Introduction
The thermal performance of a home in the House_e module is based on a simple thermal heat flow circuit, shown in Figure 1. Here, the complexity of much more detailed thermal models, as used in most building simulations, is reduced to an equivalent thermal parameter (ETP) model in which parallel or nearly parallel heat flow paths and series thermal mass elements are lumped into a few parameters and portrayed as a simple DC electric circuit. This reduces the number of details of the building design that must be specified by the user of House_e , greatly reduces memory requirements, and speeds execution (all critical when simulating populations of buildings, especially relevant where the thermal details of the population are somewhat uncertain in any event).
In the laws of physics, temperatures, conductances, thermal masses and heat flows are entirely equivalent to voltages, conductances, capacitors and current flows in the electric circuit analog. That is, the differential equations expressing conservation for energy are the same. In practice, when applied to represent heat flow in a building, this circuit is always overdamped. That is, it exhibits exponential decays and approaches toward steadystate (not oscillatory) conditions.
The ETP circuit captures the essence of the response of the home under most circumstances of importance to analysis of a smart grid: heat gains and losses and the effects of thermal mass, as a function of weather (temperature and solar radiation), occupant behavior (thermostat settings and internal heat gains from appliances), and heating/cooling system efficiencies. How these are modeled using this framework is explained in this document.
In its essence, the thermal envelope of the home has a conductance ([math]U_A[/math]) through which heat flows from the room air temperature ([math]T_A[/math]) to the outdoor air temperature ([math]T_O[/math]). The [math]U_A[/math] is the sum of all parallel heat flow paths through the envelope of the building (walls, windows, doors, ceilings, floors, and infiltration air flows). The primary simplifying assumption here is that the masses of these elements of the building envelope are relatively insignificant compared to their conductances, so their masses can be lumped inside the home.
The bulk of the mass in the home is summed to form the lumped mass [math]C_M[/math], which is coupled to the room air through a conductance that represents the sum of the products of the mass surface area and the heat transfer coefficient. The mass of the air in the interior volume of the house is represented by the much smaller mass [math]C_A[/math], which is directly couple to the room air. The primary effect of [math]C_A[/math] is to realistically dampen the effect of heat delivered to the air ([math]Q_A[/math]) from the heating/cooling (HVAC) system turning on and off, which would otherwise result in an instantaneous change in room air temperature.
Heat gains from solar radiation and from appliances are combined with that from the heating/cooling system to form the heat gains to the air, [math]Q_A[/math]. The House_e model allows a specified fraction for each of the heat gains from heating/cooling, solar radiation, and internal appliances to allow them to bypass the air node and be delivered directly to the mass to form [math]Q_M[/math]. This can be used to represent solid interior objects absorbing heat from solar radiation shining through windows, for example. This is a reasonable approximation for the wood frame construction predominant in U.S. homes. It becomes an increasingly poor assumption for buildings with massive masonry or brick exterior. Future versions of GridLabD will have the capability to model these effects explicitly with a modified approach.
Finally, a timeseries solution of the ETP circuit must be solved, with a thermostat controlling the HVAC system to maintain heating and cooling setpoints specified by the occupants. This requires modeling the output of the HVAC system, and the electric input to it, as a function of the type, capacity, and efficiency of the equipment under varying conditions such as the outdoor temperature.
The details of how these are modeled from userspecified inputs are described in the sections that follow.
Envelope
Solution to the ETP Heat Balance Equations
For the thermal circuit in Figure 1, a heat balance (conservation of energy) can be written for the air temperature node ([math]T_A[/math]) as:
 [math]Q_A  U_A (T_AT_O)  H_M (T_AT_M)  C_A \frac{dT_A}{dt} = 0 \qquad\qquad(1)[/math]
The heat balance for the mass temperature node ([math]T_M[/math]) can be written as:
 [math]Q_M  H_M (T_MT_A)  C_M \frac{dT_M}{dt} = 0\qquad\qquad(2)[/math]
As shown in ETP closed form solution, Equation (1) can be solved for [math]T_M[/math], differentiated with respect to time to provide [math]dT_M/dt[/math], and both of these substituted into (2) to form a second order linear differential equation in [math]T_A[/math] of the form
 [math]a \frac{d^2T_A}{dt^2} + b \frac{dT_A}{dt} + c\ T_A = d\qquad\qquad(3)[/math]
where:
 [math]a = \frac{C_M C_A}{H_M}[/math]
 [math]b = \frac{C_M (U_A + H_M)}{H_M} + C_A[/math]
 [math]c = U_A \![/math]
 [math]d = Q_M + Q_A + U_A T_O \![/math]
which has the solution with known, constant boundary conditions [math]T_O[/math], [math]Q_A[/math], and [math]Q_M[/math] and initial conditions at time [math]t=0[/math] of [math]T_{A_o}[/math] and [math]dT_{A_o}/dt[/math]
 [math]T_A = A_1 e^{r_1 t} + A_2 e^{r_2 t} + \frac{d}{c}\qquad\qquad(4)[/math]
where:
 [math]r_1 = \frac{b + \sqrt{b^24ac}}{2a}[/math]
 [math]r_2 = \frac{b  \sqrt{b^24ac}}{2a}[/math]
 [math]A_1 = \frac{r_2 T_{A_o}  \frac{dT_{A_o}}{dt}  r_2 \frac{d}{c}}{( r_2  r_1 )}[/math]
 [math]A_2 = T_{A_o}  \frac{d}{c}  \frac{r_2 T_{A_o}  \frac{dT_{A_o}}{dt}  r_2 \frac{d}{c}}{( r_2  r_1 )}[/math]
The initial condition [math]T_{A_o}[/math] is known as the final condition of [math]T_A[/math] from previous time step. However, at any time step at which the boundary conditions [math]T_O[/math], [math]Q_A[/math], or [math]Q_M[/math] have changed (i.e. the weather, internal gains, heating/cooling output) from the previous time interval, then the new air temperature trajectory at the beginning of the time step can be derived from Equation (1) as
 [math]\frac{dT_{A_o}}{dt} = \frac{H_M}{C_A T_{M_o}}  \frac{U_A + H_M}{C_A T_{A_o}} + \frac{U_A}{C_A T_O} + \frac{Q_A}{C_A}\qquad\qquad(5)[/math]
Then, differentiating Equation (4) and substituting it and Equation (4) into Equation (1) yields a solution for [math]T_M[/math] of the form:
 [math]T_M = A_1 A_3 e^{r_1 t} + A_2 A_4 e^{r_2 t} + g + \frac{d}{c}\qquad\qquad(6)[/math]
where:
 [math]g = \frac{Q_M}{H_M}[/math]
 [math]A_3 = \frac{r_1 C_A}{H_M} + \frac{U_A + H_M}{H_M}[/math]
 [math]A_3 = \frac{r_2 C_A}{H_M} + \frac{U_A + H_M}{H_M}[/math]
Initial Room and Mass Air Temperature
When initializing a House_E simulation, the temperature and weather history prior to the first time step is unknown. First assume the house is at the equilibrium air temperature (at steady state with the heating and cooling system off, i.e. in balance). Equilibrium is defined by [math]dT_A/dt_o = 0[/math]. Then, by differentiating (4), at the beginning of the initial time step, it can be shown that
 [math]T_{A_{eq}} = \frac{d}{c} = T_O + \frac{Q_M + Q_A}{U_A}\qquad\qquad(7)[/math]
and the corresponding mass temperature at equilibrium is
 [math]T_{M_{eq}} = T_{A_{eq}} + \frac{Q_M}{H_M}\qquad\qquad(8)[/math]
If the heating system would be “on” (based on the thermostat heating set point; see the section Heating/Cooling Thermostat Operations) at the condition [math]T_A = T_{A_{eq}}[/math], then the initial conditions are best approximated as
 [math]T_{A_o} = T_{M_o} = T_{set\ heat}\qquad\qquad(9)[/math] # Heating system “on” at [math]T_A = T_{A_{eq}}[/math]
If the cooling system would be “on” (based on the thermostat cooling set point) at the condition [math]T_A = T_{A_{eq}}[/math], then the initial conditions are best approximated as
 [math]T_{A_o} = T_{M_o} = T_{set\ cool}\qquad\qquad(10)[/math] # Cooling system “on” at [math]T_A = T_{A_{eq}}[/math]
The time of day when either of these approximate initial conditions is most correct is when the conditions in the house have been stable for a long period of time. So, starting the simulation at midnight may be a good choice. An often better choice would be the earlier of sunrise or just prior to a morning thermostat change.
If neither the heating or cooling system would be “on” at the condition [math]T_A = T_{A_{eq}}[/math], then the initial conditions are best approximated as
 [math]T_{A_o} = T_{A_{eq}}\qquad\qquad(11)[/math] # Heating/cooling system “off” at [math]T_A = T_{A_{eq}}[/math]
 [math]T_{M_o} = T_{M_{eq}}\qquad\qquad(12)[/math]
Predicting the Time of the Next Heating/Cooling State Change
[TODO]
Primary Inputs
Parameter (symbol; selections)  Default Value 

