NISTIR 7467 

Full Ensemble and Bench Scale 

Testing of Fire Fighter 

Protective Clothing

David W. Stroup 

Roy A. McLane 

William H. Twilley 

Sponsored in part by 

Department of Homeland Security

NISTIR 7467 

Full Ensemble and Bench Scale 

Testing of Fire Fighter 

Protective Clothing

David W. Stroup 

Roy A. McLane 

William H. Twilley 

Fire Research Division 

Building and Fire Research Laboratory 

National Institute of Standards and Technology 

Gaithersburg, MD 20899-8661 

November 2007 

Department of Homeland Security 

Michael Chertoff, Secretary 

Federal Emergency Management Agency 

R. David Paulison, Administrator 

United States Fire Administration 

Gregory B. Cade, Assistant Administrator 

U.S. Department of Commerce 

Carlos M.Gutierrez, Secretary 

National Institute of Standards and Technology 

James M. Turner, Acting Director 
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Table of Contents 

 Page

Abstract........................................................................................................................................... 1

1. Introduction................................................................................................................................ 1

2. Test Apparatus............................................................................................................................ 2

2.1 Bench Scale Apparatus ........................................................................................................ 2

2.2 Full Ensemble Test Apparatus............................................................................................. 3

3. Test Specimens........................................................................................................................... 4

3.1 Turnout Gear Material Mock-up.......................................................................................... 4

3.2 Fire Fighter Ensemble.......................................................................................................... 5

4. Fire Model.................................................................................................................................. 7

5. Test Results ................................................................................................................................ 8

5.1 Mock-up Samples ................................................................................................................ 8

5.1.1 Bench Scale Test Apparatus ......................................................................................... 8

5.1.2 Full Ensemble Test Apparatus...................................................................................... 9

5.2 Full-Scale Mannequin Tests .............................................................................................. 10

6. Analysis and Discussion .......................................................................................................... 12

6.1 Test Data Comparisons...................................................................................................... 13

6.2 Model Comparisons........................................................................................................... 14

7. Uncertainty Analysis................................................................................................................ 16

8. Conclusions.............................................................................................................................. 19

9. Acknowledgments.................................................................................................................... 20

10. References.............................................................................................................................. 20
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List of Figures 

 Page

Figure 1. Photograph of bench scale test apparatus with gas fired radiant panel 

operating and turn out gear mock-up sample in place .......................................... 22 

Figure 2 Sketch showing the bench scale test apparatus..................................................... 23 

Figure 3. Plan view of test apparatus including radiant panels and trolley assembly.......... 24 

Figure 4. Elevation view of test apparatus including radiant panels and trolley 

assembly................................................................................................................ 25 

Figure 5. Photograph of radiant panels and radiation shield with trolley mounted 

heat flux gauge...................................................................................................... 26 

Figure 6. Photograph of the preconditioning chamber......................................................... 27 

Figure 7. Photograph of mannequin positioned in front of the radiant panels..................... 28 

Figure 8. Photograph of turnout gear mock-up .................................................................... 29 

Figure 9. Drawing of the turnout gear mock-up sample holder ........................................... 30 

Figure 10. Photograph of the turnout gear mock-up sample holder with test sample............ 31 

Figure 11. Photograph showing mannequin without coat and instrumentation (heat 

flux gauge and thermocouples)............................................................................. 32 

Figure 12. Drawing showing thermocouple locations on the outside of the back of the 

turnout gear shell (Front Surface)......................................................................... 33 

Figure 13. Drawing showing thermocouple locations on the inside of the turnout coat 

shell (Mid-Point)................................................................................................... 34 

Figure 14. Drawing showing thermocouple locations on the inside of the thermal 

liner adjacent to the moisture barrier (Back Surface) ........................................... 35 

Figure 15. Drawing showing thermocouple locations on the outside of the 

workstation shirt (Shirt) ........................................................................................ 36 

Figure 16. Graph showing temperatures measured on the front of the mock-up shell 

material for each test conducted using the bench scale test apparatus ................. 37 

Figure 17 Graph showing temperatures measured on the back of the mock-up shell 

material for each test conducted using the bench scale test apparatus ................. 38 

Figure 18 Graph showing temperatures measured on the front of the mock-up 

thermal liner material for each test conducted using the bench scale test 

apparatus ............................................................................................................... 39 

Figure 19. Graph showing temperatures measured on the back of the mock-up 

thermal liner material for each test conducted using the bench scale test 

apparatus ............................................................................................................... 40 

Figure 20 Graph showing average temperatures measured for each of the six mockup samples using the bench scale test apparatus (TC2 eliminated for 

clarity)................................................................................................................... 41 

Figure 21 Graph showing average temperatures measured through mock-up shell 

samples using the bench scale test apparatus........................................................ 42 

Figure 22 Drawings of heat flux gauge and mock-up trolley showing the mock-up in 

position and the dimensions.................................................................................. 43 
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Figure 23. Photograph of radiation shield in place in front of the radiant panels.................. 44 

Figure 24. Graph showing the data from the thermocouple attached to the front of the 

mock-up shell material for all tests using the full ensemble test apparatus.......... 45 

Figure 25. Graph showing the data from the thermocouple attached to the back of the 

mock-up shell material for all tests using the full ensemble test apparatus.......... 46 

Figure 26. Graph showing the data from the thermocouple attached to the front of the 

mock-up thermal liner material for all tests using the full ensemble test 

apparatus ............................................................................................................... 47 

Figure 27. Graph showing the data from the thermocouple attached to the back of the 

mock-up thermal liner material for all tests using the full ensemble test 

apparatus ............................................................................................................... 48 

Figure 28. Graph showing the average temperatures obtained at the four 

thermocouple locations during the mock-up test using the full ensemble 

test apparatus......................................................................................................... 49 

Figure 29. Graphs showing temperatures measured through mock-up samples for the 

following orientations: vertical at 0.91 m (2.97 ft), vertical at 0.93 m (3.1 

ft), 20 degree angle at 0.91 m (2.97 ft), and 20 degree angle at 0.93 m (3.1 

ft)........................................................................................................................... 50 

Figure 30. Graph of temperatures through turnout coat and work station shirt for 

thermocouples associated with external thermocouple #16 when exposed 

to an external radiant flux of 2.5 kW/m2

 and no elevated temperature 

preconditioning ..................................................................................................... 51 

Figure 31. Graph of temperatures through turnout coat and work station shirt for 

thermocouples associated with external thermocouple #17 when exposed 

to an external radiant flux of 2.5 kW/m2

 and no elevated temperature 

preconditioning ..................................................................................................... 52 

Figure 32. Graph of temperatures through turnout coat and work station shirt for 

thermocouples associated with external thermocouple #18 when exposed 

to an external radiant flux of 2.5 kW/m2

 and no elevated temperature 

preconditioning ..................................................................................................... 53 

Figure 33. Graph of temperatures through turnout coat and work station shirt for 

thermocouples associated with external thermocouple #19 when exposed 

to an external radiant flux of 2.5 kW/m2

 and no elevated temperature 

preconditioning ..................................................................................................... 54 

Figure 34. Graph of temperatures through turnout coat and work station shirt for 

thermocouples associated with external thermocouple #20 when exposed 

to an external radiant flux of 2.5 kW/m2

 and no elevated temperature 

preconditioning ..................................................................................................... 55 

Figure 35. Graphs of average temperatures through turnout coat and work station 

shirt for thermocouples associated with the five external thermocouple 

locations when exposed to an external radiant heat flux of 2.5 kW/m2 and 

preconditioned at 60 oC......................................................................................... 56 

Figure 36. Graphs of average temperatures through turnout coat and work station 

shirt for thermocouples associated with the five external thermocouple 
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locations when exposed to an external radiant heat flux of 2.5 kW/m2

 and 

with no elevated temperature preconditioning...................................................... 57 

Figure 37. Graphs of average temperatures through turnout coat and work station 

shirt for thermocouples associated with the five external thermocouple 

locations when exposed to an external radiant heat flux of 2.5 kW/m2

 and 

preconditioned at 50 oC......................................................................................... 58 

Figure 38. Graphs of average temperatures through turnout coat and work station 

shirt for thermocouples associated with the five external thermocouple 

locations when exposed to an external radiant heat flux of 2.5 kW/m2 and 

preconditioned at 60 oC......................................................................................... 59 

Figure 39. Graph showing average temperatures obtained at the four thermocouple 

locations for the mock-up tests using the bench scale apparatus (labeled 

224) and the full ensemble test apparatus (labeled 205)....................................... 60 

Figure 40. Graph showing the decay of the flux field with movement in the vertical 

direction (heat flux source on right side of graph)................................................ 61 

Figure 41. Graph showing the decay of the flux field with movement away from the 

radiant panels (heat flux source is 0.91 m away from the panel on right 

side of graph) ........................................................................................................ 62 

Figure 42. Graph showing comparison between temperatures measured through 

turnout gear at thermocouple #16 location and data from mock-up samples 

in both the full ensemble test apparatus (labeled 205) and the bench scale 

apparatus (labeled 224)......................................................................................... 63 

Figure 43. Graph showing calculated temperatures for a mock-up exposed to a 2.5 

kW/m2

 heat flux using the default parameters in the heat transfer model 

[12]........................................................................................................................ 64 

Figure 44. Graph showing calculated temperatures for a mock-up exposed to a 2.5 

kW/m2 heat flux using the default parameters in the heat transfer model 

[12] except the air gaps are half the size............................................................... 65 

Figure 45. Graph showing calculated temperatures for a mock-up exposed to a 3 

kW/m2

 heat flux using the default parameters in the heat transfer model 

[12]........................................................................................................................ 66 

Figure 46. Graph showing calculated temperatures for a mock-up exposed to a 2.5 

kW/m2

 heat flux using the default parameters in the heat transfer model 

[12] except with a 75 oC ambient background temperature.................................. 67 

Figure 47. Graph comparing measured (Avg TC 16, Avg TC 1) and calculated 

temperature distributions through a turnout coat when exposed to a 2.5 

kW/m2

 heat flux using the full ensemble test apparatus....................................... 68 

Figure 48. Graph comparing measured (TC 1, TC 2, TC 3, TC 4) and calculated 

temperature distributions through a mock-up assembly when exposed to a 

2.5 kW/m2

 heat flux using the full ensemble test apparatus................................. 69 
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List of Tables 

 Page

Table 1. Thermal Properties of Mock-up Materials....................................................................... 5 

Table 2. Thermal Properties of Fire Fighter Ensemble Materials ................................................. 6 

Table 3. Summary of Air and Water Physical Properties.............................................................. 8 

Table 4. Estimated Uncertainty in Experimental Data ................................................................ 17 
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Full Ensemble and Bench Scale 

Testing of Fire Fighter Protective Clothing 

David W. Stroup, Roy A. McLane, and William H. Twilley 

Abstract 

The Thermal Protective Performance (TPP) test was developed to quantify the performance of 

fire fighter protective clothing ensembles under an intense thermal exposure. This test method 

has certainly helped to improve the thermal protection of fire fighter protective clothing. 

