The Path to Low Pressure Drop Across a High-MERV Filter

31 Comments Read/write comments

Using a high-MERV filter doesn't have to result in a large pressure drop

Last August I began a series of articles on filtration and indoor air quality.  You can find the list of them at the bottom of this article but let's do a quick review here:  We spend a lot of our time in buildings.  A lot of indoor pollutants are generated in the kitchen and not removed by the range hood.  The consensus among indoor air quality researchers is the particulate matter that's 2.5 microns or smaller (PM2.5) is one of the worst for health.  And finally, good filters (i.e., MERV-13) can remove a lot of the PM2.5 and other pollutants but experience as well as studies show they often don't, for a variety of reasons.

So how do we fix this situation?  How can we get a high-MERV filter and have it do a good job of filtration without causing problems with the air flow in the heating and cooling system?  The answer is simple:  Make the filter big enough.  John Semmelhack, owner of building science firm Think Little in Virginia, spoke about this topic last year at the North American Passive House Conference in Boston.  Also last year, we got a new Mitsubishi ducted mini-split system here in the Energy Vanguard office in Georgia (meticulously installed by PV Heating and Air).  Let me show you what's possible.

High-MERV filters with low pressure drop

Semmelhack spoke about ducted mini-split heat pumps in Boston and towards the end of his talk he got to the topic of filtration.  (Download the presentation and see the filter section starting with slide 25.)  He used a 2" deep MERV-13 filter in a filter grille.  The ducted mini-split they used was a one ton system moving 400 cubic feet per minute (cfm) of air.  The pressure drop across the MERV-13 filter was an astoundingly low 0.0274 inch of water column.  Yes, really!

What was their secret?  They used a 20"x20" filter.  That's all.  Just make the filter bigger and you get a lower pressure drop.  The key is to look at the ratio of the filter area to the air flow rate.  In their case, the filter area was 2.78 square feet (sf) so the ratio comes out to be 2.78 sf ÷ 400 cfm = 0.007 sf/cfm.  Using the nominal air flow rate of 400 cfm/ton of capacity, we can make the number look a little friendlier:  2.78 sf ÷ 1 ton = 2.78 sf/ton.

Hang onto that calculation.  I'll come back to it in a minute.

John Semmelhack's 2" filter grille with MERV-13 filter

In our office, we got a similar result, although our pressure drop is a bit higher.  We have an Aprilaire filter that's also 20"x20" but it's a 4" deep filter in a cabinet near the ducted mini-split air handler.  Our pressure drop is 0.0604 i.w.c., as you can see in the photo below.  That's higher than Semmelhack achieved with his system but still really low compared to what you might expect.

The Air Conditioning Contractors of America (ACCA) Manual J load calculation protocol says to allow 0.10 i.w.c for a filter...and that's generally for a standard 1" deep MERV-2 filter, not a 2" or 4" MERV-13.  Ask contractors what the pressure drop across a high-MERV filter is and they'll probably tell you something like 0.25 i.w.c.

The pressure drop across our MERV-13 filter is a very low 0.06 inch of water column (i.w.c.)

When we measured the air flow in our system, we got 363 cfm, so our ratio of filter area to air flow is 0.008 sf/cfm, or 3.1 sf/ton when converted using 400 cfm/ton of capacity.  We have more filter area per unit of air flow but we got a higher pressure drop than Semmelhack.  Some of you building science geeks are wondering about that, I'm sure, and so am I. 

The main difference between the two systems is that our filter cabinet is installed in the middle of the return duct whereas Semmelhack used a filter grille.  We installed a filter grille, too, and currently it doesn't have a filter in it.  We'll be testing that at some point, though.  Another difference between Semmelhack's pressure drop and ours is that he used a 2" deep filter and ours is 4" deep.  We'll keep measuring our pressure drop and I hope that with more data, our average pressure drop will be lower.

But let's not get hung up on why our pressure drop is higher than Semmelhack's.  Getting a 0.06 i.w.c. pressure drop across a MERV-13 filter is still great.  The key to whether it's a good number or not is how well it fits in with the total pressure drop in the system compared to what's allowed (the total external static pressure, or TESP).  More on that in a future article.

A simple rule of thumb for low pressure drop across a high-MERV filter

I've shown you data from two MERV-13 filters now.  Both are much lower than you'd measure across many of the MERV-13 filters installed in the wild, and I've given you the key to achieving similarly low pressure drops.  It's simply to increase the filter area relative the air flow rate. 