Floor area (A)  2,500 ft² 
Floor aspect ratio (R)  1.5  
No. Stories (n)  1  
Ceiling height (h)  8 ft 
Exterior ceiling, fraction of total (ECR)  100% 
Exterior floor, fraction of total (EFR)  100% 
Exterior wall, fraction of total (EWR)  100% 
Window/exterior wall area ratio (WWR)  7% 
Doors ([math]n_d[/math]) 4   
Area of 1 door ([math]A_1d[/math])  19.5 ft² 
Glazing layers (GL; 1, 2, 3,integer)  2 
Glazing material (GM; glass, lowe glass)  lowe glass 
Window frame (WF; none,aluminium, thermal break,wood,insulated)  TB 
Glazing treatment (GT; clear, abs, refl, lows, highs)  clear 
Window, exterior transmission coefficient (WET) For exterior shading effects None=1.0, insect screen=0.6 (ASHRAE) 
60% 
Rvalue, walls ([math]R_w[/math])  19 °F.ft².hr/Btu 
Rvalue, ceilings ([math]R_c[/math])  30 °F.ft².hr/Btu 
Rvalue, floors ([math]R_f[/math])  22 °F.ft².hr/Btu 
Rvalue, doors ([math]R_d[/math])  5 °F.ft².hr/Btu 
Infiltration volumetric air exchange rate (I)  0.5 1/hr 
Interior/exterior wall surface ratio (IWR) Based partitions for six rooms per floor 
1.5  
Interior surface heat transfer coefficient ([math]h_s[/math])  1.46 Btu/hr.°F.ft² 
Total thermal mass, per unit floor area ([math]m_f[/math]) Rule of thumb (Pratt), residential woodframe construction: 2 Btu/°F/ft² including furnishings 
2.0 Btu/°F.ft² 
Interior surface thermal mass, subtotal Typical wood frame residential (Pratt), excludes furnishings 
1.5 Btu/°F.ft² 
Solar gain fraction to mass ([math]f_s[/math])  50% 
Internal gain fraction to mass ([math]f_i[/math])  50% 
HVAC delivered fraction to mass ([math]f_m[/math])  0% 
Include solar quadrant (none, H(horizontal), N(north), S(south), E(east), W(west))  N,S,E,W 
Derived Defaults
Glazing
Translate glazing material into glazing material type (gmt) for Uvalue with a lookup table
 IF( OR(GM="glass", GM="lowe glass"), IF(GM="glass", gmt="G", gmt="L"), “Error: unrecognized glazing material" )
Based on Type = GL & gmt, and on WF, lookup the window Uvalue ([math]U_g[/math]) in Table 1 (produces the default Window Uvalue = 0.47 Btu/hroFft2)
Table 1. Window UValues as a Function of Window Characteristics
Window Uvalues, AHSRAE Handbook 2005, Table 29.2, Operable  

Type  Layers  Glazing  Uvalue (Btu / hr.°F.ft²) by Frame Type  
None  Aluminum  Tb  Wood  In  
1G  1  Glass  1.04  1.27  1.08  0.90  0.81 
2G  2  Glass  0.48  0.81  0.60  0.53  0.44 
2L  2  Lowe glass  0.30  0.67  0.47  0.41  0.33 
3G  3  Glass  0.31  0.67  0.46  0.40  0.34 
3L  3  Lowe glass  0.27  0.64  0.43  0.37  0.31 
Translate window frame into window frame type (wft) for Solar Heat Gain Coefficient (SHGC) lookup table
 IF( OR(WF="AL", WF="TB"), wft="AL/TB", IF( OR(WF="WD", WF="IN"), wft="WD/IN", IF(WF="none", wft="none", "Error: unrecognized window frame") ) )
Based on Type = GL & GT, and on wft, lookup the nominal window SHGC in the Table 2: (produces the default Window Nominal SHGC = 0.67)
Table 2. Window Solar Heat Gain Coefficients as a Function of Window Characteristics>
Window SHGCs, AHSRAE Handbook 2005, Table 29.2, Operable  