However, many fire service burn injuries can be traced to significantly lower thermal exposures 

than are simulated by the TPP test. A bench scale test method has been developed to evaluate 

the performance of fire fighter protective clothing at low heat fluxes. In addition, a full scale test 

apparatus capable of exposing both complete fire fighter ensembles and samples similar to those 

used in the bench scale test to various heat flux levels is under development. Both of these tests 

provide temperature measurements on the surface of the outer shell, at locations between the 

fabric or moisture barrier layers inside the protective clothing system, and at the thermal liner 

surface. When plotted, these temperature measurements show a detailed picture of how a 

protective clothing system performs when exposed to a given thermal environment. This report 

describes comparisons of results obtained using the bench scale test with data from the full-scale 

test apparatus. The data are also compared to results from a fire fighter protective clothing heat 

transfer model. 

Key Words: burns (injuries); fire fighters; fire fighting equipment; heat transfer; large scale fire 

tests; mannequins; protective clothing; test methods; thermal protective performance (TPP) test 

1. Introduction 

Every year, approximately 100 fire fighters die in the line of duty, and 90 000 to 100 000 are 

injured [1]. In 1999, the United States Fire Administration estimated that approximately half of 

these fatalities were caused by stress and heart attacks [2]. While not the leading cause of 

fatalities, burns do represent a significant number of fatalities and injuries. Recent reports on fire 

fighter deaths and injuries indicate that burns accounted for approximately 7 % of fire fighter 

fatalities [3] and 8.5 % of fire fighter injuries [4]. 

Fire fighter protective clothing is designed to provide the wearer with a limited amount of 

protection from burn injury. Burn injuries can occur from exposure to the heat produced by a 

fire through contact with flames, hot combustion gases, steam, burning items, or any 

combination of these conditions. Fire fighters can also receive burn injuries when their 

protective garments become compressed as a result of contact with hot objects or when 

movement compresses clothing material against the skin [5]. Test methods that quantify the 
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thermal performance of fire fighter protective clothing are specified in Standard on Protective 

Ensembles for Structural Firefighting and Proximity Fire Fighting, NFPA1971 [6]. Two 

thermal performance test methods found in NFPA 1971 have had a significant impact on 

improving the performance of fire fighters protective clothing. The Fabric Flammability Test 

(FFT) has resulted in the development of protective garments that resist flaming ignition. The 

second test, the Thermal Protective Performance (TPP) method has helped in the design of 

protective garments that reduce the rate of heat flow from a fire-fighting environment through 

the protective clothing. 

The TPP test measures heat flow through a garment while exposed to a heat flux of 

approximately 83 kW/m2

 that is intended to simulate exposure to a flashover fire. A single 

copper calorimeter is used to measure heat transfer through a protective clothing assembly. 

Work by Krasny et al., suggests that fire fighters will likely receive serious burn injuries in less 

than 10 seconds when exposed to a heat flux of 83 kW/m2

 [7]. Fortunately, very few fire fighters 

are exposed to flashover conditions. Most fire fighter burn injuries appear to result from thermal 

exposures much less severe than the flashover conditions used by the TPP test. In addition, 

many of these burn injuries appear to result from relatively long duration exposures to low or 

moderate heat fluxes [8]. 

As part of a project funded by the United States Fire Administration, the Building and Fire 

Research Laboratory (BFRL) at National Institute of Standards and Technology (NIST) is 

exploring the feasibility of developing new apparatus for evaluation of the thermal performance 

of fire fighter protective clothing. This test apparatus would be capable of measuring the thermal 

performance of fire fighters’ protective clothing over a wide range of thermal environmental 

conditions and over extended time periods. A bench scale test apparatus, using combinations of 

protective clothing material approximately 0.38 m (1.3 ft) square, has been developed [8]. A full 

scale apparatus that utilizes the full ensemble of protective clothing mounted on a mannequin to 

more effectively examine the complex geometric interactions of the protective clothing and the 

potential for various burn injuries is under development. 

This report presents the results of tests conducted using turn out gear mock-ups in both the bench 

scale apparatus and the full scale test apparatus. In addition, data obtained from the mock-up 

tests is evaluated against results from tests of complete fire fighter ensembles in the full scale test 

apparatus. Finally, the experimental data are compared to calculations from a mathematical 

computer model of heat transfer through fire fighter protective clothing systems. 

2. Test Apparatus 

2.1 Bench Scale Apparatus

A bench scale test apparatus has been developed that allows for eva1uating the thermal 

performance of protective clothing systems exposed to heat flux environments ranging from 

1.5 kW/m2

 to 50 kW/m2 [8]. A photograph of the test apparatus is shown in Figure 1. A side 
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view sketch of the apparatus is shown in Figure 2. The heat flux exposure is provided by a 

premixed air/natural gas fueled radiant panel with a radiating surface measuring 305 mm by 

457 mm (12 in by 18 in). The radiant panel is normally operated at an average surface 

blackbody temperature of 670 °C (1238 °F). The apparatus has a propane fueled pilot flame that 

may also be directed onto a test specimen to evaluate thermal performance associated with direct 

flame contact. The flame height (length) may be adjusted to a low level for determining if 

fabrics or surface finishes will ignite or the height may be increased to sweep across a specimen's 

complete surface. Thermocouples are used to measure temperatures at any location of interest 

on or inside the test specimen assembly during the test time period. Test specimens are mounted 

on a movable trolley assembly that is attached to the radiant panel test frame. Positioning of the 

trolley allows for adjustment of radiant flux exposures and provides the ability to expose test 

specimens to radiant energy environments that can be increased or decreased during a test. The 

apparatus has the ability to test wet clothing so that the effects of moisture can be studied. 

2.2 Full Ensemble Test Apparatus

A test apparatus for evaluating the thermal performance of complete fire fighter protective 

clothing ensembles is being developed. The apparatus consists of two radiant panels, a trolley 

assembly, and a preconditioning chamber. The radiant panels and trolley assembly are shown in 

plan and elevation views in Figures 3 and 4, respectively. The radiant panels with a trolley 

mounted heat flux gauge positioned in front of them are shown in Figure 5. The preconditioning 

chamber is shown in Figure 6. 

The preconditioning chamber is a commercially manufactured convection oven that has been 

modified to accommodate the mannequin and trolley assembly. The preconditioning chamber 

has a heat input of 30 kW and a maximum temperature rating of 340 °C (650 °F). Outside 

dimensions are 1.7 m (5.6 ft) wide, 2.1 m (7 ft) deep and 2.1 m (7 ft) tall, while inside 

dimensions are 1.2 m (4 ft) wide, 1.2 m (4 ft) deep, and 1.9 m (6.3 ft) tall. To facilitate a 

uniform temperature within the chamber a variable speed motor operates a fan inside the 

chamber, providing a constant circulation of interior air. Two electric resistance heating panels, 

each measuring 2.0 m (6.6 ft) high by 0.3 m wide (1.0 ft), produce the radiant energy used to 

expose the mannequin. A radiation shield (Figure 5) is placed in front of the two radiant panels 

to completely block the radiant energy from reaching the mannequin while it travels from inside 

the preconditioning chamber to the test position. This radiation shield consists of two thin 

aluminum sheets 0.5 mm (0.020 in) thick, mounted on an aluminum frame 0.66 m (2.2 ft) by 

2.2 m (7.2 ft). This frame is designed with an air gap between the two aluminum sheets of 

0.044 m (0.1 ft). Two hinged arms attached to this frame and base support tubes allow this panel 

to be moved quickly from in front of the radiant panels. The trolley assembly, used to move the 

mannequin from the preconditioning chamber to the test, consists of an aluminum plate 0.71 m 

(2.3 ft) by 0.71 m (2.3 ft) with four aluminum wheels attached. Two of these wheels have angled 

cuts into their circumference which engage a corresponding reverse angle on the trolley way. 

The trolley rides atop one aluminum rail made of flat stock 0.05 m (0.17 ft) wide and a second 

rail made from an inverted aluminum angle that mates with the inverted angle wheel to guide the 

mannequin trolley. 
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A complete fire fighter ensemble including self contained breathing apparatus (SCBA), if 

desired, can be mounted on a full sized commercial clothing store mannequin (Figure 7) for 

testing. The mannequin is 1.7 m (5.6 ft) tall, with a chest measurement of 0.91 m (3 ft), waist of 

0.81 m (2.7 ft), sleeve length of .0.81 m (2.7 ft), and an inseam of 0.71 m (2.3 ft). The 

mannequin and clothing ensemble can be thermally preconditioned from 25 oC (77 oF) to 100 oC 

(212 oF) before being exposed to a radiant heat flux ranging from 1.5 kW/m2

 to 10 kW/m2. 

Measurement data obtained using this test apparatus can provide a time/temperature response 

history for components of the protective clothing ensemble. Thermocouples are used to measure 

temperature at various locations of interest on or inside the clothing ensemble. The data obtained 

from this test can also be used for determining the latent heat or amount of energy stored in the 

garment ensemble, when exposed to a heat flux. Mock-up ensembles can be evaluated on this 

apparatus and can be correlated with the same mock-up ensembles tested on the bench scale test 

apparatus. 

3. Test Specimens 

3.1 Turnout Gear Material Mock-up

One type of test specimen can be used in both the bench scale test apparatus and the full 

ensemble test apparatus. This test specimen consisted of a three layer mock-up of a fire fighter 

clothing ensemble (Figure 8). The mock-up samples were composed of a flame resistant fabric 

shell of polybenzimidazole, known commercially as PBI, with an average dry weight of 

0.235 kg/m2 (6.9 oz/yd2), a breathable moisture barrier with an average dry weight of 

0.130 kg/m2

 (3.8 oz/yd2), and a quilted thermal liner with an average dry weight of 0.249 kg/m2

(7.3 oz/yd2). Each material measured 0.280 .m (0.92 ft) x 0.25.m (0.83 ft). The thermal and 

optical properties of similar materials used in fire fighter turnout ensembles have been measured 

[9]. The properties of the materials used in the mock-up samples are summarized in Table 1. 

In all of the mock-up tests, type K, Chromel Alumel∗

 thermocouples with a wire diameter of 

0.254 mm (0.010 in) and fiberglass braid insulation were used. These thermocouples were sewn 

on to the various layers using a procedure previously described [8]. A single thermocouple was 

sewn on or near the center of the sample on the outer face of the shell material (side closest to the 

heat source). The exact location of this thermocouple was dictated by the quilting on the thermal 

liner. The thermocouple on the shell was positioned so as to prevent the thermocouple behind it 

on the thermal liner from being in the stitching of the quilting pattern. A second thermocouple 

was sewn onto the backside of the shell material, 4 mm (0.160 in) to the side of the front 

thermocouple. No thermocouples were attached to the moisture barrier, as the needle holes 

 

∗ Certain commercial equipment, instruments, or materials are identified in this paper to foster understanding. Such 

identification does not imply recommendation or endorsement by the National Institute of Standards and 

Technology, nor does it imply that the materials or equipment are necessarily the best available for the purpose. 
 - 5 - 

might constitute an atypical thermal path through this barrier. A third thermocouple was sewn 

on the front face of the thermal liner, behind and 4 mm (0.160 in) below the location of the other 

two thermocouples. Finally a fourth thermocouple was sewn onto the back of thermal liner 

4 mm (0.16 in) beside the third thermocouple location. This offsetting pattern of the 

thermocouples was an effort to minimize any effect the thermocouples might have on the heat 

transfer. 