The two systems described above had ratios of 2.8 sf/ton and 3.1 sf/ton.  You don't have to go that high, though.  David Butler, an HVAC designer and frequent commenter here, said he uses 2 sf/ton as his guide. 

Home performance contractor extraordinaire Mike MacFarland of Energy Docs in Redding, California does it a bit differently.  He uses 250 feet per minute (fpm) as his absolute maximum face velocity for air moving across the filter but generally sticks to 200 fpm or lower.  The conversion from face velocity (ft/min) to filter area per ton of capacity (sf/ton) is straightforward using the equation q = A v.  (You may recognize the product of area and velocity from the continuity equation for air flow.)  The answer in this case is that 200 fpm = 2.0 sf/ton in this case, the same number David Butler uses.  MacFarland designs for conventional heat pumps rated for 0.5 i.w.c. total external static pressure (TESP) and had never had a system come in at a TESP higher than 0.35 i.w.c., with most of them measuring 0.30 i.w.c. or less.

With smaller capacity mini-split heat pumps, getting filter sizes to 2.5 or 3.0 sf/ton isn't that hard.  With conventional systems, it's not so easy.  With a 2.5 ton system at 3.0 sf/ton, for example, you'd need 7.5 square feet of filter area, or a 30"x36" filter, but you'd have a hard time finding one that size so you'd have to install two 18"x30" filters.  You can do it if you really want to, but if you use MacFarland's rule of 2.0 sf/ton, the resulting 24"x30" filter (or equivalent) is much easier to find space for and you can still get a low pressure drop.

So here's your rule of thumb for filter sizing:

Filter Area = 2.0 square feet (or more) for each 400 cfm of air flow

Do that (and size your ducts properly) and you shouldn't have to worry about high pressure drops across your filters...at least not when the filters are relatively clean.

 

A shoutout to our sponsors

As mentioned at the top of this article, we got a new Mitsubishi ducted mini-split (and two ductless units) installed in our office.  Mitsubishi donated the equipment for this project, and PV Heating and Air, a home performance contractor in Atlanta, donated their labor.  Ultra-Aire donated a ventilating dehumidifier for our office and now that we head into warmer, more humid weather, I'm excited to see the difference it makes in our indoor air quality and comfort.  Finally, Aprilaire donated the filter cabinet and MERV-13 and MERV-11 filters.  We like these companies and recommend their products and services.

 

Other Articles in This Series

What Percent of Time Do You Spend Indoors?

The 2 Main Problems With Kitchen Ventilation

Which Indoor Air Pollutants Matter Most?

7 Reasons Your Filter Isn't Improving Your Indoor Air Quality

The Unintended Consequences of High-MERV Filters

Do High-MERV Filters Always Reduce Air Flow?

 

NOTE: Comments are moderated. Your comment will not appear below until approved.

Comments

Very good Allison. And now for part two - at what pressure drop across the filter does it need to be replaced? Then part 2b, what season is best for filter replacements? Could winter be better than summer?

Allison
Bailes

Great questions, Danny.  I'd say the filter needs to be replaced when the TESP gets too high so you've got to know how much slack you have in the system.  Of course, it also depends on whether you have a PSC or ECM blower.  With the former, a loaded filter reduces air flow but doesn't cost you in energy.  The latter will ramp up to maintain air flow, adding to your energy use as the filter loads.

I suspect your question about the best season to change the filter is related to humidity control.  With a PSC blower, as mentioned before, the air flow goes down as the filter loads, and in a humid climate that's a good thing for removing water vapor as the coil gets colder.  But you have to be careful that the air flow doesn't go so low that you freeze the coil.

And another benefit of a loaded filter is that it filters better.

For anyone not monitoring their static pressure and air flow, it's best just to change the filter regularly.

Replacement filters for existing filter channels in existing HVAC units will normally have approximately 450 - 550 FPM face velocity as a part of OEM equipment design regarding adjacent coil maximum face velocity (water carry over). Oversized filters will measure lower pressure drops as their face velocity falls. Where face velocities are closer to the 500 FPM median, filter material and pleat designs will be the way to balance pressure drops against MERV. Filter loading qualities can effect length of life.

Interestingly, the old ASHRAE 52-76 had a final PD of 1" wg. Constant flow ECM's will meet the challenge up to 1 inch, even if it take every energy dollar you got. Constant torque ECM is the worst of both worlds. It's schizophrenic - "I want to be a fully modulating motor. No wait, I want to act like a PSC......"

