Fully articulated and comprehensive air and fluid distribution, metering, and control method and apparatus for primary movers, heat exchangers, and terminal flow devices

• US 7,854,135 B2
• Filed: 01/14/2008
• Issued: 12/21/2010
• Est. Priority Date: 05/03/2005
• Status: Expired due to Fees

• Current Assignee: Daniel Stanimirovic
• Original Assignee: Daniel Stanimirovic
• Inventors: Stanimirovic, Daniel
• Primary Examiner(s): Norman; Marc E
• Application Number:
  US12/008,724
• Publication Number:
  US 20080161975A1
• Time in Patent Office: 1,072 Days
• Field of Search: 621/766, 621/86, 236/12.1, 236/13, 236/44.C
• US Class Current: 62/176.6
• CPC Class Codes: F24F 11/30 for purposes related to the operation of the system, e.g. for safety or monitoring
• CPC Class Codes: F24F 11/32 Responding to malfunctions or emergencies
• CPC Class Codes: F24F 11/49 ensuring correct operation, e.g. by trial operation or configuration checks
• CPC Class Codes: F24F 11/89 Arrangement or mounting of control or safety devices
• CPC Class Codes: F24F 2110/30 Velocity
• CPC Class Codes: F24F 2110/40 Pressure, e.g. wind pressure

Abstract

The described method and apparatus pertains namely to the HVAC (Heating, Ventilating, and Air Conditioning) industry, though its many functions extend into any and all forms of air-fluid movement, metering, distribution, and containment. Essentially, the scope of operation of the method and apparatus encompasses all forms of scientific and engineering measurement dealing with fluid dynamics, fluid statics, fluid mechanics, thermal dynamics, and mechanical engineering as they pertain to precise, articulated control of air-fluid distribution and delivery. The described method and apparatus offers complete, comprehensive, and correct utilization of air-fluid movers and terminal devices under unique sensor logic control, from initial lab testing stages through to equipment cataloguing, selection, design and construction of any and all air-fluid distribution systems in entirety, whereas previously there was no such cohesive, total and terminal method of control for these systems or their components.

Claims

1. A method for monitoring and controlling OA/RA (Outdoor Air / Return Air) content of TA (Total Air) by multi-point temperature sensing wherein

dry and wet bulb temperature of OA/JRA air streams are measured independently prior to entering a mixing box;

dry and wet bulb MA (Mixed Air) temperatures are measured inside the mixing box; and

downstream of a heat exchanger through a multi-point traverse where air is not stratified;

a calculating step is performed to determine enthalpy change of each air stream as an initial and final state point and path function, from OA to MA, from RA to MA, and from MA to TA, the final discharge downstream of a heat exchanger;

a calculating step is performed to determine quantities of OA/RA content of TA, where any of the unknowns;

OA, RA, MA, or TA are determined by a quantum evaluation of both latent and sensible heat content from the airstreams per ton of heat exchange temperature differential in BTUH (British Thermal Units per Hour) occurring in a given time frame from point to point of each path as may be timed by an internal clock;

where one ton of cooling corresponds to 12,000 BTUH;

where one ton heat of rejection corresponds to 15,000 BTUH;

where air quantity per ton CFM (Cubic Feet per Minute) =12000 / 4.5 ×

enthalpy differential of air;

where mass flow = pounds per hour of dry air, plus or minus latent heat of vaporization or condensation;

where this figure is corrected for temperature/density as deviating from standard air volume at 13.3 cubic feet per pound at density 0.075 lbs per cubic foot and specific heat 0.24;

where pounds per hour mass flow of standard air =0.075 ×

60 =4.5;

where one short ton 2000 lbs / 4.5 =444.44 CFM of standard air, where BTUH = mass flow pounds per hour ×

specific heat ×

differential temperature;

where one corrected ton of entering air as above is applied to the known face area of a heat exchange medium per one square foot for said coil or heat exchanger to determine total unit capacity over total face area square feet or other known effective area (K Factor) for Total Air delivered as expressed in CFM;

