CN107246291B - The double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium - Google Patents
The double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium Download PDFInfo
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- CN107246291B CN107246291B CN201710516026.5A CN201710516026A CN107246291B CN 107246291 B CN107246291 B CN 107246291B CN 201710516026 A CN201710516026 A CN 201710516026A CN 107246291 B CN107246291 B CN 107246291B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/06—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using mixtures of different fluids
Abstract
The present invention is a kind of double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium, including non-azeotropic working medium storage tank and condenser, condenser is communicated with non-azeotropic working medium low pressure evaporation flow paths and non-azeotropic working medium high-pressure evaporation access, the gas vent of non-azeotropic working medium low pressure evaporation flow paths is connected to the path end entrance of low pressure turbine, the gas vent of non-azeotropic working medium high-pressure evaporation access is connected to the path end entrance of high pressure turbine, the main shaft of high pressure turbine and the main shaft of low pressure turbine are connected by first shaft coupling, the main shaft of low pressure turbine also passes through second shaft coupling and the main shaft of generator connects；First heat source access is set in non-azeotropic working medium high-pressure evaporation access, Secondary Heat Source access is set in non-azeotropic working medium low pressure evaporation flow paths, the system reduces the heat transfer temperature difference between working medium and heat source using the double pressure evaporations of non-azeotropic working medium, reduce the irreversible loss of heat transfer process, the High Efficiency Thermal of low temperature heat energy-function is converted in realization, the fast development of low temperature heat energy power generation in promotion.
Description
Technical field
The present invention relates to the non-azeotropic working mediums that low temperature heat energy in technical field of energy utilization more particularly to a kind of utilization generates electricity
Double pressures evaporate organic Rankine cycle power generation system.
Background technique
2015, continuous 15 years holding the first in the world of China's non-renewable energy consumption figure, however non-renewable energy is with coal
Main pattern does not change yet, and still above the 50% of global total quantity consumed, thermal power output accounts for national total power generation for consumption of coal
74%.The consumption of the fossil energies such as coal supports China's rapid development of economy and social progress, but caused environment is asked
Topic becomes increasingly conspicuous, haze weather made of climate change and atmosphere pollution effect that greenhouse gas emission is facilitated, in recent years
The severe challenge faced as China.
The renewable energy such as Devoting Major Efforts To Developing solar energy, geothermal energy, biomass energy and industrial exhaust heat are to reduce coal in China
The important directions of consumption and pollutant discharge amount are to realize that China promises to undertake in the climate change conference of Paris " to the year two thousand thirty
Than 2005 decline 60%-65% of unit GDP CO2 emission, the non-fossil energy account for non-renewable energy consumption ratio
Weigh to 20% or so " important channel of target.
The solar radiant energy total amount that the annual land surface in China receives is about 5 × 1016MJ；Biomass Energy Resources total amount is reachable
6.5 hundred million tons of standard coals；In recent years, China has built a collection of steam power plant using solar energy and biomass energy, solar power generation dress
Machine capacity accounts for about the 4.7% of national total installation of generating capacity, and generated energy accounts for about the 4% of national total power generation.Currently, solar energy and biology
For mass-energy generation technology still based on Steam Power Circulation, steam parameter is higher, and single machine installed capacity is big, due to sun energy-flux density
It is small, high parameter steam power station is established, the solar energy heating area needed is big, it is limited by land area, and biomass is electric
Factory then need to be high from biological materials, fuel costs such as longer-distance area transport stalks.China's geothermal resource is equivalent to
9500000000 tons of standard coals, the geothermal energy resources in main plain sediments basin are equivalent to 853,200,000,000 tons of standard coals, 3-10km dry-hot-rock geothermal
Resource is then equivalent to 860,000,000,000,000 tons of standard coals, but 70% or more is less than 150 DEG C of hot-water type low temperature geothermal source.China's work
Industry energy consumption is high, and 350 DEG C of a large amount of industrial exhaust heats below are underutilized.
In conclusion the utilization of the renewable resources such as China's solar energy, biomass energy and geothermal energy and industrial exhaust heat is latent
Power is huge, however the resource temperature convenient for exploitation is lower, and many places are in 350 DEG C hereinafter, heat energy utilization scope in belonging to, no longer suitable
Traditional Steam Power Circulation is preferably used to realize heat-function conversion.
The present inventor based on years of experience and practice in relevant industries, proposes a kind of double pressures of non-azeotropic working medium as a result,
Organic Rankine cycle power generation system is evaporated, to overcome the deficiencies of existing technologies.
Summary of the invention
The purpose of the present invention is to provide a kind of double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium, overcome existing
There is the problem of middle heat energy utilization low efficiency present in technology, which reduces working medium using the double pressure evaporations of non-azeotropic working medium
With the heat transfer temperature difference between heat source heat exchanging fluid, the irreversible loss of heat transfer process is reduced, promotes thermal efficiency of cycle, low temperature in realization
The High Efficiency Thermal of thermal energy-function is converted, the fast development of low temperature heat energy power generation in promotion.
The object of the present invention is achieved like this, a kind of double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium,
Including non-azeotropic working medium storage tank, the exit of the non-azeotropic working medium storage tank can connect with the condenser that can condense non-azeotropic working medium
Logical, the sender property outlet of the condenser is communicated with non-azeotropic working medium low pressure evaporation flow paths and non-azeotropic working medium high-pressure evaporation access,
The gas vent of the non-azeotropic working medium low pressure evaporation flow paths is connected to the path end entrance of a low pressure turbine, the non-azeotrope work
The gas vent of matter high-pressure evaporation access is connected to the path end entrance of a high pressure turbine, the bigger diameter end of the high pressure turbine and institute
The bigger diameter end for stating low pressure turbine is oppositely arranged, and main shaft one end of the main shaft of the high pressure turbine and the low pressure turbine passes through first
The main shaft other end of shaft coupling connection, the low pressure turbine is connected by the main shaft of second shaft coupling and generator；The high pressure
The bigger diameter end of turbine exports and the outlet of the bigger diameter end of the low pressure turbine can be connected to the entrance of the condenser；It is described non-total
It is provided with the first heat source access in boiling working medium high-pressure evaporation access, is provided in the non-azeotropic working medium low pressure evaporation flow paths and institute
The Secondary Heat Source access of the first heat source access connection is stated, the entrance of the first heat source access constitutes heat source heat exchanging fluid entrance,
The export mixes heat source heat exchanging fluid of the Secondary Heat Source access exports, the heat source heat exchanging fluid in the first heat source access
Flow direction is flowed to the non-azeotropic working medium in the non-azeotropic working medium high-pressure evaporation access on the contrary, in the Secondary Heat Source access
The flow direction of heat source heat exchanging fluid is opposite with the flow direction of non-azeotropic working medium in the non-azeotropic working medium low pressure evaporation flow paths.
