large-sized turbo-charging diesel motor with heat recovery equipment according to fourth embodiment of the invention,
Fig. 5 a is the chart that the Operational Limits of motor among Fig. 5 is shown,
Fig. 6 shows an alternative embodiment of the invention, and wherein said motor is used as heat pump,
Fig. 7 shows another embodiment of the present invention, does not wherein use turbosupercharger, and is the most alternative, and this embodiment is provided with and is electrically connected turbine and the blower of getting up, and
Fig. 8 is another embodiment who has used exhaust gas recirculatioon of the present invention.
Embodiment
In the following detailed description, will be described by the large-sized turbo-charging diesel motor of preferred embodiment to large two-stroke diesel engine form according to the present invention.
The structure of the large two-stroke diesel engine of large-sized turbo-charging diesel motor such as crosshead and operation are known, therefore need not to be described further in this article.Detailed description about blower operations and vent systems hereinafter is provided.
Fig. 1 shows the first embodiment according to the upper area of large two-stroke diesel engine 1 of the present invention.This motor is provided with each other side by side a plurality of cylinders of arranging in upright arrangement.Each cylinder is equipped with the exhaust valve (not shown) that is associated with cylinder head.The exhaust passage can be opened or closed by exhaust valve.Manifold is connected to exhaust receiver 3 with corresponding exhaust passage.Exhaust receiver 3 is arranged abreast with bank of cylinder.Manifold 40 openings are in exhaust receiver 3, and exhaust duct leads to the turbine of turbosupercharger from exhaust receiver.In number of cylinders very many (for example 10 s' or more) motor, exhaust receiver vertically can be divided into two or more part (not shown).
In this embodiment, exhaust receiver 3 has cylindrical shell 42, and as shown in Figure 2, cylindrical shell 42 has detachable lid 44 in its end.Cylindrical shell 42 comprises heat exchanger 23, and exhaust can be flow through this heat exchanger to produce superheated vapor.Therefore heat exchanger 23 is as boiler.Cylindrical shell 42 also comprises collecting pipe 46, and manifold 40 is discharged into exhaust in the collecting pipe 46.
As shown in Figure 2, the cylindrical shell 42 of exhaust receiver is divided into juxtaposition at two heat exchanger section 50a and 50b of 52 both sides, central outlets chamber and collects pipeline section 46a and 46b, and exhaust is left via described exhaust duct from central outlet plenum 52.So the structure of exhaust receiver 3 is about central radial plane symmetry.
Two sections 50a, 50b of heat exchanger apparatus are made of some known heat-exchanging elements that are disposed in order, and these heat-exchanging elements are isolated thing 49 separately.Each section 50a, 50b comprise respectively two heat exchanger component 57a, 58a and 57b, 58b, each heat exchanger component includes a large amount of pipe that extends along airflow direction, described airflow direction represents with the arrow that is depicted as continuous lines, is parallel to the longitudinal axis of cylindrical shell.The flow direction among each heat exchanger section 50a, 50b is opposite and toward each other.
The cross section profile of heat exchanger component 57a, 58a, 57b and the 58b of arranged off-centre is the annular fragment in the interior week of abut cylinder shape housing 42.This annular fragment can be divided into some subsegments to strengthen the simplification (not shown) of assembling.
The cylindrical shell 42 of exhaust receiver 3 is provided with partition wall 63, partition wall 63 separates heat exchanger component and exhaust receiver 3 remaining inner section, thereby the inner section of exhaust receiver is separated into passage and the collection exhaust of holding heat exchanger component and the passage that exhaust court is had the described passage guiding of heat exchanger component 57a, 58a, 57b and 58b.
An above-mentioned rear passage (manifold 40 is the passage of opening therein) is along the direction of arrow directing exhaust gas shown in the interrupt line.
Heating element can be reduced in the passage that holds heating element.Vertically outside heating element separates by the heating element of spacer 49 with inside.Whole assembly is held in place by lockplate 66.
