CN106640247B - A kind of heat power generating system with injector - Google Patents

A kind of heat power generating system with injector Download PDF

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CN106640247B
CN106640247B CN201611207815.2A CN201611207815A CN106640247B CN 106640247 B CN106640247 B CN 106640247B CN 201611207815 A CN201611207815 A CN 201611207815A CN 106640247 B CN106640247 B CN 106640247B
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temperature
working medium
heat source
pipeline
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CN106640247A (en
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张承虎
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张承虎
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K27/00Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01DNON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10Adaptations for driving, or combinations with, electric generators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00General layout or general methods of operation of complete plants
    • F01K13/006Auxiliaries or details not otherwise provided for
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00General layout or general methods of operation of complete plants
    • F01K13/02Controlling, e.g. stopping or starting
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/18Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
    • F01K3/185Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters using waste heat from outside the plant

Abstract

A kind of heat power generating system with injector, the present invention relates to a kind of electricity generation system, the present invention is in order to solve to be difficult to the contradiction coordinated between generating efficiency existing for conventional thermodynamic electricity generation system and comprehensive heat-economy, it includes turbine power generation unit, condenser, reservoir, throttle expansion valve, working medium pump, high-temperature evaporator, cryogenic vaporizer, injector, gas-liquid separator, adjustment heat exchanger, steam superheater, the first working medium pipeline, the second working medium pipeline, the 3rd working medium pipeline, high temperature heat source pipeline and the first low-temperature heat source pipeline, the present invention and is used for power field.

Description

A kind of heat power generating system with injector
Technical field
The present invention relates to a kind of electricity generation system, and in particular to a kind of heat power generating system with injector.
Background technology
Current heat power generating system mainly use Rankine cycle (Rankin Cycle), working medium mainly select water or Organic working medium, such as freon class working medium or alkanes working medium.The generating efficiency of Rankine cycle is except the thermal physical characteristic with working medium Outside matter is closely related, the difference that depends primarily between evaporating temperature and condensation temperature, it is however generally that, evaporating temperature is higher, The generating efficiency of Rankine cycle is higher, and condensation temperature is lower, and the generating efficiency of Rankine cycle is also higher.But in order to pursue Higher generating efficiency and improve evaporating temperature, may result in that the outlet temperature of high temperature heat source is too high, and high-grade thermal waste is tight Weight, reduce condensation temperature to pursue higher generating efficiency, may result in cooling thermal source outlet temperature it is too low, condensation heat No longer there is heat utilization value.This contradiction between the generating efficiency of system and comprehensive heat-economy is given up in utilization more than low temperature It is more common and prominent in the organic Rankine cycle power generation system of heat.
From the point of view of generated energy, the generated energy of Rankine cycle depends primarily on caloric receptivity and the generating of working medium evaporation process The product of efficiency, it is however generally that, generating efficiency is higher, and the generated energy of Rankine cycle is more, the caloric receptivity of working medium evaporation process More, the generated energy of Rankine cycle is also more.It is seen that even if the decrease of power generation of system some, but if can Realize that the caloric receptivity of working medium evaporation process is significantly increased, and can safeguards system gross generation it is constant, or even system is total What generated energy was increased slightly.This is difficult to the lance coordinated between the generating efficiency of solution heat power generating system and comprehensive heat-economy Shield provides a kind of new resolving ideas.
The content of the invention
The present invention is in order to solve to be difficult to assist between generating efficiency existing for conventional thermodynamic electricity generation system and comprehensive heat-economy The contradiction of tune, and then a kind of heat power generating system with injector is provided.
It is of the invention to be for the technical scheme used that solves the above problems:
1st, it includes turbine power generation unit, condenser, reservoir, throttle expansion valve, working medium pump, high-temperature evaporator, low temperature Evaporator, injector, gas-liquid separator, adjustment heat exchanger, steam superheater, the first working medium pipeline, the second working medium pipeline, the 3rd Working medium pipeline, high temperature heat source pipeline and the first low-temperature heat source pipeline, the first low-temperature heat source pipeline change with condenser and adjustment successively Hot device connects and passes through adjustment heat exchanger to set, and high temperature heat source pipeline exchanges heat with steam superheater, high-temperature evaporator, adjustment successively Device connects with cryogenic vaporizer and passes through cryogenic vaporizer to set, and the arrival end of the port of export of injector and the 3rd working medium pipeline connects Logical, the 3rd working medium pipeline divides with steam superheater, turbine power generation unit, condenser, reservoir, cryogenic vaporizer and gas-liquid successively Arrival end from device is connected, and throttle expansion valve is arranged on the 3rd working medium pipeline between reservoir and cryogenic vaporizer, gas-liquid Separator connects with the first working medium pipeline arrival end and the second working medium pipeline arrival end respectively, working medium pipeline successively with working medium pump, High-temperature evaporator connects with the injection Working-fluid intaking end of injector, the second working medium tube outlet end and injector by injection Fluid inlet end connects.
2nd, it includes turbine power generation unit, condenser, reservoir, throttle expansion valve, working medium pump, high-temperature evaporator, low temperature Evaporator, injector, gas-liquid separator, adjustment heat exchanger, steam superheater, the first working medium pipeline, the second working medium pipeline, the 3rd Working medium pipeline, high temperature heat source pipeline, the first low-temperature heat source pipeline, the second low-temperature heat source pipeline, the 3rd low-temperature heat source pipeline and Four low-temperature heat source pipelines, the first low-temperature heat source pipeline arrival end and the 3rd Low Temperature Thermal source capsule with the second low-temperature heat source pipeline respectively Road with arrival end connect, arrival end of the 3rd low-temperature heat source pipeline successively with condenser and the 4th low-temperature heat source pipeline connects, Second low-temperature heat source pipeline connects with adjustment heat exchanger and the arrival end of the 4th low-temperature heat source pipeline successively, high temperature heat source pipeline according to It is secondary to be connected with steam superheater, high-temperature evaporator, adjustment heat exchanger and cryogenic vaporizer and pass through cryogenic vaporizer to set, injection The port of export of device connects with the arrival end of the 3rd working medium pipeline, the 3rd working medium pipeline successively with steam superheater, turbine generators Group, condenser, reservoir, cryogenic vaporizer connect with the arrival end of gas-liquid separator, throttle expansion valve be arranged on reservoir with On the 3rd working medium pipeline between cryogenic vaporizer, gas-liquid separator respectively with the first working medium pipeline arrival end and the second working medium tube The connection of road arrival end, the first working medium pipeline injection Working-fluid intaking end with working medium pump, high-temperature evaporator and injector successively Connection, the second working medium tube outlet end connects with the driven fluid arrival end of injector.
3rd, it includes turbine power generation unit, condenser, reservoir, throttle expansion valve, working medium pump, high-temperature evaporator, low temperature Evaporator, injector, gas-liquid separator, adjustment heat exchanger, steam superheater, the first working medium pipeline, the second working medium pipeline, the 3rd Working medium pipeline, high temperature heat source pipeline and the first low-temperature heat source pipeline, the first low-temperature heat source pipeline change with condenser and adjustment successively Hot device connects and passes through adjustment heat exchanger to set, and high temperature heat source pipeline exchanges heat with steam superheater, high-temperature evaporator, adjustment successively Device connects with cryogenic vaporizer and passes through cryogenic vaporizer to set, and the arrival end of the port of export of injector and the 3rd working medium pipeline connects It is logical, the 3rd working medium pipeline successively with steam superheater, turbine power generation unit, condenser, reservoir, working medium pump, high-temperature evaporator Connected with the arrival end of gas-liquid separator, gas-liquid separator respectively with the first working medium pipeline arrival end and the second working medium line entry End connection, the first working medium pipeline connects with the injection Working-fluid intaking end of injector, the second working medium tube outlet end successively with Cryogenic vaporizer connects with the driven fluid entrance of injector, and throttle expansion valve is arranged on gas-liquid separator and cryogenic vaporizer Between the second working medium pipeline on.