In a preferred embodiment of the present invention, the non-azeotropic working medium low pressure evaporation flow paths include the work with condenser
The low pressure working fluid of matter outlet pumps, and a low pressure preheater (LPP, the low pressure preheating is arranged in the outlet of the low pressure working fluid pump
The first working medium passage is provided in device, the entrance of first working medium passage is connected to low pressure working fluid pump, first work
The outlet in matter channel can be connected to a low pressure evaporator, high-pressure working medium pump respectively, and the is additionally provided in the low pressure preheater (LPP
One heat source heat transfer fluid channels, the outlet of heat source heat exchanging fluid described in the export mixes of the first heat source heat transfer fluid channels, institute
The flow direction for stating the heat source heat exchanging fluid in the first heat source heat transfer fluid channels and the non-azeotropic working medium in first working medium passage
Flow direction it is opposite；Be provided with the second working medium passage in the low pressure evaporator, the entrance of second working medium passage can with it is described
The outlet of the outlet of first working medium passage, second working medium passage can communicatively be provided with low-pressure gas-liquid separator, institute
The gas vent for stating low-pressure gas-liquid separator constitutes the gas vent of the non-azeotropic working medium low pressure evaporation flow paths, the low pressure gas
The gas vent of liquid/gas separator can be connected to the path end entrance of the low pressure turbine, the liquid discharge of the low-pressure gas-liquid separator
Mouth is connected to the entrance of second working medium passage, and Secondary Heat Source heat transfer fluid channels are additionally provided in the low pressure evaporator,
The outlet of the Secondary Heat Source heat transfer fluid channels is connected to the entrance of the first heat source heat transfer fluid channels, second heat
Source heat transfer fluid channels and the first heat source heat transfer fluid channels constitute the Secondary Heat Source access, the Secondary Heat Source heat exchange
The flow direction of heat source heat exchanging fluid in fluid channel is opposite with the flow direction of non-azeotropic working medium in second working medium passage.
In a preferred embodiment of the present invention, the non-azeotropic working medium high-pressure evaporation access includes the high-pressure working medium
The outlet of pump, the high-pressure working medium pump has high pressure pre-heater, and third working medium passage, institute are provided in the high pressure pre-heater
The entrance for stating third working medium passage is connected to high-pressure working medium pump, and the outlet of the third working medium passage can be communicatively provided with
High pressure evaporator is additionally provided with third heat source heat transfer fluid channels, the third heat source heat exchanging fluid in the high pressure pre-heater
The outlet in channel is connected to the entrance of the Secondary Heat Source heat transfer fluid channels, the heat in the third heat source heat transfer fluid channels
The flow direction of source heat exchanging fluid is opposite with the flow direction of non-azeotropic working medium in the third working medium passage；It is set in the high pressure evaporator
Set the 4th working medium passage, the entrance of the 4th working medium passage can with the outlet of the third working medium passage, the described 4th
The outlet of working medium passage can communicatively be provided with high-pressure gas-liquid separator, and the gas vent of the high-pressure gas-liquid separator constitutes institute
The gas vent of non-azeotropic working medium high-pressure evaporation access is stated, the gas vent of the high-pressure gas-liquid separator can be saturating with the high pressure
Flat path end entrance connection, the liquid outlet of the high-pressure gas-liquid separator are connected to the entrance of the 4th working medium passage,
Be additionally provided with the 4th heat source heat transfer fluid channels in the high pressure evaporator, the entrance of the 4th heat source heat transfer fluid channels with
The heat source heat exchanging fluid feedway connection, the outlet of the 4th heat source heat transfer fluid channels and the third heat source exchange heat
The entrance of fluid channel is connected to, described in the 4th heat source heat transfer fluid channels and third heat source heat transfer fluid channels composition
First heat source access, the flow direction and the 4th working medium passage of the heat source heat exchanging fluid in the 4th heat source heat transfer fluid channels
The flow direction of interior non-azeotropic working medium is opposite.
In a preferred embodiment of the present invention, a working medium stream can be communicatively arranged in the outlet of first working medium passage
Distributing valve is measured, the first distribution outlet and the second distribution outlet are provided on the working medium flow distributing valve, described first distributes
Mouth can be connected to the entrance of second working medium passage, and second distribution outlet can be pumped with the high-pressure working medium be connected to.
In a preferred embodiment of the present invention, mass flowmenter is provided in the working medium flow distributing valve.
In a preferred embodiment of the present invention, the inlet connection setting first entrance of second working medium passage joins
Case, the outlet of first working medium passage and the liquid outlet of the low-pressure gas-liquid separator can be with the first entrance headers
Connection.
In a preferred embodiment of the present invention, the inlet connection setting second entrance of the 4th working medium passage joins
Case, the outlet of the third working medium passage and the liquid outlet of the high-pressure gas-liquid separator can be with the second entrance headers
Connection.
In a preferred embodiment of the present invention, the gas vent sequence of the non-azeotropic working medium high-pressure evaporation access is logical
Cross high pressure turbine valve, high pressure turbine regulating valve is connected to the path end entrance of the high pressure turbine, the non-azeotropic working medium is low
The gas vent sequence of evaporation flow paths is pressed to pass through the miner diameter end of low pressure turbine valve, low pressure turbine regulating valve and the low pressure turbine
Entrance connection.
In a preferred embodiment of the present invention, the inlet of the first heat source access is provided with high temperature refrigerant pump,
The high temperature refrigerant pump is connected to heat source feedway.
In a preferred embodiment of the present invention, condenser working medium passage, the condensation are provided in the condenser
The sender property outlet of condenser described in the export mixes of device working medium passage is additionally provided with cooling duct in the condenser, described cold
But the entrance in channel passes through the outlet of circulating cooling water pump and a cooling tower, the outlet of the cooling duct and the cooling
The circulation water inlet of tower is connected to.
