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Thermowells are tubular fittings used to protect temperature sensors installed in industrial processes. A thermowell consists of a tube closed at one end and mounted in the process stream. A temperature sensor such as a thermometer, thermocouple or resistance temperature detector is inserted in the open end of the tube, which is usually in the open air outside the process piping or vessel and any thermal insulation. Thermodynamically, the process fluid transfers heat to the thermowell wall, which in turn transfers heat to the sensor. Since more mass is present with a sensor-well assembly than with a probe directly immersed into the process, the sensor's response to process temperature changes is slowed by the addition of the well. If the sensor fails, it can be easily replaced without draining the vessel or piping. Since the mass of the thermowell must be heated to the process temperature, and since the walls of the thermowell conduct heat out of the process, sensor accuracy and responsiveness is negatively impacted by the addition of a thermowell.[1]

Traditionally the thermowell length has been based in the degree of insertion relative to pipe wall diameter. This tradition is misplaced as it can expose the thermowell to the risk of flow-induced vibration and fatigue failure. When measurement error calculations are carried out for the installation, for insulated piping or near ambient fluid temperatures, excluding thermal radiation effects, conduction error is less than one percent as long as the tip is exposed to flow, even in flanged mounted installations.

The response time of the installed sensor largely governed by the fluid velocity and considerably greater than the response time of the sensor itself. This is the result of the thermal mass of the thermowell tip, and the heat transfer coefficient between the thermowell and the fluid.

Arguments, for longer designs are based on traditional notions but rarely justified. Long thermowells may be used in low velocitiy services or in cases where historical experience justified their use. In modern high strength piping and elevated fluid velocities, each installation must be carefully examined especially in cases where acoustic resonances in the process are involved.

A representative thermowell is machined from drilled bar stock to ensure a proper sensor fit (ex: a .260-inch bore matching a .250-inch sensor). A thermowell is typically mounted into the process stream by way of a threaded, welded, sanitary cap or flanged process connection. The temperature sensor such as a thermometer, thermocouple or resistance temperature detector is inserted in the open end of the thermowell and typically spring-loaded to ensure that the outside tip of the temperature sensor is in metal to metal contact with the inside tip of the thermowell. The use of welded sections for long designs is discouraged due to corrosion and fatigue risks.

Materials and construction[edit]

The thermowell protects the instrument from the pressure, flow-induced forces, and chemical effects of the process fluid. Typically a thermowell is made from metal bar stock. The end of the thermowell may be of reduced diameter (as is the case with a tapered or stepped shank thermowell) to improve the speed of response.

For low pressures and temperatures, Teflon may be used to make a thermowell; various types of stainless steel are typical, with other metals used for highly corrosive process fluids.

Where temperatures are high and the pressure differential is small, a protection tube may be used with a bare thermocouple element. These are often made of alumina or other ceramic material to prevent chemical attack of the platinum or other thermocouple elements. The ceramic protection tube may be inserted into a heavy outer protection tube manufactured from silicon carbide or other material where increased protection is required.

Flow forces[edit]

Thermowells are typically installed in piping systems and subject to both hydrostatic and aerodynamic forces. Vortex shedding is the dominant concern for thermowells in cross-flow applications and is capable of forcing the thermowell into resonance with the possibility of fatigue failure not only of the thermowell but also of the temperature sensor. The conditions for flow-induced resonance generally govern the design of the thermowell apart from its pressure rating and materials of construction. Flow-induced motion of the thermowell occurs both in-line with and transverse to the direction of flow with the fluid forces acting to bend the thermowell. In many applications the transverse component of the fluid forces resulting from vortex shedding tends to govern the onset of flow-induced resonance, with a forcing frequency equal to the vortex shedding rate. In liquids and in high-pressure compressible fluids, a smaller but nonetheless significant component of motion in the flow-direction is also present and occurs at nearly twice the vortex shedding rate. The in-line resonance condition may govern thermowell design at high fluid velocities although its amplitude is a function of the mass-damping parameter or Scruton number describing the thermowell-fluid interaction.

The aerodynamic force coefficients and the dependence of the shedding rate are dependent on the so-called tip Reynolds number. for Reynolds numbers less than 100000 (the Critical Reynolds Number), the shedding forces are well behaved and lead to periodic forcing. For Reynolds Numbers asccosiated with the Drag Crisis (first reported by Gustav Eiffel) 100,000<Rd<1,000,000-3,000,000, the shedding forces are randomized with a corresponding reduction in magnitude. The random fluctuations are characterized by their Fourier Spectra characterized by its Strouhal Bandwidth and the root mean square magnitudes of the aerodynamic force coefficients in the lift and drag directions.

