## 1. Introduction

There are many methods for evaluating the performance of a numerical modeling system. For example, the model can be shown to reasonably reproduce an observed meteorological event. Or, it can be demonstrated that the model produces realistic features and evolutions of a phenomenon for which the model was designed to study; for example, a cloud model can be shown to reasonably predict the details of clouds, or a model designed to study the planetary boundary layer can be shown to accurately reproduce the statistical properties of this feature.

The most powerful methods for evaluating a numerical modeling system are comparisons to cases with known results that can be derived through dynamical analysis, or to benchmark solutions that converge under certain conditions. Examples of commonly used analytic and/or benchmark cases include certain mountain wave solutions (e.g., Clark 1977; Dudhia 1993), inertia-gravity waves (Skamarock and Klemp 1994), a nonlinearly evolving cold pool and density current (Straka et al. 1993), and a rising warm thermal (Tripoli 1992; Wicker and Skamarock 1998). Simulations such as these are important for a number of reasons, such as establishing the fidelity of a new numerical modeling system, or testing the accuracy, efficiency, and efficacy of a new numerical technique.

Unfortunately, none of these analytic/benchmark cases include moist processes. Moreover, despite the varying methods used to include moist processes in numerical models, there does not appear to be a commonly agreed-upon method to evaluate a moist model formulation. Typically, a model developer will demonstrate that a model produces reasonable fields of parameters such as vertical velocity, cloud/rainwater mixing ratios, rainfall, etc. for a case of deep, moist convection. While this is an important and necessary step in the development of a numerical model, the lack of a known solution limits the conclusions that can be drawn from such tests. Another common method compares the results from a new model to published results from a different model. While, again, this is an important step in evaluating the fidelity of a new numerical model, this method makes it possible to propagate questionable assumptions through time.

This paper presents a new simulation that can be used as a benchmark for testing numerical models with moisture. The design of the simulation is analogous to the nonlinear warm thermal benchmark case used by Tripoli (1992) and Wicker and Skamarock (1998), but includes phase changes of water vapor and cloud water.

The numerical model used for this study is described in section 2. The dry warm thermal simulation is presented in section 3. Then, the moist test case is presented in section 4. The utility of the test case is demonstrated in section 5 by evaluating common assumptions made in numerical models and the effects these assumptions have on the test case. A summary and conclusions are presented in section 6.

## 2. The numerical model

### a. Governing equations

^{1}for a moist atmosphere are

*i*= 1, 2, 3” signifies the

*x,*

*y,*and

*z*components, respectively, and

*δ*

_{ij}is the Kronecker delta. The symbols

*ρ*

_{a},

*p,*

*T,*

*r*

_{υ},

*r*

_{c}, and

*r*

_{t}are, respectively, dry air density, pressure, temperature, water vapor mixing ratio, cloud water mixing ratio, and total water mixing ratio. An assumption implicit in the left-hand side of (3) is that the temperature of the liquid water drops is always equal to the air temperature.

*π*) and potential temperature (

*θ*) are solved, which are defined as

*p*

_{00}= 1000 mb, and

*p*

*ρ*

_{a}

*RT*

*r*

_{υ}

*π*and

*θ*are derived, yielding

*R*

_{m}≅

*R,*

*c*

_{pml}≅

*c*

_{p}, and

*c*

_{vml}≅

*c*

_{υ}, yielding the traditional potential temperature equation,

^{2}since

*π̃*

*π*; specifically, if the pressure gradient terms were written as ∂

*π̃*

*x*

_{i}, additional terms involving the spatial derivatives of

*r*

_{υ}and

*r*

_{c}would be necessary. We have also found that a model formulated with

*π̃*

*θ̃*

*π*and

*θ,*with no perceptible improvements in accuracy.

### b. Numerical techniques

*z*direction, and primes refer to deviations from this base state. The hydrostatic equation governing the base state is

*θ*

_{ρ}(Emanuel 1994, p. 113), is defined as

Following the technique introduced by Klemp and Wilhelmson (1978), the portions of the governing equations that support acoustic waves are integrated on a smaller time step than other terms. The final term on the right-hand side of (20) is a divergence damper, where *K*_{d} is a constant and *D* = ∂*u*_{j}/∂*x*_{j}; this term helps maintains stability of the time-splitting technique (Skamarock and Klemp 1992). For the simulations presented here, the model is integrated with third order Runge–Kutta time differencing and fifth-order spatial derivatives for the advection terms (following Wicker and Skamarock 2002).

