Sequences of operations for high thermal mass radiant systems
The intent of these sequences of operation is to use slowly adjusted slab temperature setpoints to control radiant system operation to maintain comfort in the zone. The strategy operates based on a slab temperature measurement and uses information from the zone temperature during the occupied period to make minor adjustments to the slab setpoint for the next day. The strategy constrains the radiant system to take advantage of thermal inertia and condition the slab only during certain periods of time. For a given project, this allows designers to select for either: more efficient and cost effective operating hours (e.g. system only operates at night), longer operating hours to yield smaller heating or cooling plant sizes (e.g. system sized assuming 18 or 24 hour operation on the design day), or aim to provide a more uniform daily range of comfort conditions (e.g., time pre-cooling such that it approximately accounts for the slab time constant and the peak loads).
These sequences apply to zones with a high performance envelope design that use high thermal mass radiant systems for both heating and cooling, and have reasonably uniform internal loads.
These sequences do not apply to radiant metal ceiling panels, which have a faster response and can be controlled similarly to all-air systems. The sequences also do not apply where heat exhange between the ceiling and floor surfaces are substantially blocked (e.g., by a wall to wall drop ceiling), and/or where the ceiling surface is lightweight (e.g. the uppermost floor in a building which uses metal deck without concrete for the roof).
More formally, these sequences apply to cases where:
a) The response time for the radiant system in response to a step change in flow is greater than approximately 5 hours. See this paper for more detail. Faster responding systems (e.g. a VAV box, or a radiant metal ceiling panel) should not be controlled using these sequences.
b) The zone has a high performance envelope with limited direct solar. This minimizes the disturbance due to changing outside conditions. This is the case for typical radiant designs in most climates, even those with significant inter-day temperature changes, as the change in heat gain/loss to the exterior is relatively small compared to internal gains and heat stored in the mass of the zone.
c) The zone has reasonably uniform internal loads from day to day, such as an office environment. Zones with highly fluctuating and irregular schedules (e.g. an event space) should not be controlled using these sequences.
The official ASHRAE Standard 55 web tool for performing the above calculations can be found at comfort.cbe.berkeley.edu.
§ For example, for a radiant system where the changeover between heating and cooling occurs at the plant level for the whole building, and there are no mixing valves, T_water_htg and T_water_clg could be the leaving boiler and leaving chiller temperatures respectively.
§ For example, for a radiant system where a mixing valve supplies a single, or multiple radiant zones, T_water_htg and T_water_clg is the temperature downstream of that mixing valve.
§ Where §3.6 applies, the median calculation occurs every sampling instance (e.g. every minute). The minimum and maximum calculation shall be performed on these median values at the end of the occupied period.
§ If within the capabilities of the automation system programming language, the 90th and 10th percentile values are preferable to the maximum and minimum to avoid outlier measurements.
§ To prioritize nighttime pre-cooling, more efficient cooling plant conditions, lower electricity energy costs, and reduced electricity demand charges, the radiant system should be locked out during the occupied period, so that it operates during the night.
§ To prioritize uniform comfort conditions within the zone, the radiant system should be locked out for a period approximately 12-16 hours long, starting 3-5 hours before the end of the occupied period.
§ To reduce the size of the cooling or heat plant, the radiant system should be not be locked out, so that the total cooling and heating loads are distributed across the entire 24 hour period. An alternate to this is to locked out the radiant system for only the hours that correspond with peak demand and energy charges (e.g. 3p.m. to 8p.m.), which combines the benefit of avoiding peak pricing while still significantly reduced plant size.
§ This online design tool provides a rapid, simplified method for approximately evaluating the above design points. The exact design can be more accurately estimated using a simulation tool that implements the ASHRAE Heat Balance method and supports radiant systems.
§ Note that it is often advantageous (from an efficiency or utility tarif perspective) to have separate lockout periods for heating and cooling mode, depending on the heating and cooling system serving the radiant system. For example for an air-source heat pump, cooling during the night is most efficient, while heating during the middle of the day is more efficient, and the lockout schedules (independent for heating and cooling) should reflect this.
§ This avoids synchronous pulsing of valves (due to the pulsed flow control described later), mitigates issues with differential pressure control of pumps, and reduces startup loads on the heating/cooling plant when the lockout period ends.
§ For a high thermal mass system designed as the primary source of heating and cooling there will be a significant number of days per year in which the average 24 hr load is small enough that the thermal inertia of the system alone causes conditions to remain within the comfort limits. Primary heating or cooling is not required on these days. The above sequences prevent the system from providing heating and cooling to the slab during the same day and also ensures that there is at least one full day in which the slab does not operate (i.e., drifts) between mode changeovers.
§ Compared to on/off control, pulsed flow control will have lower overall pumping power and higher average return water delta temperature.
§ More detail can be found in this this more detailed paper.
§ Pulsed flow control where the (constant) open pulse duration is approximately the time required to 'flush' the tubing loop at design flow will yield a similar cooling/heating capacity to average flow relationship as idealized variable flow control (i.e., using a proportional/modulating valve). However, controllability at low part loads (i.e., ultra low flow rates) is much better for pulsed flow control than for variable flow control, and initial costs are lower.
