Design Engineering objectives should be focused towards achieving the most efficient and effective means toward a conditioned space that is within the "Human Comfort Zone, " and at an affordable investment 'payback' period."
Summer Comfort Zone.
Maximum Comfortable Temperature
Minimum Comfortable Temperature
The above comfort zone was found to be acceptable to 90% of test subjects drawn from a range of age groups and genders, with work and life-styles involving varying levels of activity and clothing. An air conditioning system that establishes and maintains indoor conditions within this zone will provide thermal comfort. It will produce a neutral sensation, occupants will feel neither too hot nor too cold. Above chart and findings From: Home Energy Magazine Online September/October 1996) Sizing Air Conditioners: If Bigger Is Not Better, What Is? by John Proctor and Peggy Albright
If you over pay for over capacity equipment, --you will be paying more every month and will not be as comfortable as you would sizing it right to also achieve the appropriate humidity levels. You must know & record the operating feet per minute (FPM) velocity & the CFM to each room & the Total CFM airflow!
When a typical HVAC contractor quotes the efficiency of the Air Conditioning equipment's SEER & Btu/hr, and leads you to believe the new equipment will automatically deliver that SEER efficiency & Btu/hr rating, think again. Typically, --installed equipment only operates at 55% to 70% of rated capacity. Oversized equipment is the worst combination there is because the duct system airflow and heatload on the cooling coil are often way off what is required!
It is important to understand that "equipment ratings are only the 'potential efficiency' of that component of the system under perfect conditions." Over half of the system’s efficiency depends on correct equipment sizing run-time, on the duct system sizing, i.e., on the quality of the complete field-installation!
The Supply Air & the Entering Return Air delta-T, - tends towards less & less as the SEER goes higher,
7 SEER or less
'Max' condenser air temp 'delta-T'
18 to 25
17 to 23
Max temp drop 'across' E-Coil
'Max' SA/Return Entering Air 'Delta-T'
therefore, dehumidification could become more difficult at the highest SEER levels. The EER & SEER levels widen, as SEER sky rockets.
Especially if your system is oversized or there are a lot of low AC load days use an adjustable differential room TH.
TH Differential: Differential is defined as the difference between the cut-in and cut-out points as measured at the thermostat under specified operating conditions. For example, if the thermostat turns the COOLING EQUIPMENT on at 78-F & OFF at 76-F that is a 2 degree differential setting; one has a 4-F adjustable differential. This is a good way to control high humidity problems & also improve SEER performance.
What you want & need is right sized equipment operating at its optimal ratings within varying conditions, for your optimal comfort and savings.
When considering initial cost and pay-back period, -- is there too much emphasis on ultra-high seer-ratings when considering the most effective engineering and marketing path towards achieving the most affordable "Human Comfort Zone" Goals?
"A lower cubic feet per minute (cfm) airflow when air is at 50% Relative Humidity or below, will condense and absorb a larger portion of the air's latent heat." With a properly sized system coupled with a properly adjusted TXV the system will better adjust to varying conditions.
I believe that optimal efficiencies under variable latent heat loads could be effectively achieved through the use of computerized engineering.
The total latent and sensible evaporator heat load needs to be optimized at your normal operating conditions. This will also optimize the condenser's heat-load.
It is best to have the supply air and return air near the ceiling where the warmest air is located.
Come on engineers, consumers need a wholly variable system to achieve optimal efficiency performance when functioning in variable humidity conditions. HVAC company engineers can do it, therefore the companies need to get them on the market in the proper climate zone areas and at reasonable price levels.
This computerized control system AC would have to be sized to the combined latent and sensible heat load targets (78ºF/50RH) and the cubic foot volume of air changes that we would like per hour. This would need to be performed accurately to achieve the requisite run time and our combined comfort zone and unit efficiency goals.
Air Temperature Drop through Evaporator Coil
Air Temperature Drop through Evaporator Coil (1987 Period)
Indoor temperature and humidity load variations graph.