To account for phase changes, the model uses a saturation adjustment technique, similar to that proposed by Soong and Ogura (1973). In this technique, the equations are advanced forward in two steps: a dynamical step and a microphysical step. In the dynamical step, the model equations are integrated forward with all terms involving phase changes neglected. Then, the microphysics step is applied, in which only the terms involving phase changes are included. This technique is identical to that used by Klemp and Wilhelmson (1978).

*ṙ*

_{cond}. The new values of

*θ*and

*π*are then used to calculate a new value of saturation mixing ratio (

*r*

_{vs}), which is then used to calculate a new guess for

*ṙ*

_{cond}. This cycle is repeated until the newest value of

*θ*converges (to within machine accuracy) to the previous value. During each iteration, the value of

*ṙ*

_{cond}is determined by the following equation from Rutledge and Hobbs (1983),

*t*is the time step. The iterative technique usually converges in 4–6 iterations.

*ρ*

_{t}) and the total energy (

*E*

_{t}) in the domain during a model integration, where

*ρ*

_{a}, is determined using the equation of state, (9). The definition of total energy used here is the sum of internal, potential, kinetic, and latent energies—it differs from that used in other studies by the inclusion of the latent energy, which is required to account for the effects of moist processes. For simulations with no flow across the boundaries, and without external sources of mass, momentum, or energy, the domain-total sum of

*ρ*

_{t}and

*E*

_{t}should, theoretically, remain constant over time.

## 3. The dry simulation

*x*

_{c}= 10.0 km,

*z*

_{c}= 2.0 km, and

*x*

_{r}=

*z*

_{r}= 2.0 km. No physical or computational diffusion is applied.

Results of a simulation with 100-m grid spacing after 1000 s of integration are presented in Fig. 1. Similar to the results of Wicker and Skamarock (1998), the thermal rises and expands over time. Two “rotors” develop on the sides of the thermal, while the top of the thermal is stretched. Large *θ* gradients develop in the middle of the thermal (i.e., within the “arch” spanning between the two rotors).

*θ*

_{0}is the reference value of potential temperature for the new simulation, and

*θ*′|

_{300}is the perturbation potential temperature field from the 300-K simulation given by (30). The results displayed in Fig. 2 are very similar to the 300-K reference simulation. Although the fields from these various simulations are not exactly the same, the key point is that the thermal has the same structural details, suggesting a relative independence to the exact thermodynamic value of the neutrally stable base state. Therefore, this property of the solution provides a benchmark for testing new model formulations.

## 4. The moist simulation

*r*

_{t}=

*r*

_{υ}+

*r*

_{c}= constant; and 2) phase changes are exactly reversible, that is, Δ

*r*

_{υ}= Δ

*r*

_{vs}= −Δ

*r*

_{c}. Under these two assumptions, a neutrally stable environment can be obtained using one conservative thermodynamic variable (see, e.g., Durran and Klemp 1982). We use the wet equivalent potential temperature, defined for a reversible moist adiabatic atmosphere by

*P*

_{d}is the partial pressure of dry air. Using (25), (26), and (34), the vertical profiles of

*π,*

*θ,*

*r*

_{υ}, and

*r*

_{c}can be obtained if values for

*θ*

_{e}and

*r*

_{t}are provided. The value of

*r*

_{t}must be greater than

*r*

_{vs}at all levels, so that the initial sounding is saturated, and

*r*

_{c}> 0 at all levels.

All other parameters are the same as for the dry case, that is, the surface pressure is 1000 mb, the initial wind field is zero, grid spacing is 100 m, and the domain dimensions are as before. No microphysics parameterization is used, other than the assumption of reversible phase changes. Precipitation fallout is not allowed.

The following simple test can be performed using a numerical model to prove that the initial state has been computed accurately, and that the model is configured properly for the benchmark simulation: if no buoyancy perturbation is applied to the model's initial conditions, then no motions should arise. In practice, we have found that small vertical motions (of order 10^{−4} m s^{−1}) may develop during this test due to truncation errors in the vertical momentum equation (particularly in the balance between the vertical pressure gradient term and the buoyancy term) and/or in the microphysics code (particularly the code that handles condensation), although the present model has been carefully coded so that no vertical motions develop.

*θ*

_{0}is 300 K. For moist conditions, buoyancy is given by

*θ*

_{ρ}, the initial

*θ*field is:

*r*

_{t}= constant, and

*r*

_{υ}=

*r*

_{vs}(

*p,*

*T*), the buoyant perturbation has slightly more water vapor and slightly less cloud water than the base-state sounding.