From the above mentioned, the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention have following beneficial to effect
Fruit:
(1) the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention pass through the double pressure evaporation collaborations of two-stage
Temperature glide characteristic in non-azeotropic working medium phase transition process improves the average endothermic temperature of non-azeotropic working medium, reduces non-azeotrope work
The Average heat transfer temperature difference between matter and heat source heat exchanging fluid reduces heat transfer process irreversible loss, improves the thermal efficiency of circulation, realizes
The High Efficiency Thermal of middle low temperature heat energy-function is converted, the fast development of low temperature heat energy power generation in promotion；
(2) high pressure turbine and low pressure are set in the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention
Turbine, the non-azeotropic working medium steam for avoiding different pressures mix in same turbine, and high pressure turbine and low pressure turbine are axis
Streaming turbine, high pressure turbine and low pressure turbine it is contrary, internal working medium flow direction is on the contrary, effectively balance portion is saturating
The axial thrust that non-azeotropic working medium flowing generates in flat；
(3) in the working medium flow distributing valve in the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention
It is provided with mass flowmenter, it can be by adjusting the distribution of double flash evaporation pressure and flow, flexible adaptation heat source in system operation
The variation of parameter or the adjustment of turbine power keep the Temperature Matching effect between heat source heat exchanging fluid and non-azeotropic working medium, pass through
The higher internal efficiency ratio of high pressure turbine is maintained, to guarantee the thermal efficiency of entire electricity generation system；
(4) the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention may be implemented 350 ° it is below too
High Efficiency Thermal-function conversion of positive energy, biomass energy, geothermal energy and industrial exhaust heat opposite can improve thermal effect compared to conventional electric power generation technology
Rate 10-30% can give full play to the advantage in middle low temperature heat energy power field；
(5) non-azeotropic working medium of the invention pair pressure evaporation organic Rankine cycle power generation systems are simple with system, run dimension
The advantages that shield is convenient and long service life, Organic Rankine Cycle installed capacity range in 1-10MW, can adaptation to local conditions be arranged in
The bulk power grids such as outlying district, frontier sentry, island are difficult to covering area, can be applied to the abundant area of renewable energy, carry out green
Color power generation, the industrial exhaust heat for being equally applicable for city distributed energy resource system and industrial and mining enterprises utilize.
Detailed description of the invention
The following drawings are only intended to schematically illustrate and explain the present invention, not delimit the scope of the invention.Wherein:
Fig. 1: for the double pressure evaporation organic Rankine cycle power generation system schematic diagrames of non-azeotropic working medium of the invention.
In figure:
100, the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium；
1, condenser；
11, cooling duct；12, circulating cooling water pump；13, cooling tower；14, non-azeotropic working medium process storage tank；
2, non-azeotropic working medium low pressure evaporation flow paths；
21, low pressure working fluid pumps；22, low pressure preheater (LPP；23, low pressure evaporator；24, low-pressure gas-liquid separator；25, working medium stream
Measure distributing valve；251, the first distribution outlet；252, the second distribution outlet；26, first entrance header；
3, non-azeotropic working medium high-pressure evaporation access；
31, high-pressure working medium pumps；32, high pressure pre-heater；33, high pressure evaporator；34, high-pressure gas-liquid separator；35, second enters
Mouth header；
4, low pressure turbine；
41, low pressure turbine valve；42, low pressure turbine regulating valve；
5, high pressure turbine；
51, high pressure turbine valve；52, high pressure turbine regulating valve；
61, first shaft coupling；62, second shaft coupling；
7, generator；
81, the first heat source heat transfer fluid channels；82, Secondary Heat Source heat transfer fluid channels；83, third heat source heat exchanging fluid is logical
Road；84, the 4th heat source heat transfer fluid channels；85, high temperature refrigerant pumps.
Specific embodiment
For a clearer understanding of the technical characteristics, objects and effects of the present invention, this hair of Detailed description of the invention is now compareed
Bright specific embodiment.
As shown in Figure 1, the present invention provides a kind of double pressure evaporation organic Rankine cycle power generation systems 100 of non-azeotropic working medium, packet
Non-azeotropic working medium storage tank (prior art is not shown in the figure) is included, in the present embodiment, nytron can be selected in non-azeotropic working medium
Object, type siloxane, hydrofluorocarbon (HFC) class, HF hydrocarbon (HFO) class mainstream body form mixed working fluid pair, and working medium proportion should ensure that
(slip temperature is related with constituent element and its molar fraction, this is binary mixture heat for the slip temperature of condensation process under design conditions
Mechanical property) less than 20 DEG C, so that the temperature rise of condensation process working medium and recirculated cooling water matches.Non-azeotropic working medium storage tank
Exit can be connected to the condenser 1 that can condense non-azeotropic working medium, in the present embodiment, be provided with condenser in condenser 1
Working medium passage, the sender property outlet of the export mixes condenser of condenser working medium passage are additionally provided with cooling duct in condenser 1
11, the entrance of cooling duct 11 passes through the outlet of circulating cooling water pump 12 and a cooling tower 13, the outlet of cooling duct 11
It is connected to the circulation water inlet of cooling tower 13.In a specific embodiment of the invention, it is communicated at the sender property outlet of condenser 1
Non-azeotropic working medium process storage tank 14, non-azeotropic working medium process storage tank 14 is used to store the non-azeotropic working medium of liquid, in the present embodiment
In, condenser 1 and 14 integrated arrangement of non-azeotropic working medium process storage tank, non-azeotropic working medium process storage tank 14 is high-order to be arranged, non-total
The outlet of boiling working medium process storage tank 14 should be higher than that low pressure working fluid pumps 21 entrance 10m or more, prevent non-azeotropic working medium in low pressure working fluid
Cavitation occurs in pump 21.The sender property outlet of non-azeotropic working medium process storage tank 14 is communicated with 2 He of non-azeotropic working medium low pressure evaporation flow paths