Therefore, the housing 42 of exhaust receiver 3 has comprised simultaneously the exhaust reception cavity and reclaimed the boiler of heat energy from exhaust.By in exhaust receiver, comprising described boiler, saved the housing of the needed space of exhaust-gas boiler and exhaust-gas boiler.
Fig. 3 shows the second embodiment with the crosshead type large two-stroke turbo-charging diesel motor 1 of air inlet system and exhaust system.Motor 1 has pressurized air receiver 2 and exhaust receiver 3.Exhaust receiver 3 can be in the type described in the first embodiment, but this not necessarily.This motor is provided with unshowned exhaust valve (each cylinder has one or more).Motor 1 can for example be used as the master motor of ocean boat or be used for driving in the power station stationary engine of generator.Total output of this motor can in 5,000 to 110,000kW scope for example, for example be the four-cycle diesel engine of 1,000kW but the present invention also can be used for output.
Pressurized air is sent to the scavenging port (not shown) of each cylinder from pressurized air receiver 2.When exhaust valve 4 was opened, exhaust flowed into exhaust receiver 3 through manifold 40, then arrived forward the turbine 6 of turbosupercharger through downtake pipe 5 from exhaust receiver 3, and last exhaust is left turbine 6 through second exhaust pipe 7.Turbine 6 drives the compressor 9 that is supplied air via suction port 10 by axle 8.Compressor 9 is transported to the pressurizing air tracheae 11 that leads to pressurized air receiver 2 with the pressurized air of pressurization.
Air inlet in the air duct 11 is through intercooler 12, is cooled to temperature near 36 ℃ near 200 ℃ scavenging when will leave compressor 9.
Cooled scavenging arrives scavenging receiver 2 through the auxiliary blower 16 of scavenging stream is pressurizeed (usually only under low-load or localised load condition), and this auxiliary compressor is driven by electric notor 17.When high load, the amount of the scavenging of carrying by turbocharger compressor 9 is enough to make the motor operation, and auxiliary blower 16 is shut down.Walk around auxiliary blower 16 by pipeline 15 this moment.
The first boiler 23 that preferably is tubular type for example or finned heat exchanger form is disposed in the downtake pipe 5, and namely the upstream of turbine 6 produces steam to utilize the heat energy in the exhaust.About 455 ℃ of temperature when exhaust enters exhaust receiver 3, and the temperature of the first boiler 23 ingress is only hanged down a bit a little.As described in front reference the first embodiment, the first boiler 23 can exhaust receiver 3 part of the whole.
Outlet pipe is in boiler 23 downstream branch, and the major part of exhaust continues to flow towards turbine 6 by outlet pipe 5, and the fraction exhaust is flowed towards power turbine 31 by pipeline 30.Additional power turbine 31 drives generator 32.
Therefore energy superfluous in the exhaust stream is converted into electric energy, namely has the energy of high radiation instinct.Can regulate the air displacement that is diverted to power turbine 31 by the changeable flow regulator (not shown) in the pipeline 30.The exhaust of leaving power turbine 31 is directed to second exhaust pipe 7 and is again introduced there main exhaust stream.
The second boiler 20 utilizes the heat in the exhaust stream to produce steam under pressure.In this stage, delivery temperature is lower than the temperature when just leaving cylinder, and the temperature of turbocharger turbine 6 outlets is in 250 ℃ to 300 ℃ scope usually.
The steam that pipeline 22 produces the second boiler 20 is directed to the entrance of the first boiler.The first boiler is about 450 ℃ exhaust heating by temperature, and this exhaust is that the water/steam that enters the first boiler 23 is evaporated/overheated very effective medium.
Superheated vapor is drawn towards the steam turbine 37 that the transformation of energy in the steam is become rotating mechanical energy by pipeline 34.Steam turbine 37 drives generator 35 to produce electric energy, and this can be used on the boat of ocean, for example, is used for perhaps being used for increasing electric power for the stationary power generation station to the cooling equipment power supply.Although not shown in this embodiment or any other embodiment, should be appreciated that described boiler and steam turbine are parts that comprises the vapor recycle of condenser, cooler and other known equipment in steam power field.
