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Formula 6-1: Qh =⎡⎣k1+k2(Ts)⎤⎦+k3(Tout)+k4(Tout)2 COP=⎡⎣c+c(T)⎤⎦+c(T )+c(Tamb)2 5% o 3×4 9 ded b pum ⎛19 ⎜⎝ Using Figure 6-4, the maximum thermal resistance of the finish floor covering(s) allowable in this situation is R-1.1oF•hr•ft2/Btu. RADIANT WALL PANELS Radiant panels can be integrated into walls and ceilings as well as floors. Several of these configurations are suitable for use with air-to-water heat pumps. The key is ensuring that the radiant panel can deliver design load output while operating at a relatively low water temperature. This favors radiant panels that provide high surface areas relative to their rate of heat delivery. It also favors panels that have low internal thermal resistance between the tubing and the surface area releasing heat to the room. One example is a radiant wall panel constructed as shown in Figure 6-5. q=k(T −T )=15=k(115−70) When finished, this “radiant wall” is indistinguishable from where: q = heat output of the underfloor tube & plate panel (Btu/ hr/ft2) k = value from Figure 6-4 Twa = average water temperature in tubing circuit (oF) Troom = room air temperature (oF) A suggested guideline in evaluating floor coverings for this type of radiant panel is to constrain the average water temperature to no higher than 115oF. This would allow the supply water temperature to be 120oF (assuming a 10oF circuit temperature drop). If this constraint is entered into Formula 6-1, a relationship between panel output, room air temperature and allowed finish floor covering resistance is established. Here’s an example. Assume that a designer has determined thattheradiantfloorneedstorelease15Btu/hr/ft2underdesign load conditions. To achieve good heat pump performance, the designer wants to limit the average water temperature in the panel to 115oF under design load conditions. What is the maximum thermal resistance of the floor coverings? wa room a standard interior wall. Its low thermal mass allows it to 15 respond quicklky =to changing= 0in.t3e3rn3al load conditions or 115−70 zone setback schedules. The rate of heat emission to the room can be estimated using Formula 6-2: Formula 6-2: where: q = heat output of wall panel (Btu/hr/ft2) T = average water temperature in panel (oF) wa q=0.71×(T −T ) wa room T room = room air temperature (oF) 48 q = 0.8 × (Twa − Troom ) V = t (Qheat source − qload ) 500(ΔT) Figure 6-4 0.6 0.5 0.4 0.3 0.2 0.1 0 0 1 2 s 3 amb 4 s asonal h q=k(Twa −Troom) ating cos t=⎢ .95 ⎣ ⎛ $16. 9 ×194. 3.4 provi heat ⎡0 seasonal average COP seasonal heating cost = 0.5 1 1.5 ⎜⎝ MMB2tu⎟⎠ ee 85 ⎞ × R-value of floor covering(s) (oF•hr•ft2/Btu) Figure 6-5 loa 66⎥ d by heat ⎤+⎡0.05× ⎦⎣ 3M pr h MBtu⎞ = backside insulation f pump 7/16" oriented strand board 3. y p 4. ⎟ season ⎠ 194.3× 43.66⎤ = $2,733 3/4" foil faced foam insulation ⎢ 1 ⎥⎦ 6" aluminum heat transfer plate 1/2" drywall ovided by aux elec. eat source 1/2" PEX-AL-PEX tubing (8" tube spacing) $3,274 q=k(Twa −Troom) q=0.8×(Twa −Troom) q=k(Twa −Troom)=15=k(115−70) k = 15 = 0.333 115−70 kPDF Image | Heat Pump Systems 2020
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