Type  Layers  Glazing Treatment 
SHGC by Frame Type  
None  Aluminum/Tb  Wood/In  
1clear  1  Clear  0.86  0.75  0.64 
1abs  1  Heatabsorbing  0.73  0.64  0.54 
1refl  1  Reflective  0.31  0.28  0.24 
2clear  2  Clear  0.76  0.67  0.57 
2abs  2  Heatabsorbing  0.62  0.55  0.46 
2refl  2  Reflective  0.29  0.27  0.22 
2lows  2  Lowsolar  0.41  0.37  0.31 
2highs  2  Highsolar  0.70  0.62  0.52 
3clear  3  Clear  0.68  0.60  0.51 
3abs  3  Heatabsorbing  0.34  0.31  0.26 
3refl  3  Reflective  0.34  0.31  0.26 
3lows  3  Lowsolar  0.27  0.25  0.21 
3highs  3  Highsolar  0.62  0.55  0.46 
 (a) lowe only
The SHGC is the product of the nominal SHGC and the window exterior transmission coefficient
 [math]SHGC = SHGC_{nom}\ WET\ A_g[/math] # See next section for derivation of [math]A_g[/math] (area of glazing)
Thermal Integrity Table Inputs and Defaults
For the convenience of the user in describing a population of buildings, we allow the thermal properties of the envelope construction to be entered as a table. This is useful because the insulation level of ceilings, walls, floors, and windows tend to be highly correlated, rather than independent, because of construction practices and/or building codes that are a function of the vintage of construction. That is, it is extremely unlikely to find a house with heavily insulated walls, but to ceiling insulation.
So, the user is allowed to enter the following primary inputs as a table, of the form shown in Table 3, with defaults as shown.
Table 3. Thermal Integrity Table
Default Thermal Integrity by Component  

Integrity Level 
Description  Ceilings °F.ft².hr/Btu 
Walls °F.ft².hr/Btu 
Floors °F.ft².hr/Btu 
Windows °F.ft².hr/Btu 
Doors °F.ft².hr/Btu 
Infiltration Air Exchange Rate (1/hr)  
Layers  Glazing  Treatment  Frame  
0  old, uninsulated  11  4  4  1  Glass  Clear  Al  3  1.5 
1  old, insulated  19  11  4  2  Glass  Clear  Al  3  1.5 
2  old, weatherized  19  11  11  2  Glass  Clear  Al  3  1.0 
3  old, retrofit upgraded  30  11  19  2  Glass  Clear  Tb  3  1.0 
4  moderately insulated  30  19  11  2  Glass  Clear  Tb  3  1.0 
5  very well insulated  30  19  22  2  Lowe glass  Clear  Tb  5  0.5 
6  extremely well insulated  48  22  30  3  Lowe glass  Heatabsorbing  In  11  0.5 
To override the defaults, the user defines a thermal integrity table defining the following primary inputs (see the Primary Inputs section above), in the following order:
Paramater (symbol)  Selections  Units 

Integrity level  (integer value)   
Rvalue, ceilings ([math]R_c[/math])  (value)  °F.ft².hr/Btu 
Rvalue, walls ([math]R_w[/math])  (value)  °F.ft².hr/Btu 
Rvalue, floors ([math]R_f[/math])  (value)  °F.ft².hr/Btu 
Glazing layers (GL)  (integer value: 1, 2, 3)   
Glazing material (GM)  (glass, lowe glass)   
Window frame (WF)  (none,aluminium,thermal break,wood,insulated)   
Rvalue, doors ([math]R_d[/math])  (value)  °F.ft².hr/Btu 
Infiltration volumetric air exchange rate (I)  (value)  1/hr 
 Note: Any set of (columnwise) values in an integrity table will be overridden by entry of a primary input.
Heat Loss Coefficient ([math]U_A[/math])
Compute exterior surface areas:
 Define the following, based on rectangular geometry. Let x = width, y = depth.
 Then the aspect ratio is [math]R = y / x[/math]
 The floor area is [math]A = x y n[/math]
 and the volume is [math]V = A h[/math]
The gross exterior wall area ([math]A_{wt}[/math]) can be derived by introducing the perimeter (p), as follows:
 [math]y\ x = A / n[/math]
 [math]y = R\ x[/math]
 [math]R\ x^2 = A / n[/math]
 [math]x^2 = \frac{A}{n R}[/math]
 [math]x = \sqrt{\frac{A}{nR}}[/math]
 [math]p\ = 2x + 2y = 2x + 2Rx = 2x (1 + R)[/math]
 [math]p\ = 2 (1 + R)\sqrt{\frac{A}{nR}} [/math]
 [math]A_{wt} = n\ h\ p [/math]
Then
[math]A_{wt} = 2 n h (1 + R) \sqrt{\frac{A}{nR}} [/math]  The gross exterior wall area ([math]A_{wt}[/math])  
[math]A_g = WWR\ A_{wt}\ EWR[/math]  The gross window area ([math]A_g[/math])  
[math]A_d = n_d\ A_{1d}[/math]  The total door area ([math]A_d[/math])  
[math]A_w = (A_{wt}(A_g + A_d))\ EWR[/math]  The net exterior wall area ([math]A_w[/math])  
[math]A_c = \frac{A}{n} ECR[/math]  The net exterior ceiling area ([math]A_c[/math])  
[math]A_f = \frac{A}{n} EFR[/math]  The net exterior floor area ([math]A_f[/math]) 
The total heat loss coefficient (conductance), [math]U_A[/math], for the house (the last term is for air infiltration); the defaults produce [math]U_A[/math] = 522.1 Btu/°F.hr
 [math]U_A = A_g U_g + \frac{A_d}{R_d} + \frac{A_w}{R_w} + \frac{A_c}{R_c} + \frac{A_f}{R_f} + 0.018 A h I [/math]
 Note: 0.018 is the volumetric heat capacity of air at standard conditions (Btu/°F.ft³stdairpressure)
Interior Mass Surface Conductance ([math]H_m[/math])
Surface area is estimates as total exterior walls (less doors and windows) + interior walls + ceilings
 [math]H_m = h_s\ (\frac{A_w}{EWR}) + A_{wt} IWR + \frac{A_c n}{ECR}[/math]
Total “Air” Mass ([math]C_a[/math])
Based on tuning to typical home heating system cycling times, the “air mass” seems to be well approximated as 3 times the volumetric capacitance of the interior air volume.
 [math]C_a = 3\ (0.018 A\ h)[/math] # Shortcycle thermal mass
Total Thermal Mass ([math]C_m[/math])
 [math]C_m = A\ m_f  2\ (0.018 A\ h)[/math] # Thermal mass (daily cycle), less that added to the “air” mass
HVAC Systems
Primary Inputs
Parameter (symbol; selections)  Default Value  