4th, it includes turbine power generation unit, condenser, reservoir, throttle expansion valve, working medium pump, high-temperature evaporator, low temperature Evaporator, injector, gas-liquid separator, adjustment heat exchanger, steam superheater, the first working medium pipeline, the second working medium pipeline, the 3rd Working medium pipeline, high temperature heat source pipeline, the first low-temperature heat source pipeline, the second low-temperature heat source pipeline, the 3rd low-temperature heat source pipeline and Four low-temperature heat source pipelines, the first low-temperature heat source pipeline arrival end and the 3rd Low Temperature Thermal source capsule with the second low-temperature heat source pipeline respectively Road with arrival end connect, arrival end of the 3rd low-temperature heat source pipeline successively with condenser and the 4th low-temperature heat source pipeline connects, Second low-temperature heat source pipeline connects with adjustment heat exchanger and the arrival end of the 4th low-temperature heat source pipeline successively, high temperature heat source pipeline according to It is secondary to be connected with steam superheater, high-temperature evaporator, adjustment heat exchanger and cryogenic vaporizer and pass through cryogenic vaporizer to set, injection The port of export of device connects with the arrival end of the 3rd working medium pipeline, the 3rd working medium pipeline successively with steam superheater, turbine generators Group, condenser, reservoir, working medium pump, high-temperature evaporator connect with the arrival end of gas-liquid separator, and gas-liquid separator is respectively with The injection working fluid of one working medium pipeline arrival end and the connection of the second working medium pipeline arrival end, the first working medium pipeline and injector enters The connection of mouth end, driven fluid arrival end of the second working medium pipeline successively with cryogenic vaporizer and injector connect, throttling expansion Valve is arranged on the second working medium pipeline between gas-liquid separator and cryogenic vaporizer.
The beneficial effects of the invention are as follows:
Although the 1, the present invention reduces the inlet pressure of turbine power generation unit 1, the generating efficiency of system is reduced, greatly Width reduces the outlet temperature of high temperature heat source, adds the caloric receptivity of working medium evaporation, can be in identical high temperature heat source and low temperature Under conditions of thermal source flow and inlet temperature, realize that generating total amount is constant or even is increased slightly, especially the present invention can increase The outlet temperature of high temperature heat source can be greatly reduced in the temperature levels of low-temperature heat source, the present invention, in safeguards system gross generation not Under conditions of change, the temperature levels of cooling thermal source, the value of increase generating discharge used heat and the synthesis of system are greatly improved Heat-economy, so a kind of protect electric temperature-increasing type heat power generating system, " protecting electricity " refers to ensure that gross generation is not reduced, and " heating " is Refer to the temperature levels of increase cooling thermal source, in order to lift the synthesis heat-economy of whole heat power generating system.
2nd, before injector 8 is placed in turbine power generation unit 1 by the present invention, the suction energy of high-pressure working medium steam is made full use of Power, lower evaporating pressure and evaporating temperature can be created in cryogenic vaporizer 7, so as to more greatly reduce high temperature heat source Outlet temperature, fully seize high temperature heat source heat energy be used for generate electricity.
3rd, the present invention is provided with gas-liquid separator 9, and is disposed between high-temperature evaporator 6 and cryogenic vaporizer 7 In pipe-line system, it can adaptively meet the working medium flow distribution between high-temperature evaporator 6 and cryogenic vaporizer 7, fully protect The steady operation of card system, reduce the control difficulty of system.
4th, the present invention is provided with adjustment heat exchanger 10, both can adaptively meet high-temperature evaporator 6 and cryogenic vaporizer 7 Between heat exchange amount ratio, realize the outlet temperature of lower high temperature heat source, while can also further lift low-temperature heat source Outlet temperature.
5th, present invention could apply to waste-heat power generation project or solar energy project more than middle low temperature, can fully seize The heat energy of remaining used heat, the temperature levels of low-temperature heat source are lifted while ensureing total generate electricity, meet the requirement of conventional heating, generate electricity with Heating kills two birds with one stone.
Brief description of the drawings
Fig. 1 is the overall structure diagram of the scheme of the specific embodiment of the invention one, and Fig. 2 is the specific embodiment of the invention The overall structure diagram of two schemes, Fig. 3 are the overall structure diagrams of the scheme of the specific embodiment of the invention three, and Fig. 4 is this The overall structure diagram of the scheme of invention embodiment four.
Embodiment
Embodiment one:Illustrate present embodiment, a kind of heating power with injector described in present embodiment with reference to Fig. 1 Electricity generation system, it include turbine power generation unit 1, condenser 2, reservoir 3, throttle expansion valve 4, working medium pump 5, high-temperature evaporator 6, Cryogenic vaporizer 7, injector 8, gas-liquid separator 9, adjustment heat exchanger 10, steam superheater 11, the first working medium pipeline 41, second Working medium pipeline 42, the 3rd working medium pipeline 43, the low-temperature heat source pipeline 51 of high temperature heat source pipeline 61 and first, the first low-temperature heat source pipeline 51 successively with condenser 2 and adjustment heat exchanger 10 connect and through adjustment heat exchanger 10 set, high temperature heat source pipeline 61 successively with Steam superheater 11, high-temperature evaporator 6, adjustment heat exchanger 10 are connected with cryogenic vaporizer 7 and set through cryogenic vaporizer 7, The port of export of injector 8 connects with the arrival end of the 3rd working medium pipeline 43, the 3rd working medium pipeline 43 successively with steam superheater 11, Turbine power generation unit 1, condenser 2, reservoir 3, cryogenic vaporizer 7 connect with the arrival end of gas-liquid separator 9, throttle expansion valve 4 are arranged on the 3rd working medium pipeline 43 between reservoir 3 and cryogenic vaporizer 7, gas-liquid separator 9 respectively with the first working medium tube The arrival end of road 41 and the arrival end of the second working medium pipeline 42 connection, the first working medium pipeline 41 successively with working medium pump 5, high-temperature evaporator 6 Connected with the injection Working-fluid intaking end of injector 8, the driven fluid of the port of export of the second working medium pipeline 42 and injector 8 enters The connection of mouth end.
The thermodynamic cycle process of present embodiment working medium:Reservoir 3 collects the liquid refrigerant of condensation, and liquid refrigerant is in pressure difference Driving under, by entering cryogenic vaporizer 7, the liquid refrigerant quilt in cryogenic vaporizer 7 after the reducing pressure by regulating flow of throttle expansion valve 4 High temperature heat source heating and explosive evaporation, carry out gas-liquid separation, the liquid refrigerant after separation is by working medium into gas-liquid separator 9 afterwards Entering high-temperature evaporator 6 after the driving boosting of pump 5, liquid refrigerant heats simultaneously explosive evaporation by high temperature heat source in high-temperature evaporator 6, Caused high-pressure working medium steam enters injector 8 and is used as injection working fluid, and injection is divided by gas-liquid separator 9 in injector 8 The low pressure working fluid steam come is separated out, the middle pressure working substance steam that injector 8 exports is carried out into steam superheater 11 by high temperature heat source After heating, expansion work and generating are carried out into turbine power generation unit 1 is interior, condenser 2 is entered back into after decrease temperature and pressure, is condensing Gaseous working medium is cooled down by low-temperature heat source and condensed in device 2, and the liquid refrigerant after condensing enters reservoir 3, so just constitutes work The thermodynamic cycle of matter.Injector 8 and throttle expansion valve 4 have built the environment under low pressure of cryogenic vaporizer 7 and gas-liquid separator 9, draw Emitter 8 and working medium pump 5 have built the hyperbaric environment of high-temperature evaporator 6.
The exothermic process of high temperature heat source:High temperature heat source enters system by high temperature heat source pipeline 61, first in steam superheating Heat release in device 11, the middle pressure working substance steam that heating injector 8 exports can increase the sensible heat amount of working substance steam and follow-up generating Amount, while high temperature heat source realizes and cooled for the first time that high temperature heat source heat release in high-temperature evaporator 6 afterwards, heating high-pressure working medium makes Explosive evaporation, while high temperature heat source realizes that second cools, and high temperature heat source heat release in adjustment heat exchanger 10, heating are low afterwards Temperature-heat-source is allowed to heat up, while high temperature heat source realizes that third time cools, and the heat release in cryogenic vaporizer 7 of final high temperature thermal source, adds Heat low working medium is allowed to explosive evaporation, while high temperature heat source realizes the 4th cooling.High temperature heat source for the first time, second and the 4th The discharged heat of secondary cooling is generated electricity into system, ensures that gross generation meets to require, cool discharged heat for the third time The heating for low-temperature heat source is measured, improves the temperature levels of low-temperature heat source.
