CN102062494B - Hybrid boosting type refrigeration complex circular indirect air cooling system and operation adjustment method - Google Patents
Hybrid boosting type refrigeration complex circular indirect air cooling system and operation adjustment method Download PDFInfo
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Abstract
The invention relates to a hybrid boosting type refrigeration complex circular indirect air cooling system, wherein a refrigeration cycle formed by connecting a jet mixer in series with a first boost pump is independently connected in series with a turbine exhaust port through a dual-phase change heat exchanger; an exit of the first boost pump is communicated with an inlet of an air cooling radiator through a gas-liquid separator to form a hybrid boosting type refrigerating cycle which only operates at high-temperature time period; at low-temperature time period, partial functions of the reverse refrigeration cycle of the prior art can be still implemented only by properly adjusting the operation conditions with the operation adjustment method provided by the invention, namely partially utilizing the environment low-temperature resources; the jet mixer is mainly used for sufficiently mixing gaseous refrigerant and liquid refrigerant, and thus the flow structure of a jet head of the jet mixer is preferably aimed at maximum jet coefficient; the boost function of the refrigeration cycle is implemented by the post-first boost pump; and the system has the advantages of simple structure, reasonable design, low construction cost, good implementation feasibility and high cost performance.
Description
Technical field
The present invention relates to air cooling and refrigeration system technical field indirectly, is a kind of mixing boost type refrigeration combined-circulation indirect air cooling system and operation method of adjustment.
Background technology
Chinese invention patent application publication number CN101368767A; Title " adopt parallel connection just, the indirect air cooling method and the system of the working medium of contrary kind of refrigeration cycle "; Chinese invention patent application publication number CN101504219A, title " air indirect cooling method and the system of the circulation of ammonia water absorbing compound-refrigerating " and Chinese invention patent application publication number CN101608848A " air indirect cooling method of electric jet type combined kind of refrigeration cycle and system " disclose three kinds of indirect cooling systems.Adopt parallel connection just, the working medium of contrary kind of refrigeration cycle between cooling system be cooling system between compression, the compressor of cooling system consumes the mechanical power amount and enlarges markedly with the rising of ambient air temperature between compression, though can make steam turbine oepration at full load in summer, cost is big; Though the cooling system wasted work has only about 1/10 of cooling system between compression between ammonia water absorbing compound-refrigerating circulation, system complex, bulky, coefficient of refrigerating performance is low, and the technology barrier of maximization still can't be gone beyond at present; Cooling system boosts cold-producing medium with injector between electric jet type combined kind of refrigeration cycle, and efficient is very low, and the space of boosting is limited.And the contrary kind of refrigeration cycle of above-mentioned three kinds of cooling systems does not still have economically viable embodiment at present.
Summary of the invention
The objective of the invention is; Provide a kind of simple and reasonable for structure; The ratio of performance to price is high; Make the steam turbine oepration at full load at high temperature period mixing boost type refrigeration capable of using combined-circulation, then can realize the mixing boost type refrigeration combined-circulation indirect air cooling system that the part of low ambient temperature resource is utilized and move method of adjustment through suitable operation adjustment in the low temperature period.
Realize that the technical scheme that the object of the invention adopted is: a kind of mixing boost type refrigeration combined-circulation indirect air cooling system; It is characterized in that: it comprises that the steam entry of two phase-change heat-exchanger 5 high temperature sides is connected with steam turbine exhaust outlet 4, and the hot well port of export of two phase-change heat-exchangers 5 is connected with the condensate pump of Steam Power Circulation 6 inlets; The cold-producing medium output of two phase-change heat-exchanger 5 low temperature sides sucks end through the first stop valve 8a with the gaseous refrigerant of jet mixer 12 and is communicated with; The cold-producing medium output of two phase-change heat-exchanger 5 low temperature sides is communicated with gas-liquid separator 14 inputs through the second stop valve 8b; The output of jet mixer 12 is communicated with gas-liquid separator 14 inputs through first booster 13; The liquid output of gas-liquid separator 14 is communicated with liquid reserve tank 17 inputs through the 4th stop valve 19; The gaseous state output of gas-liquid separator 14 is communicated with the input of air cooling heat radiator 15; The output of air cooling heat radiator 15 is communicated with the input of liquid reserve tank 17; The output of liquid reserve tank 17 is communicated with second booster 21 of parallel connection and the input of choke valve 20 through first output of triple valve 18, and second booster 21 of parallel connection and the output of choke valve 20 are communicated with the input of two phase-change heat-exchanger 5 low temperature sides; The output of liquid reserve tank 17 is communicated with the input of the 3rd stop valve 10 through second output of triple valve 18; The output of the 3rd stop valve 10 is communicated with the constant pressure pump 9 of parallel connection and the input of by-passing valve 11, and the constant pressure pump 9 of parallel connection and the output of by-passing valve 11 are communicated with the liquid refrigerant injector head input of jet mixer 12.
