<html><head><style type="text/css"><!-- DIV {margin:0px;} --></style></head><body><div style="font-family:times new roman,new york,times,serif;font-size:10pt"><div>Michael:<br><br>Thank you very much for the offer. Next time I am auditing a site with a York, I will be sure to contact you.<br><br>Paul Diglio<br></div><div style="font-family: times new roman,new york,times,serif; font-size: 10pt;"><br><div style="font-family: times new roman,new york,times,serif; font-size: 12pt;"><font face="Tahoma" size="2"><hr size="1"><b><span style="font-weight: bold;">From:</span></b> "Michael.Hupel@jci.com" <Michael.Hupel@jci.com><br><b><span style="font-weight: bold;">To:</span></b> Carol Gardner <cmg750@gmail.com><br><b><span style="font-weight: bold;">Cc:</span></b> "equest-users@lists.onebuilding.org" <equest-users@lists.onebuilding.org>; equest-users-bounces@lists.onebuilding.org<br><b><span style="font-weight: bold;">Sent:</span></b>
Wed, November 3, 2010 2:07:37 PM<br><b><span style="font-weight: bold;">Subject:</span></b> Re: [Equest-users] Chiller Curves (oh boy!)<br></font><br>
<br><font face="sans-serif" size="2">As the OEM rep for YORK chillers I am
more than willing to provide NPLV/IPLV and other part loading efficiency
data. Can even provide a comparison to other chiller manufacturers
or some of the options such as VSDs or hot gas by-pass options. </font>
<br>
<br><font face="sans-serif" size="2">Chillers are normally specified to supply
cooling for the hottest day of the year and yes add a factor for potential
future load such as increased occupancy, equipment etc. </font>
<br>
<br><font face="sans-serif" size="2"><br>
<br>
<br>
Michael Hupel, </font><font face="sans-serif" size="1">B.Tech., LEED AP</font><font face="sans-serif" size="2"><br>
Account Executive<br>
Project & Business Development<br>
Johnson Controls L. P.<br>
3070 Mainway Drive <br>
Burlington, ON L7N 3X1<br>
(905) 335-3325 ext. 237<br>
(905) 730-9642 cell</font>
<br>
<br>
<br>
<table width="100%">
<tbody><tr valign="top">
<td><font color="#5f5f5f" face="sans-serif" size="1">From:</font>
</td><td><font face="sans-serif" size="1">Carol Gardner <cmg750@gmail.com></font>
</td></tr><tr valign="top">
<td><font color="#5f5f5f" face="sans-serif" size="1">To:</font>
</td><td><font face="sans-serif" size="1">"John T. Forester" <JohnTF@bvhis.com></font>
</td></tr><tr>
<td valign="top"><font color="#5f5f5f" face="sans-serif" size="1">Cc:</font>
</td><td><font face="sans-serif" size="1">"equest-users@lists.onebuilding.org"
<equest-users@lists.onebuilding.org></font>
</td></tr><tr valign="top">
<td><font color="#5f5f5f" face="sans-serif" size="1">Date:</font>
</td><td><font face="sans-serif" size="1">11/03/2010 01:54 PM</font>
</td></tr><tr valign="top">
<td><font color="#5f5f5f" face="sans-serif" size="1">Subject:</font>
</td><td><font face="sans-serif" size="1">Re: [Equest-users] Chiller Curves (oh
boy!)</font></td></tr></tbody></table>
<br>
<hr noshade="noshade">
<br>
<br>
<br><font size="3">I agree with you, John, but have a couple of other thoughts
to add. The first is I have not met a mechanical engineer that does not
select a chiller that is capable of supplying all loads. In fact, they
generally oversize a bit to accommodate possible future loads. The only
piece of equipment I have ever seen selected at over 100% was a VRV system
and that is because they actually work better at 120% loading. The second
is that you can generally get a catalog from a manufacturer to have on
your shelf that has technical information like how the chiller unloads
based on temperatures and what the efficiency is at part load so you can
look up the chiller you need info for and not need to bother the ME or
the vendor. If you can't get/don't want a hard copy, most of this info
is on line, just look for technical specifications.<br>
<br>
Best,<br>
<br>
Carol<br>
</font>
<br><font size="3">On Wed, Nov 3, 2010 at 9:48 AM, John T. Forester <</font><a rel="nofollow" ymailto="mailto:JohnTF@bvhis.com" target="_blank" href="mailto:JohnTF@bvhis.com"><font color="blue" size="3"><u>JohnTF@bvhis.com</u></font></a><font size="3">>
wrote:</font>
<br><font color="#000080" face="Arial" size="2">Nick,</font>
<p><font color="#000080" face="Arial" size="2"> </font>
</p><p><font color="#000080" face="Arial" size="2">I think you’re on the right
track. Below are some of my thoughts on your conclusions. I
hope the modeling community will set me straight if I’m wrong here.</font>
</p><p><font color="#000080" face="Arial" size="2"> </font>
<br><font face="sans-serif" size="2">1. </font><font color="#000080" face="Arial" size="2">Getting
multiple performance runs from vendors that show part-load performance
independent of the CW and CHW temps can often be challenging. Adding
the “maximum capability” task to that for each of the conditions requires
a pretty detailed understanding of the selection software. I’d say
if you can get PLR data for 3-4 different CHW temps while holding the CW