Heat system type (gas, heat pump, resistance, none)  heat pump   
Cool system type (electric, none)  none   
Cooling COP, standard conditions^{e}  3.50   
Heating COP, standard conditions^{a}  3.50   
Latent cooling, fraction, of sensible cooling  35%   
Thermostat set point, heat (Tset_heat; value, or a schedule)^{b}  70  °F 
Thermostat set point, cool (Tset_cool; value, or a schedule)^{c}  75  °F 
Thermostat deadband (dTdeadband)^{d}  2.0  °F 
Thermostat cycle time, minimum (tmin)  2.0  min 
Auxiliary heat (electric, none)^{e}  electric   
Auxiliary heat deadband (dTaux; value, none)^{e,f,g}  2.0  °F 
Auxiliary heat outdoor lockout temperature (Taux; value, none)^{e,h}  none  °F 
Auxiliary heat time delay (taux)^{e,h}  none  min 
Fan type (1speed, 2speed, none)^{h,i}  1speed   
Fan power, lowspeed, fraction of hispeed^{j}  %   
Heating COP curve (default, flat, linear, curved)  default   
Cooling COP curve (default, flat, linear, curved)  default   
Heating capacity curve (default, flat, linear, curved)  default   
Cooling capacity curve (default, flat, linear, curved)  default   
Use latent heat (true, false)  true   
Include fan heat gain (true, false)  true   
^{a} For resistance heat system type, the default COP is 1.0 and not settable by the user.  
^{b} Applicable to all heat system types, other than none.  
^{c} Applicable to electric cool system type only.  
^{d} Temperature range of a thermostat from "on" to "off" (centered on thermostat setpoint). To prevent simultaneous heating and cooling, throw a
warning if T_{set_cool}  T_{set_heat} < dT_{deadband}  
^{e} Applicable to heat pump heat system type only.  
^{f} Applicable to heat pump heat system type with electric auxiliary heat only.  
^{g} To control auxiliary heat, at least one of [math]dT_{aux}[/math], [math]T_{aux on}[/math] and [math]t_{aux}[/math] must be given a value; otherwise throw a warning.  
^{h} Cool system type electric and heat system types heat pump and gas require a 1speed or 2speed fan, so none is not a valid selection in cases.  
^{i} 1speed or 2speed indicates a forced air system. 1speed fan is off when heating and cooling are off. 2speed fan operates continually at low power when heating and cooling are off.  
^{j} Applicable to 2speed fan types only. 
How to Specify Common HVAC Systems
The types of equipment that form a residential heating/ventilating/air conditioning (HVAC)system is defined in House_e by the input parameters Heat_system_type, the Cool_system_type, and the Fan_type.
Air Conditioning (Cooling)
House_e only supports electricallypowered forcedair vaporcompression cooling, which can represent either a central air conditioner or a window/wall unit that cycles on and off to maintain the air temperature below the cooling thermostat setpoint. This is defined as an electric Cool_system_type. If no air conditioning is provided, input none for this parameter.
An air conditioner uses an electricallypowered refrigerant pump to move heat from the cooled space and reject it outdoors. Hence, it can remove more heat from the house than the electricity input to the pump, and the COP is thus typically much greater than 1.0 (conservation of energy requires that the heat rejected outdoors is equal to the heat removed from the house plus the energy input to the pump).
The laws of thermodynamics governing the vaporcompression cycle show that the COP decreases as the outdoor temperature increases, because of the increased difficulty of rejecting the heat outdoors. House_e models this phenomena. Similarly, the COP decreases as the supply air temperature decreases, and as the temperature and humidity of the air from the house increase, but these variations are assumed to be relatively small and House_e does not model them.
Default values for the other input parameters are characteristic of a central air conditioner or heat pump. Window/wall air conditioners generally are less efficient, so the Cooling COP under standard conditions is likely to be lower than the default value. A house may utilize multiple window/wall air conditioners in different locations, each with its own thermostat. House_e simulates them together as a single equivalent unit controlled by a single thermostat. It is not uncommon for these units to be too small to keep a house at the cooling setpoint during very hot weather. If this is the case, the user can specify a negative oversizing factor (see the next section, Design Loads and HVAC System Sizing)
Heating
House_e supports a variety of heating system types:
 The absence of a heating system is indicated by a Heat_system_type parameter of value none.
 In a resistance Heat_system_type, heat is provided by an electric resistance heating coil (either in a forcedair furnace, or electric baseboard radiators) that cycles on and off to try to maintain the air temperature above the heating thermostat setpoint. The COP of a resistance heating system is a constant 1.0, being unaffected by the outdoor air temperature. The capacity is likewise unaffected.
 In a gas Heat_system_type, heat is provided by a gaspowered furnace or a boiler that cycles on and off to try to maintain the air temperature above the heating thermostat setpoint, but places no load on the electricity distribution system (except for its fan; see the next section). Its capacity is a constant unaffected by the outdoor air temperature. This can be used to model heating systems supplied by natural gas, propane, wood/biomass, and other nonelectric sources.
 In a heat pump heat_system_type, heat is provided by a heat pump that is a reversible vapor compression cycle, i.e. and air conditioner running in "reverse" that pumps heat from outdoors and rejects it indoors. It cycles on and off to try to maintain the air temperature above the heating thermostat setpoint, but places no load on the electricity distribution system( excpet for its fan; see the next section). Its capacity is a constant unaffected by the outdoor air temperature.
Like an air conditioner, a heat pump's heating COP is not a constant, but instead decreases as the outdoor temperature decreases, because of the increased difficulty of pumping heat from outdoors. House_e models this phenomena. Similarly, the COP and capacity decrease as the supply air temperature increases and as the temperature of the air from the house increases, but these variations are assumed to be relatively small and House_e does not model them.
Auxiliary heating(For Heat Pumps Only)
An auxiliary heating system can be specified for a heat pump Heat_system_type by providing a value of electric for the input parameter Auxiliary_heat. A heat pump is generally sized to meet the peak cooling requirement, and its heating capacity under standard conditions is generally equal to its cooling capacity. Given its reduced output at very cold outdoor temperatures, it may not have enough capacity to maintain the house at the desired heating setpoint. An auxiliary heat system serves this function. A value of none for the Auxilairy_heat parameter indicates no such auxiliary heat is provided.
If auxiliary heat is specified (the default), then a control strategy for it must also be specified. Three types of control can be modeled by House_e. Atleast one must be specified; two or all three can be specified to work in combination. Each auxiliary heat control strategy can call for auxiliary heat to turn on and the heat pump heating cycle to turn off. The auxiliary heat control strategies supported by House_e are:
 If a value is provided for the Auxiliary_heat_deadband input parameter, then the auxiliary heat comes "on" when the indoor air temperature drops by more than the value below the heating setpoint and remains "on" until the thermostat is satisfied (i.e., when the heating system would normally go "off"). This is the default control strategy (value=2°F) and the most common one in usage in the U.S in the decades 19802010. The problem with it is that if the thermostat is set back at night , it will trigger auxiliary heat when the thermostat is set up in the morning, even under relatively warm conditions.
 If a value is provided for the Auxiliary_heat_lockout_temperature input parameter, then the auxiliary heat comes "on" whenever the thermostat calls for heating and the outdoor air temperature is below value. It remains "on" until the thermostat is satisfied (i.e.,when the heating system would normally go "off"). The default value = none. This is an older control strategy particularly common to early heat pump systems in the U.S.
(NOTE: If used, this parameter should be diversified to represent a realistic range of values in the population by using a distribution as the input. Otherwise an entire population of homes will shift to auxilairy heat at the same time in a GridLABD simulation)
 If a value is provided for the Auxiliary_time_delay input parameter, then the auxiliary heat comes "on" whenever the heating system has been "on" for more than value minutes but the heating thermostat remains unsatisfied. The auxilairy heat remains "on" until the thermostat is satisfied (i.e.,when the heating system would normally go "off"). The default value is none. This is the most advanced control strategy and is designed to minimize auxiliary heating by giving the heat pump a chance to satisfy the heating requirement before turning to auxiliary heat.
Circulation Fan
Air conditioners and heat pumps require a fan to be specified (Fan_type parameter equal to /speed or 2speed). For resistance heating systems without an air conditioning, a fan is optional. If fan_type is none, then the heating system is implicitly a baseboard/radiator system. otherwise 9and by default) a fan is assumed to be present, and will be sized to meet the larger of the heating or cooling air flow rate required to meet the heating and cooling design loads, respectively.
A 1speed Fan_type is "on" when the cooling, heating, or auxiliary heating system is "on". This is the default, and the most common case in the u.S.
The heat from the power to the fan is added to the output of the HVAC system, and the power is add to the electrical load placed by the HVAC system on the electric distribution system.
A 2speed Fan_type is "on" continually, at full speed when the cooling, heating, or auxiliary heating system is "on", and at low speed to circulate air when the cooling,heating, and auxiliary heating system are each "off" or not present. At low speed, the power of the fan is reduced by the factor of the input parameter Fan_power_low_speed_fraction_of_high_speed. Note that fan power is generally proportional to the square of the flow rate; if the air flow is 50% at lowspeed, then the power at low speed is (50%)^{2} , i.e. 25%.
Example HVAC System Specification
[TO DO]
Design Loads and HVAC System Sizing
User Inputs (and Defaults)
Parameter  Default Value  Units 