I am really curious what the upper limit of TSP is and why it is an upper limit. Most gas furnaces say TSP not to exceed .50. Some heat pump air handlers say .25. But I have never had any manufacturer tell me why.

Danny, I have been wondering why a Carrier 59TP6 VS Furnace is not ramping up to overcome the 0.7 static pressure of the system (yeah i know - all typical residental texas flex duct). Then I looked at the fan curve and was surprised, because I would have assumed that the CFMs should be constant, regardless of TESP. But e.g. on the 800 CFM at 0.5 TESP nominal setting the CFM goes down to 770 CFM for 0.6 TESP and 735 CFM for 0.7 TESP.

Is this motor what you refer to as an ECM that wants to behave like a PSC? Why in the world would Carrier install this and call it a VS furnace when it is not maintaining CFMs even though the motor is capable of ramping up? Just to save a few dollars on some logic?

See page 6 for air delivery CFM per TESP for this furnace in case you want to see the charts yourself.
https://dms.hvacpartners.com/docs/1009/public/09/59tp6a-02pd.pdf

I feel your frustration Robert. The chart shows the behavior of a constant torque ECM (X13). The curve gives it away. It mirrors a PSC but doesn't drop off as dramatically. Its all in how they program the microprocessor. I have the same question as you. WHY?????

Hopefully I can clear up some of the confusion. ECM blowers come in more than two flavors. In particular, variable speed is NOT synonymous with constant flow, i.e., not all variable speed blowers have the constant flow feature. You can tell immediately by looking at the blower performance table. VS blowers that aren't constant flow drop off in airflow as static increases, as with non-variable ECM blowers. Also like non-variable ECM's, these motors are 'constant torque' (within a limited range). The 59TP6 furnace Robert mentions is an example. So I suppose you could say there are 3 flavors of ECM's: non-variable constant torque, variable constant torque, and variable constant flow. Most variable speed blowers have the constant flow feature, which is probably why there's so much confusion on this point.

BTW, constant flow blowers attempt to maintain the selected CFM within the operational external static range, but you'll see some fall-off at the top end.

Danny wrote: "Constant torque ECM is the worst of both worlds."
I beg to differ. It's important to keep in mind that (all else being equal) all three flavor ECM's have the same efficiency at a given static pressure-CFM combination. I typically specify non-variable ECM's for applications that don't require variable speed since VS blowers cost significantly more. Why speed big bucks on constant flow when the application doesn't demand it?

As an aside... In the real world, constant flow blowers are often misused by dealers who like the fact that they'll deliver the correct airflow through their overly restrictive ducts. SEER ratings are meaningless when you operate at high static. Sigh.

Yeah i feel like it is deceiving marketing too. When you read the website and brochures it always states "Variable-speed, high-efficiency, ECM blower motor" for this model. There is nothing besides the detailed fan performance table that would suggest this blower behaves differently from the Infinity furnace which has the true constant CFM VS motor. That one also says "Variable-speed, ECM blower motor" in all marketing materials ... just doesn't feel right.

David,

I "beg to differ" with your "beg to differ." And you will likely "beg to differ" with my "beg to differ". So let's agree up front to "beg to differ".

I hate varying indoor airflow. And you know I am OCD about this. It is not consistent with good design.

Just yesterday, I completed a load on a 2 story, 3,300 sq. ft home with a 14,400 btuh heat gain (sensible 10,400+4,000 latent). My best guess is we will have 24 supply terminals that must accommodate a whopping 650 CFM. So I go about selecting these 4"x2.5", 6"x2.5" etc bar linears to provide some semblance of throw and along comes your X13 to trash their performance when the filter loads with four particles of 2.5 um of skin flakes, insect parts and Ovaltine. Considering the consequences and the over all budget, a constant flow blower isn't "big bucks". I am not using ECM's for energy efficiency anyway.

Robert, It is an ECM (electronically commutated motor). So it would be described as a variable speed, brushless motor that uses about 1/2 the energy as a PSC. They just come in two flavors. Some manufacturers allow you to choose constant torque or constant flow. Constant flow is always more $$. If you are accustomed to using constant flow, it is unsettling the see this performance.

BTW, if you are using the SEZ, it only has .20 inches wg TSP. So you must be judicious with the duct resistance.

Then I would say your application demands constant flow. I don't have a problem with that, but likewise, you shouldn't discount the usefulness of constant torque ECM's in applications that don't demand constant flow. Not everyone is OCD about the impact several hundredths of an inch of static on system flow as the filter loads.

