CN101415908A - 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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- CN101415908A CN101415908A CNA2006800541824A CN200680054182A CN101415908A CN 101415908 A CN101415908 A CN 101415908A CN A2006800541824 A CNA2006800541824 A CN A2006800541824A CN 200680054182 A CN200680054182 A CN 200680054182A CN 101415908 A CN101415908 A CN 101415908A
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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]
-
- 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
Landscapes
- 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 obtains reclaiming by 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,, cause overall structure to become relatively huge and complicated by between the turbine of exhaust receiver and turbosupercharger, placing a boiler.In addition, the increase of the flow-path-length between exhaust valve and the turbosupercharger can reduce the response of turbosupercharger to quickening.In addition, this motor only reclaims heat energy, and the energy of form that can not the transformation of energy one-tenth that be reclaimed is more useful, as energy of rotation 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 compact more 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 all is connected to exhaust receiver by corresponding manifold; Upstream exhaust pipe, this upstream exhaust pipe are used for exhaust is guided to from described exhaust receiver the inlet of the turbine of turbosupercharger; The downstream row tracheae, this downstream exhaust gas pipe is used for exhaust is guided to atmosphere from the outlet of the turbine of described turbosupercharger; Be used for reclaiming the 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 from exhaust.
By one in the described boiler is placed in the exhaust receiver, make the compact area of parts at the large-sized turbo-charging diesel motor top of system no longer need any space effectively.This measure has produced more spaces around motor, has reduced the stringing amount simultaneously.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 the cavity that is used to hold 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 makes heat exchange area significantly reduce (every other parameter too), thereby causes 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.Place this moment the boiler in the exhaust receiver to be used to make the steam superheating that boiler produced of turbosupercharger low voltage side.So the quality of steam has improved, 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 convert energy of rotation to electric energy.
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.This purpose realizes that by a kind of large-sized turbo-charging diesel motor is provided this large-sized turbo-charging diesel motor comprises according to claim 9: 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 by use from the high pressure side of turbocharger turbine, quantitatively improved the energy total amount that can from exhaust, reclaim, especially change under the bigger condition in operating mode, because compare with produce more energy of rotation by power turbine, this system is suitable for producing more thermal 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, first boiler can be by all blast air mistakes, and the discharge portion that is used for power turbine is simultaneously shunted in the downstream of this first exhaust heating boiler.Allow to the total amount maximization of the energy that reclaims like this.
On the other hand, the splitter section that first boiler can only be deflated flows through, and this does not influence the thermal equilibrium of turbosupercharger, has guaranteed the responsiveness of accelerating period turbocharger turbine by this way.
Leave the exhaust of power turbine and can be introduced main exhaust stream again 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 very attractive form energy flexibly.
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 realizes by a kind of large supercharged two-stroke diesel engine is provided according to claim 23, this large supercharged two-stroke diesel engine comprises: the exhaust gas drive turbine that drives generator, drive the booster air compressor of motor driven 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 the energy that the use of the on high-tension side heat exchanger of while turbine has been guaranteed to reclaim in the exhaust well and comprised with bigger degrees of freedom.
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 control electric energy that generator produced and stored electric energy.
Described motor can also comprise by the steam turbine that steam drove 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 realizes by the boosting explosive formula motor of a kind of use in cogeneration power plant is provided according to claim 23, 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 lot of energy, and use the less relatively turbine of effective turbine area, the colder relatively expansion of 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.Total fuel efficiency be can obtain, good and economic and environment friendly shown thus apparently higher than 100%.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 big capacity by being 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, the temperature of exhaust of leaving cylinder is between 400 ℃ to 500 ℃, and the temperature of exhaust of leaving the exhaust heating boiler is 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 blast air.
Described motor can comprise steam turbine, the steam driven that heat produced that this steam turbine is extracted from exhaust by described heat exchanger utilization.
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.
The temperature of exhaust of leaving turbine is 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, the temperature of exhaust of leaving turbine is 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 that this supercharged combustion engine comprises that a gas handling system is used under external pressure and temperature, described gas handling system comprises: compressor, this compressor are used for the pressurized air of pressure more than external pressure is transported to the cylinder of described internal combustion engine; First turbine by the given effective turbine area of having of exhaust gas drive; 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, this compressor are 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 of operating 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; First turbine by the given effective turbine area of having of exhaust gas drive; 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 by following detailed description.