Refrigeration & Air-Conditioning (ARI) Second Edition,
Page 624, © 1987
Page 618, Refrigeration & Air-Conditioning (ARI) Second Edition, C 1987
Those lower SEER units had higher condenser splits than 12-SEER and higher units.
Sorry, I defiled the graph, 90-db outdoor, 80-db indoors with 67 wet bulb or 50% RH represents the condenser splits shown above graph. Graph: 80-DB & 80-WB line-intersect is 100% Relative Humidity.
A graphic illustration of how the latent heat capacity of the DX coil "increases with the increase in room relative humidity, and the total condenser load also increases proportionally. Total system capacity to remove heat in Btu/hr increases above the manufactures' ratings which are at 50% RH when the Relative Humidity is much higher. Total Heat (Enthalpy) is the total heat content of the air and water vapor mixture. It is the sum of both sensible and latent values, expressed in Btu per pound of air.
With "a properly sized system," thoroughly sealed duct system, and proper evaporator heatload airflow you will have consistent optimal nominal heat absorption removal capacity, coupled with requisite longer run-time cycles. I believe that optimal efficiencies by using a variable ratio latent/sensible heat loading, could be effectively achieved through the use of computerized system control components.If you do not know whether the metering device is a TXV or orifice?
Hook up your manifold gauges, block off considerable condenser air intake. If the suction pressure starts rising, you have a piston, or a cap tube.Normally plus or minus 3-degrees is acceptable for Subcooling therefore, 12 +/- 3 = 15 or 9-F SC.
If only the high side goes up, you have a TXV.
If it is a piston, get the CFM airflow correct first, then use the superheat method to charge it.
If it is a TXV, subcooling is the way to charge it, but check the Superheat to verify the TXV is holding within specs.
New Efficiency Component Technologies
Multi Split Air Conditioning
This operates in much the same way as the 'split' system. The 'Multi-split' system enables a number of indoor units to be individually controlled from a single outdoor condenser.
- Up to four units can be operated in cooling only or heat only form.
- 'Multi-split' systems offer an ideal way to treat a number of areas whilst minimising the space required for outdoor units.
Variable Refrigerant Flow systems are the most modern and sophisticated development of the 'split' systems.
- Up to 16 indoor units can be connected to a single large outdoor condenser.
- The outdoor condenser is constructed to respond proportionately to the number of indoor units operating, each being controlled for heating or cooling.
- Offering the ultimate in flexibility, individual indoor unit temperature can be changed independently, allowing personal choice as indoor and outdoor conditions change.
- VRF systems offer a year round solution to indoor climate control with unrivalled flexibility and energy efficiency.
EXVs - Electronic Expansion Valves - Control system for heat pump/air-conditioning system for improved cyclic performance
The microprocessor-based control system optimizes efficiency of the ON/OFF cycle by shutting the expansion valve fully closed at the beginning of each OFF cycle to maintain system pressure differential. At the beginning of each ON cycle the expansion valve is opened to an initial larger than average of three openings to allow the system to quickly reach steady state operating levels. Thereafter, the valve opening is reduced to an average of the last three steady state settings. After a predetermined time, control of the valve opening is passed to an adaptive control algorithm which adjusts the valve setting for optimized performance during steady state.
The Digital Scroll compressor delivers excellent seasonal energy efficiency (SEER). The SEER advantage becomes even greater for a tandem configuration. When both compressors are operating, the example system has a high EER of 11.3 and at 50% capacity, when only one compressor is operating at full load, the compressor operates at a high EER of 11.3 too. The operating range for a single Digital Scroll is from 10% to 100% and in a tandem configuration is from 5% to 100%. Wide operating range ensures fewer start-stops on the compressor. Fewer start-stops ensure higher system performance. Coupled with two speed condenser fan motors!
