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Rules of thumb comes with experience. If you are still beginning with your career, I would suggest to first understand the HVAC fundamentals, and learn manual calculations before dealing with softwares.

Possible condensation in plate heat exchanger?

What is your desired indoor condition? What is your sensible heat ratio? Are you using steam? Do you have a psychrometric chart? Do you have a steam table?

Check NFPA 850 (2015) Ch. 9.5

In my understanding the hose stream allowance is for combined inside and outside.

From NFPA 415 (2016) 4.5.5 Water Supply. Water supply from public or private sources shall be adequate to supply maximum calculated sprinkler demand plus a minimum of 500 gpm (1893 L/min) for hose streams. The supply shall be available at the rate specified for a period of at least 1 hour.

Did you mean a,b,c,d and e are not the same?

NFPA 24-2013 edition section 7.2.3 says not less than 12m from building or other structure, this is also used in one of our O&G project.

EloyRD, 150 m2? That is a small room and ventilating it will result to over 40 air changes per hour, imagine that draft inside the room. Probably you have to double check on the chiller motors heat (open type or hermetic type), which maybe not that much as I assumed to be the same as pump...

Hi, Why mechanical efficiency is used to estimate the heat generated by motors? Based on your data, assuming all pumps and chillers are running at the same time and motor heat dissipation is 5% of motor rating (95% efficiency), I get 72 kW of heat, that is approximately 6 m3/s (12,713 cfm) of...

What is your delta T? For pipes 50mm and below, consider max velocity 1.2 m/s and max friction loss of 600 Pa/m. For pipes larger than 50mm, consider max velocity 2.4 m/s and max friction loss of 400 Pa/m. If it's in then you should be good.

That would be additional load to your split units, unless you cool it before you supply to basement.

You need to read NFPA 13, everything is there.

Look in NFPA 13.

RMERMP where you from? First, with just ventilation you cannot mainatain 24C inside if your outdoor temp is 28C, even 28C indoor will be unrealistic. Should be air conditioned to do that. Your delta T will be based on how much temp rise your electrical room will maintain at the peak of summer...

Better to ask your electrical engineer, but to give you a rough estimate normally it is 3% of total panel load.

If you are using ambient air, calculate how much air will require to remove heat dissipated by panels based on max temp required inside room. But I reckon you need to air condition the room to protect your equipment not only from high temperature but also humidity, depends on where you from.

Air or any fluid inlet are normally designed with bell mouth to minimize aerodynamic drag or in this case a reverse nozzle effect.

Office 1: Zone load = 40000 btu/hr RA = 2000 cfm Ducted return Office 2: Zone load = 30000 btu/hr Plenum load = 10000 btu/hr (sensible) RA = 2000 cfm Plenum return Is this what you mean? There should be no recognizable difference at all for the return DB or WB temperature, unless one office...

Not in IFC, but in IBC or your local code.