CN110529283A - A kind of cooling coupled system with cogeneration of tank armored vehicle engine - Google Patents

A kind of cooling coupled system with cogeneration of tank armored vehicle engine Download PDF

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Publication number
CN110529283A
CN110529283A CN201910773781.0A CN201910773781A CN110529283A CN 110529283 A CN110529283 A CN 110529283A CN 201910773781 A CN201910773781 A CN 201910773781A CN 110529283 A CN110529283 A CN 110529283A
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China
Prior art keywords
steam
engine
cooling
superheater
evaporator
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CN201910773781.0A
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谷操
李源浩
张敏
刘洋
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China North Vehicle Research Institute
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China North Vehicle Research Institute
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Classifications

    • 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
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • 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
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P9/00—Cooling having pertinent characteristics not provided for in, or of interest apart from, groups F01P1/00 - F01P7/00
    • F01P9/02—Cooling by evaporation, e.g. by spraying water on to cylinders
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G1/00—Steam superheating characterised by heating method
    • F22G1/16—Steam superheating characterised by heating method by using a separate heat source independent from heat supply of the steam boiler, e.g. by electricity, by auxiliary combustion of fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/046—Condensers with refrigerant heat exchange tubes positioned inside or around a vessel containing water or pcm to cool the refrigerant gas
    • 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
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
    • 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 present invention provides a kind of cooling coupled systems with cogeneration of tank armored vehicle engine, including liquid working substance, water pump, evaporator, superheater, turbine, generator, condenser and blower；Liquid working substance is driven into evaporator using water pump, and evaporator heats the liquid working substance up to flashing to steam, cooling engine using engine coolant as heat source；Steam flows into superheater, and superheater is heated to overtemperature as superheated steam using engine exhaust heat as heat source, by steam；Superheated steam drives turbo driving, drives electrical power generators, superheat steam temperature, pressure are decreased as Low Temperature Steam；Low Temperature Steam enters condenser, and by fan radiating, Low Temperature Steam is condensed into liquid；Liquid flows into water pump and realizes closed cycle.The present invention can cool down engine, while be generated electricity using engine exhaust heat.