S - Net System
S- Net is the Samsung proprietary "system monitoring" program. The software can be used to monitor the functioning as well as the health of the system - pressures and temperatures at all key points in the air-conditioning system. Each indoor unit can now be controlled remotely through this software. S - Net is available in both RS232 protocol and also TCP/IP. It is now easy to monitor the health of an air-conditioning system through the Internet, from a remote monitoring site. Figure 7 shows the S- Net cycle monitoring screen. Figure 8 shows the S- Net remote controlling screen.
INTRODUCTION TO TOTAL COOLING PERFORMANCE
Mr. Slim Split-System-Ductless Air Conditioning Unique Quite Efficiency Features ?
May be better than window units?
how installing a 3-ton system can become a 1.5-ton system of actual delivered cooling (SURPRISE!):
It is better to slightly undersize than to over size, as proper sizing results in gains in run time and latent moisture removal. Short-cycling wastes energy in obvious ways, start-up uses extra power, it also takes at least 5 minutes for the unit to reach its cooling capacity.
These are major Problems with most Manufacture's Ratings' Data
Air conditioners selected based on standard indoor conditions of 80°F Dry Bulb (DB) with 50% relative humidity (which is the standard ARI capacity rating condition) will be incorrectly sized for 76°F Dry Bulb. Unfortunately, many of the major manufacturers' provide information only at 80°F. It would be a great improvement if the manufacturers' provided tables that presented the sensible and latent capacities at 76°F Dry Bulb for a variety of indoor humidities.
There is more to the "System Btu/hr Capacity Ratings in respect to the conditioned air space," than meets the eye. "It all depends on what is included or excluded in the capacity ratings in respect to motor heat Btu/hr that does nothing to reduce the total heatload of the conditioned space air." Motor heat is a factor to be dealt with, perhaps more so on the smaller units. I will list the formulas and illustrate the impact of the motor heat from the three motor sources.
Some possible Factors to consider when figuring the actual conditioned space Sensible Heat-Load to be removed and the variable Latent Heat-Load to be removed.
You can use the high-side (SCT) Saturation Condensing Temperature on your manifold gauge's dial, minus the outdoors-ambient Temperature; the difference gives you the condenser temp-rise or temp/split. There is NO excuse for not utilizing this important diagnostic check. Always use an accurate volt meter and amprobe to make sure you are not overloading the compressor's Wattage Service Factor and check the compressor discharge line to see that it is under 225-F.
First, figure the 'rated' gross capacity of the condensing unit. To determine the "Gross BTUH Heat Ejection" of the outdoor condenser: New Data = Let's take the total 'Watts' from the data sheets on an 17,500-Net-BTUH Heil condenser with a 2-ton DX evaporator coil with a TEV/TXV refrigerant control.
Add the condenser motor heat: 1591-watts X's my low Power Factor of 0.90= 1432 X's 3.413= motor heat additive of 4887-BTUH + 17,500-BTUH = 22,387-BTUH Gross condenser heat ejection.
22,387 / 1400-CFM of condenser fan = 16-F X's 1.08 = 17.3-F Rated Temp rise split off the condenser. A properly operating matched system should be within 10% of the condenser's gross temperature rise.
Take the "listed watts" of the compressor and Condenser fan and multiply that wattage by the Power Factor, they used to use 0.90, then times 3.413 to get the BTUH heat additive of the motor, then add the listed BTUH of the condenser to that figure, and then divide by the condenser's CFM. Multiply that figure by 1.08 to get the temperature rise.
Brother Don’s 18,400-Btu/hr, I used 17,500-Btu/hr rated 13-SEER Heil central A/C unit. Two ton Evaporator with TXV & Scroll compressor
1.08 *Xs 10-F split = 10.8 X 1400-cfm = 15,120-Btu/hr (outdoor) condenser, minus 4887-Btu/hr motor heat = 10,233-net-Btu/hr Xs .76 sensible = 7,777 sensible .24 X 10,233 or 2,456 latent heat transfer.
7777/16-F indoor split = a mere 486-cfm | I want at least 750-cfm when supply and returns are at floor level!