where likewise one corrected ton of entering air (OA to MA or RA to MA) is applied over known area inlet openings to derive actual individual and Mixed Air quantities (OA +RA);

where net differences in specific heat or net changes in enthalpy BTU per pound per degree of change adjusts these figures to establish actual quantity over time for a given path;

where the final discharge air quantity from path MA to TA is determined downstream of the heat exchanger with BTUH Qtotal derived from this final path enthalpy differential;

where one ton of fluid heat exchanger change corresponds to 2.4 GPM (Gallons Per Minute) of chilled water, or 3.0 GPM of condenser water (heat of rejection);

where the GPM fluid flow quantity is determined through path in and out of heat exchanger with above conditions using equation GPM = Qtotal / 500×

differential fluid temp (e.g. 1 ton 12,000 BTUH / 500 ×

10 =2.4 gpm) or GPM = tons ×

24 / temperature differential;

where the heat exchanger may be a refrigerant gas or other fluid;

where same mass flow tonnage capacity is applied with temperature/density. specific heat, and specific gravity correction at initial and final states;

where the above capacities per ton may be adjusted to one short ton or one long ton;

where the above paths may be redirected, re-quantified, and all variables arbitrarily set for a desired outcome to the final path TA or any individual path;

modulating a damper position over said known area inlet openings to alter OA/ RA individual air quantities, MA Mixed Air quantities and subsequently, output of final path TA Total Air quantities based on input from said sensors and said calculating steps;

modulating a refrigerant gas or other fluid valve position over heat exchanger output to alter GPM quantity or overall capacity per ton based on input from said sensors and said calculating steps;

repeating said calculating steps across adjusted areas (changing coefficients) produced by said damper or valve throttling;

modulating a primary mover to alter quantity or overall capacity per ton based on input from said sensing and calculating steps; and

re-sampling data obtained from said sensing as needed to achieve stable condition of flow output capacity per designated or other arbitrary setting.

2. The method of claim 1, wherein:

a calculating step is performed to determine the Mixed Air enthalpy (Hm) with quantities of OA and RA content and dry and wet bulb temperatures;

comparing the previous step with same multi-point readings downstream of the heat exchanger (8);

determining total flow quantity from the path MA to TA;

performing a calculating step to determine total, latent, and sensible loads on the beat exchanger (8).

3. A method for controlling loading characteristics of a heat exchanger (8) comprising the steps of

modulating parallel damper control of a mixing box;

adjusting OA and RA content, or primary and secondary air streams comprising Total Air content,

comparing OA/RA enthalpy as separate airstreams

altering the value of Mixed Air enthalpy by decreasing OA or RA individual air stream content to dilute the OA / RA content of one or the other air stream,

thus incurring latent or sensible changes and applying the equation that stipulates 1 ton of sensible cooling equates to 12000 BTUH / 1.08×

sensible temperature differential from path OA to MA and from path RA to MA for sensible changes, and deducting any latent changes from total quantity 12000 BTUH / 4.5×

enthalpy differential along the same paths;

and providing specific conditions of total, latent, or sensible heat exchange as displayed on a psychrometric chart (6);

thus following the vectorial lines of the chart as depicted in accordance with thermal dynamic relationships based on dry air moisture content;

modulating said parallel damper positions to conform to vectorial lines of said psychrometric chart.

4. The method of claim 3 wherein the value of mixed air enthalpy is controlled by means of humidification or dehumidification;

wherein latent heat of vaporization may be precisely controlled through induced evaporation or condensation.

5. The method of claim 3 or 4 wherein the value of mixed air enthalpy is controlled by means of adjusting pounds per pound or grains per pound of air moisture content.

6. The method of claim 3 or 4 wherein as dry bulb decreases are incurred where sensible heat content approaches zero, enthalpy is held constant by inducing humidification to allow only adiabatic saturation to occur within an adiabatic boundary chamber for latent energy to be stored and released through controlled evaporation and condensation.