CN114000926A - Exhaust and shunt two-stage waste heat utilization system of low-speed diesel engine - Google Patents

Exhaust and shunt two-stage waste heat utilization system of low-speed diesel engine Download PDF

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Publication number
CN114000926A
CN114000926A CN202111279372.9A CN202111279372A CN114000926A CN 114000926 A CN114000926 A CN 114000926A CN 202111279372 A CN202111279372 A CN 202111279372A CN 114000926 A CN114000926 A CN 114000926A
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China
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low
communicated
diesel engine
temperature
exhaust
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Pending
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CN202111279372.9A
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Chinese (zh)
Inventor
路勇
牛羽
何丰硕
潘振嘉
路彤
周功杰
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Harbin Engineering University
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Harbin Engineering University
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Priority to CN202111279372.9A priority Critical patent/CN114000926A/en
Publication of CN114000926A publication Critical patent/CN114000926A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/02—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of multiple-expansion type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10—Adaptations for driving, or combinations with, electric generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/30—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines using exhaust steam only
    • 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 from exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using heat
    • 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
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • 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

Abstract

The invention discloses an exhaust and flow-dividing two-stage waste heat utilization system of a low-speed diesel engine, which comprises a low-speed diesel engine body, wherein a low-temperature gas collecting pipe and a high-temperature gas collecting pipe are communicated with the low-speed diesel engine body, and a low-temperature ORC system is arranged outside the low-temperature gas collecting pipe. The invention constructs a composite cycle for efficiently recycling exhaust gas waste heat of the marine diesel engine by stage flow distribution based on ORC systems with different temperature levels, the cycle fully utilizes gradient waste heat formed in the exhaust process of the diesel engine, reduces irreversible loss in the system, improves the energy utilization rate, flexibly selects organic working media by stage utilization of the energy after the exhaust gas of the diesel engine is stage flow distribution, flexibly matches the organic working media according to heat sources with different levels, and can utilize high-low temperature exhaust waste energy to the maximum extent on the premise that the heat after the exhaust flow distribution vortex is higher than the heat after the exhaust flow distribution vortex, thereby improving the overall efficiency of the low-speed diesel engine.