temps constant at 85, 75, 65 (and sometimes lower) – you’re ahead of
most modelers. Working with the Mechanical Design Engineer and the
vendor together has been successful for me in the past.</font>
<br><font face="sans-serif" size="2">2. </font><font color="#000080" face="Arial" size="2">Defining
the chiller capabilities at the “maximum” may only come into play if
you expect your model to overload the chiller above the specified design
capacity (I’m thinking building additions or process loads). At this point,
this data (or knowing what the default eQuest curves do in that range)
would be useful. Depending on your project, the time spent on developing
curves for PLR >1.0 may not be justified.</font>
<br><font face="sans-serif" size="2">3. </font><font color="#000080" face="Arial" size="2">If
you don’t have “max” data and don’t want eQuest to assume performance
at a part-load ratio >1.0, you can set the DESIGN-PLR to 1.0.</font>
<br><font face="sans-serif" size="2">4. </font><font color="#000080" face="Arial" size="2">Either
way, you want your curves to be normalized at whatever condition you specify
(Design or Rated) and you want to enter those values on the Basic Specifications
tab.</font>
</p><p><font color="#000080" face="Arial" size="2"> </font>
</p><p><font color="#000080" face="Arial" size="2">John</font>
</p><p><font color="#000080" face="Arial" size="2"> </font>
</p><p><font color="#808080" face="Arial" size="1">John T. Forester, P.E., LEED
AP, Mechanical Design Engineer </font><font color="#0000a1" face="Arial" size="1"><b>I
BVH Integrated Services I</b></font><font face="Arial" size="1"><b> </b></font><font color="#808080" face="Arial" size="1">617.658.9008
tel </font><font color="#0000a1" face="Arial" size="1"><b>I</b></font><font color="#808080" face="Arial" size="1"><b>
</b>617.244.3753 fax</font><font color="#0000a1" face="Arial" size="1"> <b>I</b></font><font color="#808080" face="Arial" size="1"><b>
</b>One Gateway Center Suite 506, Newton MA 02458 </font><font color="#0000a1" face="Arial" size="1"><b>I
</b></font><a rel="nofollow" target="_blank" href="http://www.bvhis.com/"><font color="blue" face="Arial" size="1"><b><u>www.bvhis.com</u></b></font></a><font color="#0000a1" face="Arial" size="1"><b> I
Hartford ● New Haven ● Boston</b></font>
</p><div align="center">
<p><font face="Times New Roman" size="3">size=2 width="100%" align=center
tabindex=-1> </font></p></div>
<p><font face="Tahoma" size="2"><b>From:</b> Nick Caton [mailto:</font><a rel="nofollow" ymailto="mailto:ncaton@smithboucher.com" target="_blank" href="mailto:ncaton@smithboucher.com"><font color="blue" face="Tahoma" size="2"><u>ncaton@smithboucher.com</u></font></a><font face="Tahoma" size="2">]
<b><br>
Sent:</b> Wednesday, November 03, 2010 12:06 PM<b><br>
To:</b> John T. Forester; </font><a rel="nofollow" ymailto="mailto:equest-users@lists.onebuilding.org" target="_blank" href="mailto:equest-users@lists.onebuilding.org"><font color="blue" face="Tahoma" size="2"><u>equest-users@lists.onebuilding.org</u></font></a>
</p><p><font face="Tahoma" size="2"><b><br>
Subject:</b> RE: [Equest-users] Chiller Curves (oh boy!)</font>
</p><p><font face="Times New Roman" size="3"> </font>
</p><p><font color="#004080" face="Calibri" size="2">John,</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">The design/max ratio is exactly
what I’m discussing below when I say “DESIGN-PLR ratio,” so we’re definitely
in the same ballpark =).</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">I’d like to apply/paraphrase
your advice to a few conditions to be sure I’m getting it correctly:
</font>
</p><p><font color="#004080" face="Calibri" size="2">-</font><font color="#004080" face="Times New Roman" size="1">
</font><font color="#004080" face="Calibri" size="2">If we create all 3 custom
curves, and normalize each to a point at maximum (not design) capacity,
then the design-to-max ratio (DESIGN-PLR) should be set to 1.00.</font>
</p><p><font color="#004080" face="Calibri" size="2">-</font><font color="#004080" face="Times New Roman" size="1">
</font><font color="#004080" face="Calibri" size="2">If we create <u>only</u>
the part load efficiency curve (EIR-FPLR or EIR-FPLR&dT), and wish
to use the library defaults for EIR-FT and CAP-FT, then we should normalize
this curve’s data points to ARI conditions (as that’s what the library
curves are normalized to, per James’s email – I think I’ve read this
somewhere also), specify an ARI capacity, EIR and conditions on the
basic specifications tab, and enter a DESIGN-PLR of [ARI capacity/maximum
capacity (for the same conditions)].</font>
</p><p><font color="#004080" face="Calibri" size="2">-</font><font color="#004080" face="Times New Roman" size="1">
</font><font color="#004080" face="Calibri" size="2">If we create all 3 custom
curves, and try to normalize each to either ARI or design conditions, then
we should specify capacity, EIR, CHWT, CWT and condenser GPM corresponding
to either the ARI or design conditions of that normalizing point.