Has MAN B﹠amp; W
The example of the second embodiment's of 12K98ME motor Operational Limits is provided in the following table 1.This is a kind of motor that to have 12 cylinder diameters be the cylinder of 98cm.The compressor that should be noted that turbosupercharger adds that possible auxiliary blower needs the input power of about 2500kW.That this power extracts from exhaust and/or provide by other auxiliary blowers.
Based on energy conservation, can determine the optimum value of the power that from whole system, extracts.This finally depends on the circumstances, such as the use condition of boiler type, steam turbine type and large two-stroke diesel engine.The main concern provides the rotation energy in the boat of ocean, then pays close attention to equally the production (when being used for district heating) of heat energy and the production of electric power in the stationary power generation station.
Utilize the power of the variable size that the first boiler 23 and power turbine 31 obtain from exhaust, this system can move under various operating points.
The power that the power that extracts from the first boiler 23 that is arranged in turbocharger turbine 6 upstreams will make turbocharger turbine 6 and power turbine 31 use reduces, and the power that extracts from the second boiler 20 can not exert an influence to the power of turbosupercharger and power turbine.
In the example of table 1, from the first boiler 23, extracted the power delivery of 10,000kW to steam turbine 37 (for this example, performance number is optional, can select as shown in Figure 3A other value).
Fig. 3 A shows the figure of the result of calculation of the power that extracts the varying number value in the first boiler 23.Use the power that the percentage of engine shaft power is represented various parts among the figure, this explanation the present invention can be used for the motor of various sizes.Can see that on figure when the energy that extracts at the first boiler 23 that is arranged in turbocharger turbine 6 upstreams increased, the energy that extracts in can the driven force turbine just reduced.Can decide best running position according to needed kind of energy (heat energy or rotation energy/electric energy).
If need simultaneously heat energy and rotation energy, for example not only providing electric energy but also provide in the stationary power generation station of heat energy, described best operating point most probable tends to extract maximum energy by the first boiler 23.Even this operating point requirement auxiliary blower 16 under full-load conditions also will be worked.
The main energy that needs at the ocean boat is thrust power, namely drives the rotation energy of propeller cavitation (not shown).The needed heat of whole ship is usually relatively low, and needed electric weight is then according to the ship type and difference, and the required electric weight of bulk carrier is relatively low.
The Container ship that transports cooling or LNG Liquefied natural gas needs a large amount of electric energy.This moment, with 5,000-10, the energy of 000KW was moved by the mode that the first boiler extracts from comprehensive energy efficiency viewpoint of advantage.
Fig. 4 shows the third embodiment of the present invention.Except the type difference of scavenging cooler 12a, this embodiment corresponds essentially to the second embodiment.Described scavenging cooler is the scrubber that injects and evaporate large water gaging.The water that injects is warm water preferably, for example is to utilize the seawater (when motor is installed on the boat of ocean) of waste heat of (water) cooling system (not shown) of motor 1 or river when stationary power generation station (near motor is installed in rivers).Scrubber 12a operation has about 70 ℃ temperature and 100% relative moisture basically so that leave the air of scrubber outlet.The absolute humidity of described scavenging approximately is about five times of scavenging that leave intercooler 12 among the second embodiment.So energy contained in scavenging and the exhaust significantly increases.Therefore have in the exhaust more available energy boiler of feeding 20,23 and power turbine 31 extract.
Has MAN
The example of the 3rd embodiment's of 12K98ME motor Operational Limits is illustrated in the table 1.
In order to produce this scavenging condition, it is about 25 that turbocharger compressor and possible auxiliary blower need, and the input power of 000kW also will realize further injecting about 7, and the water of 5kg/s is at the compressor outlet air evaporation.
This power (25000kW) must extract from exhaust and/or be provided by other auxiliary blower.
In the present embodiment, in the first boiler 23, extract 10,000kW and be transported to steam turbine 37 (to this example, this value is optional, can select other values shown in Fig. 4 A).
