CN102344178A - Thermal steam compression, evaporation and desalination system with function of steam reheating and method - Google Patents
Thermal steam compression, evaporation and desalination system with function of steam reheating and method Download PDFInfo
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- 238000010612 desalination reaction Methods 0.000 title claims abstract description 23
- 230000006835 compression Effects 0.000 title claims abstract description 21
- 238000007906 compression Methods 0.000 title claims abstract description 21
- 238000001704 evaporation Methods 0.000 title claims abstract description 21
- 230000008020 evaporation Effects 0.000 title claims abstract description 20
- 238000000034 method Methods 0.000 title claims abstract description 10
- 238000003303 reheating Methods 0.000 title claims abstract 7
- 238000010438 heat treatment Methods 0.000 claims abstract description 44
- 239000013535 sea water Substances 0.000 claims abstract description 32
- 239000007789 gas Substances 0.000 claims abstract description 3
- 239000011552 falling film Substances 0.000 claims description 15
- 239000000126 substance Substances 0.000 claims description 6
- 238000011084 recovery Methods 0.000 claims description 5
- 239000002918 waste heat Substances 0.000 claims description 3
- 238000000605 extraction Methods 0.000 claims 1
- 239000010842 industrial wastewater Substances 0.000 claims 1
- 238000005265 energy consumption Methods 0.000 abstract description 12
- 238000002347 injection Methods 0.000 abstract description 5
- 239000007924 injection Substances 0.000 abstract description 5
- 239000002351 wastewater Substances 0.000 abstract description 3
- 238000005516 engineering process Methods 0.000 abstract description 2
- 230000007613 environmental effect Effects 0.000 abstract description 2
- 238000004519 manufacturing process Methods 0.000 abstract description 2
- 238000006243 chemical reaction Methods 0.000 abstract 1
- 239000002440 industrial waste Substances 0.000 abstract 1
- 235000019600 saltiness Nutrition 0.000 description 24
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 24
- 238000010586 diagram Methods 0.000 description 15
- 230000001939 inductive effect Effects 0.000 description 15
- 239000002912 waste gas Substances 0.000 description 8
- 239000002910 solid waste Substances 0.000 description 7
- 238000000746 purification Methods 0.000 description 6
- 239000002994 raw material Substances 0.000 description 6
- 239000013505 freshwater Substances 0.000 description 5
- 238000011033 desalting Methods 0.000 description 4
- 239000010795 gaseous waste Substances 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000000740 bleeding effect Effects 0.000 description 3
- 238000004364 calculation method Methods 0.000 description 3
- 239000002826 coolant Substances 0.000 description 3
- 238000009776 industrial production Methods 0.000 description 2
- 238000002156 mixing Methods 0.000 description 2
- 238000007670 refining Methods 0.000 description 2
- FAPWRFPIFSIZLT-UHFFFAOYSA-M Sodium chloride Chemical compound [Na+].[Cl-] FAPWRFPIFSIZLT-UHFFFAOYSA-M 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 239000012267 brine Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000004821 distillation Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000003546 flue gas Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000010813 municipal solid waste Substances 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000010865 sewage Substances 0.000 description 1
- 239000011780 sodium chloride Substances 0.000 description 1
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A20/00—Water conservation; Efficient water supply; Efficient water use
- Y02A20/124—Water desalination
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02W—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO WASTEWATER TREATMENT OR WASTE MANAGEMENT
- Y02W10/00—Technologies for wastewater treatment
- Y02W10/30—Wastewater or sewage treatment systems using renewable energies
- Y02W10/37—Wastewater or sewage treatment systems using renewable energies using solar energy
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- Heat Treatment Of Water, Waste Water Or Sewage (AREA)
- Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
Abstract
一种带蒸汽再热的热力蒸汽压缩蒸发脱盐系统与方法，该系统特征是在卷吸蒸汽进入热力压缩机之前设置加热装置对卷吸蒸汽进行再热以提高其温度和比焓，从而提高热力蒸汽压缩蒸发海水淡化系统中的关键设备热力压缩机的引射系数，减少热力压缩机的工作蒸汽的耗量，降低系统能耗，提高系统性能比。本发明所涉及的加热装置的热源来源广泛，可以利用太阳能等可再生能源，也可以采用热泵等先进供能技术提供的能量，或常规能量生产、转换系统中产生的低品位能量，还可以应用工业废气、废水等作为加热热源，回收了热量，减少了环境热污染，节约了能量。
A thermal vapor compression evaporative desalination system and method with steam reheating, the system is characterized in that before the entrained steam enters the thermal compressor, a heating device is set to reheat the entrained steam to increase its temperature and specific enthalpy, thereby increasing the thermal power The injection coefficient of the thermal compressor, the key equipment in the vapor compression evaporation seawater desalination system, reduces the consumption of working steam of the thermal compressor, reduces the energy consumption of the system, and improves the system performance ratio. The heat source of the heating device involved in the present invention has a wide range of sources, and can use renewable energy such as solar energy, or energy provided by advanced energy supply technologies such as heat pumps, or low-grade energy generated in conventional energy production and conversion systems, and can also be used Industrial waste gas, waste water, etc. are used as heating heat sources to recover heat, reduce environmental heat pollution, and save energy.