Non-azeotropic working medium high-pressure evaporation access 3, two evaporating pressures of non-azeotropic working medium according to working medium evaporation process bubble point temperature into
Row preferably, sets in two evaporating pressures higher pressure as high pressure, sets in two evaporating pressures lower pressure as low pressure,
The specific value of high pressure and low pressure by production it is practical (high pressure turbine and low pressure turbine output work, heat source heat exchanging fluid flow and
Temperature etc.) it determines, the bubble point temperature difference of non-azeotropic working medium is not in a specific embodiment of the invention, under two evaporating pressures
Lower than 10 DEG C, the bubble point temperature of non-azeotropic working medium is had a certain difference under two evaporating pressures, to strengthen the excellent of double pressure evaporations
Gesture, to be conducive to reduce the heat transfer temperature difference between non-azeotropic working medium and heat source heat exchanging fluid.Non-azeotropic working medium low pressure evaporation flow paths 2
Gas vent be connected to the path end entrance of a low pressure turbine 4, the gas vent and one of non-azeotropic working medium high-pressure evaporation access 3
The path end entrance of high pressure turbine 5 is connected to, and the bigger diameter end of the bigger diameter end and low pressure turbine 4 of high pressure turbine 5 is oppositely arranged, and high pressure is saturating
Flat main shaft (prior art) is connect with main shaft one end (prior art) of low pressure turbine by first shaft coupling 61, high pressure turbine
5 and low pressure turbine 4 can rotate coaxially, high pressure turbine 5 and low pressure turbine 4 are set in system, avoid the non-azeotrope of different pressures
Refrigerant vapor mixes in same turbine, and high pressure turbine and low pressure turbine are axial turbine, and non-azeotropic working medium steam is swollen
Not only radial force is generated when swollen, but also generates axial force, high pressure turbine and the contrary setting of low pressure turbine, internal working medium flowing side
To on the contrary, the axial thrust that effectively non-azeotropic working medium flowing generates in balance portion turbine；The main shaft other end of low pressure turbine 4
It is connect by second shaft coupling 62 with the main shaft of generator 7；The bigger diameter end of the bigger diameter end outlet and low pressure turbine 4 of high pressure turbine 5
Outlet can be connected to the entrance of condenser 1；The first heat source access is provided in non-azeotropic working medium high-pressure evaporation access 3, it is non-total
It is provided with the Secondary Heat Source access being connected to the first heat source access in boiling working medium low pressure evaporation flow paths 2, the first heat source access enters
Mouthful constitute heat source heat exchanging fluid entrance, Secondary Heat Source access export mixes heat source heat exchanging fluid outlet, heat source heat exchanging fluid according to
Secondary the first heat source access, Secondary Heat Source access and the non-azeotropic working medium of passing through exchanges heat, the heat source heat exchanging fluid in the first heat source access
Flow direction and the non-azeotropic working medium in non-azeotropic working medium high-pressure evaporation access 3 flow direction on the contrary, heat source in Secondary Heat Source access
The flow direction of heat exchanging fluid is opposite with the flow direction of non-azeotropic working medium in non-azeotropic working medium low pressure evaporation flow paths 2.First heat source access
Non-azeotropic working medium in interior heat source heat exchanging fluid and non-azeotropic working medium high-pressure evaporation access 3 exchanges heat, desuperheated heat source heat exchange
Fluid flows to Secondary Heat Source access, in the heat source heat exchanging fluid in Secondary Heat Source access and non-azeotropic working medium low pressure evaporation flow paths 2
Non-azeotropic working medium heat exchange.The heat source of high temperature (high temperature refers to that temperature is higher than the heat source heat exchanging fluid after heat exchange cools down herein)
Heat exchanging fluid first heats high pressure non-azeotropic working medium, and the heat source heat exchanging fluid of cooling heats low pressure non-azeotropic working medium, realizes heat source
Heat exchanging fluid thermal energy makes full use of, and improves the average endothermic temperature of circulation, improves efficiency, and reduces irreversible loss.Heat source changes
Hot fluid can be the conduction oil of GEOTHERMAL WATER, biomass boiler or solar thermal collector heating, can also be flue gas in industry,
Exhaust gas etc..
The double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention are non-by the double pressure evaporation collaborations of two-stage
Temperature glide characteristic in azeotropic working medium phase transition process improves the average endothermic temperature of non-azeotropic working medium, reduces non-azeotropic working medium
With the heat transfer temperature difference between heat source heat exchanging fluid, heat transfer process irreversible loss is reduced, the thermal efficiency of circulation, low temperature in realization are improved
The High Efficiency Thermal of thermal energy-function is converted, the fast development of low temperature heat energy power generation in promotion；The double pressure evaporations of non-azeotropic working medium of the invention have
High pressure turbine and low pressure turbine are set in machine Rankine cycle electricity generation system, avoid the non-azeotropic working medium steam of different pressures same
Mixing in one turbine, high pressure turbine and low pressure turbine are contrary, and internal working medium flow direction is on the contrary, effectively balance portion
The axial thrust that non-azeotropic working medium flowing generates in turbine；The double pressure evaporation Organic Rankine Cycle power generations of non-azeotropic working medium of the invention
High Efficiency Thermal-function conversion of 350 ° of solar energy, biomass energy, geothermal energy and industrial exhaust heat below may be implemented in system, compared to biography
Generation technology of uniting opposite can improve thermal efficiency 10-30%, can give full play to the advantage in middle low temperature heat energy power field；This hair
The double pressure evaporation organic Rankine cycle power generation systems of bright non-azeotropic working medium are simple with system, operation and maintenance are convenient and service life
The advantages that long, Organic Rankine Cycle installed capacity range in 1-10MW, can adaptation to local conditions be arranged in outlying district, border sentry
The bulk power grids such as institute, island are difficult to covering area, can be applied to the abundant area of renewable energy, and Developing Green power generation also may be used
It is utilized applied to city distributed energy resource system and the industrial exhaust heat of industrial and mining enterprises.
