CN103258097A - Optimum design method of pipeline length of organic Rankine cycle heat exchanger considering flow pattern - Google Patents
Optimum design method of pipeline length of organic Rankine cycle heat exchanger considering flow pattern Download PDFInfo
- Publication number
- CN103258097A CN103258097A CN2013101816489A CN201310181648A CN103258097A CN 103258097 A CN103258097 A CN 103258097A CN 2013101816489 A CN2013101816489 A CN 2013101816489A CN 201310181648 A CN201310181648 A CN 201310181648A CN 103258097 A CN103258097 A CN 103258097A
- Authority
- CN
- China
- Prior art keywords
- flow
- heat
- formula
- wavy
- working medium
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Landscapes
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention discloses an optimum design method of the pipeline length of an organic Rankine cycle heat exchanger considering a flow pattern. When organic working media are in a single-phase flow state, an average Nu of one section is calculated to get heat exchange amount of the section, the heat exchange amount is compared with actual heat exchange amount, and a pipe length value of the section is determined. When the organic working media are in a two-phase flow state, a convective heat-transfer coefficient calculation method of a corresponding flow pattern is selected to obtain a convective heat-transfer coefficient of the section, heat exchange amount of the section is calculated according to the convective heat-transfer coefficient value and an assumed pipe length in the end, the heat exchange amount is compared with the actual heat exchange amount, the pipe length of each dividing section is determined, and the pipeline length of the heat exchanger can be obtained. Computational accuracy of the heat exchange amount is obviously improved through consideration of flow pattern changes of media in the process of two-phase evaporation and condensation, and the optimum design method can be applied to determination of pipeline lengths of organic Rankine cycle heat exchangers using various commonly-used fluids.
Description
Technical field
The present invention relates to a kind of organic Rankine circulation heat exchanger duct length Optimization Design of considering flow pattern.
Technical background
Within 2011, China GDP is about 7.30 trillion dollars, and the primary energy total quantity consumed is 26.13 hundred million tons of oil equivalents.China GDP accounts for 10.47% of world GDP total amount, but the energy for this reason consumed accounts for 21.29% of world's total energy consumption.Statistics shows, ten thousand yuan of GDP energy consumptions of China are 2.03 times of world average level, 2.38 times of the U.S., 4.18 times of Germany, 4.40 times of Japan.China's industrial energy consumption accounts for more than 70% of whole society's energy consumption, and the industrial energy consumption height is the main cause that causes China's per Unit GDP Energy Consumption high.And 60% – 65% of industrial energy consumption transforms for the waste heat that carrier is different, temperature is different, wherein, middle-low temperature heat quantity is extremely huge, but, because its grade is low, substantially can not be recycled by traditional water vapor power cycle.
In the face of so severe energy crisis and higher GDP energy consumption, find the only way that new forms of energy and research and development power-saving technology have become China's sustainable economic development.With regard to China's current situation, the renewable and clean energy resources such as development geothermal energy and sun power, reclaim the middle-low temperature heat resource that wide, the traditional water vapor power cycle of industrial process amount multiaspect is difficult to the high efficiente callback utilization and can not only effectively alleviate the situation of domestic energy supply anxiety, but also be conducive to improve environment.Waste heat, geothermal energy and the sun power etc. of industrial process discharge all belong to middle low-temperature heat source, and, in middle-low temperature heat recovery field, organic Rankine circulation becomes the desirable approach of high efficiente callback middle-low temperature heat because of advantages such as its efficiency are high, simple in structure and cost of investment is low.Therefore, optimal design seems especially important as the evaporator of organic Rankine circulation vitals and the duct length of condenser.
In existing evaporator and condenser tubes Design of length method, be to select a certain experimental formula to be calculated substantially, and do not consider the flow pattern in two-phase evaporation and condensation process, therefore caused the computational accuracy of heat exchanger tube length low.Simultaneously, the narrow application range of experimental formula, be unfavorable for research, popularization and the application of organic Rankine circulation.
Summary of the invention
The purpose of this invention is to provide a kind of organic Rankine circulation heat exchanger duct length Optimization Design, it has considered the flow pattern in two-phase evaporation and condensation process, computational accuracy is high, and can be applicable to use the determining of organic Rankine circulation heat exchanger duct length of various fluids commonly used.