The endothermic process of low-temperature heat source:Low-temperature heat source enters system by the first low-temperature heat source pipeline 51, is condensing first Absorbed heat in device 2, condense the working substance steam after expansion work, while realize the first time heating of low-temperature heat source, afterwards Low Temperature Thermal Source is absorbed heat in adjustment heat exchanger 10, and the temperature for reducing high temperature heat source is allowed to the temperature requirement for meeting working medium thermodynamic cycle, simultaneously Realize second of heating of low-temperature heat source.The temperature levels of low-temperature heat source can have more values and synthesis after improving Heat-economy.
The high temperature heat source applied in the present invention can be industrial exhaust steam, the waste gas or flue gas that more than 150 DEG C of high temperature, middle height The liquid water that more than 100 DEG C of temperature, oil etc., or collection heat carrier of solar energy etc..Low-temperature heat source is primarily referred to as water.Working medium can To use water, freon class working medium, or alkanes working medium.
When the inlet temperature of low-temperature heat source is relatively low, it is adapted to use the present embodiment.
The reasons why injector 8 is arranged at into turbine power generation 1 upstream of unit is as follows:Most working medium have following hot thing Rationality matter rule, i.e., when saturation temperature level is higher, the difference of the saturation pressure corresponding to the difference of identical saturation temperature will be got over Greatly, for example, water temperature to be 50 DEG C with the saturation pressure difference corresponding to 40 DEG C be 0.12335-0.07375=0.04960bar, and water temperature is 120 DEG C are 1.9854-1.4327=0.5527bar with the saturation pressure difference corresponding to 110 DEG C, when stress level is lower in other words, The difference of saturation temperature corresponding to the difference of identical saturation pressure will be bigger.Can also be summarized as stress level it is lower when, pressure Heat quality loss caused by drop is bigger, and when stress level is higher, the heat quality loss caused by pressure drop is just smaller.
Based on this rule, injector 8 is arranged at before turbine power generation unit 1 by the present invention.In order to ensure that injector 8 has Enough ejector capacities, it is necessary to assure meet certain operting differential pressure between the inlet and outlet of injector 8.If injector 8 is set Be placed in after turbine power generation unit 1, because the inlet pressure of injector 8 is relatively low, cause injector 8 inlet and outlet to meet it is identical Operting differential pressure, the condensation temperature of condenser 2 must be greatly reduced, it reduce the heat quality of condensation heat and heat economy valency Value.Lower condensation temperature also improves difficulty for the preparation of low-temperature heat source.If injector 8 is arranged at turbine power generation unit Before 1, because working substance steam pressure is very high, it is easier to meet the requirement of the inlet and outlet operting differential pressure of injector 8, and injection pressure drop Caused heat quality loss is just smaller, and this is more beneficial for the raising of system overall efficiency.
The reasons why setting steam superheater 11 is as follows:The setting of injector 8 adds the working medium steaming available for expansion power generation The mass flow of vapour, but the pressure into the working substance steam of turbine power generation unit 1 is reduction of, under generating efficiency is caused Drop, but working substance steam expansion power generation rely primarily on be working substance steam sensible heat heat energy, high temperature heat source can pass through steam superheating The middle pressure working substance steam that device 11 exports to injector 8 carries out reheating, increases the sensible heat heat energy of working substance steam, and lifting working medium is steamed The temperature of vapour, the generating efficiency of turbine power generation unit 1 can be so improved, partly or entirely offset caused by pressure reduces Generating efficiency is lost, and the generating efficiency of safeguards system is in higher level.
The reasons why setting gas-liquid separator 9 is as follows:In pipe-line system between high-temperature evaporator 6 and cryogenic vaporizer 7 There is provided gas-liquid separator 9 so that the liquid refrigerant of high-temperature evaporator 6 and cryogenic vaporizer 7 forms the form of series flow, excellent The evaporation traffic demand of cryogenic vaporizer is first ensured, according to the principle of mass conservation, unevaporated liquid refrigerant disclosure satisfy that naturally The evaporation traffic demand of high-temperature evaporator 6, this system architecture, which is set, can adaptively meet that high-temperature evaporator 6 and low temperature steam The working medium flow distribution between device 7 is sent out, fully ensures that the steady operation of system, reduces the control difficulty of system.
The reasons why setting adjustment heat exchanger 10 is as follows:When systems are functioning properly, the state of working medium thermodynamic cycle is clear and definite , i.e. high-temperature evaporator 6 and 7 respective evaporating temperature of cryogenic vaporizer is clear and definite, and heat exchange amount ratio therebetween And clearly.If high temperature heat source is directly entered cryogenic vaporizer 7 after entering high-temperature evaporator 6, it will high warm occurs The temperature drop process in source can not meet the requirement of the evaporating temperature and the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7 simultaneously, So that system can not be realized.
Such as the high temperature heat source inlet temperature of the high-temperature evaporator 6 of requirement of system design is 155 DEG C, outlet temperature 35 DEG C, the evaporating temperature of high-temperature evaporator 6 is 100 DEG C, and the evaporating temperature of cryogenic vaporizer 7 is 30 DEG C, high-temperature evaporator 6 and low temperature Heat exchange amount ratio between evaporator 7 is 10:6, then if high temperature heat source is directly entered low temperature after entering high-temperature evaporator 6 Evaporator 7, then maximum temperature drop of the high temperature heat source in high-temperature evaporator 6 is 55 DEG C, is 65 in the minimum temperature drop of cryogenic vaporizer 7 DEG C, it is that can not meet that the ratio between heat exchange amount is 10 anyway:6 requirement.
Therefore increase on high temperature heat source pipeline 61 of the present invention between high-temperature evaporator 6 and cryogenic vaporizer 7 and be provided with Heat exchanger 10 is adjusted, it can be adaptively adjusted the inlet temperature of the high temperature heat source of cryogenic vaporizer 7, realize cryogenic heat exchanger The regulation of 7 heat exchange amounts so that the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7 meets the requirement of thermodynamic cycle.
Still above-mentioned example is directed to, it is 105 DEG C that design high-temperature evaporator 6, which exports high temperature heat source temperature, increase adjustment heat exchange After device 10, adjustment heat exchanger 10, which exports high temperature heat source temperature, can be adjusted to 65 DEG C, the outlet high temperature heat source of cryogenic vaporizer 7 Temperature is 35 DEG C, then temperature drop of the high temperature heat source in high-temperature evaporator 6 is 50 DEG C, and the temperature drop in cryogenic vaporizer 7 is 30 DEG C, Ignore the ratio thermal change of high temperature heat source, then it is 10 that can meet the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7:6 The requirement of thermodynamic cycle.
Embodiment two:Illustrate present embodiment, a kind of heating power with injector described in present embodiment with reference to Fig. 2 Electricity generation system, it include turbine power generation unit 1, condenser 2, reservoir 3, throttle expansion valve 4, working medium pump 5, high-temperature evaporator 6, Cryogenic vaporizer 7, injector 8, gas-liquid separator 9, adjustment heat exchanger 10, steam superheater 11, the first working medium pipeline 41, second Working medium pipeline 42, the 3rd working medium pipeline 43, high temperature heat source pipeline 61, the first low-temperature heat source pipeline 51, the second low-temperature heat source pipeline 52nd, the 3rd low-temperature heat source pipeline 53 and the 4th low-temperature heat source pipeline 54, the first low-temperature heat source pipeline 51 respectively with the second Low Temperature Thermal The arrival end on source capsule road 52 and the 3rd low-temperature heat source pipeline 53 with arrival end connect, the 3rd low-temperature heat source pipeline 53 successively with it is cold Condenser 2 connects with the arrival end of the 4th low-temperature heat source pipeline 54, the second low-temperature heat source pipeline 52 successively with adjustment heat exchanger 10 and 4th low-temperature heat source pipeline 54 arrival end connection, high temperature heat source pipeline 61 successively with steam superheater 11, high-temperature evaporator 6, Adjustment heat exchanger 10 is connected with cryogenic vaporizer 7 and set through cryogenic vaporizer 7, the port of export of injector 8 and the 3rd working medium Pipeline 43 arrival end connection, the 3rd working medium pipeline 43 successively with steam superheater 11, turbine power generation unit 1, condenser 2, storage Liquid device 3, cryogenic vaporizer 7 connect with the arrival end of gas-liquid separator 9, and throttle expansion valve 4 is arranged on reservoir 3 and low-temperature evaporation On the 3rd working medium pipeline 43 between device 7, gas-liquid separator 9 respectively with the arrival end of the first working medium pipeline 41 and the second working medium pipeline 42 arrival ends connect, and the first working medium pipeline 41 enters with the injection working fluid of working medium pump 5, high-temperature evaporator 6 and injector 8 successively The connection of mouth end, the port of export of the second working medium pipeline 42 connect with the driven fluid arrival end of injector 8.