The structure of described jet mixer 12 is; Comprise liquid refrigerant injector head 23, mixing chamber 24, trunnion 25 and diffuser 26; Liquid refrigerant injector head 23 places the front end in the mixing chamber 24, and mixing chamber 24 is connected with trunnion 25, diffuser 26 order on same axis.
The structure of the liquid refrigerant injector head 23 of described jet mixer is; Comprise the circular arc face shield 28 that the port of export with high pressure liquid refrigerant pipeline 27 is connected; Be embedded with several nozzles of arranging ringwise on the circular arc face shield 28; Several nozzles that the core space of circular arc face shield 28 is embedded with all are contraction and enlargement nozzles 29, and several nozzles that the peripheral all circles of the core space of circular arc face shield 28 are embedded with all are negative throat noz(zle)s 22; The axis of contraction and enlargement nozzle 29 and jet mixer axially parallel, the axis of negative throat noz(zle) 22 are all perpendicular with circular arc face shield 28 outer surfaces.
Described trunnion 25 is cylindrical trunnion, and its length is 16～35 times of internal diameter.
A kind of operation method of adjustment of mixing boost type refrigeration combined-circulation indirect air cooling system is characterized in that: implemented automatically according to the adjustment software of operation method of adjustment establishment by industrial computer:
The high ambient temperature period: implement positive kind of refrigeration cycle operation; The saturated gaseous refrigerant of two phase-change heat-exchanger 5 low temperature sides outlets is connected with the gaseous refrigerant suction inlet of jet mixer 12 through the first stop valve 8a; Gaseous refrigerant is sucked mixing chamber 14 by the high pressure liquid refrigerant that penetrates from the liquid refrigerant injector head; And then mix and flowing in the trunnion 15 back of further mixing, boost and get into first booster 13, after the mutually mixed uniformly cold-producing medium of gas-liquid is boosted to the condensing pressure of air cooling heat radiator, get into gas-liquid separator 14 and separate; Isolated liquid refrigerant gets into liquid reserve tank 17 through the 4th stop valve 19; Gaseous refrigerant then gets into air cooling heat radiator 15 condensation heat releases, and through 18 fens two-way of triple valve, one tunnel condensed liquid refrigerant enters the mouth to choke valve 20 through first output of triple valve 18 condensed liquid refrigerant through liquid reserve tank 17; The pressure ratio of pressing the instruction appointment of industrial computer gets into the low temperature side inlet that two-phase becomes heat exchanger 5 after throttling, implement positive kind of refrigeration cycle operation; The condensed liquid refrigerant in another road is through second output of triple valve 18; Arrive the by-passing valve 11 and constant pressure pump 9 inlets of parallel connection through the 3rd stop valve 10; Equally after constant pressure pump 9 boosts, get back to liquid refrigerant pipeline 27 inlets of jet mixer 12 through by-passing valve 11 or by the pressure ratio of appointment, implement the suction gaseous refrigerant and mix with it by the instruction of industrial computer;
The low ambient temperature period: positive kind of refrigeration cycle is out of service; By industrial computer automatically operation second booster 21 make the steam turbine delivery temperature follow ambient air temperature when changing and to keep the low temperature side cold-producing medium boiling parameter and the air cooling heat radiator 15 condensation of refrigerant parameters of two phase-change heat-exchangers 5 identical; The low temperature side outlet gaseous refrigerant of two phase-change heat-exchangers 5 directly gets into gas-liquid separator 14 through the second stop valve 8b, and isolated liquid refrigerant gets into liquid reserve tank 17 through the 4th stop valve 19; Isolated gaseous refrigerant is through the gas-distribution pipe of air cooling heat radiator 15 and get into each cooling duct respectively and carry out the condensation heat release; Liquid refrigerant after condensing gets into liquid reserve tank 17; Arrive the arrival end of second booster 21 again through triple valve 18 first outputs; Get into the low temperature side inlet that two-phase becomes heat exchanger 5 by the pressure ratio of the instruction appointment of the industrial computer back of boosting, implements virtual contrary kind of refrigeration cycle and move.
The advantage applies of mixing boost type refrigeration combined-circulation indirect air cooling system of the present invention exists: the one, and system is in the high temperature period; Be in series with jet mixer serial connection booster composition refrigeration machine and Steam Power Circulation; Its outlet then is connected with the air cooling heat radiator inlet through gas-liquid separator, implements positive kind of refrigeration cycle operation; The calculation control software that the low temperature period then utilizes industrial computer to work out according to custom-designed operation method of adjustment is implemented virtual contrary kind of refrigeration cycle operation automatically, has not only simplified system but also saved investment; The 2nd, specialized designs of the present invention a kind of capital equipment---refrigerant superheat device and prime mover that need not contrary kind of refrigeration cycle; But still can realize the operation method of adjustment of its partial function; In servicely utilize industrial computer to instigate system to follow ambient air temperature automatically to change and adjust accordingly according to the operation method of adjustment; Utilize the low ambient temperature resource with part, promptly implement contrary kind of refrigeration cycle function of the prior art; The 3rd, the multi-jet jet mixer of long trunnion is mainly used in the abundant mixing of liquid refrigerant and gaseous refrigerant; Can guarantee that through preferred injector head fluidal texture blender has the highest mass ratio of induced-to-inducing air, thereby make the rearmounted booster wasted work of implementing boost function minimum; The 4th, system architecture is simple, reasonable, and cheap, operational feasibility is better, and the ratio of performance to price is high.
