Sound Attenuators

Sound Attenuators

At Spiral Pipe of Texas, we have been making sound attenuators for over 35 years. Our products have been tested by an independent testing laboratory** for dynamic insertion loss, pressure drop and self-generated noise in accordance with ASTM Standard E477 test standards. We offer rectangular sound attenuators in high (type SA), medium (type MA) and low (type LA) pressure drop configurations. Individual modules can be assembled into assemblies to match most any size of duct. Our circular sound attenuators (type SC-C) are available in 12” through 60” diameter. We offer four configurations (models TGL, TGU, TGS and TGZ) of our transfer and return silencers. We can also make custom silencers using different materials and configurations, including flat oval shapes. Our basic sound attenuators are classified as dissipative silencers — metal construction with sound absorptive media (mineral fiber), covered by perforated metal to protect it from airflow erosion. For more information about sound attenuators and methods of HVAC noise reduction, you can refer to the 2015 ASHRAE Handbook — HVAC Applications (Chapter 48 – Noise and Vibration Control).

** testing performed at ETL Testing Laboratories, Inc., Cortland, NY (report# 483042)

Rectangular Sound Attenuators

22 ga. galvanized steel shells
22 ga. perforated galvanized steel baffles
4 lb/ft³ mineral fiber insulation
Module sizes 6×6 to 48×48 available

Round Sound Attenuators

Galvanized steel spiral pipe outer shell
Perforated galvanized steel inner shell
4 lb/ft³ mineral fiber insulation
Outer shell 8” larger than inside perforated liner
Spun metal head and cone shaped tail

Rectangular Sound Attenuators

Engineering Data

Spiral Pipe of Texas offers three models of rectangular sound attenuators — models SA, MA and LA. Each model is, in turn, offered in three standard lengths — 3, 5 and 7 feet long. Using our nomenclature, a model SA attenuator in a five-foot length would be a “Model SA-5”. We offer these different models and lengths because the selection of a sound attenuator requires some trade-offs between acoustical performance and pressure loss. Dissipative silencers operate by putting the flow of acoustic energy (and air) in contact with our sound absorptive media. When we increase the amount of contact — either by making the sound attenuator longer or decreasing the width of channels between baffles — we get more sound attenuation. But we also get a higher pressure drop.

Model	Sound Attenuation	Static Pressure Loss
SA	Higher	Higher
MA	Medium	Medium
LA	Lower	Lower

So, why would we ever be okay with a high pressure loss? It’s all about velocity and where we locate the sound attenuator. The actual static pressure is high or low relative to the velocity. If you locate your sound attenuators in a low velocity area — like a plenum — there may be very little real difference between the total pressure loss of either model, but you would still get a higher sound attenuation from a model SA.

Our sound attenuators have been tested in an independent testing laboratory and in accordance with ASTM Standard E477. For selection and comparison, our data is published for five face velocities — zero flow, 1000 FPM (+ and -) and 1500 FPM (+ and -). Self-Noise Sound Power Ratings are published for four referenced velocities (less zero flow where no self-noise is generated). Using our Air Flow Performance Data, you can obtain the applicable static pressure loss (Pd) if your actual CFM is known, using the following equations:

Rectangular Sound Attenuators from Spiral Pipe of Texas are constructed of 22 GA galvanized shells with 22 GA galvanized perforated baffles and 4#/ft3 mineral fiber fill. They will withstand a differential air pressure of 8” WG without structural failure. We offer a full complement of sizes from 6”x6” to 48”x48” and they can be arranged in an almost unlimited number of arrays. We offer other optional materials and constructions as well (please contact factory for information).

When ordering, please include model number and dimensions in the following order:

	Width	Height	Length	Model
example:	24	24	60	SA-5

In an ongoing effort to improve our products, Spiral Pipe of Texas reserves the right to revise the design and specifications at any time.