The difference of present embodiment and embodiment one is that low-temperature heat source is entered by the first low-temperature heat source pipeline 51 It is divided into two-way after system, is absorbed heat all the way by the 3rd low-temperature heat source pipeline 53 in condenser 2, condense the work after expansion work Matter steam, while the temperature lifting of the road low-temperature heat source is realized, another way is exchanged heat by the second low-temperature heat source pipeline 52 in adjustment Absorbed heat in device 10, the temperature for reducing high temperature heat source is allowed to the temperature requirement for meeting thermodynamic cycle, while realizes the road low-temperature heat source Temperature lifting, the two-way low-temperature heat source after heating up, which finally converges, is incorporated to the 4th low-temperature heat source pipeline 54 and outflow system.
The thermodynamic cycle process of present embodiment working medium:Reservoir 3 collects the liquid refrigerant of condensation, and liquid refrigerant is in pressure difference Driving under, by entering cryogenic vaporizer 7, the liquid refrigerant quilt in cryogenic vaporizer 7 after the reducing pressure by regulating flow of throttle expansion valve 4 High temperature heat source heating and explosive evaporation, carry out gas-liquid separation, the liquid refrigerant after separation is by working medium into gas-liquid separator 9 afterwards Entering high-temperature evaporator 6 after the driving boosting of pump 5, liquid refrigerant heats simultaneously explosive evaporation by high temperature heat source in high-temperature evaporator 6, Caused high-pressure working medium steam enters injector 8 and is used as injection working fluid, and injection is divided by gas-liquid separator 9 in injector 8 The low pressure working fluid steam come is separated out, the middle pressure working substance steam that injector 8 exports is carried out into steam superheater 11 by high temperature heat source After heating, expansion work and generating are carried out into turbine power generation unit 1 is interior, condenser 2 is entered back into after decrease temperature and pressure, is condensing Gaseous working medium is cooled down by low-temperature heat source and condensed in device 2, and the liquid refrigerant after condensing enters reservoir 3, so just constitutes work The thermodynamic cycle of matter.Injector 8 and throttle expansion valve 4 have built the environment under low pressure of cryogenic vaporizer 7 and gas-liquid separator 9, draw Emitter 8 and working medium pump 5 have built the hyperbaric environment of high-temperature evaporator 6.
The exothermic process of high temperature heat source:High temperature heat source enters system by high temperature heat source pipeline 61, first in steam superheating Heat release in device 11, the middle pressure working substance steam that heating injector 8 exports can increase the sensible heat amount of working substance steam and follow-up generating Amount, while high temperature heat source realizes and cooled for the first time that high temperature heat source heat release in high-temperature evaporator 6 afterwards, heating high-pressure working medium makes Explosive evaporation, while high temperature heat source realizes that second cools, and high temperature heat source heat release in adjustment heat exchanger 10, heating are low afterwards Temperature-heat-source is allowed to heat up, while high temperature heat source realizes that third time cools, and the heat release in cryogenic vaporizer 7 of final high temperature thermal source, adds Heat low working medium is allowed to explosive evaporation, while high temperature heat source realizes the 4th cooling.High temperature heat source for the first time, second and the 4th The discharged heat of secondary cooling is generated electricity into system, ensures that gross generation meets to require, cool discharged heat for the third time The heating for low-temperature heat source is measured, improves the temperature levels of low-temperature heat source.
When the inlet temperature of low-temperature heat source is higher, it is adapted to use the present embodiment.Because when the import temperature of low-temperature heat source When spending higher, it will to adjust heat exchanger using being connected in series still by condenser 2 and adjustment heat exchanger 10 in Low Temperature Thermal source 10 low-temperature heat source inlet temperature is too high and loses accommodation function, and still condenser 2 and adjustment exchange heat in Low Temperature Thermal source Device 10 can avoid the problem using being connected in series.
The high temperature heat source applied in the present invention can be industrial exhaust steam, the waste gas or flue gas that more than 150 DEG C of high temperature, middle height The liquid water that more than 100 DEG C of temperature, oil etc., or collection heat carrier of solar energy etc..Low-temperature heat source is primarily referred to as water.Working medium can To use water, freon class working medium, or alkanes working medium.
The reasons why injector 8 is arranged at into turbine power generation 1 upstream of unit is as follows:Most working medium have following hot thing Rationality matter rule, i.e., when saturation temperature level is higher, the difference of the saturation pressure corresponding to the difference of identical saturation temperature will be got over Greatly, for example, water temperature to be 50 DEG C with the saturation pressure difference corresponding to 40 DEG C be 0.12335-0.07375=0.04960bar, and water temperature is 120 DEG C are 1.9854-1.4327=0.5527bar with the saturation pressure difference corresponding to 110 DEG C, when stress level is lower in other words, The difference of saturation temperature corresponding to the difference of identical saturation pressure will be bigger.Can also be summarized as stress level it is lower when, pressure Heat quality loss caused by drop is bigger, and when stress level is higher, the heat quality loss caused by pressure drop is just smaller.
Based on this rule, injector 8 is arranged at the upstream of turbine power generation unit 1 by the present invention.In order to ensure that injector 8 has There are enough ejector capacities, it is necessary to assure meet certain operting differential pressure between the inlet and outlet of injector 8.If by injector 8 It is arranged at after turbine power generation unit 1, because the inlet pressure of injector 8 is relatively low, causes the inlet and outlet of injector 8 to meet phase Same operting differential pressure, must be greatly reduced the condensation temperature of condenser 2, it reduce the heat quality of condensation heat and heat economy Value.Lower condensation temperature also improves difficulty for the preparation of low-temperature heat source.If injector 8 is arranged at turbine generators Before group 1, because working substance steam pressure is very high, it is easier to meet the requirement of the inlet and outlet operting differential pressure of injector 8, and injection pressure Heat quality loss caused by drop is just smaller, and this is more beneficial for the raising of system overall efficiency.
The reasons why setting steam superheater 11 is as follows:The setting of injector 8 adds the working medium steaming available for expansion power generation The mass flow of vapour, but the pressure into the working substance steam of turbine power generation unit 1 is reduction of, under generating efficiency is caused Drop, but working substance steam expansion power generation rely primarily on be working substance steam sensible heat heat energy, high temperature heat source can pass through steam superheating The middle pressure working substance steam that device 11 exports to injector 8 carries out reheating, increases the sensible heat heat energy of working substance steam, and lifting working medium is steamed The temperature of vapour, the generating efficiency of turbine power generation unit 1 can be so improved, partly or entirely offset caused by pressure reduces Generating efficiency is lost, and the generating efficiency of safeguards system is in higher level.
The reasons why setting gas-liquid separator 9 is as follows:In pipe-line system between high-temperature evaporator 6 and cryogenic vaporizer 7 There is provided gas-liquid separator 9 so that the liquid refrigerant of high-temperature evaporator 6 and cryogenic vaporizer 7 forms the form of series flow, excellent The evaporation traffic demand of cryogenic vaporizer is first ensured, according to the principle of mass conservation, unevaporated liquid refrigerant disclosure satisfy that naturally The evaporation traffic demand of high-temperature evaporator 6, this system architecture, which is set, can adaptively meet that high-temperature evaporator 6 and low temperature steam The working medium flow distribution between device 7 is sent out, fully ensures that the steady operation of system, reduces the control difficulty of system.
The reasons why setting adjustment heat exchanger 10 is as follows:When systems are functioning properly, the state of working medium thermodynamic cycle is clear and definite , i.e. high-temperature evaporator 6 and 7 respective evaporating temperature of cryogenic vaporizer is clear and definite, and heat exchange amount ratio therebetween And clearly.If high temperature heat source is directly entered cryogenic vaporizer 7 after entering high-temperature evaporator 6, it will high warm occurs The temperature drop process in source can not meet the requirement of the evaporating temperature and the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7 simultaneously, So that system can not be realized.
Such as the high temperature heat source inlet temperature of the high-temperature evaporator 6 of requirement of system design is 155 DEG C, outlet temperature 35 DEG C, the evaporating temperature of high-temperature evaporator 6 is 100 DEG C, and the evaporating temperature of cryogenic vaporizer 7 is 30 DEG C, high-temperature evaporator 6 and low temperature Heat exchange amount ratio between evaporator 7 is 10:6, then if high temperature heat source is directly entered low temperature after entering high-temperature evaporator 6 Evaporator 7, then maximum temperature drop of the high temperature heat source in high-temperature evaporator 6 is 55 DEG C, is 65 in the minimum temperature drop of cryogenic vaporizer 7 DEG C, it is that can not meet that the ratio between heat exchange amount is 10 anyway:6 requirement.