Mixing boost type of the present invention refrigeration combined-circulation indirect air cooling system and operation method of adjustment be applicable to thermoelectricity, nuclear power, gas-steam combined circulation, integral coal gasification generating and solar energy thermal-power-generating and in, the steam exhausting cooling method and the system of the steam turbine that utilizes of low temperature exhaust heat, or the indirect air cooling method and the system thereof of the working medium that is cooled of the big-and-middle-sized cooler of multiple industries such as iron and steel, oil, chemical industry, nonferrous metallurgy, weaving, papermaking, food, pharmacy.
Description of drawings
Fig. 1 is a mixing boost type refrigeration combined-circulation indirect air cooling system structure sketch map of the present invention.
Fig. 2 is jet mixer 12 structure cutaway views.
Fig. 3 is an A-A profile among Fig. 2.
Fig. 4 is liquid refrigerant injector head 23 structure cutaway views.
Fig. 5 is the right view of Fig. 4.
Fig. 6 is an I partial enlarged drawing among Fig. 4.
Fig. 7 is an II partial enlarged drawing among Fig. 4.
Fig. 8 is the diffuser dimensional drawing.
Fig. 9 is the change curve of exposure with ambient air temperature.
Among the figure: 1 steam turbine air inlet, 2 steam turbines, 3 generators, 4 steam turbine exhaust outlets, 5 pairs of phase-change heat-exchangers, 6 condensate pumps; 7 go heat regenerative system, 8a first stop valve, 8b second stop valve, 9 constant pressure pumps, 10 the 3rd stop valves, 11 by-passing valves; 12 jet mixers, 13 first boosters, 14 gas-liquid separators, 15 air radiators, 16 air cooling blower fans, 17 liquid reserve tanks; 18 triple valves, 19 the 4th stop valves, 20 choke valves, 21 second boosters, 22 negative throat noz(zle)s, 23 liquid refrigerant injector heads; 24 mixing chambers, 25 trunnions, 26 diffusers, 27 high pressure liquid refrigerant pipelines, 28 circular arc face shields, 29 contraction and enlargement nozzles.
The specific embodiment
Utilize the accompanying drawing and the specific embodiment that the present invention is described further below.
With reference to Fig. 1; Mixing boost type refrigeration combined-circulation indirect air cooling system of the present invention comprises that the steam entry of two phase-change heat-exchanger 5 high temperature sides is connected with steam turbine exhaust outlet 4, and the hot well port of export of two phase-change heat-exchangers 5 is connected with the condensate pump of Steam Power Circulation 6 inlets; The cold-producing medium output of two phase-change heat-exchanger 5 low temperature sides sucks end through the first stop valve 8a with the gaseous refrigerant of jet mixer 12 and is communicated with; The gaseous refrigerant output of two phase-change heat-exchanger 5 low temperature sides is communicated with gas-liquid separator 14 inputs through the second stop valve 8b; The output of jet mixer 12 is communicated with gas-liquid separator 14 inputs through first booster 13; The liquid output of gas-liquid separator 14 is communicated with liquid reserve tank 17 inputs through the 4th stop valve 19; The gaseous state output of gas-liquid separator 14 is communicated with the input of air cooling heat radiator 15; The output of air cooling heat radiator 15 is communicated with the input of liquid reserve tank 17; The output of liquid reserve tank 17 is communicated with second booster 21 of parallel connection and the input of choke valve 20 through first output of triple valve 18, and second booster 21 of parallel connection and the output of choke valve 20 are communicated with the input of two phase-change heat-exchanger 5 low temperature sides; The output of liquid reserve tank 17 is communicated with the input of the 3rd stop valve 10 through second output of triple valve 18; The output of the 3rd stop valve 10 is communicated with the constant pressure pump 9 of parallel connection and the input of by-passing valve 11, and the constant pressure pump 9 of parallel connection and the output of by-passing valve 11 are communicated with the liquid refrigerant injector head input of jet mixer 12.
With reference to Fig. 1～7; The structure of described jet mixer 12 is; Comprise liquid refrigerant injector head 23, mixing chamber 24, trunnion 25 and diffuser 26, liquid refrigerant injector head 23 places the front end in the mixing chamber 24, and mixing chamber 24 is connected with trunnion 25, diffuser 26 order on same axis.