In that case, we also specify a DESIGN-PLR using either the ARI or design
capacity divided by the maximum capacity for the same conditions.</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2"><u>Profound (to me) Conclusion</u>:
In <u>No</u> instance should we <u>Ever</u> attempt creating custom curves
and NOT have at least one run from our manufacturer telling us what the
maximum (not design) capacity is for the normalizing point. This
conclusion would only apply to centrifugal chillers only.</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">Does this all sound right?</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">~Nick</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">James, </font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">Yeah, if all the part load
data you received held the same CHWT and CWT equal, you might be able to
make your part-load curve if it could have been a quadratic EIR-FPLR curve
(like a reciprocating chiller), but not a bi-quadratic EIR-FPLR&dT
(as with my centrifugal VSD chiller). You definitely could not approach
generating custom EIR-FT or CAP-FT curves without varying condenser and
chilled water temps. That exact issue happened to me the first few
times I tried to reign my chiller reps in =). </font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">This time, I convinced my
rep to give me multiple part load runs holding the CHWT constant and varying
the CWT incrementally. This let me build the bi-quadratic EIR-FPLR&dT
curve as I had at least three different dT’s represented in my part load
data points. I plotted the 3D curve in excel to check my work and
darned if the generated coefficients seem to be really accurate =)!
It’s currently looking like a bittersweet revelation however –
the library curve for a water-cooled centrifugal VSD chiller (see attached
visualization) seems a LOT more generous (more efficient) at low part loads
than the one I’ve generated which matches my rep’s data… I might
share a visual of my custom curve for comparison once I’m dead-sure it’s
accurate – I’m trying to clarify a few things with my rep right now.</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">~Nick</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p>
</p><p><font color="#37605e" face="Stylus BT" size="2"><b> </b></font>
</p><p><font color="#37605e" face="Stylus BT" size="2"><b>NICK CATON, E.I.T.</b></font>
</p><p><font color="#bfbf00" face="Calibri" size="1">PROJECT ENGINEER</font>
</p><p><font color="#37605e" face="Calibri" size="2">25501 west valley parkway</font>
</p><p><font color="#37605e" face="Calibri" size="2">olathe ks 66061</font>
</p><p><font color="#37605e" face="Calibri" size="2">direct 913 344.0036</font>
</p><p><font color="#37605e" face="Calibri" size="2">fax 913 345.0617</font>
</p><p><font color="#37605e" face="Calibri" size="2"><i>Check out our new web-site
@ </i></font><a rel="nofollow" target="_blank" href="http://www.smithboucher.com/"><font color="blue" face="Calibri" size="2"><u>www.smithboucher.com</u></font></a><font color="blue" face="Calibri" size="2"><u>
</u></font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font face="Tahoma" size="2"><b>From:</b> John T. Forester [mailto:</font><a rel="nofollow" ymailto="mailto:JohnTF@BVHis.com" target="_blank" href="mailto:JohnTF@BVHis.com"><font color="blue" face="Tahoma" size="2"><u>JohnTF@BVHis.com</u></font></a><font face="Tahoma" size="2">]
<b><br>
Sent:</b> Wednesday, November 03, 2010 10:29 AM<b><br>
To:</b> Nick Caton; </font><a rel="nofollow" ymailto="mailto:equest-users@lists.onebuilding.org" target="_blank" href="mailto:equest-users@lists.onebuilding.org"><font color="blue" face="Tahoma" size="2"><u>equest-users@lists.onebuilding.org</u></font></a><font face="Tahoma" size="2"><b><br>
Subject:</b> RE: [Equest-users] Chiller Curves (oh boy!)</font>
</p><p><font face="Times New Roman" size="3"> </font>
</p><p><font color="#000080" face="Arial" size="2">Nick,</font>
</p><p><font color="#000080" face="Arial" size="2"> </font>
</p><p><font color="#000080" face="Arial" size="2">When defining a centrifugal
chiller in eQuest, one of the items on the Basic Specifications tab under
the Design vs. Rated Conditions is a Design/Max Cap ratio. By default,
this is 92% for a water cooled unit. I believe this gets at the discussion
in the help pages that talks about maximum capacity versus design capacity
and how the chiller vendor will spec a piece of equipment. Typically,
vendors don’t often get asked (or provide) what the “Maximum” capacity