Fig. 4 A shows the figure of the result of calculation of the power that extracts the varying number value in the first boiler.Use the power that the percentage of engine shaft power is represented various parts among the figure, this explanation the present invention can be used for the motor of various sizes.Can see that on figure when the increased power that extracts at the first boiler 23 that is arranged in turbocharger turbine 6 upstreams, the power that extracts in can driven force turbine 31 just reduces.In this embodiment, power is not being given in the situation of auxiliary blower 16, can from the first boiler 23, extracted the power that surpasses 25,000kW.In the motor according to the second embodiment, power is not being given in the situation of auxiliary blower 16, can only in the first boiler, extract about 14,000kW.Because it only is to descend very slightly that the fuel efficiency of motor self is subjected to the effect of damp and hot scavenging, so combine according to the overall fuel efficiency of the motor 1 of the exhaust energy reclaiming system of the present invention motor with exhaust energy reclaiming system (for example the second embodiment) apparently higher than routine.Be similar to operating point according to the second embodiment's motor according to the desirable operating point of the 3rd embodiment's motor.
In the 3rd embodiment's a modification, the motor utilization comes work in the low-down exhaust of outlet port temperature.This temperature can be hanged down-40 ℃, this means that the water in the exhaust will experience twice phase transformation: from steam to liquid and from liquid to the solid, the exhaust of for example leaving motor may comprise the ice of snow or similar form.Therefore, described motor is as heat pump, and this is to cause especially concern not only needing mechanical energy but also needing in the application of heat energy, as being used for providing the cogeneration power plant of electric energy and district heating.Obtain described running state by in the first boiler 23, extracting a large amount of energy, in the example of table 1, extracted 72.000kW.In addition, the useful area of turbine 6 is compared with aforementioned exemplary/embodiment and has been reduced approximately 1/3rd, produces-25 ℃ delivery temperature.The result that the turbine useful area reduces is that the energy limited that compressor 9 can be used reduces (when the turbine useful area reduced, (because gas expansion) falls in the temperature of exhaust in turbine to be increased).So volume and the power consumpiton of auxiliary blower have increased.In this embodiment, auxiliary blower 16 all moves under all load conditions, for example also can move under full load situation, even produce all required scavengings because the power that turbine 6 produces when the motor full load can not satisfy compressor 9.
When motor used heavy fuel oil or diesel oil, the exhaust component that are positioned at the dew point downstream adopted corrosion-resistant material to consist of, and they can tackle the acidic deposits (containing sulfuric acid in the condensation product) that the sulfur-bearing in the fuel becomes branch to cause like this.
When motor uses rock gas or other to be substantially free of the fuel of sulphur, just do not need these measures.
Has MAN
In " 3 is cold " hurdle of the table 1 that the example of the Operational Limits of the 3rd embodiment's of 12K98ME motor described modification is provided at.
In this modification of the 3rd embodiment, because the low temperature of the exhaust behind the turbocharger turbine does not have the second boiler in low voltage side.So this system only comprises and is positioned on high-tension side the first boiler 23 of turbine.
In another modification (not shown) of this embodiment, motor is provided with the second turbine, be used for when to the demand of heat energy lower and to rotation can demand to move with higher delivery temperature in turbine high pressure side and low voltage side when higher (be 50 ℃ to 200 ℃ in low voltage side for example, 150 ℃ to 350 ℃ in the high pressure side), the summer operation of cogeneration power plant for example.This system can switch to has large effectively the second turbine of turbine area, to obtain to be lower than the delivery temperature of ambient temperature, perhaps the second turbine also can have the turbine area of less, two in parallel uses of turbine that useful area is less, and each receives a part of exhaust stream.In service in higher exhaust gas temperature, two turbines with less effective turbine area with the turbine of large effectively turbine area or parallel running will be to the enough power of compressor transmission, so that auxiliary blower only need to just start when running on the lower load.The power that extracts in boiler 23 correspondingly reduces, and adapts to the delivery temperature of leaving boiler 23 of the desirable delivery temperature of turbine 6 low voltage sides with acquisition.Perhaps, and use two turbine in contrast, can use a kind ofly to have the single turbine (not shown) of variable effective turbine area to obtain the flexibility of needed effective turbine area.So this second modification can operate under the pattern of paying close attention to heat energy production and very high total energy efficiency, another pattern is then paid close attention to rotation and can be produced, and this system is optimised under this pattern to make it have the maximum efficient that energy is rotated in extraction from fuel.