§ The designer can calculate the flush time for their specific case using design flow rate, diameter, and length. However, capacity is not highly sensitive within the range of variation in 'flush' time for typical radiant system designs (3-7 minutes). 4 minutes is a reasonable default value.
i. A call for cooling shall occur at the start of the available period (i.e. immediately after the end of the lockout period, L_end), when all of the following conditions are met:
a. the slab temperature (T_slab) is greater than the slab setpoint (T_slab_ stpt); and
b. the zone is in cooling mode; and
c. the supply water temperature (T_water_clg) is 2 °F or more below the slab temperature (T_slab).
ii. At the end of the lockout period, a proportional control loop shall be used to control the pulse rate. The loop percentage (Clg_loop_out) shall be calculated as the error between the slab temperature and the setpoint divided by the proportional band according to Clg_loop_out = (T_slab - T_slab_stpt)/PB where PB is the proportional band (typically 2 °F, adjustable). The duration of the closed pulse shall be determined based on the output of the above proportional control loop according to P_closed = P_closed_max * (1 - Clg_loop_out).
i. A call for heating shall occur at the start of the available period (i.e. immediately after the end of the lockout period, L_end), when all of the following conditions are met:
a. the slab temperature (T_slab) is less than the slab setpoint (T_slab_ stpt); and
b. the zone is in heating mode; and
c. the heating supply water temperature (T_water_htg) is 2 °F or more above the slab temperature (T_slab).
ii. At the end of the lockout period, a proportional control loop shall be used to control the pulse rate. The loop percentage (Htg_loop_out) shall be calculated as the error between the slab and the setpoint divided by the proportional band according to Htg_loop_out = (T_slab_ stpt - T_slab)/PB where PB is the proportional band (typically 2 °F, adjustable).The duration of the closed pulse shall be determined based on the output of the above proportional control loop according to P_closed = P_closed_max * (1 - Htg_loop_out).
iii. A call for cooling shall occur at the start of the available period (i.e. immediately after the end of the lockout period, L_end), when all of the following conditions are met:
d. the slab temperature (T_slab) is greater than the slab setpoint (T_slab_ stpt); and
e. the zone is in cooling mode; and
f. the supply water temperature (T_water_clg) is 2 °F or more below the slab temperature (T_slab).
iv. At the end of the lockout period, a on/off control loop shall be used to control the valve based on the slab setpoint (T_slab_stpt).
iii. A call for heating shall occur at the start of the available period (i.e. immediately after the end of the lockout period, L_end), when all of the following conditions are met:
a. the slab temperature (T_slab) is less than the slab setpoint (T_slab_ stpt); and
b. the zone is in heating mode; and
c. the heating supply water temperature (T_water_htg) is 2 °F or more above the slab temperature (T_slab).
iv. At the end of the lockout period, a on/off control loop shall be used to control the valve based on the slab setpoint (T_slab_stpt).
This requirement prevents uneccessary pumping power if the supply water temperature is close to the slab temperature.
i. Respond to a call for cooling by opening the valve(s) to provide flow through the radiant system
ii. Respond to a call for heating by creating a heating changeover request to the changeover system.
i. Respond to a call for heating by opening the valve(s) provide flow through the radiant system.
ii. Respond to a call for cooling by creating a cooling changeover request to the changeover system.
This paper describes an early version of the slab temperature setpoint reset strategy in more detail, along with simulation data showing the effect on the results.
Note that the outside weather based control option allows for significant simplification of the sequences. Aside from the slab temperature setpoint, potentially, the radiant zone mode can also be determined solely based on the outside air temperature. However, both of these solutions will likely require manual tuning after the building has been operating, which may be difficult to ensure in practice.
§ Excluding the offset ensures that the supplementary heating and cooling system is secondary to the radiant system. These secondary systems should operate to maintain comfort in the zone when either average daily zone loads or short term peaks in zone load exceed the capacity of the radiant system to handle or respond to.
§ This prevents the slab reset from from continually decreasing the slab setpoint, causing overcooling.
§ This prevents the slab reset from from continually increasing the slab setpoint, causing overheating.
A water temperature control zone can serve:
a) an individual thermal
zone (i.e., a single large room);
b) a group of thermal zones where the loads are likely to be similar and/or
which are closely thermally coupled to each other (e.g. three water temperature
control zones each encompassing all thermal zones on all floors for South,
North, and Interior respectively);
c) all thermal zones in the building (e.g. the leaving temperature from the
heating/cooling plant) where the expected variation between loads within the
building is low.
This very slow feedback loop gradually adjusts for seasonal demand for higher and lower water temperatures respectively. The advantage of this approach is that it is a feedback loop based on actual performance.
This approach has the advantages of being deterministic and not requiring another control loop. However, the relationships must be initially calculated (e.g. based on simplified model and daily steady state envelope heat loss estimates), making assumptions that are unlikely to match the actual building, and thus, these relationships (min/max temperatures and slopes) typically require modification after a period of observation.
Figure 1: Visual representation of radiant sequences in cooling mode with Top) pulse width modulation (PWM) and Bottom) ON/OFF manifold valve control. Data is from the building automation systems of two different California large office buildings, not from simulation.