of a spec’d unit is. Therefore the performance data that they provide
are at “design conditions.”</font>
</p><p><font color="#000080" face="Arial" size="2"> </font>
</p><p><font color="#000080" face="Arial" size="2">If you change the chiller type
to a reciprocating chiller, this “Design/Max Cap” ratio is disabled and
the default specified condition changes from “Design Conditions” to “Rated
Conditions.” This suggests that there is little “extra” capacity
when a selection is done for that type of chiller.</font>
</p><p><font color="#000080" face="Arial" size="2"> </font>
</p><p><font color="#000080" face="Arial" size="2">If you do get “maximum capacity”
data and create curves from that data, you will want to change the Design/Max
Cap ratio to 1.0 so eQuest knows that there isn’t any spare capacity at
the chiller. Also if the data points you are using to normalize your
curves are different than the design conditions for your energy model,
you will want to change the “Chiller Specified at” value to “Rated Conditions”
and enter the rated conditions for CHW temp, CW temp and CW gpm/ton to
match your normalized curves.</font>
</p><p><font color="#000080" face="Arial" size="2"> </font>
</p><p><font color="#000080" face="Arial" size="2">Hope this helps,</font>
</p><p><font color="#000080" face="Arial" size="2"> </font>
</p><p><font color="#000080" face="Arial" size="2">John</font>
</p><p><font color="#000080" face="Arial" size="2"> </font>
</p><p><font color="#808080" face="Arial" size="1">John T. Forester, P.E., LEED
AP, Mechanical Design Engineer </font><font color="#0000a1" face="Arial" size="1"><b>I
BVH Integrated Services I</b></font><font face="Arial" size="1"><b> </b></font><font color="#808080" face="Arial" size="1">617.658.9008
tel </font><font color="#0000a1" face="Arial" size="1"><b>I</b></font><font color="#808080" face="Arial" size="1"><b>
</b>617.244.3753 fax</font><font color="#0000a1" face="Arial" size="1"> <b>I</b></font><font color="#808080" face="Arial" size="1"><b>
</b>One Gateway Center Suite 506, Newton MA 02458 </font><font color="#0000a1" face="Arial" size="1"><b>I
</b></font><a rel="nofollow" target="_blank" href="http://www.bvhis.com/"><font color="blue" face="Arial" size="1"><b><u>www.bvhis.com</u></b></font></a><font color="#0000a1" face="Arial" size="1"><b> I
Hartford ● New Haven ● Boston</b></font>
</p><div align="center">
<p><font face="Times New Roman" size="3"><hr size=2 width="100%"
align=center tabindex=-1> </font></p></div>
<p><font face="Tahoma" size="2"><b>From:</b> </font><a rel="nofollow" ymailto="mailto:equest-users-bounces@lists.onebuilding.org" target="_blank" href="mailto:equest-users-bounces@lists.onebuilding.org"><font color="blue" face="Tahoma" size="2"><u>equest-users-bounces@lists.onebuilding.org</u></font></a><font face="Tahoma" size="2">
[mailto:</font><a rel="nofollow" ymailto="mailto:equest-users-bounces@lists.onebuilding.org" target="_blank" href="mailto:equest-users-bounces@lists.onebuilding.org"><font color="blue" face="Tahoma" size="2"><u>equest-users-bounces@lists.onebuilding.org</u></font></a><font face="Tahoma" size="2">]
<b>On Behalf Of </b>Nick Caton<b><br>
Sent:</b> Wednesday, November 03, 2010 11:03 AM<b><br>
To:</b> Carol Gardner; </font><a rel="nofollow" ymailto="mailto:equest-users@lists.onebuilding.org" target="_blank" href="mailto:equest-users@lists.onebuilding.org"><font color="blue" face="Tahoma" size="2"><u>equest-users@lists.onebuilding.org</u></font></a><font face="Tahoma" size="2"><b><br>
Subject:</b> Re: [Equest-users] Chiller Curves (oh boy!)</font>
</p><p><font face="Times New Roman" size="3"> </font>
</p><p><font color="#004080" face="Calibri" size="2">Thanks for the response Carol!</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">That 120% load case is what
I’m getting at – let me try to explain a little further:</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">In the DOE2 help files, the
vocabulary for centrifugal chillers is “design capacity” and “maximum
capacity,” where “design” means the capacity at the rated or designed
conditions (at which you define / specify your chiller), and “maximum”
means the capacity the chiller is really capable of under the same conditions
if it runs balls-out (maximum power to the refrigerant drive).</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">The help file excerpt I copied
below with the red line is pretty explicitly telling us to normalize the
part load values to the <u>maximum</u> capacity for centrifugal chillers.