Technical solution of the present invention is as follows:
In heat transfer process, when organic working medium is the single-phase flow state (supercooled liquid or gaseous state), at first according to the division segment pipe range initial value of supposition, utilize the Gnielinski formula to calculate the average nusselt number of this section
nu, and then average according to this
nunumber calculates the heat exchange amount of this section, and compares with actual heat exchange amount, if not identical, change and divides segment pipe range value, until its relative error is less than or equal to 1%; When organic working medium is the two-phase flow state, at first the pipe range of segment is divided in supposition, then according to evaporation or condensing temperature, round tube inside diameter
d, the working medium mass velocity
g, the heat flow density of dividing segment
q(pipe range based on supposition) and average gas massfraction
xdetermine this section residing two-phase evaporation or condensation flow pattern, and then choose convective heat-transfer coefficient calculating formula under corresponding flow pattern to obtain the convective heat-transfer coefficient of this section, the heat exchange amount of last this section of length calculation according to this convective heat-transfer coefficient value and supposition, and compare with actual heat exchange amount, if not identical, change and divide segment pipe range value, until its relative error is less than or equal to 1%.The pipe range of two-phase evaporation and the every division segment of condensation process can be determined in this way, and then the duct length of whole evaporator and condenser can be obtained.
The present invention, by considering the variations in flow patterns of working medium in two-phase evaporation and condensation process, has significantly improved the computational accuracy of heat exchange amount, can be applicable to use organic Rankine circulation heat exchanger duct length definite of various fluids commonly used.
The accompanying drawing explanation
Fig. 1 is definite process flow diagram of evaporator pipeline length;
Fig. 2 is definite process flow diagram of condenser tubes length;
Fig. 3 is layering two-phase flow cross sectional representation;
Fig. 4 is two-phase evaporation flow regime map;
Fig. 5 is the changing trend diagram of two-phase evaporation heat transfer coefficient with the gaseous mass mark;
Fig. 6 is two-phase condensation flow regime map;
Fig. 7 is the changing trend diagram of two-phase condensation coefficient with the gaseous mass mark.
Embodiment
, duct length determines when evaporator and condenser single phase flow heat transfer
The present invention has chosen the Gnielinski formula that accuracy in computation is the highest up to now and has calculated the convective heat-transfer coefficient under working medium single-phase flow state in evaporator and condenser.Under evaporator and condenser single-phase flow state, definite step of duct length is as follows:
Step 1: according to working medium and heat source fluid, divide the working medium kinetic viscosity under the section medial temperature
μ i , specific heat capacity at constant pressure
c p,i and coefficient of heat conductivity
k i calculate the Prandtl number of working medium at these two kinds of temperature
pr i (for gas, only needing to calculate the Prandtl number of dividing under section working medium medial temperature), wherein the Prandtl number calculating formula is
Step 2: according to the density under the working medium medial temperature
ρ i , kinematic viscosity
υ i mass rate with working medium
, the flow velocity of calculating working medium
u i and Reynolds number
re i , its concrete calculating formula is respectively
Step 3: suppose
ithe pipe range of dividing section is
l j,i ;
Step 4: according to the Gnielinski formula, calculate nusselt number
nu i , its concrete calculating formula is
To liquid
To gas
In formula,
l j,i be
idivide section the
j+1inferior calculating pipe range;
f i for the mobile Darcy resistance coefficient of intraductal turbulance, press Fu Luonianke (Filonenko) formula
calculate.
Step 5: according to
nu f,
i the relative error of unit of account time heat transfer capacity, its calculating formula is
If Δ
i 1%, change
idivide the pipe range of section
l j,
i , repeating step 3 ~ step 4; If Δ
i ≤ 1%,
l j,
i be
idivide the pipe range of section.
Step 6: calculate the pipeline total length under evaporator or condenser single-phase flow state
l, its calculating formula is
In formula,
nfor the duct segments research number under evaporator or condenser single-phase flow state.
, duct length determines during the heat exchange of evaporator biphase gas and liquid flow
1) drafting of evaporator flow pattern of gas-liquid two-phase flow figure and flow pattern determines
Two-phase is evaporated to flow pattern and be divided into stratified flow (stratified flow, S), wavy stratified flow (stratified-wavy flow, SW), slug flow/wavy stratified flow (slug/stratified-wavy flow, Slug+SW), slug flow (Slug flow, Slug), annular flow (annular flow, A), intermittent flow (intermittent flow, I), dry stream (dryout flow, D) and eight kinds of mist flows (mist flow, M).The concrete drawing process of its flow regime map is as follows:
Step 1: according to evaporating temperature
t evap(in order to calculate working medium gaseous state and the liquid thermal physical property parameters such as density), round tube inside diameter
d, the working medium mass velocity
gand gaseous mass mark
xcalculate the ratio of xsect gas area occupied
, the shared xsect of liquid and gas the dimensionless area
a ldwith
a vd, the layering angle of circumference
θ strat, dimensionless liquid is high
h ldwith dimensionless gas-liquid two-phase interphase girth
p id, as shown in Figure 3, in figure, 1 is gas, 2 is liquid.Concrete calculating formula is as follows:
,
In formula,
ρ vwith
ρ lbe respectively the density of gaseous state and liquid refrigerant;
gfor acceleration of gravity;
σfor the working medium surface tension.