Description of drawings
In the detailed description, the exemplary embodiment shown in is described in more details the present invention with reference to the accompanying drawings below this specification, 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 the 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 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 first embodiment according to the upper area of large two-stroke diesel engine 1 of the present invention.This motor is provided with a plurality of cylinders of arranging in upright arrangement side by side each other.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 a plurality of) 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 and two the heat exchanger section 50a and the 50b that put in 52 both sides, central outlets chamber and collect 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 separated by spacer 49.Each section 50a, 50b comprise two heat exchanger component 57a, 58a and 57b, 58b respectively, each heat exchanger component includes a large amount of pipe that extends along airflow direction, described airflow direction is represented 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 the plurality of sub section 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 back 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 the external heated 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 the exhaust reception cavity simultaneously and reclaimed the boiler of heat energy from exhaust.By in exhaust receiver, comprising described boiler, saved the housing of needed space of exhaust-gas boiler and exhaust-gas boiler.
Fig. 3 shows second embodiment of the crosshead type large two-stroke turbo-charging diesel motor 1 that has 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 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 the scope of 000kW, for example be 1 but the present invention also can be used for output for example 5,000 to 110, the four-cycle diesel engine of 000kW.
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, arrived the turbine 6 of turbosupercharger then forward 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 pressurized air pipe 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.
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 blast air is converted into electric energy, promptly 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 introduced main exhaust stream there again.
The steam that pipeline 22 produces second boiler 20 is directed to the inlet of first boiler.First boiler is about 450 ℃ exhaust heating by temperature, and this exhaust is that the water/steam that enters 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.Though, 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 not shown in this embodiment or any other embodiment.
Has MAN B﹠amp; W
The example of 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, as the use condition of boiler type, steam turbine type and large two-stroke diesel engine.The main concern provides energy of rotation in the boat of ocean, then pays close attention to the production (when being used for district heating) of heat energy and the production of electric power in the stationary power generation station with being equal to.
Utilize the power of the variable size that 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 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 second boiler 20 can not exert an influence to the power of turbosupercharger and power turbine.
In the example of table 1, from first boiler 23, extracted 10, the power delivery of 000kW is given steam turbine 37 (for this example, performance number is optional, can select other value as shown in Figure 3A).
Fig. 3 A shows the figure of the result of calculation of the power that extracts the varying number value in first boiler 23.Use the power of the percentage of engine shaft power being 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 first boiler 23 that is arranged in turbocharger turbine 6 upstreams increased, the energy that can extract just reduced from power turbine.Can decide best running position according to energy needed type (heat energy or energy of rotation/electric energy).
If need heat energy and energy of rotation simultaneously, 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 first boiler 23.Even this operating point requirement auxiliary blower 16 under full-load conditions also will be worked.
The main energy that needs on the boat of ocean is a thrust power, promptly drives the energy of rotation of propeller cavitation (not shown).The needed heat of whole ship is relatively low usually, 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 from comprehensive energy efficiency viewpoint of advantage with 5,000-10, the energy of 000KW is moved by the mode that first boiler extracts.
Fig. 4 shows the third embodiment of the present invention.Except the type difference of scavenging cooler 12a, this embodiment corresponds essentially to second embodiment.Described scavenging cooler is the scrubber that injects and evaporate big 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 second embodiment.So energy contained in scavenging and the exhaust significantly increases.Therefore there are more available energy boiler of feeding 20,23 and power turbine 31 to extract in the exhaust.
Has MAN B﹠amp;
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, extract 10 in first boiler 23,000kW is 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 first boiler.Use the power of the percentage of engine shaft power being 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 power that extracts at first boiler 23 that is arranged in turbocharger turbine 6 upstreams increased, the power that can extract just reduced from power turbine 31.In this embodiment, power is not being given under the situation of auxiliary blower 16, can from first boiler 23, extracted above 25 the power of 000kW.In motor according to second embodiment, power is not being given under the situation of auxiliary blower 16, can only in 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 second embodiment) apparently higher than routine.Be similar to operating point according to the desirable operating point of the 3rd embodiment's motor according to second 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 concern especially not only needing mechanical energy but also needing in the application of heat energy, as is used to provide the cogeneration power plant of electric energy and district heating.Obtain described running state by in first boiler 23, extracting lot of energy, in the example of table 1, extracted 72.000kW.In addition, the useful area of turbine 6 is compared with foregoing example/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 expands) falls in the temperature of exhaust in turbine to be increased).So the 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 constitute, 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 B﹠amp; W
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 second boiler in low voltage side.So this system only comprises and is positioned on high-tension side first boiler 23 of turbine.