I’ve highlighted a second line for clarity. The EDR guidelines I
linked below are saying you can instead normalize to the <u>design</u>
capacity for the EIR-PLR curve if that’s all your field measurements or
manufacturer rep can provide.</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">I’m asking – are both approaches
right? </font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">My first and second questions
are kinda tied together… How would choosing to normalize to either the
maximum or design conditions affect how we should handle the DESIGN-PLR
ratio, if at all?</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font color="#004080" face="Calibri" size="2">~Nick.</font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p>
</p><p><font color="#37605e" face="Stylus BT" size="2"><b> </b></font>
</p><p><font color="#37605e" face="Stylus BT" size="2"><b>NICK CATON, E.I.T.</b></font>
</p><p><font color="#bfbf00" face="Calibri" size="1">PROJECT ENGINEER</font>
</p><p><font color="#37605e" face="Calibri" size="2">25501 west valley parkway</font>
</p><p><font color="#37605e" face="Calibri" size="2">olathe ks 66061</font>
</p><p><font color="#37605e" face="Calibri" size="2">direct 913 344.0036</font>
</p><p><font color="#37605e" face="Calibri" size="2">fax 913 345.0617</font>
</p><p><font color="#37605e" face="Calibri" size="2"><i>Check out our new web-site
@ </i></font><a rel="nofollow" target="_blank" href="http://www.smithboucher.com/"><font color="blue" face="Calibri" size="2"><u>www.smithboucher.com</u></font></a><font color="blue" face="Calibri" size="2"><u>
</u></font>
</p><p><font color="#004080" face="Calibri" size="2"> </font>
</p><p><font face="Tahoma" size="2"><b>From:</b> Carol Gardner [mailto:</font><a rel="nofollow" ymailto="mailto:cmg750@gmail.com" target="_blank" href="mailto:cmg750@gmail.com"><font color="blue" face="Tahoma" size="2"><u>cmg750@gmail.com</u></font></a><font face="Tahoma" size="2">]
<b><br>
Sent:</b> Tuesday, November 02, 2010 10:04 PM<b><br>
To:</b> Nick Caton<b><br>
Cc:</b> </font><a rel="nofollow" ymailto="mailto:equest-users@lists.onebuilding.org" target="_blank" href="mailto:equest-users@lists.onebuilding.org"><font color="blue" face="Tahoma" size="2"><u>equest-users@lists.onebuilding.org</u></font></a><font face="Tahoma" size="2"><b><br>
Subject:</b> Re: [Equest-users] Chiller Curves (oh boy!)</font>
</p><p><font face="Times New Roman" size="3"> </font>
</p><p><font face="Times New Roman" size="3">Let me take a crack at this. If
by design capacity you mean the chiller running at 100% load, you would
create the curve(s) by normalizing around your ARI design conditions i.e.
the PLR curve would be 1.0 at this point, call it ARI Cap and the other
points would be 90% Cap/ARI Cap, 80% Cap/ARI Cap, etc. The same would go
for your temp curves. If, however, your chiller is operating at 120%, or
some such other level, I would normalize the curve around the ARI design
conditions of the chiller at 120%. I had to do this for a VRV hp that was
selected at the 120% design condition.<br>
<br>
I find this from the DOE2 manual the most helpful:</font>
</p><p><font face="Times New Roman" size="3"> </font>
</p><p><a rel="nofollow" target="_blank" href="http://volume2dictionary.htm/"><font color="blue" face="Times New Roman" size="3"><u>Volume
2: Dictionary</u></font></a><font face="Times New Roman" size="3"> > </font><a rel="nofollow" target="_blank" href="http://hvaccomponents.htm/"><font color="blue" face="Times New Roman" size="3"><u>HVAC
Components</u></font></a><font face="Times New Roman" size="3"> > </font><a rel="nofollow" target="_blank" href="http://curvefit.htm/"><font color="white" face="Times New Roman" size="3"><u>CURVE</u></font><font color="blue" face="Times New Roman" size="3"><u>-</u></font><font color="white" face="Times New Roman" size="3"><u>FIT</u></font></a><font face="Times New Roman" size="3">
> </font><a rel="nofollow" target="_blank" href="http://inputtypedata.htm/"><font color="blue" face="Times New Roman" size="3"><u>INPUT-TYPE
= DATA</u></font></a>
</p><p><font face="Times New Roman" size="2"><b>INDEPENDENT-2</b></font>
</p><p><font face="Times New Roman" size="3">Used for all </font><font color="white" face="Times New Roman" size="3">curves</font><font face="Times New Roman" size="3">
having two independent variables. A list of up to twenty values of the
second independent variable. The number of values should be the same as
for DEPENDENT.</font>
</p><p><font face="Arial" size="3"><b>Example 1</b></font><font size="3">: defining
a </font><font color="white" size="3">curve</font><font size="3"> by inputting
a set of data points.</font>
</p><p><font face="Times New Roman" size="3">A packaged system (PZS) has cooling
performance significantly different from that used in the default
model. The manufacturer lists the data shown in Table 46, for cooling capacity,
at 2000 cfm design air flow rate, as a function of outside dry-bulb temperature