Table 1. Thermal Properties of Mock-up Materials 

Property Shell Moisture 

Barrier 

Thermal 

Liner 

Thermal 

Conductivity 

(W/m °C) 

0.0007 T + 0.0354 0.0003 T + 0.0299 0.0003 T + 0.0304 

Specific Heat 

(J/g °C) 

-2E-7 T3

+0.0004 T2-0.037 T 

+1.8212 

2E-6 T3+7E-5 T2-0.0274 T 

+2.9263 

-7E-6 T3+0.0012 T2-0.0446 T 

+1.798 

Thickness 

(mm) 0.80 0.96 3.59 

Transmissivity 0.120 0.187 0.121 

Reflectivity 0.219 0.268 0.236 

Void Fraction 0.7 0.7 0.7 

Density (kg/m3) 321.8 143.1 74.2 

T – Material Temperature (°C) 

The three layers of fabric were mounted in a calcium silicate holder 0.36 m (1.2 ft) x 0.36 m 

(1.2 ft) x 0.013 m (0.04 ft) thick. The center of the holder had been cut 0.25 ft (0.83 ft) x 0.25 ft 

(0.83 ft) as the area exposed to the radiant heat source (Figures 9 and 10). This calcium silicate 

frame was then completely covered with one layer of 0.03 mm thick aluminum foil. The tests 

were conducted using an open back, i.e., the back of the thermal liner was open to the room air 

and not in contact with a piece of calcium silicate backing board or other backing material. Tests 

can be conducted in the bench scale test apparatus using either an open back or closed back 

specimen holder. The open back configuration allows the test operator to observe both sides of 

the test specimen for physica1 changes. The closed back configuration reduces heat loss from 

the backside by replacing the open back portion of the specimen holder with a backing board of 

calcium silicate. At 23 °C, calcium silicate has a thermal conductivity of 0.111 W/m °C, a 

specific heat of 778 J/kg °C and an approximate density of 670 kg/m3

. It is estimated that the 

actual thermal performance of fire fighters protective clothing falls between the open back and 

closed back configuration. 

3.2 Fire Fighter Ensemble

For the full ensemble apparatus tests, a complete set of fire fighter bunker gear (helmet, pants 

coat, boots, gloves, and hood) and a workstation shirt were used. The fire fighting coat was 

composed of an external shell made from a blend of 40 % PBI and 60 % Kevlar, a thermal liner 

made of “Caldura”, and a moisture barrier made of “E-89 Spunlaced”. Bunker pants were also 
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fitted to the mannequin although there was no instrumentation in these pants. The bunker pants 

are considered an integral part of the fire fighters protective ensemble and were included for 

completeness. The inclusion of pants also helped to ensure that the coat was fitted in a way that 

was representative of real world fire ground conditions. The bunker pants were composed of a 

shell material made of 0.255 kg/m2 (7.5 oz./sq yd.) Nomex III aramid, a moisture barrier coated 

with polycotton (65 % Polyester/35 % cotton), and a thermal liner made of 100 % aramid. 

The turnout coat on the mannequin and the mock-up sample materials were not an exact fabric 

for fabric match, but both the mock-ups and the turnout coat utilize PBI. The thermal and optical 

properties [9] of the turnout coat materials are summarized in Table 2. The material used as the 

thermal liner in the fire fighter turnout coat was not tested. This thermal liner material was 

produced by the same manufacturer that made the material used in the thermal liner portion of 

the mock-up sample. An examination of available manufacturer’s literature suggests that the 

material has a composition similar to the thermal liner material used for the mock-up tests. With 

the exception of weight, the materials have similar physical and fire resistance properties. The 

density of the thermal liner in the fire fighter coat was estimated based on the heavier material 

and shown in Table 2. 

Table 2. Thermal Properties of Fire Fighter Ensemble Materials 

Property Shell Moisture 

Barrier 

Thermal 

Liner 

Thermal 

Conductivity 

(W/m C) 

0.0007 T + 0.0354 0.0003 T + 0.0299 * 

Specific Heat 

(J/g °C) 

-2E-6 T3

+0.0004 T2-0.037 T 

+1.8212 

2E-6 T3+7E-5 T2-0.0274 T 

+2.9263 * 

Thickness 

(mm) 0.80 0.96 * 

Transmissivity 0.120 0.187 * 

Reflectivity 0.219 0.268 * 

Void Fraction 0.7 0.7 * 

Density (kg/m3) 321.8 143.1 83.3 

T – Material Temperature (°C) 

* - material not tested [9] 

A short sleeve workstation uniform shirt was placed on the mannequin underneath the firefighter 

coat. This workstation shirt was instrumented with thermocouples on the outside which 

approximately matched the locations of those thermocouples on the firefighter coat. The 

workstation shirt was composed of 55 % FFR (Fibrous Flame Retardant fabric) and 45 % cotton. 

The workstation shirt complied with the appropriate requirements of NFPA 1975, Station/Work 

Uniforms for Fire and Emergency Services [10]. Since the bunker pants were not instrumented, 

it was not necessary to provide any other clothing underneath the pants. 
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The workstation uniform shirt, turnout coat and bunker pants were fitted to the mannequin in 

such a way as to simulate as close as possible how these garments would fit an actual firefighter. 

The workstation shirt was open at the collar but the rest of the shirt was buttoned and tucked into 

the bunker pants. There was no “undershirt” or foundation garments. The coat was latched up 

completely and the collar was up, and all hook and loop fasteners were snugly closed. The head 

and neck were covered with a Nomex protective hood, which was also tucked into the coat, just 

as it would normally be used. A fiberglass fire service helmet was strapped to the mannequin’s 

head. A total heat flux gauge had been attached to the helmet and positioned along the centerline 

(spine) of the mannequin (Figure 11). This gauge was further aligned in the same horizontal 

plane as that of the thermocouples on the turnout coat. 

The time/temperature profile through each test specimen was then monitored using a series of 

thermocouples. Type K thermocouples with a wire diameter of 0.254 mm (0.010 in) were 

carefully sewn onto the surface of the various layers of fabric used to make up the ensemble. 

The heat flow as tracked by a set of four thermocouples was simultaneously monitored at five 

different locations. These thermocouples were used to measure heat flow through the firefighter 

coat and to the surface of the workstation shirt. 

The procedure used to prepare and attach the thermocouples to the turnout coat has been 

described previously [8]. The thermocouple locations on the turnout coat are shown in Figures 

12 - 15. As can be seen in Figure 12, there were five thermocouple locations on the back of the 

coat. At each of these locations, four thermocouples have been attached to the various layers of 

the coat and workstation shirt. This allowed for the evaluation of the thermal performance at 

several locations on the coat simultaneously. The first set of thermocouples was attached to the 

outer shell fabric; this was the outermost portion of the garment. Trim material was present on 

the outer portion of the coat, but the thermocouples were placed to avoid this additional layer of 

material. This thermocouple will be referred to as the front surface thermocouple. The second 

set of thermocouples was attached to the inside surface of the shell material, offset from the 

centerline of the garment by 5 mm (0.20 in). This set was identified as the mid-point 

thermocouples. The third set of thermocouples was attached to the thermal liner on the side 

closest to the wearer. These thermocouples were identified as the back surface thermocouples. 

These thermocouples are located on the centerline of the garment 5 mm (0.20 in) up above the 

front surface thermocouples. A fourth set of thermocouples was attached to the centerline of the 

outer surface of the workstation shirt about 10 mm (0.39 in) above the front surface 

thermocouples and identified as the shirt thermocouples. 

4. Fire Model 

A mathematical model has been developed to study the performance of fire fighter protective 

clothing when exposed to thermal radiation [11]. Mell and Lawson developed the first version of 

this model in 2000 [12]. The model was further developed and enhanced by Prasad, et al. [13]. 

The latest version of this model tracks the transient movement of heat and moisture through 

multiple layers of fabric. The model calculates the response of textile fabrics to an applied heat 
 - 8 - 

exposure. Heat is applied to the fabric as a combination of an external heat flux and an ambient 

gas temperature. The moisture in the fabric, the ambient environment, material properties and 

any air gaps are considered in the model. 

The model has been successfully compared to several sets of experimental data. Early 

comparisons indicated that “the model performed well, especially inside the garment” [12]. In 

the absence of fabric-specific optical properties, the predicted temperatures on the outside of the 

fire fighter material differed by as much as 24 °C from the experimental data while the 

temperatures inside where within 5 °C. A comparison of the improved model with moisture 

transport indicates agreement between predicted results and experimental data is within 5 %. 

When the model was used to predict results obtained from Thermal Protective Performance Test 

(TTP) [14], the model was determined to provide “good agreement” with experimental results 

[15]. 

In addition to the properties of the fabric materials, the physical properties of air and water must 

be specified to use the model. The air and water physical properties that were used for the model 

comparison discussed in this paper are summarized in Table 3 [16]. 

Table 3. Summary of Air and Water Physical Properties 

Property Air Water 

Thermal Conductivity 

(W/m oC) 26.3 x 10-3 0.61 

Specific Heat 

(J/g oC) 1.006 4.18 

Density (kg/m3) 1.177 995.8 

Viscosity (m2/s) 15.9 x 10-6 

5. Test Results 

5.1 Mock-up Samples

5.1.1 Bench Scale Test Apparatus 

A series of tests were conducted using a bench scale test apparatus described previously [8]. 

These tests were conducted using the established protocol for this test apparatus with three 

modifications. First, the sample holders used for these tests were made of a single piece of 

Bakelite plastic with an aluminum clamp to hold the fabrics in place. Second, the total heat flux 

gauge was not used with a calcium silicate board. The flux gauge was suspended from a rod 

attached to the trolley assembly in the bench scale apparatus. This configuration more closely 

resembled how the flux gauge was suspended when setting the radiant panel flux in the full-scale 

mannequin test apparatus. Third, no water was ever intentionally applied to the mock-up 

samples. The mock-up samples were environmentally conditioned at 23 °C (73 °F) and 50 % 

relative humidity. This did add some moisture to the mock-ups (approx. 5.2 % by weight) but no 
 - 9 - 

additional water was intentionally added. While the bench-scale test apparatus has the capability 

to expose the test sample to both a radiative flux and direct flame exposure, the mock-up samples 

were only exposed to a radiative flux; none were exposed to direct flames. The exposure heat 

flux was 2.5 kW/m2

. 

For these mock-up tests, four thermocouples were attached to the various material surfaces. One 

thermocouple (#1) was attached to the outside surface of the shell material closest to the radiant 

panel. A second thermocouple (#2) was attached to the inside of the shell. The third 

thermocouple (#3) was attached to the surface of the thermal liner closest to the radiant panel, 

and the last thermocouple (#4) was attached to the back of the thermal liner. Six “identical” 

mock-ups (labeled A – F) were used for these tests as well as the mock-up tests conducted in the 

full ensemble apparatus. 

The results for the four thermocouple locations are plotted in Figures 16 – 19. The average 

results from three replicate tests of each of the six samples (A – F) are shown in Figure 20, and 

the averages for all tests at each thermocouple location are shown in Figure 21. The temperature 

measurements on the front and back of the shell material were similar values and so for clarity 

temperature values from TC #2 were not plotted in Figure 20. Peak temperatures obtained on the 

surface of shell ranged from approximately 120 °C (250 °F) to 125 °C (260 °F). Peak 

temperatures on the front surface of the thermal liner were between 78 °C (170 °F) and 85 °C 

(185 °F) while temperatures on the back were approximately 65 °C (150 °F) to 70 °C (160 °F). 