New 13-SEER 1.5-Ton Goodman, Model GSC 13 0 181A Match. -° From Goodman's Expanded Performance Data
85°F (OAT) Outdoor Ambient Temperature; 80 IDB; 71 IWB / 64% RH; 675-cfm; 212 psig - 105.5°F SCT minus 85°F OAT = "Condenser split 20.5-F;" SA/RA delta T (split) 20°F.
New 13-SEER Goodman Model GSC 13 0 181A Match. - From Goodman's Expanded Performance Data
At the ARI Rating: 95 OAT; 80 IDB; 67 IWB / 50% RH; 600-cfm; 229 psig - 113.32 SCT minus 95 OAT = Aprox 18.32 Condenser split ; 84 psig 50-F Coil Temp; SA/RA delta T (split) 21-F.
New 13-SEER Goodman Model GSC 13 0 181A Match.
At 85-F Outdoor Ambient Temp (OAT); (75 IDB; 67 IWB;) 525-cfm; 193 psig = 99 SCT minus 85 = [Condenser Split 14-F;] SA/RA delta T at 17-F
For the uninitiated, Delta-T is the difference between the air temperature entering and leaving the outdoor AC condensing unit. This is a good diagnostic check because it measures the latent heat of condensation as well as the sensible heat absorbed by the vaporizing refrigerant in the indoor evaporator coil. I'm betting when you find out approximately how many BTUH that the AC system is actually transferring outside, you may be shocked by how far it is below its BTUH rating.
His condenser usually has a 10-F temp delta T, the evaporator appears to be under CFM heat-loaded or, it has an unbalanced heatload on the DX coil's circuitry allowing liquid refrigerant in the return line causing the TXV sensing bulb to reduce the refrigerant flow thus reducing the DX coil's heat absorption capacity.The probable cause is "an unbalanced airflow/heatload through the evaporator coil. "I have a Thermo Pride OL 11 oil furnace. Those oil furnaces have a very large round heat exchanger that goes to near the top of the furnace, --due to a low basement ceiling the DX coil sets perhaps illegally close to the heat exchanger causing a few of the coil's circuits to be under heatloaded. Since the liquid refrigerant is not completely evaporated it will cause the outlet line that the TEV sensor bulb is on to be too cold and the TEV will shut-down the flow, which greatly reduces the BTUH capacity of the DX coil and the system. On piston refrigerant control systems, they may flood back liquid which could damage the compressor, unless the system is way under-charged. Thermo Pride could install airflow turning vanes just above the heat exchanger to funnel the air directly into the DX coil, instead of most of the airflow hitting the bottom of the DX's drain pan causing extreme turbulence back-pressure and an imbalanced DX coil circuitry heatload!
The chart split listed below is at Condenser Design conditions: Indoor Return Air 80-F dry bulb 67-F Wet Bulb or 50% Relative Humidity as you go up to 99% RH the condenser split could increase by up to 6-F; down as much as 4-F at a low humidity of 55-F Wet Bulb.
Do your own figuring based on this formula. Motor BTU/hr additive = Watts X's PF x's 3.413 for Btu/Watts additive added to rated BTUH, divided by condenser fan CFM X's 1.08 = condenser Temp-Split. Get the Motor Power Factors (PF) of the compressor and fan motor from the manufacturers.
Some of the temp-split figures need correcting, will do ASAP. Some Splits rounded.
Do your own figuring based on this formula. Get the Motor Power Factors (PF) of the compressor and fan motor from the manufacturers.ARI Conditions are: 95ºF-OAT; 80ºF-IDB; 67ºF-IWB or 50%RH | TVA conditions; 95-OAT; 75ºFIDB; 63-IWB or around 50%RH | Try 85ºF-OAT
CONDENSER TEMP-SPLITS 12-SEER units - Comfortmaker® | Heil® | Temp Star® - used 0.88 Motor Power Factors
1.5-Ton 18,000 21-F Split Cond. CFM 1400 WATTS 1536 1.5-Ton is from actual published DATA - Only ARI Rating Conditions
Brother Don's perfect combination Heil, Model: HAC218AKA1, Scroll compressor 12-SEER, matched with a 2-Ton evaporator with a TXV metering device, 1.5-Ton 18,400-BTUH @ 95ºF (OAT) Outdoor Ambient Temperature; Indoors: 75-(IDB) Indoor Dry Bulb; 63ºF-(IWB) Indoor Wet Bulb, or near 50%RH; @ 600-CFM; ; "18ºF condenser split" | @ 85ºF OAT; 67-IWB or 66.5%RH; "+20ºF cond. split."