Description
Technical field
Method of the present invention belongs to thermodynamic steam Compression Evaporation class method for desalting seawater, is mainly used in the desalination of seawater, brackish water and saline sewage.Through the improvement of certain way, can significantly reduce the energy consumption of thermodynamic steam Compression Evaporation seawater desalination system.
Background technology
Thermodynamic steam compression (thermal vapor compress TVC) is in thermal compressor (or being called the injection type compressor), to attract secondary steam to improve its temperature with high pressure steam; Steam after will compressing then sends back to continuation heating feed liquid in the evaporator room again, recycles the method for desalting seawater of steam latent heat.Thermodynamic steam Compression Evaporation method for desalting seawater is because the latent heat of low-pressure steam has obtained utilization repeatedly, thereby it is low to have energy consumption, and the advantage that equivalent water generation ratio is high has tangible technical superiority in many method for desalting seawater.
Fig. 1 is thermodynamic steam Compression Evaporation seawater desalination system figure, and existing is the workflow of example explanation TVC seawater desalination system with Fig. 1: mass rate is m
r, temperature is t
r, saltiness is s
rPending raw material seawater 11 get into the steam 9 that is come from falling-film evaporator 1 in the condensers 10 (mass rate be m
Sc, temperature is t
b, saltiness is 0) and to be preheating to temperature be t
f(mass rate is m to a raw material seawater part 15 after the preheating
f, temperature is t
f, saltiness is s
f) getting into falling-film evaporator 1, (mass rate is m to another part 13
Fc, temperature is t
f, saltiness is s
f) discharge as water coolant.(mass rate is m to raw material seawater 15 in the entering falling-film evaporator 1 by steam 2
s+ m
p, temperature is t
v, saltiness is 0) and the hot spots evaporation, (mass rate is m in heating steam 2
s+ m
p, temperature is t
v, saltiness is 0) a part to be condensed into mass rate by seawater be m
d, temperature is t
d, saltiness is 0 fresh water 8, and the part steam that is not condensed in steam that raw material seawater 15 evaporations produce in the falling-film evaporator 1 and the heating steam 2 is discharged falling-film evaporator together, and (mass rate is m to this part steam 7
Ec, temperature is t
b, saltiness is 0) and be divided into two portions, (mass rate is m to a part 5
s, temperature is t
b, saltiness is 0) and entrainmented 3 compressions of entering thermal compressor, (mass rate is m to another part 9
Sc, temperature is t
b, saltiness is 0) and get into preheating material seawater in the condenser 10.Mass rate is m
p, temperature is t
p, pressure is p
g High pressure steam 4 will (mass rate be m from the low-pressure steam 5 of falling-film evaporator 1
s, temperature is t
b, saltiness is 0) entrainment and get into thermal compressor 3 and boil down to high temperature saturation steam 2 (mass rate is m
s+ m
p, temperature is t
v, saltiness is 0) and get into falling-film evaporator 1 as heating medium.