Fig. 5 shows the fourth embodiment of the present invention.This embodiment corresponds essentially to the second embodiment, and difference is that the first boiler 23 is arranged in from the exhaust stream that outlet pipe 5 branches away.So, only have the splitter section of exhaust to flow through the first boiler 23.Pipeline 30 is guided to power turbine 31 with exhaust from the outlet of the first boiler 23.This embodiment's advantage is that exhaust can flow directly to turbocharger turbine 6 from exhaust receiver 3, this means that motor has better response to the acceleration situation.The outlet of power turbine 31 is connected to 20 entrances of the second boiler or is connected to the end portion of outlet pipe 21 shown in dashed line.The outlet temperature of power turbine 31 is depended in the selection that connects.If the outlet temperature of power turbine 31 is markedly inferior to the outlet temperature of turbocharger turbine 6, so the outlet of power turbine is connected to the end portion of outlet pipe 21.
Has MAN
In " 4 " hurdle of the table 1 that the example of the 4th embodiment's of 12K98ME motor Operational Limits is provided at.
In this example, 20% exhaust shunts to produce power turbine output power (PO towards power turbine
PT) or the auxiliary blower input power.
Can determine the optimum value about the power that from whole system, extracts.This finally depends on the circumstances, such as the use condition of boiler type, steam turbine type and large two-stroke diesel engine.The main concern provides the rotation energy in the boat of ocean, then pays close attention to equally the production (when being used for district heating) of heat energy and the production of electric power in the stationary power generation station.
Available power in the exhaust stream (160kg/s, 455 ℃, 3.35bar (abs.)) can be used in four equipment.
1) the first boiler 23 of turbocharger turbine 6 upstreams;
2) power turbine 31;
3) second boiler 20 in turbocharger turbine 6 downstreams; And
4) turbocharger turbine 6.
Utilize the power of the variable size that the first boiler 23 and power turbine 31 obtain from exhaust, this system can move under various operating points.
The power that the power that extracts from the first boiler 23 that is arranged in turbocharger turbine 6 upstreams will make turbocharger turbine 6 and power turbine 31 use reduces, and the power that extracts from the second boiler 20 can not exert an influence to the power of turbosupercharger and power turbine.
The result of the energy of other amounts that extract from the first boiler 23 is presented in the chart of Fig. 5 A.
In the 4th embodiment's a modification (not shown), the cooling unit 12 humidifying unit 12a that is cooled replaces, and cooling humidifying unit 12a is to adding a large amount of water (steam) in the pressurized air.In this embodiment, pressurized air is not cooled to not such low temperature among the embodiment to the pressurized air humidification.This embodiment's Operational Limits is shown in " 4 is wet " hurdle of table 1.
Fig. 6 shows the fifth embodiment of the present invention.This embodiment corresponds essentially to the second embodiment, and difference is not have the second boiler 20.In addition, this motor moves by the low-down exhaust of outlet port temperature.This temperature can be hanged down-40 ℃, this means that the water in the exhaust will experience twice phase transformation: from steam to liquid and from liquid to the solid, the exhaust of for example leaving motor may comprise the ice of snow or similar form.So this motor is as heat pump, this is to cause especially concern not only needing mechanical energy but also needing in the application of heat energy, for example is used for providing the cogeneration power plant of electric energy and district heating.
Obtain described exhaust low temperature by in boiler 23, extracting a large amount of energy, so that it is relatively low to leave the temperature of exhaust of boiler 23.The exhaust next expansion in turbosupercharger causes delivery temperature further to reduce.Described temperature reduction is not limited to ambient temperature, significantly is lower than ambient temperature but can drop to.Therefore this burning type engine is called so-called " heat pump ", absorbs low grade heat energy and produce high-grade heat energy at this " heat pump " from environment.