Therefore increase on high temperature heat source pipeline 61 of the present invention between high-temperature evaporator 6 and cryogenic vaporizer 7 and be provided with Heat exchanger 10 is adjusted, it can be adaptively adjusted the inlet temperature of the high temperature heat source of cryogenic vaporizer 7, realize cryogenic heat exchanger The regulation of 7 heat exchange amounts so that the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7 meets the requirement of thermodynamic cycle.
Still above-mentioned example is directed to, it is 105 DEG C that design high-temperature evaporator 6, which exports high temperature heat source temperature, increase adjustment heat exchange After device 10, adjustment heat exchanger 10, which exports high temperature heat source temperature, can be adjusted to 65 DEG C, the outlet high temperature heat source of cryogenic vaporizer 7 Temperature is 35 DEG C, then temperature drop of the high temperature heat source in high-temperature evaporator 6 is 50 DEG C, and the temperature drop in cryogenic vaporizer 7 is 30 DEG C, Ignore the ratio thermal change of high temperature heat source, then it is 10 that can meet the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7:6 The requirement of thermodynamic cycle.
Embodiment three:Illustrate present embodiment, a kind of heating power with injector described in present embodiment with reference to Fig. 3 Electricity generation system, it include turbine power generation unit 1, condenser 2, reservoir 3, throttle expansion valve 4, working medium pump 5, high-temperature evaporator 6, Cryogenic vaporizer 7, injector 8, gas-liquid separator 9, adjustment heat exchanger 10, steam superheater 11, the first working medium pipeline 41, second Working medium pipeline 42, the 3rd working medium pipeline 43, the low-temperature heat source pipeline 51 of high temperature heat source pipeline 61 and first, the first low-temperature heat source pipeline 51 successively with condenser 2 and adjustment heat exchanger 10 connect and through adjustment heat exchanger 10 set, high temperature heat source pipeline 61 successively with Steam superheater 11, high-temperature evaporator 6, adjustment heat exchanger 10 are connected with cryogenic vaporizer 7 and set through cryogenic vaporizer 7, The port of export of injector 8 connects with the arrival end of the 3rd working medium pipeline 43, the 3rd working medium pipeline 43 successively with steam superheater 11, Turbine power generation unit 1, condenser 2, reservoir 3, working medium pump 5, high-temperature evaporator 6 connect with the arrival end of gas-liquid separator 9, gas Liquid/gas separator 9 connects with the arrival end of the first working medium pipeline 41 and the arrival end of the second working medium pipeline 42 respectively, the first working medium pipeline 41 Connected with the injection Working-fluid intaking end of injector 8, the port of export of the second working medium pipeline 42 successively with cryogenic vaporizer 7 and injection The driven fluid entrance of device 8 connects, and throttle expansion valve 4 is arranged on the second working medium between gas-liquid separator 9 and cryogenic vaporizer 7 On pipeline 42.
The endothermic process of low-temperature heat source:Low-temperature heat source enters system by the first low-temperature heat source pipeline 51, is condensing first Absorbed heat in device 2, condense the working substance steam after expansion work, while realize the first time heating of low-temperature heat source, afterwards Low Temperature Thermal Source is absorbed heat in adjustment heat exchanger 10, and the temperature for reducing high temperature heat source is allowed to the temperature requirement for meeting working medium thermodynamic cycle, simultaneously Realize second of heating of low-temperature heat source.The temperature levels of low-temperature heat source can have more values and synthesis after improving Heat-economy.
The high temperature heat source applied in the present invention can be industrial exhaust steam, the waste gas or flue gas of high temperature (more than 150 DEG C), in The liquid water of high temperature (more than 100 DEG C), oil etc., or collection heat carrier of solar energy etc..Low-temperature heat source is primarily referred to as water.Work Matter can use water, freon class working medium, or alkanes working medium.
When the inlet temperature of low-temperature heat source is relatively low, it is adapted to use the present embodiment.
The thermodynamic cycle process of working medium:Reservoir 3 collects the liquid refrigerant of condensation, and liquid refrigerant drives liter by working medium pump 5 Enter high-temperature evaporator 6 after pressure, liquid refrigerant heats simultaneously explosive evaporation by high temperature heat source in high-temperature evaporator 6, enters afterwards Gas-liquid separator 9 carries out gas-liquid separation, and the liquid refrigerant after separation after the reducing pressure by regulating flow of restriction expansion device 4 by entering low temperature Evaporator 7, liquid refrigerant heats simultaneously explosive evaporation by high temperature heat source in cryogenic vaporizer 7, what gas-liquid separator 9 was separated High-pressure working medium steam enters injector 8 and is used as injection working fluid, and injection evaporates generation by cryogenic vaporizer 7 in injector 8 Low-pressure steam, injector 8 export middle pressure working substance steam heated into steam superheater 11 by high temperature heat source after, entrance Expansion work and generating are carried out in turbine power generation unit 1, enters back into condenser 2 after decrease temperature and pressure, the gaseous state work in condenser 2 Matter is cooled down by low-temperature heat source and condensed, and the liquid refrigerant after condensing enters reservoir 3, and the heating power for so just constituting working medium follows Ring.Injector 8 and restriction expansion device 4 have built the environment under low pressure of cryogenic vaporizer 7, and injector 8 and working medium pump 5 have built height The hyperbaric environment of warm evaporator 6 and gas-liquid separator 9.
The exothermic process of high temperature heat source:High temperature heat source enters system by high temperature heat source pipeline 61, first in steam superheating Heat release in device 11, the middle pressure working substance steam that heating injector 8 exports (can increase the sensible heat amount of working substance steam and follow-up generating Amount), while high temperature heat source realizes and cooled for the first time that high temperature heat source heat release in high-temperature evaporator 6 afterwards, heating high-pressure working medium makes Explosive evaporation, while high temperature heat source realizes that second cools, and high temperature heat source heat release in adjustment heat exchanger 10, heating are low afterwards Temperature-heat-source is allowed to heat up, while high temperature heat source realizes that third time cools, and the heat release in cryogenic vaporizer 7 of final high temperature thermal source, adds Heat low working medium is allowed to explosive evaporation, while high temperature heat source realizes the 4th cooling.High temperature heat source for the first time, second and the 4th The discharged heat of secondary cooling is generated electricity into system, ensures that gross generation meets to require, cool discharged heat for the third time The heating for low-temperature heat source is measured, improves the temperature levels of low-temperature heat source.
The reasons why injector 8 is arranged at into turbine power generation 1 upstream of unit is as follows:Most working medium have following hot thing Rationality matter rule, i.e., when saturation temperature level is higher, the difference of the saturation pressure corresponding to the difference of identical saturation temperature will be got over Greatly, for example, water temperature to be 50 DEG C with the saturation pressure difference corresponding to 40 DEG C be 0.12335-0.07375=0.04960bar, and water temperature is 120 DEG C are 1.9854-1.4327=0.5527bar with the saturation pressure difference corresponding to 110 DEG C, when stress level is lower in other words, The difference of saturation temperature corresponding to the difference of identical saturation pressure will be bigger.Can also be summarized as stress level it is lower when, pressure Heat quality loss caused by drop is bigger, and when stress level is higher, the heat quality loss caused by pressure drop is just smaller.
Based on this rule, injector 8 is arranged at the upstream of turbine power generation unit 1 by the present invention.In order to ensure that injector 8 has There are enough ejector capacities, it is necessary to assure meet certain operting differential pressure between the inlet and outlet of injector 8.If by injector 8 It is arranged at after turbine power generation unit 1, because the inlet pressure of injector 8 is relatively low, causes the inlet and outlet of injector 8 to meet phase Same operting differential pressure, must be greatly reduced the condensation temperature of condenser 2, it reduce the heat quality of condensation heat and heat economy Value.Lower condensation temperature also improves difficulty for the preparation of low-temperature heat source.If injector 8 is arranged at turbine generators Before group 1, because working substance steam pressure is very high, it is easier to meet the requirement of the inlet and outlet operting differential pressure of injector 8, and injection pressure Heat quality loss caused by drop is just smaller, and this is more beneficial for the raising of system overall efficiency.