To figure this; units pressure chart, the Temps, instead of IWB the %RH, & CFM, For users, No gauges required, to check if your A/C is near specs! However, the temperatures & indoor humidity make a big differenence in the condenser split. (Airflow with a proper heatload on the evaporator, is key!) Make that outdoor condenser WORK by putting a high heatload on the indoor evaporator coil!
Take the both the indoor Supply Air & Return Air DB, WB or %RH , too! If you have an accurate airflow CFM, I can Ballpark the BTUH your A/C or Heat Pump is delivering in the cooling mode.
1.8-Ton 18,000 +18-F Temp-S Cond. CFM 1400 - one story - 1000-sq.ft.
1.5-Ton 18,000 18-F @ 63-F IWB 50% RH conditions to 20-F Condenser Temp Split @ 67-F IWB 66.5% RH; Don's low airflow @ 10-F Split - needs critical attention!
2-Ton 24,000 23-F Temp-S Cond. CFM 1400 WATTS 2067x.90=1860x3.413=6349+24000=30349/1400=21.7x1.08=23.4 (All ARI Conditions)
2.5-T 30,000 21-F Temp-S Cond. CFM 2000 WATTS 2778x.90= 2500=8533+30000=38533/19.2x1.08=20.8
3-Ton 35,600 14.8-F T-Sp Cond. CFM 2800 WATTS 3096x.90= 2786+35600=38386/2800=13.7x1.08=14.8
3.5 T 42,500 17.6-F T-Sp Cond. CFM 2800 WATTS 3578x.90=3220+42500=45720/2800=16.3x1.08=17.6
4-Ton 48,500 19.5-F Split Cond. CFM 3400 WATTS 4174x.90=3756.6x3.413=12821+48500=61321/3400=18x1.08=19.5
5-Ton 59,000 23-F Temp-S Cond. CFM 3400 WATTS 5043x.90=4539x3.413=15,490+59000=74490/3400=21.9
A modern 2-ton 13-seer system would produce around .70 of per-ton or 8,400-Btu/hr, however at 70% Relative Humidity its capacity would increase to around 1.1 per-ton or 13,200-Btu/hr or over half of the 2-tons would be used for the latent heat-load. "That is around a 36% increase in latent capacity" and a 36% reduction in sensible capacity, --due to a higher humidity.
There are four main factors to humidity control. These are related to equipment selection and installation and the effects of the performance of the four equipment factors. The Four Factors are: evaporator coil selection, airflow, refrigerant control device, and superheat setting of the refrigerant cycle.
Proper duct sizing and location is important. Most older homes need reduced ambient (outside) air infiltration and more effective use of vapor barriers, coupled with adequate insulation. Windows and doors are special areas to work on. My upstairs windows around the pulley wheels for the weights, allowed air to blow through almost unrestricted from the attic area both winter and summer.
When it comes to airflow, the laws of physics apply. Air follows the line of least resistance. So many of the duct systems are poorly designed that ductwork problems can seriously curtail proper system performance. These factors usually show up in uneven temperatures through the conditioned area. In addition, airflow across the cooling coil can affect humidity removal. Too much air will result in poor dehumidification. Too little air can cause the registers to sweat. The right amount of air is usually between 325 CFM and 400 CFM per ton. Lower airflow will produce increased humidity removal, but compromises sensible heat removal. Finding the right air flow and run time balance can eliminate most of the comfort zone humidity problems.