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Model SA

Rectangular Sound Attenuator

Dynamic Insertion Loss

Silencer Model No.	Octave Bands	2	3	4	5	6	7	8
	Center Frequency	125	250	500	1000	2000	4000	8000
	Face Velocity FPM	Net Insertion Loss in Decibels (dB)
SA-3	-1500	8	22	28	38	39	26	14
	-1000	10	22	32	42	39	30	17
	0	8	18	30	42	40	31	19
	+1000	6	15	28	42	42	32	19
	+1500	6	14	25	32	34	30	17
SA-5	-1500	15	33	46	47	41	35	26
	-1000	13	30	45	53	50	47	26
	0	12	26	42	53	58	49	27
	+1000	11	23	40	52	55	49	29
	+1500	9	21	40	50	50	44	29
SA-7	-1500	16	36	45	48	42	34	31
	-1000	15	36	48	57	54	52	34
	0	15	35	46	54	53	52	34
	+1000	15	34	45	55	55	52	35
	+1500	10	33	44	47	48	41	35

Self-Noise Sound Power Ratings (P.W.L.) — (dB re 10^-12 watts)

Silencer Model No.	Octave Bands	2	3	4	5	6	7	8
	Center Frequency	125	250	500	1000	2000	4000	8000
	Face Velocity FPM	Self Noise Sound Power Levels in Decibels (dB)
SA-3 SA-5 SA-7	-1500	56	51	53	56	65	66	55
	-1000	46	42	44	50	55	49	40
	+1000	51	44	43	46	48	45	39
	+1500	64	55	54	53	57	58	54

Face Area Adjustments	Area (sq.ft.)	2	4	8	16	32
	Adjustment	– 3	0	+ 3	+ 6	+ 9

Air Flow Performance Data

Model	Static Pressure Loss (inches WG)
SA-3	0.07	0.12	0.18	0.24	0.38	0.49
SA-5	0.07	0.13	0.20	0.27	0.42	0.55
SA-7	0.10	0.18	0.27	0.36	0.56	0.73
Face Velocity FPM	365	490	610	705	875	1000

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Model MA

Rectangular Sound Attenuator

Dynamic Insertion Loss

Silencer Model No.	Octave Bands	2	3	4	5	6	7	8
	Center Frequency	125	250	500	1000	2000	4000	8000
	Face Velocity FPM	Net Insertion Loss in Decibels (dB)
MA-3	-1500	9	17	23	32	39	20	13
	-1000	7	15	21	36	40	21	13
	0	6	14	20	35	42	24	16
	+1000	6	13	19	34	42	25	16
	+1500	6	13	18	34	42	25	17
MA-5	-1500	12	25	43	54	49	31	17
	-1000	11	24	42	55	55	32	19
	0	9	21	39	56	57	34	19
	+1000	9	20	38	55	57	35	21
	+1500	9	20	37	54	53	36	21
MA-7	-1500	15	30	36	46	48	32	18
	-1000	15	28	47	57	56	36	20
	0	14	26	46	57	58	38	22
	+1000	14	25	46	58	58	41	23
	+1500	12	25	43	57	56	42	25

Self-Noise Sound Power Ratings (P.W.L.) — (dB re 10^-12 watts)

Silencer Model No.	Octave Bands	2	3	4	5	6	7	8
	Center Frequency	125	250	500	1000	2000	4000	8000
	Face Velocity FPM	Self Noise Sound Power Levels in Decibels (dB)
MA-3 MA-5 MA-7	-2000	58	55	57	57	64	64	56
	-1000	51	43	44	46	46	36	29
	+1000	43	37	34	37	35	25	28
	+2000	56	50	49	47	54	54	49

Face Area Adjustments	Area (sq.ft.)	2	4	8	16	32
	Adjustment	– 3	0	+ 3	+ 6	+ 9

Air Flow Performance Data

Model	Static Pressure Loss (inches WG)
MA-3	0.05	0.07	0.11	0.15	0.24	0.33
MA-5	0.07	0.10	0.15	0.20	0.32	0.44
MA-7	0.11	0.15	0.23	0.31	0.49	0.69
Face Velocity FPM	585	705	860	1000	1255	1490

