Kan behovsstyrt ventilasjon erstatte lokal varme? Axel Cablé, SINTEF Seminar
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1 Kan behovsstyrt ventilasjon erstatte lokal varme? Axel Cablé, SINTEF Seminar
2 Kan behovsstyrt ventilasjon erstatte lokal varme? Principles Challenges VABAT Project 2
3 Principles Increased envelope performances + Low heating demand 3
4 Principles Increased envelope performances + Low heating demand - Indoor air quality Overheating 4
5 Principles Increased envelope performances + Low heating demand - Indoor air quality Overheating Energy brought by the ventilation air exclusively 5
6 Heating with air: historical perspective First used in the 70s: High heating demand High temperature blowing Poor indoor climate: Radiative assymetry Stratification Carbonization of particles 6
7 Heating with air: historical perspective First used in the 70s: High heating demand High temperature blowing Poor indoor climate: Radiative assymetry Stratification Carbonization of particles Bad reputation 7
8 Heating with air: nowadays Lower heating demand: Low ΔT, hygienic Q Low thermal inertia of air Temperature controlled DCV Suited for refurbishment Is it possible? Indoor climate? 8
9 Supply temperature required (Wigenstad et al., 2012) Example 80m 2 apartment Outside design T: -20 C Heating demand (NS 3700): Passiv: 17 W/m 2 ACR: ~1,6 m 3 /h/m 2 Required T supply : ~50 C 9
10 Supply temperature required (Wigenstad et al., 2012) Example 80m 2 apartment Outside design T: -20 C Heating demand (NS 3700): Passiv: 17 W/m 2 ACR: ~1,6 m 3 /h/m 2 Required T supply : ~50 C Schools: ACR: ~8 m 3 /h/m 2 Office: ACR: ~6 m 3 /h/m 2 Required T supply : ~26-28 C 10
11 Economic impact of Indoor Climate Operating expense in a typical office building (REHVA Guidebook 17, 2012) Building related cost Salary and employee related cost Miscellaneous cost 80% Thermal comfort/iaq is the priority! 11
12 Ventilation efficiency Contaminant removal effectiveness (Sandberg, 1981) Temperature efficiency (Awbi et Gan, 1993) CRE = C out C supply C room C supply ε T = T out T supply T room T supply 12
13 Thermal comfort EN15251 / ISO7730 : Operative temperature heating: Top = 21,5 C Operative temperature cooling: Top = 25,5 C Maximum air velocity heating: Vair < 0,15 m/s Maximum air velocity cooling: Vair < 0,25 m/s Thermal stratification < 4,2 C between 0,1 and 1,7m 13
14 Overheating Løvåshagen, Bergen: percentage of dissatisfied by overheating (Berge&Mathisen, 2013) 14
15 VABAT Project ( ) Methods Low energy buildings Is the system relevant? - Thermal comfort - Ventilation efficiency - Airflow patterns Energy refurbishment Measurements (climate chamber) CFD simulations 15
16 Test chamber Supply 2,60m Exhaust Dummy 3,08m 4,26m 16
17 Sensors ~180 sensors Occupied zone: 27 stations Boundary conditions (walls, supply, exhaust) 17
18 Tsupply( C) Test cases Steady-state Heating, Cooling 0, 1 or 2 occupants Tested cases P = 8 W/m2 P= 18 W/m2 P =1 W/m ACH Heating Cooling 18
19 CFD simulations STAR-CCM+ Turbulence modelling Air diffuser modelling Boundary conditions = experiments 19
20 Heating T supply = 31,2 C ACR = 1,6 vol/h Air velocity (m/s) CFD EXP The warm air jet reaches the opposite wall 20
21 Heating T supply = 31,2 C ACR = 1,6 vol/h Air velocity (m/s) CFD The warm air jet reaches the opposite wall EXP V air < 0,15 m/s No discomfort by draught 21
22 Heating T supply = 31,2 C ACR = 1,6 vol/h Air velocity (m/s) CFD The warm air jet reaches the opposite wall Short-circuiting? Thermal stratification? EXP V air < 0,15 m/s No discomfort by draught 22
23 Ventilation efficiency CRE close to 1 ε T > = 1 Good ventilation efficiency 23
24 Influence of heat sources Med Moy Max Min 24
25 Influence of heat sources Med Moy Max Min Internal heat sources beneficial 25
26 PMV Predicted Mean Vote 0,00-0,10-0,20-0,30-0,40-0,50-0,60-0,08-0,13-0,11-0,19-0,24-0,25-0,34-0,49 C0+ C1- C2- C2+ Experimental results Cat. I EN Cat. II EN Good values of PMV (EN NS 15251) 26
27 Z (m) Thermal stratification 2 1,8 1,6 20,921,2 21,4 1,4 1,2 20,0 20,7 21,2 1 0,8 0,6 0,4 0,2 19,2 20,0 20,8 0 19,0 19,5 20,0 20,5 21,0 21,5 22,0 22,5 23,0 T air ( C) C0+ C1- C2- C2+ C0+ CFD C1- CFD C2- CFD C2+ CFD T max = 1,7 C < 4,2 C No discomfort by thermal stratification 27
28 Cooling ACR = 3,5 Negative buoyancy forces Drop of the jet inside of the occupied zone! ACR = 1,6 0 ACR = 1 28
29 Cooling T supply = 21,5 C T supply = 17,0 C T supply = 14,9 C Deflexion of the air jet Tridimensionnal airflow Negative influence of the heat sources on the airflow 29
30 Can DCV replace local heating? Yes! If: Low heating demand (envelope, climate) Educational/office buildings/dwellings Well functionning DCV Refurbishment Overheating (active air diffuser) Norway: more measurements needed! 30
31 Perspectives ForKlima (Forenklet behovsstyrt klimatisering av kontorbygg med svært lavt oppvarmingsbehov) GK miljøhuset 31
32 Perspectives Noise level Distribution losses in ventilation ducts Dry air in winter 32
33 Thank you! Questions? 33
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