Description

A kind of cooling coupled system with cogeneration of tank armored vehicle engine
Technical field
The present invention relates to car engine thermal efficiency technical fields, and in particular to a kind of tank armored vehicle engine it is cooling with The coupled system of cogeneration.
Background technique
The power and electric power energy of Tank and Armoured Vehicle both are from engine, and engine transitions are the heat of Effective power at present The 30%~40% of fuel combustion calorific value (input heat) is only accounted for, 30%~40% will be accounted for by being vented the heat taken away, cooling system The heat that regiment commander walks accounts for about 20%~25%, other heat dissipations account for about 10% or so.The power technology of Tank and Armoured Vehicle develops, and leads to It crosses using high temperature cooling technique, adiabatic engine technology etc., is the power density in order to improve engine, improves the burning of fuel Thermal transition is the ratio of Effective power.But it is limited by thermodynamic cycle characteristic, the fuel combustion converting heat of engine is Effective power Ratio is limited；And with the extensive application of novel actuation techniques, electromagnetic technique and other pulse techniques, for electric power energy The demand in source is increasing, and energy consumption is caused increasingly to improve.Under this situation background, the demand of efficiency of energy utilization is improved more Urgently, the recycling benefit of the engine exhaust heats such as the thermal efficiency for fuel being improved for the waste heat by engines such as recycling exhaust gas heats It is paid more and more attention with technology.
At present for the research of cogeneration technology, it is concentrated mainly on engine exhaust heat utilization, is ignored to cooling The heat recovery of system.Currently based on the engine exhaust heat generation technology of Rankine cycle there are a series of defects, directly make The about application on vehicle, is mainly manifested in: energy consumption of compressor in system is higher, condenser condensation temperature is lower causes Condensation energy consumption is higher to influence recovery efficiency, and the component of system is more, the space occupied is big, the work of working medium side enclosed circulation The problems such as making pressure height, requirement matched to flow resistance harshness.
Summary of the invention
In view of this, the present invention provides a kind of cooling coupled system with cogeneration of tank armored vehicle engine, Engine can be cooled down, while being generated electricity using engine exhaust heat.
The technical solution adopted by the present invention is as follows:
A kind of cooling coupled system with cogeneration of tank armored vehicle engine, the coupled system includes liquid work Matter, water pump, evaporator, superheater, turbine, generator, condenser and blower；
Liquid working substance is driven into evaporator using water pump, and evaporator heats the liquid using engine coolant as heat source Body working medium is up to flashing to steam, cooling engine；Steam flow into superheater, superheater using engine exhaust heat as heat source, Steam is heated to overtemperature as superheated steam；Superheated steam drives turbo driving, drives electrical power generators, superheated steam Temperature, pressure are decreased as Low Temperature Steam；Low Temperature Steam enters condenser, and by fan radiating, Low Temperature Steam is condensed into Liquid；Liquid flows into water pump and realizes closed cycle.
Further, the liquid working substance is engine coolant.
Further, the condenser uses belt concurrent flow aluminium pipe structure.
The utility model has the advantages that
1, the present invention utilizes Rankine (Rankine) Cyclical Theory, and the heat of engine-cooling system is introduced into the circulation In system, when the condensation temperature of working medium is increased to close with the operating temperature of engine cooling system, cooling system is utilized Heat realizes that the evaporation of working medium can be further improved superheated steam with the heat steam generation superheated steam of exhaust Temperature improves the generating capacity of turbogenerator；Condenser is cooled down using the cooling wind of cooling system simultaneously.In existing component Engine exhaust heat generation technology is applied on Tank and Armoured Vehicle under the premise of volume, limited mass are increased, improves engine Fuel energy utilization rate so that improve the performance of engine and the performance of vehicle.
2, condenser of the present invention uses belt concurrent flow aluminium pipe structure, the compact coefficient of belt concurrent flow aluminium pipe structure it is high and It is light-weight, thus compared to raw water radiator space and weight, volume, the weight of condenser do not increase.
Detailed description of the invention
Fig. 1 is Rankine of the present invention (Rankine) systematic schematic diagram；
Fig. 2 is that Rankine of the present invention (Rankine) recycles thermodynamic state Parameter Map；
Wherein, P- water pump, E- evaporator, S- superheater, T- turbine, G- generator, C- condenser, F- blower.
Specific embodiment
The present invention will now be described in detail with reference to the accompanying drawings and examples.
A kind of cooling coupled system with cogeneration of tank armored vehicle engine is present embodiments provided, Rankine is based on (Rankine) it recycles, including liquid working substance, water pump P, evaporator E, superheater S, turbine T, generator G, condenser C and original dissipate The blower F of hot systems substitutes the radiator of former cooling system.