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Model LA

Rectangular Sound Attenuator

Dynamic Insertion Loss

Silencer Model No.	Octave Bands	2	3	4	5	6	7	8
	Center Frequency	125	250	500	1000	2000	4000	8000
	Face Velocity FPM	Net Insertion Loss in Decibels (dB)
LA-3	-1500	5	11	23	41	26	14	7
	-1000	5	10	22	41	26	14	8
	0	4	9	22	41	26	15	10
	+1000	4	9	22	40	26	16	10
	+1500	4	8	20	38	26	17	9
LA-5	-1500	7	15	31	47	40	18	10
	-1000	9	16	33	50	43	21	13
	0	6	13	30	47	40	21	11
	+1000	6	12	29	46	41	22	13
	+1500	6	12	27	44	41	23	13
LA-7	-1500	13	20	34	52	48	25	14
	-1000	13	19	37	51	51	28	14
	0	12	18	37	53	50	30	15
	+1000	12	17	35	52	49	28	15
	+1500	12	17	34	50	49	29	17

Self-Noise Sound Power Ratings (P.W.L.) — (dB re 10^-12 watts)

Silencer Model No.	Octave Bands	2	3	4	5	6	7	8
	Center Frequency	125	250	500	1000	2000	4000	8000
	Face Velocity FPM	Self Noise Sound Power Levels in Decibels (dB)
LA-3 LA-5 LA-7	-2000	59	56	55	57	61	47	47
	-1000	45	41	44	44	39	28	28
	+1000	45	36	35	37	32	26	28
	+2000	57	52	49	49	54	52	45

Face Area Adjustments	Area (sq.ft.)	2	4	8	16	32
	Adjustment	– 3	0	+ 3	+ 6	+ 9

Air Flow Performance Data

Model	Static Pressure Loss (inches WG)
LA-3	0.02	0.03	0.07	0.09	0.14	0.20
LA-5	0.03	0.04	0.08	0.11	0.17	0.25
LA-7	0.04	0.06	0.11	0.15	0.24	0.34
Face Velocity FPM	490	610	860	1000	1255	1500

Model SC-C

Round Sound Attenuators

Engineering Data

Round Sound Attenuators from Spiral Pipe of Texas are double-wall construction with the outer shell of galvanized spiral pipe 8” larger than the inside perforated liner. The center absorber is designed with a spun metal head and cone-shaped tail for maximum attenuation and optimum pressure drop. The attenuator is filled with 4#/ft3 mineral fiber insulation.

Standard models are available in 12” through 60” diameter. They are sized to fit ductwork without other transitions. Other materials and flanged ends are available as an option (contact factory for more information).

Ordering Information: Give model number and inside diameter (in inches). Standard length is 2 X diameter unless otherwise stated. Overall length of the unit is 4” longer (including 2” slip collar at each end). If flanged ends are added as an option, the overall make-up length is (2 x dia.) + 4”.

Our sound attenuators have been tested in an independent testing laboratory and in accordance with ASTM Standard E477. For selection and comparison, our data is published for five face velocities — zero flow, 1000 FPM (+ and -) and 2000 FPM (+ and -). Self-Noise Sound Power Ratings are published for four referenced velocities (less zero flow where no self-noise is generated). Using our Air Flow Performance Data, you can obtain the applicable static pressure loss (Pd) if your actual CFM is known, using the following equations:

In an ongoing effort to improve our products, Spiral Pipe of Texas reserves the right to revise the design and specifications at any time.