The results after 1000 s of integration for a case in which *θ*_{e} = 320 K and *r*_{t} = 0.020 are presented in Fig. 3. The results of this moist case are very similar to the results of the dry case (Fig. 1), especially with regards to the structural details such as the two rotors that form on the sides of the thermal and the thin arch that connects them. The moist thermal rises slightly faster than the dry thermal, and after 1000 s the vertical velocity field has higher maximum and minimum values. Nevertheless, the structural details are remarkably similar.

It is important to reiterate that the model formulation for this simulation does not neglect any term in the governing equations. In particular, the specific heat of liquid water (*c*_{pl}) is included, and the diabatic contribution to the pressure equation is included; it is a common assumption in numerical models to neglect these two effects. Furthermore, the error in total mass and energy conservation is quite small (about 10^{−4} %), especially compared to model formulations that ignore certain terms in the governing equations (which will be presented in the next section). Given this high degree of accuracy in mass and energy conservation, and the similarity to the dry case, it seems reasonable that this case can be considered a moist benchmark to which moist numerical models can be compared. Additionally, as in the dry case, the simulation proposed here is remarkably insensitive to the values used to define the initial neutrally stable sounding. For example, Fig. 4 shows the results from simulations with *θ*_{e} = 360 K and *r*_{t} = 0.024, and a case with *θ*_{e} = 280 K and *r*_{t} = 0.004. Again, the results are nearly identical. These results show that the design of the moist simulation is robust, that is, the correct result is not dependent on a specific initial thermodynamic environment. This is an important point, since it provides further confidence that the results of the simulation truly represent a benchmark solution.

## 5. Sensitivity to model formulation

### a. Governing equations

The assumptions of reversible phase changes and the absence of hydrometeor fallout clearly make this test case a simplification of reality. However, we have found the case to be valuable for testing the formulation of numerical models, such as defining the governing equations of the model, and for testing numerical techniques involving moist terms. As an example, four different model formulations are tested and presented in this section. Three of these model formulations are found in the literature. The fourth ignores a term that scale analysis suggests has negligible effects on the potential temperature tendency. In all of these cases, only the thermodynamic equation and/or pressure equation is modified.

*θ*

_{il}) of Tripoli and Cotton (1981) for the thermodynamic equation, where

*θ*

_{il}is defined as

*r*

_{l}is the liquid water mixing ratio (which is simply

*r*

_{c}in the benchmark simulation), and the ice phase has been ignored. Equation set D also neglects the diabatic contribution to the pressure equation, and the specific heats of water vapor and liquid water in the pressure equation. This equation set is similar to that used in Regional Atmospheric Modeling System (RAMS) (Pielke et al. 1992) and in the University of Wisconsin Nonhydrostatic Modeling System (Tripoli 1992).

Before proceeding, it should be noted that all of the equations listed in Table 1 become identical to the “benchmark” equations in the absence of water. Therefore, simulations of the dry thermal case (section 3) are identical for all model formulations presented here. However, if water vapor is present but no liquid water develops (i.e., phase changes either do not occur or are not allowed), then the various equations sets are not identical. This is because the terms involving divergence in the thermodynamic and pressure equations [second terms on the right-hand side of (11) and (12)] only go to zero when water vapor *and* liquid water mixing ratios are zero.

For these simulations, the initial environment is defined by *θ*_{e} = 320 K and *r*_{t} = 0.020. The results in Figs. 5 and 6 clearly show the dramatic impact of neglecting terms from the complete thermodynamic and pressure equations—none of the simulations using approximate equations compare well with the benchmark solution (Fig. 3). In all of these cases, the thermal rises much slower than the thermal in the benchmark run, which reaches about 8.2 km. In the *θ*_{e} fields, large undershoots (i.e., anomalously low values, depicted by dashed contours in Fig. 6) develop in all cases.