In formula,
across-sectional area for interior conduit in evaporator;
Step 2: the transition value of the calculation of parameter " I – A " of trying to achieve according to hot working fluid physical parameter and step 1;
In formula,
μ lwith
μ vbe respectively the dynamic viscosity coefficient of gaseous state and liquid refrigerant;
Step 3: the transition value of calculating " S – SW "
,
And work as
x<
x iAthe time,
g strat=
g strat(
x iA);
Step 4: calculate transition value
g wavy
(a) in interval
x<
x iA, when
g wavy?
g?
g wavy(
x iA) time, this zone is slug flow;
(b) in interval
x<
x iA, when
g wavy(
x iA)
g?
g strat(
x iA) time, this zone is slug flow/wavy stratified flow;
(c) in interval
x?
x iA, when
g wavy?
g?
g stratthe time, this zone is wavy stratified flow.
Step 5: according to working as the density of geothermal heat flow parameter
q, the transition value of calculating " A – D ".
In formula, core pond evaporation critical heat flux density
,
h lVfor evaporation latent heat.
When
g strat(
x i )>=
g dryout(
x i ) time,
g dryout(
x i )=
g strat(
x i );
When
g wavy(
x i )>=
g dryout(
x i ) time,
g wavy(
x i )=
g dryout(
x i ).
Step 6: the transition value of calculating " D – M ".
,
When
g dryout(
x i )>=
g mist(
x i ) time,
g dryout(
x i )=
g mist(
x i ).
By constantly increasing progressively the gaseous mass mark
x, follow above-mentioned calculation procedure, finally can draw out the two-phase evaporation flow regime map under specified criteria, as shown in Figure 4.
Step 7: according to the mass velocity under concrete state
gwith each flow pattern transition value be known two-phase now evaporation flow pattern.
2) evaporator Heat transfer of gas-liquid two-phase coefficient determines
The calculating formula difference of the two-phase evaporation heat transfer coefficient of different flow patterns, concrete condition is as follows:
If a) flow pattern is mist flow, its convective heat-transfer coefficient
In formula,
re hfor the homogeneous phase Reynolds number;
pr vfor the gas phase Prandtl number;
yfor composite factor;
λ vfor the gas phase coefficient of heat conductivity.Its concrete calculating formula is
In formula,
c pv
specific heat capacity at constant pressure for the working medium gaseous state.
B) if, when flow pattern is intermittent flow, annular flow, stratified flow, slug flow, slug flow/wavy stratified flow and wavy stratified flow, the computation process of its convective heat-transfer coefficient is as follows:
Step 1: calculate dry angle of circumference
θ dry.
I) if flow pattern is intermittent flow, annular flow and slug flow, dry angle of circumference equals zero;
If ii) flow pattern is stratified flow, dry angle of circumference
θ dry=
θ strat;
If iii) flow pattern is wavy stratified flow, dry angle of circumference
;
If iv) flow pattern is slug flow/wavy stratified flow, dry angle of circumference
。
Step 2: calculate thickness of liquid film
δ.
If
δ?
d/ 2,
δ=
d/ 2.
Step 3: calculate gas semiconvection heat transfer coefficient, its calculating formula is
Step 4: calculate liquid semiconvection heat transfer coefficient, its calculating formula is
Wherein,
h cbwith
h nbcalculating formula be respectively
In formula, Renault number of liquid membrane
; Liquid Prandtl number
;
λ lfor the liquid phase coefficient of heat conductivity.
Step 5: calculate total convective heat-transfer coefficient, its calculating formula is
。
C) if flow pattern is dry stream, its convective heat-transfer coefficient
Wherein,
x diwith
x debe respectively dry starting point and end point, its calculating formula is
In certain mass speed
gunder, by constantly increasing progressively the gaseous mass mark
x, follow above-mentioned calculation procedure, finally can calculate the two-phase evaporation heat transfer coefficient under specified criteria, as shown in Figure 5.
3) duct length determines
According to above-mentioned calculating gained two-phase evaporation convection heat transfer coefficient
hwith supposition the
idivide segment pipe length
l i can calculate
idivide the relative error of the unit interval heat transfer capacity of section, its calculating formula is
In formula,
with
be respectively the medial temperature of i division section heat source fluid and working medium;
with
be respectively
idivide the specific enthalpy of section working medium entrance and exit place working medium.
If Δ
i 1%, change
idivide the pipe range of section
l i , the double counting Δ
i ; If Δ
i ≤ 1%,
l i be
idivide the pipe range of section.
The total pipeline length gauge formula of evaporator two-phase region is
,
In formula,
nfor the duct segments research number under evaporator two-phase flow state.
