Kele Blog

Measuring Flow in Tight Spots

Posted on by Kele Inc

Often, one of the most challenging aspects of applying a flow-sensing device is the hunt. Tracking down the elusive and mysterious twenty diameters of straight, accessible pipe that the sensor manufacturer demands can be impossible at times. Let’s face it – it isn’t often that the Architect, Engineer, General Contractor, and all the subcontractors conspire to make the automation guy’s job easier, is it?

If the length of straight pipe upstream and downstream of a flow measuring device doesn’t meet the manufacturer’s published specs, then the manufacturer’s guarantee of accuracy no longer applies. But just how bad will the results be? As long as a few common criteria are met, the answer is “not as bad as you’d expect!”

To insure the best accuracy possible, the flow profile of the fluid to be measured must be as uniform as possible across the pipe or duct, and the velocity must be high enough to ensure turbulent flow. With uniform turbulent flow, almost any placement of a differential pressure or turbine device across the pipe or duct diameter will give a good representation of the average fluid velocity. As the flow profile loses uniformity (close to an elbow or tee, for example), error is introduced since the device placement might be in a region with a higher or lower velocity than the actual average. The same effect can occur if the velocity slows enough to create laminar flow. The flow profile illustration to the right indicates these effects.

Robert Benedict’s Fundamentals of Temperature, Pressure, and Flow Measurement cites several studies in the International Journal of Heat and Fluid Flow which demonstrate that about 8 upstream diameters of straight pipe after an elbow are sufficient to produce ±1 percent variance with an orifice meter. Reduction of straight pipe to only 4 diameters yields ±2 percent variance if a constant correction factor of 0.98 is applied to the orifice discharge coefficient. In either case, the downstream straight pipe need only be two to four pipe diameters in length. If the upstream problem is more obstructive than a simple elbow (a valve, perhaps, or a bullhead tee), the lengths of straight pipe needed are closer to 16 diameters upstream for ±1 percent, and 8 diameters for ±2 percent. Table 1 is derived from Benedict’s work, and is valid for any fluid in fully developed turbulent flow. In typical HVAC applications, turbulence is pretty certain. If in doubt, check to see if the flow in question has a product of velocity (V, feet per minute) and the equivalent circular pipe or duct diameter (D, in inches) that meets the following criteria:

For Air, V x D > 650
For Water, V x D > 20
For Steam, V x D > 110

In summary, even if there isn’t enough straight pipe or duct to meet the manufacturer’s requirements, it is often possible to get a “pretty good” reading anyway, and the results will be very repeatable even if they’re off by a few percent.

Table 1: Effects of Upstream Obstructions on Flow Profiles. Add the “Resulting Variance” to the manufacturer’s stated accuracy to get an idea of expected behavior of a flow transmitter when the published straight pipe (or duct) length exceeds those in the table. While we cannot guarantee these figures for every application, they are valid for most HVAC/R flow ranges, and may even be improved upon with the use of straightening vanes or honeycomb flow straighteners.

Table 1: Effects of Upstream Obstructions on Flow Profiles

Lighting Controls Can Brighten Business Picture

Posted on by Kele Inc

Reprinted from January 1992 Insights

Forty to sixty percent of the average commercial utility bill is for lighting.  That bit of gloomy news for building owners is good news for companies that sell and install devices designed to control lighting and lighting costs.  Thanks to the availability of a variety of lighting control options, contractors can take advantage of this potentially lucrative business with a minimum of effort.  Convincing a customer to decide on a new or retrofit control installation is made easier because of attractive paybacks that can be projected.  These payback projections can be enhanced when tied to utility company rebates and investment programs that encourage these installations.  As a result, the customer saves money, relationships are reinforced, and energy waste is curbed as much as possible.

Lighting control methods can be relatively simple to extremely sophisticated – with price tags that escalate with complexity.  Among the more common of these methods in use today are: on-off control, occupancy sensors, and light level control.

On-Off Control

The simplest of all lighting controls is the use of mechanical or electronic time clocks. Their function is to turn lights on and off at pre-set times of the day. Each time clock can control one or more lighting circuits.  The down side to time clock control is lack of flexibility and override capability.

Flexibility can be achieved by interfacing with lighting panels that have either their own time-of-day capability or are controlled from a building automation system. The lighting panel allows multiple lighting circuits to be controlled from one switch or control point on an automation system.  These panels also allow flexibility in the assignment of those circuits to various time schedules.

Most lighting panels or automation systems allow for some sort of override function for after hours use and a “flash system” to notify tenants of an impending “lights out” condition.  Another way of accomplishing the override is with a SENTRY switch that replaces the normal light switch to provide manual override of the time-of-day function in individual zones and which can be “swept” off from the lighting panel or automation system.  A sweep function will reset the lights to an “off” condition periodically during unoccupied hours.  These types of systems may also incorporate a remote dial-in function.

The “time-of-day” capability can be especially effective in retail stores and supermarkets.  The store could automatically be illuminated at 100% during store hours, reduced to 60% during stocking, then further reduced to 40% illumination for janitorial duties.  As a side note, these time-of-day system scan be tied to a security system (like an override) and all the lights can be turned on if the building is burglarized.

