Numerical Analysis of Comfort and Energy Performance of Radiant Heat Emission Systems

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Numerical Analysis of Comfort and Energy Performance of Radiant Heat Emission Systems. Fabian Ochs, Mara Magni, Michele Bianchi Janetti, Dietmar Siegele Unit for Energy Efficient Buildings, UIBK z / [m]....3...9 8 7.8 0. 6.7 0 Comsol Conference, 06, Munich.. 3. 3. y / [m]. 0. 0 3 x / [m].6. 0.0.06 Arbeitsbereich Energieeffizientes Bauen

Motivation Recently so-called infrared-heating systems are increasingly discussed as a cost-effective heating system. Relative small areas of typically 0.6 m x. m with high surface temperatures of up to 0 C are used. Definition: With a radiant heating system more than 0 % of heat emission occurs as long-wave radiation (infrared) 0.0.06 Arbeitsbereich Energieeffizientes Bauen

Questions What is the appropriate dimensioning of the radiant system depending on the load of the building? What are the comfort conditions with radiant heating systems and how should they be determined and evaluated? What is the energy performance compared to reference systems such as hydronic heat emission systems e.g. with air-sourced heat pump? Is there a benefit in intermittent operation due to the relative fast response of these heating systems?

Scheme of simple 3D Room Model (shoe-box) Variation of size and position of the radiant heater window fraction envelope quality Comparison with heating demand in case of convective heating Control according to the operative temperature z y x

Simplified Model of a Radiative Heater h = C Δθ n Q tot = Q rad + Q conv = P = U I Q conv = h A (θ θ conv ) Assumption : Q loss θ conv Q rad = σ A e (T T i ) Grey (i.e. diffuse) radiator Homogeneous temperature (J R ) Homogenous emissivity (e) of each surface T i Assumption : Q loss = 0

Thermal Comfort - Operative Temperature Operative Temperature (approximation) θ op = θ rad+θ conv θ rad : radiative Node Operative Temperature (improved approach) θ op = a θ rad + a θ conv a = h C h C + h R here: 0.3 < a < 0. ConveCtive heat transfer coefficient h C =. ((θ conv θ s )/D) / Radiative heat transfer coefficient h R = σ e θ s + θ rad (θ s + θ rad )

Thermal Comfort - Radiant Temperature Asymmetry Asymmetric heating or cooling of a human due to different radiant temperatures of the surrounding surfaces can lead to dis-comfort. The room is divided into two half-rooms for the evaluation of the radiant temperature asymmetry. The temperature differences between the two halfrooms should not exceed certain values. Table: Maximum Radiant Temperature Asymmetry DIN 96- ISO 7730 Glück Warm ceiling 3. K K 8. K Cold wall 8 K 0 K 8. K Cold ceiling 7 K K.3 K Warm wall 9 K 3 K. K

Building Models -Zone * Modell (convective and radiative node) -Zone Model with detailed physical radiation approach Simpliefied Building Model Approaches R rad J C J R R conv J S R comb J a * model starnode model z.b. Dynbil, Matlab/Simulink, Energy+ z.b. EN ISO 3970, TRNSYS, Energy+

Physical Model - Convective Node θ fully mixed ceiling convective θ 6 θ Z C Z C θ C θ θ 3 y J floor Temperature Stratification in a room for different heating situations θ Modell for convective heat transfer (6 surfaces) Remark: Ideally mixed room applies with good approximation for buildings with very good envelope quality (PH). For a more accurate analysis, in addition, a computational flow simulation (CFD) for determining the temperature stratification would be needed.

Models for Radiation Heat Transfer H i R Triangle-Configuration (black body) Star-Configuration Physical Model with Radiosity H (Grey body) n Q ij = σ A i e i e j F ij (T i T j ) Q ir = σ A i e i e R F i (T i T R ) H i = ε i σ T i + ( ε i ) j= F ij H j n Q i = A i (δ ij F ij ) H j j=

Physical Room Model - Radiation ε σ T r H View factors depend only on geometry Not on surface properties. ε 6 σ T 6 r 6 H 6 H r ε σ T Sphere o cube representing a person ε σ T r R 6 R R 3 H 3 r 3 ε 3 σ T 3 H R ij = A i F ij r i = A i ε i ε i r H ε σ T