, duct length determines during the heat exchange of condenser biphase gas and liquid flow
1) drafting of condenser flow pattern of gas-liquid two-phase flow figure and flow pattern determines
Two-phase condensation flow pattern is divided into to stratified flow (stratified flow, S), wavy stratified flow (stratified-wavy flow, SW), annular flow (annular flow, A), intermittent flow (intermittent flow, I), mist flow (mist flow, M) and six kinds of bubble flows (bubbly flow, B).The concrete drawing process of its flow regime map is as follows:
Step 1: according to round tube inside diameter
d, the working medium mass velocity
gand condensing temperature
t condunder the hot working fluid physical parameter, calculate homogeneous phase gas space mark
, Rouhani-Axelsson gas space mark
, logarithmic mean gas space coefficient
, liquid dimensionless cross-sectional area
a ld, gaseous state dimensionless cross-sectional area
a vd, the layering angle of circumference
θ strat, dimensionless liquid is high
h ldwith dimensionless interphase girth
p id.Its concrete calculating formula is as follows:
Step 2: according to the transition value of the calculation of parameter " S – SW " of calculating in the thermal physical property parameter of working medium and step 1.
Step 3: the transition value of calculating " SW – I " and " SW – A ".
When
x?
x wavyminthe time,
g wavy=
g wavy(
x wavymin), wherein
x wavyminfor
g wavyget minimum value in interval (0,1)
g wavy(
x wavymin) time local gaseous mass mark.
Step 4: the transition value of calculating " I – A ".
Step 5: the transition value of calculating " I – M " and " A – M ".
In formula,
.
When
x?
x mistminthe time,
g mist=
g mist(
x mistmin), wherein
x mistminfor
g wavyget minimum value in interval (0,1)
g wavy(
x mistmin) time local gaseous mass mark.
Step 6: the transition value of calculating " M – B ".
。
Follow above-mentioned calculation procedure, finally can draw out the two-phase condensation flow regime map under specified criteria, as shown in Figure 6.The reason that does not occur bubble flow in figure is that this flow pattern only appears under high-quality speed, higher than illustrated mass velocity scope.
According to the mass velocity under concrete situation
gcan determine two-phase condensation flow pattern now with each flow pattern transition value.
2) condenser Heat transfer of gas-liquid two-phase coefficient determines
The calculating formula difference of the two-phase condensation convective heat-transfer coefficient of different flow patterns, its concrete calculation procedure is as follows:
Step 1: the dry angle of calculating different two-phase condensation flow patterns.
If a) annular flow, intermittent flow and mist flow, dry angle of circumference
θ drybe zero, the inside surface roughness modifying factor
f i calculating formula be
B) if wavy stratified flow, layering angle of circumference
θ strat, dry angle of circumference
θ drywith the inside surface roughness modifying factor
f icalculating formula be respectively
C) if stratified flow, dry angle of circumference
θ dryequal the layering angle of circumference
θ strat.
Step 2: calculate the convection current condensation coefficient
h c.
Step 3: calculate pipe top membrane type condensation coefficient
h f.
Step 4: calculate total condensation convective heat-transfer coefficient
h tp.
In formula,
rfor the pipe inside radius.
Follow above-mentioned calculation procedure, finally can calculate the two-phase condensation coefficient under specified criteria, as shown in Figure 7.
3) duct length determines
According to above-mentioned calculating gained two-phase condensation convective heat-transfer coefficient
h tpwith supposition the
idivide segment pipe length
l i can calculate
idivide the relative error of the unit interval heat transfer capacity of section, its calculating formula is
In formula,
with
be respectively the medial temperature that i divides section working medium and heat eliminating medium;
with
be respectively
idivide the specific enthalpy of section sender property outlet and porch working medium.
If Δ
i 1%, change
idivide the pipe range of section
l i , the double counting Δ
i ; If Δ
i ≤ 1%,
l i be
idivide the pipe range of section.
The duct length calculating formula of condenser two-phase region is
In formula,
nfor the duct segments research number under condenser two-phase flow state.
According to above-mentioned calculation procedure, to the organic Rankine circulating evaporator that uses R600 and condenser tube progress row calculating.Result of calculation is based on following condition: 1) mass rate of heat source fluid and specific heat capacity at constant pressure are respectively 1kgs
-1and 1kJkg
-1k
-1; 2) cooling water inlet temperature and cooling water side pressure are respectively 283.15K and 101.325kPa; 3) minimum temperature difference of evaporator and condenser diabatic process is respectively 10K and 1K; 4) evaporating temperature, condensing temperature and environment temperature are respectively 333.15K, 293.15K and 288.15K; 5) evaporator and condenser round tube inside diameter are 20mm, wall thickness 2.5mm.