In any case, my comment regarding efficiency was directed at the folks who upsell or specify variable speed AHU's (even with single stage equipment) based on the incorrect assumption that variable speed ECM is inherently more efficient than non-variable ECM.

We had up-speced to VS because of the dehumidify feature, being in the Houston climate. The system dehumidified so well that I was surprised how well this works. But then I also realized that I don't get full cooling capacity because the system couldn't get to design temp of 75 on a typical 96 design temp day. I got the HVAC contractor to bring out a manometer (he had to borrow one from a friend) and showed him where to take the readings (he said he never uses it) and we realized the system static was 0.7. I first thought, no big deal, the VS blower just works harder than for the designed 0.5 ... but then why do i not get the full cooling capacity? Took me a lot of research to realize that my VS blower is the constant-torque variety. And now I also understand why I get such good de-humidification ...

The builder HVAC guy still has no solution. I would love to try to get to 0.5 design as hoped. I asked him to redo the return plenum so that the two 12" flex duct don't bend 180 degrees before coming into the return, but he insists that's not the problem and that the system is operating just fine.

David, by any chance do you have a good reference for a Houston HVAC contractor? I remember reading that when you do designs you sometimes also interview various contractors so maybe you have come across a reputable Houston HVAC contractor? I won't get any further with the builder and his contractor. I already called 5 different companies with great reviews on google and when talking to them on the phone and asking about how they would measure airflow, not one had an idea besides measuring Delta-T. When I asked about static pressure they said that's not something they typically measure ... am I just unlucky or is this really the state of the Houston Residential HVAC industry?

Robert,
This is not a static problem. It's an airflow problem, reflected by the static and the characteristics of constant torque ECM's. Moreover, you are likely getting close to full capacity or 98% or so. What you are seeing is more total capacity being used to remove moisture. Hence senisble capacity is down and the thermostat isn't gettingsatisfied.

FYI, more airflow = more capacity and higher sensible heat ratio. Lower airflow = a wee bit less total capacity and a lower SHR.

If the contractor knows so little about system performance as you state, my bet is the refrigerant charge is likely incorrect as well. Proper refrigerant charge metrics are always assumed for "x" CFM (typically 400) per ton. So if your airflow has dropped to 300 or 350, the contractor, who apparently doesn't understand airflow, see low suction pressure and is duped into thinking the unit was undercharged. Then he runs to get the R-410A jug and packed more in. After-all more is better.......Overcharging will definitely reduce capacity. I have seen it hundreds of times.

This is one of the primary rebuttals from the contracting folk in discussing rightsizing. The unit is under airflow, resulting in overcharge, creating a warm house. Then they say "You see, I tried to tell you we should have installed that 7 1/2 ton unit".

I'm anxious to see David's response.

@Robert, although we can't diagnose your system from afar, Danny's point about impact of airflow on total capacity and charging is spot on. You can increase sensible capacity by increasing airflow at the expense of some dehumidification capacity. It sounds like you may be able to give up a bit of dehumidification without sacrificing comfort.

If refrig charge is off (because tech didn't understand airflow vs. charge), then fixing that should free up some additional capacity. You can't properly charge a system based on pressure unless airflow is correct and ambient conditions within an acceptable range. Best to charge by weight.

Regarding airflow / high static, I'd want to know the supply and return static breakdown before making a recommendation, as well as the pressure drop across the filter. But in my experience, the return side is often the culprit and is usually the easiest to fix. I can't comment on the usefulness of rebuilding your return plenum to eliminate elbows without seeing how that would work, but you should look for a way to add another return and depending on current filter size, increase the surface area.

Lastly, the best way to 'have your cake and eat it too' is to reduce the moisture load on your system. In humid climates, that means reducing infiltration (through strategic air sealing). Tightening your enclosure is a 'two-fer' as it also would reduce the sensible load. You can further reduce sensible loads by keeping blinds closed on windows that aren't shaded by trees and overhangs, especially on south and west facades. Direct sunlight into the house is your enemy during cooling season.

I feel your pain regarding the state of the industry. Unfortunately, I can't help with a referral. I suggest starting with the NATE referral engine (natex.org). It sounds like you have a general understanding of the concepts discussed in this thread, so ideally you should talk with prospective techs before hiring someone, but that's easier said than done!