Description

Exhaust and shunt two-stage waste heat utilization system of low-speed diesel engine
Technical Field
The invention relates to the technical field of diesel engine energy conservation, in particular to an exhaust and shunt two-stage waste heat utilization system of a low-speed diesel engine.
Background
The current environmental problem is increasingly outstanding, the tasks of energy conservation and emission reduction are more urgent, the improvement of the waste heat utilization efficiency of the diesel engine is one of the important links for improving the overall efficiency of the diesel engine at present, the ship transportation cost is low, the cargo capacity is large, and the contribution of the ship diesel engine cannot be made.
The temperature of the exhaust gas after the vortex of the large-sized marine low-speed diesel engine is about 220 ℃, the highest thermal efficiency of the marine diesel engine device is only 45-50%, most of the generated heat is not utilized, and the generated heat is discharged to the atmosphere by various forms of energy to cause waste.
Disclosure of Invention
The invention mainly aims to provide an exhaust and shunt two-stage waste heat utilization system of a low-speed diesel engine, which aims to solve the technical problems of waste heat resource waste and low waste heat utilization rate of the low-speed diesel engine in the prior art.
In order to achieve the purpose of the invention, the invention provides an exhaust and flow-dividing two-stage waste heat utilization system of a low-speed diesel engine, which comprises a low-speed diesel engine body, wherein a low-temperature gas collecting pipe and a high-temperature gas collecting pipe are communicated with the low-speed diesel engine body, a low-temperature stage ORC system is arranged outside the low-temperature gas collecting pipe, a turbocharger body is communicated with the high-temperature gas collecting pipe, and a high-temperature stage ORC system is arranged outside the turbocharger body.
The high-temperature ORC system comprises a first evaporator, the evaporator is communicated with a turbocharger body, a first expander is communicated with the outside of the first evaporator, the outside of the first expander is electrically connected with a first generator, the outside of the first expander is also communicated with a heat regenerator, a first working medium pump is communicated with the outside of the heat regenerator, the outside of the first working medium pump is communicated with a heat exchanger, the heat exchanger is communicated with a low-speed diesel engine body, and meanwhile the first working medium pump is communicated with the first evaporator.
The low-temperature ORC system comprises a second evaporator, the second evaporator is communicated with the low-temperature gas collecting pipe, a second expander is communicated with the outside of the second evaporator, the outside of the second expander is electrically connected with a second generator, a second condenser is communicated with the outside of the second expander, a second liquid storage tank is communicated with the outside of the second condenser, a second working medium pump is communicated with the outside of the second liquid storage tank, and the second working medium pump is communicated with the second evaporator.
Preferably, a power turbine is communicated with an air outlet of the second evaporator, a speed reducer is fixedly connected to the outside of the power turbine, and a third generator is electrically connected to the outside of the speed reducer.
Preferably, a first organic working medium and a second organic working medium are respectively arranged in the high-temperature stage ORC system and the low-temperature stage ORC system according to actual conditions, and the boiling point of the second organic working medium is lower than that of the first organic working medium.
Preferably, the other end of the turbocharger body is communicated with an intercooler, and the intercooler is communicated with the diesel engine body.
Preferably, the outside of the diesel engine body is communicated with a waste gas diversion control valve, the waste gas diversion control valve is a three-way valve and is respectively communicated with the diesel engine body, the low-temperature gas collecting pipe and the high-temperature gas collecting pipe, and a temperature sensor is fixedly arranged between the waste gas diversion control valve and the low-speed diesel engine.
Preferably, the outside of heat exchanger and the inside host computer cylinder liner water of diesel engine body lead to the water pipe intercommunication, and the water pipe includes two, is outlet pipe and wet return respectively, and fixed mounting has the control valve on the outlet pipe.
Preferably, the external part of the heat regenerator is communicated with a first condenser, the external part of the first condenser is communicated with a first liquid storage tank, and the first liquid storage tank is communicated with the heat regenerator.
Preferably, an air guide pipe is fixedly installed at an air outlet of the first evaporator and is communicated with the soot blowing opening.
1. The invention constructs a composite cycle for efficiently recycling the waste heat of the exhaust graded-flow flue gas of the marine diesel engine based on ORC systems with different temperature grades, the method circularly and fully utilizes the gradient waste heat formed in the exhaust process of the diesel engine, reduces the irreversible loss in the system, improves the energy utilization rate, and after the exhaust is divided in stages, the temperature of the exhaust gas after the vortex is improved, the range of waste heat recovery is enlarged, a higher heat source is provided for a cascade waste heat recovery system, the waste heat utilization efficiency is improved, compared with the recovery systems such as a common waste heat boiler and the like, the boiling point of the circulating working medium of the organic Rankine power generation system is lower, can be changed into superheated steam when the temperature of the heat source is lower, is more suitable for energy recovery after exhaust gas is shunted, has high waste heat utilization efficiency, therefore, the combination of the exhaust gas fractional flow and the organic Rankine cycle can show great advantages in the aspect of low-speed engine waste heat recovery.
