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Application of a New Dynamic Heating System Model Using a Range of Common Control Strategies

Department of Mechanical & Construction Engineering, Northumbria University, Newcastle NE1 8ST, UK
DesignBuilder Software Limited, Stroud GL5 2AD, UK
Welsh School of Architecture, Cardiff University, Cardiff CF10 3NB, UK
Author to whom correspondence should be addressed.
Buildings 2016, 6(2), 23;
Received: 23 March 2016 / Revised: 24 May 2016 / Accepted: 27 May 2016 / Published: 3 June 2016
(This article belongs to the Special Issue Modelling of Heating and Cooling in Buildings)


This research investigates the overall heating energy consumptions using various control strategies, secondary heat emitters, and primary plant for a building. Previous research has successfully demonstrated that a dynamic distributed heat emitter model embedded within a simplified third-order lumped parameter building model is capable of achieving improved results when compared to other commercially available modelling tools. With the enhanced ability to capture transient effects of emitter thermal capacity, this research studies the influence of control strategies and primary plant configurations on the rate of energy consumption of a heating system. Four alternative control strategies are investigated: zone feedback; weather-compensated; a combination of both of these methods; and thermostatic control. The plant alternative configurations consist of conventional boilers, biomass boilers, and heat pumps supporting radiator heating and underfloor heating. The performance of the model is tested on a primary school building and can be applied to any residential or commercial building with a heating system. Results show that the new methods reported offer greater detail and rigor in the conduct of building energy modelling.

1. Introduction

The role of Heating Ventilation and Air-Conditioning (HVAC) systems and controls within a building is an important one as it has significant impact on the energy consumption and internal comfort [1]. HVAC systems with efficient control increases the productivity and comfort satisfaction of a building’s occupants [2]. In terms of cost and energy savings, a reduction of up to 30% can be achieved [3]. Thus, it is of utmost importance for designers to make informed decisions on the choice and design of HVAC systems and controls [4] to take into consideration both energy and comfort requirements.
Advances in computing technology have led to the possibility of modelling sophisticated controls and system performance in great detail. However, building energy simulation tools today are rigid and lack flexibility in terms of modelling a variety of HVAC systems and control options. As a result, this limits practitioners from exploring various system design and control strategies and deters them from seeking alternative system designs that could reveal opportunities to save energy.
This research builds on previous research by investigating the performance of a complete (primary and secondary) heating system developed specifically for a third-order lumped parameter building model [5]. Primary plant refers to the source of heat energy, such as conventional boilers, biomass boilers, and heat pumps, The model allows three possible configurations of primary plant, namely conventional only (boilers), renewables only, or hybrid (boilers and renewables). Secondary plant refers to room-based equipment that is used to distribute the heat energy to the occupants, such as underfloor heating and radiators. The model is capable of adopting all of the common control strategies for these secondary plant items and is applicable to any commercial or residential building which has a heating system.

2. Modelling of HVAC Systems and Controls

HVAC systems and controls are traditionally modelled using either menu-based or component-based tools to cater for different levels of user skills and modelling capabilities. Of the two, the menu-based approach is a simple and straightforward method adopted by most tools such as DOE-2, eQuest, Building Analyser, BLAST, and DesignBuilder which is a graphical user interface for the extensively-used EnergyPlus simulation engine. This approach provides preconfigured and packaged heating/cooling systems that are represented in the form of a menu for users to insert the parameters.
The component-based system approach requires users to have a deeper understanding of HVAC systems as it provides greater flexibility in terms of system customization. Good examples of tools adopting this approach are IES-APACHE and TRNSYS. Each system is represented by individual components encapsulated with mathematical algorithms and energy balancing equations where the output of each component is connected to the input of the next component to make up a system [6].
For the purpose of comparing HVAC systems and evaluating different control strategies, detailed dynamic HVAC models are required [7,8,9,10,11]. These detailed dynamic HVAC models have higher explicitness, thus requiring a greater number of user input parameters and in-depth specialist knowledge of controls. In addition, many tools available today use a fictitious and immeasurable parameter as an input parameter for the controller such as the use of the exact energy demand (so-called “heat-balance models”) to achieve the setpoint.
Previous research [12] successfully developed a user-friendly, dynamic heat emitter model that has achieved improved results when compared to commercially available tools, such as IES and EnergyPlus. This research expands on previous work to inform sustainability engineers and modelers of the energy performance of alternative heating systems and showcases a range of control strategies available.
The objectives for this research are as follows:
Develop robust circuit control strategies with multi-zone functionality commonly adopted in current design practice for secondary system side and advanced system control strategies;
Embed primary and secondary HVAC systems and component models within parent code; and
Test and demonstrate the capabilities of the primary and secondary HVAC systems adopting a wide range of control strategies and primary plant system configurations.

