This derivation was provided by Howard Cheung but was originally carried out by Jim Braun. Editorial modifications have been made by Ian Bell.
Partial-wet-partial-dry analysis is the technique given in Braun  used to estimate the performance of an air-to-refrigerant evaporating coil with a higher accuracy for estimating the latent heat transfer than completely wet or dry analysis. The methodology is to divide the heat exchanger into two sections by locating the point on the heat exchanger surface where the dewpoint is reached. For the part with surface temperature below dewpoint, they are lumped together for a completely wet analysis. The remaining one is lumped together as a dry section.
To illustrate the idea, the document gives an example on a steady counterflow air-to-refrigerant heat exchanger in which air is cooled and moisture is condensed on the heat exchanger surface. The governing equations are listed based on the assumptions, and an algorithm is derived to solve the implicit mathematical model for the analysis.
In the following analysis, the following assumptions are employed:
The analysis can be divided into three parts:
Initially, the dry analysis is implemented. Should the surface temperature at the air outlet be higher than the dewpoint of the air, the dry coil assumption is accepted. Otherwise the wet analysis is carried out on the entire heat exchanger and the surface temperature at the air inlet is examined. If the temperature is lower than dewpoint, the completely wet coil assumption is accepted. If both assumptions are rejected, there must exist a point on the heat exchanger where the temperature is at the dewpoint and the partial-wet-partial-dry analysis is implemented.
These equations can be solved analytically for the heat exchanger performance. After solving the heat exchanger, one may find the temperature on the surface of the heat exchanger at the air outlet by Equation (9).
If the temperature is higher than dewpoint of inlet air, the coil is said to be dry and the heat exchanger performance analysis is completed. Otherwise completely wet analysis is conducted.
In the case of wet analysis, the unity Lewis number is used such that the temperatures in the method are converted to the corresponding air-water mixture enthalpies to account for the condensation of moisture from air on the heat exchanger surface. The method is modified to form governing equations listed from Equation (10) to (19).
These equations are formed explicitly and can be solved analytically for the performance of the heat exchanger. The wet coil assumption is verified by comparing the heat exchanger surface temperature with the dewpoint of inlet air. The temperature can be calculated by Equation (20) which the definition of is given in Equation (21).
If the temperature is lower than the dewpoint, the completely wet coil assumption is accepted. Otherwise the calculation will proceed to the next part: partial-wet-partial-dry analysis.
The partial-wet-partial-dry analysis divides the heat exchanger into two regions: a wet region and a dry region. The heat transfer rate can be divided into two parts as shown in Equation (22):
Both sections can be addressed based on method except that a separate set of governing equations are used for each section. The dry section can be described as lists of equations from Equation (23) to (26).
At the intersection between the dry and wet region, the heat transfer is governed as Equation (33).
Unlike the previous analyses, these equations cannot be solved analytically because only the inlet conditions of refrigerant and air are known. To solve equations iteratively, a bounded solver on can be used because is proved to be between 0 and 1 from the previous analysis. One way is to calculate the refrigerant outlet temperature based on the dry region only and on both wet and dry region and compare the error between the two methods. Should the error close to zero, the heat exchanger is solved. In this case, one can derive a function which when the solution is reached, the function equals to zero as Equation (34).
The function is defined as Equation (35) as a function of and a solution of is said to be found if equals some value very close to zero.
The following subsections describe how to find and .
With the dry region only, a simplification is first conducted on Equation (26).
An can be defined with as Equation (49).
For convenience, another dimensionless variable is defined in Equation (51).
Another term can be defined as in Equation (57).
Because the specific heat of air is taken to be constant, . Thus, the enthalpy of the air at the wet-dry interface can be given by
The value of can be substituted from Equation (29) which yields the value for of
By solving Equations (26), (32), (68) and (69), one can find in Equation (35). The in Equation (35) can be found for diffferent and the one which gives a function value close to zero is the numerical solution of . With the value of , all other variables in the partial-dry-partial-wet analysis can be computed and the heat exchanger performance can be solved.
|Surface Area [m2]|
|Dimensionless variable [–]|
|Capacity Rate [W/K]|
|Specific Heat Capacity [J/kg/K]|
|Analogous specific heat capacity for air-water enthalpy [J/kg/K]|
|Proportion of dry section [–]|
|Function to be solved [any]|
|Air-water mixture enthalpy [J/kgha]|
|Dimensionless variable [–]|
|Mass Flow Rate [kg/s]|
|Number of transfer unit [–]|
|Overall Number of transfer units [–]|
|Heat Transfer Rate [W]|
|Heat Transfer Coefficient [W/m2/K]|
|Overall Heat Conductance [W/K]|
|Overall Heat and Mass Transfer Conductance [W/K]|
|Solution of [any]|
|Heat Exchanger Effectiveness [–]|
|Dimensionless variable [–]|
|Of air side|
|Of dry region|
|Of partial condition|
|Of refrigerant side; in the case of , it means the air-water enthalpy at the temperature of the refrigerant|
|Of wet region|
|Of/Adjusted for mass transfer|
|||Braun, J. E., 1988. Methodologies for the Design and Control of Central Cooling Plants. Ph.D. thesis, University of Wisconsin - Madison.|