The data appears reproducible between samples and between tests with peak temperatures 

varying approximately 5 °C or less than 10 %. These small scale experiments did not utilize any 

elevated temperature preconditioning. 

5.1.2 Full Ensemble Test Apparatus 

Seventeen tests were conducted exposing the mock-up samples to a radiative heat flux of 

2.5 kW/m2 using the full ensemble test apparatus. To allow for testing of the mock-up samples 

in the full-scale mannequin testing apparatus, the heat flux calibration cart was modified with the 

addition of two support arms (Figure 22). These arms were attached approximately 0.18 m 

(0.6 ft) above and below the normal location of the total heat flux gauge on the calibration cart. 

The exact location of these support arms is determined by placing one of the mock-up samples in 

its holder between the two support arms and adjusting them so that the exact center of the 

exposed mock-up sample corresponds with the location of the total heat flux gauge when it is 

positioned at the “center point” of the radiative flux field. This “center point” corresponds to a 

centerline position 0.91 m (3.1 ft) from the inside heater edge and 1.6 m (5.3 ft) up from the flat 

trolley guide rail. The mock-up sample is shown at the start of a test in Figure 23. 

Figure 24 presents the data from the thermocouple attached to the front of the mock-up shell 

material. Figures 25, 26, and Figure 27 show the data obtained for all 17 tests on the inside of 

the shell material, the front side of the thermal liner, and the back side of the thermal liner, 

respectively. The average temperatures obtained during the tests at the four thermocouple 

locations are shown in Figure 28. 
 - 10 - 

The data for each thermocouple location was very reproducible with the greatest variation 

occurring at the back of the sample. The mock-up shell surface thermocouple reached a peak 

value of about 132 °C (270 °F) at a 2.5 kW/m2

 exposure. The temperature profile obtained on 

the back of the shell was essentially the same as the front side. The shell material alone has a 

very small insulating capability. Peak temperatures of approximately 85 °C (185 °F) and 70 °C 

(160 °F) were obtained on the front and back surface of the thermal liner, respectively. 

Another set of experiments was conducted to examine the placement of the sample relative to the 

radiant panels. With the heat flux at the “center point” set at 2.5 kW/m2, the mock-up and holder 

were moved away from the radiant panels by 0.025 m (0.083 ft) or approximately 0.93 m 

(3.05 ft) from the radiant panels (Figure 29). These tests did result in a slightly lower peak 

temperature of approximately 130 °C (266 °F) as compared to 135 °C (275 °F) from the test with 

the mock-up 0.90 m (2.95 ft) away from the panels. 

Additional experiments were conducted in order to characterize the change in surface heating 

when the angle of the incident radiant flux is something other than perpendicular to the sample 

face. These experiments involved modifying the arms normally used to hold the mock-up 

samples in the vertical orientation. The ends of both arms were modified with a hinge system so 

the holders could accept mock-up samples at angles other than vertical. Modifying the lower 

arm by cutting it in half and adding a length of tubing between the two sections allowed the 

angle of the mock-ups to be changed. With these modifications completed, a mock-up sample 

was inserted in the arms such that the sample was at an angle of about 20 degrees off vertical. 

The upper edge of the mock-up was farthest away from the panel. Other angled tests involved 

simply moving the angled sample 0.025 m (0.083 ft) closer to the radiant panels. This position 

placed the center point of the tests sample 0.91 m (2.97 ft) away from radiant panels. 

Tests were conducted with the following configurations: vertical at 0.91 m (2.97 ft) from the 

radiant panel, vertical at 0.93 m (3.1 ft) from the radiant panel, 20 degree angle at 0.91 m 

(2.97 ft) from the radiant pane, and 20 degree angle at 0.93 m (3.1 ft) from the radiant pane. 

Each test was conducted four times to develop an average, and the results are shown in Figure 

29. It is interesting to note that peak shell temperatures obtained from the two sloped tests differ 

by only about 2 °C to 3 °C with a change in distance from the radiant panels of 0.025 m 

(0.081 ft). The peak shell temperatures in the two vertical tests differed by about 2 °C for this 

same 0.025 m (0.081 ft) change in distance from the radiant panels. Peak surface temperatures 

changed rather modestly and seem to follow the flux regression curve regardless of the 

orientation of the mock-up. 

5.2 Full-Scale Mannequin Tests

For the full scale mannequin tests, the radiative heat flux exposure was suddenly applied to the 

ensemble after first being thermally preconditioned at one of four temperatures: 27 °C (80.6 °F), 

37 °C (98.6 °F), 50 °C (122 °F) or 60 °C (140 °F). These preconditioning temperatures represent 

a warm summer evening 27 °C (80.6 °F), a hot summer day or normal body temperature 37 °C 
 - 11 - 

(98.6 °F), an extremely hot summer day in the Arizona desert or the temperature inside a closed 

automobile on a sunny day 50 °C (122 °F), and lastly some type of externally applied heat source 

60 °C (140 °F). The preconditioning temperatures were measured at five different locations on 

the protective clothing ensemble covering the full size mannequin. 

For a preconditioned temperature of 27 °C (80.6 °F), the temperature measurements at each of 

the thermocouple locations going down the spine of the turnout coat on the mannequin are 

shown in Figures 30 – 34. Each plot presents the data from five repeat tests for the four locations 

through the turnout coat (shell surface, inside of shell, body side of thermal liner, and outer 

surface of workstation shirt). These graphs provide a visual representation of the variation in the 

thermal profile through the garment and vertically along the centerline of the coat at each of the 

five thermocouple stations. 

While the external heat flux was applied, the temperature on the outside and immediately inside 

the shell is shown to increase rapidly in the first 200 s. After the first 200s, the increase becomes 

more gradual changing by approximately 20 °C over the next 400 s. Consistent with the 

insulating capabilities of the turnout coat, the temperature increases on the body side of the 

thermal liner, and the outer surface of the workstation shirt are much more gradual. For the 

thermal liner, the rate of temperature increase is approximately 0.25 °C/s during the first 400 s 

and decreases to 0.05 °C/s over the next 200 s. For the outer surface of the workstation shirt, the 

rate of temperature increase is approximately 0.125 °C/s during the first 400s and decreases to 

0.05 °C/s over the next 200 s. Once the external flux is removed, all of the temperatures begin to 

decrease rapidly. The inner and outer shell temperatures decrease more rapidly than thermal 

liner or workstation shirt temperatures. Ultimately, the shell temperatures fall below the thermal 

liner and workstation shirt temperatures. 

For each of the four preheat conditions, the average temperatures for five repeat tests measured 

at each vertical location on the turnout coat are shown in Figures 35 - 38. These graphs give a 

simple “snap shot” of the thermal wave moving through the coat portion of the fire fighter 

protective ensemble for the four preconditioning temperatures. From these graphs, the impact of 

construction and fit on the thermal wave at the respective locations along and through the turnout 

coat can be examined. 

With the exception of thermocouple #5, the fabric layers were exactly the same over the test 

area. The starting temperature and preconditioning are uniform through out the fabric layers, and 

the total radiant heat flux is uniform over the test area within 3%. A comparison of the surface 

thermocouples at the five locations demonstrates that the temperatures associated with #17, #18, 

#19, and #20 thermocouple locations were very similar. One thermocouple differs significantly 

from the other four. This particular thermocouple, #16, is as much as 21 °C cooler at the end of 

the exposure portion of the test than any of the other four surface thermocouples. This 

phenomenon was observed regardless of the level of thermal preconditioning. Thermocouples 

inside the ensemble (thermocouple #11, #6 and #1) also show this same trend of significantly 

lower temperatures when compared with corresponding thermocouples at adjacent locations. 
 - 12 - 

There could be several possible explanations for this variation. One possibility is that the flux 

field is not as uniform as the calibration testing has demonstrated. A dramatic flux discontinuity 

at this particular thermocouple location (thermocouple # 16) seems very unlikely considering the 

flux gauge mounted on the mannequin’s helmet is only 0.18 m (0.59 ft) above this thermocouple 

and is consistently reading 2.5 kW/m2 (+/- 0.1). Another possibility is that the thermocouples 

are not in the same relative plane as the other four sets of thermocouples. Using a 0.61 m (2 ft) 

level up against the thermocouples along the spine of the mannequin and a meter stick, revealed 

that four sets of thermocouples were in very close vertical alignment while the fifth set of 

thermocouples, the one in question, was 0.025 m (0.082 ft) farther away from those other four 

sets. In addition, the upper thermocouples were placed on a sloping portion of the turnout gear. 

It is possible that a plume of heated gases moving up the back of the turnout gear could be 

cooling the upper thermocouples. This would be a consistent explanation for the large 

temperature disparity between this string of thermocouples (#1, #6, #11, and #16) and adjacent 

thermocouple strings. 

6. Analysis and Discussion 

The two objectives of this work were 1) to compare results from the full ensemble test apparatus, 

the bench scale test apparatus and a protective clothing heat transfer model and 2) to monitor the 

thermal wave moving through a protective clothing ensemble when exposed to a known thermal 

radiant flux. The full ensemble and bench scale data were used to evaluate the performance of 

the heat transfer model. If the heat transfer model successfully simulates the temperatures, then 

the model can be a useful tool in examining different combinations of existing materials and help 

develop new materials/combinations. The thermal wave moving through the ensemble was 

monitored as the fire fighter protective clothing materials were exposed to a radiant heat flux of 

2.5 kW/m2

. This 2.5 kW/m2 radiant heat flux represented a low to moderate intensity exposure 

for most fire ground situations. This type of radiant exposure might be encountered some 

distance away from a fully involved large structure or when a fire fighter moves down a hallway 

toward a burning room with flames extending a short distance into that hallway. This moderate 

exposure intensity can be useful in gaining insight into thermal properties of the protective 

clothing ensemble without degrading the fabrics during repeated exposures. 

Both the experimental and calculated results were obtained for a total test time of 900 s. During 

this time, the protective clothing ensemble was exposed to a radiant heat flux for 600 s. The test 

ensemble was allowed to cool in ambient temperature air during the remaining 300 s. 

All the protective clothing assemblies were tested or modeled in a near dry condition (less than 

5 % moisture by weight). The presence of moisture can have a significant effect on the heat 

transfer through fire fighter protective clothing and its effectiveness [13]. Several studies have 

documented that moisture in the protective clothing can change its thermal performance 

properties [17, 18]. By controlling the moisture in the garment, the propagation of the thermal 

wave through the fabric layers and the impact of preheating, construction and fit on this thermal 
 - 13 - 

wave can be investigated. From this information, a realistic method for the evaluation of fullscale fire fighter protective clothing ensembles can be developed. 

6.1 Test Data Comparisons

The data obtained from the mock-up tests in both the bench scale apparatus and the full ensemble 

test show similar trends. Data obtained at the four thermocouple locations during tests in both 

the bench scale and full ensemble tests are shown in Figure 39. The general trend of the data is 

the same for both test apparatus. The peak temperatures obtained using the full ensemble 

apparatus are approximately 5 °C higher than those from the bench scale apparatus. This higher 

peak temperature is reflected in the measurements obtained throughout the turnout gear mockups. Once the exposure heat flux is stopped, the materials begin cooling at the same rate with all 

of the temperatures, mock up and full-scale apparatus, following the same curve. 