3. Development of HVAC Systems and Controls

The following commonly-used control strategies have been developed for the purpose of this research. These control strategies are easy to implement allowing modelers to make comparative assessment in terms of comfort and energy:
Constant Temperature, Varying Flow rate (1CTVF), typically used in zone feedback control;
Varying Temperature, Constant Flow rate (2VTCF), typically used in weather-compensated control;
Varying Temperature, Varying Flow rate (3VTVF), typically used when both of the above methods are combined; and
Constant Temperature, Constant Flow rate (4CTCF), typically used in simple thermostatic (i.e., “on-off”) control.

3.1. Variable Flow Rate

The variable flow (VF) rate control is most commonly found on domestic radiators where a thermostatic radiator valve (TRV) regulates the flow rate into the emitter by adjusting the valve. (The term “thermostatic” in this context is a misnomer because these types of valves vary the flow rate to each radiator in response to local room temperature conditions). This method of control takes the internal temperature of the treated zone as an input to control the flow rate. Flow rate is regulated linearly between zero and the designed mass flow rate with reference to the deviation between the upper and lower limits of the proportional band imposed on the setpoint, also known as the throttling range. Once the internal temperature reaches above the upper limit, when heating is no longer required, the controller delivers zero flow, turning the emitter off. Conversely, the heat emitter receives the designed mass flow rate to provide maximum thermal output when the internal temperature is below the lower limit. Equation (1) shows the calculation method to determine the mass flow rate when varying:
m ( z ) = m Des ( z ) { 1 ( T ai ( z ) Lower Limit ( z ) Proportional band ( z ) ) }

3.2. Variable Temperature

Variable (VT) temperature control, better known as weather-compensating control, modulates flow temperature in accordance to the external temperature [13]. This method of control is frequently adopted in the UK [14] because it has a low installation cost and enables the heating system to be adjusted in relation to the coldness of the weather [15].
The external dry bulb temperature and the flow temperature are required as inputs for the weather compensating control to function. The flow temperature serves as a feedback input to ensure the required temperature is met. The flow temperature, which varies between the design water temperature and minimum flow water temperature, is linearly proportional to the design external dry bulb temperature (typically, −3 °C) and a balance point temperature [12], shown in Equation (2). The balance point temperature refers to an external temperature, typically 15–20 °C dry bulb temperature, where heating is no longer required [15]. The minimum flow water temperature is dependent on the type of emitter. Typical minimum flow water temperatures for radiators and underfloor heating are 20 °C and 35 °C respectively [15,16].
T f _ curr ( z ) = min ( T fDes ( z ) , max ( T fMin ( z ) , T fDes ( z ) ( T fDes ( z ) T fMin ( z ) ) × ( T ao _ c u r r T aoDes T BP ( z ) T aoDes ) ) )

3.3. Constant Temperature and/or Constant Flow Rate

The control strategies 1, 2, and 3 developed for the emitter models have either flow temperature and/or the flow rate varying. Emitters adopting strategies with constant flow (CF) temperature will receive water temperature at design value dependent on the type of emitter, typically 80 °C for radiators and 45 °C for underfloor heating.
Similarly, constant flow rate control circuits will be supplied with the designed mass flow rate. Control strategy 4, with constant temperature and constant flow (CTCF) control, better known as ON/OFF thermostatic control, toggles between fully on when the internal zone temperature falls below the heating setpoint, and fully off when it is above the setpoint.