In another modification (not shown) of this embodiment, motor is provided with second turbine, be used for when lower and (be 50 ℃ to 200 ℃ for example with higher delivery temperature operation when higher in low voltage side in turbine high pressure side and low voltage side to the demand of energy of rotation to the demand of heat energy, in the high pressure side is 150 ℃ to 350 ℃), the summer operation of cogeneration power plant for example.This system can switch to has big effectively second turbine of turbine area, to obtain to be lower than the delivery temperature of ambient temperature, perhaps second turbine also can have less relatively turbine area, two in parallel uses of turbine that useful area is less, and each all receives a part of blast air.In service in higher exhaust gas temperature, having the big effectively turbine of turbine area or two turbines with less effective turbine area of parallel running will make auxiliary blower only need just start when running on the lower load to the enough power of compressor transmission.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 energy of rotation production, this system under this pattern optimised makes its have maximum from fuel the efficient of extraction energy of rotation.
Fig. 5 shows the fourth embodiment of the present invention.This embodiment corresponds essentially to second embodiment, and difference is that first boiler 23 is arranged in from the blast air that outlet pipe 5 branches away.So, have only the splitter section of exhaust to flow through first boiler 23.Pipeline 30 is guided to power turbine 31 with exhaust from the outlet of 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 inlets of 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 B﹠amp; W
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 is shunted to produce power turbine output power (PO towards power turbine
PT) or the auxiliary blower input power.
Can determine optimum value about the power that from whole system, extracts.This finally depends on the circumstances, as the use condition of boiler type, steam turbine type and large two-stroke diesel engine.The main concern provides energy of rotation in the boat of ocean, then pays close attention to the production (when being used for district heating) of heat energy and the production of electric power in the stationary power generation station with being equal to.
Available power in the blast air (160kg/s, 455 ℃, 3.35bar (abs.)) can be used in four equipment.
1) 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 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 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 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 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 gives and adds 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 second embodiment, and difference is not have 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 concern especially not only needing mechanical energy but also needing in the application of heat energy, for example is used to provide the cogeneration power plant of electric energy and district heating.
Obtain described exhaust low temperature by in boiler 23, extracting lot of energy, make that the temperature of the exhaust of leaving boiler 23 is relatively low.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 constitute, 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 first boiler 23 of turbine.
Use MAN B﹠amp; W
" 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 blast air (160kg/s, 455 ℃, 3.30bar (abs.)) can be used in three equipment.
1) first boiler 23 of turbocharger turbine 6 upstreams;
2) power turbine 31; And
3) turbosupercharger 6.
Utilize the power of the Variable quantity that first boiler 23 and power turbine 31 obtain from exhaust, this system can move under various operating points.
The power that extracts from 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 the relative efficient (heat energy and electric energy that relative motor is produced calculate) of paying close attention to the energy of rotation that from fuel, extracts with overall fuel energy.
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 ' electric energy is provided.Any dump energy that generator 32 ' produced that increases all is used to other purpose.The management of the electric energy that generator 32 ' produced can be by the control of controller unit (not shown), and this controller unit is operated according to power management program or under operator's direct instruction.This motor of fixedly connected permission between turbine that saves and the compressor moves 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 the fluctuation of stabilizing blower 16 ' institute's energy requirement, thereby improved the response of motor to quickening, 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 blast air stream.
The function of starting according to the 6th embodiment is moved in the power range that can extract in boiler 23 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 ", as heat pump, delivery temperature is not in 50 ℃ to 200 ℃ scope for this motor.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 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 many more, and the delivery temperature of leaving turbine just becomes low more.
In setting in " winter ", all temps and pressure 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 generator and motor respectively).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 pressure of being carried by pump can be used to supply with oil hydraulic motor like this.