A series of tests were conducted exposing a complete fire fighting ensemble to a 2.5 kW/m2

 heat 

flux using the full ensemble test apparatus. The fire fighting ensemble was preheated to one of 

four temperatures, ambient (no preheating), 37 oC (98.6 oF), 50 C (122 oF), or 60 oC (140 oF) 

using the preconditioning chamber. The average results obtained from the tests at each 

thermocouple location are shown in Figures 35 – 38. Each graph presents the temperature 

distribution through the turnout coat at each location as a function of time. The peak 

temperatures and the rate of increase of temperature appear to be relatively insensitive to the 

initial temperature of the turnout gear resulting from the preheating. Since the peak temperatures 

are similar regardless of initial temperature, the temperature profiles through the turnout coat at 

each location are also similar. 

The heat flux profile obtained along a vertical axis at a fixed horizontal distance from the radiant 

panels is shown in Figure 40. Comparison of the thermocouple locations with the heat flux 

profile indicates that the thermocouples are all located in an area where the heat flux varies by 

less than 5%. The major variation is associated with the thermocouple #20 position. The 

thermocouple #16, #17, #18, and #19 positions fall within 0.1 m above to 0.2 m below the 

centerline. The measured heat flux is almost uniform over this area. Thermocouple #20 is 

0.278 m below the centerline in a position where the heat flux has decreased to 2.4 kW/m2

. 

The peak temperatures obtained on the surface of the turnout coat exposed to the radiant heat 

flux are very similar between the different locations with the exception of the thermocouple #16 

position. Since the heat flux in the vertical direction is relatively uniform, another possibility for 

the temperature difference between location #16 and the other thermocouple locations would be 

the horizontal distance. Since the radiant heat flux deceases with distance away from the radiant 

panels as shown in Figure 41, location #16 is exposed to less radiation. Figure 29 illustrates the 

impact of moving a turnout gear mock-up away from the radiant panels and sloping it 20°. 

These changes result in at most a 5 oC change in peak temperatures. This suggests that the 

increased distance and sloping orientation may account for some of the temperature difference at 

thermocouple location #16, but not all 20 oC observed when the turnout coat is exposed to a 

2.5 kW/m2

 heat flux using the full ensemble apparatus (Figures 35 - 38). 
 - 14 - 

The peak temperature obtained at thermocouple #16 in the full ensemble tests compares 

favorably with the data from the mock-up tests using both the full ensemble apparatus and the 

bench scale apparatus. The rate of temperature increase on the surface of the exposed shell and 

the inside of the shell also compare favorable with the mock-up tests. The rate of increase with 

the turnout gear as indicated by the thermal liner temperature measurements differ significantly 

from the mock-up tests. In addition, the cooling (time period after 600 s) within the turnout gear 

differs from that obtained using the mock-up samples. Figure 42 shows a comparison between 

temperature measurements through the turnout gear at the thermocouple #16 location and data 

obtained using mock-up samples. 

Peak temperatures obtained at the thermocouple #16 location during the full ensemble tests agree 

responsibly well with the peak temperatures obtained from the mock-up tests (Figure 42). The 

peak temperatures at thermocouple #16 are significantly below those obtained at the other 

locations of the shell surface during full ensemble testing. In addition, the temperatures on the 

unexposed side of the shell are seen to increase above the exposed surface temperatures for most 

of the thermocouple locations regardless of preheat temperature (Figures 35 -38). The lower 

peak temperatures obtained at thermocouple #16 and during the mock-up tests are probably the 

result of two phenomena. Given the location of thermocouple #16 and the small size of the 

mock-up samples, it is likely that the thermocouple bead is “viewing” less of the radiant panel 

and more of the ambient environment. This would result in the thermocouple indicating a lower 

temperature. It also appears that a convective boundary layer may be cooling the thermocouples 

along the exposed side of the turnout coat shell. This would account for the crossover of the 

inner and outer thermocouple temperatures. While these differences may limit comparison of 

data from the full ensemble and mock-up tests, it should not impact either test as a means to 

investigate heat transfer through fire fighting ensemble materials. 

6.2 Model Comparisons

For comparison purposes, a combination of materials used in a fire fighting coat were exposed to 

an external heat flux of 2.5 kW/m2

 for 600 s using the fire fighter clothing heat transfer model. 

The results are presented in Figure 43 for an air gap of 1 mm (0.04 in) between each layer. 

Figure 44 presents the results for the sample model calculations with the air gap between each 

layer reduced by half. The affects of the reduced air gaps are readily apparent in the decreased 

difference between the outside and inside temperatures of each of the three layers of material 

(shell, moisture barrier, and thermal liner). When the original air gaps are used together with an 

external heat flux of 3 kW/m2, the peak temperatures increase by approximately 15 °C (Figure 

45). Figure 46 illustrates the impact of an increased external ambient temperature. When the 

background temperature is increased from 27 °C to 75 °C, the peak temperatures increase by 

almost 25 °C. 

The model predictions for a set of turnout coat materials exposed to a 2.5 kW/m2

 external heat 

flux are compared to data obtained from the full ensemble test apparatus in Figure 47. The 

model prediction for the external part of the shell (Shell-Outside) compares favorably with the 
 - 15 - 

temperature data obtained on the exterior of the turnout coat Avg TC 16). However, the 

agreement between the prediction (Cotton_Outside) and the measured values (Avg TC 1) for the 

outer surface of the workstation shirt is not as good. The peaks are close, but the trends are very 

different. The almost linear growth of the measured data is consistently evident in the measured 

data obtained inside the fire fighting ensemble using the full ensemble test apparatus. The 

agreement between measured data (TC 1, TC 2, TC 3, and TC4) and predicted values (ShellOutside, Shell-Inside Moist_Barrier-Outside, Moist_Barrier-Inside Thermal_Liner-Outside, 

Thermal_Liner-Inside and Cotton_Outside) is much better throughout the material combination 

for a turnout gear mock-up (Figure 48). 

The comparisons of experimental data and model calculations provide some insight into some of 

the differences between measurements at various thermocouple locations. It is likely that the 

higher peak temperatures measured at thermocouple locations #17, #18, #19, #20 are the result 

of those thermocouples “viewing” more of the radiant panels. Thermocouple #16 is located 

higher on the coat and would view less of the radiant panel area. Similarly, the mock-ups both 

when exposed to the electric radiant panel and the gas fired radiant panel would see a small 

portion of the panels relative to the surrounding ambient environment. Using the model with an 

increased ambient temperature results in peak temperature prediction similar to those obtained at 

thermocouple locations #17, #18, #19, and #20. As discussed previously, thermocouple #16 may 

represent the best location for comparison with mock-up tests. Any of the thermocouple 

locations should be useful for analysis of the heat transfer through the turnout gear material. 

The almost linear temperature increase within the turnout coat during the full ensemble tests is 

more difficult to explain. Since this increase is not evident in either the mock-up tests or the 

model predictions, it is likely that the linear increase is the result of interactions within the 

turnout coat. These interactions could be difficult to address completely in any model. Non 

uniform air gaps, material contact, seams, and other issues could impact these results [13]. 

There are certain underlying assumptions that have been made for all of these mannequin tests. 

First, the fabric shell, moisture barrier, thermal liner, and workstation uniform are unique and 

separate layers, but considered to be homogeneous materials throughout each layer within the 

ensemble. The thermal wave moves through each layer from the surface of the outer shell, 

through the moisture barrier, thermal liner and to the workstation uniform. As the heat wave 

moves through the layers, the heat can move within a material layer or through one layer and into 

the next material layer. Air trapped between different layers can also slow the movement of heat 

from one layer to another layer. On the other hand, sections where stitching compresses two 

layers together may allow the heat wave to be conducted more quickly through the gear. 

The thermocouples were located such that none of them are shielded by trim or seams or exposed 

to perforations such as needle holes. Trim and seams are a normal part of all fire fighter 

protective clothing ensembles. During the installation of the thermocouples on the various layers 

of fabric, considerable effort was expended to closely align these thermocouples, but not exactly 

overlap them. This specific slight misalignment was considered necessary to minimize the 

impacts of the thermally conductive thermocouples on the movement of the heat wave. This 
 - 16 - 

staggering of the thermocouples was designed to prevent one thermocouple from “shading” an 

adjacent thermocouple or creating a line of heat sinks. 

In addition to the intentional thermocouple offsets, the final location of the thermocouples is also 

dependant on the shifting of the different layers of the fabric when the mannequin is completely 

dressed. Effort was made to insure that the thermocouples were in their desired locations when 

installation was completed. 

7. Uncertainty Analysis 

Uncertainties are grouped into two categories according to the method used to estimate them. 

Type A uncertainties are those which are evaluated by statistical methods, and Type B are those 

which are evaluated by other means [19]. Type B analysis of systematic uncertainties involves 

estimating the upper (+ a) and lower (- a) limits for the quantity in question such that the 

probability that the value would be in the interval (± a) is essentially 100%. After estimating 

uncertainties by either Type A or B analysis, the uncertainties are combined in quadrature to 

yield the combined standard uncertainty. Multiplying the combined standard uncertainty by a 

coverage factor of two results in the expanded uncertainty which corresponds to a 95 percent 

confidence interval (2 Φ). 

There are different components of uncertainty in the gas temperatures and heat flux 

measurements reported here. Components of uncertainty are summarized in Table 4. For these 

tests, the main variables that impact the uncertainty of the measurements are: 1) the gas 

temperatures, 2) the heat flux measurements and 3) the data acquisition equipment. The affect 

the thermocouples have on the precision of the test can further be broken down into three sub 

categories: a) variations in thermocouple manufacturing, b) variations in thermocouple 

attachment, and c) variations in thermocouple response time dependent largely on thermocouple 

wire and bead size. The total expanded uncertainty for an individual temperature measurement 

is estimated to be ± 18 %, and the total heat flux total expanded uncertainty is estimated to be 

± 17 %. The components of uncertainty are tabulated in Table 4. 

Imprecise and inconsistent thermocouple attachment to the various fabric layers can result in 

inaccurate measurement of temperatures on these fabric surfaces. Reference [8] specifies a 

specific protocol for the attachment of the thermocouples to the fabric layers. This protocol was 

followed rigorously when attaching all the thermocouples. The positioning of the 

thermocouples, the mannequin, and the heat flux gauge could also produce uncertainties in the 

results. The relative placement of the various instruments and test equipment is estimated to be 

within ± 5 %. 

Variations in response times of different wire size thermocouples have been documented in other 

publications [20]. By using a 0.254 mm (0.010 in) diameter wire in the thermocouples for all of 

the experiments, a compromise has been made between a very quick response time and the 

durability and workability of the wire. Temperature lag for this size thermocouple is estimated 
 - 17 - 

to be on the order of 0.25 s. With a wire size of 0.254 mm (0.010 in), the typically formed bead 

size will average about 0.635 mm (0.025 in). This translates to a thermal radiation correction of 

approximately + 2.5 °C (+5.5 °F) during the steady state part of the test. This radiation error 

represents a temperature correction of about 5 % [20]. 