1) splitting scheme of evaporator liquid segment is: divide equally by worker quality liquid section temperature, and divide the number of segment=round (evaporating temperature-working medium evaporator temperature)+1.Each result of calculation of dividing the segment pipe range is as shown in table 1.In table, data show, the relative error that the evaporator liquid segment of application the inventive method calculating gained is divided the segment pipe range is less, and maximal value is only 0.987%, and average relative error is 0.445%.
2) splitting scheme of evaporator and condenser Gas-liquid phase region is: divide equally the number of division segment=100 by the Working medium gas massfraction.Each result of calculation of dividing the segment pipe range is as shown in table 2 and table 3.In table, data show, the evaporator of application the inventive method calculating gained and the relative error of condenser gas-liquid two-phase Division segment pipe range are all less, and maximal value is respectively 0.999% and 0.938%, and average relative error is respectively 0.563% and 0.471%.
3) splitting scheme of condenser gas section is: divide equally by Working medium gas section temperature, and divide the number of segment=round (working medium condenser inlet temperature-condensing temperature)+1.Each result of calculation of dividing the segment pipe range is as shown in table 4.In table, data show, the relative error that the condenser gas section of application the inventive method calculating gained is divided the segment pipe range is less, and maximal value is only 0.938%, and average relative error is 0.337%.
Table 1
Table 2
Table 3
Table 4.
Claims (3)
1. an organic Rankine circulation heat exchanger duct length Optimization Design of considering flow pattern, it is characterized in that: in organic Rankine cycle heat exchange process, when organic working medium is the two-phase flow state, at first suppose that working medium evaporation or condensation divide the pipe range of segment, then according to evaporation or condensing temperature, round tube inside diameter
d, the working medium mass velocity
g, the heat flow density of dividing segment
qwith the average gas massfraction
xdetermine the residing evaporation of this division segment or condensation two-phase flow pattern, and then choose convective heat-transfer coefficient calculating formula under corresponding flow pattern to obtain the convective heat-transfer coefficient of this division segment, the heat exchange amount of last this section of division segment length calculation according to this convective heat-transfer coefficient value and supposition, and compare with actual heat exchange amount, if not identical, change and divide segment pipe range value, until its relative error is less than or equal to 1%; The pipe range of every division segment under certain cycle characteristics parameter can be determined in this way, and then the duct length of whole evaporator and condenser can be obtained; In evaporator and condenser, working medium, when the single-phase flow state, selects the Gnielinski formula to calculate its convective heat-transfer coefficient, comprises the following steps:
Step 1: according to the working medium kinetic viscosity under working medium and heat source fluid medial temperature
μ, specific heat capacity at constant pressure
c p and coefficient of heat conductivity
kcalculate the Prandtl number of working medium at these two kinds of temperature
pr, only need calculate the Prandtl number of dividing under section working medium medial temperature for gas, wherein the Prandtl number calculating formula is
Step 2: according to the density under the working medium medial temperature
ρ, kinematic viscosity
υmass rate with working medium
, the flow velocity of calculating working medium
uand Reynolds number
re, its concrete calculating formula is respectively
Step 3: according to the Gnielinski formula, calculate nusselt number
nu, its concrete calculating formula is
To liquid
To gas
2. a kind of organic Rankine circulation heat exchanger duct length Optimization Design of considering flow pattern according to claim 1, it is characterized in that: in evaporator, working medium is when biphase gas and liquid flow, calculate the coefficient of heat transfer of pipeline according to the convective heat-transfer coefficient calculating formula based on two-phase evaporation flow pattern, comprise the following steps:
Step 1: according to evaporating temperature
t evap, round tube inside diameter
d, the working medium mass velocity
gand gaseous mass mark
xcalculate the ratio of xsect gas area occupied
, the shared xsect of liquid and gas the dimensionless area
a ldwith
a vd, the layering angle of circumference
θ strat, dimensionless liquid is high
h ldwith dimensionless gas-liquid two-phase interphase girth
p id;
Concrete calculating formula is as follows:
In formula,
ρ vwith
ρ lbe respectively the density of gaseous state and liquid refrigerant;
gfor acceleration of gravity;
σfor the working medium surface tension;
In formula,
across-sectional area for interior conduit in evaporator;
,
Step 2: the transition value of the calculation of parameter of trying to achieve according to hot working fluid physical parameter and step 1 " have a rest stream – annular flow ";
In formula,
μ lwith
μ vbe respectively the dynamic viscosity coefficient of gaseous state and liquid refrigerant;
Step 3: the transition value of calculating " Fen Ceng Liu – wavy stratified flow ";
And work as
x<
x iAthe time,
g strat=
g strat(
x iA);
Step 4: calculate transition value
g wavy;
(a) in interval
x<
x iA, when
g wavy?
g?
g wavy(
x iA) time, this zone is slug flow;
(b) in interval
x<
x iA, when
g wavy(
x iA)
g?
g strat(
x iA) time, this zone is slug flow/wavy stratified flow;
(c) in interval
x?