Dynamic Insertion Loss

Silencer Model No.	Octave Bands	2	3	4	5	6	7	8
	Center Frequency	125	250	500	1000	2000	4000	8000
	Face Velocity FPM	Net Insertion Loss in Decibels (dB)
SC-C	-2000	9	13	22	33	35	22	17
	-1000	9	12	22	32	34	21	16
	0	7	11	21	32	34	22	18
	+1000	7	11	20	31	34	22	18
	+2000	7	10	19	30	33	21	18

Self-Noise Sound Power Ratings (P.W.L.) — (dB re 10^-12 watts)

Silencer Model No.	Octave Bands	2	3	4	5	6	7	8
	Center Frequency	125	250	500	1000	2000	4000	8000
	Face Velocity FPM	Self Noise Sound Power Levels in Decibels (dB)
SC-C	-2500	60	57	59	59	62	55	48
	-2000	56	52	55	56	56	46	39
	+2000	53	49	45	44	42	34	30
	+3000	61	58	55	53	53	50	44

Face Area Adjustments	Diameter	12″	18″	24″	36″	48″	60″
	Adjustment (dB)	– 6	– 3	0	+ 3	+ 6	+ 8

Air Flow Performance Data

Model	Static Pressure Loss (inches WG)
SC-C	0.027	0.04	0.11	0.17	0.245	0.33
Face Velocity FPM	1000	1500	2000	2500	3000	3500

Sound Attenuator Performance

Sound attenuators can be an effective method for reducing unwanted noise in HVAC systems and other applications. At Spiral Pipe of Texas, we have tested our products at an independent laboratory and in accordance with ASTM Standard E477 test standards. When designing a system using sound attenuators, it is important to understand the terminology, the purpose of the data we provide, and a few design criteria that will help you get the results you need.

Terminology

Noise – to put it simply, noise is unwanted sound. Sound attenuators are designed to reduce or eliminate noise. But how we define noise can get a little complicated.

Frequency – sound is a vibration — or “variation of pressure” — occurring as a frequency (cycles or fluctuations per second). The human ear can respond to a wide range of sound frequencies (the “audible range”) from 20 Hz to 20,000 Hz (Hz or Hertz is a unit of frequency corresponding to one cycle per second).

Octave Bands – we usually are not dealing with “pure tones” — sound occurring on a single frequency. For HVAC applications, we deal with what is referred to as “broadband noise”. Noise is usually “louder” (greater sound pressure) at different frequencies than others. Sound attenuators are also more-or-less effective at different frequencies. In addition, the amount we typically object to noise varies between frequencies. To simplify our understanding and treatment of noise, we divide the audible range into “octave bands”. If you’ve ever had musical training you will be familiar with the term “octave”. Basically, each octave is a doubling of frequency over the previous octave. We measure at the “center frequency” of each octave and nine octave bands cover the audible range. We use numbers 2 through 8.

Octave Bands	1	2	3	4	5	6	7	8	9
Center Frequency (Hz)	62.5	125	250	500	1,000	2,000	4,000	8,000	16,000

Sound Pressure – “sound pressure” and “sound pressure level” are two terms that allow us to quantify what our ears perceive as “loudness”. When you consider sound as a variation or fluctuation in pressure, sound pressure is the amount — or amplitude — of that fluctuation. The accepted unit of measurement for sound pressure is Newtons per square meter (N/m2). Our ears are receptive to a very wide range of these fluctuations in everyday life, ranging from about 0.00006 N/m2 (6 x 10-5), which is considered the threshold of good hearing, all the way to 6.3 N/m2 (a loud rock band) which is considered the threshold of discomfort.

However, the way we perceive these fluctuations as “loudness” is not linear. As amplitude increases our ears become less responsive to the increase. Doubling the sound pressure does not double the “loudness”. To simplify this, we have borrowed the term “decibels” (dB) from electrical and illumination engineering to create a numerical correlation between the changes in sound pressure and changes in perceived “loudness”. The equation is as follows:

P = the root mean squared (RMS) value of the sound pressure fluctuations in N/m²
Pref = a standard reference sound pressure equal to 2 x 10^-5 N/m²

The following is a representation of some typical sound pressure levels and their decibel values.