2. The invention flexibly selects the organic working medium by cascade utilization of the energy after the exhaust of the diesel engine is graded and divided, flexibly matches the organic working medium according to the heat sources of different grades, and enables the system to utilize the exhaust residual energy of high and low temperature to the maximum extent on the premise that the heat after the exhaust is divided into the vortex is higher than the heat after the vortex is not divided, thereby improving the overall efficiency of the low-speed diesel engine.
Drawings
FIG. 1 is a schematic view of an apparatus of the present invention;
FIG. 2 is a schematic diagram of the high temperature stage ORC system of the present invention;
fig. 3 is a schematic diagram of the low temperature stage ORC system of the present invention.
The system comprises a low-speed diesel engine body 1, a low-temperature gas collecting pipe 2, a high-temperature gas collecting pipe 3, a turbocharger body 4, a high-temperature ORC system 5, a first evaporator 51, a first expander 52, a first generator 53, a heat regenerator 54, a first condenser 55, a first liquid storage tank 56, a first working medium pump 57, a heat exchanger 58, an intercooler 6, a low-temperature ORC system 7, a second evaporator 71, a second expander 72, a second generator 73, a second condenser 74, a second liquid storage tank 75, a second working medium pump 76, a power turbine 8, a speed reducer 9 and a third generator 10.
The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.
Detailed Description
It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Referring to fig. 1-2, a low-speed diesel engine exhaust diversion two-stage waste heat utilization system comprises a low-speed diesel engine body 1, and is characterized in that a low-speed gas collecting pipe 2 and a high-temperature gas collecting pipe 3 are communicated with the low-speed diesel engine body 1, a waste gas diversion control valve is communicated with the outside of the diesel engine body 1 and is a three-way valve and is respectively communicated with the diesel engine body 1, the low-temperature gas collecting pipe 2 and the high-temperature gas collecting pipe 3, a temperature sensor is fixedly arranged between the waste gas diversion control valve and the low-speed diesel engine, so that the gas discharged by the low-speed diesel engine can be classified in two stages, the waste heat recovery with different gradients is performed, the waste heat recovery is performed with higher efficiency, a low-temperature stage ORC system 7 is arranged outside the low-temperature gas collecting pipe 2, a turbocharger body 4 is communicated with the high-temperature gas collecting pipe 3, and an intercooler 6 is communicated with the other end of the turbocharger body 4, intercooler 6 is linked together with diesel engine body 1, can compress air under the drive of waste gas through turbo charger body 4 and intercooler 6, increase inlet pressure and density, improve the air input, turbo charger body 4 outside is provided with high-temperature ORC system 5, be provided with first organic working medium and second organic working medium respectively according to actual conditions in high-temperature ORC system 5 and the low-temperature ORC system 7, the boiling point of second organic working medium is less than the boiling point of first organic working medium.
The high-temperature-stage ORC system 5 comprises a first evaporator 51, an air guide pipe is fixedly installed at an air outlet of the first evaporator 51, the air guide pipe is communicated with a soot blowing opening and can further utilize the residual energy in the heat-exchanged flue gas, for example, the air guide pipe is used for soot blowing, the first evaporator 51 is communicated with the turbocharger body 4, the first evaporator 51 is communicated with a first expander 52, the first expander 52 is electrically connected with a first generator 53, the first expander 52 is also communicated with a heat regenerator 54, the heat regenerator 54 is communicated with a first condenser 55, the first condenser 55 is communicated with a first liquid storage tank 56, the first liquid storage tank 56 can store a first organic working medium, the phenomenon that the heat transfer area is reduced due to excessive accumulation of condensate in the condenser is avoided, the heat transfer effect of the first condenser 55 is influenced, the first liquid storage tank 56 is communicated with the heat regenerator 54, the outside intercommunication of regenerator 54 has first working medium pump 57, first working medium pump 57 outside intercommunication has heat exchanger 58, heat exchanger 58 intercommunication low-speed diesel engine body 1, the outside of heat exchanger 58 and the inside host computer cylinder liner water of diesel engine body 1 lead to the water pipe intercommunication, can heat up to accomplish to first organic working medium and preheat, and the water pipe includes two, be outlet pipe and wet return respectively, fixed mounting has the control valve on the outlet pipe, first working medium pump 57 is linked together with first evaporimeter 51 simultaneously, can be convenient for control preheating the flow.
The low-temperature stage ORC system 7 comprises a second evaporator 71, a power turbine 8 is communicated with an air outlet of the second evaporator 71, a speed reducer 9 is fixedly connected to the outside of the power turbine 20, the outside of the speed reducer 9 is electrically connected with a third generator 10, when the system is used, the residual kinetic energy of the flue gas after heat exchange can be further utilized, so that the flue gas after heat exchange enters the power turbine to drive the power turbine to do work and convert the kinetic energy into electric energy, a low-temperature stage power system is formed, the exhaust energy of the low-temperature gas collecting pipe 2 is fully utilized, the second evaporator 71 is communicated with the low-temperature gas collecting pipe 2, the outside of the second evaporator 71 is communicated with a second expander 72, the outside of the second expander 72 is electrically connected with a second generator 73, the outside of the second expander 72 is communicated with a second condenser 74, the outside of the second condenser 74 is communicated with a second liquid storage tank 75, the outside of the second liquid storage tank 75 is communicated with a second working medium pump 76, second working medium pump 76 communicates with second evaporator 71.