The structure of the liquid refrigerant injector head 23 of described jet mixer is; Comprise the circular arc face shield 28 that the port of export with high pressure liquid refrigerant pipeline 27 is connected; Be embedded with several nozzles of arranging ringwise on the circular arc face shield 28; Several nozzles that the core space of circular arc face shield 28 is embedded with all are contraction and enlargement nozzles 29, and several nozzles that the peripheral all circles of the core space of circular arc face shield 28 are embedded with all are negative throat noz(zle)s 22; The axis of contraction and enlargement nozzle 29 and jet mixer axially parallel, the axis of negative throat noz(zle) 22 are all perpendicular with circular arc face shield 28 outer surfaces.
The spacing that is positioned at contraction and enlargement nozzle 29 exit end faces and the mixing chamber outlet cross section at said liquid refrigerant injector head 23 centers is 2～1.5 times of high pressure liquid refrigerant pipeline 27 internal diameters.Described trunnion 25 is cylindrical trunnion, and its length is 16～35 times of internal diameter.
The high ambient temperature period: implement positive kind of refrigeration cycle operation; The saturated gaseous refrigerant of two phase-change heat-exchanger 5 low temperature sides outlets is connected with the gaseous refrigerant suction inlet of jet mixer 12 through the first stop valve 8a; Gaseous refrigerant is sucked mixing chamber 14 by the high pressure liquid refrigerant that penetrates from the liquid refrigerant injector head; And then mix and flowing in the trunnion 15 back of further mixing, boost and get into first booster 13; After the mutually mixed uniformly cold-producing medium of gas-liquid is boosted to the condensing pressure of air cooling heat radiator 15; Get into gas-liquid separator 14 and separate, isolated liquid refrigerant gets into liquid reserve tank 17 through the 4th stop valve 19, and gaseous refrigerant then gets into air cooling heat radiator 15 condensation heat releases; Condensed liquid refrigerant passes through liquid reserve tank 17 through 18 fens two-way of triple valve; One tunnel condensed liquid refrigerant enters the mouth to choke valve 20 through first output of triple valve 18, and the pressure ratio of pressing the instruction appointment of industrial computer gets into the low temperature side inlet that two-phase becomes heat exchanger 5 after throttling, implement positive kind of refrigeration cycle operation; The condensed liquid refrigerant in another road is through second output of triple valve 18; Arrive the by-passing valve 11 and constant pressure pump 9 inlets of parallel connection through the 3rd stop valve 10; Equally after constant pressure pump 9 boosts, get back to liquid refrigerant pipeline 27 inlets of jet mixer 12 through by-passing valve 11 or by the pressure ratio of appointment, implement the suction gaseous refrigerant and mix with it by the instruction of industrial computer;
The low ambient temperature period: positive kind of refrigeration cycle is out of service; By industrial computer automatically operation second booster 21 make the steam turbine delivery temperature follow ambient air temperature when changing and to keep the low temperature side cold-producing medium boiling parameter and the air cooling heat radiator condensation of refrigerant parameter of two phase-change heat-exchangers 5 identical; The low temperature side outlet gaseous refrigerant of two phase-change heat-exchangers 5 directly gets into gas-liquid separator 14 through the second stop valve 8b, and isolated liquid refrigerant gets into liquid reserve tank 17 through the 4th stop valve 19; Isolated gaseous refrigerant is through the gas-distribution pipe of air cooling heat radiator 15 and get into each cooling duct respectively and carry out the condensation heat release; Liquid refrigerant after condensing gets into liquid reserve tank 17; Arrive the arrival end of second booster 21 again through triple valve 18 first outputs; Get into the low temperature side inlet that two-phase becomes heat exchanger 5 by the pressure ratio of the instruction appointment of the industrial computer back of boosting, implements virtual contrary kind of refrigeration cycle and move.The above-mentioned method of operation and switchover operation are realized through optimization operation adjustment software controlled by industrial computer; Industrial computer is the commercially available prod; Plant characteristic is controlled in its basis of compilation of optimizing operation adjustment software program automatically and technique of computer measurement and control requires establishment, is the technology that those skilled in the art were familiar with.