Further, as shown in Figure 1, non-azeotropic working medium low pressure evaporation flow paths 2 include being connected to the sender property outlet of condenser 1
A low pressure preheater (LPP 22 is arranged in the outlet of low pressure working fluid pump 21, low pressure working fluid pump 21, and the is provided in low pressure preheater (LPP 22
One working medium passage, the outlet of entrance and the low pressure working fluid pump 21 of the first working medium passage, the outlet of the first working medium passage can divide
It is not connected to a low pressure evaporator 23, high-pressure working medium pump 31, in the present embodiment, the outlet of the first working medium passage can be connected to
A working medium flow distributing valve 25 is arranged in ground, and the first distribution outlet 251 and second is provided on working medium flow distributing valve 25 and is distributed
Mouth 252, the first distribution outlet 251 can be connected to the entrance of low pressure evaporator 23, and the second distribution outlet 252 can be pumped with high-pressure working medium
31 connections.In the present embodiment, mass flowmenter is provided in working medium flow distributing valve 25, and (prior art is not shown in figure
Out), mass flowmenter is used to control the aperture of the first distribution outlet 251 and the second distribution outlet 252, by adjusting the first distribution
Outlet 251 and the second distribution export the working medium flow of 252 aperture regulation two distribution outlets, and then adjust and enter low pressure evaporation
The working medium flow of device 23 and high pressure pre-heater 32, working medium flow distributing valve 25 not only play the role of triple valve, but also play flow point
The effect matched.The first heat source heat transfer fluid channels 81, the first heat source heat transfer fluid channels 81 are additionally provided in low pressure preheater (LPP 22
The outlet of export mixes heat source heat exchanging fluid, the flow direction and first of the heat source heat exchanging fluid in the first heat source heat transfer fluid channels 81
The flow direction of non-azeotropic working medium in working medium passage is opposite.The second working medium passage is provided in low pressure evaporator 23, the second working medium is logical
The entrance in road can be with the outlet of the first working medium passage, the first distribution outlet 251 and second on working medium flow distributing valve 25
The entrance of working medium passage is connected to, and the outlet of the second working medium passage can communicatively be provided with low-pressure gas-liquid separator 24, low-pressure gas-liquid
Separator 24 can carry out gas-liquid separation, low pressure non-azeotropic working medium gas institute to the non-azeotropic working medium heated through low pressure evaporator 23
The drop of carrying forms non-azeotropic working medium dry saturation vapor after being separated in low-pressure gas-liquid separator 24, does not need using overheat
Device, dry saturation vapor have mainstream bulk properties, and non-azeotropic working medium dry saturation vapor is not in two-phase section in low pressure turbine 4
Expansion.The gas vent of low-pressure gas-liquid separator 24 constitutes the gas vent of non-azeotropic working medium low pressure evaporation flow paths 2, low-pressure gas-liquid
The gas vent of separator 24 can be connected to the path end entrance of low pressure turbine 4, the liquid outlet of low-pressure gas-liquid separator 24 with
The entrance of second working medium passage is connected to, and in the present embodiment, the inlet connection setting first entrance of the second working medium passage joins
Case 26, the outlet of the first working medium passage and the liquid outlet of low-pressure gas-liquid separator 24 are connected to first entrance header 26.It is low
Secondary Heat Source heat transfer fluid channels 82, the outlet of Secondary Heat Source heat transfer fluid channels 82 and first are additionally provided in pressure evaporator 23
The entrance of heat source heat transfer fluid channels 81 is connected to, 81 structure of Secondary Heat Source heat transfer fluid channels 82 and the first heat source heat transfer fluid channels
At Secondary Heat Source access above-mentioned, the flow direction and the second working medium of the heat source heat exchanging fluid in Secondary Heat Source heat transfer fluid channels 82 are logical
The flow direction of non-azeotropic working medium in road is opposite.
As shown in Figure 1, in the present embodiment, gas vent, that is, low-pressure gas-liquid of non-azeotropic working medium low pressure evaporation flow paths 2
The gas vent sequence of separator 24 passes through the miner diameter end of low pressure turbine valve 41, low pressure turbine regulating valve 42 and low pressure turbine 4
Entrance connection.When stopping process, working medium are not up to relevant parameter, low pressure turbine valve 41 is in closed state, and system was run
Cheng Zhong, low pressure turbine valve 41 are in open state；The load of low pressure turbine 4 can be adjusted in low pressure turbine regulating valve 42,
When variable parameter operation, when turbine total load is lower than Design cooling load, the non-azeotrope work of non-azeotropic working medium low pressure evaporation flow paths 2 should be controlled
Mass flow amount, it is preferential to guarantee that high pressure turbine 5 is run under optimum condition, to guarantee higher heat-power conversion efficiency.
Further, as shown in Figure 1, non-azeotropic working medium high-pressure evaporation access 3 includes high-pressure working medium above-mentioned pump 31, high pressure work
The outlet of matter pump 31 has high pressure pre-heater 32, and third working medium passage, third working medium passage are provided in high pressure pre-heater 32
Entrance and high-pressure working medium pump 31 outlet, the outlet of third working medium passage can communicatively be provided with high pressure evaporator 33,
It is additionally provided with third heat source heat transfer fluid channels 83 in high pressure pre-heater 32, the outlet of third heat source heat transfer fluid channels 83 and the
The entrances of two heat source heat transfer fluid channels 82 is connected to, the flow direction of the heat source heat exchanging fluid in third heat source heat transfer fluid channels 83 with
The flow direction of non-azeotropic working medium in third working medium passage is opposite.4th working medium passage, the 4th working medium are set in high pressure evaporator 33
The entrance in channel can communicatively be provided with high-pressure gas-liquid with the outlet of third working medium passage, the outlet of the 4th working medium passage
Separator 34, high-pressure gas-liquid separator 34 can carry out gas-liquid separation to the non-azeotropic working medium heated through high pressure evaporator 33, high
Drop entrained by pressure non-azeotropic working medium gas forms the dry saturation of non-azeotropic working medium after being separated in high-pressure gas-liquid separator 34
Steam is not needed using superheater, and dry saturation vapor has mainstream bulk properties, and non-azeotropic working medium dry saturation vapor is in high pressure turbine
It is not in the expansion of two-phase section in 5.The gas vent of high-pressure gas-liquid separator 34 constitutes non-azeotropic working medium high-pressure evaporation access 3
Gas vent, the gas vent of high-pressure gas-liquid separator 34 can be connected to the path end entrance of high pressure turbine 5, high-pressure gas-liquid point
Liquid outlet from device 34 is connected to the entrance of the 4th working medium passage, in the present embodiment, the inlet of the 4th working medium passage
The liquid outlet of connection setting second entrance header 35, the outlet of third working medium passage and high-pressure gas-liquid separator 34 can be with the
The connection of two influent headers 35.The 4th heat source heat transfer fluid channels 84, the 4th heat source heat exchange stream are additionally provided in high pressure evaporator 33
The entrance in body channel 84 and heat source heat exchanging fluid feedway (prior art is not shown in the figure) are connected to, the 4th heat source heat exchange stream
The outlet in body channel 84 is connected to the entrance of third heat source heat transfer fluid channels 83, the 4th heat source heat transfer fluid channels 84 and third
Heat source heat transfer fluid channels 83 constitute the first heat source access above-mentioned, and the heat source in the 4th heat source heat transfer fluid channels 84, which exchanges heat, to flow
The flow direction of body and the flow direction of the non-azeotropic working medium in the 4th working medium passage on the contrary, in the present embodiment, the first heat source access
The entrance of i.e. the 4th heat source heat transfer fluid channels 84 in inlet is provided with high temperature refrigerant and pumps 85 (400 DEG C of highest heatproofs), high temperature work
Matter pump 85 is connected to heat source feedway (prior art is not shown in the figure), and high temperature refrigerant pump 85 is heat source heat exchanging fluid the
Flowing provides power in one heat source access and Secondary Heat Source access.