Thermal compressor (or being called the injection type compressor) is the key equipment in the TVC seawater desalination system, and the quality of its serviceability is the important factor that influences TVC seawater desalination system energy consumption.Fig. 2 is the structure diagram of thermal compressor.The serviceability of thermal compressor is represented with the fluid mass of every kilogram of working steam institute injection, is called mass ratio of induced-to-inducing air,
Under the complete appropriate design condition of thermal compressor, as shown in Figure 1, according to the energy-balance equation of thermal compressor 3, m
ph
V, p+ m
sh
V, s=(m
p+ m
s) h
V, c(2) and utilize the definition (1) of mass ratio of induced-to-inducing air
H wherein
V, pBe the specific enthalpy of working steam 4, J/kg, h
V, sFor entrainmenting the specific enthalpy of steam 5, J/kg, h
V, cBe the specific enthalpy of thermal compressor outlet mixing steam 2, J/kg, η
ThBe the thermodynamics sophistication of thermal compressor 3, η under the ideal situation
ThBe 1.
In existing thermodynamic steam Compression Evaporation (TVC) seawater desalination system, entrainment steam 5 and get into thermal compressor 3 temperature t before
bWith specific enthalpy h
V, sLower; Be unfavorable for the raising of thermal compressor 3 mass ratio of induced-to-inducing airs and the reduction of system energy consumption, the present invention is intended to improve temperature of entrainmenting steam 5 and the specific enthalpy that gets into thermal compressor 3, to improve the serviceability of thermal compressor 3; Improve its mass ratio of induced-to-inducing air, reduce system energy consumption.
Summary of the invention
For reaching the mass ratio of induced-to-inducing air that improves thermal compressor 3; Reduce the purpose of thermodynamic steam Compression Evaporation (TVC) seawater desalination system energy consumption; The present invention intends and takes following technical scheme: in thermodynamic steam Compression Evaporation (TVC) seawater desalination system; This system comprises falling-film evaporator successively; Thermal compressor, flow distributor and condenser; It is characterized in that: between thermal compressor and flow distributor, be provided with and carry out the heating unit of heat again entrainmenting steam.Carry out again heat improving its temperature and specific enthalpy to entrainmenting steam 5, thereby improve the mass ratio of induced-to-inducing air of thermal compressor 3, reduce the energy consumption of system.
Described to entrainmenting the heating unit solar thermal collection system that steam carries out heat again; Heat pump; Trade effluent, waste gas Waste Heat Recovery System (WHRS), perhaps thermal power plant, the low-grade steam heat recovery system in chemical plant and work main steam bleed reheat system etc. all can entrainment system and the device of steam heating to preset temperature.
Use the method for said system, it is characterized in that: the steam that entrainments being obtained by falling-film evaporator evaporation is provided with heating unit before getting into thermal compressor and carries out heat improving its temperature and specific enthalpy to entrainmenting steam again, and reheat temperature is no more than 70 ℃.Thereby improve the mass ratio of induced-to-inducing air of thermal compressor, reduce the working steam consumption of thermal compressor, reduce the energy consumption of thermodynamic steam Compression Evaporation seawater desalination system, improve the performance ratio of system.
The temperature of entrainmenting after the steam heating can change in very wide scope in theory, but is understood that it at the most near the temperature out of thermal compressor steam (also i.e. first vaporization temperature of imitating falling-film evaporator), and good more near this temperature more.Certainly, the concrete numerical value of this temperature mainly confirmed by the factor of two aspects, one be the heat source temperature that can be used for heating reheated steam (for example, if with sun power as the boosting thermal source, then present stage real Heating temperature should not be above 60 ℃; And if with high-temperature residual heats such as flue gases, then this temperature can be higher), another is the height of the working temperature of TVC system, when working temperature was high, reheat temperature also can be higher
Technical scheme synoptic diagram of the present invention as shown in Figure 3.Existing is that principle of the present invention is set forth in example and the introduction that combines aforementioned background art with Fig. 3: suc as formula (3)
Shown in the expression formula of thermal compressor 3 mass ratio of induced-to-inducing airs, at the parameter (m of given working steam 4
p, t
p, h
V, p) and the maximum operating temperature t of thermodynamic steam Compression Evaporation seawater desalination system
v, (thermal compressor outlet steam 2 is saturation steam, so, if its temperature t
v, confirm that it is than enthalpy h so
V, cAlso confirm thereupon) and thermal compressor thermodynamic(al) efficiency η
ThPrerequisite under, improve to get into the specific enthalpy h that entrainments steam 5 of thermal compressor 3
V, sCan improve the mass ratio of induced-to-inducing air and the serviceability of thermal compressor 3, reduce system energy consumption.The thermal source that is used to heat the heating unit 24 that entrainments steam 5 among Fig. 3 can obtain from following approach:
A. thermal power plant, the low-grade steam in chemical plant
Can fully reclaim the heat of the low-grade steam in thermal power plant and chemical plant, improve the thermo-efficiency in thermal power plant and chemical plant.