It can be understood that the heat exchanger 58 can also preheat the first organic working medium by using the heat energy of the compressor in the turbocharger body 4; and cooling lubricating oil can be used for preheating, a secondary ORC system can be added to further recover waste heat in the arrangement form of the high-temperature stage ORC system 5 and the low-temperature stage ORC system 7, or exhaust gas in the low-temperature gas collecting pipe 2 and outlet flue gas in the high-temperature stage ORC system 5 are combined and the temperatures of the exhaust gas and the outlet flue gas are guaranteed to be the same to be used as a heat source of the secondary ORC, so that a series-parallel multi-stage ORC recovery system is formed.
It is to be noted that the first evaporator 51 and the second evaporator 71 in the present embodiment may be embodied as shell-and-tube heat exchangers, the first condenser 55 and the second condenser 74 may be embodied as plate-fin heat exchangers, and the first expander 52 and the second expander 72 may be embodied as screw expanders.
According to the invention, the energy after the exhaust of the diesel engine is graded and divided is utilized in a gradient manner, the organic working medium is flexibly selected, the organic working medium is flexibly matched according to heat sources of different grades, on the premise that the heat after the exhaust is divided and whirled is higher than the heat after the exhaust is not divided and whirled, the system can utilize the exhaust residual energy of high and low temperatures to the maximum extent, the overall efficiency of the low-speed diesel engine is improved, meanwhile, a composite cycle for efficiently recycling the exhaust graded and divided flue gas residual heat of the marine diesel engine is constructed based on ORC systems of different temperature grades, the gradient residual heat formed in the exhaust process of the diesel engine is fully utilized, the irreversible loss in the system is reduced, and the energy utilization rate is improved.
Specifically, after the exhaust gas of the low-speed diesel engine 1 is divided in stages, the high-temperature exhaust gas flows into the turbocharger body 4 to drive the compressor to rotate, then the high-temperature exhaust gas is introduced into the intercooler 6 to be cooled, then air is compressed, the inlet pressure and density are increased, the air inlet amount is improved, the flue gas after the turbine enters the first evaporator 51 as the heat source of the high-temperature ORC system 5, the flue gas after the turbine exchanges heat with the first working medium after the turbine in the high-temperature first evaporator 51, the first organic working medium absorbs heat in the high-temperature first evaporator 51 to become superheated steam, then the superheated steam enters the first expander 52 to expand and do work to drive the first generator 53 to work, the energy is stored in the form of electric energy, a part of the first organic working medium after the expander does work to enter the heat regenerator 54 as the air extraction, the condensed first organic working medium is preheated, and the rest of the first organic working medium enters the first condenser 55, the first organic working medium is condensed and cooled by cooling water, the first organic working medium enters the first liquid storage tank 56, the pressure of the first organic working medium passing through the first liquid storage tank 56 is increased by the first working medium pump 57, preparation is made for entering the high-temperature-level first evaporator 51, the first organic working medium before entering the high-temperature-level first evaporator 51 enters the heat exchanger 58 firstly, heat exchange is carried out with the main engine cylinder sleeve water of the low-speed diesel engine body 1, the first organic working medium enters the high-temperature-level first evaporator 51 after being increased by a certain temperature, and one-time high-temperature-level organic Rankine cycle is completed.
Flue gas after exhaust of a marine diesel engine is subjected to fractional diversion by a low-temperature gas collecting pipe enters a second evaporator 71 as a heat source of a low-temperature stage ORC system 7, low-temperature flue gas in the low-temperature stage second evaporator 71 exchanges heat with a second organic working medium, the second organic working medium absorbs heat in the low-temperature stage second evaporator 71 and becomes superheated steam, the second organic working medium discharged from the low-temperature stage second evaporator 71 enters a second expander 72 to perform expansion work, so that a second generator 73 is driven to work, energy is stored in an electric energy form, the second organic working medium passing through the second expander enters a second condenser 74 to be condensed, and then enters a second liquid storage tank 75, and then the second working medium is extracted by a second working medium pump 76 and finally returns to the low-temperature stage second evaporator 71 to complete one-time low-temperature stage organic Rankine cycle.
The low-temperature flue gas after heat exchange from the low-temperature stage second evaporator 71 enters the power turbine 8, the low-temperature flue gas drives the power turbine 8 to do work, and simultaneously drives the third generator 10 to generate electricity after being decelerated by the speed reducer 9, so that a low-temperature stage power system is formed, and the exhaust energy after the low-temperature gas collecting pipe is fully utilized.
The above description is only a preferred embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications of equivalent structures and equivalent processes, which are made by using the contents of the present specification and the accompanying drawings, or directly or indirectly applied to other related technical fields, are included in the scope of the present invention.

