Line connections |
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1 |
Inlet (cold medium, flows inside the tubes) |
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2 |
Outlet (cold medium, flows inside the tubes) |
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3 |
Inlet (hot medium, flows external to the tubes) |
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4 |
Outlet (hot medium, flows external to the tubes) |
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5 |
Auxiliary condensate inlet (without throttle) |
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6 |
Control inlet for KAN (as H) |
General User Input Values Characteristic Lines Physics Used Displays Example
Component 10 can be used, when a gas (steam or superheated steam) is to be condensed to heat a cold medium (gas or liquid).
Typical application examples are the modeling of a
Like most components, the component can be designed with a design calculation, i.e. nominal values are calculated, transferred and stored in a design calculation. Alternatively, it is also possible to completely describe the component by entering geometry and material data.
In this case a transient calculation is also possible, i.e. time-dependent heat input and output processes in the component material can be calculated.
In all calculation modes component 10 calculates the required steam quantity to be condensed for the respective specifications. If this steam quantity is specified from the outside, the condenser (component 7) or the heat consumer (component 35) can be used instead.
The component represents the desuperheating of the superheated steam and its condensation, but no sub cooling. The outgoing condensate is therefore basically saturated liquid. To model sub cooling, an after cooler (component 27) has to be added.
The cold medium is usually water, almost all other media can be used, e.g. for modeling a steam LUVO. The warm medium can be steam, two-phase fluid, binary mixture or a corresponding universal fluid.
In case of design, FSPECD has to be set: Either
The result of the design calculation is, among other things, the nominal value for k*A, known as KAN. In the case of the geometry-based calculation (FGHXT=1), the NTU-Effectiveness correction factor CORCFN and the cleanliness factor CLTUBE are calculated in the design calculation.
k: overall heat transfer coefficient,
A: heat transfer surface,
k*A: heat transfer capability, product of k and A
KAN: Heat transfer capacity at the design point (nominal value)
The component can also be used with fluid type Binary fluid as warm fluid. If this fluid is overheated, the grade DT3S2N refers to the dew point temperature of the fluid (as for component 7), otherwise to the fluid temperature.
Radiation losses can be specified via a related loss factor. The switch FDQLR is used to set how DQLR (factor for modeling heat losses) should be interpreted. In a calculation with geometry, radiation losses are calculated from the parameters for the insulation (THISO, LAMISO), the external convective heat transfer coefficient ALPHO and the ambient temperature.
As a real heat exchanger, unlike the model component, is not a pure counter current heat exchanger, the calculation of the heat transfer is corrected with a cross-flow correction factor (value < 1). This factor is determined in the design calculation according to a stirred tank model (VDI-Wärmeatlas edition 11 chapter C1) and stored as nominal value CORCFN for the partial load calculation.
The partial load behaviour is calculated with one of these methods:
Switching is done with the FRABEK and FGHXT switches.
In the case of superheated steam at the inlet, component 10 considers two zones: the desuperheating zone and the condensation zone. In both zones the heat transfer coefficients (alpha numbers) between the warm fluid and the tube wall are different. In no case is an analytical calculation method used.
The alpha number (Convective Heat Transfer Coefficient) for the condensation zone is named AL34N, the alpha number for the desuperheating zone is named AL34DN.
- The heat transfer between the cold fluid (12) and the tube wall
- The heat transfer between the warm fluid (34) and the tube wall
- The heat transfer between the warm fluid (34) and the jacket wall
- The temperature curve in the pipe wall
- The temperature curve in the jacket wall
Similar to other components, a FIDENT switch has been introduced to activate the identification mode.
FIDENT has the settings:
FIDENT =-11 and FIDENT =11 were made accessible for special data reconciliation requirements, which corresponded to the previous settings, under FSPEC=-11 and FSPEC =11 respectively.
In order not to change the behaviour of existing models, the switch FSPEC can still be used. In this case the settings for FIDENT and FSPECD are ignored.
Note in connection with the Rabek method:
Since this method is non-linear, when using quality grades as correction factors, a correction factor determined in part load cannot simply be used to correct the nominal values. EBSILON®Professional provides the result value KANRAB for this purpose. This is the fictitious value for KAN, which in a partial load calculation without identification mode would lead to the result obtained in identification mode.