The reasons why setting steam superheater 11 is as follows:The setting of injector 8 adds the working medium steaming available for expansion power generation The mass flow of vapour, but the pressure into the working substance steam of turbine power generation unit 1 is reduction of, under generating efficiency is caused Drop, but working substance steam expansion power generation rely primarily on be working substance steam sensible heat heat energy, high temperature heat source can pass through steam superheating The middle pressure working substance steam that device 11 exports to injector 8 carries out reheating, increases the sensible heat heat energy of working substance steam, and lifting working medium is steamed The temperature of vapour, the generating efficiency of turbine power generation unit 1 can be so improved, partly or entirely offset caused by pressure reduces Generating efficiency is lost, and the generating efficiency of safeguards system is in higher level.
The reasons why setting gas-liquid separator 9 is as follows:In pipe-line system between high-temperature evaporator 6 and cryogenic vaporizer 7 There is provided gas-liquid separator 9 so that the liquid refrigerant of high-temperature evaporator 6 and cryogenic vaporizer 7 forms the form of series flow, excellent The evaporation traffic demand of cryogenic vaporizer is first ensured, according to the principle of mass conservation, unevaporated liquid refrigerant disclosure satisfy that naturally The evaporation traffic demand of high-temperature evaporator 6, this system architecture, which is set, can adaptively meet that high-temperature evaporator 6 and low temperature steam The working medium flow distribution between device 7 is sent out, fully ensures that the steady operation of system, reduces the control difficulty of system.
The reasons why setting adjustment heat exchanger 10 is as follows:When systems are functioning properly, the state of working medium thermodynamic cycle is clear and definite , i.e. high-temperature evaporator 6 and 7 respective evaporating temperature of cryogenic vaporizer is clear and definite, and heat exchange amount ratio therebetween And clearly.If high temperature heat source is directly entered cryogenic vaporizer 7 after entering high-temperature evaporator 6, it will high warm occurs The temperature drop process in source can not meet the requirement of the evaporating temperature and the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7 simultaneously, So that system can not be realized.
Such as the high temperature heat source inlet temperature of the high-temperature evaporator 6 of requirement of system design is 155 DEG C, outlet temperature 35 DEG C, the evaporating temperature of high-temperature evaporator 6 is 100 DEG C, and the evaporating temperature of cryogenic vaporizer 7 is 30 DEG C, high-temperature evaporator 6 and low temperature Heat exchange amount ratio between evaporator 7 is 10:6, then if high temperature heat source is directly entered low temperature after entering high-temperature evaporator 6 Evaporator 7, then maximum temperature drop of the high temperature heat source in high-temperature evaporator 6 is 55 DEG C, is 65 in the minimum temperature drop of cryogenic vaporizer 7 DEG C, it is that can not meet that the ratio between heat exchange amount is 10 anyway:6 requirement.
Therefore increase on high temperature heat source pipeline 61 of the present invention between high-temperature evaporator 6 and cryogenic vaporizer 7 and be provided with Heat exchanger 10 is adjusted, it can be adaptively adjusted the inlet temperature of the high temperature heat source of cryogenic vaporizer 7, realize cryogenic heat exchanger The regulation of 7 heat exchange amounts so that the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7 meets the requirement of thermodynamic cycle.
Still above-mentioned example is directed to, it is 105 DEG C that design high-temperature evaporator 6, which exports high temperature heat source temperature, increase adjustment heat exchange After device 10, adjustment heat exchanger 10, which exports high temperature heat source temperature, can be adjusted to 65 DEG C, the outlet high temperature heat source of cryogenic vaporizer 7 Temperature is 35 DEG C, then temperature drop of the high temperature heat source in high-temperature evaporator 6 is 50 DEG C, and the temperature drop in cryogenic vaporizer 7 is 30 DEG C, Ignore the ratio thermal change of high temperature heat source, then it is 10 that can meet the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7:6 The requirement of thermodynamic cycle.
Embodiment four:Illustrate present embodiment, a kind of heating power with injector described in present embodiment with reference to Fig. 4 Electricity generation system, it include turbine power generation unit 1, condenser 2, reservoir 3, throttle expansion valve 4, working medium pump 5, high-temperature evaporator 6, Cryogenic vaporizer 7, injector 8, gas-liquid separator 9, adjustment heat exchanger 10, steam superheater 11, the first working medium pipeline 41, second Working medium pipeline 42, the 3rd working medium pipeline 43, high temperature heat source pipeline 61, the first low-temperature heat source pipeline 51, the second low-temperature heat source pipeline 52nd, the 3rd low-temperature heat source pipeline 53 and the 4th low-temperature heat source pipeline 54, the first low-temperature heat source pipeline 51 respectively with the second Low Temperature Thermal The arrival end on source capsule road 52 and the 3rd low-temperature heat source pipeline 53 with arrival end connect, the 3rd low-temperature heat source pipeline 53 successively with it is cold Condenser 2 connects with the arrival end of the 4th low-temperature heat source pipeline 54, the second low-temperature heat source pipeline 52 successively with adjustment heat exchanger 10 and 4th low-temperature heat source pipeline 54 arrival end connection, high temperature heat source pipeline 61 successively with steam superheater 11, high-temperature evaporator 6, Adjustment heat exchanger 10 is connected with cryogenic vaporizer 7 and set through cryogenic vaporizer 7, the port of export of injector 8 and the 3rd working medium Pipeline 43 arrival end connection, the 3rd working medium pipeline 43 successively with steam superheater 11, turbine power generation unit 1, condenser 2, storage Liquid device 3, working medium pump 5, high-temperature evaporator 6 connect with the arrival end of gas-liquid separator 9, gas-liquid separator 9 respectively with the first working medium The arrival end of pipeline 41 and the connection of the arrival end of the second working medium pipeline 42, the injection working fluid of the first working medium pipeline 41 and injector 8 Arrival end connects, and driven fluid arrival end of the second working medium pipeline 42 successively with cryogenic vaporizer 7 and injector 8 connects, and saves Stream expansion valve 4 is arranged on the second working medium pipeline 42 between gas-liquid separator 9 and cryogenic vaporizer 7.
The difference of present embodiment and embodiment three is that low-temperature heat source is entered by the first low-temperature heat source pipeline 51 It is divided into two-way after system, is absorbed heat all the way by the 3rd low-temperature heat source pipeline 53 in condenser 2, condense the work after expansion work Matter steam, while the temperature lifting of the road low-temperature heat source is realized, another way is exchanged heat by the second low-temperature heat source pipeline 52 in adjustment Absorbed heat in device 10, the temperature for reducing high temperature heat source is allowed to the temperature requirement for meeting thermodynamic cycle, while realizes the road low-temperature heat source Temperature lifting, the two-way low-temperature heat source after heating up, which finally converges, is incorporated to the 4th low-temperature heat source pipeline 54 and outflow system.
When the inlet temperature of low-temperature heat source is higher, it is adapted to use the present embodiment.Because when the import temperature of low-temperature heat source When spending higher, it will to adjust heat exchanger using being connected in series still by condenser 2 and adjustment heat exchanger 10 in Low Temperature Thermal source 10 low-temperature heat source inlet temperature is too high and loses accommodation function, and still condenser 2 and adjustment exchange heat in Low Temperature Thermal source Device 10 can avoid the problem using being connected in series.
The thermodynamic cycle process of working medium:Reservoir 3 collects the liquid refrigerant of condensation, and liquid refrigerant drives liter by working medium pump 5 Enter high-temperature evaporator 6 after pressure, liquid refrigerant heats simultaneously explosive evaporation by high temperature heat source in high-temperature evaporator 6, enters afterwards Gas-liquid separator 9 carries out gas-liquid separation, and the liquid refrigerant after separation after the reducing pressure by regulating flow of restriction expansion device 4 by entering low temperature Evaporator 7, liquid refrigerant heats simultaneously explosive evaporation by high temperature heat source in cryogenic vaporizer 7, what gas-liquid separator 9 was separated High-pressure working medium steam enters injector 8 and is used as injection working fluid, and injection evaporates generation by cryogenic vaporizer 7 in injector 8 Low-pressure steam, injector 8 export middle pressure working substance steam heated into steam superheater 11 by high temperature heat source after, entrance Expansion work and generating are carried out in turbine power generation unit 1, enters back into condenser 2 after decrease temperature and pressure, the gaseous state work in condenser 2 Matter is cooled down by low-temperature heat source and condensed, and the liquid refrigerant after condensing enters reservoir 3, and the heating power for so just constituting working medium follows Ring.Injector 8 and restriction expansion device 4 have built the environment under low pressure of cryogenic vaporizer 7, and injector 8 and working medium pump 5 have built height The hyperbaric environment of warm evaporator 6 and gas-liquid separator 9.