Another modification (not shown) of the 6th embodiment utilizes 180 ℃ exhaust to move, and the low voltage side at power turbine 31 ' has 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 extracted, and correspondingly select suitable effective turbine area, this motor also can utilize the delivery temperature of leaving turbine with any desired temperature between above-mentioned two kinds of 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 bigger.In this modification, motor can (set the winter of cogeneration power plant) only move by the turbine with less effective turbine area under the low-down situation of the delivery temperature of its low voltage side, and be under the situation of moderate temperature (cogeneration power plant spring/set autumn) in the delivery temperature of its low voltage side and only move, and (set the summer of cogeneration power plant) uses two turbines to move by parallel connection under the delivery temperature condition with higher of its low voltage side by having the big effectively turbine of turbine area.
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 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 inlet of 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 blast air 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 blast air, and all energy in the flow circuits all are utilized in first boiler 23.
The inlet temperature of 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 inlet string of 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 difference of air inlet system and exhaust system.
Though the foregoing description 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 ℃.The pressure of exhaust of cylinder that leaves this motor is generally more than 2bar, usually between 3bar to 4bar.
Especially, the idea that exhaust is expand in turbine below the ambient temperature can be used for 2 strokes and 4 stroke combustion formula motors.
Other elements or step do not got rid of in " comprising " speech used in the claim.A plurality of situations do not got rid of in " one " this speech 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 under the situation that does not deviate from protection domain of the present invention.
Claims (46)
1. a kind of large-sized turbo-charging diesel motor comprises:
A plurality of cylinders, each cylinder all is connected to exhaust receiver by corresponding manifold,
Upstream exhaust pipe, this upstream exhaust pipe are used for exhaust is guided to the inlet of the turbine of turbosupercharger from described exhaust receiver,
The downstream row tracheae, this downstream exhaust gas pipe is used for exhaust is guided to atmosphere from the outlet of the turbine of described turbosupercharger, and
Be used for reclaiming the one or more exhaust heating boilers or the heat exchanger of heat energy from exhaust,
Described large-sized turbo-charging diesel motor is characterised in that
At least one boiler in described boiler or the heat exchanger or heat exchanger are arranged in the described exhaust receiver.
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 produced that described boiler in the exhaust receiver is used to make the low voltage side that is positioned at turbosupercharger.
3. motor as claimed in claim 1 or 2 also comprises the steam-powered steam turbine that is produced by described boiler.
4. motor as claimed in claim 3, wherein, described power turbine drives generator.
5. 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 laterally 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 basic annular, has ring segment-shaped substantially boiler section in the cross section of this basic annular.
9. large-sized turbo-charging diesel motor comprises:
Turbosupercharger with exhaust gas drive turbine, this turbosupercharger is connected to booster air compressor,
Be positioned at the on high-tension side first exhaust heating boiler of turbosupercharger,
Power turbine, a part of exhaust gas drive that this power turbine is distributed by the high pressure side from turbosupercharger.
10. motor as claimed in claim 9 also comprises the second exhaust heating boiler of the low voltage side that is positioned at described turbosupercharger.
11. as claim 10 or 11 described motors, wherein said first boiler is by all blast air mistakes, and the discharge portion that is used for described power turbine distributes from the downstream of the described first exhaust heating boiler.
12. as claim 10 or 11 described motors, wherein, the discharge portion that described first boiler is only distributed flows through.
13., wherein, leave the exhaust of described power turbine and introduced main exhaust stream again in the low voltage side of described turbosupercharger as each described motor in the claim 9 to 12.
14. as each described motor in the claim 9 to 13, wherein, described power turbine drives generator.
15. as each described motor in the claim 9 to 14, wherein, the described second exhaust gas drive boiler is as preboiler, and the described first exhaust heating boiler is used to make the steam superheating of described second exhaust heating boiler generation.
16. motor as claimed in claim 15 also comprises steam turbine, this steam turbine is driven by the superheated vapor that the described first exhaust heating boiler and the second exhaust heating boiler are produced.
17. motor as claimed in claim 15, wherein, described motor is operated to reclaim and is used for obtaining the highly big energy of described first exhaust-gas boiler of superheated vapor, thereby improves the efficient of described steam turbine.