As shown in Figure 1, in the present embodiment, gas vent, that is, high-pressure gas-liquid of non-azeotropic working medium high-pressure evaporation access 3
The gas vent sequence of separator 34 passes through the miner diameter end of high pressure turbine valve 51, high pressure turbine regulating valve 52 and high pressure turbine 5
Entrance connection, when stopping process, working medium are not up to relevant parameter, high pressure turbine valve 51 is in closed state, and system was run
Cheng Zhong, high pressure turbine valve 51 are in open state；The load of high pressure turbine 5 can be adjusted in high pressure turbine regulating valve 52,
When variable parameter operation, when turbine total load is lower than Design cooling load, it should preferentially guarantee that high pressure turbine 5 is run under optimum condition, with
Guarantee higher heat-power conversion efficiency.
In the present embodiment, low pressure preheater (LPP 22, low pressure evaporator 23, high pressure pre-heater 32, high pressure evaporator 33
Temperature inductor is respectively provided on outlet conduit, temperature inductor energy real-time monitoring simultaneously shows low pressure preheater (LPP 22, low pressure evaporator
23, the Temperature of Working that high pressure pre-heater 32, high pressure evaporator 33 export, also sets up on low pressure evaporator 23, high pressure evaporator 33
Pressure inductor, pressure inductor can monitor and show low pressure evaporator 23, the pressure value in high pressure evaporator 33, and high pressure is saturating
It puts down and is respectively provided with DEH governing system (prior art) on 5 and low pressure turbine 4, the non-azeotrope flowed out in low pressure preheater (LPP 22
It is two strands that working medium is divided to by working medium flow distributing valve 25, and the flow of two strands of non-azeotropic working mediums is according to high pressure turbine 5 and low pressure turbine 4
Power regulation characteristic, non-azeotropic working medium and heat source heat exchanging fluid Temperature Matching characteristic determine, the flow and heat of non-azeotropic working medium
Relationship between the heat exchanging fluid temperature of source can be determined by test.
In the present embodiment, low pressure preheater (LPP 22, low pressure evaporator 23, high pressure pre-heater 32, high pressure evaporator 33 are equal
For shell-and-tube heat exchanger, the first working medium passage is the shell channel in low pressure preheater (LPP 22, the first heat source heat transfer fluid channels 81
For the tube bank channel in low pressure preheater (LPP 22；Second working medium passage is the shell channel in low pressure evaporator 23, and Secondary Heat Source changes
Zone of heat liberation 82 is the tube bank channel in low pressure evaporator 23；Third working medium passage is that the shell in high pressure pre-heater 32 is logical
Road, third heat source heat transfer fluid channels 83 are the tube bank channel in high pressure pre-heater 32；4th working medium passage is high pressure evaporator
Shell channel in 33, the 4th heat source heat transfer fluid channels 84 are the tube bank channel in high pressure evaporator 33.
The work of one specific embodiment of the double pressure evaporation organic Rankine cycle power generation systems 100 of non-azeotropic working medium of the invention
Operational process is as follows:
Non-azeotropic working medium storage tank is connected to condenser 1 first, the non-azeotropic working medium injected in condenser 1 meets system need
After the amount of asking, non-azeotropic working medium storage tank is closed.Non-azeotropic working medium exchanges heat in condenser 1 with the recirculated water in cooling duct 11
It is condensed into liquid, the non-azeotropic working medium of liquid is entered the first working medium passage of low pressure preheater (LPP 22 after 21 pressurization of low pressure working fluid pump
Interior, the non-azeotropic working medium in heat source heat exchanging fluid and the first working medium passage in the first heat source heat transfer fluid channels 81 passes through adverse current
Mode exchanges heat, and non-azeotropic working medium is heated to the bubble lower than relevant pressure in the first working medium passage of low pressure preheater (LPP 22
After 3 DEG C of temperature of point, the first working medium passage of connection and working medium flow distributing valve 25, non-azeotropic working medium pass through working medium flow distributing valve 25
It is divided into two strands, one non-azeotropic working medium enters the second working medium passage of low pressure evaporator 23, the second heat through first entrance header 26
The non-azeotropic working medium in heat source heat exchanging fluid and the second working medium passage in source heat transfer fluid channels 82 is carried out by reflux type
Heat exchange, non-azeotropic working medium are heated to dew-point temperature (non-azeotropic working medium can be evaporated to dry saturation vapor state when dew-point temperature),
Non-azeotropic working medium enters low-pressure gas-liquid separator 24 from the second working medium passage, and low-pressure gas-liquid separator 24 is to low pressure non-azeotropic working medium
Drop entrained by gas carries out gas-liquid separation, and the liquid phase non-azeotropic working medium isolated is back to first entrance header 26, with work
The liquid phase non-azeotropic working medium that the distribution of matter flow divider valve 25 comes enters low pressure evaporator 23 together, and gas phase non-azeotropic working medium is through low
It presses turbine valve 41, low pressure turbine regulating valve 42 to enter 4 expansion work of low pressure turbine, rotates low pressure turbine 4, after expansion work
Lack of gas be back to condenser 1 into subsequent cycle；
Another stock is pumped by the non-azeotropic working medium that the second distribution outlet 252 of working medium flow distributing valve 25 shunts through high-pressure working medium
Enter the third working medium passage of high pressure pre-heater 32, the heat source heat exchanging fluid in third heat source heat transfer fluid channels 83 after 31 pressurizations
Exchanged heat with the non-azeotropic working medium in third working medium passage by reflux type, it is heated after non-azeotropic working medium pass through second
Influent header 35 enters the 4th working medium passage of high pressure evaporator 33, and the heat source in the 4th heat source heat transfer fluid channels 84, which exchanges heat, to flow
Body is exchanged heat with the non-azeotropic working medium in the 4th working medium passage by reflux type, and non-azeotropic working medium is heated to dew-point temperature
(non-azeotropic working medium can be evaporated to dry saturation vapor state when dew-point temperature), non-azeotropic working medium enters high pressure from the 4th working medium passage
Gas-liquid separator 34, high-pressure gas-liquid separator 34 carry out gas-liquid separation to drop entrained by high pressure non-azeotropic working medium gas, point
The liquid phase non-azeotropic working medium separated out is back to second entrance header 35, with the liquid phase non-azeotropic working medium come from the stream of high pressure pre-heater 32
Enter high pressure evaporator 33 together, gas phase non-azeotropic working medium enters high pressure through high pressure turbine valve 51, high pressure turbine regulating valve 52
5 expansion work of turbine rotates high pressure turbine 5, and the lack of gas after expansion work are back to condenser 1 into subsequent cycle；
High pressure turbine 5 and low pressure turbine 4 are connected by first shaft coupling 61, low pressure turbine 4 by second shaft coupling 62 and
The main shaft of generator 7 is connected, the main shaft coaxial rotating of high pressure turbine 5, low pressure turbine 4 and generator 7, completes power generation operation.