Table 4. Estimated Uncertainty in Experimental Data 

Component 

Standard 

Uncertainty 

Combined 

Standard 

Uncertainty 

Total 

Expanded 

Uncertainty 

GasTemperature 

 Calibration 

 Position 

 Bead Size 

 Radiative Cooling 

 Radiative Heating 

 Repeatability1

 Random1

± 1 % 

± 5 % 

± 5 % 

- 5 % to + 0 % 

- 0 % to + 5 % 

± 5 % 

± 3 % 

± 9 % ± 18 % 

Total Heat Flux 

 Calibration 

 Zero 

 Position 

 Repeatability1

 Random1

± 3 % 

± 2 % 

± 5 % 

± 5 % 

± 3 % 

± 9 % ± 17 % 

Data Acquisition 

 Calibration 

 Resolution 

 Repeatability1

 Random1

± 5 % 

± 1 % 

± 3 % 

± 3 % 

± 5 % ± 10 % 

Note: 1. Random and repeatability evaluated as Type A, other components as Type B. 

The total heat flux was measured with a commercially manufactured, continuously reading, 

water-cooled, Schmidt/Boelter type thermopile gauge. This gauge has a maximum non-linearity 

of ± 2 %, a repeatability of ± 5 %, and an accuracy of ± 3 %. The non-linearity aspect of this 

gauge is of reduced importance when setting up and doing many repeat experiments, at the same 

radiant heat flux setting. A repeatability of ± 5% translates into about ± 0.1 kW/m2

 for the 

mannequin test apparatus. The manufacture’s statement of accuracy would reflect a 

± 0.3 kW/m2

. This much divergence from the actual flux reading would be undesirable. To 

mitigate this problem, this flux gauge was checked against a transfer standard gauge. The two 

gauges differed by slightly less than 1 % or 0.1 kW/m2

. 

The data acquisition equipment has certain limitations in its ability to accurately measure the 

temperature using a thermocouple. The greatest source of error in the thermocouple temperature 

measurements are a) the limits of error of the thermocouple wire itself, b) the reference 
 - 18 - 

temperature determined with the thermistor built into the data logger, c) the accuracy of the 

voltage measurement, and d) errors in the thermocouple and reference temperature polynomials. 

Beyond the limits of error of the thermocouple wire itself, the next largest possible source of 

temperature error is the thermistor (RTD) used to obtain the temperature of the reference 

junction. This RTD is accurate to ± 0.1 °C (1.8 °F). This RTD device can also be the source of 

other temperature measuring errors. The RTD is an integral part of the cold junction reference 

point. If the cold junction reference is not isothermal relative to the thermocouple terminal strip, 

any deviation from the RTD calculated temperature would show up as an error in the 

temperature measurement of the thermocouple. Careful placement of the data logger away from 

hot or cold drafts, and protection from uneven radiative heating will help to minimize this type of 

error. The environmentally conditioned laboratory space, used to conduct these experiments, 

should also substantially mitigate this source of temperature error. 

The accuracy of the thermocouple voltage measurements in the data loggers used in these 

experiments is between 0.07 % to 0.10 %. For the relatively small (< 160 °C) temperature 

changes developed in these tests, the temperature error due to the voltage measurement error on 

the order of a 0.02 °C. Another potential source of thermocouple temperature error is in the 

polynomials used to convert the RTD output and the thermocouple voltage to a temperature. 

This error is ± 0.01 °C between –50 °C and 950 °C. Other potential sources of error in the 

thermocouple temperature measurement are the rate at which the thermocouples are scanned. 

Very high data logger scan rates of a very large number of thermocouples as well as switching 

ranges can result in insufficient settling times between each reading. This phenomenon can 

cause some degradation of the precise voltage measurement with a corresponding loss of 

temperature measurement precision. The data loggers used in these experiments were operated 

at a slow enough speed that this type of error could be assumed to be negligible. 

The data logger has some inaccuracy associated with its internal clock. This clock error is about 

one minute per month. This represents a shift of approximately ± 0.3 s over the 900 s test 

interval. With a scan interval of 2 s, this clock error would be insignificant. There are other 

possible sources of temperature measurement error not directly related to or attributable to the 

data logger equipment. Such things as extraneous electro magnetic radiation inducing stray 

voltages on to the thermocouple circuits are an example of this type of nonspecifically induced 

temperature measurement errors. The data logger does have a mechanism to cope with the most 

common type of electro magnetic interference, that being the typical 60-hertz found on the AC 

power lines. Other nonspecific electro magnetic interference inducing errors are difficult to 

quantify. Prevention and suppression of these interference sources is by far the best method of 

dealing with them. 
 - 19 - 

8. Conclusions 

The full ensemble test apparatus provides a means for examining the thermal performance of fire 

fighter protection clothing. The apparatus can be used to measure the heat transfer through a 

complete fire fighting ensemble when exposed to a wide range of external heat flux values. The 

apparatus can be operated for extended periods of time simulating exposure times that could 

occur during fire fighting operations. Testing of complete ensembles is a vital supplement to the 

bench scale testing of mock-up samples. As additional work is undertaken to incorporate a fire 

fighter submodel into various computer-based fire models such as the Fire Dynamics Simulator 

[21], results from this full ensemble test apparatus will be critical for development and 

verification. 

Test results are reasonably reproducible for a given test scenario (apparatus type, turn out gear 

materials, and mock-up or full ensemble arrangement). Data from fire fighter turnout gear 

mock-up tests using the full ensemble apparatus compare favorably with similar materials tested 

in the bench scale apparatus. Peak temperatures obtained when the materials are exposed to a 

2.5 kW/m2

 heat flux are similar for mock-up samples tested in both the bench scale apparatus 

and the full ensemble test apparatus. Peak temperatures obtained using a complete ensemble 

differ from both the mock-up sample tests and at different locations on the ensemble when 

exposed to the same heat flux. These differences indicate the importance of clothing lay and air 

gaps in determining the transmission of heat through the turn out gear ensemble. In addition, the 

testing of mock-up samples with an open back sample holder appears to impact the heat transfer 

within the samples. 

Given the location of the higher thermocouple and the small size of the mock-up samples, it is 

likely that the thermocouple bead would be “viewing” less of the radiant panel and more of the 

ambient environment. This would result in the thermocouple indicating a lower temperature. It 

also appears that a convective boundary layer may be cooling the thermocouples along the 

exposed side of the turnout coat shell. This would account for the crossover of the inner and 

outer thermocouple temperatures. While these differences may limit comparison of data from 

the full ensemble and mock-up tests, it should not impact either test as a means to investigate 

heat transfer through fire fighting ensemble materials. 

Data from mock-up sample tests and full ensemble tests have been compared to results obtained 

from a computer-based mathematical model of heat transfer through fire fighter protective 

clothing [12]. Measured and calculated temperatures at the shell outer and inner surface agree 

quite well for the mock-up sample tests. The calculated rate of temperature increase at all of the 

measurement points is similar to the data obtained from the mock-up tests. However, the 

measured and predicted temperatures within the material layers are different. The computer 

model over predicts the temperatures at the various measurement locations when compared to 

data from the full ensemble tests. 
 - 20 - 

9. Acknowledgments 

The authors would like to thank the United States Fire Administration, especially Mr. William 

Troup and Mr. Robert T. McCarthy, for their sponsorship and support of this important research 

10. References 

[1] Beyler, C.L., “Fire Safety Challenges in the 21st Century,” Journal of Fire Protection 

Engineering, Vol. 11, No.1, pp. 4-15, 2001. 

[2] Fire Fighter Fatalities in the United States in 1999, United States Fire Administration, 

Emmitsburg, MD, July 2000. 

[3] LeBlanc, P.R. and Fahy, R.F., “Firefighter Fatalities in the United States - 2003,” 

National Fire Protection Association, Quincy, MA, June 2004. 

[4] Karter, M.J. and Molis, J.L., “U.S. Fire Fighter Injuries - 2002,” National Fire Protection 

Association, Quincy, MA, November 2003. 

[5] Lawson, J.R., “Fire Fighter’s Protective Clothing and Thermal Environments of 

Structural Fire Fighting,” NISTIR 5804, National Institute of Standards and Technology, 

Gaithersburg, MD, August 1996. 

[6] National Fire Protection Association, Standard on Protective Ensembles for Structural 

Fire Fighting and Proximity Fire Fighting, NFPA Standard 1971-2000, National Fire 

Protection Association, Quincy, MA, 2000. 

[7] Krasney, J.F., Rockett, J.A., and Huang, D., “Protecting Fire Fighters Exposed in Room 

Fires: Comparison of Results of Bench Scale Test for Thermal Protection and Conditions 

During Room Flashover,” Fire Technology, 24 No. 1, pp. 5-19, 1988. 

[8] Lawson, J.R. and Twilley, W.H., “Development of an Apparatus for Measuring the 

Thermal Performance of Fire Fighters’ Protective Clothing,” NISTIR 6400, National 

Institute of Standards and Technology, Gaithersburg, MD, October 1999. 

[9] Lawson, J.R., Walton, W.D., Bryner, N.P., and Amon, F.K., “Estimates of Thermal 

Properties for Fire Fighters’ Protective Clothing Materials,” NISTIR 7282, National 

Institute of Standards and Technology, Gaithersburg, MD, June 2005. 

[10] National Fire Protection Association, Station/Work Uniforms for Fire and Emergency 

Services, NFPA Standard 1975-2004, National Fire Protection Association, Quincy, MA, 

2004. 

[11] Prasad, K., Ho Dac, H.M., and Kukuck, S., “Thermal Performance of Fire Fighters’ 

Protective Clothing. 2. Protective Clothing Performance Simulator – User’s Manual,” 

NISTIR 6901, National Institute of Standards and Technology, Gaithersburg, MD, 

January 2003. 

[12] Mell, W.E., and Lawson, J.R., “Heat Transfer Model for Fire Fighters’ Protective 

Clothing,” Fire Technology, Vol. 36, No. 1, pp. 39-68, February 2000. 

[13] Prasad, K., Twilley, W.H., and Lawson, J.R., “Thermal Performance of Fire Fighters’ 

Protective Clothing. 1. Numerical Study of Transient Heat and Water Vapor Transfer,” 

NISTIR 6881, National Institute of Standards and Technology, Gaithersburg, MD, 

August 2002. 
 - 21 - 

[14] International Organization for Standardization, Clothing for protection against heat and 

flame – Determination of heat transmission on exposure to both flame and radiant heat, 

ISO Standard 17492, Geneva, Switzerland, 2003. 

[15] Kukuck, S., and Prasad, K., “Thermal Performance of Fire Fighters’ Protective Clothing. 

3. Simulating a TPP Test for Single-Layered Fabrics,” NISTIR 6993, National Institute 

of Standards and Technology, Gaithersburg, MD, January 2003. 

[16] DiNenno, P.J.,” Appendix B – Property Data,” The SFPE Handbook of Fire Protection 

Engineering, 3rd Edition, Society of Fire Protection Engineers, Bethesda, MD, pp. A-23 

to A33, 2002. 

[17] Lawson, J.R., “Thermal Performance and Limitations of Bunker Gear,” Fire Engineering, 

Vol. 151, No. 8, pp. 37, 40, 42, 44, 46, 50 – 52, 55 - 56, August 1998. 

[18] North Carolina State University, “Evaluating the Effects of Moisture on the Thermal 

Protective Performance of Firefighter Protective Clothing in Low Level Heat Exposures,” 

Annual Report, National Institute of Standards and Technology, Gaithersburg, MD, 

December 2001. 