Other useful conclusions can be drawn from these results. In particular, the *w* and *θ*_{e} fields from runs A and B are very similar. Both thermals rise to ∼6.9 km, and the vertical motion patterns are nearly identical. This result suggests that the extra effort required to conserve mass in a numerical model (by including the diabatic contribution to the pressure equation) may not lead to significant improvements in results unless total energy is also conserved (as in the benchmark). Despite the similarity of the *w* and *θ*_{e} fields, the time series of mass and energy errors are dramatically different (Fig. 7). The time series for run A (the short-dashed lines in Fig. 7) has an oscillatory nature, with a period of about 62 s. In contrast, the same time series for run B (dotted lines in Fig. 7) evolves smoothly, with only very minor changes through the simulations. Furthermore, run A loses considerable mass and energy throughout the simulation, with a total mass error that is about 30 times greater than the mass error in the benchmark simulation after 1000 s. Run B has nearly identical mass errors to the benchmark simulation, and has a slight increase in total energy. It is unclear how such dramatically different runs in terms of mass and energy errors can have such similar dynamic and thermodynamic fields (e.g., Figs. 5 and 6).

The results from run C were surprising. Among all the simulations, this run least resembles the benchmark case. The thermal only reached 5.8 km, and the vertical motion pattern is quite different from the other runs. However, it is interesting to note that mass and energy errors from run C are comparable to those in the benchmark simulation (Fig. 7). Apparently, this formulation produces unacceptable results due to an approximation that was made in only one equation, without making a consistent approximation in another equation. Perhaps a “counterbalancing” assumption in the pressure equation would improve the results. It is worthwhile to note that other equations sets make consistent approximations throughout, for example, in equation set B, the specific heats of water are ignored in every equation. On the other hand, equation set A ignores a term in the pressure equation, but does not make a counterbalancing approximation in any other equation, yet the results from equation set A are more acceptable than the results from equation set C. Whatever the reason behind the poor results of equation set C, this test highlights the danger of neglecting terms that may seem unimportant under a scale analysis.

The simulation that used *θ*_{il} as the governing variable (run D) produced *w* and *θ*_{e} fields that most closely match the benchmark result. The thermal reaches ∼7.6 km, and becomes only slightly distorted in shape. Although the results from the run D formulation are encouraging, this formulation has the largest total mass and total energy errors out of all runs presented here (Fig. 7). On the other hand, *θ*_{il} has other advantages that are not revealed by this test case. As discussed by Tripoli and Cotton (1981), *θ*_{il} is an appropriate variable to use in mixing terms for subgrid-scale turbulence closures. The test case that has been presented here does not include subgrid turbulent processes, nor is a constant background mixing coefficient added. Background mixing was avoided here in order to focus on the formulation of the governing equations, and to highlight the importance of mass and energy conservation in numerical models. It is possible that any disadvantages of *θ*_{il} that are revealed by this simulation are superceded by a more accurate representation of mixing processes.

Although the model used in this paper does not exactly conserve mass, momentum, or energy, the results strongly suggest that conservation of these basic variables can be necessary to obtain accurate results in some instances. This result supports the need to construct numerical models around conservation principles, which is the driving principle behind several recent model development efforts (e.g., Ooyama 2001; Skamarock et al. 2001; Satoh 2002).

The results of this section suggest that the form of the governing equations used in a numerical model may have a profound effect on the simulation of deep, moist convection. On the other hand, one might wonder whether these results only come about due to the unphysical initial environment that must be used to obtain the benchmark solution. Despite the unphysical aspects, this design is required in order for a benchmark solution to be obtained—without this setup, a “correct” solution would not be known, and it would be impossible to objectively evaluate the various model configurations.

Another potential criticism of the simulations presented in this section is the value chosen for *r*_{t}, which is abnormally high for the imposed temperature sounding. A comparison of simulations with different values for *θ*_{e} and *r*_{t} reveals that the differences presented here (Figs. 5 and 6) are accentuated over those one would expect to find in more “normal” environments. Nevertheless, it is clear that the mass-conserving and energy-conserving form of the thermodynamic and pressure equations can produce the desired results in all environments, and that these equations should be preferred over approximate equation sets.

We have conducted additional simulations using realistic initial environments (e.g., conditionally unstable and subsaturated initial conditions) to address whether the conclusions drawn from this paper hold for more typical uses of numerical models. We have simulated several forms of deep moist convection, including multicell thunderstorms, supercells, and squall lines using the three-dimensional numerical model with the various equation sets. For these simulations, the Kessler microphysics parameterization is used, hydrometeor fallout is allowed, and a complete subgrid turbulence model is included. Overall, results using the five equation sets are similar. In particular, convective organization is not modified in the any of the tests we have performed (e.g., all of the simulations with environments favoring supercells do produce supercells). However, some of the conclusions noted in this paper are evident in subtle ways. For example, the simulations with the mass- and energy-conserving equation set tends to have the strongest updrafts, the highest cloud tops, and the most rainfall. Simulations with the benchmark equation set tend to have about 10% more rainfall than simulations with equation set A. Based on these results, we have concluded that the form of the governing equations used in a numerical model does have an impact on the results, although perhaps a small impact for most uses.