B. heat pump or solar energy heat collector
Heat pump be a kind of with consume portion of energy by way of compensation condition be the thermal power transfer that can not directly be utilized in air, soil, the water the energy-efficient energy use device of utilizable heat energy; Therefore, the thermal source of heating unit 24 can consider to adopt this efficient energy-saving device in the synoptic diagram 3 of the present invention.Except that heat pump, solar thermal collection system is owing to have energy clean and safe, and simple in structure, the advantage of reliable operation also can be considered as and heat the heating unit that entrainments steam 5 among the present invention.
C. industrial colling, industrial gaseous waste
Produce a large amount of water coolant that carries certain heat and waste gas in the various industrial production,, it is discharged in the environment, not only can cause the thermal pollution of environment, and cause the waste of energy if do not reclaim this heat wherein.Therefore, the thermal source of heating unit 24 of the present invention also can be realized with the form that reclaims cooling water of industrial production and waste gas.
D. combine with the solid waste roasting kiln
The steam that utilizes waste heat boiler to produce remakes as thermal source or after the generating of intermediate steam turbine and is thermal source.
The present invention has following major technique advantage:
1. thermo-efficiency is high.Thermodynamic steam Compression Evaporation seawater desalination system itself is owing to the latent heat that has made full use of secondary steam just has than higher thermo-efficiency; The present invention is provided with 24 pairs of heating units before getting into thermal compressors 3 and entrainments steam 5 and carry out heat to improve its temperature and specific enthalpy again entrainmenting steam 5; Improve the mass ratio of induced-to-inducing air of thermal compressor 3, thereby can further improve the thermo-efficiency of whole thermodynamic steam Compression Evaporation seawater desalination system.
2. energy consumption is low.Compare with existing thermodynamic steam Compression Evaporation seawater desalination system,, reduced the consumption of working steam 4 owing to improved the mass ratio of induced-to-inducing air of thermal compressor 3.Be used to heat the heating unit 24 that entrainments steam 5 and try one's best, alleviated environmental thermal pollution, practiced thrift energy to reclaim trade effluent, waste gas or to adopt energy-efficient energy use device to realize.
3. practical.Heating unit 24 can utilize the low-grade steam in solar thermal collection system, heat pump, thermal power plant and chemical plant, trade effluent and waste gas and solid waste boiler etc., and more than device or system all are the technical development comparative maturities, and be therefore, workable.
Description of drawings
Fig. 1 is the heating power distillation seawater desalination system figure that calms the anger;
Fig. 2 is the structure diagram of thermal compressor;
Fig. 3 is a technical scheme synoptic diagram of the present invention;
Fig. 4 is the system diagram of embodiment one;
Fig. 5 is the system diagram of embodiment two;
Fig. 6 is the system diagram of embodiment three;
Fig. 7 is the system diagram of embodiment four;
Fig. 8 is the system diagram of embodiment five;
Fig. 9 is the system diagram of embodiment six;
Figure 10 is the system diagram of embodiment seven;
Label is among the accompanying drawing 1-10:
The 1-falling-film evaporator
(mass rate is m to 2-thermal compressor outlet steam
s+ m
p, temperature is t
v, saltiness is 0)
3-thermal compressor (injection type compressor)
(mass rate is m to 4-thermal compressor import step steam
p, temperature is t
p, pressure is p
g)
The 5-thermal compressor entrainments steam, and (mass rate is m
s, temperature is t
b, saltiness is 0)
The 6-flow distributor
(mass rate is m to 7-falling-film evaporator evaporated vapor
Ec, temperature is t