Design indoor temperature, heating  70  °F 
Design indoor temperature, cooling  75  °F 
Design outdoor temperature, heating  (^{a})  °F 
Design outdoor temperature, cooling  (^{b})  °F 
Design solar radiation  195^{c}  Btu/hr.ft^{2} 
Design internal gains  (^{d})  Btu/hr 
Oversizing factor  0%   
Cooling supply air temperature  50  °F 
Heating supply air temperature  150  °F 
Duct pressure drop  [math]\frac{1}{2}[/math]  in. water 
^{a} If a weather file is provided, the default is the minimum hourly outdoor temperature in the weather file. If no file provided, then the default is 0°F.  
^{b} If a weather file is provided, the default is the maximum hourly outdoor temperature in the weather file. If no file provided, then the default is 95°F.  
^{c} Typical clear day incident radiation for 35° latitiude and equal window areas in each of the eight cardinal directions (N, NE/NW, E/W, SE/SW, and S respectively) is 1/8 * (60+2*201+2*261+2*213+153) = 195 Btu/hr.ft^{2}. (ASHRAE Handbook of Fundamentals, 2005).  
^{d} A function of floor area (see next section Design Internal Gains): 167.09*(floor_area)^{0.442} 
Design Internal Gains
The design internal gains as a function of floor area are approximated as a regression against mean annual ELCAP consumption data for the “Other” end use by floor area categories, as follows (from spreadsheets ELCAP Load Shapes_Q3.xls and Internal Gains Default.xls):
Table 4. Regression of ELCAP “Other” Annual End Use Load vs. Floor Area
End Use  Size of Home (ft^{2})  Regression: ln(Other) = ln(a) + b ln(x)  
850  1350  2100  2475  Parameter  Value  Std. Error  
Other  6730  7298  9066  11079  ln(a)  5.7834  0.8017 
ln( End Use )  ln( Size of Home (ft^{2}) )  b  0.4420  0.1088  
6.745  7.208  7.650  7.814  r2  0.8918  
ln( Other )  8.814  8.895  9.112  9.313  a  324.9  45.0 
Predicted End Use  Size of Home (ft^{2})  EU = a x^{b}  
850  1350  2100  2475  ln(EU) = ln(a) + ln(x^{b}  
Other  6403  7856  9550  10269  ln(EU) = ln(a) + b ln(x) 
For the “Other” end use (excludes heating and water heating) in the ELCAP metered end use data project, the results of a linear regression of the average annual energy consumption as a function of floor area of the form Other = a x^{b} can be converted by an axis transformation into a linear regression of the form
 [math]log_e (kWh/yr) = log_e(a) + b\ log_e(floor area, ft^2)[/math]
with the resulting coefficients a and b shown in the table above.
Also from ELCAP, the ratio of 1) the maximum hourly load of the summer average load shape to 2) the mean hourly load for the year is 1.32 (hour 18). Combined with the regression results, and converting the units from kWh/yr to Btu/hr, the design internal gains as a function of floor area is
 Design_internal_gains = 324.9 * (floor_area)^{0.442} * 1.32 * 3413 / 8760
Sizing Calculations
This section describes how sensibly sized HVAC units are created.
 Design heating load (Btu/hr) = UA * (Design indoor temperature heating – Design outdoor temperature heating)
 Design sensible cooling load (Btu/hr) = UA * (Design outdoor temperature cooling  Design indoor temperature cooling) + Design internal gains * 3.413 (Btu/hrkW) +
Design solar_radiation * Ag * SHGC * WET
 Design total cooling load (Btu/hr) = Design_sensible_cooling load * (1 + Latent_cooling_fraction)
For cool system types other than none, the design cooling capacity is nearest 6,000 Btu/hr increment above design cooling load (otherwise the Design_cooling_capacity = 0)
 Design_cooling_capacity (Btu/hr) = Round( (Design_total_cooling_load * (1 + Oversizing_ factor) + 3000) / 6000 ) * 6000
Other than for heat pumps, the design heating capacity is nearest 10,000 Btu/hr increment above design heating load (otherwise the Design_heating_capacity (Btu/hr) = 0)
 Design_heating_capacity (Btu/hr) = Round( (Design_heating_load * (1 + Oversizing_factor) + 5000) / 10000 ) * 10000 # Heat system types other than heat pump
For heat pumps (only), a rule of thumb is that the heating capacity is equal to the cooling capacity, and the auxiliary heating capacity is equal to the
 Design_heating_capacity (Btu/hr) = Design_cooling_capacity # heat pump Heat system type only
For heat pump Heat system types with electric auxiliary heat only:
 Auxiliary_capacity (Btu/hr) = Round( (Design_heating_load * (1 + Oversizing_factor) + 5000) / 10000 ) * 10000 # heat pump Heat system type only
For all other cases, the Auxiliary capacity = 0.
For Fan types other than none and Heat system types other than none, determine the volumetric flow rate of air at standard conditions and 150 °F to deliver the greater of the Design_heating_capacity and the Auxiliary_capacity:
 Design_heating_airflow = Max(Design_heating_capacity and the Auxiliary_capacity)/( 0.018 * (Design_heating_supply_temperature  Design_indoor_temperature_heating))/ 60
For Cool system types other than none, size a fan to deliver a sufficient volume of air at 50 °F to deliver the Design_cooling _cfm:
 Design_cooling_airflow = Design_cooling_capacity /(1 + Latent_fraction)/(0.018 * (Design_indoor_temperature_cooling  Design_cooling_supply_temperature)/60
The power input to the fan is based on the greater of the Design_cooling_airflow and the Design_heating_airflow, assuming a ½ in. of water pressure drop, a 42% efficient fan, and an 88% efficient motor sized to the nearest 1/8 HP (for Fan type none, Fan power = 0)
 Fan_power = Round(0.117 * Duct_pressure_drop * Max(Design_cooling_airflow, Design_heating_airflow)/[math]\frac {0.42}{745.7} + \frac {1}{16})/ \frac{1}{8}))*\frac{1}{8} * \frac{745.7}{0.88}[/math]
Heating/Cooling Thermostat Operations
For convenience, define a set of HVAC functionality indicators, F, which define the capabilities of the HVAC system and whether they are enabled at a given time:
 F_{cool} = Boolean(Cool_system_type = electric & cooling system is enabled )
 F_{heat} = Boolean(Heat_system_type [math]\neq[/math] none & heating system is enabled)
 F_{aux} = Boolean(Heat_system_type = heat pump & Auxiliary_heat = electric & heating system is enabled )
 F_{fan} = Boolean(Fan type[math]\neq[/math]none)
Also define a set of state variables:
 Cool_{on} = Boolean(Cooling system is “on” )
 Cool_{off} = Boolean(Cooling system is “off” )=[math]1\text{Cool}_\text{on}[/math]
 Heat_{on} = Boolean(Cooling system is “on” )
 Heat_{off} = Boolean( Heating system is “off” )=[math]1\text{Heat}_\text{on}[/math]
For heat pumps with electric auxiliary heat, define additional functionality indicators and state variables:
 F_{aux_deadband} = Boolean(F_{aux} & [math]dT_\text{aux}\neq[/math]none)
 F_{aux_lockout}=Boolean(F_{aux} & T_{aux_on}[math]\neq[/math]none)
 F_{aux_delay}=Boolean(F_{aux} & t_{aux_on} [math]\neq[/math]none )
 Aux_{on} = Boolean( Auxiliary heat is “on” )
 Aux_{off} = Boolean(Auxiliary heat is “off” ) = 1  Aux_{on}
Further, define the time (in minutes) from the last state change as thvac.
To initialize the timeseries, heating, cooling (and auxiliary heat) are “off”: Cool_{on} = Heat_{on} = Aux_{on} = 0 Cool_{off} = Heat_{off} = Aux_{off} = 1
Cooling Thermostat
 Cool_{on} = Boolean(Cool_{off} [math]t_\text{hvac}[/math] > [math]t_\text{min}[/math] & [math]F_\text{cool}[/math] & [math]T_\text{air}[/math] > (Tset_cool + ½ dTdeadband))
 Cool_{off} = Boolean(Cool_{on}&t_{hvac} > t_{min}& F_{cool} & T_{air} [math]\leq [/math](T_{set_cool}  ½ dTdeadband))
Heating Thermostat
 Heat_{on} = Boolean( Heat_{off} & t_{hvac} > t_{min} & F_{heat} & T_{air} [math] \leq [/math](Tset_heat  ½ dT_{deadband}))
 Heat_{off} = Boolean( Heat_{on} & t_{hvac} > t_{min} & F_{heat} & T_{air} > (T_{set_heat} + ½ dT_{deadband}) )
Auxiliary Heating Control (Heat Pumps Only)
To allow a state change from heating to auxiliary to occur in a single time step, the heating and cooling state change evaluations should be followed by:
 Aux_{on} = Boolean( Heat_{on} & Aux_{off} & OR(NOT(F_{aux_deadband}) * ( T_{air} [math] \leq [/math]( T_{set_heat}  ½ dT_{aux}) ) & OR (NOT(F_{aux_lockout} * (T_{air} [math] \leq [/math] T_{aux}) & OR(NOT (F_{aux_delay},(t_{hvac} > t_{aux}) )
 Aux_{off} = Boolean( Aux_{on} & T Faux_deadband * ( Tair > (Tset_heat + dTdeadband) ) & thvac > tmin )
If Aux_{on} then Heat_{off} = 1 and Heat_{on} = 0
Band control
Under band control regime (e.g., object house {thermostat_control BAND;}
), the setpoint and deadband settings are ignore, and instead the HVAC control uses the band control variables:
 TauxOn
 The indoor temperature at which auxiliary heating is turned on.
 TheatOn
 The indoor temperature at which normal heating is turned on.
 TheatOff
 The indoor temperature at which heating is turned off.
 TcoolOff
 The indoor temperature at which cooling is turned off.
 TcoolOn
 The indoor temperature at which cooling is turned on.
The control regime is used for external controllers that wish to directly control the actual temperatures at which the HVAC system changes state.
No control
Under no control regime, i.e., object house { thermostat_control NONE;}
, all control variables are ignored and the HVAC system mode is not changed by any internal logic. The variable system_mode
determines the state of the HVAC system and must be controlled directly from the external controller.
Outdoor Temperature Adjustments to Capacity and COP
The DOE2 building stimulation program provides curves that adjust nameplate COPs and capacities for heat pumps and air conditioners as a function of the wetbulb temperature (Twb) of the return air and/or the outdoor air temperature (Tout). The curves relevant to the House_e model (from DOE2 Reference Manual, Part 1, Version 1.2, pg IV.194199) are shown in Table 5, below. Variables involving CAP refer to capacity and variables involving EIR refer to DOE2’s energy input ratio, which is the inverse of COP.
Table 5. DOE2 SystemEquipment Default Curves
DOE2 SystemEquipment Default Curves Extracted from Table IV.11, DOE2 Reference Manual, Part 1, Version 1.2 (pg IV.7273)  