and entering wet-bulb temperature.</font>
</p><p><a rel="nofollow" name="12c12a536c514b6a__Ref490744859"></a><a rel="nofollow" name="12c12a536c514b6a__Ref490744804"></a><font face="Times New Roman" size="3">Table
46 Cooling capacity (kBtu/hr) vs. temperature</font>
</p><p>
<table align="center" border="3">
<tbody><tr valign="top">
<td rowspan="2" bgcolor="#00ffff">
<div align="center"><font face="Times New Roman" size="3"><b>Outside<br>
Dry-bulb</b></font></div>
</td><td colspan="3" bgcolor="#00ffff">
<div align="center"><font face="Times New Roman" size="3"><b>Entering Wet-bulb</b></font></div>
</td></tr><tr valign="top">
<td bgcolor="#00ffff">
<div align="center"><font face="Times New Roman" size="3"><b>72F</b></font></div>
</td><td bgcolor="#00ffff">
<div align="center"><font face="Times New Roman" size="3"><b>67F</b></font></div>
</td><td bgcolor="#00ffff">
<div align="center"><font face="Times New Roman" size="3"><b>62F</b></font></div>
</td></tr><tr valign="top">
<td>
<div align="center"><font face="Times New Roman" size="3">85F</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">69</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">65</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">60</font></div>
</td></tr><tr valign="top">
<td>
<div align="center"><font face="Times New Roman" size="3">95F</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">68</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">63 (ARI)</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">57</font></div>
</td></tr><tr valign="top">
<td>
<div align="center"><font face="Times New Roman" size="3">105F</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">65</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">60</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">53</font></div>
</td></tr><tr valign="top">
<td>
<div align="center"><font face="Times New Roman" size="3">115F</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">62</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">55</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">49</font></div></td></tr></tbody></table>
</p><p><font face="Times New Roman" size="3"> </font>
</p><p><font face="Times New Roman" size="3">In this example the independent
variables are the entering wet-bulb temperature and the outside dry-bulb
temperature. Because there are two independent variables and they have
units of temperature, we input a </font><font color="white" face="Times New Roman" size="3">curve</font><font face="Times New Roman" size="3">
of TYPE BI-QUADRATIC-T using the given data points. The dependent variable
is not the cooling capacity listed in the table but rather the cooling
capacity divided by the cooling capacity at the ARI rating point (95 F
outside dry-bulb and 67 F entering wet-bulb). In other words, the capacities
should be normalized to the ARI rating point., as shown in Table 47</font>
</p><p><a rel="nofollow" name="12c12a536c514b6a__Ref490745029"></a><font face="Times New Roman" size="3">Table
</font><font size="3">47 Normalized capacity vs. temperature</font>
</p><p>
<table align="center" border="3">
<tbody><tr valign="top">
<td rowspan="2" bgcolor="#00ffff">
<div align="center"><font face="Times New Roman" size="3"><b>Outside<br>
Dry-bulb</b></font></div>
</td><td colspan="3" bgcolor="#00ffff">
<div align="center"><font face="Times New Roman" size="3"><b>Entering Wet-bulb</b></font></div>
</td></tr><tr valign="top">
<td bgcolor="#00ffff">
<div align="center"><font face="Times New Roman" size="3"><b>72F</b></font></div>
</td><td bgcolor="#00ffff">
<div align="center"><font face="Times New Roman" size="3"><b>67F</b></font></div>
</td><td bgcolor="#00ffff">
<div align="center"><font face="Times New Roman" size="3"><b>62F</b></font></div>
</td></tr><tr valign="top">
<td>
<div align="center"><font face="Times New Roman" size="3">85F</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">1.095</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">1.032</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">0.952</font></div>
</td></tr><tr valign="top">
<td>
<div align="center"><font face="Times New Roman" size="3">95F</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">1.079</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">1.0 (ARI)</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">0.905</font></div>
</td></tr><tr valign="top">
<td>
<div align="center"><font face="Times New Roman" size="3">105F</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">1.032</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">0.952</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">0.841</font></div>
</td></tr><tr valign="top">
<td>
<div align="center"><font face="Times New Roman" size="3">115F</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">0.984</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">0.873</font></div>
</td><td>
<div align="center"><font face="Times New Roman" size="3">0.778</font></div></td></tr></tbody></table>
