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<DIV>Mike,</DIV>
<DIV>Yes, that does help regarding the supply air temperature reset question. Does anyone know whether these addenda are approved by USGBC? The LEED reference guide specifically refers to A90.1 "without amendments" which is an interesting choice of words, but it appears that some of the addenda were driven by USGBC. My understanding is that someone has submitted a CIR asking for clarification, but I haven't seen a response yet.</DIV>
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<DIV>Regarding the chilled water supply temperature reset, I will plan on submitting a continuous maintenance proposal taking into account some of the feedback received from 90.1ecb.</DIV>
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<DIV>Also wanted to ask what the intent was for how the reset sequence is implemented. If you are using chilled water from a central loop in your proposed design where reset temperature is not provided, the reset would need to occur at the building through pump/valve/mixing control schemes. If your building includes chilled water generation, the reset could occur at the source. For the baseline building, A90.1 requires you to model chillers. While previous correspondence indicated that the intent was to use minimum efficiency chiller equipment as the baseline comparison, this seems as though there is a lot of potential for unsupportable variations in cooling costs between the baseline and proposed design. If the model is using purchased chilled water rates in the proposed design and electricity rates in the baseline model, you could see cost penalties or savings that are unwarranted depending on how the purchased chilled water rate is structured. The best comparison would to be to have both the baseline and proposed models use the same chilled water source. </DIV>
<DIV>Thanks,</DIV>
<DIV>Bill Talbert, AEI</DIV>
<DIV> </DIV>
<DIV><BR>>>> "Michael Rosenberg" <Michael.Rosenberg@state.or.us> 3/15/2007 11:28 AM >>><BR>Bill,<BR><BR>I will take a crack at these. In general Appendix G has tried to eliminate options in modeling the baseline building. This is so that users can not try various baseline options and choose the one that shows the most savings. So when options are available in other parts of the Standard, G has chosen what seems to make the most sense for use in the baseline. That sometimes causes problems like the one you brought up. Maybe we need to propose some modification language that states that if CW reset results in unmet dehumidification loads greater than the proposed building, the reset temperature needs to be dropped lower (but not less than proposed), until the loads are equal. Do you want to try putting together a continuos maintenance proposal for this?<BR><BR>The supply air reset issue has already been addressed in Addendum A. Now that sections states;<BR>" The air temperature for cooling shall be reset higher by 5°F (2.3°C) under the minimum cooling load conditions". <BR>Non of the sizing language remains. This was published in the 90.1 interim addenda release, and will be in the 2007 version of the Standard.<BR><BR>Hope that helped<BR><BR>Mike<BR><BR><BR>Michael Rosenberg<BR>Oregon Department of Energy<BR>625 Marion St. N.E.<BR>Salem, OR 97301-3742<BR>Phone : (503) 373-7809<BR>Fax: (503) 373-7806<BR><BR>>>> "Bill Talbert" <btalbert@aeieng.com> 03/15/07 08:42AM >>><BR>All,<BR>I have a question regarding ASHRAE 90.1-2004 Section G3.1.3.8 - Chilled Water Supply Temperature Reset. Can anyone offer some background as to the intent of this section? Appendix G does not appear to allow any exceptions and requires chilled water supply temperature reset based on outdoor air drybulb (CWT = 44 to 54 deg F during outdoor drybulb range of 80 to 60 deg F).The equivalent prescriptive path section (6.5.4.3) exempts reset controls when VFD pump control is used or if reset controls would cause heating, cooling, humidifying, or dehumidifying loads to not be met and also allows reset based on return water temperature rather than outdoor drybulb only. It appears that if you are designing a space with sensitive humidity and/or low space temperature requirements, supply temperature reset could result in space conditions not being met. What was the thinking in eliminating the exceptions and the return water temperature option and were the full range of potential thermal comfort requirements considered? Is the intent that if you are trying to serve an Operating Room with a VAV/Chilled water system and you need 68 deg F/50% RH at the space, a supplemental DX cooling coil or dehumidification system is preferred?<BR><BR>Also Section G3.1.3.12 - Supply Air Temperature Reset indicates that "supply air temperature shall be reset based on zone demand from the design temperature difference to a 10 deg F temperature difference under minimum load conditions" and that "design air flow rates shall be sized for the reset supply air temperature, i.e., a 10 deg F temperature difference." This appears to require design air flows to be calculated based on a 10 deg F temperature difference, effectively doubling air flow rates from the standard 20 deg F temperature difference. If you only need to reset supply air temperature down to a 10 deg F delta during minimum load conditions, why would you size the system based on a 10 deg F delta? What is the intent of this requirement? Doesn't this result in larger air side systems, i.e. more materials and larger fans?<BR><BR>I am curious how others are dealing with these requirements.<BR><BR>Thanks,<BR>Bill Talbert, AEI<BR><BR><BR><BR>=========================================================================You received this e-mail because you are subscribed to the 901ECB@GARD.COM <BR>mailing list. To unsubscribe from this mailing list send blank a message to<BR>901ecb-unsubscribe@gard.com<BR><BR>=========================================================================You received this e-mail because you are subscribed to the 901ECB@GARD.COM<BR>mailing list. To unsubscribe from this mailing list send blank a message to<BR>901ecb-unsubscribe@gard.com<BR><BR></DIV><PRE>
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