The exothermic process of high temperature heat source:High temperature heat source enters system by high temperature heat source pipeline 61, first in steam superheating Heat release in device 11, the middle pressure working substance steam that heating injector 8 exports (can increase the sensible heat amount of working substance steam and follow-up generating Amount), while high temperature heat source realizes and cooled for the first time that high temperature heat source heat release in high-temperature evaporator 6 afterwards, heating high-pressure working medium makes Explosive evaporation, while high temperature heat source realizes that second cools, and high temperature heat source heat release in adjustment heat exchanger 10, heating are low afterwards Temperature-heat-source is allowed to heat up, while high temperature heat source realizes that third time cools, and the heat release in cryogenic vaporizer 7 of final high temperature thermal source, adds Heat low working medium is allowed to explosive evaporation, while high temperature heat source realizes the 4th cooling.High temperature heat source for the first time, second and the 4th The discharged heat of secondary cooling is generated electricity into system, ensures that gross generation meets to require, cool discharged heat for the third time The heating for low-temperature heat source is measured, improves the temperature levels of low-temperature heat source.
The high temperature heat source applied in the present invention can be industrial exhaust steam, the waste gas or flue gas of high temperature (more than 150 DEG C), in The liquid water of high temperature (more than 100 DEG C), oil etc., or collection heat carrier of solar energy etc..Low-temperature heat source is primarily referred to as water.Work Matter can use water, freon class working medium, or alkanes working medium.
The reasons why injector 8 is arranged at into turbine power generation 1 upstream of unit is as follows:Most working medium have following hot thing Rationality matter rule, i.e., when saturation temperature level is higher, the difference of the saturation pressure corresponding to the difference of identical saturation temperature will be got over Greatly, for example, water temperature to be 50 DEG C with the saturation pressure difference corresponding to 40 DEG C be 0.12335-0.07375=0.04960bar, and water temperature is 120 DEG C are 1.9854-1.4327=0.5527bar with the saturation pressure difference corresponding to 110 DEG C, when stress level is lower in other words, The difference of saturation temperature corresponding to the difference of identical saturation pressure will be bigger.Can also be summarized as stress level it is lower when, pressure Heat quality loss caused by drop is bigger, and when stress level is higher, the heat quality loss caused by pressure drop is just smaller.
Based on this rule, injector 8 is arranged at the upstream of turbine power generation unit 1 by the present invention.In order to ensure that injector 8 has There are enough ejector capacities, it is necessary to assure meet certain operting differential pressure between the inlet and outlet of injector 8.If by injector 8 It is arranged at after turbine power generation unit 1, because the inlet pressure of injector 8 is relatively low, causes the inlet and outlet of injector 8 to meet phase Same operting differential pressure, must be greatly reduced the condensation temperature of condenser 2, it reduce the heat quality of condensation heat and heat economy Value.Lower condensation temperature also improves difficulty for the preparation of low-temperature heat source.If injector 8 is arranged at turbine generators Before group 1, because working substance steam pressure is very high, it is easier to meet the requirement of the inlet and outlet operting differential pressure of injector 8, and injection pressure Heat quality loss caused by drop is just smaller, and this is more beneficial for the raising of system overall efficiency.
The reasons why setting steam superheater 11 is as follows:The setting of injector 8 adds the working medium steaming available for expansion power generation The mass flow of vapour, but the pressure into the working substance steam of turbine power generation unit 1 is reduction of, under generating efficiency is caused Drop, but working substance steam expansion power generation rely primarily on be working substance steam sensible heat heat energy, high temperature heat source can pass through steam superheating The middle pressure working substance steam that device 11 exports to injector 8 carries out reheating, increases the sensible heat heat energy of working substance steam, and lifting working medium is steamed The temperature of vapour, the generating efficiency of turbine power generation unit 1 can be so improved, partly or entirely offset caused by pressure reduces Generating efficiency is lost, and the generating efficiency of safeguards system is in higher level.
The reasons why setting gas-liquid separator 9 is as follows:In pipe-line system between high-temperature evaporator 6 and cryogenic vaporizer 7 There is provided gas-liquid separator 9 so that the liquid refrigerant of high-temperature evaporator 6 and cryogenic vaporizer 7 forms the form of series flow, excellent The evaporation traffic demand of cryogenic vaporizer is first ensured, according to the principle of mass conservation, unevaporated liquid refrigerant disclosure satisfy that naturally The evaporation traffic demand of high-temperature evaporator 6, this system architecture, which is set, can adaptively meet that high-temperature evaporator 6 and low temperature steam The working medium flow distribution between device 7 is sent out, fully ensures that the steady operation of system, reduces the control difficulty of system.
The reasons why setting adjustment heat exchanger 10 is as follows:When systems are functioning properly, the state of working medium thermodynamic cycle is clear and definite , i.e. high-temperature evaporator 6 and 7 respective evaporating temperature of cryogenic vaporizer is clear and definite, and heat exchange amount ratio therebetween And clearly.If high temperature heat source is directly entered cryogenic vaporizer 7 after entering high-temperature evaporator 6, it will high warm occurs The temperature drop process in source can not meet the requirement of the evaporating temperature and the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7 simultaneously, So that system can not be realized.
Such as the high temperature heat source inlet temperature of the high-temperature evaporator 6 of requirement of system design is 155 DEG C, outlet temperature 35 DEG C, the evaporating temperature of high-temperature evaporator 6 is 100 DEG C, and the evaporating temperature of cryogenic vaporizer 7 is 30 DEG C, high-temperature evaporator 6 and low temperature Heat exchange amount ratio between evaporator 7 is 10:6, then if high temperature heat source is directly entered low temperature after entering high-temperature evaporator 6 Evaporator 7, then maximum temperature drop of the high temperature heat source in high-temperature evaporator 6 is 55 DEG C, is 65 in the minimum temperature drop of cryogenic vaporizer 7 DEG C, it is that can not meet that the ratio between heat exchange amount is 10 anyway:6 requirement.
Therefore increase on high temperature heat source pipeline 61 of the present invention between high-temperature evaporator 6 and cryogenic vaporizer 7 and be provided with Heat exchanger 10 is adjusted, it can be adaptively adjusted the inlet temperature of the high temperature heat source of cryogenic vaporizer 7, realize cryogenic heat exchanger The regulation of 7 heat exchange amounts so that the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7 meets the requirement of thermodynamic cycle.
Still above-mentioned example is directed to, it is 105 DEG C that design high-temperature evaporator 6, which exports high temperature heat source temperature, increase adjustment heat exchange After device 10, adjustment heat exchanger 10, which exports high temperature heat source temperature, can be adjusted to 65 DEG C, the outlet high temperature heat source of cryogenic vaporizer 7 Temperature is 35 DEG C, then temperature drop of the high temperature heat source in high-temperature evaporator 6 is 50 DEG C, and the temperature drop in cryogenic vaporizer 7 is 30 DEG C, Ignore the ratio thermal change of high temperature heat source, then it is 10 that can meet the ratio between heat exchange amount of high-temperature evaporator 6 and cryogenic vaporizer 7:6 The requirement of thermodynamic cycle.

Claims (4)

  1. A kind of 1. heat power generating system with injector, it is characterised in that:It include turbine power generation unit (1), condenser (2), Reservoir (3), throttle expansion valve (4), working medium pump (5), high-temperature evaporator (6), cryogenic vaporizer (7), injector (8), gas-liquid Separator (9), adjustment heat exchanger (10), steam superheater (11), the first working medium pipeline (41), the second working medium pipeline (42), the Three working medium pipelines (43), high temperature heat source pipeline (61) and the first low-temperature heat source pipeline (51), the first low-temperature heat source pipeline (51) according to It is secondary connect and through adjustment heat exchanger (10) setting with adjustment heat exchanger (10) with condenser (2), high temperature heat source pipeline (61) according to It is secondary to be connected with steam superheater (11), high-temperature evaporator (6), adjustment heat exchanger (10) and cryogenic vaporizer (7) and pass through low temperature Evaporator (7) is set, and the port of export of injector (8) connects with the arrival end of the 3rd working medium pipeline (43), the 3rd working medium pipeline (43) successively with steam superheater (11), turbine power generation unit (1), condenser (2), reservoir (3), cryogenic vaporizer (7) and The arrival end connection of gas-liquid separator (9), throttle expansion valve (4) are arranged on the between reservoir (3) and cryogenic vaporizer (7) On three working medium pipelines (43), gas-liquid separator (9) respectively with the first working medium pipeline (41) arrival end and the second working medium pipeline (42) Arrival end connects, and the first working medium pipeline (41) works with the injection of working medium pump (5), high-temperature evaporator (6) and injector (8) successively Fluid inlet end connects, and second working medium pipeline (42) port of export connects with the driven fluid arrival end of injector (8).