3.4. Assumptions for Primary HVAC Systems

The following assumptions are made for the primary HVAC systems and controls developed for this research and for the other software used for comparison:
  • All emitter systems are connected to a single main circuit on the secondary side;
  • A maximum of three units of primary plant have been specified for each of the heating systems tested and compared in this research;
  • Pressure loss effects in pipe fittings and plant are neglected;
  • The schedule controller is designed to offer the minimum number of primary plant (e.g., boilers) to satisfy load requirements;
  • Loads are shared equally between the online primary plant;
  • Flow rate entering the primary plant is constant; and
  • Required flow water temperature by the secondary systems is constantly met.

3.5. Modelling of Primary HVAC Systems

Modelling of the primary plant for this research is carried out in three stages by passing parameters from one node to the next as illustrated in Figure 1 below. Node, in this context, refers to a conjunction point where variables are passed from one model/side to another stage. The first stage at the (1) Low Loss Header Node is where variables from the secondary system side are passed to the primary side (heat generator (s)). These parameters are fed into the next stage at the (2) Controller Node to determine the status (es) of the generators/s based on energy demand from the building. Lastly, the flow rates between the flow and return sections on the primary side are balanced in the (3) Balance Pipe Node.

3.5.1. Step 1: Low Loss Header Node

The low loss header node is an intersection point that balances the flow rates and temperatures between primary plant and secondary systems. Variables for the primary side are calculated using return outputs from the secondary side at the low loss header node. For future expansion, secondary systems, such as domestic hot water (DHW) and heating coils for all air systems, can be easily connected to the low loss header node.

(a) Weighted average return water temperature across all zones 

The weighted average of the return water temperature is a single return water temperature from all secondary circuits returning to the primary system calculated using Equation (3):
T wrt =   [ ( T r ( z = 1 ) × m r ( z = 1 ) ) + ( T r ( z = 2 ) × m r ( z = 2 ) ) +   + ( T r ( z = N ) × m r ( z = Z ) ) ] [ m r ( z = 1 )   +   m r ( z = 2 )   +   + m r ( z = Z ) ]

(b) Sum of total mass flow rate of all zones 

Mass flow rates for all treated zones are summed as an input for the boiler model using Equation (4):
Σ m Ret = [ m ( z = 1 )   +   m ( z = 2 ) +   m ( z = 3 ) + m ( z = Z ) ]  

3.5.2. Step 2: Controller Node

The modulating sequence controller determines the operational status and percentage load capacity of the primary plant side using the input parameters calculated at the low loss header. The energy demand of the secondary systems is shared equally amongst the online primary plant to meet the load demand.
At the start, all three generators are offline when loads are below the assumed 25% (i.e., the assumed minimum turn-down ratio) of the lead generator. Once the load increases to above 25% of the maximum generator capacity, the lead generator comes online. When the load exceeds the lead generator’s maximum capacity, the sequence controller will schedule the next generator to come online and share the total load equally. The same process is repeated when the load exceeds the capacity of two generators and the third generator will be brought online to share the load equally.

Primary Plant Systems Configurations

The various configurations of primary plant are one of the highlights of this paper. It allows users to model different plant combinations to conduct comparative analysis on their energy performances. Three possible primary plant configurations as shown below have been developed for this research. Users would simply select one configuration from the three options available. For the hybrid system plant configuration, the low carbon renewable system(s) will serve as the lead with the conventional plant topping-up.
Conventional system(s) only;
Renewables system(s) only; and
Hybrid system(s).