From the above mentioned, the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention have following beneficial to effect
Fruit:
(1) the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention pass through the double pressure evaporation collaborations of two-stage
Temperature glide characteristic in non-azeotropic working medium phase transition process improves the average endothermic temperature of non-azeotropic working medium, reduces non-azeotrope work
The Average heat transfer temperature difference between matter and heat source heat exchanging fluid reduces heat transfer process irreversible loss, improves the thermal efficiency of circulation, realizes
The High Efficiency Thermal of middle low temperature heat energy-function is converted, the fast development of low temperature heat energy power generation in promotion；
(2) high pressure turbine and low pressure are set in the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention
Turbine, the non-azeotropic working medium steam for avoiding different pressures mix in same turbine, and high pressure turbine and low pressure turbine are axis
Streaming turbine, high pressure turbine and low pressure turbine it is contrary, internal working medium flow direction is on the contrary, effectively balance portion is saturating
The axial thrust that non-azeotropic working medium flowing generates in flat；
(3) in the working medium flow distributing valve in the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention
It is provided with mass flowmenter, it can be by adjusting the distribution of double flash evaporation pressure and flow, flexible adaptation heat source in system operation
The variation of parameter or the adjustment of turbine power keep the Temperature Matching effect between heat source heat exchanging fluid and non-azeotropic working medium, pass through
The higher internal efficiency ratio of high pressure turbine is maintained, to guarantee the thermal efficiency of entire electricity generation system；
(4) the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium of the invention may be implemented 350 ° it is below too
High Efficiency Thermal-function conversion of positive energy, biomass energy, geothermal energy and industrial exhaust heat opposite can improve thermal effect compared to conventional electric power generation technology
Rate 10-30% can give full play to the advantage in middle low temperature heat energy power field；
(5) non-azeotropic working medium of the invention pair pressure evaporation organic Rankine cycle power generation systems are simple with system, run dimension
The advantages that shield is convenient and long service life, Organic Rankine Cycle installed capacity range in 1-10MW, can adaptation to local conditions be arranged in
The bulk power grids such as outlying district, frontier sentry, island are difficult to covering area, can be applied to the abundant area of renewable energy, carry out green
Color power generation, the industrial exhaust heat for being equally applicable for city distributed energy resource system and industrial and mining enterprises utilize.
The foregoing is merely the schematical specific embodiment of the present invention, the range being not intended to limit the invention.It is any
Those skilled in the art, made equivalent changes and modifications under the premise of not departing from design and the principle of the present invention,
It should belong to the scope of protection of the invention.
Claims (4)
1. a kind of double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium, including non-azeotropic working medium storage tank, described non-total
The exit for boiling working medium storage tank is connected to the condenser of condensation non-azeotropic working medium, it is characterised in that: the working medium of the condenser goes out
Mouth is communicated with non-azeotropic working medium low pressure evaporation flow paths and non-azeotropic working medium high-pressure evaporation access, the non-azeotropic working medium low pressure evaporation
The gas vent of access is connected to the path end entrance of a low pressure turbine, and the gas of the non-azeotropic working medium high-pressure evaporation access goes out
Mouth is connected to the path end entrance of a high pressure turbine, and the bigger diameter end of the high pressure turbine is opposite with the bigger diameter end of the low pressure turbine
Setting, the main shaft of the high pressure turbine are connect with main shaft one end of the low pressure turbine by first shaft coupling, and the low pressure is saturating
The flat main shaft other end is connected by the main shaft of second shaft coupling and generator；The high pressure turbine bigger diameter end outlet and it is described
The bigger diameter end outlet of low pressure turbine is connected to the entrance of the condenser；Setting in the non-azeotropic working medium high-pressure evaporation access
There is the first heat source access, second be connected to the first heat source access is provided in the non-azeotropic working medium low pressure evaporation flow paths
The entrance of heat source access, the first heat source access constitutes heat source heat exchanging fluid entrance, the outlet structure of the Secondary Heat Source access
It is exported at heat source heat exchanging fluid, the flow direction and the non-azeotropic working medium high pressure of the heat source heat exchanging fluid in the first heat source access
The flow direction of non-azeotropic working medium in evaporation flow paths on the contrary, the flow direction of the heat source heat exchanging fluid in the Secondary Heat Source access with it is described
The flow direction of non-azeotropic working medium in non-azeotropic working medium low pressure evaporation flow paths is opposite；
The non-azeotropic working medium low pressure evaporation flow paths include the low pressure working fluid pump being connected to the sender property outlet of condenser, the low pressure
A low pressure preheater (LPP is arranged in the outlet of working medium pump, is provided with the first working medium passage in the low pressure preheater (LPP, and described first
The entrance of working medium passage is connected to the low pressure working fluid pump discharge, and the outlet of first working medium passage is evaporated with a low pressure respectively
Device, high-pressure working medium pump are connected to, and are additionally provided with the first heat source heat transfer fluid channels, first heat source in the low pressure preheater (LPP
Heat source heat exchanging fluid described in the export mixes of heat transfer fluid channels exports, and the heat source in the first heat source heat transfer fluid channels changes
The flow direction of hot fluid is opposite with the flow direction of non-azeotropic working medium in first working medium passage；It is provided in the low pressure evaporator
Second working medium passage, the outlet of the entrance of second working medium passage and first working medium passage, second working medium
It is provided with to the outlet in channel low-pressure gas-liquid separator, the gas vent of the low-pressure gas-liquid separator constitutes described non-total
Boil the gas vent of working medium low pressure evaporation flow paths, the gas vent of the low-pressure gas-liquid separator and the path of the low pressure turbine