b, saltiness is 0)
(mass rate is m to 8-fresh water
d, temperature is t
d, saltiness is 0)
(mass rate is m to the steam of 9-entering condenser preheating seawater
Sc, temperature is t
b, saltiness is 0)
The 10-condenser
(mass rate is m to the 11-raw material seawater
r, temperature is t
r, saltiness is s
r)
12-condenses, and (mass rate is m to fresh water
Df, temperature is t
Df, saltiness is 0)
(mass rate is m to 13-row water coolant
Fc, temperature is t
f, saltiness is s
f)
(mass rate is m to the 14-strong brine
Ex, temperature is t
Ex, saltiness is s
Ex)
(mass rate is m to the raw material seawater of 15 entering falling-film evaporators
f, temperature is t
f, saltiness is s
f)
16-thermal compressor high-pressure work steam
The 17-suction chamber
The 18-jet pipe
19-throat
The 20-thermal compressor entrainments steam
The 21-straight length
The 22-diffuser pipe
The 23-mixing steam
The 24-heating unit
25-water-vapour interchanger
The 26-flat-plate solar collector
The 27-steam water heat exchanger
The 28-compressor
The 29-coil heat exchanger
The 30-reservoir
The 31-trade effluent
The 32-pump
33-trade effluent-vapour interchanger
The 34-waste water purification device
The 35-industrial gaseous waste
The 36-blower fan
37-industrial gaseous waste-vapour interchanger
The 38-waste gas purification apparatus
39-working steam-entrainment vapor heat exchanger
40-steam turbine of thermal power plant lower pressure stage is drawn gas
41-entrainments steam-low-pressure pumping steam interchanger
42-thermal power plant condenser
43-power plant boiler supplementary feed
44-solid waste burning boiler
The water vapour that 45-solid waste burning boiler produces
46-steam-electric power turbine
The exhaust steam of 47-steam-electric power turbine final stage
48-entrainments steam-final stage exhaust steam interchanger
49-exhaust steam condensed water
Embodiment
A thermodynamic steam Compression Evaporation brackish water desalination system of overlapping 200 tons of fresh water of daily output that plans to build with certain the Northwest is that example illustrates effect of the present invention below:
The cover single-action TVC brackish water desalination system that establishes is planned to build in NORTHWEST CHINA drought and water shortage area.As shown in Figure 3, require fresh water yield m
D, nBe 200t/d, the temperature t of pending brackish water 11
rWith saltiness s
rBe respectively 25 ℃ and 0.015kg/kg, concentrated solution 14 saltiness S
ExBe 0.05kg/kg.The s main working parameters of thermal compressor 3 is: working steam 4 pressure P
gBe 0.3MPa, temperature t
pBe 133.556 ℃, the pressure p of initially entrainmenting steam 5
eAnd temperature t
bBe respectively 0.0096MPa and 45 ℃, the temperature t of thermal compressor 3 outlet steam 2
vAnd pressure p
vBe respectively 70 ℃ and 0.031MPa.Heating unit 24 heating are set entrainment steam 5, the steam 5 that entrainments that gets into thermal compressor 3 is heated to 50 ℃ respectively, 55 ℃, 60 ℃, the mass ratio of induced-to-inducing air μ of calculating and its thermal compressor 3 of comparison, the consumption m of working steam 4
p(kg/s), entrainment the flow m of steam 5
s(kg/s) and system performance than PR, calculation result is as shown in table 1:
Table 1 difference is entrainmented the system performance parameter calculation result of vapor temperature
| Entrainment vapor temperature t b(℃) | 45 | 50 | 55 | 60 |
| Mass ratio of induced-to-inducing air μ | 2.0375 | 2.6019 | 3.5985 | 5.8329 |
| Working steam consumption m p(kg/s) | 0.7914 | 0.6702 | 0.5270 | 0.3560 |
| Entrainment steam flow m s(kg/s) | 1.6126 | 1.7438 | 1.8962 | 2.0767 |
| System performance compares PR | 2.9249 | 3.4539 | 4.3924 | 6.5022 |
Calculation result by table 1 can find out that along with the raising of the temperature of entrainmenting steam 5, the mass ratio of induced-to-inducing air of thermal compressor 3 improves gradually, and the consumption of working steam 4 reduces, and the flow that entrainments steam 5 increases, and system performance is than rising.