View factor Determination by means of integration analytically Numerical integration with Comsol Multiphysics F A A A cos cos da da r h A F, 8 arctan ( a / h) ( b / h) ( a / h) ( b / h) b A a

View Factor View factor between heater and sphere in the center of the room depending on the distance (h) to the heater 0. 0. 0. 0.3 0.3 8*6 *3 *. * Sitting person F / [-] 0. 0. 0. 0. 0.0 0 0 0... h / [m]

3D-Model in Comsol (FE-Modell) Determination of view factor from surface to surface 9 x 9 Determination on view factor from sphere in room to the surrounding surfaces 9 per each position (x,y,z) in the room

View Factor Calculation in Comsol Radiosity approach with the irradiation G (here G is the mutual irradiation coming from the other boundaries), the radiosity H and the emissivity e: ( e) G H e T Surface to surface radiation physics, where it is necessary to run one simulation for every view factor which has to be calculated. The COMSOL operators radopd(h up, H down ) and radopu(h up, H down ) are used. Heat Transfer with Surface-to-Surface Radiation physics where surfaces are presented as solid objects. H i Q i ( ei ) e A i i T i

View Factor Calculation in Comsol The emissivity can be a function of wavelength (l) and surface temperature (T). Complex geometries also with obstructions can be considered. However, the hypothesis of diffuse grey surface has to hold i.e. every surface has the absorption coefficient equal to the emissivity coefficient and emissivity and absorptivity are independent of the angle of emission or absorption, respectively.

Positionen and Size of Radiant Heater Position Ceiling Floor Side wall Rear wall Size m² (Small) Medium Large Room Dimensions: L x B x H [m] 8 x 6 x.7 Window fraction 30 % and 60 %

Matrix of investigated cases Size of the heater Rear wall (3) Position of the heater Floor () Ceiling (6) Side wall ( or ) Small (m x m) X X X Medium 0% wall area X X X X Large 90% wall area X X X

STEADY STATE: ceiling small W30 centered Operative Temperature = 0 C Qdot_tot = 06.77 W Temperature Heater =.99 C Radiative exchange Heater = 67.78 %. J rad / [ C] 0.99 0.. 9.99 0 3. 7.67 9.6 7.67 9. y / [m] 3 9. 0 0.0 0.7 0.03 8.. 8-0.06-6 - - 0 6 7. 0. 0 3 6 7 8 x / [m] 9.99 0 0.0 0.0 0.03 0.0 0.0 0.06 0.07 0.08 0.09

STEADY STATE: ceiling medium W30 centered Operative Temperature = 0 C Qdot_tot = 0.0 W Temperature Heater =.8 C Radiative exchange Heater = 8.0 %. J rad / [ C] 0.8 0.. 0 9.8 3. 7. 9. 7. 9. y / [m] 3 9. 0 9.9 0.0 9.9 8.. 8-9.93-6 - - 0 6 7. 0. 0 3 6 7 8 x / [m] 9.9 0 0.0 0. 0. 0. 0.

STEADY STATE: ceiling large W30 centered Operative Temperature = 0 C Qdot_tot = 0. W Temperature Heater = 0.89 C Radiative exchange Heater = 8.8 %. J rad / [ C] 0 0.89 0.. 9.8 0 3. 7.8 9.3 7.7 9. y / [m] 3 9. 0 9.9 0.0 9.9 8.. 8-9.93-6 - - 0 6 0. 0 3 6 7 8 x / [m] 7. 0 0.0 0. 0. 0. 0.

STEADY STATE: sidewall small W30 centered Operative Temperature = 0 C Qdot_tot = 06.97 W Temperature Heater = 39.8 C Radiative exchange Heater = 7.70 %. J rad / [ C] 0 0.08 0.. 0 3. 7.63 9.63 7.7 9.96 9. y / [m] 3 9. 0 0.03 0.0 39.8 8.. 8-0.0-6 - - 0 6 7. 0. 0 3 6 7 8 x / [m] 9.98 0 0.0 0.0 0.06 0.08 0. 0. 0. 0.6

Transient Simulations 6 surface temperatures 8 surface temperatures 60 3 3 6 7 8 6 6 7 8 9 9 0 J / [ C] 0 J / [ C] 3 0 30 8 0 0 0 00 0 00 0 300 30 time / [day] 6 0 0 00 0 00 0 300 30 time / [day] Example of Surface temperature with (left) radiative heater and (right) convective heating