Thanks David and Danny. I actually do have the static pressure measurements, because I showed the HVAC tech where to put the probes and wrote down the numbers of the various tests. I also cross checked various combinations and did the math to make sure we got it all right.
Total across system: approx 0.7
Return: 0.23
Filter: 0.10 (Honeywell F100 4x25x16 - MERV11)
Coil: 0.12
Supply: 0.25

Infiltration per builder was 2200cfm50 which came out to around 4 ACH50 (our building code unfortunately still allows 5 instead of 3 further north). Duct leakage should not be an issue since they all run in the open web trusses and the AC system sits in a storage room inside the conditioned space on the second floor.

I designed the house myself with no west facing windows and all south facing windows having 2.5 ft overhangs, so no direct sunlight on the windows from April-October (though I did opt for thermally broken aluminum which I know have a big penalty, but we wanted lot of large windows for natural daylight - all of that was in the Manual J)

The return is clearly not ideal, but no idea whether getting the 180 degree u-turn in the flex duct away and instead have a 90 to the side of the plenum will make a huge difference on the static or not. The link below has some pictures of the "beautiful" flex duct install, but at least I got them to put in hard metal 90ies at the supply plenum. Not on the return though where they put the hole into the subfloor in a bad spot which required this weird horeshoe bend on one of the two 12 " flex returns. https://hvac-talk.com/vbb/showthread.php?2196258-New-Home-AC-System-unab...

There is also an issue with the coil cooling not evenly and one side of the supply plenum being warmer than the other which is even noticeable in the ducts. They first thought it was a bad coil, replaced it, same story. Then they put in a transition between upflow furnace and coil: a bit better, but still 10 degree temperature difference between the duct exiting to the right of the plenum (50 degrees) vs. the left (60 degrees) while the return temp is 75.

By now I feel like I know way too much about AC systems already for a home owner. I just need to get a really good and reputable HVAC technician, then I'm sure my problems can be fixed. As David suggested, I have already called 8 companies and insisted to talk to a tech prior to having them come out, about half of them there is no way to talk to a tech, you can't get passed the scheduling assistant without paying for a $80 diagnostic on-site visit. The others I did get the tech on the phone but no one appeared really competent. The minute I tell them it's 2 tons for 1850sf they tell me the system is just too small. *sigh* One guy that got referred to me as a "duct system expert" asked me how many take offs from the plenum. When I told him 2x10 inch, 1x9 inch and 1x8 inch he told me that clearly my supply ducts were too large which was creating issues (yeah I'm sure that would help the air flow to reduce the ducts and increase the static pressure even more :S) ... sorry for the ramble/rant ... you would think in a city where 9 months of the year the AC runs and dehumidification is a key requirement, there should be a huge talent and knowledge pool for HVAC ...

Just following, I had the same question as Danny.

I'm in the final design stage for my new construction home unit using the Mitsubishi concealed cabinet model.

Allison
Bailes

Lee, the recommendation by John Semmelhack in his comment is the best advice I've heard on that issue:  Replace the filter when the pressure drop across it doubles...or until you can't stand how dirty it looks.  Of course, that method shouldn't apply to a filter that's already causing the whole duct system problems but since you're putting in a ducted mini-split, I'm sure you'll have a well-designed duct system with low TESP.

oops, Lee I made a comment to Robert that was intended for you. If you are using the Mitsubishi SEZ air handler, be careful. It only has .20 inches wg of total static pressure available. So the ducts (filter and terminals) must be extremely aerodynamic.

Danny, I'm using the SEZ and did notice the 0.2" ESP. I was originally considering having to do an independent HEPA, but I will check to see if the oversized MERV 13 can be incorporated into the SEZ. Wondering if it will help to toss out the SEZ factory filter since it would probably stay spotless anyway. Any thought?

Allison
Bailes

Lee, the Mitsubishi ducted air handler we installed is an SEZ unit.  Even with 0.06" across the MERV-13 filter, out total static is only about 0.1".  So yes, it's certainly possible to do MERV-13 in a low static air handler.  And yes, toss the factory installed filter. 

One more point:  As with most air handlers, there are several settings that determine what fan curve is used, and 0.2" is what you get on the highest setting.  But the system comes from factory set for the next highest setting, 0.14".

Now if we could just get the manufacturers to build in enough smarts to measure the pressure drop effectively and recommend filter replacements based on actual need as opposed to every X days.

Allison
Bailes

Wouldn't that be nice! 

You would think a 4" MERV-13 filter would do a decent job at filtering room air. Did it? No mention of before/after PM2.5 measurements. Also - from the photo it looks like the Aprilaire filter cabinet is in-line with the ducted return, so that means dirt in the return ducts prior to the filter and need for some periodic cleaning. What about the ductless units you also had installed?