When motor used heavy fuel oil or diesel oil, the exhaust component that are positioned at the dew point downstream adopted corrosion-resistant material to consist of, and they can tackle the acidic deposits (containing SO3--sulfuric acid in the condensation product) that the sulfur-bearing in the fuel becomes branch to cause like this.
When motor uses rock gas (LNG Liquefied natural gas), liquefied petroleum gas (LPG), dimethyl ether, alcohol or other to be substantially free of the fuel of sulphur, just do not need above-mentioned measure.
In the 5th embodiment, because the low temperature of the exhaust behind the turbocharger turbine does not have boiler in low voltage side.So this system only comprises on high-tension side the first boiler 23 of turbine.
Use MAN
" the 5﹠amp of the table 1 that the example of the 5th embodiment's of 12K98ME motor Operational Limits is illustrated in; 6 " in the hurdle.
Available power in the exhaust stream (160kg/s, 455 ℃, 3.30bar (abs.)) can be used in three equipment.
1) the first boiler 23 of turbocharger turbine 6 upstreams;
2) power turbine 31; And
3) turbosupercharger 6.
Utilize the power of the Variable quantity that the first boiler 23 and power turbine 31 obtain from exhaust, this system can move under various operating points.
The power that extracts from the first boiler 23 that is arranged in turbocharger turbine 6 upstreams will make the available power of turbocharger turbine 6 and power turbine 31 reduce.
In the 5th embodiment's a modification (not shown), motor is the motor with two turbines among aforementioned the 3rd embodiment, so that motor can be with the operation of higher delivery temperature, and relative with overall fuel energy pay close attention to the rotation from fuel, extracted can efficient (heat energy and energy calculate that relative motor produces draw).
Fig. 7 shows the sixth embodiment of the present invention.This embodiment is similar to the embodiment among Fig. 6, and difference is to have omitted turbosupercharger 8.Electric blower 16 ' (no longer being called as " auxiliary blower ") pressurizes to scavenging.At exhaust side, the power turbine 31 ' of increase serves as turbocharger turbine, and drives motor 17 ' for the electricity of blower 16 ' by generator 32 ' to provide electric energy.Any dump energy that the generator 32 ' that increases produces all is used to other purpose.The management of the electric energy that generator 32 ' produces can be by the control of controller unit (not shown), and this controller unit operates according to power management program or under operator's direct instruction.Being fixedly connected with between the turbine that saves and the compressor allows this motor to move more neatly, because compare the situation that exists fixing axle to connect between turbine and the compressor, the power that this power turbine produces can be assigned with more neatly.Accumulator system (not shown) such as battery pack are used as stabilizing the fluctuation of blower 16 ' institute's energy requirement, thereby improved the response of motor to accelerating, because the output of blower can increase simultaneously along with the increase of fuel injection amount, and need not wait for that turbine is about increasing the response of exhaust stream stream.
The function of starting according to the 6th embodiment is being moved in the boiler 23 interior power ranges that can extract flexibly.So set or running state in " winter ", when needing a large amount of heat energy for district heating, this motor is as heat pump, be starkly lower than 0 ℃ in the outlet port delivery temperature, set or running state in " summer ", this motor is not used as heat pump, and delivery temperature is in 50 ℃ to 200 ℃ scope.For setting summer, the second turbine (not shown) and turbine 31 ' are used in combination or replace turbine 31 ', thereby increase whole effective turbine area.Perhaps, use the single turbine with variable effective turbine area.The change of running state is also determined by the amount of the energy that extracts at boiler 23.The energy that extracts at boiler 23 is more, and the delivery temperature of leaving turbine just becomes lower.
In setting in " winter ", various temperature and pressures are corresponding to example given to the 5th embodiment in the table 1.
In the 6th embodiment's a modification (not shown), turbine 31 ' drives oil hydraulic pump, and blower 16 is by fluid motor-driven (replacing respectively generator and motor).For flexibility, oil hydraulic pump and motor can be the positive displacement devices with stroke changeable.Described oil hydraulic pump links to each other with pipeline by the valve by controller 27 operations with motor, and the hydraulic energy of being carried by pump like this is used to supply with oil hydraulic motor.