HD / [kwh/(m² a)] Convective vs. Radiative Heating for Different Positions and Sizes of the Radiative Heater.0 0. 0.0 9. 9.0 8. For small radiative heating surfaces local comfort can be provided with leads to minor reduction of the heating demand (ca. % for wall and 0 % for ceiling mounted systems (remark: violation of the comfort conditions with regard to the maximum radiant temperature asymmetry) 8.0 w\ C w\ small ceiling w\ small wall w\ large floor w\ large ceiling Large radiant surfaces have higher heating demand than convective heating Innsbruck, 60 m³/h with MVHR

HD / [kwh/(m² a)] reduction / [-] Energetically effective Air Exchange Rate Heating demand (HD) for the small radiative heater on the ceiling (R C) and wall (R W) and reduction with respect to convective heating (C) depending on the energetically effective air exchange rate n eff = n (-h) + n inf 0 8 6 C R C R W 0. 0. 0.0 0.08 0.06 0.0 0.0 Remark: With small radiant heater the radiant temperature asymmetry can exceed the limit according to ISO 3370 0 0 0 energetically effective air exchange rate / [m³/h] 0.00

Conclusions Radiant vs. Convective Heating Radiant Heaters increase the radiant, i.e. surface temperature Allow to decrease the convective temperature for the same comfort conditions (operative temperature) Hence, there are with radiant heaters (slightly) increased transmission losses (slightly) decreased ventilation losses For the same temporal and spatial comfort, no significant differences between a predominantly convective heat emission system and one which emits predominantly longwave radiation can be determined within the model accuracy.

Conclusion - Local Comfort If comfort is only defined for the occupied space, i.e. traffic area (in the same way as in case of ventilation on demand indoor air quality is defined only during presence i.e. there is no loss of comfort with regard to the temporal and local presence of the user), a low energy saving can be achieved without loss of comfort (i.e. with local comfort). It must be noted that the potential to create thermal comfort only locally is greater for small (and consequently hot) areas while however, the radiant temperature asymmetry in this case can even exceed the limit defined in ISO 7730.

Conclusion Building Modell In order to compute the differences of a heat emission system, which is predominantly convective or predominantly radiative with sufficient accuracy, a building model with a detailed calculation of the radiation exchange (between each of the surrounding areas, as well as between the surrounding surfaces and a sphere that is used for calculating the operative temperature) is required. With such a model, these effects can be figured out more precisely than with a two-star or star node model, as usually used for building simulations. The assumption of an ideal mixing of air is acceptable in rooms with very good insulation level and mechanical ventilation with heat recovery, however, it does not apply in case of radiative ceiling and/or ventilation without heat recovery. A computational flow simulation (CFD) for determining the temperature stratification would be required additionally for a more accurate analysis.

Outlook A) Dimensioning Tool B) Complex Geometries C) Coupled CFD and Radation Exchange Model

Acknowledgements IFI Institut für Infrarotwärme GmbH initiated this work. The authors thank IFI Institut für Infrarotwärme GmbH for this initiative and for their support. For part of this work financial support was provided by the Austrian research funding association (FFG) under the scope of Innovationscheck Plus. Thanks.

STEADY STATE: ceiling small W30 centered Operative Temperature = 0 C Qdot_tot = 06.77 W Temperature Heater =.99 C Radiative exchange Heater = 67.78 %. J rad / [ C] 0.99 0.. 9.99 0 3. 7.67 9.6 7.67 9. y / [m] 3 9. 0 0.0 0.7 0.03 8.. 8-0.06-6 - - 0 6 7. 0. 0 3 6 7 8 x / [m] 9.99 0 0.0 0.0 0.03 0.0 0.0 0.06 0.07 0.08 0.09

STEADY STATE: ceiling medium W30 centered Operative Temperature = 0 C Qdot_tot = 0.0 W Temperature Heater =.8 C Radiative exchange Heater = 8.0 %. J rad / [ C] 0.8 0.. 0 9.8 3. 7. 9. 7. 9. y / [m] 3 9. 0 9.9 0.0 9.9 8.. 8-9.93-6 - - 0 6 7. 0. 0 3 6 7 8 x / [m] 9.9 0 0.0 0. 0. 0. 0.