Allison
Bailes

David, we just got the system finished recently and haven't set up testing for everything yet.  Also, we don't have PM2.5 data from before the system was running but we can see what happens with the system turned off to get an idea of the baseline. 

Yes, there is a little bit of ductwork upstream of the filter you see above, but the grille is about 10' off the floor and it's a filter grille.  I prefer filter grilles to keep the ducts clean, but we set it up this way so we can do some testing on different configurations.  And we can always use a low-resistance filter at the grille as a pre-filter.

The ductless units have their factory-installed filters. 

Our general rule is that when the pressure drop across the filter doubles from the initial, clean pressure drop, it's probably time for a change. With big, deep filters this can take a loooooooong time, and the filters will look absolutely disgusting well before the pressure drop would indicate that it's time for a change.

In my presentation slides that Allison linked to, I tested a dirty filter versus clean filter (20x20x2 MERV-13) after 10 months of continuous use on a 3/4-ton heat pump in my own house. The increase in pressure drop was a little less than 0.03in.w.c., which also happens to be roughly double the initial pressure drop of the filter. The filter probably could have gone another 2 months, but it was too disgusting to look at to put it back in the grille.

Please note that we suspect loading time varies significantly, especially with filter design/construction. Our preferred filters have what we call a "high loft" fabric that enables them to load with particles for a long time without significantly increasing pressure drop. We've also tested some "low loft" MERV 8 filters (also 20x20x2 at a similar airflow) that, per our testing, need to be changed out monthly because they load up so quickly.

How would one distinguish a high loft filter from a low loft one, especially when ordering online? My system uses a 16x20x4 MERV 11 Honeywell or equivalent.

Here is a question for you Dr B and others.

Do you know of any research showing the particulate reduction using a self contained bypass HEPA, such as made by LifeBreath (https://www.lifebreath.com/us/product/tfp3000hepa/) , Clean Comfort (https://www.cleancomfort.com/products/filtration/hepa-air-cleaners), Lennox (https://www.lennox.com/products/indoor-air-quality/air-purification/hepa) and others. It sits parallel to the air handler/furnace and only filters a portion of the total system airflow. BUT it is HEPA. Of course if you are a millionaire, you can always use an IQ Air Perfect 16 (https://www.iqair.com/perfect-16-support-tech-specs)

I always thought the 4" & 5" pleated filters had a surface area advantage over a 1" or 2" pleated. Should the increased surface area be given consideration when sizing for two square foot per ton versus simply using the outside dimensions such as 20" x 25"?

Allison
Bailes

Great question, rjp.  Lower pressure drop with deeper filters is definitely the story that gets told a lot, but a study published in Home Energy magazine in 2009 found little difference between 1" and 4" deep filters.  I wrote about this back in January and said in the last paragraph in the Study #2 section:

The final result I'll mention here is that they didn't see as much difference [in pressure drop] as they expected for filters of different depths.  For example, "the 4-inch Filtrete 1550 (MERV 12) was only marginally better than the 1-inch Filtrete 1700 (also MERV 12) and the two other [1-inch] MERV 11 filters of the same brand (1000 and 1085)."

Here's a link to my article on that:

Do High-MERV Filters Always Reduce Air Flow?

So to use the rule of thumb I proposed here, just use the width and height of the filter, not the depth or the manufacturer's stated filter area.

In my practice of environmental consulting, I find that for consumers, the most well-received recommendation is to stick with the manufacturer filter in the HVAC to protect the coil/system, and buy a supplemental HEPA filter to address the breathing air. Part of the reason is that I am not an HVAC tech and I don't diagnose systems beyond whether or not they are meeting the needs (temp/humidity/outdoor air introduction) at the time I am there. I don't take static or airflow measurements or obtain design specs. If the system is not meeting demand, I recommend testing/commissioning of the system by a qualified HVAC contractor. But the add-on high- MERV filters in my experience often don't get installed properly, maintained properly, or make enough difference, especially in PM2.5. A MERV 13 filter isn't going to make as much of a dent in PM2.5 at a MERV 17 (HEPA). And consumer products tend to be more idiot-resistant with filter installation than HVAC filter boxes. Of course every situation is different, and some homes (and most offices) have a properly engineered system to take care of indoor pollutants. That is a minority, and in most cases only lasts as long as the original owner or contractor maintaining the system. So my "rule-of-thumb" for home IAQ is 1) HVAC maintenance per design, and 2) Supplemental HEPA room air purifiers if needed.

Add new comment