Another modification (not shown) of the 6th embodiment utilizes 180 ℃ exhaust to move, and the low voltage side at power turbine 31 ' has the second boiler simultaneously, so that the maximizing efficiency in " summer " setting.The engine parameter of this moment is corresponding to the parameter (referring to table 1) of the 3rd embodiment in " 3 is cold " hurdle.
This motor not only can move under above-mentioned two kinds of extreme cases, in fact, by being adjusted in the amount of the energy that boiler 23 extracts, and correspondingly select suitable effective turbine area, this motor also can utilize the delivery temperature of leaving turbine with any preferred temperature between the above-mentioned two situations to move.This motor can comprise that also two have the different effectively turbines of turbine area, and effective turbine area of a turbine is less, and effective turbine area of a turbine is larger.In this modification, motor can (set the winter of cogeneration power plant) only move by the turbine with less effective turbine area in the low-down situation of the delivery temperature of its low voltage side, and be in the situation of moderate temperature (cogeneration power plant spring/set autumn) in the delivery temperature of its low voltage side and only move by having the large effectively turbine of turbine area, and (set the summer of cogeneration power plant) moved with two turbines by parallel connection in the higher situation of the delivery temperature of its low voltage side.
Fig. 8 shows the seventh embodiment of the present invention.This embodiment is similar to the 4th embodiment.But, in the 7th embodiment, air flows to turbosupercharger 8, the exhaust of flowing out from turbosupercharger/power turbine simultaneously reduces 20%, because 20% exhaust is got back to scavenging system by the first boiler 23, recirculation conduit 19, blower 18 and scrubber 18a in the pipeline 11 places recirculation of intercooler 12 upstreams.The outlet of power turbine 31 is connected to the entrance of the second boiler 20 or is connected to the end portion of outlet pipe 21 shown in dashed line.The outlet temperature of power turbine 31 is depended in the selection that connects.If the outlet temperature of power turbine 31 significantly is lower than the outlet temperature of turbocharger turbine 6, so the outlet of power turbine is connected to the end portion of outlet pipe 21.
In " 7 " hurdle of the table 1 that the example of the Operational Limits of the present embodiment of same engine is illustrated in use and the previous embodiment.
In order to produce the air quantity of the 128kg/s with 3.6bar scavenging pressure, turbocharger compressor needs the power input of about 20.000kW.
This power must be extracted from exhaust by turbocharger turbine.Contain 22.400kW in the exhaust.Turbocharger turbine only needs the exhaust stream of 20000/22400*100%=89% to produce required 20.000kW.Remaining 11% can be utilized by power turbine 31.In addition, exhaust gas recirculatioon stream will be 20% of total exhaust stream, and all energy in the flow circuits all are utilized in the first boiler 23.
The inlet temperature of the second boiler 20 can change according to the power that extracts in boiler 1, simultaneously should not be lower than about 300 ℃, because the low temperature that is lower than 300 ℃ can cause outlet temperature to be lower than 180 ℃ (if use not fuel of sulfur-bearing of natural gas or other, then utilize the condensation of exhaust and possible freezing, that temperature can be selected is lower, so that the total energy efficiency maximization).
The power of power turbine 31 only depends on the inlet temperature of power turbine, perhaps in fact depends in the power turbine entrance string of the first boiler 23 to have extracted how much power.
The boiler inlet temperature is current in addition is the mixed number of turbosupercharger outlet temperature and power turbine outlet temperature.
This embodiment is particularly advantageous, because obtained low NOx value in exhaust.
Table 1
Embodiment recited above describes with the two-stage vapour system.But described vapour system also may be embodied as single level system or more than the system of two-stage.
The embodiment who is provided with boiler in exhaust receiver shown in seeing figures.1.and.2 can make up with the embodiment shown in Fig. 3,3a, 4,4a and Fig. 5-Fig. 8.
Example recited above all is the motor that operates under the maximum continuous rating (MCR).Should be noted that these motors also can move under other loads, this causes the temperature and pressure of air inlet system and exhaust system different.