x iA, when
g wavy?
g?
g stratthe time, this zone is wavy stratified flow;
Step 5: according to working as the density of geothermal heat flow parameter
q, calculate the transition value of " Huan Zhuan Liu – is dry to flow ";
When
g strat(
x i )>=
g dryout(
x i ) time,
g dryout(
x i )=
g strat(
x i );
When
g wavy(
x i )>=
g dryout(
x i ) time,
g wavy(
x i )=
g dryout(
x i );
Step 6: the transition value of calculating " dry Liu – mist flow " (" D – M ");
When
g dryout(
x i )>=
g mist(
x i ) time,
g dryout(
x i )=
g mist(
x i );
Step 7: according to mass velocity
gjudge the now residing two-phase evaporation of working medium flow pattern with the transition value of each flow pattern;
Step 8: choose corresponding convection heat transfer' heat-transfer by convection calculating formula according to evaporation flow pattern of living in and carry out the calculating of the coefficient of heat transfer, concrete condition is as follows:
(1) if flow pattern is mist flow, its convective heat-transfer coefficient
In formula,
re hfor the homogeneous phase Reynolds number;
pr vfor the gas phase Prandtl number;
yfor composite factor;
λ vfor the gas phase coefficient of heat conductivity; Its concrete calculating formula is
,
In formula,
c pv
specific heat capacity at constant pressure for the working medium gaseous state;
(2) if, when flow pattern is intermittent flow, annular flow, stratified flow, slug flow, slug flow/wavy stratified flow and wavy stratified flow, the computation process of its convective heat-transfer coefficient is as follows:
A) calculate dry angle of circumference
θ dry;
I) if flow pattern is intermittent flow, annular flow and slug flow, dry angle of circumference equals zero;
If ii) flow pattern is stratified flow, dry angle of circumference
θ dry=
θ strat;
If iii) flow pattern is wavy stratified flow, dry angle of circumference
If iv) flow pattern is slug flow/wavy stratified flow, dry angle of circumference
B) calculate thickness of liquid film
δ
If
δ?
d/ 2,
δ=
d/ 2;
C) calculate gas semiconvection heat transfer coefficient, its calculating formula is
D) calculate liquid semiconvection heat transfer coefficient, its calculating formula is
Wherein,
h cbwith
h nbcalculating formula be respectively
In formula, Renault number of liquid membrane
; Liquid Prandtl number
;
λ lfor the liquid phase coefficient of heat conductivity;
E) calculate total convective heat-transfer coefficient, its calculating formula is
(3) if flow pattern is dry stream, its convective heat-transfer coefficient
Wherein,
x diwith
x debe respectively dry starting point and end point, its calculating formula is
3. a kind of organic Rankine circulation heat exchanger duct length Optimization Design of considering flow pattern of stating according to claim 2, it is characterized in that: in condenser, working medium is when biphase gas and liquid flow, calculate the coefficient of heat transfer of pipeline according to the convective heat-transfer coefficient calculating formula based on two-phase condensation flow pattern, comprise the following steps:
Step 1: according to round tube inside diameter
d, the working medium mass velocity
gand condensing temperature
t condunder the hot working fluid physical parameter, calculate homogeneous phase gas space mark
, Rouhani-Axelsson gas space mark
, logarithmic mean gas space coefficient
, liquid dimensionless cross-sectional area
a ld, gaseous state dimensionless cross-sectional area
a vd, the layering angle of circumference
θ strat, dimensionless liquid is high
h ldwith dimensionless interphase girth
p id; Its concrete calculating formula is as follows:
Step 2: according to the transition value of the calculation of parameter of calculating in the thermal physical property parameter of working medium and step 1 " a minute layer stream – wavy stratified flow ";
Step 3: the transition value of calculating " Fen layer wave Liu – intermittent flow " (" SW – I ") and " Fen layer wave Liu – annular flow ";
When
x?
x wavyminthe time,
g wavy=
g wavy(
x wavymin), wherein
x wavyminfor
g wavyget minimum value in interval (0,1)
g wavy(
x wavymin) time local gaseous mass mark;
Step 4: the transition value of calculating " Jian Xie Liu – annular flow " (" I – A ");
Step 5: the transition value of calculating " Jian Xie Liu – mist flow " (" I – M ") and " Huan Zhuan Liu – mist flow " (" A – M ");
When
x?