Claims (8)

1. The exhaust and flow-dividing two-stage waste heat utilization system of the low-speed diesel engine comprises a low-speed diesel engine body (1) and is characterized in that the low-speed diesel engine body (1) is communicated with a low-temperature gas collecting pipe (2) and a high-temperature gas collecting pipe (3), a low-temperature ORC system (7) is arranged outside the low-temperature gas collecting pipe (2), a turbocharger body (4) is communicated with the high-temperature gas collecting pipe (3), and a high-temperature ORC system (5) is arranged outside the turbocharger body (4);
the high-temperature-stage ORC system (5) comprises a first evaporator (51), the first evaporator (51) is communicated with the turbocharger body (4), the outside of the first evaporator (51) is communicated with a first expander (52), the outside of the first expander (52) is electrically connected with a first generator (53), the outside of the first expander (52) is also communicated with a heat regenerator (54), the outside of the heat regenerator (54) is communicated with a first working medium pump (57), the outside of the first working medium pump (57) is communicated with a heat exchanger (58), the heat exchanger (58) is communicated with the low-speed diesel engine body (1), and meanwhile, the first working medium pump (57) is communicated with the first evaporator (51);
the low-temperature ORC system (7) comprises a second evaporator (71), the second evaporator (71) is communicated with the low-temperature gas collecting pipe (2), the outside of the second evaporator (71) is communicated with a second expansion machine (72), the outside of the second expansion machine (72) is electrically connected with a second power generator (73), the outside of the second expansion machine (72) is communicated with a second condenser (74), the outside of the second condenser (74) is communicated with a second liquid storage tank (75), the outside of the second liquid storage tank (75) is communicated with a second working medium pump (76), and the second working medium pump (76) is communicated with the second evaporator (71).
2. The two-stage exhaust heat utilization system of the exhaust gas bypass of the low-speed diesel engine according to claim 1, wherein a power turbine (8) is communicated with an air outlet of the second evaporator (71), a speed reducer (9) is fixedly connected to the outside of the power turbine (20), and a third generator (10) is electrically connected to the outside of the speed reducer (9).
3. The two-stage exhaust heat utilization system of exhaust gas diversion of low-speed diesel engine according to claim 1, wherein a first organic working medium and a second organic working medium are respectively arranged in the high-temperature stage ORC system (5) and the low-temperature stage ORC system (7) according to actual conditions, and the boiling point of the second organic working medium is lower than that of the first organic working medium.
4. The two-stage exhaust gas diversion waste heat utilization system of the low-speed diesel engine as claimed in claim 1, wherein the other end of the turbocharger body (4) is communicated with an intercooler (6), and the intercooler (6) is communicated with the diesel engine body (1).
5. The exhaust and bypass two-stage waste heat utilization system of the low-speed diesel engine according to claim 1, wherein an exhaust bypass control valve is communicated with the outside of the diesel engine body (1), the exhaust bypass control valve is a three-way valve and is respectively communicated with the diesel engine body (1), the low-temperature gas collecting pipe (2) and the high-temperature gas collecting pipe (3), and a temperature sensor is fixedly installed between the exhaust bypass control valve and the low-speed diesel engine (1).
6. The two-stage exhaust gas diversion waste heat utilization system of the low-speed diesel engine according to claim 1, wherein the outside of the heat exchanger (58) is communicated with the main engine cylinder liner water inside the diesel engine body (1) through two water pipes, which are respectively a water outlet pipe and a water return pipe, and a control valve is fixedly installed on the water outlet pipe.
7. The exhaust gas diversion two-stage waste heat utilization system of the low-speed diesel engine according to claim 1, wherein the external part of the heat regenerator (54) is communicated with a first condenser (55), the external part of the first condenser (55) is communicated with a first liquid storage tank (56), and the first liquid storage tank (56) is communicated with the heat regenerator (54).
8. The two-stage exhaust gas diversion waste heat utilization system of the low-speed diesel engine according to claim 1, wherein an air guide pipe is fixedly installed at an air outlet of the first evaporator (51), and the air guide pipe is communicated with a soot blowing opening.
CN202111279372.9A 2021-11-01 2021-11-01 Exhaust and shunt two-stage waste heat utilization system of low-speed diesel engine Pending CN114000926A (en)

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US20050268955A1 (en) * 2004-06-08 2005-12-08 Meyerkord Daniel J Diesel-electric locomotive engine waste heat recovery system
CN103352772A (en) * 2013-06-25 2013-10-16 天津大学 Combined cycle thermoelectric conversion system utilizing multi-grade waste heat of internal combustion engine
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CN108167038A (en) * 2018-01-18 2018-06-15 北京工业大学 Organic Rankine Cycle-Trans-critical cycle CO2Heat pump engine exhaust heat recycles association system
CN110107384A (en) * 2019-05-13 2019-08-09 哈尔滨工程大学 A kind of energy recovery utilizing system being classified separation output based on low speed machine exhaust energy
CN110905618A (en) * 2019-11-18 2020-03-24 天津大学 Internal combustion engine cogeneration waste heat recovery system suitable for distributed energy system
CN214304016U (en) * 2021-02-19 2021-09-28 中国重汽集团济南动力有限公司 Two-stage waste heat recovery system of diesel engine

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