End entrance connection, the liquid outlet of the low-pressure gas-liquid separator are connected to the entrance of second working medium passage, the low pressure
Secondary Heat Source heat transfer fluid channels, the outlet of the Secondary Heat Source heat transfer fluid channels and described first are additionally provided in evaporator
The entrance of heat source heat transfer fluid channels is connected to, the Secondary Heat Source heat transfer fluid channels and the first heat source heat transfer fluid channels
Constitute the Secondary Heat Source access, the flow direction of the heat source heat exchanging fluid in the Secondary Heat Source heat transfer fluid channels and described second
The flow direction of non-azeotropic working medium in working medium passage is opposite；
The non-azeotropic working medium high-pressure evaporation access includes the high-pressure working medium pump, and the outlet of the high-pressure working medium pump has height
Preheater is pressed, third working medium passage, the entrance of the third working medium passage and the high pressure are provided in the high pressure pre-heater
Working medium pump outlet, is provided with to the outlet of the third working medium passage high pressure evaporator, in the high pressure pre-heater
Third heat source heat transfer fluid channels are additionally provided with, the outlet of the third heat source heat transfer fluid channels and the Secondary Heat Source exchange heat
The entrance of fluid channel is connected to, the flow direction and the third work of the heat source heat exchanging fluid in the third heat source heat transfer fluid channels
The flow direction of non-azeotropic working medium in matter channel is opposite；4th working medium passage, the 4th working medium are set in the high pressure evaporator
The outlet of the entrance in channel and the third working medium passage is provided with high pressure to the outlet of the 4th working medium passage
Gas-liquid separator, the gas that the gas vent of the high-pressure gas-liquid separator constitutes the non-azeotropic working medium high-pressure evaporation access go out
Mouthful, the gas vent of the high-pressure gas-liquid separator is connected to the path end entrance of the high pressure turbine, the high-pressure gas-liquid point
It is connected to from the liquid outlet of device with the entrance of the 4th working medium passage, the 4th heat source is additionally provided in the high pressure evaporator and is changed
The entrance of zone of heat liberation, the 4th heat source heat transfer fluid channels is connected to the heat source heat exchanging fluid feedway, described
The outlet of 4th heat source heat transfer fluid channels is connected to the entrance of the third heat source heat transfer fluid channels, and the 4th heat source changes
Zone of heat liberation and the third heat source heat transfer fluid channels constitute the first heat source access, the 4th heat source heat exchanging fluid
The flow direction of heat source heat exchanging fluid in channel is opposite with the flow direction of non-azeotropic working medium in the 4th working medium passage；
One working medium flow distributing valve is set to the outlet of first working medium passage, is arranged on the working medium flow distributing valve
There are the first distribution outlet and the second distribution outlet, first distribution outlet is connected to the entrance of second working medium passage, institute
The second distribution outlet is stated to be connected to high-pressure working medium pump；
Mass flowmenter is provided in the working medium flow distributing valve；
The inlet connection setting first entrance header of second working medium passage, the outlet of first working medium passage and described
The liquid outlet of low-pressure gas-liquid separator is connected to the first entrance header；
The inlet connection setting second entrance header of 4th working medium passage, the outlet of the third working medium passage and described
The liquid outlet of high-pressure gas-liquid separator is connected to the second entrance header；
The low pressure preheater (LPP, the low pressure evaporator, the high pressure pre-heater, the high pressure evaporator outlet conduit on
Be arranged temperature inductor, the temperature inductor real-time monitoring and show low pressure preheater (LPP, low pressure evaporator, high pressure pre-heater,
The Temperature of Working of high pressure evaporator outlet, also sets up pressure inductor on the low pressure evaporator, the high pressure evaporator, described
Pressure inductor monitors and shows low pressure evaporator, the pressure value in high pressure evaporator；
Non-azeotropic working medium is heated to the bubble point temperature 3 lower than relevant pressure in the first working medium passage of the low pressure preheater (LPP
℃；The bubble point temperature difference of non-azeotropic working medium is more than or equal to 10 DEG C in the high pressure evaporator and the low pressure evaporator.
2. the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium as described in claim 1, it is characterised in that: described
The gas vent sequence of non-azeotropic working medium high-pressure evaporation access passes through high pressure turbine valve, high pressure turbine regulating valve and the high pressure
The path end entrance of turbine is connected to, and the gas vent sequence of the non-azeotropic working medium low pressure evaporation flow paths passes through low pressure turbine gas
Door, low pressure turbine regulating valve are connected to the path end entrance of the low pressure turbine.
3. the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium as described in claim 1, it is characterised in that: described
The inlet of first heat source access is provided with high temperature refrigerant pump, and the high temperature refrigerant pump connects with heat source heat exchanging fluid feedway
It is logical.
4. the double pressure evaporation organic Rankine cycle power generation systems of non-azeotropic working medium as described in claim 1, it is characterised in that: described
Condenser working medium passage is provided in condenser, the working medium of condenser described in the export mixes of the condenser working medium passage goes out
Mouthful, cooling duct is additionally provided in the condenser, the entrance of the cooling duct passes through circulating cooling water pump and a cooling tower
Circulating water outlet connection, the outlet of the cooling duct is connected to the circulation water inlet of the cooling tower.
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| CN108561202A (en) * | 2018-01-10 | 2018-09-21 | 西安交通大学 | A kind of low-temperature solid bulk cargo heat utilization power generating system that anti-solid particle washes away |
| JP6941076B2 (en) * | 2018-06-05 | 2021-09-29 | 株式会社神戸製鋼所 | Power generation method |
| CN111396272B (en) * | 2020-02-18 | 2021-08-31 | 天津大学 | Groove type solar direct expansion type combined heat and power system adopting non-azeotropic working medium |
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| JP5738110B2 (en) * | 2011-07-20 | 2015-06-17 | 三菱重工業株式会社 | Double pressure radial turbine system |
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