As shown in Figure 1, cooling is as follows with the coupling process of cogeneration:
1-2-3 process: water pump P drives liquid working substance to flow into evaporator E, and evaporator E is using engine coolant as heat source, liquid It is evaporated to steam after the heat of body working medium absorption engine coolant, steam flows into superheater S, and superheater S is arranged with engine Gas is heat source, enables the heat of vapor absorption engine exhaust, becomes high temperature super heated steam, this process is isobaric heat absorption process, is related to And Thermodynamics Formulas are as follows:
The heat Q that working medium sucks in evaporator E are as follows:
Q=m (h3-h1) (1)
M is working medium quality, h in formula1、h3For specific steam enthalpy under the operating condition.
The heat dissipation capacity for absorbing engine-cooling system is evaporated for working medium:
Q1-1=mL (2)
M is working medium quality in formula, and L is the enthalpy that gasifies under the operating condition.
The heat dissipation capacity of engine coolant:
Q1=m1·Cp1·(t11-t12) (3)
M in formula1For engine cool water quality, Cp1For cooling water specific heat, t11、t12Water temperature is passed in and out for cooling water.
Heat Q1It is transmitted and is completed by evaporator E, heat exchange amount:
Q1=K1·F1·Δtm1=Q1-1 (4)
K in formula1For evaporator heat transfer coefficient, F1For evaporator heat transfer area, Δ tm1For heat transfer temperature difference.
Engine exhaust heat is absorbed to the heat of working medium into superheated steam:
Q1-2=m (h3-h2) (5)
M is working medium quality, h in formula2、h3For specific steam enthalpy under the operating condition.
The heat dissipation capacity of engine exhaust:
Qg=mg·Cpg·(t2g-t1g) (6)
M in formulagFor engine exhaust quality, CpgTo be vented specific heat, t2g、t1gTemperature is passed in and out for exhaust.
Heat QgIt is transmitted and is completed by superheater S, heat exchange amount:
Qg=Kg·Fg·Δtmg=Q1-2 (7)
K in formulagFor superheater heat transfer coefficient, FgFor superheater heat transfer area, Δ tmgFor heat transfer temperature difference.
Q=Q1-1+Q1-2 (8)
3-4 process: turbine T is driven by high temperature super heated steam, and generator G is driven externally to do work Wt, it produces electricl energy, steam Temperature reduces, pressure reduces, this process is isentropic expansion process, is related to Thermodynamics Formulas are as follows:
Working medium is externally done work in turbine T are as follows:
Wt=m (h3-h4) (9)
M is working medium quality, h in formula4、h3For specific steam enthalpy under the operating condition.
4-5 process: cooling down condenser C using the blower F of former cooling system, and condenser C is cooling by the steam after acting For saturated liquid working medium, this process is isothermal exothermic process, is related to Thermodynamics Formulas are as follows:
The external heat release of working medium in condenser C
Q2=m (h4-h5) (10)
M is working medium quality, h in formula4、h5For specific steam enthalpy under the operating condition.
The caloric receptivity of cooling air:
Qcg=mcg·Cpcg·(t2cg-t1cg) (11)
M in formulacgFor cooling air quality, CpcgTo be vented specific heat, t2cg、t1cgTemperature is passed in and out for cooling air.
The heat is completed by condenser C transmitting, heat exchange amount:
Q2=K2·F2·Δtm2=Qcg (12)
K in formula2For condenser thermal transfer coefficient, F2For condenser thermal transfer area, Δ tm2For heat transfer temperature difference.
5-1 process: working medium drives through water pump P to be flowed and pressurizes, this process is isentropic Compression process, consumes external input Function；Working medium receives external work
M is working medium quality in formula, and υ ' is worker quality liquid than volume, P5、P4For operating condition point pressure.
Net output work:
W=Wt-Wp (14)
W in formulapTo consume function in turbine T；WTFor output work.
When the result of formula (14) is greater than zero, system operation is effectively that is, external output work disappears greater than system Wasted work.
It is assumed that engine basic parameter: the turbocharged and intercooled diesel engine of rated power 400kW, the capacity under declared working condition 0.7kg/s, turbine T are pressurized 550 DEG C of heel row temperature, cooling system heat dissipation capacity 240kW, cooling water flow 500L/min.Selection is started Machine coolant liquid (working medium side operating pressure is less than 0.1MPa) is used as liquid working substance.
Look into saturated water and saturated vapor thermodynamic property table: corresponding saturation pressure P at 85 DEG C of evaporating point1=0.058MPa, Liquid is than volume υ '1=0.0010326m3/ kg, steam is than volume υ "1=2.8300m3/ kg, liquid specific enthalpy h '1=355.92kJ/ Kg, specific steam enthalpy h "1=2652.1kJ/kg, enthalpy of vaporization (latent heat) L1=2292.6kJ/kg, liquid specific entropy s '1=1.1343kJ/ (kgK), steam specific entropy s "1=7.5459kJ/ (kgK).
The corresponding saturation pressure of 70 DEG C of condensation point degree is P5=0.0312MPa, liquid is than volume υ '5=0.0010228m3/ Kg, steam is than volume υ "5=2.83005.0479m3/ kg, liquid specific enthalpy h '5=292.96kJ/kg, specific steam enthalpy h "5= 2626.8kJ/kg, enthalpy of vaporization (latent heat) L5=2333.8kJ/kg, liquid specific entropy s '5=0.9548kJ/ (kgK), steam specific entropy s”5=7.7565kJ/ (kgK).
Had by 85 DEG C of liquid working substance evaporation and heat-exchange according to formula (2) according to cooling system heat dissipation capacity for 240kW:
M=Q1-1/L1=240/2292.6=0.105kg/s
Setting delivery temperature is reduced to 450 DEG C, is vented specific heat Cpg=1kJ/ (kgK), according to formula (5), (6), (7) It calculates, available:
Qg=mg·Cpg·(t2g-t1g)=0.7 × 1 × (550-450)=70kW
h″3=h "2+ 70/0.105=h "1+ 70/0.105=3318.8kJ/kg
Saturated water and saturated vapor thermodynamic property table 0.05MPa are looked into, superheat steam temperature can be obtained and reach 425 DEG C.
Unsaturated water and superheated steam thermodynamic property table are looked into, the thermodynamic properties of steam under the state are as follows: steam is than volume υ "3 =17.718m3/ kg, steam specific entropy s "3=9.1486kJ/ (kgK).
It is isentropic procedure that steam, which flows through turbine T expansion work, and the end of a period pressure after expansion process is consistent with condensing pressure, is pressed According to steam specific entropy s "4=s "3=9.1486kJ/ (kgK), condensation point pressure P4≈P5=0.0312MPa looks into water and steam h- S scheme (enthalpy-entropy diagram), as shown in Fig. 2, after available expansion steam than enthalpy h "4=2750kJ/kg.
Expansion work is calculated according to formula (9), that is, is used for the output work of driven generator G:
Wt=m (h "3-h″4)=0.105 × (3318.8-2750)=59.724kW
It is such as 0.8 to calculate according to turbine T generating efficiency, then it can generated output are as follows: 0.8 × 59.724=47.78kW
Condensing heat-exchange amount is calculated according to formula (10):
Q=m (h4″-h′5)=0.105 × (2750-292.96)=28kW
Water is insulation isentropic procedure by water pump P compression, and the wasted work of water pump P is calculated according to formula (13):
WP=mv (P1-P4)=0.105 × 0.0010228 × (0.057803-0.031161) × 106=2.86kW
If the efficiency of water pump P is calculated according to 0.9, then water pump P wasted work are as follows: 2.86/0.9=3.18kW
Net output work is calculated according to formula (14):
Do not consider that power generation when efficiency exports only: W=Wt-Wp=59.724-2.86=56.864kW
Compared with the output power of engine: 56.864/400=0.142=14.2%
Consider the net output power of reality of efficiency: W=Wt-Wp=47.78-3.18=44.60kW
Compared with the output power of engine: 44.60/400=0.112=11.2%
The calculating of evaporator E:
Heat source side (i.e. the outlet of engine cooling water) temperature of evaporator E is calculated according to formula (3):
t12=t11-Q1/(m1·Cp1)=105-240/ (500/60 × 4.18)=98.11 DEG C
Evaporating temperature is 85 DEG C, calculating logarithmic temperature difference are as follows: Δ tm1=16.313 DEG C
It is calculated according to formula (4), the K of evaporator E1·F1=Q1/Δtm1=240/16.313=14.712kW/ DEG C
Because it is water that the heat of evaporator E, which surveys working medium, therefore the Coefficient K of evaporator E1Can achieve 5000W/m2 DEG C with On, i.e. the heat exchange area of evaporator E is not more than 3m2, using aluminum plate fin type structure, volume, the weight of evaporator E compares It is small.
The calculating of superheater S:
Front has obtained, and the exhaust side temperature of superheater S is 550 DEG C of import, 450 DEG C of outlet, the entrance of working substance steam For 85 DEG C, outlet be 425 DEG C, heat exchange amount 70kW.
Logarithmic mean temperature difference (LMTD) is calculated: Δ tmg=223.97 DEG C
It is calculated according to formula (7), the K of superheater Sg·Fg=Qg/Δtmg=70/223.97=0.313kW/ DEG C
The heat transfer coefficient of the heat transfer process of steam and exhaust gas, superheater S is relatively low, according to 50W/m2DEG C calculate, mistake The heat exchange area of hot device S is in 6.26m2, using plate-fin structure, volume, the weight of superheater S is smaller.
The calculating of condenser C:
The cooling fan air quantity of former cooling system is set as 8m3/ s calculates the wind side outlet of condenser C according to formula (11) Temperature:
t2cg=t1cg+Qcg/(mcg·Cpcg)=35+258/ (8 × 1.005)=67.09 DEG C
Condensation temperature is 70 DEG C, calculating logarithmic temperature difference are as follows: Δ tm2=12.902 DEG C
It is calculated according to formula (12), the K of condenser C2·F2=Q2/Δtm2=258/12.902=19.997kW/ DEG C
If being calculated and having been obtained according to front: t using raw water radiator12=98.11 DEG C
The then logarithmic mean temperature difference (LMTD) of water radiator are as follows: t=50.779 DEG C of Δ
T=240/50.779=4.726kW/ DEG C of the KF=Q/ Δ of water radiator
Although the heat transfer coefficient of condenser C can be higher than the heat transfer coefficient of water radiator, found from above-mentioned comparing calculation cold Heat exchange area required for condenser C is still bigger than water radiator, generallys use aluminium sheet for Tank and Armoured Vehicle water radiator Wing formula structure, and condenser C can then use belt concurrent flow aluminium pipe structure, the compact coefficient of belt concurrent flow aluminium pipe structure is wanted It is much higher and light-weight, therefore can be solved in raw water radiator space and weight；Especially if can by evaporating temperature and Condensation temperature improves, it will substantially improves volume, the weight of condenser C.
Comprehensive analysis, can be by the coupled systemes of engine cool and cogeneration using Rankine (Rankine) Cyclical Theory System is applied on the Tank and Armoured Vehicle.
In conclusion the above is merely preferred embodiments of the present invention, being not intended to limit the scope of the present invention. All within the spirits and principles of the present invention, any modification, equivalent replacement, improvement and so on should be included in of the invention Within protection scope.