For drilled bar-stock thermowells, the most common form of failure is bending fatigue at its base where the bending stresses are greatest. In extreme flow conditions (high-velocity liquids or high-velocity, high-pressure gases and vapors) catastrophic failure may occur with bending stresses exceeding the ultimate strength of the material. For extremely long thermowells, the static component of the bending stresses may govern design. In less demanding services, fatigue failure is more gradual and often preceded by a series sensor failures. The latter are due to the acceleration of the thermowell tip as it vibrates, this motion causes the element to lift off the bottom of the thermowell and batter itself to pieces. In cases where the acceleration stresses have been measured, sensor accelerations at resonant conditions often exceed 250 Gs and have destroyed the accelerometer.

The natural frequencies of thermowell bending modes are dependent upon the dimensions of the thermowell, the compliance (or flexibility) of its support, and to a lesser extent dependent upon the mass of the sensor and the added mass of the fluid surrounding the thermowell.

The ASME Performance Test Code PTC 19.3TW-2016 ("19.3TW") defines criteria for the design and application of thermowells. However, these thermowells must be manufactured from bar stock or forged material where certain dimensional requirements and manufacturing tolerances are met. Coatings, sleeves, velocity collars, special machined surfaces such as spirals or fins are expressly outside the scope of the 19.3TW standard.[2]


The ASME PTC 19.3 TW (2016) Thermowells Standard is a widely used Code for thermowells machined from bar stock and includes those welded to or threaded into a flange as well as those welded into a process vessel or pipe with or without a weld adaptor.

See also[edit]


Regarding Measurement Error:

[1] Benedict, R.P, Murdock, J.W. (1963) "Steady-State Thermal Analysis of a Thermowell," ASME J. Eng. Power, July 1963, pp. 235-244.

More recent references involve radiation induced measurment error, sooting flames, proximity of heat sources.

Regarding Thermowell Design:

[1] ASME Performance Test Codes (2016), ASME PTC 19.3TW.

[2] Brock, James E., (1974),"Stress analysis of thermowells," Report NPS – 59B074112A, Naval Postgraduate School , Monterey California.

[3] Koves, William (2008) Question raised in PTC 19.3TW Committee meeting dealing with Brock’s support compliance and metal thickness.

[4] Porter, M.A., Martens, D.H. (2002) "Thermowell vibration investigation and analysis," ASME Press. Vessels and Piping 2002-1500, pp.171-176.

[5] Report (2007) "Extension and update of the guidelines for the avoidance of vibration induced fatigue of process pipework, Intrusive Element Assessment," Energy Inst. Report AVIFF-2005-13, pp.1-25.

[6] Leissa, A.W. (1973) "Vibration of Shells," NASA SP-288 , pp. 32-38.

[7] Karczub, D.G. (2006) "Expressions for direct evaluation of wave number in cylindrical shell vibration studies using the Flügge equations of motion," J. Acoust. Soc. Am. 119(6), pp. 3553-3557. DOI:10.1121 / 1.2193814.

[8] Bijlaard, P.P. (1955) "Stresses from local loadings in Cylindrical Shells," Trans. ASME, 77, p.p. 805-816.

[9] Sanders, J. L., Simmonds, J.G.(1970) "Concentrated Forces on Shallow Cylindrical Shells," ASME J. Applied Mech., 37, pp. 367-373.

[10] Steel, C.R, Steele , M.L. (1983) "Stress Analysis of Nozzles in Cylindrical Vessels With External Load," ASME J. Press. Vessel Tech., 105, pp. 191-200.

[11] Xue, Ming-De, Li, D. F., Hwang, K.C. (2005) "A Thin Shell Theoretical Solution for Two Intersecting Cylindrical Shells Due to External Branch Pipe Moments," ASME J. Press. Vessel Tech., 127 pp. 357-368.

[12] Wais, E. A., Rodabaugh, E.C., Carter, R. (1999) "Stress Intensification Factors and Flexibility Factors for Unreinforced Branch Connections," ASME Proc. Press. Vessels and Piping, 383, pp. 159-168.