  2. A kind of 2. heat power generating system with injector, it is characterised in that:It include turbine power generation unit (1), condenser (2), Reservoir (3), throttle expansion valve (4), working medium pump (5), high-temperature evaporator (6), cryogenic vaporizer (7), injector (8), gas-liquid Separator (9), adjustment heat exchanger (10), steam superheater (11), the first working medium pipeline (41), the second working medium pipeline (42), the Three working medium pipelines (43), high temperature heat source pipeline (61), the first low-temperature heat source pipeline (51), the second low-temperature heat source pipeline (52), Three low-temperature heat source pipelines (53) and the 4th low-temperature heat source pipeline (54), the first low-temperature heat source pipeline (51) respectively with the second Low Temperature Thermal The arrival end on source capsule road (52) and the 3rd low-temperature heat source pipeline (53) with arrival end connect, the 3rd low-temperature heat source pipeline (53) according to The secondary arrival end with condenser (2) and the 4th low-temperature heat source pipeline (54) connects, the second low-temperature heat source pipeline (52) successively with tune Suitable heat exchanger (10) connects with the arrival end of the 4th low-temperature heat source pipeline (54), high temperature heat source pipeline (61) successively with steam superheating Device (11), high-temperature evaporator (6), adjustment heat exchanger (10) are connected with cryogenic vaporizer (7) and set through cryogenic vaporizer (7) Put, the port of export of injector (8) connects with the arrival end of the 3rd working medium pipeline (43), the 3rd working medium pipeline (43) successively with steam Superheater (11), turbine power generation unit (1), condenser (2), reservoir (3), cryogenic vaporizer (7) and gas-liquid separator (9) Arrival end connects, and throttle expansion valve (4) is arranged on the 3rd working medium pipeline (43) between reservoir (3) and cryogenic vaporizer (7) On, gas-liquid separator (9) connects with the first working medium pipeline (41) arrival end and second working medium pipeline (42) arrival end respectively, and first Working medium pipeline (41) connects with the injection Working-fluid intaking end of working medium pump (5), high-temperature evaporator (6) and injector (8) successively, Second working medium pipeline (42) port of export connects with the driven fluid arrival end of injector (8).
  3. A kind of 3. heat power generating system with injector, it is characterised in that:It include turbine power generation unit (1), condenser (2), Reservoir (3), throttle expansion valve (4), working medium pump (5), high-temperature evaporator (6), cryogenic vaporizer (7), injector (8), gas-liquid Separator (9), adjustment heat exchanger (10), steam superheater (11), the first working medium pipeline (41), the second working medium pipeline (42), the Three working medium pipelines (43), high temperature heat source pipeline (61) and the first low-temperature heat source pipeline (51), the first low-temperature heat source pipeline (51) according to It is secondary connect and through adjustment heat exchanger (10) setting with adjustment heat exchanger (10) with condenser (2), high temperature heat source pipeline (61) according to It is secondary to be connected with steam superheater (11), high-temperature evaporator (6), adjustment heat exchanger (10) and cryogenic vaporizer (7) and pass through low temperature Evaporator (7) is set, and the port of export of injector (8) connects with the arrival end of the 3rd working medium pipeline (43), the 3rd working medium pipeline (43) steamed successively with steam superheater (11), turbine power generation unit (1), condenser (2), reservoir (3), working medium pump (5), high temperature Hair device (6) connected with the arrival end of gas-liquid separator (9), gas-liquid separator (9) respectively with first working medium pipeline (41) arrival end Connected with second working medium pipeline (42) arrival end, the injection Working-fluid intaking end of the first working medium pipeline (41) and injector (8) Connection, driven fluid entrance of the second working medium pipeline (42) successively with cryogenic vaporizer (7) and injector (8) connect, and throttle Expansion valve (4) is arranged on the second working medium pipeline (42) between gas-liquid separator (9) and cryogenic vaporizer (7).
  4. A kind of 4. heat power generating system with injector, it is characterised in that:It include turbine power generation unit (1), condenser (2), Reservoir (3), throttle expansion valve (4), working medium pump (5), high-temperature evaporator (6), cryogenic vaporizer (7), injector (8), gas-liquid Separator (9), adjustment heat exchanger (10), steam superheater (11), the first working medium pipeline (41), the second working medium pipeline (42), the Three working medium pipelines (43), high temperature heat source pipeline (61), the first low-temperature heat source pipeline (51), the second low-temperature heat source pipeline (52), Three low-temperature heat source pipelines (53) and the 4th low-temperature heat source pipeline (54), the first low-temperature heat source pipeline (51) respectively with the second Low Temperature Thermal The arrival end on source capsule road (52) and the 3rd low-temperature heat source pipeline (53) with arrival end connect, the 3rd low-temperature heat source pipeline (53) according to The secondary arrival end with condenser (2) and the 4th low-temperature heat source pipeline (54) connects, the second low-temperature heat source pipeline (52) successively with tune Suitable heat exchanger (10) connects with the arrival end of the 4th low-temperature heat source pipeline (54), high temperature heat source pipeline (61) successively with steam superheating Device (11), high-temperature evaporator (6), adjustment heat exchanger (10) are connected with cryogenic vaporizer (7) and set through cryogenic vaporizer (7) Put, the port of export of injector (8) connects with the arrival end of the 3rd working medium pipeline (43), the 3rd working medium pipeline (43) successively with steam Superheater (11), turbine power generation unit (1), condenser (2), reservoir (3), working medium pump (5), high-temperature evaporator (6) and gas-liquid Separator (9) arrival end connection, gas-liquid separator (9) respectively with the first working medium pipeline (41) arrival end and the second working medium pipeline (42) arrival end connects, and the first working medium pipeline (41) connects with the injection Working-fluid intaking end of injector (8), the second working medium tube Driven fluid arrival end of the road (42) successively with cryogenic vaporizer (7) and injector (8) is connected, and throttle expansion valve (4) is set On the second working medium pipeline (42) between gas-liquid separator (9) and cryogenic vaporizer (7).
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Publication number Priority date Publication date Assignee Title
JPS60247004A (en) * 1984-05-23 1985-12-06 Tokyo Inst Of Technol Complex cycle heat power plant
JP2000161015A (en) * 1998-11-19 2000-06-13 Takeshi Hatanaka Closed-cycle power system
CN101025096A (en) * 2007-03-27 2007-08-29 陈深佃 Generating system utilizing low-temperature heat-source or environment heat-source to generat power
CN103629860A (en) * 2013-12-04 2014-03-12 重庆大学 Transcritical CO2 cooling heat and power combined circulation system
CN103775145A (en) * 2014-01-15 2014-05-07 天津大学 Organic Rankine circulating system with double-ejector supercharging device
CN104676946A (en) * 2015-02-03 2015-06-03 北京建筑大学 Two-stage ejection heat exchange unit and operating mode thereof

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KR101623309B1 (en) * 2015-06-18 2016-05-20 한국에너지기술연구원 Supercritical carbon dioxide powder plant

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60247004A (en) * 1984-05-23 1985-12-06 Tokyo Inst Of Technol Complex cycle heat power plant
JP2000161015A (en) * 1998-11-19 2000-06-13 Takeshi Hatanaka Closed-cycle power system
CN101025096A (en) * 2007-03-27 2007-08-29 陈深佃 Generating system utilizing low-temperature heat-source or environment heat-source to generat power
CN103629860A (en) * 2013-12-04 2014-03-12 重庆大学 Transcritical CO2 cooling heat and power combined circulation system
CN103775145A (en) * 2014-01-15 2014-05-07 天津大学 Organic Rankine circulating system with double-ejector supercharging device
CN104676946A (en) * 2015-02-03 2015-06-03 北京建筑大学 Two-stage ejection heat exchange unit and operating mode thereof

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