3.5.3. Step 3: Balance Pipe Node

The balance pipe is used to balance the flow rates between the flow and return streams of the primary side. Depending on the number of generators online, the flow rate required by the return stream entering the plant can be determined and the excess flow rate between the flow and return streams is automatically balanced by the balance pipe.
When the flow rate required by the plant is less than the flow rate on the return side, the excess flow rate is diverted away from the return to the flow stream in the balance pipe. This would result in cooler return water mixing directly to the flow stream and is compensated by the plant generating higher supply temperature.
Conversely, when the plant requires additional flow rate to operate, flow is directed from the supply stream with the higher temperature and mixed directly with the cooler return stream, raising the temperature of the flow entering the plant.

3.6. Development of Primary Plant Models

Three primary plant models have been developed for this research:
  • Conventional gas-fired boiler;
  • Biomass boilers; and
  • Heat pumps.

3.6.1. Development of Conventional and Biomass Boiler Models

The boiler model developed for this research adopts the British European Standards (BS EN 15316 series) for development of conventional boilers [17] and biomass boilers [18]. The standard is in compliance with the Council Directive 92/42/ECC regarding boiler efficiency [19].
The model has a convenient setup which requires a total of only four input parameters by the user. These are the type of boiler (conventional low temperature or condensing), burner (atmospheric, fan-assisted, gas or oil), location (room temperature or naturally ventilated space) and, lastly, boiler capacity.
In each of the BS EN standards, three steady state methods with increasing complexities have been detailed. The intermediate complexity boiler efficiency calculation method has been adopted for this research as it offers more detail than the simpler method whilst not requiring iteration/loops that will add to the computational effort found in the more complex method.
The method consists of a total of 21 and 29 calculations steps for the conventional boiler and biomass boiler as detailed in Appendix F of British European Standard 15316: 4:1 and Appendix A of British European Standard 15315: 4:7 respectively. The calculation steps for both conventional and biomass boiler types can be categorized into three main sections. The first section consists of calculation steps to generate parameters that are kept constant throughout the simulation at full, intermediate, and zero load points, such as boiler efficiency and thermal losses. The second section adjusts the efficiencies, thermal losses, auxiliary power, and fuel consumption with reference to the load using interpolation at each time-step. Finally, the latter variables are summed and scaled up by multiplying by the number of operational hours to calculate overall energy performance.
This procedure is re-calculated and updated at each time-step providing a realistic representation of the system over a full operating cycle of the plant after which the results are integrated to form operating cycle total energy consumptions, etc.

3.6.2. Development of Heat Pump Models

The heat pump models developed for this research have been curve-fitted from manufacturer’s data [20]. At each time-step, the equation below is used to determine the load on the evaporator/condenser and compressor by assuming a 5K temperature difference. A, B, C, D, E, F are coefficients obtained from the regression curve fitting method and models fitted for the purpose of this research and can be found in Table 1. These heat pump models have been selected based solely on the capacity of the systems and availability of the data. Subsequently, the coefficient of performance (CoP) can be determined. For further details of this method, see [21]:
y = A + B x 1 + C x 1 2 + D x 2 + E x 2 2 + F x 1 x 2
where: x 1 : external dry bulb temperature (°C); x 2 : return water temperature (°C).

4. Testing/Debugging of Primary Plant Models

Tests were carried out independently on separate components using manual calculations and analytically verified on a spreadsheet. The systems are then integrated as a complete heating primary-side system and extensively tested by manually stepping through the code for various possible scenarios to ensure the robustness and functionality of the model.