Claims (3)

1. a kind of cooling coupled system with cogeneration of tank armored vehicle engine, which is characterized in that the coupled system Including liquid working substance, water pump, evaporator, superheater, turbine, generator, condenser and blower；
Liquid working substance is driven into evaporator using water pump, and evaporator heats the liquid work using engine coolant as heat source It is upright to flashing to steam, cooling engine；Steam flows into superheater, and superheater will be steamed using engine exhaust heat as heat source Vapour is heated to overtemperature as superheated steam；Superheated steam drives turbo driving, drives electrical power generators, superheated steam temperature Degree, pressure are decreased as Low Temperature Steam；Low Temperature Steam enters condenser, and by fan radiating, Low Temperature Steam is condensed into liquid Body；Liquid flows into water pump and realizes closed cycle.
2. the cooling coupled system with cogeneration of tank armored vehicle engine as described in claim 1, which is characterized in that The liquid working substance is engine coolant.
3. the cooling coupled system with cogeneration of tank armored vehicle engine as described in claim 1, which is characterized in that The condenser uses belt concurrent flow aluminium pipe structure.
CN201910773781.0A 2019-08-21 2019-08-21 A kind of cooling coupled system with cogeneration of tank armored vehicle engine Pending CN110529283A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113187562A (en) * 2021-04-15 2021-07-30 花潍 Thermal working medium generator

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102192673A (en) * 2010-03-16 2011-09-21 乐金电子(天津)电器有限公司 Flat-tube heat exchanger structure and assembling method thereof
CN102305151A (en) * 2011-08-03 2012-01-04 天津大学 System for efficiently recovering waste heat energy from internal combustion engine
CN102418622A (en) * 2010-09-24 2012-04-18 株式会社丰田自动织机 Rankine cycle system
CN205279535U (en) * 2015-12-16 2016-06-01 广州坤江汽车配件工业制造有限公司 Concurrent flow pipe belt type car condenser
CN108691639A (en) * 2018-04-03 2018-10-23 天津大学 A kind of two turbocharging systems

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102192673A (en) * 2010-03-16 2011-09-21 乐金电子(天津)电器有限公司 Flat-tube heat exchanger structure and assembling method thereof
CN102418622A (en) * 2010-09-24 2012-04-18 株式会社丰田自动织机 Rankine cycle system
CN102305151A (en) * 2011-08-03 2012-01-04 天津大学 System for efficiently recovering waste heat energy from internal combustion engine
CN205279535U (en) * 2015-12-16 2016-06-01 广州坤江汽车配件工业制造有限公司 Concurrent flow pipe belt type car condenser
CN108691639A (en) * 2018-04-03 2018-10-23 天津大学 A kind of two turbocharging systems

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113187562A (en) * 2021-04-15 2021-07-30 花潍 Thermal working medium generator

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Application publication date: 20191203