The liquid refrigerant injector head 23 of jet mixer 12 of the present invention comprises the circular arc face shield 28 that the port of export with high pressure liquid refrigerant pipeline 27 is connected; Be embedded with several nozzles of arranging ringwise on the circular arc face shield 28; Several nozzles that the core space of circular arc face shield 28 is embedded with all are contraction and enlargement nozzles 29, and several nozzles that the peripheral all circles of the core space of circular arc face shield 28 are embedded with all are negative throat noz(zle)s 22; The axis of contraction and enlargement nozzle 29 and jet mixer axially parallel, the axis of negative throat noz(zle) 22 are all perpendicular with circular arc face shield 28 outer surfaces.Negative throat noz(zle) 22 is identical with the inlet pressure of contraction and enlargement nozzle 29, and outlet diameter and effluxvelocity distribute and can confirm based on experimental data optimization; Jet direction is then like following arrangement: the liquid refrigerant jet of all negative throat noz(zle)s 22 is thin-line-shaped ejection; The jet direction streamwise is diffusion type; Effluxvelocity is descending variation by inner ring to the outer ring, thereby hydrostatic pressure then is from low to high and changes, and because the layout of negative throat noz(zle) 22 adopts close fork row in outer the dredging; Thereby the distribution of liquid refrigerant jet also is close in outer the dredging; Overall like this liquid refrigerant jet field appears: core space forms the column low-pressure area have a little diffusion, beyond the core space each circle be then that pressure is high outside and low outside, density dredge outward in the flow field of close distribution, thereby can attract gaseous refrigerant to pass multilayer fine shape liquid metal jet flow and get into core space; Increased the contact area of gas-liquid phase greatly; And each jet diameter is again all much smaller than the down existing all kinds of injector of same liquid refrigeration agent flux, thereby the contact area of gas-liquid two-phase more will be much larger than existing injector, and then can obviously improve the mass ratio of induced-to-inducing air of jet mixer 12; In addition, as long as the tapering of middle minute conical surface streamwise of gaseous refrigerant suction passage is moderate, the reaction force of the internal face convection cell of mixing chamber 24 then capable of using; Improve gas-liquid micel collision probability, gas-liquid two-phase can fully be mixed, and the direction after its collision is basic consistent with the jet direction in jet core district; Can reduce flow pressure drop again; The fluidal texture of the injector head that above-mentioned each item designing institute obtains is convenient to attract more gaseous refrigerants to get into core space, carries out effective collision, mixes with the liquid refrigerant jet, compares sufficient momentum-exchange; Thereby can carry gaseous refrigerant as much as possible secretly to obtain maximum mass ratio of induced-to-inducing air, also claim jet coefficient.
Mixer: its mixer comprises horizontal round table-like mixing chamber 24 and cylindrical trunnion 25; When liquid refrigerant injector head 23 stretches into horizontal round table-like mixing chamber 24; Liquid refrigerant injector head 23 outer walls and mixing chamber 24 inwalls form the suction passage of conical gaseous refrigerant jointly; The vertex of a cone of the middle minute conical surface of tapered channel is positioned at the circle centre position at cylindric trunnion 25 and round table-like mixing chamber 24 interfaces, and the spacing that is positioned at contraction and enlargement nozzle 29 exit end faces and the mixing chamber outlet cross section at said liquid refrigerant injector head 23 centers is 2～1.5 times of high pressure liquid refrigerant pipeline 27 internal diameters; Trunnion 25 is cylindrical trunnion, and its length is generally 16～35 times of internal diameter.
Diffuser: the little diffuser 26 of the axial length of trunnion 25 ports of export of the present invention can make partial velocity can convert into pressure can, to improve the inlet pressure of first booster 13 thereafter, help the work of first booster 13 and energy-conservation.But in the present invention, the function that makes injector through said structure by traditional cold-producing medium is boosted be converted into the gas-liquid two-phase that mainly makes cold-producing medium evenly be mixed into emulsion, the boosting then to move back of diffuser is secondary function.See Fig. 8, the length L of the diffuser of jet mixer is confirmed by following formula usually:
L＝(d
o-d
i)/(2tanθ/2) (1)
Formula (1), d
i-be the diffuser inlet diameter, that is throat pipe diameter, mm;
d
o-diffuser outlet diameter, mm; Can be selected according to design demand;
θ is an angle of flare, and empirical value is 6 °～12 °;
The output of the jet mixer 12 of said structure respectively is connected in series a frequency modulation booster with its liquid refrigerant input: first booster 13 and constant pressure pump 9; A kind of four kinds of kind of refrigeration cycle of tradition that are different from just have been combined into; That is: air cycle refrigeration circulation; Vapor Compression Refrigeration Cycle, the injection mixing+electric pump of Absorption Cooling System and steam-sprayed kind of refrigeration cycle boosts, and is called for short and mixes boost type kind of refrigeration cycle or refrigeration machine.Wherein liquid refrigerant and gaseous refrigerant are mixed into emulsion through jet mixer 12, and then available first booster 13 is brought up to air cooling heat radiator 15 condensing pressures that ambient air temperature determines with its pressure from jet mixer 12 outlet pressures; This jet mixer 12 is connected in series Combination application in combined-circulation indirect air cooling system with first booster 13, has just constituted mixing boost type refrigeration combined-circulation indirect air cooling system.The injector of absorber, generator and EFI formula that replaces compressor, the ammonia water absorbing of compression with mixing boost type refrigeration machine refrigeration modes such as boost with above-mentioned technical characterictic; The advantage that can keep aforementioned three can be eliminated their above-mentioned defective again.