</p><p><font face="Times New Roman" size="3"> </font>
</p><p><font face="Times New Roman" size="3">The </font><font color="white" face="Times New Roman" size="3">CURVE</font><font face="Times New Roman" size="3">-</font><font color="white" face="Times New Roman" size="3">FIT</font><font face="Times New Roman" size="3">
input will look like the following:</font>
</p><p><font face="Times New Roman" size="3">CAP-</font><font color="white" face="Times New Roman" size="3">CURVE</font><font face="Times New Roman" size="3">-1
= </font><font color="white" face="Times New Roman" size="3">CURVE</font><font face="Times New Roman" size="3">-</font><font color="white" face="Times New Roman" size="3">FIT</font><font face="Times New Roman" size="3"><br>
TYPE
= BI-QUADRATIC-T<br>
INPUT-TYPE = DATA<br>
DEPENDENT = (1.000,1.079,0.905,1.032,0.952,0.841,<br>
0.984,0.873,0.778,1.095,1.032,0.952) ..<br>
IN-TEMP1 =
( 67, 72, 62, 72,
67, 62,<br>
72, 67, 62,
72, 67, 62) ..<br>
IN-TEMP2 =
( 95, 95, 95, 105, 105,
105,<br>
115, 115, 115, 85
85, 85) ..</font>
</p><p><font face="Arial" size="3"><b>Example 2:</b></font><font size="3"> Defining
a </font><font color="white" size="3">curve</font><font size="3"> by inputting
coefficients</font>
</p><p><font face="Times New Roman" size="3">We want a furnace to have a constant
efficiency as a function of part load. To do this we must replace the default
FURNACE-HIR-FPLR with a </font><font color="white" face="Times New Roman" size="3">curve</font><font face="Times New Roman" size="3">
that will give a constant efficiency. The </font><font color="white" face="Times New Roman" size="3">curve</font><font face="Times New Roman" size="3">
TYPE is QUADRATIC in the part load ratio (PLR). PLR correction </font><font color="white" face="Times New Roman" size="3">curves</font><font face="Times New Roman" size="3">
are always multiplied by the unit capacity, not the load, to obtain the
energy (fuel or electricity) use. Thus the </font><font color="white" face="Times New Roman" size="3">curve</font><font face="Times New Roman" size="3">
we want is: 0.0 + 1.0*PLR + 0.0*PLR*PLR. The input will look like:</font>
</p><p><font face="Times New Roman" size="3">New-Furnace-HIR-fPLR = </font><font color="white" face="Times New Roman" size="3">CURVE</font><font face="Times New Roman" size="3">-</font><font color="white" face="Times New Roman" size="3">FIT</font><font face="Times New Roman" size="3"><br>
TYPE
= QUADRATIC<br>
INPUT-TYPE = COEFFICIENTS<br>
COEFFICIENTS = (0.0,1.0,0.0) ..</font>
</p><p><font face="Times New Roman" size="3">Then in the SYSTEM command we include:</font>
</p><p><font face="Times New Roman" size="3"> FURNACE-HIR-FPLR =
New-Furnace-HIR-fPLR</font>
</p><p><font face="Times New Roman" size="3"> </font>
</p><p><font face="Times New Roman" size="3">On Tue, Nov 2, 2010 at 3:21 PM,
Nick Caton <</font><a rel="nofollow" ymailto="mailto:ncaton@smithboucher.com" target="_blank" href="mailto:ncaton@smithboucher.com"><font color="blue" face="Times New Roman" size="3"><u>ncaton@smithboucher.com</u></font></a><font face="Times New Roman" size="3">>
wrote:</font>
</p><p><font color="#004080" face="Times New Roman" size="3">Hi everyone!</font>
</p><p><font color="#004080" face="Times New Roman" size="3"> </font>
</p><p><font color="#004080" face="Times New Roman" size="3">I think I have <u>finally</u>
wrapped my mind completely around custom chiller performance curves for
a centrifugal VSD chiller. I’ve got a few specific questions now
that I’m on the other side of the fence:</font>
</p><p><font color="#004080" face="Times New Roman" size="3"> </font>
</p><p><font color="#004080" face="Times New Roman" size="3">1.</font><font color="#004080" size="1">
</font><font color="#004080" size="3">Is it necessary for the data points of
a part load efficiency curve (EIR-FPLR&dT in my case) to originate
from data with a 1.0 (100%) PLR ratio corresponding to a maximum vs. a
design load capacity? From what I gather in </font><a rel="nofollow" target="_blank" href="http://www.energydesignresources.com/Portals/0/documents/DesignGuidelines/EDR_DesignGuidelines_%20HVAC_Simulation.pdf"><font color="blue" size="3"><u>the
EDR reference</u></font></a><font color="#004080" size="3"> (re: “Method 2”
on PDF page 32/65), this curve can be generated using part-load readings
assuming a <u>design</u> capacity at the 100% loading mark… but the DOE2
help entry for “EIR-FPLR” seems to suggest otherwise (copied below –
see highlighted line).</font>
</p><p><font color="#004080" face="Times New Roman" size="3">2.</font><font color="#004080" size="1">
</font><font color="#004080" size="3">If the above part load efficiency curve
is created based on data where the 100% loading point corresponds to the
maximum (not design) capacity, should “DESIGN-PLR” (the ratio of design
to maximum capacity) be set to 1.00 and the capacity of the chiller be
specified at its maximum (not design) for the design/rated conditions?