4.1. Test Case Building Model

For the purpose of this research, a naturally-ventilated 25-zone actual school building, shown in Figure 2 and Figure 3, with a gross floor area of 4870 m2 has been adopted [22]. The models developed for this research are tested against EnergyPlus (version, U.S. Department of Energy, Washington D.C., U.S.) and IES VE (version, Integrated Environmental Solutions, Glasgow, U.K.), two building energy modelling tools widely used in both academia and industry. Inter-model comparison [23] is an accepted tool to verify simulation software results.
The building was first modelled in DesignBuilder (version, DesignBuilder Software Ltd., Stroud, U.K.) and exported to XML format, which was further modified to incorporate the detailed HVAC module developed for this research. In order to fully embed the developments of this research, modifications had to be made to the XML schema, which contains the input parameters of the systems and the source code of the third order lumped parameter building model to read the input parameters. The HVAC module developed for this research is fully embedded within the simulation tool that reads and calls upon the relevant modules when required.
For simulations in EnergyPlus, the same model developed in DesignBuilder was used and exported to IDF format. For further comparison the same information was used to create an identical model in IES VE.
Results from two key zones (Nursery and Classroom) on the ground floor have been selected as indicated (red dots) in the floor plan above to provide results for zones with different usage patterns. Simulations were performed using a local Newcastle weather file [24,25] for the building which adopts construction templates used in the COPSE Project [22] shown in Table 2.
Temperature profiles and energy output rates for the variants in the table listed below (Table 3) have been presented. Parameters investigated are emitters with different thermal capacities, various control strategies and primary plant configurations. Results are presented for a peak winter week with a typical day extracted providing a clearer representation of the emitter and control strategies in terms of temperature and energy profiles.

4.2. Thermal Comfort

Figure 4 and Figure 5 present results generated for underfloor heating (left column) and radiators (right column) for various control strategies (top to bottom) for a peak winter week. Looking from top to bottom at the various control strategies imposed on the emitters, it is clear that the first three control strategies are capable of successfully achieving the setpoint temperature of 20 °C and demonstrate stable results throughout the peak winter week. Circuit 4 however is the thermostatic control and the inherent deviations in controlled temperature (often known as “saw-toothing”) are clearly evident.
Comparing underfloor heating and radiators (left and right), the ability of the model to capture the transient effects and thermal responsiveness of both emitters can be seen. The radiator model can be seen to achieve the setpoint at a quicker rate of within 30 min (Figure 5) compared to the underfloor heating system which can take up to two hours or more to achieve the heating setpoint of 20 °C.
The higher responsiveness of the radiator is accurately captured in the weather-compensating Variable Temperature, Constant Flow (2VTCF) control strategy. This method of control often causes overheating because it is based on an external dry bulb temperature without accounting for the zone’s internal temperature and useful internal heat gains.

4.3. Energy Consumption by Primary Plant

This research developed a convenient, and yet rigorous, approach to model different control strategies and switch between conventional, renewables, and hybrid plant configurations to evaluate energy consumption. Heating energy consumption calculated over the treated floor area is presented in Table 4 for various emitters, circuit controls, and plant configurations.
Energy benchmarks for a primary school building are 164 kWh/m2 fuel and 32 kWh/m2 electricity for typical practice, and 113 kWh/m2 fuel and 22 kWh/m2 electricity for good practice [26] over the treated area. Results in Table 4 show that the energy predictions made by the detailed HVAC module developed for this research are within limits of good and typical practices for the test scenarios, as recommended by CIBSE [26].
On closer examination, it is evident that the constant temperature and constant flow rate thermostatic control requires significantly more energy when compared to other strategies. This is due to the nature of the controller as it toggles between maximum capacity instead of modulating between proportional bands (VF) and/or in accordance to the external temperature (VT). The high frequency of delivering heating at maximum capacity has thus led to higher energy consumption.
Energy consumption by the radiator system is larger when compared to the underfloor heating system when adopting weather-compensated control. Other than operating at different flow and return water temperatures between the systems, the higher energy consumption by the radiators is largely caused by the higher thermal responsiveness of the emitter causing conflicts between heating and cooling systems.
Unlike weather-compensated control (2VTCF), 1CTVF and 3VTVF take into account zone internal temperatures. In the case of constant temperature variable flow (1CTVF), the underfloor heating system is seen to consume more energy than the radiator system. This is mainly due to the systems having a different response time influenced by the emitter’s thermal capacity. The difference in heating energy profile is governed by the response time of the emitter (i.e., thermal capacity) in which a lesser amount of energy is required by the fast responding radiator and a larger amount of energy is required to overcome the thermally-heavy underfloor heating system. In addition to the mathematical representation for each of the control strategies in previous work by Fong et al. [12], the table below (Table 5) summarizes the advantages and disadvantages for each of the strategies based on energy consumption.