My scan of my doctored Thermopride OL 11 "Oil Furnace" Graphed Blower-Curve-Chart (Same as my brother's Oil furnace)
Thermopride OL 11 Graph ipg image - Thank you Dave Staso, CA. for the better expandable image!
"After it loads Right click "Show Original Images" - Move cursor arrow over graph - Click + when 'over graph' for expanded image," then print on the highest quality setting.
Notice at 700-RPM with a quarter 1/4HP motor, I checked his actual airflow at less than 300-CFM (no appreciable duct air leaks). The graph shows 5.24" SP.
Now, we switch to a 1/3HP motor @800-RPM, the graph shows 6.85" SP & only 400-CFM, not nearly enough airflow for 1.5-Ton of cooling. Therefore we have to raise the evaporator coil 6" above the furnace on rails & then check the airflow. Eliminating that restriction using a 1/3HP motor, hopefully that will be adequate at +800-rpm & say +5.5" SP & +700-CFM. Formula: SP2= (SP2/SP1)2 X's SP1
Condensation forming on supply air diffusers or registers can be caused by humid attic air flowing to the register - due to lack not sealing off the attic air & insulating it properly.
Refrigerant Control Device
The device used to make a cooling coil evaporate refrigerant and thus absorb senile heat and latent heat of humidity is called a Thermostatic Expansion Valve refrigerant control. The most effective refrigerant metering control in this application is "a external equalized &/or for extreme variable temperature conditions, a balanced port (TEV/TXV) expansion valve." The expansion valve provides consistent performance over a wide range of conditions that exist in any home. Without an expansion valve the entire system performance is compromised. Adding an expansion valve to an existing system can often improve performance, reduce operating costs, and extend the life of the compressor & overall system.
Too many do not properly purge & evacuate contaminated central air conditioning systems.The Triple Evacuation Method is normally done on refrigeration systems, R-410a systems require it on central air conditioning systems:
First, remove any valve cores with a special valve core remover this will speed up the evacuation time. Back service valves two turns off their back seat.
1) Re-claim unit charge (Recover all the refrigerant)
2) Charge system to 150 PSIG with dry nitrogen and leak test
3) On contaminated systems replace the filter dryers. Then Repair all leak(s)
4) Evacuate system to 500 microns valve off & see if it holds 500 microns for ten minutes, if it holds, break the vacuum with dry nitrogen
5) Evacuate system to a deeper 400 microns, valve off vac pump, & again break the vacuum with dry nitrogen
6) Evacuate system to 400 microns and & then Check to see if it holds. (Recharge with fresh clean refrigerant)
7) Check to see if the Supply and Return air ducts were correctly sized & sealed by the original installer.
If a vacuum pump will not evacuate a system below 1500 microns there is a problem with the pump itself, a leak in the system, or moisture in the system. Moisture is most likely because water vaporizes at 1500 microns.
Many HVAC contractors will consider this excessive time & effort for contaminated residential air conditioning systems, however it is a must for low temp applications.
The “micron” is a metric unit of measure for distance. The micron is a unit of linear measure; one micron equals 1/25,400ths of an inch. Modern high capacity vacuum pumps help speed up the evacuation process.
When a system has been evacuated below 500 microns, the pump is valved-off with the micron gauge connected, if the vacuum rises to 1500 microns and stops, there is moisture remaining in the system. If it rises above 1500 microns & continues to rise there is a leak. You should allow at least 15 minutes after the pump has been shut off an accurate micron gauge reading. When a system will not evacuate below 1500 microns there is either a lot of water or there is a system leak.
One factor that is often overlooked in trying to increase humidity removal is the the superheat of the suction gas. Superheat can often be out of design conditions and the system seems to work fine. A five degrees warmer coil temperature can reduce humidity removal by 20% or more. Correct TXV adjusted superheat for optimal latent removal should be between 5-F and 7-F degrees at the coil. The best time to adjust the superheat is on hot summer days, under normal HUMIDITY load conditions 75-F indoors strive for 55-F degree discharge air or 20 + degree drop. Humidity levels & CFM airflow levels determine the indoor latent & sensible SA/RA variable temperature split. (Using only TXV metering devices with external equalizers & balanced ports' for extreme variable weather conditions, is compliant with best practices.)