STEADY STATE: ceiling large W30 centered Operative Temperature = 0 C Qdot_tot = 0. W Temperature Heater = 0.89 C Radiative exchange Heater = 8.8 %. J rad / [ C] 0 0.89 0.. 9.8 0 3. 7.8 9.3 7.7 9. y / [m] 3 9. 0 9.9 0.0 9.9 8.. 8-9.93-6 - - 0 6 0. 0 3 6 7 8 x / [m] 7. 0 0.0 0. 0. 0. 0.

STEADY STATE: ceiling small W30 centered Operative Temperature = C Qdot_tot = 7.7 W Temperature Heater = 6.7 C Radiative exchange Heater = 68.3 % 3. J rad / [ C] 0 6.7...99 9.9.6 9.9. 3. y / [m] 3. 0.0.8.0 0.. 0 -.07-6 - - 0 6 9. 0. 0 3 6 7 8 x / [m].99.0.0.03.0.0.06.07.08.09

STEADY STATE: ceiling medium W30 centered Operative Temperature = C Qdot_tot =.8 W Temperature Heater = 3.7 C Radiative exchange Heater = 8. % 3. J rad / [ C] 0 3.7...8 3. 9.3.7 9.3. y / [m] 3. 0.90.0.90 0.. 0 -.9 0. 0 3 6 7 8 x / [m] -6 - - 0 6 9..9.0....

STEADY STATE: ceiling large W30 centered Operative Temperature = C Qdot_tot = 6.06 W Temperature Heater =.96 C Radiative exchange Heater = 8.93 % 3. J rad / [ C] 0.96...8 3. 9.38.0 9.38. y / [m] 3. 0.93.0.9 0.. 0 -.93-6 - - 0 6 0. 0 3 6 7 8 x / [m] 9..0....

STEADY STATE: floor large W30 centered Operative Temperature = 0 C Qdot_tot = 0.6 W Temperature Heater = 0.7 C Radiative exchange Heater = 68.99 %. J rad / [ C] 0 0.0 0.. 0 3. 7.7 9. 7.7 9.83 9. y / [m] 3 9. 0 9.9 0.7 9.9 8.. 8-9.9 0. 0 3 6 7 8 x / [m] -6 - - 0 6 7. 0 0.0 0.0 0.06 0.08 0. 0. 0. 0.6 0.8

STEADY STATE: floor large W30 centered Operative Temperature = C Qdot_tot = 6.3 W Temperature Heater =.77 C Radiative exchange Heater = 68.9 % 3. J rad / [ C] 0.0.. 3. 9.38.8 9.38.8. y / [m] 3. 0.9.77.9 0.. 0 -.93 0. 0 3 6 7 8 x / [m] -6 - - 0 6 9..98.0.0.06.08....6.8

STEADY STATE: rear wall small W30 centered Operative Temperature = 0 C Qdot_tot = 07.06 W Temperature Heater = 39.8 C Radiative exchange Heater = 7.77 %. J rad / [ C] 0 0.07 0.. 0 3. 7.68 9.6 7.68 9. y / [m] 3 9. 0 0.03 0.06 0.03 8.. 9.96 8-39.8 0. 0 3 6 7 8 x / [m] -6 - - 0 6 7. 9.98 0 0.0 0.0 0.06 0.08 0. 0. 0. 0.6

STEADY STATE: sidewall small W30 centered Operative Temperature = 0 C Qdot_tot = 06.97 W Temperature Heater = 39.8 C Radiative exchange Heater = 7.70 %. J rad / [ C] 0 0.08 0.. 0 3. 7.63 9.63 7.7 9.96 9. y / [m] 3 9. 0 0.03 0.0 39.8 8.. 8-0.0-6 - - 0 6 7. 0. 0 3 6 7 8 x / [m] 9.98 0 0.0 0.0 0.06 0.08 0. 0. 0. 0.6

STEADY STATE: sidewall large W30 centered Operative Temperature = 0 C Qdot_tot = 06.77 W Temperature Heater =.3 C Radiative exchange Heater = 70..6 %. J rad / [ C] 0 0.09 0.. 0 3. 7.6 9.66 7.7 9.9 9. y / [m] 3 9. 0 0.03 0.07.3 8.. 8-0.07 0. 0 3 6 7 8 x / [m] -6 - - 0 6 7. 0.0 0. 0. 0. 0. 0.3 0.3

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