5. Conclusions

The aim of this research was to demonstrate a new building energy modelling method capable of conveniently dealing with alternative control strategies and generating plant options. The results presented here are based on the modelling procedure described in [12] to enable the study of energy consumption in heating systems. A case study was modelled in order to demonstrate the full capabilities and functionalities of the new method. Temperature profiles and energy consumption for different emitters adopting various circuit control strategies are presented.
A number of zone and system control configurations have been simulated over a range of possible primary plant configurations. It has been shown that these are convenient to implement and that this enables comparative evaluation of various plant configurations (including hybrid schemes) to be conducted. Predictions of temperatures made by the various control circuits have demonstrated the ability to provide a realistic representation of how the controllers work in the real world and the results generated compare favorably with established benchmark data.

6. Limitations

The authors recognize that this research is limited by the functionality of each given modelling tool in terms of detail and calculation methods. Furthermore, the validity of the results from this research is based upon inter-model comparison [23] with tools widely used in industry which could be verified further with empirical measurements.

7. Future Work

The recommendations for future research are as follows:
  • Extend the control options at primary system level to include advance control options;
  • Extend the library of components to encompass a larger variety of primary system types;
  • Conduct empirical validation of the new program; and
  • Modify the detailed HVAC module to incorporate sophisticated features in C++ for better memory management to further improve computational efficiency.


The authors would like to thank DesignBuilder Software Ltd. for their technical support and financial assistance for this work.

Author Contributions

Joshua Fong did the modelling and had an equal contribution to paper authorship with Jeremy Edge. Chris Underwood provided advice and editorial support. Andy Tindale and Steve Potter supplied the parent code used in the analysis and also advised on modelling. Hu Du provided formatted weather data for use in the simulations.

List of Symbols

( z ) zone index
m emitter mass flow rate (kg/s)
m Des emitter mass flow rate at design (kg/s)
m r emitter return mass flow rate (kg/s)
m Ret sum of mass flow rate (kg/s)
Proportional Band proportional band (Kelvin)
T ao _ c u r r external dry bulb temperature at current time-step (°C)
T aoDes external dry bulb temperature at design (°C)
T ai internal air temperature (°C)
  T B P ( z ) balance point temperature (°C)
T f _ curr emitter flow water temperature at current time-step (°C)
T fDes emitter flow water temperature at design (°C)
T fMin emitter flow water temperature at minimum (°C)
T r emitter return water temperature (°C)
T w r t emitter weighted return water temperature (°C)
Ztotal number of zones