If any of the above factors are not correct you can expect that humidity problems will occur. Other factors can affect the humidity levels. The way the house was built — the number of people that live there and the life style of the occupants. The correction of humidity problems in any residence may be accomplished by applying the above factors. This is why it is essential that you find a company that you can trust to solve your humidity problems. if neglected, humidity problems only get worse.
In my opinion all the components of air conditioning systems should be engineered and specially designed for the climate zone conditions where they will be shipped and used.
In humid climate areas, the use of a dehumidistat and variable speed programmable indoor blower motors that use half the electricity of conventional motors could be used. Also, ask your Utility company about their "high efficiency Rebate Program," these programs can add to your energy cost savings.
Arid climates can use a higher temperature operating oversized coil, coupled with 450-cfm or more, per Btu/hr ton of cooling, -- cycling through the evaporator coil along with a lower rated btu/hr compressor to condenser ratio.
There ought to be a code requiring every manufacturer of an airhandler or furnace to provide capped taps ahead of the evaporator coil and ahead of the blower for easy static pressure testing access.
All air conditioning condenser manufacturers' should publish the CFM and normal temperature rise range across the condenser coil, so that the service tech's can measure the heat transferred from the evaporator coil. Most high efficiency units will have temperature degree rises between 18 and 25ºF. Older lower SEER condensers can have temperature rises up to 28 or more degrees.
Such temperature rise data provides a guide to the actual heat transfer by the evaporator coil to the outdoor condenser coil, and therefore also, whether the proper design amount of (cubic feet per minute) CFM of indoor air/per ton of cooling Btu/hr, is passing through the heat absorbing -- cooling coil.
Most higher efficiency units are designed to operate at higher evaporator coil temperatures which results in less temperature drop, also the high outside and inside humidity levels will put a heavy latent heat-load on the evaporator coil will delay the conditioned area's temperature drop.
You may also have too much outside air infiltration into your home, check it out and reduce it, because warmer high humidity air will overload the evaporator coil with latent heat removal with the result being little if any reduction in humidity levels and no lowering of the actual sensible temperature readings in the conditioned areas.
In high humidity climates everything in the home is loaded with the latent heat of moisture. Humid air contains a lot of heat-loaded vapor. Some moisture is airborne but most of it resides or hides in the bricks, wooden furniture, carpeting, walls, and the concrete floors we walk on, etc. Dish washers, clothes washers and taking hot showers, etc., all add a lot of moisture to the air and to home materials.
This latent moisture in the conditioned area is vaporizing in the air, and as it is being conditioned it gives up its latent heat to the evaporator coil's liquid refrigerant causing it to boil into the heat absorbing refrigerant vapor. That heat-loaded vapor is then sucked back to the compressor where it is compressed into a high temperature gas in the condenser coils, where the outside air cooler outside air cools it below its condensing temperature point causing the vapor to condense into a liquid.
I do NOT assume any responsibility for how anyone uses the information on my Web pages.
All HVAC/R work should always be done by a licensed Contractor! This information is only placed on these pages for your understanding & communication with contractors & techs.
This information is for the edification of contractors and techs. I am NOT liable for what you do, you are liable for what you do!
- Darrell Udelhoven
Darrell's Refrigeration Heating and Air Conditioning - Federal Refrigerant Licensed - Retired Licensed Contractor
Please write me if you have anything you'd like to contribute! - Darrell
Please feel free to link your web pages to any of mine.
- MY HVAC BLOG - YOUR QUESTIONS & COMMENTS WELCOME New 7/12/08
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· OIL HEATING AIRFLOW TEST Using Thermometers -Best Practices Guide for residential HVAC retrofit
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