As I write this question it sounds like I’m chasing my tail – someone
straighten me out =)!</font>
</p><p><font color="#004080" face="Times New Roman" size="3">3.</font><font color="#004080" size="1">
</font><font color="#004080" size="3">When you veterans finish a project with
sets of custom performance curves, do you have any suggestions for a naming
scheme for future reference/re-use? I’m currently thinking to keep
the curves grouped in an .inp snippet I for importing along with an equipment
cutsheet… but I’m certain I’ll forget the all the details as quickly
as humanly possible when this project is behind me…</font>
</p><p><font color="#004080" face="Times New Roman" size="3"> </font>
</p><p><font color="#004080" face="Times New Roman" size="3"> ~Nick</font>
</p><p><font color="#004080" face="Times New Roman" size="3"> </font>
</p><p>
</p><p><font color="#37605e" face="Times New Roman" size="3"><b> </b></font>
</p><p><font color="#37605e" face="Times New Roman" size="3"><b>NICK CATON, E.I.T.</b></font>
</p><p><font color="#bfbf00" face="Times New Roman" size="1">PROJECT ENGINEER</font>
</p><p><font color="#37605e" face="Times New Roman" size="2">25501 west valley
parkway</font>
</p><p><font color="#37605e" face="Times New Roman" size="2">olathe</font><font color="#37605e" size="2">
ks 66061</font>
</p><p><font color="#37605e" face="Times New Roman" size="2">direct 913 344.0036</font>
</p><p><font color="#37605e" face="Times New Roman" size="2">fax 913 345.0617</font>
</p><p><font color="#37605e" face="Times New Roman" size="2"><i>Check out our new
web-site @ </i></font><a rel="nofollow" target="_blank" href="http://www.smithboucher.com/"><font color="blue" size="2"><u>www.smithboucher.com</u></font></a><font color="blue" size="2"><u>
</u></font>
</p><p><font face="Times New Roman" size="2"><b>EIR-FPLR</b></font>
</p><p><font face="Times New Roman" size="3">Takes the U-name of a curve that
adjusts the electric input ratio as a function of</font>
</p><p><font face="Symbol" size="3">· </font><font size="3"><u>The part load ratio
(PLR)</u> – The PLR is defined as the ratio of the hourly load to
the hourly capacity; Load / Cap<sub>hour</sub></font>
</p><p><font face="Symbol" size="3">· </font><font size="3"><u>The evaporator/condenser
dT</u> - The temperature differential between the condenser and leaving
chilled-water. The meaning of the condenser temperature varies according
to condenser type. </font>
</p><p><font face="Times New Roman" size="3">For most chillers, the dT has a
relatively small effect on part-load performance. However, for variable-speed
centrifugal chillers, the effect of dT is as important as the PLR.
This is because the pressure rise across the impeller is proportional to
the square of the impeller’s speed. Unless some form on condenser temperature
relief is employed to reduce the temperature (and pressure) differential
across the chiller at part load, the performance of a variable-speed chiller
may not be significantly different than that of a constant-speed chiller.</font>
</p><p><font face="Times New Roman" size="3">To model power consumption as a
function of the PLR only, use a CURVE-FIT of TYPE = QUADRATIC or CUBIC.
To model as a function of both PLR and dT, use a BI-QUADRATIC-RATIO&DT
curve. </font><font color="red" face="Times New Roman" size="3"><b>The curve
must be normalized to 1.0 at full load and the rated temperature differential.
</b></font>
</p><p><font color="red" face="Times New Roman" size="3"><b>Note that, for centrifugal
chillers, ‘full load’ is defined as the ‘maximum capacity’, not the
‘design capacity’.</b></font><font size="3"> Refer to the DESIGN-PLR keyword
for more information.</font>
</p><p><font face="Times New Roman" size="3"> </font>
</p><p><font face="Times New Roman" size="3"><br>
_______________________________________________<br>
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</p><p><font face="Times New Roman" size="3"><br>
<br>
<br>
-- <br>
Carol Gardner PE</font>
<br><font size="3"><br>
_______________________________________________<br>
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