Keyword  Curve  Variables  Curve Type ^{*} 
Applicable SYSTEMTYPE(s) 
Default Curve Coefficients  
a  b  c  d  e  f  
COOLCAPFT  SDLC1  Twb,Tout  bilinear  RESYS  0.59815404  0.01329987  0.0  0.00514995  0.0  0.0 
COOLEIRFT  SDLC11  Twb,Tout  bilinear  RESYS  0.49957503  0.00765992  0.0  0.01066989  0.0  0.0 
HEATCAPFT  SDLC51  Tout  quadratic  RESYS  0.34148808  0.00894102  0.00010787  0.0  0.0  0.0 
HEATEIRFT  SDLC56  Tout  cubic  RESYS  2.03914613  0.03906753  0.00045617  0.00000203  0.0  0.0 
House_e does not explicitly model moisture in the home, so the Twb is assumed to be at the standard test condition 67°F. Eliminating Twb as a variable and inverting the EIR equations to produce equivalent COP equations gives the correction factor equations of the forms:
 F_COP_T = [math] \frac{1}{EIRFT} = \frac{1}{(K_{0} + K_{1} * T_{out} + K_{2} * T_{out}^{2} + K_{3} * T_{out}^{3})}[/math]
 F_Capacity_Tout = CAPFT = [math] K_{0} + K_{1} * T_{out} + K_{2} * T_{out}^{2} + K_{3} * T_{out}^{3}[/math]
The resulting coefficients used by GridLABD are shown in the Table 6, below.
Table 6. GridLABD Equipment COP Factors
HVAC Equipment COP Factors  