Component 10 enables the modeling of transient cases (time-dependent temperature distribution). This type of calculation is activated with the switch FINST. A thermodynamic equilibrium between the liquid and the gaseous phase in the condensate space is assumed.
For the transient calculation, the specification of the geometrical details of the heat exchanger is necessary, such as the geometrical and material specifications of the casing or jacket. For this purpose the switch FGHXT=1 is used. From the geometrical data the fluid volume, the wall storage mass and the exchange surface between wall and fluid are calculated. The properties of the wall material such as density, thermal conductivity, heat capacity can either be selected from the stored library (switch FMTUBE, FMSHELL) or directly specified by the user.
With FGHXT=1 the heat transfer is calculated also in stationary case with geometry.
For the stationary solution of heat exchange with FGHXT=1 (geometry based) component 10 uses the numerical algorithm, because no simple analytical relation between K-number and alpha-numbers in case of 2-zones (desuperheating and condensation) is possible. With this numerical algorithm the result depends on the number of points in the direction of flow (NFLOW).
The transient mass balance takes into account a level change in the condensate space during the time step. For the mass balance, the user can use the FSPIN switch to decide between setting the level or the mass flow M4. The calculated level is output as the volume fraction of the liquid phase in the volume between the values of VMIN and VMAX at port 6 as mass flow M6.
(see also: Edit objects --> Connections)
To make component properties such as efficiencies or heat transfer coefficients (variation quantity) accessible from the outside (for control or validation) it is possible to place the corresponding value as indexed measured value (default value FIND) on an auxiliary line. The same index must then be entered in the component as default value IPS.
It is also possible to place this value on a logic line at connection 6, which is directly connected to the component (see FVALKA=2, variation size: KAN, dimension: enthalpy). The advantage is that the assignment is now graphically visible and thus errors (for example by copying) are avoided.
Grade RPFHX
For the assessment of the condition of component 10 the quotient of the current value for k*A (result value KA) and the k*A expected at the respective load point due to the component physics or characteristics (result value KACL) is used. The quotient KA/KACL is output in the result value RPFHX.
If the RABEK method is used, the quotient KANRAB/KAN is displayed in RPFHX instead.
For further general information with reference to most common heat exchangers see Heat Exchangers, General Remarks
For more information on comparing this heat exchanger with other heat exchangers, see Heat Exchangers, General Components
FINST |
Transient mode: 0: Transient solution (time series or single calculation) 1: Always steady state solution |
FMODE |
Flag for calculation mode design/off-design =0: global =1: local off-design (i.e. always off-design mode, even when a design calculation has been done globally) =2: special local off-design (special case for compatibility with earlier Ebsilon-versions, not to be used in new models, because the results of the real off-design calculations are not consistent) = -1: local design |
FFU |
Flag for activating the component = 1: Heat exchanger switched on = 0: No heating of the cold steam. In this mode only a heating of the feed water is prevented. However, the condensate outlet is still kept at saturated water conditions. When super-cooled auxiliary condensate is fed, then only so much steam is extracted that this can be warmed to the saturated water temperature. =-1: The steam supply is completely stopped. When super cooled auxiliary condensate is supplied, then this comes out as super cooled too. The pressure drop for the cold side is treated the same way in all cases. |