On the other hand; For guaranteeing that liquid refrigerant has enough pressure so that can all extract steam turbine 2 maximum capacities out, get liquid reserve tank 17 outlet pressures under the high ambient temperature in location, factory site usually as the inlet pressure design load of the liquid refrigerant injector head 23 of jet mixer 12.In case ambient air temperature is lower than design load, the preposition constant pressure pump 9 that can start jet mixer 12 is constant with the inlet pressure of keeping liquid refrigerant injector head 23 to be design load.What is more important is thisly aspirated the gaseous state of same cold-producing medium with liquid refrigerant, has both avoided the relatively big deficiency of traditional stream-jet ejector size, and again because of mixed process belongs to the unary system heterogeneous equilibrium, theoretical treatment more is prone to carry out.So, the present technique scheme just can with simple in structure, function is more, cheap, easy to maintenance, widely applicable, the advantage that is easy to promote replaces compression, ammonia water absorbing and EFI formula and become the kind of refrigeration cycle of the 4th kind of pattern of cooling system between combined-circulation.Wherein " widely applicable " mainly is meant and adopts combined-circulation indirect air cooling system of the present invention not to be only applicable to short northern area of high temperature period, segment length's low latitudes in the time of also can being used for high temperature economically.
Realize in the operation method of adjustment of mixing boost type of the present invention refrigeration combined-circulation indirect air cooling system that contrary kind of refrigeration cycle function is meant under the situation that single kind of refrigeration cycle and power cycle are in series; Meteorological condition and unit cold junction characteristics design according to the factory site are moved the adjustment mode accordingly, to realize the power utilization of low ambient temperature resource.The operation method of adjustment that this specific aim is very strong is: the association analysis by system's each evaluation index of heat-economy can know that temperature T is twisted in the economy commentaries on classics
tRelevant with steam turbine exhaust back pressure, two phase-change heat-exchanger and air cooling heat radiator heat transfer temperature difference, ambient air temperature, turbine low pressure cylinder efficient and compression set efficient etc.(benefit-cost difference BCD) does the difference of the income-expenditure of system
First of right-hand member is theoretical power (horse-power) and the ambient air temperature T that cold steam turbine is sent out under steam discharge back pressure 4.9Kpa between combined-circulation in the formula (2)
eThe theoretical power (horse-power) that direct-cooled steam turbine is sent out of same capacity, same factory site, same model is poor down, and hereinafter to be referred as income, second of right-hand member is the theoretical power (horse-power) (hereinafter to be referred as expenditure) that is consumed under the 4.9Kpa in the steam discharge back pressure for compression device; Both differences are called theoretical exposure, and note is made BCD
t
In the formula (2): P
AcBe a certain ambient air temperature T
eThe condensing pressure of following air cooling heat radiator, Kpa; Usually can be by T
e+ Δ T
AcGained air cooling heat radiator condensation temperature T
AcLook into and get; H
C, 32.5And H
C, TacBe respectively T
eCold unit is the exhaust enthalpy of 4.9Kpa and the exhaust enthalpy of direct-cooled unit between following combined-circulation, KJ/Kg; P
1, V
1Pressure, temperature for the following pair of saturated gaseous refrigerant of phase-change heat-exchanger cold side of same operating mode.If count each item efficient of power consumption and production capacity equipment, then formula (2) can be rewritten as following formula
The difference that the middle right-hand member of formula (3) is two is actual exposure, and note is made BCD
aMake BCD respectively
t=0 and BCD
a=0, can obtain theory or actual the commentaries on classics twisted temperature T
T, tAnd T
T, a,, promptly power consumption and production capacity are distinguished corresponding ambient air temperature with the intersection point of ambient air temperature change curve.
The temperature association equation of each parts of kind of refrigeration cycle:
T
exh＝T
e+ΔT
ac-ΔT
c+ΔT
bpc (4)
In the formula (4): T
eThe on-site ambient air temperature of-unit, ℃; T
Exh-steam turbine delivery temperature, ℃; P
Exh-steam turbine exhaust back pressure, Kpa; Δ T
BpcThe logarithmic mean temperature difference (LMTD) of-two phase-change heat-exchangers (log-meantemperature difference, LMTD), ℃; Δ T
AcThe LMTD of-air cooling heat radiator, ℃; Δ T
cThe cold-producing medium temperature rise that-compression process produces.For keeping two phase-change heat-exchanger high temperature side condensate not freeze, its minimum exhaust parameter is answered T at least
Exh>=1 ℃, P
Exh>=0.66Kpa.