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Figure 1. Modelling of primary HVAC systems.
Figure 1. Modelling of primary HVAC systems.
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Figure 2. 3D model of test building in DesignBuilder.
Figure 2. 3D model of test building in DesignBuilder.
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Figure 3. Floor plan of test building.
Figure 3. Floor plan of test building.
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Figure 4. Temperature and energy profiles for a peak winter week.
Figure 4. Temperature and energy profiles for a peak winter week.
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Figure 5. Temperature and energy profiles for a typical winter day.
Figure 5. Temperature and energy profiles for a typical winter day.
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Table 1. Example fitted coefficients for heat pump models [20].
Table 1. Example fitted coefficients for heat pump models [20].
Capacity 63.7 kWCapacity 213 kWCapacity 286.7 kW
Condenser Coeff.Compressor Coeff.Condenser Coeff.Compressor Coeff.Condenser Coeff.Compressor Coeff.
Table 2. Building materials.
Table 2. Building materials.
NameExternal Wall(mm)Flat Roof(mm)Partitions(mm)Ceiling Floor(mm)Ground Floor(mm)
Outside LayerBrickwork100Stone Chippings10Plaster13Synthetic Carpet10London Clay500
Layer 2Dense EPS Slab Insulation58Bitumen5Brickwork105Cast Concrete100Brickwork250
Layer 3Concrete block100Cast Concrete150Plaster13Cast Concrete100
Layer 4Gypsum Plastering13Glass Wool134Dense EPS Slab Insulation6.35
Layer 5Ceiling Tiles10Chipboard2.5
Table 3. Variants to be explored.
Table 3. Variants to be explored.
Types of Emitter:
1Underfloor HeatingUFH
Types of Circuit Control Strategy:
1Constant Temperature, Variable Flow rate1CTVF
2Variable Temperature, Constant Flow rate2VTCF
3Variable Temperature, Variable Flow rate3VTVF
4Constant Temperature, Constant Flow rate4CTCF
Types of Primary System Configurations:
1Conventional 2 × 300 kW Conventional BoilerCBLR
2Conventional 3 × 200 kW Conventional BoilerCBLR
3Renewables2 × 300 kW Biomass BoilerBMB
4Renewables3 × 200 kW Biomass BoilerBMB
5Renewables2 × 300 kW Heat PumpHP
6Renewables3 × 200 kW Heat PumpHP
7Hybrid1 × 300 kW Biomass BoilerBMB
1 × 300 kW Conventional BoilerCBLR
8Hybrid1 × 300 kW Heat PumpHP
1 × 300 kW Conventional BoilerCBLR
Table 4. Rate of energy consumption.
Table 4. Rate of energy consumption.
TypeSystem ConfigurationEnergy ConsumptionUnderfloor HeatingRadiator
1Conventional2 × 300 kW Conventional BoilerGAS kWh/m2174.5294.98113.85231.15123.30119.60186.50236.17
2Conventional3 × 200 kW Conventional BoilerGAS kWh/m2177.80101.97120.73231.67121.95117.54186.88237.51
3Renewables2 × 300 kW Biomass BoilerGAS kWh/m2215.93121.18144.09279.48149.47149.99231.73285.01
4Renewables3 × 200 kW Biomass BoilerGAS kWh/m2218.84128.76152.20280.80148.50146.11231.04287.36
5Renewables2 × 300 kW Heat PumpELECT kWh/m276.2354.9155.2081.97138.2083.80113.39163.95
6Renewables3 × 200 kW Heat PumpELECT kWh/m274.0547.4449.6684.2773.4161.9392.09108.77
7Hybrid1 × 300 kW Biomass Boiler,
1 × 300 kW Conventional Boiler
GAS kWh/m2184.7893.84111.53255.29104.2095.07194.82259.61
8Hybrid1 × 300 kW Heat PumpELECT kWh/m245.4038.7337.6541.7496.8061.5962.0982.36
1 × 300 kW Conventional BoilerGAS kWh/m268.3118.7028.99113.839.546.6754.30117.73
Table 5. Comparison between various methods of control.
Table 5. Comparison between various methods of control.
1CTVF—Constant Temperature, Variable FlowCommonly and widely adopted by radiators
2CTVF—Variable Temperature, Constant FlowInexpensive method of control
Commonly and widely implemented
Ignorant of zone internal temperature
Increased risk of overheating
Zones must be zonal controlled according to orientation/facing
3VTVF—Variable Temperature, Variable FlowTakes into account of zone internal temperaturesIncreased cost to implement control for both temperature and flow rate in terms of mechanically and control wiring
4CTCF—Constant Temperature, Constant FlowInexpensive method of controlRequires more energy (especially for fast acting radiators) as it toggles between fully on and fully off

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Fong, J.; Edge, J.; Underwood, C.; Tindale, A.; Potter, S.; Du, H. Application of a New Dynamic Heating System Model Using a Range of Common Control Strategies. Buildings 2016, 6, 23.

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Fong J, Edge J, Underwood C, Tindale A, Potter S, Du H. Application of a New Dynamic Heating System Model Using a Range of Common Control Strategies. Buildings. 2016; 6(2):23.

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Fong, Joshua, Jerry Edge, Chris Underwood, Andy Tindale, Steve Potter, and Hu Du. 2016. "Application of a New Dynamic Heating System Model Using a Range of Common Control Strategies" Buildings 6, no. 2: 23.

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