FIDENT |
Component identification =0: NO Identification =2: T2 (outlet temperature of cold stream) given externally in off-design, KA calculated =-11: Consider mass and energy balances and H4=H' only =11: Consider mass and energy balances and Fourier equation LMTD*KAN-M1*(H2-H1)=0 |
FSPECD |
Design specification method =0: Design using DT3S2N =1: Design using T2 (given externally) |
DT3S2N |
Upper terminal temperature difference T3S-T2 (Default only in design case) |
FDP12 |
Cold side pressure drop handling =1: Calculation of the pressure loss from the nominal value DP12N =-1: P2 Pressure specification from outside |
DP12N |
Cold side pressure drop, line 1 to 2 (nominal) |
FDP34 |
Hot side pressure drop handling =1: Calculation of the pressure loss from the nominal value DP34N =-1: P4 Pressure specification from outside |
DP34N |
Warm side pressure drop, line 3 to 4 (nominal) |
FDPNUM |
Pressure loss handling in the numerical solution =0: Using the average fluid pressure between inlet and outlet |
FP5 |
Throttling of secondary condensate =0: No throttling (P5 = P3) |
FDQLR |
Heat loss handling =0: Constant (DQLR*QN in all load cases) |
DQLR |
Relative heat loss to the environment |
TOL |
Accuracy of the energy balance for the internal iteration |
FRABEK |
Calculation according to the method of Rabek =0: No (instead, using the characteristic lines) =1: Yes (Characteristic lines are ignored) |
FFLOW |
Direction of flow =0: (currently not used) |
FSPEC (deprecated) |
Deprecated specification combi switch =-999: unused (FSPECD and FIDENT used instead) Deprecated values: =0: Outlet temperature T2 calculated (in design from DT3S2N, in off-design using Fourier's law) =5: Outlet temperature T2 specified externally in design, calculated in off-design =-1: Outlet temperature T2 specified externally in all load cases (constant) (identification mode) =-11: Consider mass and energy balances and H4 = H' only. =11: Consider mass and energy balances and Fourier Equation LMTD * KAN - M1*(H2-H1) = 0 |
FADAPT |
Flag for using the adaptation polynomial / adaptation function =0: Off=1: Correction factor for k*A [KA = KAN * carlines factor *polynomial] =2: Calculation of k*A [KA = KA * polynomial] =1000: Not used but ADAPT evaluated as RADAPT (Reduction of the computing time) =-1: Correction factor for k*A [KA = KAN * carlines factor *function] =-2: Calculation of k*A [KA = KA * function] =-1000: Not used but EADAPT evaluated as RADAPT (Reduction of the computing time) |
EADAPT |
Adaptation function for KA |
FVALKA |
Validation of k* =0: KAN used without validation =1: Pseudo measurement point identified by IPS used (can be validated) =2: KAN given by enthalpy on logic line 6 |
IPS |
Index for pseudo measurement point |
KAN |
k*A (nominal) - Design Heat Transfer Capability |
M1N |
Cold side mass flow (nominal) |
M3N |
Hot side mass flow (nominal) |
V1N | Cold side specific volume (nominal) |
V3N | Hot side specific volume (nominal) |
QN |
Heat quantity given off at nominal load (nominal) |
CORCFN |
NTU-Effectiveness correction factor (re-computed in design only) |
FGHXT |
Use geometry based approach (e.g. HEI, VDI) in heat transfer calculation 0: No 1: Use Alpha and Lambda values according to FALPH and FMTUBE |
FTUBG |
Tube geometry specification (HEI, transient calc.) 0: Use DTUBEIN and DTUBEOU 1: Use DTUBEIN and DWALL 2: Use DTUBEOU and DWALL |
DWALL | Tube wall thickness |
DTUBEIN | Inner diameter of tube |
DTUBEOU | Outer diameter of tube |
FBUNDL |
Tube bundle specification 0: Use NTUBE, NPASS and ATUBE 1: Use NTUBE, NPASS and TUBELEN |
NTUBE | Number of tubes |
NPASS | Number of tube passes |
ATUBE | Total outside tube surface area |
TUBELEN | Tube length |
SDIAM | Shell diameter |
SLENG | Shell length |
SWALLT | Shell wall thickness |
THISO | Thickness of insulation |
CLTUBE | Cleanliness factor |
FINIT |
Flag: Initializing state =0: Global, which is controlled via global variable "Transient mode" under Model Options =1: First run -> Initializing while calculating steady state values |