[19] Taylor, B.N., and Kuyatt, C.E., “Guidelines for Evaluating and Expressing the 

Uncertainty of NIST Measurements Results,” NIST Technical Note 1297, National 

Institute of Standards and Technology, Gaithersburg, MD, September 1994. 

[20] Blevins, L.G., and Pitts, W.M., “Modeling of Bare and Aspirated Thermocouples in 

Compartment Fires,” Fire Safety Journal, Vol. 33, pp. 239-259, 1999. 

[21] McGrattan, K.B., “Fire Dynamics Simulator (Version 4) Technical Reference Guide,” 

NIST SP 1018, NIST Special Publication 1018, National Institute of Standards and 

Technology, Gaithersburg, MD, July 2004. 
 - 22 - 

Figure 1. Photograph of bench scale test apparatus with gas fired radiant panel operating 

and turn out gear mock-up sample in place. 
 - 23 - 

Figure 2. Sketch showing the bench scale test apparatus. 
 - 24 - 

Figure 3. Plan view of test apparatus including radiant panels and trolley assembly. 

3.62 m 

(142.5”) 

2.48 m 

 (97.5”) 

2.16 m. 

(85”) 

Conditioning 

Chamber 

Mannequin 

Trolley 

And Stand 

Chain/ Cable 

Drive 

Guide 

Tube 

Electric 

Radiant Panels 

Trolley 

Guide Rails 

Radiation Shield 

0.68m 

(26.5”) 

1.73 m 

(68”) 

Motor Driver For 

Mannequin Trolley 

Not To Scale 
 - 25 - 

Figure 4. Elevation view of test apparatus including radiant panels and trolley 

assembly. 

Radiant Electric Panels 

Total Heat 

Flux Gauge 

Floor 

1.98 m 

(78”) 1.89 m 

(74.5”) 

1.83 m 

(72”) 

368 mm 

(14.5”) 305 mm 

(12”) 

Chain Drive 

Cart Link 

To Chain 

Drive 
 - 26 - 

Figure 5. Photograph of radiant panels and radiation shield with trolley mounted 

heat flux gauge. 
 - 27 - 

Figure 6. Photograph of the preconditioning chamber. 
 - 28 - 

Figure 7. Photograph of mannequin positioned in front of the radiant panels. 
 - 29 - 

Figure 8. Photograph of turnout gear mock-up. 
 - 30 - 

Figure 9. Drawing of the turnout gear mock-up sample holder. 

356 mm 

(14”)

356 mm 

(14”)

6.35mm 

(0.25”)

19 mm 

(0.75”)

12.7mm 

(0.5”)

Drill 4.5 mm (.177’) 

Dia. Hole. 4 Places. 

50.8mm (2”) From Edge 

Mill Slot 6.35 mm (0.25”) Wide 

1.5 mm (0.60’) Deep,6.35 mm 

(0.25’) From Inside Edge

254 mm 

(10”)

254 mm 

(10”)

241 mm 

(9.5”)

25.4 mm 

(1”)

6.35 mm 

(0.5”)

19 mm 

(0.75”)

3 mm 

Drill And Tap 8-32, 2 Places. Locate Holes To Align (.118”)

With Holes In Frame When Prismatic Is Resting In 

Milled Slot NOT TO SCALE 
 - 31 - 

Figure 10. Photograph of the turnout gear mock-up sample holder with test sample. 
 - 32 - 

Figure 11. Photograph showing mannequin without coat and instrumentation (heat 

flux gauge and thermocouples). 
 - 33 - 

Figure 12. Drawing showing thermocouple locations on the outside of the back of the 

turnout gear shell (Front Surface). 

CL 

5mm. Offset 

(0.2”) 

Total Heat Flux Gauge 

Attached To Back Of Helmet 

Collar 

Thermocouple #16 

Thermocouple #17 

Thermocouple #18 

Thermocouple #19 

Thermocouple #20 

Yellow Reflective Trim 

Yellow Reflective Trim

95 mm 

(3.74”) 

80 mm 

(3.15”)

100 mm 

(3.94”) 

Seam 

Seam 

101mm 

(3.98”) 

85 mm 

(3.35”) 

92 mm 

(3.62”) 

385 mm 

(15.16”) 

Left 

Sleeve 

Right 

Sleeve 

Collar Seam 

Center Of Radiative 

Flux Field, Position 

D1 
 - 34 - 

Figure 13. Drawing showing thermocouple locations on the inside of the turnout coat 

shell (Mid-Point). 

CL 

5 mm. Offset 

(0.2”)

Back Side Of Trim 

Back Side Of Trim 

Thermocouple #11 

Thermocouple #12 

Thermocouple #13 

Thermocouple #15 

Left 

Sleeve

Right 

Sleeve 

80 mm 

(3.15”)

95 mm 

(3.74”)

101 mm 

(3.98”)

85 mm 

(3.35”)

92 mm 

(3.62”)

Seam 

Seam 

Collar Seam 

Thermocouple #14 
 - 35 - 

Figure 14. Drawing showing the thermocouple locations on the inside of the thermal 

liner adjacent to the moisture barrier (Back Surface). 

CL 

Left 

Sleeve

Right 

Sleeve 

88 mm 

(3.46”)

92 mm 

(3.62”)

105 mm 

(4.13”)

90 mm 

(3.54”)

115 mm 

(4.53”)

Thermocouple #6 

Thermocouple #7 

Thermocouple #8 

Thermocouple #9 

Thermocouple #10 
 - 36 - 

Figure 15. Drawing showing thermocouple locations on the outside of the 

workstation shirt (Shirt). 

CL 

80 mm 

(3.15”) 

90 mm 

(3.54”) 

100 mm 

(3.94”) 

80 mm 

(3.15”) 

Thermocouple #1 

Thermocouple #4 

Thermocouple #5 

Right 

Sleeve 

Thermocouple #2 

Left 

Sleeve 

55 mm 

(2.17”) 

Seam 

Collar 

Thermocouple #3 

Top Belt Line of Bunker Pants 
 - 37 - 

Figure 16. Graph showing temperatures measured on the front of the mock-up shell 

material for each test conducted using the bench scale test apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

A TC 1

A TC 1

A TC 1

B TC 1

B TC 1

B TC 1

C TC 1

C TC 1

C TC 1

D TC 1

D TC 1

D TC 1

E TC 1

E TC 1

E TC 1

F TC 1

F TC 1

F TC 1

Temperature (

oC)

Time (s)
 - 38 - 

Figure 17. Graph showing temperatures measured on the back of the mock-up shell 

material for each test conducted using the bench scale test apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

A TC 2

A TC 2

A TC 2

B TC 2

B TC 2

B TC 2

C TC 2

C TC 2

C TC 2

D TC 2

D TC 2

D TC 2

E TC 2

E TC 2

E TC 2

F TC 2

F TC 2

F TC 2

Temperature (

oC)

Time (s)
 - 39 - 

Figure 18. Graph showing temperatures measured on the front of the mock-up 

thermal liner material for each test conducted using the bench scale test 

apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

A TC 3

A TC 3

A TC 3

B TC 3

B TC 3

B TC 3

C TC 3

C TC 3

C TC 3

D TC 3

D TC 3

D TC 3

E TC 3

E TC 3

E TC 3

F TC 3

F TC 3

F TC 3

Temperature (

oC)

Time (s)
 - 40 - 

Figure 19. Graph showing temperatures measured on the back of the mock-up 

thermal liner material for each test conducted using the bench scale test 

apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

A TC 4

A TC 4

A TC 4

B TC 4

B TC 4

B TC 4

C TC 4

C TC 4

C TC 4

D TC 4

D TC 4

D TC 4

E TC 4

E TC 4

E TC 4

F TC 4

F TC 4

F TC 4

Temperature (

oC)

Time (s)
 - 41 - 

Figure 20. Graph showing average temperatures measured for each of the six mockup samples using a bench scale test apparatus (TC2 eliminated for clarity). 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

A TC 1

A TC 3

A TC 4

B TC 1

B TC 3

B TC 4

C TC 1

C TC 3

C TC 4

D TC 1

D TC 3

D TC 4

E TC 1

E TC 3

E TC 4

F TC 1

F TC 3

F TC 4

Temperature (

oC)

Time (s)
 - 42 - 

Figure 21. Graph showing average temperatures measured through mock-up samples 

using a bench scale test apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg-TC1

Avg-TC2

Avg-TC3

Avg-TC4

Temperature (

oC)

Time (s)
 - 43 - 

Figure 22. Drawings of heat flux gauge and mock-up trolley showing the mock in 

position and the dimensions. 

EMT Tubing 

19 mm Non. 

(.75” Nom.) 

1.92 m 

(75.5”)

 70 mm. 

 (2.75”) 

Floor 

305 

mm

381 

mm

Mock-up 

Sample 

Total Heat 

Flux Gauge; 

180 Deg. Out 

Of Position 

Mock-up 

Frame Support 

Mock-up 

Sample In 

Sample Holder 

Exposed Area 

254 x 254 mm 

(10 X 10”) 

1.18 m. 

( 46.3”)

584 mm 

(23”)

Center Of Radiative Flux 

Field, Position D-1 
 - 44 - 

Figure 23. Photograph of the radiation shield in place in front of the radiant panels. 
 - 45 - 

Figure 24. Graph showing the data from the thermocouple attached to the front of the 

mock-up shell material for all tests using the full ensemble test apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

A-TC 1

A-TC 1

B-TC 1

B-TC 1

B-TC 1

C-TC 1

C-TC 1

C-TC 1

D-TC 1

D-TC 1

D-TC 1

E-TC 1

E-TC 1

E-TC 1

F-TC 1

F-TC 1

F-TC 1

Temperature (

oC)

Time (s)
 - 46 - 

Figure 25. Graph showing the data from the thermocouple attached to the back of the 

mock-up shell material for all tests using the full ensemble test apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

A-TC 2

A-TC 2

B-TC 2

B-TC 2

B-TC 2

C-TC 2

C-TC 2

C-TC 2

D-TC 2

D-TC 2

D-TC 2

E-TC 2

E-TC 2

E-TC 2

F-TC 2

F-TC 2

F-TC 2

Temperature (

oC)

Time (s)
 - 47 - 

Figure 26 Graph showing the data from the thermocouple attached to the front of the 

mock-up thermal liner material for all tests using the full ensemble test 

apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

A-TC 3

A-TC 3

B-TC 3

B-TC 3

B-TC 3

C-TC 3

C-TC 3

C-TC 3

D-TC 3

D-TC 3

D-TC 3

E-TC 3

E-TC 3

E-TC 3

F-TC 3

F-TC 3

F-TC 3

Temperature (

oC)

Time (s)
 - 48 - 

Figure 27. Graph showing the data from the thermocouple attached to the back of the 

mock-up thermal liner material for all tests using the full ensemble test 

apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

A-TC4

A-TC 4

B-TC 4

B-TC 4

B-TC 4

C-TC 4

C-TC 4

C-TC 4

D-TC 4

D-TC 4

E-TC 4

E-TC 4

E-TC 4

F-TC 4

F-TC 4

D-TC 4

F-TC 4

Temperature (

oC)

Time (s)
 - 49 - 

Figure 28. Graph showing the average temperatures obtained at the four 

thermocouple locations during the mock-up tests using the full ensemble 

test apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

G Avg of All TC 1 Tests A-F,205

G Avg of All TC 2 Tests A-F,205

G Avg of All TC 3 Tests A-F,205

G Avg of All TC 4 Tests A-F,205

Temperature (

oC)

Time (s)
 - 50 - 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC # 1, 90.5 cm, Vert.