Occupancy Sensors

Occupancy sensors provide another method of lighting control.  These devices will automatically turn lights off after a pre-determined amount of time if there is no one in a given area. There are a number of different types of occupancy sensors on the market today.  The most common of these are the infrared and ultrasonic occupancy sensors.  The infrared occupancy sensor detects body heat and the ultrasonic type senses a breakup of the ultrasonic signal due to motion. Some occupancy sensors have a wall switch replacement type of detector for easier installation.  In all cases, care must be taken in selecting the location, sensitivity and length of time for which these sensors are set, based on the type of sensor and where it is to be used.

Light Level Control

Lighting effectiveness is being built into modern office buildings and shopping malls as more windows and skylights are being used than ever before.  To take advantage of this, some lighting control systems allow for a footcandle setpoint and then control the level of lighting required based on a photocell input that senses actual footcandles in a given space.  A number of dimming and ballast control systems are available to achieve this type control.  Two types of sensors, photo resistive or photo diode, are available as inputs.  This method allows the natural lighting in an area to be utilized to its fullest.

Another advantage to this type of control is that various lighting levels can be set based on need.  Hallways and open areas would require less light than stores or office areas.

Parking lot and store sign lights can also be controlled. Typically the store lights would come on earlier than the parking lot lights for their advertising effect. The reverse would happen at closing. The store sign lights would go out first to let people know the store is closed.  The parking lot lights could remain on long enough to allow store employees to close the store or until the following dawn for security reasons.

Future Trends in Lighting

Higher efficiency lights and new types of reflectors that put more light into the space are the latest in attempts to reduce lighting costs.  As control manufacturers study and design new control systems, improved dimming and ballast controls, astronomical time of day control and new strategies in demand control using lighting will be introduced and enhanced.  This new lighting technology is continually creating a wide array of innovative products that offer increased savings for customers and, at the same time, provide contractors potentially greater profits.

Between now and the turn of the century, lighting controls could prove to be one of the brightest spots in your business plan.

 

The Time is Ripe To Do Something About Multi-Zone Air Handlers

Posted on by Kele Inc

Written by Gil Avery, P.E. – Reprint from September 1991 Insights

Multi-zone blow-through air handlers were popular 20 to 40 years ago when energy was cheap.  Fortunately these units are not as popular today.  Because they have so many negative qualities, they are prime for retrofit and offer a real opportunity to save lots of energy while improving the performance of the A.C. System.

A few of the negative features of conventional multi-zone air handlers are:

  • Multi-zone air handlers use a fan that blows into a hot and cold coil plenum.  As a result the fan discharge velocity pressure is lost.  Multi-zone fan systems require 20 to 30% more H.P. than single-zone draw-through air handlers, with the same CFM capacity.
  • The pressure drop through the coil section varies greatly with the position of the zone dampers.  Consider, for example, a multi-zone air handling unit with four equal zones.  Assume the drop through the cooling coil is 1″w.g. when all the dampers are in the full cooling position.  The drop will only be 1/16″w.g. if only one of the four cooling dampers is wide open and the other three are in the full heat position.  Almost 1″ of additional pressure is available to the cooling zone.  Balancing the air flow on multi-zone units is almost impossible.
  • Summer humidity conditions may be unacceptable.  Raw, humid outside air is bypassed around the cooling coil when a zone is not in the full cooling position.
  • The multi-zone unit is a re-heat unit. The zone thermostat is satisfied by mixing heated and cooled air and the re-heating and re-cooling are increased more than normal when the zone dampers are in a mixing mode.  The air flows have increased because of the decrease in the pressure drop across the coils.
  • The heating requirements of multi-zone units with an outside air economizer are high.  Zones requiring heat must use mixed outside and return air at 55°F instead of return air at room temperature.

Converting a constant volume multi-zone air handler to a variable air volume unit will correct most of these issues.

The changes that have to be made to convert to VAV include: 

Adding a variable volume control assembly to each zone of the multi-zone unit.  Each assembly consists of:

  1. Opposed blade zone damper (A) and zone thermostat (J) (Existing thermostat may be reused.)
  2. Modulating zone damper actuator (B)
  3. Reversing relay (C) for zone actuator (B)
  4. Two-position switching relay (D) for zone heating and cooling damper actuator (E)
  5. Adding a static pressure controller (SP) (Connect to the fan discharge plenum.)
  6. Adding a variable frequency drive (Control the drive speed with the static pressure controller. Many contractors just let the fan ride the curve, but the speed controller is generally a good investment, since the power varies as the cube of the flow. The savings add up fast.)

The controls will operate as follows: 

  • If the system is on a heating cycle (damper (F) open) and the space temperature is rising, control damper (A) will modulate closed to shut off the warm air.
  • After damper (A) is fully closed, hot deck damper (F) closes completely and cold deck damper (G) opens fully.
  • On a continued rise in room temperature, damper (A) modulates back open to provide cooling.
  • Cycle reverses on a drop in room temperature.
  • Fan speed controller (H) is modulated by the static pressure sensor (SP) to maintain the proper pressure in the fan discharge plenum.

Some of the features of this retrofit are:

  • Zone air volume and heating and cooling capacity will all be enhanced.  Converting to a VAV system takes full advantage of zone diversity.  The air is squeezed to the zone with the largest load.
  • Zone humidity conditions will be lower in the summer.  All the air passes through the cooling coil and is dehumidified when the zone is on a cooling cycle.
  • All mixing of heated and cooled air is eliminated, which means no more re-heat.
  • Fan H.P. will be reduced from 30-50%
  • Cooling load will not only be reduced by eliminating the re-heat but also by the redirection in fan H.P.

* Available from Kele