18. as each described motor in the claim 9 to 17, wherein, described scavenging is by humidification and be cooled to higher relatively temperature, make the scavenging enter cylinder have high water vapor absolute content, thereby increased the energy content that is used for carrying out subsequent recovery in the exhaust at described boiler and/or power turbine.
19. as each described motor in the claim 9 to 18, described motor comprises a plurality of cylinders, each cylinder all is connected to exhaust receiver by corresponding manifold, and the wherein said first exhaust heating boiler and/or the second exhaust heating boiler are arranged in the described exhaust receiver.
20., wherein, be chosen to make delivery temperature below ambient temperature the cooling capacity of described first boiler and/or second boiler as each described motor in the claim 9 to 19.
21. as each described motor in the claim 9 to 20, wherein, a part of blast air is recycled.
22. motor as claimed in claim 21 wherein, partly is to distribute from the blast air that is arranged in the described first boiler downstream with the blast air that is recycled.
23. a large supercharged two-stroke diesel engine comprises:
Drive the exhaust gas drive turbine of generator,
Drive the booster air compressor of motor driven by electricity, and
Be positioned at the on high-tension side heat exchanger of described turbine, this heat exchanger is used for extracting heat energy from exhaust.
24. large supercharged two-stroke diesel engine as claimed in claim 23, this motor does not comprise turbosupercharger.
25. as claim 23 or 24 described large supercharged two-stroke diesel engines, wherein, described heat exchanger is used to produce steam.
26. the described large supercharged two-stroke diesel engine of claim 25 also comprises the device of a part that is used to accumulate the electric energy that is produced by described generator and the device that stored supply of electrical energy is driven motor to electricity.
27. large supercharged two-stroke diesel engine as claimed in claim 26 also comprises the assigned unit that is used for controlling the electric energy that produced by described generator and stored electric energy.
28. as each described large supercharged two-stroke diesel engine in the claim 25 to 27, also comprise steam turbine, this steam turbine is by driving by means of the steam that heat energy produced from described heat exchanger.
29. as each described large supercharged two-stroke diesel engine in the claim 23 to 28, wherein, described heat exchanger is configured to make the temperature of the exhaust of leaving described heat exchanger to be reduced to and makes the degree of delivery temperature below ambient temperature of leaving the turbine that is positioned at described heat exchanger downstream.
30. a large supercharged two-stroke diesel engine comprises:
Drive the exhaust gas drive turbine of oil hydraulic pump,
By the booster air compressor of hydraulic drive motor driving, and
Heat exchanger, this heat exchanger is positioned at the high pressure side of turbine, is used for extracting heat from exhaust.
31. a boosting explosive formula motor that is used in the cogeneration power plant, 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, this compressor is used for the pressurized air of pressure more than external pressure is transported to the cylinder of described internal combustion engine,
By the turbine 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,
Described heat exchanger and turbine are configured to obtain to be lower than the turbine low voltage side delivery temperature of ambient temperature.
32. boosting explosive formula motor as claimed in claim 31, the delivery temperature that wherein is lower than ambient temperature are by the big capacity that is used for increasing the heat exchanger that falls through the temperature of the exhaust of described heat exchanger and are used for increasing little effective turbine area that exhaust falls in the temperature of described turbine inflation process and obtain.
33. boosting explosive formula motor as claimed in claim 31, wherein, the temperature of exhaust of leaving described cylinder is between 400 ℃ to 500 ℃, and the temperature of exhaust of leaving described exhaust heating boiler is below 110 ℃, and the pressure of exhaust that leaves described boiler is more than 2bar.
34. as each described boosting explosive formula motor in the claim 31 to 34, wherein, described turbine is connected to form turbosupercharger by axle with compressor.
35. boosting explosive formula motor as claimed in claim 34, also comprise auxiliary blower, this blower is used for preferably helping described turbine pressurized air to be transported to the cylinder of described internal combustion engine when described internal combustion engine moves under maximum continuous rating.
36. as claim 34 or 35 described boosting explosive formula motors, wherein said motor also comprises power turbine, this power turbine is by the exhaust gas drive of the turbocharger turbine that is diverted to described boiler downstream from blast air.
37. as each described boosting explosive formula motor in the claim 31 to 36, also comprise steam turbine, the steam that heat produced that this steam turbine is extracted from exhaust by described heat exchanger utilization drives.