Sound Pressure Level (dB)	Source	Subjective Reaction	Sound Pressure (N/m2)
0	Threshold of excellent youthful hearing	Threshold of hearing	0.00002 M/m2
10	Threshold of good hearing		0.00006 N/m2
20	Buzzing insect at 3 feet	Faint	0.0002 N/m2
30	Whispered conversation at 6 feet		0.0006 N/m2
40	Quiet residential area (ambient)		0.002 N/m2
50	Window air conditioner (ambient)	Moderate	0.006 N/m2
60	Conversational speech at 3 feet		0.02 N/m2
70	Freight train at 100 feet		0.06 N/m2
80	Computer printout room	Loud	0.2 N/m2
90	Unmuffled large diesel engine at 130 fe	et           Very loud	0.6 N/m2
100	Platform of subway station		2 N/m2
110	Loud rock band	Threshold of discomfort	6.3 N/m2
120	Passenger ramp at jet airliner (peak)	Threshold of pain	20 N/m2
130	Artillery fire at 10 feet	Extreme danger	63.2 N/m2
140	Military jet takeoff at 100 feet	You went too far	200 N/m2

Sound Power – sound is energy. And as the force of acoustical energy increases, we perceive an increase in “sound power”. If you grew up coveting high-end stereo equipment you should readily understand this concept. Both a cheap and high-end amplifier can be cranked up to an equally “loud” level. But there is a perceptible difference in the “sound power” coming from the one producing more energy. This “sound power” is expressed in terms of watts of power (remember wanting the amplifier with more “watts per channel). But as a practical matter, the range of sound power, expressed in watts, that we perceive in everyday life covers an extremely wide range — from as little as 0.00000000001 (10-11) watts up to 100,000,000 (108) watts. We needed a shorthand for this, so we once again borrowed the term “decibels” (dB). This describes an exponential increase in sound power with a standard reference sound power of 10-12 watts. Sound power level in decibels is determined by the following equation:

W = Sound Power in watts
Wref = 10-12 watts (standard reference)

Example Sound Power Levels:

Sound Power Level (dB re: 10-12 watts)	Example	Sound Power (watts)
10 dB	Human Breath	10-11
30 dB	Voice in Soft Whisper	10-9
70 dB	Voice at Conversational Level	10-5
90 dB	Voice Shouting	10-3

Now, all of this may be starting to get confusing. We’ve just used the same term (decibels) to quantify two completely different things — “sound pressure” (loudness) and “sound power” (energy). And in HVAC, why do we even care about “energy” when all we want is to make the system “less loud”? The reason we care is that “sound pressure” only has a significance at the point at which it is measured. This “sound” is just a series of air pressure waves that is radiating outward from a noise source. And these pressure waves are a result of acoustical energy transfer from the noise source to the surrounding air. We need a way of predicting how that noise source is perceived at different locations and conditions. After all, our building occupants are not standing next to the fan.

In HVAC applications, our concern is that noise follows a “path” — our duct system — from the source to where it is perceived, and we want to know how much of that “sound energy” reaches the end. Some of it simply leaves the duct — what we refer to as breakout noise. This leads to the somewhat misleading claims made by fabric and flexible duct manufacturers that their products are “sound attenuating”. In reality, little sound energy was actually lost. These materials are simply not capable of containing and transporting the sound energy, so it “breaks out” soon after entering these ducts and into that surrounding space. Metal ducts are much more effective at containing and transporting sound energy — just as they’re more effective at containing and transporting air.

Fortunately for us in our efforts to reduce “noise”, much of that acoustical energy can be lost — or attenuated — as it is transported through the duct system. Some is lost through breakout, and this is greatly affected by the shape and rigidity of the duct (rectangular duct walls vibrate much more readily than round or flat oval duct walls — which can be a bad thing). Friction and reflection account for a significant portion of the rest. The use of sound-absorptive media — such as fiberglass insulation or liner — will also greatly decrease acoustical energy. Information on attenuation of various types of ducts can be found in the 2015 ASHRAE Handbook — HVAC Applications (chapter 48 “Noise and Vibration Control”).