FMTUBE |
Steel grade for the tubes see Material Properties of Steel =-1 : Properties computed from kernel expression ERHOT, ELAMT, ECPT |
ERHOT | Function for tube material density |
ELAMT | Function for tube material heat conductivity |
ECPT | Function for tube material heat capacity |
FMSHELL |
Steel grade for the shell see Material Properties of Steel =-1 : Properties computed from kernel expression ERHOS, ELAMS, ECPS |
ERHOS | Function for shell material density |
ELAMS | Function for shell material heat conductivity |
ECPS | Function for shell material heat capacity |
LAMISO | Thermal conductivity insulation |
FALPH12 |
Determination of alpha fluid12 to wall 0: Using internal formulas from VDI Wärmeatlas Edition 11 Chapter G1 1: from constant value AL12N 2: from kernel expression EALPH12 |
AL12N | Cold side heat transfer coefficient (nom.) |
EALPH12 | Function for ALPH12 |
FALPH34D |
Determination of AL34D 0: from constant value AL34DN 1: from AL34DN and flow rate exponent EX34D |
AL34DN | Heat transfer coefficient desuperheating zone |
EX34D | Flow rate exponent of AL34D |
FALPH34 |
Determination of alpha fluid34 to wall 0: Using internal formulas from VDI Wärmeatlas Edition 11 Chapter J1 1: from constant value AL34N 2: from kernel expression EALPH34 |
AL34N | Hot side heat transfer coefficient (nom.) |
EALPH34 | Function for ALPH34 |
FALPHO |
Determination of alpha outside 0: from specification value ALPHO 1: from function EALPHO |
ALPHO | Outer heat transfer coefficient (to ambient) |
EALPHO | Function for alpha outside |
FSPIN |
Transient balance calculation mode 0: Liquid level given, mass flows computed 1: Mass flows given, liquid level computed |
VF | Averaged liquid volume fraction (liquid level) during the time step |
VMIN | Volume at liquid volume fraction 0 |
VMAX | Volume at liquid volume fraction 1 |
FLVCALC |
Liquid volume calculation mode 0: linear between VMIN and VMAX 1: Using ELV |
ELV | Function for the liquid volume computation |
NFLOW | Number of points in flow direction (max. 100) |
FNUMSC |
Numeric scheme 0: Upwind (highest stability) 1: Central differences (high accuracy) |
TMIN | Lower limit for storage temperature |
TMAX | Upper limit for storage temperature |
FSTAMB |
Definition of ambient temperature 0: by specification value TAMB 1: defined by reference temperature (comp. 46) |
TAMB | Ambient temperature |
The parameters marked in blue are reference quantities for the off-design mode. The actual off-design values refer to these quantities in the equations used .
Generally, all inputs that are visible are required. But, often default values are provided.
For more information on colour of the input fields and their descriptions see Edit Component\Specification values
For more information on design vs. off-design and nominal values see General\Accept Nominal values
Q21 |
Heat quantity, by which the cold stream (line 1 to line 2) is heated |
QT |
Heat quantity calculated from the product of KA * logarithmic temperature difference |
QT354 |
Heat quantity, which is extracted from the main and auxiliary condensate (sum from line 3 and 5 after line 4) The values of Q21, QT and QT354 should match in their calculation efficiency. Differences indicate errors or inadequate convergence. |
KA |
Heat transfer coefficient * area |
KANR |
Used value for KAN |
KANRAB |
Fictitious value for the nominal value KAN, which would lead to the value for k*A when the Rabek-method is used, which is currently set (owing to temperature specifications). This value helps in determining the quality grade of the component from the measurement values. Owing to the non-linearity of the Rabek-formalism this cannot be done simply from the ratio of KA/KACL, but instead it must be determined through a reverse calculation of the Rabek-formula of the value for KAN, which leads to KA through the measured values in the actual load case. KANRAB is calculated only when
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RPFHX |
Performance factor Heat transfer |
DTM |