COP Factor  K_{0}  K_{1}  K_{2}  K_{3}  Limit 
F_Cool_COP_T_{out}  0.01363961  0.01066989  0.0  0.0  40 
F_Heat_COP_T_{out}  2.03914613  0.03906753  0.00045617  0.00000203  80 
F_Cooling_Capacity_T_{out}  1.48924533  0.00514995  0.0  0.0   
F_Heating_Capacity_T_{out}  0.34148808  0.00894102  0.00010787  0.0   
These are then used to compute the actual COP and capacity as a function of outdoor temperature, as follows:
Note that partload effects (the effect of starting a heating/cooling cycle are not yet accounted for in GridLABD). They will be added in a future release.
HVAC and Electrical Loads
 If the Heat system type is not a heat pump, then the heating capacity is
 Heating_capacity = Design_heating_capacity
 If the Heat system type is a heat pump, then the heating capacity is determined using Table 6 and the previous section to evaluate F_Heating_Capacity_Tout
 Heating_capacity = Design_heating_capacity * F_Heating_Capacity_Tout
 The actual capacity at operating conditions for air conditioning is determined using Table 6 and the previous section to evaluate F_Cooling_Capacity_Tout
 Cooling_capacity = Design_cooling_capacity * F_Cooling_Capacity_Tout
 The electrical load of the fan is
 P_{fan} = F_{fan} * (HVAC_{on} * Fan_power +F_{2speed}* HVAC_{off} * Fan_power_low_speed_fraction
 The sensible heat provided by the HVAC system to the air (Qhvac), with a sign convention of heating positive and cooling negative, is
 Q_{hvac} = Heat_{on} * Heating_capacity + Aux_{on} * Auxiliary_capacity –Cool_{on} * Cooling_capacity / (1 + Latent_cooling_fraction) + P_{fan}
 If use_latent_heat is set to TRUE the latent heat is
 Latent_heat_load = Cooling_capacity * (1  1 / Latent_cooling_fraction)
 if use_latent_heat is set to FALSE, the latent heat is
 Latent_heat_load = 0;
 If the Heat system type is not a heat pump, then the heating COP is
 Heat_COP = 1
 If the Heat system type is not a heat pump, then the heating COP is determined using Table 6 and the previous section to evaluate F_Heating_Capacity_Tout
 Heat_COP = Heat_COP_std * F_Heat_COP_Tout
 The cooling capacity is determined using Table 6 and the previous section to evaluate F_Cool_COP_Tout
 Cool_COP = Cool_COP_std * F_Cool_COP_Tout
 Define additional HVAC functionality indicators, indicating electricity as the source for heating and the presence of a twospeed fan
 F_{electric} = Boolean(Heat_system_type = heat pump <OR>
Heat_system_type = resistance )
 F_{2speed} = Boolean(Fan_type = 2speed )
 Define additional state variables indicating that heating/cooling is “on” or “off”
 Hvac_{on} = Boolean( Heat_{on} <OR> Cool_{on} )
 Hvac_{off} = Boolean( Heat_{off} & Cool_{off} )
 The electrical power drawn by the HVAC system (Phvac, kW) is the sum of the heating, cooling, and fan electricity consumption
P_{hvac} = F_{electric}Heat_{on} * ( Heating_Capacity / 3.413 (Btu/hr
kW) ) / Heating_COP + (Cooling_Capacity / 3.413 (Btu/hrkW) ) * 1 + Latent_Cooling_Fraction) /
Cooling_COP + P_{fan}
Using House_E
The following section explains how to use house_e inside GLM files. The code snippets are meant as file excerpts and samples.
HVAC Settings
Two methods exist for describing the HVAC system presence.
The first method exclusively uses the "system_type" property for describing a house's HVAC system. It contains a set of values joined by pipes to describe the system. The valid options are
 GAS for natural gas heating
 AIRCONDITIONING for electric cooling units
 FORCEDAIR for the presence of a central ventilation system (including duct fans)
 TWOSTAGE for twospeed central ventilation fan systems
 RESISTIVE for purely resistive heating
If neither GAS nor RESISTIVE are set, the model will assume that a given house has a heat pump, a onespeed central ventilation fan, auxiliary heating with an auxiliary deadband for heating.
The second method uses a combination of "heating_system_type", "cooling_system_type", "auxiliary_system_type", "auxiliary_strategy", and "fan_type" to describe the HVAC system more explicitly.
The three system types controls what mechanism, if any, is used. The fan_type controls the presence of central ventilation and whether or not it has a lowpower setting. Auxiliary heat strategies can be put together with pipes (with the exception of "NONE", which has adds nothing) to combine the control options.
The valid settings are:
heating_system_type