Avg TC # 2, 90.5 cm, Vert.

Avg TC # 3, 90.5 cm, Vert.

Avg TC # 4, 90.5 cm, Vert.

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC # 1, 93.0 cm, Vert.

Avg TC # 2, 93.0 cm, Vert.

Avg TC # 3, 93.0 cm, Vert.

Avg TC # 4, 93.0 cm, Vert.

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC # 1, 90.5 cm, 20 Deg Angle

Avg TC # 2, 90.5 cm, 20 Deg Angle

Avg TC # 3, 90.5 cm, 20 Deg Angle

Avg TC # 4, 90.5 cm, 20 Deg Angle

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC # 1, 93.0 cm, 20 Deg Angle

Avg TC # 2, 93.0 cm, 20 Deg Angle

Avg TC # 3, 93.0 cm, 20 Deg Angle

Avg TC # 4, 93.0 cm, 20 Deg Angle

Temperature (oC)

Time (s)

Figure 29. Graphs showing temperatures measured through mock-up samples for the 

following orientations: vertical at 0.91 m (2.97 ft), vertical at 0.93 m (3.1 

ft), 20 deg. angle at 0.91 m (2.97 ft), and 20 deg. angle at 0.93 m (3.1 ft). 
 - 51 - 

Figure 30. Graph of temperatures through turnout coat and work station shirt for 

thermocouples associated with external thermocouple #16 when exposed 

to an external radiant flux of 2.5 kW/m2

 and no elevated temperature 

preconditioning. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

TC 1

TC 6

TC 11

TC 16

TC 1

TC 6

TC 11

TC 16

TC 1

TC 6

TC 11

TC 16

TC 1

TC 6

TC 11

TC 16

TC 1

TC 6

TC 11

TC 16

Temperature (

oC)

Time (s)
 - 52 - 

Figure 31. Graph of temperatures through turnout coat and work station shirt for 

thermocouples associated with external thermocouple #17 when exposed 

to an external radiant flux of 2.5 kW/m2

 and no elevated temperature 

preconditioning. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

TC 2

TC 7

TC 12

TC 17

TC 2

TC 7

TC 12

TC 17

TC 2

TC 7

TC 12

TC 17

TC 2

TC 7

TC 12

TC 17

TC 2

TC 7

TC 12

TC 17

Temperature (

oC)

Time (s)
 - 53 - 

Figure 32. Graph of temperatures through turnout coat and work station shirt for 

thermocouples associated with external thermocouple #18 when exposed 

to an external radiant flux of 2.5 kW/m2

 and no elevated temperature 

preconditioning. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

TC 3

TC 8

TC 13

TC 18

TC 3

TC 8

TC 13

TC 18

TC 3

TC 8

TC 13

TC 18

TC 3

TC 8

TC 13

TC 18

TC 3

TC 8

TC 13

TC 18

Temperature (

oC)

Time (s)
 - 54 - 

Figure 33. Graph of temperatures through turnout coat and work station shirt for 

thermocouples associated with external thermocouple #19 when exposed 

to an external radiant flux of 2.5 kW/m2

 and no elevated temperature 

preconditioning. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

TC 4

TC 9

TC 14

TC 19

TC 4

TC 9

TC 14

TC 19

TC 4

TC 9

TC 14

TC 19

TC 4

TC 9

TC 14

TC 19

TC 4

TC 9

TC 14

TC 19

Temperature (

oC)

Time (s)
 - 55 - 

Figure 34. Graph of temperatures through turnout coat and work station shirt for 

thermocouples associated with external thermocouple #20 when exposed 

to an external radiant flux of 2.5 kW/m2

 and no elevated temperature 

preconditioning. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

TC 5

TC 10

TC 15

TC 20

TC 5

TC 10

TC 15

TC 20

TC 5

TC 10

TC 15

TC 20

TC 5

TC 10

TC 15

TC 20

TC 5

TC 10

TC 15

TC 20

Temperature (

oC)

Time (s)
 - 56 - 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 1

Avg TC 6

Avg TC 11

Avg TC 16

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 2

Avg TC 7

Avg TC 12

Avg TC 17

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 3

Avg TC 8

Avg TC 13

Avg TC 18

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 5

Avg TC 10

Avg TC 15

Avg TC 20

Temperature (oC)

Time (s)

Figure 35. Graphs of average temperatures through turnout coat and work station 

shirt for thermocouples associated with the five external thermocouple 

locations when exposed to an external radiant heat flux of 2.5 kW/m2

 and 

no elevated temperature preconditioning. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 4

Avg TC 9

Avg TC 14

Avg TC 19

Temperature (oC)

Time(s)
 - 57 - 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 1

Avg TC 6

Avg TC 11

Avg TC 16

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 2

Avg TC 7

Avg TC 12

Avg TC 17

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 3

Avg TC 8

Avg TC 13

Avg TC 18

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 4

Avg TC 9

Avg TC 14

Avg TC 19

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 5

Avg TC 10

Avg TC 15

Avg TC 20

Temperature (oC)

Time (s)

Figure 36. Graphs of average temperatures through turnout coat and work station 

shirt for thermocouples associated with the five external thermocouple 

locations when exposed to an external radiant heat flux of 2.5 kW/m2

 and 

preconditioned at 37 oC. 
 - 58 - 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 1

Avg TC 6

Avg TC 11

Avg TC 16

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 2

Avg TC 7

Avg TC 12

Avg TC 17

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 3

Avg TC 8

Avg TC 13

Avg TC 18

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 4

Avg TC 9

Avg TC 14

Avg TC 19

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 5

Avg TC 10

Avg TC 15

Avg TC 20

Temperature (oC)

Time (s)

Figure 37. Graphs of average temperatures through turnout coat and work station 

shirt for thermocouples associated with the five external thermocouple 

locations when exposed to an external radiant heat flux of 2.5 kW/m2 and 

preconditioned at 50 oC. 
 - 59 - 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 1

Avg TC 6

Avg TC 11

Avg TC 16

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 2

Avg TC 7

Avg TC 12

Avg TC 17

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 3

Avg TC 8

Avg TC 13

Avg TC 18

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 4

Avg TC 9

Avg TC 14

Avg TC 19

Temperature (oC)

Time (s)

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 5

Avg TC 10

Avg TC 15

Avg TC 20

Temperature (oC)

Time (s)

Figure 38. Graphs of average temperatures through turnout coat and work station 

shirt for thermocouples associated with the five external thermocouple 

locations when exposed to an external radiant heat flux of 2.5 kW/m2

 and 

preconditioned at 60 oC. 
 - 60 - 

Figure 39. Graph showing average temperatures obtained at the four thermocouple 

locations for the mock-up tests using the bench scale apparatus (labeled 

224) and the full ensemble test apparatus (labeled 205). 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC1 - 224

Avg TC1 - 205

Avg TC2 - 224

Avg TC2 - 205

Avg TC3 - 224

Avg TC3 - 205

Avg TC4 - 224

Avg TC4 - 205

Temperature (

oC)

Time (s)
 - 61 - 

-0.6

-0.4

-0.2

0

0.2

0.4

0.6

0 0.5 1 1.5 2 2.5

Vertical Distance From Centerline (m)

Heat Flux (kW/m2)

Figure 40. Graph showing the decay of the flux field with movement in the vertical 

direction (heat flux source on right side of graph). 
 - 62 - 

1.2

1.4

1.6

1.8

2

2.2

2.4

2.6

0.6 0.5 0.4 0.3 0.2 0.1 0

Heat Flux (kW/m

2

)

Distance Away from Radiant Panels (m)

Figure 41. Graph showing the decay of the flux field with movement away from the 

radiant panels (heat flux source is 0.91 m away from the panel on right 

side of graph). 
 - 63 - 

Figure 42. Graph showing comparison between temperatures measured through 

turnout gear at thermocouple #16 location and data from mock-up samples 

in both the full ensemble test apparatus (labeled 205) and the bench scale 

apparatus (labeled 224). 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg1-27

Avg6-27

Av11-27

Av16-27

Avg TC1 - 224

Avg TC1 - 205

Avg TC2 - 224

Avg TC2 - 205

Avg TC3 - 224

Avg TC3 - 205

Avg TC4 - 224

Avg TC4 - 205

Temperature (

oC)

Time(s)
 - 64 - 

Figure 43. Graph showing calculated temperatures for a mock-up exposed to a 2.5 

kW/m2

 heat flux using the default parameters in the heat transfer model 

[12]. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Shell-Outside

Shell-Inside

Moist_Barrier-Outside

Moist_Barrier-Inside

Thermal_Liner-Outside

Thermal_Liner-Inside

Cotton_Outside

Temperature (

oC)

Time (s)
 - 65 - 

Figure 44. Graph showing calculated temperatures for a mock-up exposed to a 2.5 

kW/m2

 heat flux using the default parameters in the heat transfer model 

[12] except the air gaps are half the size. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Shell-Outside

Shell-Inside

Moist_Barrier-Outside

Moist_Barrier-Inside

Thermal_Liner-Outside

Thermal_Liner-Inside

Cotton_Outside

Temperature (

oC)

Time (s)
 - 66 - 

Figure 45. Graph showing calculated temperatures for a mock-up exposed to a 3 

kW/m2

 heat flux using the default parameters in the heat transfer model 

[12]. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Shell-Outside

Shell-Inside

Moist_Barrier-Outside

Moist_Barrier-Inside

Thermal_Liner-Outside

Thermal_Liner-Inside

Cotton_Outside

Temperature (

oC)

Time (s)
 - 67 - 

Figure 46. Graph showing calculated temperatures for a mock-up exposed to a 2.5 

kW/m2

 heat flux using the default parameters in the heat transfer model 

[12] except with a 75 oC ambient background temperature. 

40

60

80

100

120

140

160

0 200 400 600 800 1000

Shell-Outside

Shell-Inside

Moist_Barrier-Outside

Moist_Barrier-Inside

Thermal_Liner-Outside

Thermal_Liner-Inside

Cotton-Outside

Temperature (

oC)

Time (s)
 - 68 - 

Figure 47. Graph comparing measured (Avg TC 16, Avg TC 1) and calculated 

temperature distributions through a turnout coat when exposed to a 2.5 

kW/m2

 heat flux using the full ensemble test apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

Avg TC 16

Shell-Outside

Avg TC 1

Cotton_Outside

Temperature (

oC)

Time (s)
 - 69 - 

Figure 48. Graph comparing measured (TC 1, TC 2, TC 3, TC 4) and calculated 

temperature distributions through a mock-up assembly when exposed to a 

2.5 kW/m2

 heat flux using the full ensemble test apparatus. 

0

20

40

60

80

100

120

140

160

0 200 400 600 800 1000

TC 1

TC 2

TC 3

TC 4

Shell-Outside

Shell-Inside

Moist_Barrier-Outside

Moist_Barrier-Inside

Thermal_Liner-Outside

Thermal_Liner-Inside

Cotton_Outside

Temperature (

oC)

Time (s)