Although above-described embodiment and example are based on a specific large two-stroke diesel engine model, the burning type engine of other sizes and type also can advantageously use in conjunction with the present invention described herein.
Usually, leave the temperature of exhaust of cylinder of large two-stroke diesel engine between 400 ℃-500 ℃.Leave the pressure of exhaust of cylinder of this motor generally more than 2bar, usually between 3bar to 4bar.
Especially, the idea that exhaust is expand into below the ambient temperature in turbine can be used for 2 strokes and 4 stroke combustion formula motors.
Other elements or step do not got rid of in " comprising " word used in the claim.A plurality of situations do not got rid of in " one " this word used in the claim.
Reference character in the claim should not be construed as the scope of restriction claim.
Although for illustrative purposes the present invention is had been described in detail, be to be understood that these detailed descriptions only are used for the example purpose, and those of ordinary skills can carry out various modification in the situation that does not deviate from protection domain of the present invention.
Claims (8)
1. a large cross-head type turbosupercharging two-stroke diesel engine (1) comprising:
A plurality of cylinders, each cylinder is connected to exhaust receiver (3) by corresponding manifold (40), so that exhaust directly flows to the described exhaust receiver (3) from described manifold (40),
Upstream exhaust pipe (5), this upstream exhaust pipe (5) is connected in the outlet of described exhaust receiver (3), is used for exhaust is guided to the entrance of the turbine (6) of turbosupercharger from described exhaust receiver (3),
Downstream row tracheae (7,21), this downstream row tracheae (7,21) are used for exhaust is guided to atmosphere from the outlet of the turbine (6) of described turbosupercharger, and
Be used for reclaiming from exhaust one or more exhaust heating boilers or the heat exchanger (23) of heat energy,
Described large cross-head type turbosupercharging two-stroke diesel engine is characterised in that
In described boiler or the heat exchanger (23) at least one is arranged in the described exhaust receiver (3).
2. motor as claimed in claim 1 also comprises the preboiler of the low voltage side that is positioned at described turbosupercharger, wherein, is arranged on the steam superheating that described boiler that described boiler in the exhaust receiver is used for making the low voltage side that is positioned at turbosupercharger produces.
3. motor as claimed in claim 2 also comprises the steam-powered steam turbine that is produced by the described boiler that is arranged in the exhaust receiver.
4. motor as claimed in claim 3, wherein, described vapor wheel machine driving generator.
5. such as each described motor in the claim 1 to 4, wherein, described exhaust receiver holds a plurality of boilers.
6. motor as claimed in claim 5, wherein, described a plurality of boilers form the multistage steam superheated vapor that comprises preboiler and overheated boiler and produce system.
7. motor as claimed in claim 1, wherein, described exhaust receiver longitudinally is divided into exhaust gas collection passage and heat exchanger channels.
8. motor as claimed in claim 7, wherein, described heat exchanger channels has the cross section of annular, has ring segment-shaped boiler section in this annular cross section.
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| CN201210244655.4A CN102900483B (en) | 2006-04-12 | 2006-04-12 | There is the large cross-head type two-stroke diesel engine of energy recycle device |
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| PCT/EP2006/003355 WO2007115579A2 (en) | 2006-04-12 | 2006-04-12 | A large turbocharged diesel engine with energy recovery arrangment |
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| CN201210245082.7A Division CN102900484B (en) | 2006-04-12 | 2006-04-12 | Large-scale turbocharged diesel engine with energy recovery device |
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Also Published As
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| DK200801354A (en) | 2008-09-29 |
| KR20080113402A (en) | 2008-12-30 |
| WO2007115579A2 (en) | 2007-10-18 |
| KR101238728B1 (en) | 2013-03-05 |
| JP4709923B2 (en) | 2011-06-29 |
| JP2009532614A (en) | 2009-09-10 |
| CN101415908A (en) | 2009-04-22 |
| DK178133B1 (en) | 2015-06-15 |
| WO2007115579A3 (en) | 2008-06-26 |
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