With the ambient air temperature is transverse axis, and exposure is the longitudinal axis, is cross variable with the steam discharge back pressure, and Fig. 9 is then arranged.Visible by Fig. 9, when other conditions are identical, steam discharge back pressure and T
tCorresponding one by one: the steam discharge back pressure is low more, T
tMore little, exposure is big on the occasion of more; When ambient air temperature is lower than 0 ℃ and when constantly descending, exposure slightly reduces or be constant basically; And temperature is low more, and exposure is big on the occasion of more.This explanation, when virtual contrary kind of refrigeration cycle was moved under low temperature environment, as long as back pressure reduces and proportional decline with ambient air temperature, then exposure was bigger on the occasion of.Certainly, this revenue and expenditure difference multiple merit of only deriving from steam turbine 2 deducts the wasted work of compression set.Air cooling heat radiator 15 exports the difference work done of condensation of refrigerant liquid enthalpys under enthalpy that the superheater that not have a contrary kind of refrigeration cycle in view of the present invention and prime mover are implemented to utilize pair phase-change heat-exchangers 5 to export cold-producing mediums and the same ambient air temperature, thereby the part of can only saying so has been utilized the low ambient temperature resource.
Based on above-mentioned, it is following in the adjustment computational methods of low temperature period optimization operation to mix boost type refrigeration combined-circulation indirect air cooling system:
Positive kind of refrigeration cycle is stopped transport, at this moment the Δ T in the temperature association equation (formula (4))
c=0:
If ambient air temperature T
eDescend, because of Δ T
AcWith Δ T
BpcAs long as it is constant that heat-transfer surface in service is maintained in the clean condition, then both numerical value perseverance is a design load.So can confirm the delivery temperature and the corresponding back pressure of steam turbine by formula (4); And then solve BCD by formula (2) and formula (3)
tAnd BCD
aVisible by virtual calculated example Fig. 9, need only exhaust back pressure in the 8Kpa-2.3Kpa scope, BCD
tCertainly on the occasion of.In other words, even if stop using positive kind of refrigeration cycle, i.e. Δ T
c=0, let the steam discharge back pressure be not less than present enforceable no minimum 2.3Kpa, then theoretical exposure BCD with ambient air temperature decline and by formula (4) requirement downward modulation
tCertainly on the occasion of, actual exposure BCD
aThen look device efficiency and confirm that by formula (3) calculating the result is as shown in Figure 9.This method of operation also can be called virtual contrary kind of refrigeration cycle operation.
Mixing boost type refrigeration combined-circulation indirect air cooling system of the present invention and operation method of adjustment; Once adopted China east Inner Mongolia somewhere actual environment temperature year hour distributed data; With the direct-cooled unit of subcritical 600MW is standard of comparison; The performance of cold unit has been carried out virtual calculating between the virtual combined-circulation of same environment, same capacity, same model but different low pressure (LP) cylinders, and the result shows: the average 14g/kW.h of net coal consumption rate can debase the standard; Year reduces discharging CO
2Measure 1,130 ten thousand tons; 6462.5 ten thousand tons of annual water-saving amounts; Utilization rate of equipment and installations significantly improves: ability oepration at full load in summer, there is not freeze injury winter, and (filling) wind that falls does not trip.Target of the present invention and effect have all been realized.
Claims (5)
1. one kind is mixed boost type refrigeration combined-circulation indirect air cooling system; It is characterized in that: it comprises that the steam entry of two phase-change heat-exchanger (5) high temperature sides is connected with steam turbine exhaust outlet (4), and the hot well port of export of two phase-change heat-exchangers (5) is connected with condensate pump (6) inlet of Steam Power Circulation; The cold-producing medium output of two phase-change heat-exchangers (5) low temperature side sucks end through first stop valve (8a) with the gaseous refrigerant of jet mixer (12) and is communicated with; The cold-producing medium output of two phase-change heat-exchangers (5) low temperature side is communicated with gas-liquid separator (14) input through second stop valve (8b); The output of jet mixer (12) is communicated with gas-liquid separator (14) input through first booster (13); The liquid output of gas-liquid separator (14) is communicated with liquid reserve tank (17) input through the 4th stop valve (19); The gaseous state output of gas-liquid separator (14) is communicated with the input of air cooling heat radiator (15); The output of air cooling heat radiator (15) is communicated with the input of liquid reserve tank (17); The output of liquid reserve tank (17) is communicated with second booster (21) of parallel connection and the input of choke valve (20) through first output of triple valve (18), and second booster (21) of parallel connection and the output of choke valve (20) are communicated with the input of two phase-change heat-exchanger (5) low temperature sides; The output of liquid reserve tank (17) is communicated with the input of the 3rd stop valve (10) through second output of triple valve (18); The output of the 3rd stop valve (10) is communicated with the constant pressure pump (9) of parallel connection and the input of by-passing valve (11), and the constant pressure pump (9) of parallel connection and the output of by-passing valve (11) are communicated with the liquid refrigerant injector head input of jet mixer (12).
2. mixing boost type refrigeration combined-circulation indirect air cooling system according to claim 1; It is characterized in that: the structure of described jet mixer (12) is; Comprise liquid refrigerant injector head (23), mixing chamber (24), trunnion (25) and diffuser (26); Liquid refrigerant injector head (23) places the front end in the mixing chamber (24), and mixing chamber (24) is connected with trunnion (25), diffuser (26) order on same axis.