x mistminthe time,
g mist=
g mist(
x mistmin), wherein
x mistminfor
g wavyget minimum value in interval (0,1)
g wavy(
x mistmin) time local gaseous mass mark;
Step 6: the transition value of calculating " Wu Zhuan Liu – bubble flow " (" M – B ");
Step 7: according to mass velocity
gcan determine the now residing two-phase condensation of working medium flow pattern with the transition value of each flow pattern;
Step 8: choose corresponding convection heat transfer' heat-transfer by convection calculating formula according to condensation flow pattern of living in and carry out the calculating of the coefficient of heat transfer, detailed process is as follows:
(1) calculate the dry angle of different two-phase condensation flow patterns;
If a) annular flow, intermittent flow and mist flow, dry angle of circumference
θ drybe zero, the inside surface roughness modifying factor
f i calculating formula be
;
B) if wavy stratified flow, layering angle of circumference
θ strat, dry angle of circumference
θ drywith the inside surface roughness modifying factor
f icalculating formula be respectively
C) if stratified flow, dry angle of circumference
θ dryequal the layering angle of circumference
θ strat
(2) calculate the convection current condensation coefficient
h c
(3) calculate pipe top membrane type condensation coefficient
h f
Wherein,
qthe pipe range of value based on supposition;
(4) calculate total condensation convective heat-transfer coefficient
h tp
In formula,
rfor the pipe inside radius.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201310181648.9A CN103258097B (en) | 2013-05-16 | 2013-05-16 | Consider the method for optimal design organic Rankine bottoming cycle heat exchanger tube length of flow pattern |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201310181648.9A CN103258097B (en) | 2013-05-16 | 2013-05-16 | Consider the method for optimal design organic Rankine bottoming cycle heat exchanger tube length of flow pattern |
Publications (2)
Publication Number | Publication Date |
---|---|
CN103258097A true CN103258097A (en) | 2013-08-21 |
CN103258097B CN103258097B (en) | 2016-02-10 |
Family
ID=48962011
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CN201310181648.9A Expired - Fee Related CN103258097B (en) | 2013-05-16 | 2013-05-16 | Consider the method for optimal design organic Rankine bottoming cycle heat exchanger tube length of flow pattern |
Country Status (1)
Country | Link |
---|---|
CN (1) | CN103258097B (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106126803A (en) * | 2016-06-20 | 2016-11-16 | 珠海格力电器股份有限公司 | Refrigeration system analogy method and device |
CN106404829A (en) * | 2016-08-31 | 2017-02-15 | 上海交通大学 | CHF measuring method based on heat flux correction |
CN107514757A (en) * | 2017-08-31 | 2017-12-26 | 四川长虹电器股份有限公司 | The apparatus and method that a kind of refrigeration system pipeline length obtains |
CN108956692A (en) * | 2018-08-29 | 2018-12-07 | 仲恺农业工程学院 | Mass dryness fraction transition formula evaporator performance calculation method and its dryness measurement device |
CN109376447A (en) * | 2018-11-08 | 2019-02-22 | 湖南科技大学 | Extract the surface air cooler optical tube length calculation method of super long tunnel percolating water cooling capacity |
CN109446692A (en) * | 2018-11-08 | 2019-03-08 | 湖南科技大学 | Extract water flow velocity optimization method in the surface air cooler light pipe of super long tunnel percolating water cooling capacity |
CN109668750A (en) * | 2019-01-06 | 2019-04-23 | 东北电力大学 | A kind of passage aisle heat exchange equipment heat transfer deterioration prediction technique in parallel based on pressure drop signal analysis |
CN113378404A (en) * | 2021-06-29 | 2021-09-10 | 上海电气电站设备有限公司 | Segmented thermal calculation method for heat exchanger |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050171736A1 (en) * | 2004-02-02 | 2005-08-04 | United Technologies Corporation | Health monitoring and diagnostic/prognostic system for an ORC plant |
-
2013
- 2013-05-16 CN CN201310181648.9A patent/CN103258097B/en not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050171736A1 (en) * | 2004-02-02 | 2005-08-04 | United Technologies Corporation | Health monitoring and diagnostic/prognostic system for an ORC plant |
Non-Patent Citations (4)
Title |
---|
朱启的 等: "工质类型对回收中低温余热有机朗肯循环性能的影响", 《中南大学学报(自然科学版)》 * |
李艳 等: "有机朗肯循环系统及其透平设计研究", 《工程热物理学报》 * |
柯文: "基于有机朗肯循环的铝电解槽烟气余热发电技术研究", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》 * |
郑浩 等: "有机朗肯循环工质研究进展", 《有机朗肯循环工质研究进展》 * |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106126803A (en) * | 2016-06-20 | 2016-11-16 | 珠海格力电器股份有限公司 | Refrigeration system analogy method and device |
CN106126803B (en) * | 2016-06-20 | 2019-01-11 | 珠海格力电器股份有限公司 | Refrigeration system analogy method and device |
CN106404829A (en) * | 2016-08-31 | 2017-02-15 | 上海交通大学 | CHF measuring method based on heat flux correction |
CN106404829B (en) * | 2016-08-31 | 2019-06-21 | 上海交通大学 | Based on the modified CHF measurement method of hot-fluid |