Example 1 is done with solar water heater and is entrainmented steam thermal source again.Fig. 4 is the system schematic of this example.The collector area of entrainmenting the flat-plate solar heat collector 26 of steam 5 settings for heating can be calculated by following formula (4):
Wherein:
A
cBe solar energy collector collector area, m
2
Q
WBe daily water consumption, kg;
t
EndBe the final temperature of water in the water tank, ℃;
C
WFor specific heat of water holds, kJ/kg. ℃;
t
iBe the initial temperature of water, ℃;
J
TBe the average daily radiation quantity of the sun on the heat collector heating surface, kJ/m
2
F is the sun power fraction, zero dimension;
η
CdBe the full-time collecting efficiency of heat collector;
η
LBe pipeline and water tank heat loss rate, zero dimension;
Through the collector area that calculates required solar energy collector is 20.34m
2
Example 2 with heat pump as entrainmenting steam thermal source again.System parameter is identical with example 1, and system diagram as shown in Figure 5.The device that steam 5 is entrainmented in heating is with comprising steam water heat exchanger 27, compressor 28, and coil heat exchanger 29, reservoir 30 is at interior earth-source hot-pump system.Elder generation gets into thermal compressor 3 through heating in the steam water heat exchanger 27 in the heat pump after the raising temperature again before entrainmenting steam 5 entering thermal compressors 3.Heat pump need supply with entrainment steam 5 heat by formula Q
h=m
s(h
60-h
45) (5) calculating, through calculating Q
h=42.717774kW.Heating efficiency formula COP by heat pump
h=Q
h/ P (6), the heating efficiency COP of heat-obtaining pump
h=4, be 10.68kW through the power P that calculates heat pump consumption.
Example 3 with trade effluent as entrainmenting steam thermal source again.System performance parameter is identical with example 1, and the thermal source that steam 5 is entrainmented in heating adopts trade effluent, and system diagram as shown in Figure 6.The trade effluent 31 that comes out from production plant is delivered into trade effluent-vapour interchanger 33 and is entrainmented steam 5 and carry out thermal exchange by pump 32; Steam 5 is entrainmented in heating; Heat is able to reclaim the back and gets into waste water purification device 34, after the refining plant purification reaches emission standard, is discharged in the environment.
Example 4 with industrial gaseous waste as entrainmenting steam thermal source again.System performance parameter is identical with example 1, and the thermal source that steam 5 is entrainmented in heating adopts industrial gaseous waste, and system diagram as shown in Figure 7.The waste gas 35 that gives off from industrial equipments such as engine, boiler etc. is delivered into industrial gaseous waste-vapour interchanger 37 and is entrainmented steam 5 and carry out thermal exchange by blower fan 36; Steam 5 is entrainmented in heating; Heat is able to reclaim the back and gets into waste gas purification apparatus 38, after the refining plant purification reaches emission standard, is discharged in the environment.
Example 5 is bled as entrainmenting steam thermal source again with main steam.System performance parameter is identical with example 1, and the thermal source that steam 5 is entrainmented in heating adopts working steam 4 to bleed, and system schematic as shown in Figure 8.Before entrainmenting steam 5 entering thermal compressors 3, from the higher working steam 4 of temperature and pressure, extract a part of steam out and be used for heating entrainmenting steam 5, entrainment the temperature and the specific enthalpy of steam 5 with raising.
Example 6 is bled as entrainmenting steam thermal source again with steam turbine in thermal power plant.System performance parameter is identical with example 1, entrainments steam 5 with the steam turbine in thermal power plant steam heating of bleeding, and system schematic as shown in Figure 9.The steam turbine in thermal power plant steam 40 of bleeding was used for earlier before getting into condenser 42 to entrainmenting steam 5 heating, sent behind the recovery part heat that preboiler supplementary feed 43 further reclaims heats in the steam-condenser of thermal power plants 42 back to again.This scheme can make full use of bleeding of heat power plant; Be specially adapted to sea water desaltination-thermal power generation association system; Not only improved the energy utilization rate of power plant; Improved simultaneously the mass ratio of induced-to-inducing air of the temperature, specific enthalpy and the thermal compressor that entrainment steam again; Reduce the working steam consumption, reduced the energy consumption of thermodynamic steam Compression Evaporation seawater desalination system.