When our duct system cannot dissipate enough of our acoustical energy between the noise source and our target space, an effective option can be the use of a sound attenuator. The sound attenuators offered by Spiral Pipe of Texas are known as dissipative silencers. They use a sound-absorptive media (mineral fiber or fiberglass) as the primary means of attenuating sound. A baffle or series of baffles disrupts the path and increases the amount of contact between the sound path (or airflow path) and the transported sound energy. The absorptive media is covered by perforated metal, and in some cases fiberglass cloth or polymer film, to protect it from erosion by airflow. By disrupting the airflow, sound attenuators have an effect on air flow and system pressure.

Narrower paths between baffles and attenuator walls increase the loss of sound energy, but also increase the loss of duct static pressure. Specially designed nose pieces and tail cones can decrease the static pressure loss by reducing air turbulence. The location of a sound attenuator can also greatly impact both attenuation and pressure loss. Sound attenuators should generally be located as close to the noise source as possible, but far enough away to have a uniform, laminar profile of air flow. One common mistake is to locate a sound attenuator too close to a fan. The result is system effect — highly turbulent air with much greater pressure drop and irregular flow profile. Not only is the attenuator less effective at absorbing sound energy, the turbulence can cause the sound attenuator to generate more noise than it attenuates. The recommendation is to locate the sound attenuator with 3 to 5 diameters of straight, unobstructed duct on both inlet and discharge ends, or located at the plenum discharge/inlet with unobstructed duct at the ducted end for 3 to 5 diameters.

Now that we’ve covered some of the basics of acoustics and noise control, we need to go over how to use the information published by sound attenuator manufacturers. Spiral Pipe of Texas has had their sound attenuators independently tested with procedures outlined in ASTM Standard E477 as recommended by ASHRAE. We strongly encourage using only sound attenuators tested consistent with these procedures, and recommend independent testing for consistent and verifiable results. Our testing was performed at ETL Testing Laboratories, Inc. (Cortland, NY), a widely respected facility, and results are available upon request. Using ASTM Standard E477, performance is measured and reported as “insertion losses”.

Because these employ a substitution technique — the sound attenuator is substituted for an equal length of standard duct — we can have reasonably precise values for dynamic insertion losses, airflow-generated noises and airflow static pressure losses (see 2015 ASHRAE Handbook chapter 48 for deviation and confidence results based on round-robin testing). The following information is published for sound attenuators from Spiral Pipe of Texas:

Dynamic Insertion Loss – these are presented as a chart showing the net insertion loss (in decibels) of a sound attenuator in the second through eighth octave bands. These are “sound power” decibels – the ones referring to watts of acoustic energy that are attenuated. This insertion loss is “dynamic” because performance changes under different flow rates and conditions. We publish our net insertion loss in decibels in five flow conditions — two negative velocities, two positive velocities and no flow.

Self-Noise Sound Power Ratings – as previously stated, sound attenuators disrupt the flow profile of air and the resulting turbulence creates noise. This is not an issue when there is no flow, so we publish noise created in four flow conditions — two negative velocities and two positive velocities.

Face Area Adjustment – size impacts the self-noise generation of a sound attenuator, but all potential sizes are not listed. A face area adjustment table is provided to make the needed corrections. Determine the face area of the sound attenuator (ft2). Then take the applicable “adjustment” from the table and add it to each octave band number for self-noise sound power ratings.

The adjusted airflow-generated Self-Noise Sound Power Ratings represent the noise floor — the lowest level achievable, regardless of high insertion loss values. It is logarithmically proportional to the sound attenuator’s cross sectional area, but it generally does not vary with silencer length.

Air Flow Performance Data (static pressure loss in inches WG) – the actual static pressure loss does change with both length and velocity. Since sound attenuator model numbers are associated with length, values are given for each model. Static pressure losses are presented in the tables for six reference face velocities. If you know your actual flow volume (CFM) you can determine your actual static pressure using the following two correction equations:

Face Velocity = CFM / Area (ft²)

Actual Static Pressure Loss = Pd = (Face Velocity/Referenced Table Velocity)² X Table Pressure Loss