### b. Numerics and assumptions

The moist benchmark simulation proposed here can also be used to test other components of the modeling system. For example, we tested whether saturation adjustment was necessary on the Runge–Kutta time steps. In one case, saturation adjustment was applied once, after the three Runge–Kutta steps were advanced with only dry processes. This simulation was compared to one in which saturation adjustment was applied during each of the three Runge–Kutta steps. The results were nearly identical. Since the former approach is considerably less expensive, we have decided to retain this method in our modeling system.

## 6. Summary and conclusions

A simulation has been designed to evaluate moist nonhydrostatic numerical models. The simulation shares many common characteristics with a dry benchmark simulation that has been used in previous studies. Given a statically stable initial environment, with an identical initial buoyancy perturbation, the moist simulation produces qualitatively similar results to the dry simulation, such as nearly identical structural details. Also, like the dry case, the moist simulation is virtually independent of the exact thermodynamic values of the initial state, provided the environment is neutrally stable. For these reasons, this experimental design is considered to be a benchmark that can be used to evaluate the design of moist nonhydrostatic numerical models.

Using this benchmark, it was shown how the formulation of governing equations can impact the evolution of a rising thermal. Some results obtained from these tests include:

Both mass-conserving

*and*energy-conserving equation sets were required to produce acceptable results.When using a common form of the thermodynamic equation, the inclusion of a mass-conserving pressure equation did not improve the result.

The neglect of one typically small term from the thermodynamic equation unexpectedly produced the worst results, highlighting the danger of using scale analysis to neglect terms from the governing equations.

The results of a simulation using ice–liquid water potential temperature (Tripoli and Cotton 1981) was closest to the benchmark solution, despite having the largest total mass and total energy errors.

The benchmark case is limited for several reasons, including neglect of physical and computational mixing, neglect of ice phase, neglect of hydrometeor fallout, and assumed reversibility of phase changes. Despite these limitations, we have found this case to be extremely useful for evaluating the accuracy and efficiency of numerical techniques and assumptions in a numerical model with moisture.

## Acknowledgments

We greatly appreciate the insight provided by Dave Stauffer and Richard James. All figures were created using the Grid Analysis and Display System (GrADS). This work was supported by NSF Grant ATM 9806309.

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## APPENDIX

### Definition of Constants and Thermodynamic Variables Not Defined in the Text

Variable Description Value or definition

*c*_{p}Specific heat of dry air at constant pressure 1004 J kg^{−1}K^{−1}*c*_{pl}Specific heat of liquid water at constant pressure 4186 J kg^{−1}K^{−1}*c*_{pml}Specific heat of moist air at constant pressure*c*_{pml}=*c*_{p}+*c*_{pv}*r*_{υ}+*c*_{pl}*r*_{l}*c*_{pv}Specific heat of water vapor at constant pressure 1885 J kg^{−1}K^{−1}*c*_{υ}Specific heat of dry air at constant volume 717 J kg^{−1}K^{−1}*c*_{vml}Specific heat of moist air at constant volume*c*_{vml}=*c*_{υ}+*c*_{vv}*r*_{υ}+*c*_{pl}*r*_{l}*c*_{vv}Specific heat of water vapor at constant volume 1424 J kg^{−1}K^{−1}*g*Acceleration due to gravity 9.81 m s^{−2}*L*_{υ}Latent heat of vaporization*L*_{υ}=*L*_{υ0}− (*c*_{pl}−*c*_{pv}) (*T*−*T*_{0})*L*_{υ0}Reference value of*L*_{υ}2.5 × 10^{6}J kg^{−1}*r*_{l}Liquid water mixing ratio*r*_{l}=*r*_{c}in this work*R*Gas constant of dry air 287 J kg^{−1}K^{−1}*R*_{m}Gas constant of moist air*R*_{m}=*R*+*R*_{υ}*r*_{υ}*R*_{υ}Gas constant of water vapor 461 J kg^{−1}K^{−1}*T*_{0}Reference temperature 273.15 Kε Ratio of

*R*to*R*_{υ}ε =*R*/*R*_{υ}

Summary of thermodynamic and pressure equations