Example 7 application garbage burning boiler systems provide entrainments the hot more required heat of steam.System performance parameter is identical with example 1, and the thermal source that steam 5 is entrainmented in heating utilizes the solid waste burning boiler to produce, and the steam after the generating of intermediate steam turbine is as thermal source, and system schematic as shown in figure 10.Extract out from steam turbine last stage from the water vapour 45 entering steam-electric power turbines 46 acting backs that solid waste burning boiler 44 produces; Get into interchanger 48 and entrainment steam 5 and carry out thermal exchange; Improve the temperature of entrainmenting steam 5; Reclaim the heat of exhaust steam 47, exhaust steam 47 heating are entrainmented and are condensed into condensed water 49 behind the steam 5 and return solid waste burning boiler 44.
Claims (3)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011102172225A CN102344178A (en) | 2011-07-29 | 2011-07-29 | Thermal steam compression, evaporation and desalination system with function of steam reheating and method |
Applications Claiming Priority (1)
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| CN2011102172225A CN102344178A (en) | 2011-07-29 | 2011-07-29 | Thermal steam compression, evaporation and desalination system with function of steam reheating and method |
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Cited By (8)
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| CN102705273A (en) * | 2012-06-05 | 2012-10-03 | 天津大学 | Method and device for mechanically pressurizing, injecting and recovering waste steam for suction section |
| CN102718273A (en) * | 2012-06-25 | 2012-10-10 | 潘育坛 | Grease-containing wastewater evaporation concentrating equipment and concentrating method thereof |
| CN103383169A (en) * | 2013-08-12 | 2013-11-06 | 南京协众汽车空调集团有限公司 | Air conditioning system using engine waste heat |
| CN103910398A (en) * | 2014-03-28 | 2014-07-09 | 南京航空航天大学 | System and method for desalinating seawater through absorbing solar energy via liquid-solid fluidized bed |
| CN106178572A (en) * | 2016-08-21 | 2016-12-07 | 侴乔力 | Condensing source heat pump backheat drives multi-effect distilling technique |
| CN106241961A (en) * | 2016-09-06 | 2016-12-21 | 大唐环境产业集团股份有限公司 | A kind of water treatment facilities utilizing residual heat of electric power plant and method |
| CN107976056A (en) * | 2017-11-24 | 2018-05-01 | 广州泉能智能科技股份有限公司 | Heat pump vacuum evaporator |
| CN113896266A (en) * | 2021-11-15 | 2022-01-07 | 江苏科技大学 | A compression ejection composite heat pump sewage treatment system and its operation method |
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Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102705273A (en) * | 2012-06-05 | 2012-10-03 | 天津大学 | Method and device for mechanically pressurizing, injecting and recovering waste steam for suction section |
| CN102718273A (en) * | 2012-06-25 | 2012-10-10 | 潘育坛 | Grease-containing wastewater evaporation concentrating equipment and concentrating method thereof |
| CN102718273B (en) * | 2012-06-25 | 2013-09-04 | 潘育坛 | Grease-containing wastewater evaporation concentrating equipment and concentrating method thereof |
| CN103383169A (en) * | 2013-08-12 | 2013-11-06 | 南京协众汽车空调集团有限公司 | Air conditioning system using engine waste heat |
| CN103910398A (en) * | 2014-03-28 | 2014-07-09 | 南京航空航天大学 | System and method for desalinating seawater through absorbing solar energy via liquid-solid fluidized bed |
| CN106178572A (en) * | 2016-08-21 | 2016-12-07 | 侴乔力 | Condensing source heat pump backheat drives multi-effect distilling technique |
| CN106241961A (en) * | 2016-09-06 | 2016-12-21 | 大唐环境产业集团股份有限公司 | A kind of water treatment facilities utilizing residual heat of electric power plant and method |
| CN107976056A (en) * | 2017-11-24 | 2018-05-01 | 广州泉能智能科技股份有限公司 | Heat pump vacuum evaporator |
| CN113896266A (en) * | 2021-11-15 | 2022-01-07 | 江苏科技大学 | A compression ejection composite heat pump sewage treatment system and its operation method |
| CN113896266B (en) * | 2021-11-15 | 2023-05-02 | 江苏科技大学 | Compression injection combined heat pump sewage treatment system and operation method thereof |
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