Average logarithmic temperature difference. In the counter current mode (which is always the case in this component): DTM = ((T3S-T2)-(T4S-T1)) / LN ((T3S-T2)/(T4S-T1)) Thereby, T3S and T4S are the saturation temperatures for the pressures P3 and P4 respectively. Since in the calculation method according to Rabek negative terminal temperature differences can occur, in this case an effective DTM is output from the quotients of the exchanged heat quantity and k*A. |
DT4S1 |
Lower terminal temperature difference In the counter current mode (which is always the case in this component): DT4S1 = T4S-T1 |
DT3S2 |
Upper terminal temperature difference In the counter current mode (which is always the case in this component): DT3S2 = T3S-T2 |
X1 |
Steam quality (cold side outlet) (pin 2). |
X2 |
Steam quality (hot side outlet) (pin 4). |
DP12 |
Calculated cold side pressure difference |
DP34 |
Calculated hot side pressure difference |
M1M1N |
Ratio of the actual cold side mass flow to its nominal value: |
M3M3N |
Ratio of the actual hot side mass flow to its nominal value: |
KAKAN |
Ratio of the actual k*A to its nominal value: |
KACL |
Fictitious value of k*A, which would result, if the calculation was done only with characteristic lines:
KACL is the same as the product of KAN and both the factors from the 1/2 and the 3/4 KA-characteristic lines. |
RADAPT |
Value of the adaptation polynomial used This value is calculated only when the adaptation polynomial is used; else it is 1. |
PINP |
Pinch point The pinch point is defined as the temperature difference at the transition point between deheating zone and the condensation zone: PINP = T3S - TP whereby TP is the temperature of the primary medium, which is set when one adds only the heat of condensation to the primary medium (i.e. without the heat from deheating). The following is true: HP = H1 + ((H(T3S)-H4)/(H3-H4)) * (H2-H1) TP is then the temperature calculated from HP and P2 with the water-steam table. |
HSAT |
Hot side saturated steam enthalpy |
TSAT |
Hot side saturation steam temperature |
PSAT |
Hot side saturation steam pressure |
SSAT |
Hot side saturated steam entropy |
1st Characteristic Line CKAM1 FK1 = f (M1/M1N)
2nd Characteristic Line CKAM3 FK2 = f (M3/M3N)
(K*A)/(K*A)N = FK1 * FK2
Characteristic line1: (k*A)-Characteristic line CKAM1 : (k*A)1/(k*A)N = f (M1/M1N) |
X-Axis 1 M1/M1N 1st point |
Characteristic line 2: (k*A)-Characteristic line CKAM3: (k*A)2/(k*A)N = f (M3/M3N) |
X-Axis 1 M3/M3N 1st point |
Design case (Simulation flag: GLOBAL = design case and FMODE = GLOBAL) |
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T3S = f'(P3) P2 = P1 - DP12N T2 = T3S DT3S2 H2 = f(P2,T2) M2 = M1 Q2 = M2 * H2 DQ = M2 * H2 - M1 * H1 P4 = P3 - DP34N P4 = P5 Q4 = Q3 + Q5 - DQ/(1-DQLR) M4 = M3 + M5 H4 = Q4/M4 T4 = f(P4,H4) DTL = T4 - T1 DTU = T3 - T2 LMTD = (DTU - DTL)/(ln(DTU) - ln(DTL)) M3 = (DQ/(1-DQLR)-M5*(H5-H4S))/(H3-H4S) |
Off-design case (Simulation flag: GLOBAL = off-design or FMODE = local off-design) |
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F1 = (M1/M1N) ** 2 P2 = P1 - DP12N * F1 M2 = M1 Fk1 =f(M1/M1N) from characteristic line 1 Fk2 =f(M3/M3N) from characteristic line 2 (k*A) = (k*A)N * Fk1 * Fk2 F3 = (M3/M3N) ** 2 P4 = P3 - DP34N * F3 P4 = P5 M4 = M3 + M5 Pre-estimation before beginning the iteration T4 = f'(P4) H4 = f'(P4) H2max = f(P2,T3) Q12max = M1 * (H2max - H1) Q34max = Q3 + Q5 - M4 * H4 Qmax = min(Q12max,Q34max) Q12 = 0.5* Qmax Start of iterationH2 = H1 - Q12/M2 T2 = f (P2,H2) DTL = T4 - T1 DTU = T3 - T2 LMTD = (DTU - DTL)/(ln(DTU) - ln(DTL)) QQ = (k*A) * LMTD DQQ = Q12 QQ Start of the Regula Falsi method Q12 = Q12 - DQQ * grad End of the Regula Falsi method DQ = | DQQ/((Q12+QQ)/2.0) | If DQ < TOL, then end of iteration M3=(Q12+QN*DQLR-M5*(H5-H4) )/(H3-H4) Q4 = M4 * H4 Q12 = (Q3 + Q5 - Q4 - QN*DQLR) Q2 = Q1 + Q12 H2 = Q2 / M2 T2 = f (P2,H2) DQ = M2 * H2 - M1 * H1 |
Display Option 1 |
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Display Option 2 |
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