CN107514757A (en) * | 2017-08-31 | 2017-12-26 | 四川长虹电器股份有限公司 | The apparatus and method that a kind of refrigeration system pipeline length obtains |
CN108956692A (en) * | 2018-08-29 | 2018-12-07 | 仲恺农业工程学院 | Mass dryness fraction transition formula evaporator performance calculation method and its dryness measurement device |
CN108956692B (en) * | 2018-08-29 | 2023-06-30 | 仲恺农业工程学院 | Dryness jump type evaporator thermodynamic performance calculation method and dryness measurement device thereof |
CN109376447A (en) * | 2018-11-08 | 2019-02-22 | 湖南科技大学 | Extract the surface air cooler optical tube length calculation method of super long tunnel percolating water cooling capacity |
CN109446692A (en) * | 2018-11-08 | 2019-03-08 | 湖南科技大学 | Extract water flow velocity optimization method in the surface air cooler light pipe of super long tunnel percolating water cooling capacity |
CN109668750A (en) * | 2019-01-06 | 2019-04-23 | 东北电力大学 | A kind of passage aisle heat exchange equipment heat transfer deterioration prediction technique in parallel based on pressure drop signal analysis |
CN113378404A (en) * | 2021-06-29 | 2021-09-10 | 上海电气电站设备有限公司 | Segmented thermal calculation method for heat exchanger |
Also Published As
Publication number | Publication date |
---|---|
CN103258097B (en) | 2016-02-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CN103258097A (en) | Optimum design method of pipeline length of organic Rankine cycle heat exchanger considering flow pattern | |
Wang et al. | Experimental study on the heat transfer performance of a molten-salt printed circuit heat exchanger with airfoil fins for concentrating solar power | |
CN103542621B (en) | A kind of method for designing of general combination pipe diameter air conditioner heat exchange equipment fluid passage | |
Zhang et al. | Experimental and numerical investigation on a CO2 loop thermosyphon for free cooling of data centers | |
Xie et al. | Condensation heat transfer of R245fa in tubes with and without lyophilic porous-membrane-tube insert | |
Hao et al. | Numerical study on heat transfer of oily wastewater spray falling film over a horizontal tube in a sewage source heat pump | |
Kukulka et al. | Comparison of condensation and evaporation heat transfer on the outside of smooth and enhanced 1EHT tubes | |
CN103514326B (en) | A kind of thermal calculation method of continuous helical deflecting plate pipe and shell type heat exchanger | |
He et al. | A general and rapid method for performance evaluation of enhanced heat transfer techniques | |
Cao et al. | R245fa condensation heat transfer in a phase separation condenser | |
Sun et al. | Two-phase heat transfer in horizontal dimpled/protruded surface tubes with petal-shaped background patterns | |
Zhang et al. | Experimental study of condensation heat transfer in a condenser with a liquid-vapor separator | |
CN109387104A (en) | A kind of loop circuit heat pipe | |
Cao et al. | Condensation heat transfer of R245fa in a shell-tube heat exchanger at slightly inclined angles | |
Su et al. | Experimental study on the constituent separation performance of binary zeotropic mixtures in horizontal branch T-junctions | |
Moghaddam et al. | Flow pattern maps, pressure drop and performance assessment of horizontal tubes with coiled wire inserts during condensation of R-600a | |
Wu et al. | Mathematical modeling and performance analysis of seawater heat exchanger in closed-loop seawater-source heat pump system | |
Ma et al. | R410A and R32 condensation heat transfer and flow patterns inside horizontal micro-fin and 3-D enhanced tubes | |
Zheng et al. | Heating performance and spatial analysis of seawater-source heat pump with staggered tube-bundle heat exchanger | |
Na et al. | Experimental and theory investigations on falling film flow characteristics and heat extraction performance of spray heat exchanger for sewage heat pump system | |
Tong et al. | CFD simulation on the operation characteristics of CO2 two-phase thermosyphon loop | |
Liu et al. | Analysis of the heat transfer characteristics of the liquid-vapor separation condenser based on a condensate growth model in horizontal tube | |
Li et al. | Thermodynamics performance analysis of flue gas treatment process using ceramic membranes | |
Zhang et al. | Experimental study on heat transfer and flow resistance characteristics of integral rolled spiral finned tube bundles heat exchangers | |
Xiao et al. | Numerical investigation on maldistribution of S-CO2 flow inside PCHE under rolling conditions |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
C06 | Publication | ||
PB01 | Publication | ||
C10 | Entry into substantive examination | ||
SE01 | Entry into force of request for substantive examination | ||
C14 | Grant of patent or utility model | ||
GR01 | Patent grant | ||
CF01 | Termination of patent right due to non-payment of annual fee | ||
CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160210 Termination date: 20170516 |