38., also comprise the on high-tension side pressurized air humidifying unit that is positioned at described compressor as each described boosting explosive formula motor in the claim 31 to 37.
39. as each described boosting explosive formula motor in the claim 31 to 38, wherein, the pressure that leaves the exhaust of described turbine equals or a little more than external pressure.
40. as each described boosting explosive formula motor in the claim 31 to 39, wherein, at least at described motor during in its maximum continuous rating operation, the temperature of exhaust of leaving described turbine is below ambient temperature.
41. as each described boosting explosive formula motor in the claim 31 to 40, wherein, at least at described motor during in its maximum continuous rating operation, the temperature of exhaust of leaving described turbine is between-5 ℃ to-40 ℃.
42. as each described boosting explosive formula motor in the claim 31 to 41, also comprise another turbine, described another turbine is used to make the effective turbine area of motor with the operation of the turbine low voltage side delivery temperature more than the ambient temperature as replacing described turbine or being used in combination with described turbine with change.
43. as each described boosting explosive formula motor in the claim 31 to 41, wherein said turbine is to have to be used to make the type of motor with variable effective turbine area of different delivery temperature operations.
44. boosting explosive formula motor, comprise: the gas handling system that is used for the air under the absorbing environmental pressure and temperature, this gas handling system comprises: compressor, this compressor are used for the pressurized air of pressure more than external pressure is transported to the cylinder of described internal combustion engine; First turbine by the given effective turbine area of having of exhaust gas drive; 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.
45. boosting explosive formula motor, comprise: the gas handling system that is used for the air under the absorbing environmental pressure and temperature, this gas handling system comprises: compressor, this compressor are 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.
46. method of operating boosting explosive formula motor, described boosting explosive formula 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; First turbine by the given effective turbine area of having of exhaust gas drive; 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| 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 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/EP2006/003355 WO2007115579A2 (en) | 2006-04-12 | 2006-04-12 | A large turbocharged diesel engine with energy recovery arrangment |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210244655.4A Division CN102900483B (en) | 2006-04-12 | 2006-04-12 | There is the large cross-head type two-stroke diesel engine of energy recycle device |
| CN201210245082.7A Division CN102900484B (en) | 2006-04-12 | 2006-04-12 | Large-scale turbocharged diesel engine with energy recovery device |
Publications (2)
| Publication Number | Publication Date |
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| CN101415908A true CN101415908A (en) | 2009-04-22 |
| CN101415908B CN101415908B (en) | 2013-03-13 |
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| CN2006800541824A Active CN101415908B (en) | 2006-04-12 | 2006-04-12 | Large-sized turbo-charging diesel motor with energy recovery apparatus |
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|---|---|
| JP (1) | JP4709923B2 (en) |
| KR (1) | KR101238728B1 (en) |
| CN (1) | CN101415908B (en) |
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| WO (1) | WO2007115579A2 (en) |
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| CN107869407A (en) * | 2016-09-27 | 2018-04-03 | 翰昂汽车零部件有限公司 | It is integrated with the exhaust thermal management module of exhaust gas recirculatioon, recuperation of heat and latent heat storage |
| CN107387217A (en) * | 2017-07-31 | 2017-11-24 | 中国船舶重工集团公司第七研究所 | Power turbine TRT |
| CN107435574A (en) * | 2017-09-06 | 2017-12-05 | 哈尔滨工程大学 | Diesel exhaust waste heat ECR fan pressure charging system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2009532614A (en) | 2009-09-10 |
| WO2007115579A3 (en) | 2008-06-26 |
| JP4709923B2 (en) | 2011-06-29 |
| CN101415908B (en) | 2013-03-13 |
| WO2007115579A2 (en) | 2007-10-18 |
| KR20080113402A (en) | 2008-12-30 |
| DK178133B1 (en) | 2015-06-15 |
| DK200801354A (en) | 2008-09-29 |
| KR101238728B1 (en) | 2013-03-05 |
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Address after: Copenhagen, Denmark Patentee after: Mannone solutions (mannone solutions Germany) branch Address before: Copenhagen, Denmark Patentee before: Mann Diesel & Turbine, an associate company of Mann Diesel & Turbine Europe AG |