cooling_system_type

fan_type

auxiliary_system_type

auxiliary_strategy

It is assumed that any system with a heat pump will have electric auxiliary heating, and that any system with central heating or cooling will include a fan for circulation.
Thermal Envelope Settings
The primary values for the thermal envelope of a modeled house are "Rroof", "Rwall", "Rfloor", "Rwindows", and "Rdoors". The Rvalue of a surface is the inverse of its Uvalue. If one or more of these values are set explicitly, they will be used over the values set by the following options for that field.
Thermal Integrity Option
"thermal_integrity_level" is usable to provide unambiguous insulation settings. It will override any values not already set, but will override that objects initial values. The valid options are "VERY_LITTLE", "LITTLE", "BELOW_NORMAL", "NORMAL", "ABOVE_NORMAL", "GOOD", "VERY_GOOD", and "UNKNOWN". The default value is "UNKNOWN", which will not use the thermal integrity level value lookup table.
Window Options
The type of glass, the window frame material, the window glazing, and the number of window pane layers can all be set, and will be used to fill in the window Rvalue and the window solar transmission coefficient.
Both "aluminum" and "aluminium" are accepted keyword spellings for the window frame type.
glass_type

window_frame

glazing_treatment

glazing_layers

Example HVAC Configurations
The following snippets can be used to define the HVAC system within a house. The two methods will results in the same system in both cases. The values for the houses with the separate system types are being set explicitly for clarity, even if the defaults would apply the same value.
Only one method is listed for the auxiliary heating strategies because the older style of describing the HVAC system did not include options for auxiliary heating types, presence, or strategies. A combination with system_type, auxiliary_system_type, and auxiliary_strategy, will work without options colliding.
Gas heating
object house{ system_type GAS; }
object house{ heating_system_type GAS; cooling_system_type NONE; auxiliary_system_type NONE; }
Heat pump
object house{ system_type AIRCONDITIONINGFORCEDAIR; }
object house{ heating_system_type HEAT_PUMP; cooling_system_type HEAT_PUMP; auxiliary_system_type ELECTRIC; auxiliary_system_type DEADBAND; fan_type ONE_SPEED; }
Heat pump with twospeed fan
object house { system_type AIRCONDITIONINGTWOSTAGE; }
object house{ heating_system_type HEAT_PUMP; cooling_system_type ELECTRIC; fan_type TWO_SPEED; auxiliary_system_type ELECTRIC; auxiliary_strategy DEADBAND; }
Baseboard heating
object house{ system_type RESISTIVE; }
object house{ heating_system_type RESISTANCE; cooling_system_type NONE; auxiliary_system_type NONE; fan_type NONE; }
Electric heat and central air
object house{ system_type RESISTIVEFORCEDAIR; }
object house{ heating_system_type RESISTANCE; cooling_system_type NONE; auxiliary_system_type NONE; fan_type ONE_SPEED; }
Auxiliary heat with timer
object house{ heating_system_type HEAT_PUMP; cooling_system_type ELECTRIC; auxiliary_system_type ELECTRIC; auxiliary_strategy TIMER; }
Auxiliary heat with deadband
object house{ heating_system_type HEAT_PUMP; cooling_system_type ELECTRIC; auxiliary_system_type ELECTRIC; auxiliary_strategy DEADBAND; }
Auxiliary heating with Timer and Lockout
object house{ heating_system_type HEAT_PUMP; cooling_system_type ELECTRIC; auxiliary_system_type ELECTRIC; auxiliary_strategy TIMERLOCKOUT; }
Auxiliary heating with Deadband and Lockout
object house{ heating_system_type HEAT_PUMP; cooling_system_type ELECTRIC; auxiliary_system_type ELECTRIC; auxiliary_strategy DEADBANDLOCKOUT; }
Auxiliary heating with Deadband, Lockout, and Timer
object house{ heating_system_type HEAT_PUMP; cooling_system_type ELECTRIC; auxiliary_system_type ELECTRIC; auxiliary_strategy DEADBANDLOCKOUTTIMER; }
Solar heat gain from the east, south, west, and horizontal with no latent heat, no fan heat, and linear COP and capacity curves
object house{ include_solar_quadrant HESW; use_latent_heat FALSE; include_fan_heatgain FALSE; heating_cop_curve LINEAR; cooling_cop_curve LINEAR; heating_cap_curve LINEAR; cooling_cap_curve LINEAR; }
New Features
This section will document changes from the original model (as specified above). Most of these are optional features that have been requested by specific projects.
Window Openings
This model is designed to represent the effects of people opening their windows during shoulder temperature periods. This is a complicated human interaction to model, as it is often related to current temperature, forecast of the temperature and other weather conditions, history of temperature, humidity, etc. This model is designed to be a brute force approach to representing this impact.
Basically, you activate the model (simulate_window_openings is FALSE by default), then describe the upper and lower cutoffs of when the window WILL absolutely be open versus absolutely WILL NOT be open (window_low_temperature_cutoff and window_high_temperature_cutoff).
The three coefficients listed below then describe a probability curve between the two cutoff points – the probability of opening or closing a window is now a function of the outside air temperature. The “delta” variable is “how often” to update the model as a function of outdoor air temperature, i.e., if outside air changes by 5 degrees, let's see if the human has changed their mind.
The effect is that if windows are closed, normal operation. If open, the HVAC is overridden (to OFF) and UA is raised by a factor of 10 (which makes heat transfer very fast).
What we don’t have a great model for is the probability curve or what the cutoff values should be! For previous work, we found that a simple linear between the cutoffs was a pretty good representation. I think for cutoffs, we used 2 to +8 around the setpoint.
Parameter  Default Value  Units  

simulate_window_openings  FALSE  Boolean  activates a representation of an occupant opening a window and deactivating the HVAC system 
is_window_open  FALSE  double  (output only) defines the state of the window opening, 1=open, 2=closed 
window_low_temperature_cutoff  60  °F  lowest temperature at which the window opening might occur 
window_high_temperature_cutoff  80  °F  highest temperature at which the window opening might occur 
window_quadratic_coefficient  0  none  quadratic coefficient for describing function between low and high temperature cutoffs 
window_linear_coefficient  0  none  linear coefficient for describing function between low and high temperature cutoffs 
window_constant_coefficient  1  none  constant coefficient for describing function between low and high temperature cutoffs 
window_temperature_delta  5  °F  change in outdoor temperature required to update the window opening model 
See Also
 Residential module
 User's Guide
 Appliances
 house class – Singlefamily home model.
 residential_enduse class – Abstract residential enduse class.
 occupantload – Residential occupants (sensible and latent heat).
 ZIPload – Generic constant impedance/current/power enduse load.
 Technical Documents