3. mixing boost type refrigeration combined-circulation indirect air cooling system according to claim 2; It is characterized in that: the structure of the liquid refrigerant injector head (23) of described jet mixer (12) is; Comprise the circular arc face shield (28) that the port of export with high pressure liquid refrigerant pipeline (27) is connected; Be embedded with several nozzles of arranging ringwise on the circular arc face shield (28); Several nozzles that the core space of circular arc face shield (28) is embedded with all are contraction and enlargement nozzle (29), and several nozzles that the peripheral all circles of the core space of circular arc face shield (28) are embedded with all are negative throat noz(zle) (22); The axis of contraction and enlargement nozzle (29) and jet mixer axially parallel, the axis of negative throat noz(zle) (22) are all perpendicular with circular arc face shield (28) outer surface.
4. mixing boost type refrigeration combined-circulation indirect air cooling system according to claim 2, it is characterized in that: described trunnion (25) is cylindrical trunnion, and its length is 16～35 times of internal diameter.
5. want the operation method of adjustment of 1 described mixing boost type refrigeration combined-circulation indirect air cooling system according to right, it is characterized in that: the adjustment software by industrial computer is worked out according to the operation method of adjustment is implemented automatically:
The high ambient temperature period: implement positive kind of refrigeration cycle operation; The saturated gaseous refrigerant of two phase-change heat-exchangers (5) low temperature side outlet is connected with the gaseous refrigerant suction inlet of jet mixer (12) through first stop valve (8a); Gaseous refrigerant is sucked mixing chamber (24) by the high pressure liquid refrigerant that penetrates from the liquid refrigerant injector head; And then mix and flowing in the trunnion (25) back of further mixing, boost and get into first booster (13); After the mutually mixed uniformly cold-producing medium of gas-liquid is boosted to the condensing pressure of air cooling heat radiator; Get into gas-liquid separator (14) and separate, isolated liquid refrigerant gets into liquid reserve tank (17) through the 4th stop valve (19), and gaseous refrigerant then gets into air cooling heat radiator (15) condensation heat release; Condensed liquid refrigerant divides two-way through liquid reserve tank (17) through triple valve (18); One tunnel condensed liquid refrigerant enters the mouth to choke valve (20) through first output of triple valve (18), and the pressure ratio of pressing the instruction appointment of industrial computer gets into the low temperature side inlet that two-phase becomes heat exchanger (5) after throttling, implement positive kind of refrigeration cycle operation; The condensed liquid refrigerant in another road is through second output of triple valve (18); Arrive the by-passing valve (11) and constant pressure pump (9) inlet of parallel connection through the 3rd stop valve (10); Same instruction by industrial computer is got back to liquid refrigerant pipeline (27) inlet of jet mixer (12) through by-passing valve (11) or by the pressure ratio of appointment after constant pressure pump (9) boosts, implement the also mixing with it of suction gaseous refrigerant;
The low ambient temperature period: positive kind of refrigeration cycle is out of service; By industrial computer automatically operation second booster (21) make the steam turbine delivery temperature follow ambient air temperature when changing and to keep the low temperature side cold-producing medium boiling parameter and air cooling heat radiator (15) the condensation of refrigerant parameter of two phase-change heat-exchangers (5) identical; The low temperature side outlet gaseous refrigerant of two phase-change heat-exchangers (5) directly gets into gas-liquid separator (14) through second stop valve (8b), and isolated liquid refrigerant gets into liquid reserve tank (17) through the 4th stop valve (19); Isolated gaseous refrigerant is through the gas-distribution pipe of air cooling heat radiator (15) and get into each cooling duct respectively and carry out the condensation heat release; Liquid refrigerant after condensing gets into liquid reserve tank (17); Arrive the arrival end of second booster (21) again through triple valve (18) first outputs; Get into the low temperature side inlet that two-phase becomes heat exchanger (5) by the pressure ratio of the instruction appointment of the industrial computer back of boosting, implements virtual contrary kind of refrigeration cycle and move.
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| CN102562122B (en) * | 2012-03-08 | 2014-12-10 | 中国海洋大学 | Mobile liquid cooling device without electric drive and liquid cooling method |
| CN106224275B (en) * | 2016-08-24 | 2017-10-24 | 西安西热节能技术有限公司 | A kind of direct air cooling system running optimizatin method |
| CN107860242B (en) * | 2017-11-09 | 2019-06-04 | 温高 | A kind of method and system promoting direct air cooling system exchange capability of heat |
| CN112510481A (en) * | 2020-11-30 | 2021-03-16 | 中国科学院西安光学精密机械研究所 | Method and device for cooling microchannel semiconductor laser by high-speed gas carrying refrigerant |
| CN114674119B (en) * | 2022-04-02 | 2024-03-01 | 浙江青风环境股份有限公司 | Frosting-inhibiting type powder cold dryer |
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