[12] Xue, L., Widera, G.E.O., Seng, Z. (2006) "Flexibility Factors for Branch Connections Subject to In-plane and Out-of-plane moments,” ASME J. Press. Vessel Tech., 128, pp. 89-94.

[14] Ming, R.S., Pan, J., Norton, N. P. (1999) "The mobility functions and their application in calculating power," J. Acoust. Soc. Am. 105(3), pp. 1702-1713.

[15] Fegeant, O. (2001) "Closed form solutions for the point mobilities of axi-symmetrically excited cylindrical shells," J. of Sound and Vibration, 243(1), pp. 89-115.

[16] Motriuk, R. W. (1996) "Verification of Two Methods to Mitigate High Frequency Pipe Shell Vibration," ASME Proc., Montreal, PVP-FIV 328, pp. 405-413.

[17] Zhou, Z. J., Motriuk, R. W. (1996) "Influence of Tapered Thermowell Length on Temperature Measurement," ASME Proc., Integrity of Structures, PVP-333, pp. 97-104.

[18] O’Donnell, W.J. (1960) "The Additional Deflection of a Cantilever Due to the Elasticity of the Support," ASME J. Applied Mech., 27(3), pp.461-464.

[19] Brown, J.M., Hall, A.S. (1962) "Bending deflection of a circular shaft terminating in a semi-infinite body," ASME J. Applied Mech., 29(1), pp. 86-90. [20] MacBain, J.C., Genin, J. (1973) "Natural Frequencies of a Beam Considering Support Characteristics," J. Sound and Vibration, 27 (2), pp. 197-206 .

[21] Brock, J.E. (1974) "Stress analysis of thermowells," Report NPS – 59B074112A, Naval Postgraduate School Report AD/A-001 617, Naval Postgraduate School, Monterey California.

[22] Weaver, W., Timoshenko, S.P., Young, D.H. (1990) Vibration Problems in Engineering, 5th Ed., John Wiley & Sons, New York. [24] Han, S. M., Benaroya, H. , Wei, T. (1999) "Dynamics of Transversely Vibrating Beams Using Four Engineering Theories," Journal of Sound and Vibration, 225(5), pp. 935-988.

[25] Barthoff, L.W. (1981) "Thermowell Flow-Induced Vibrations Measured in Laboratory and FFTF Plant Piping," ASME PVP Conference , DEN PVP-168, Denver Colorado.

[26] Ogura, K., Fuji, T. (1999) "Flow-induced vibration test of thermowell in secondary cooling system of the prototype FBR," 7th Intl. Conf. on Nuclear Engineering, Tokyo Japan, ICONE 7380.

Regarding Published Failure Reports:

[1] Heffner, R.E., Gleave, S.W., Norberg, J.A. (1962) "SPERT III Thermowell Failure and Replacement," Atomic Energy Corp. Research and Development Report IDO-16741.

[2] Marten, W.F. (1973) "Thermowell Failure at Sodium Components Test Installation (SCTI)," Atomic Energy Corp. Research and Development Report, LDO-TDR-73-4. [3] Private Communication (1984), Off-Gas Temperature Measurement Case.

[4] Permana, Yhenda (1995) "Thermowell failure as a result of vortex shedding phenomena," Vibration Institute, Proc. 19th, Annual. Meeting, pp. 55-59.

[5] Eckert, B. (2010) "Centrifugal Compressor Case Study," Gas Mach. Conf., GMC 2010.

[6] SIGTTO Report Summary (2011) "Thermowells in LNG Liquid Carrier Lines," Soc. Int'l Gas Tanker and Terminal Operators, April 2011.

[7] El Batahgry, A.M., Fathy, G. (2013) "Fatigue failure of thermowells in feed gas supply downstream pipeline at a natural gas production plant," Case Studies in Engineering Failure Analysis, 1, pp. 79-84, DOI: 10.1016/J. CSEFA 2013.04.001.

[8] Kawamura, T., Nakao, T., Hashi, M., Murayama, K., (2001), "Strouhal Number Effect on Synchronized Vibration of a Circular Cylinder in Cross Flow", JSME Series B, 44(4), pp. 729-737.

[9] Rice, S. O. (1944), "Mathematical Analysis of Random Noise," Bell Sys. Tech. J., 23, pp. 282-332.

[10] Bendat, J.S., Piersol, A. G., (1971) Random Data: Analysis and Measurement, Wiley Interscience, N.Y.

[11] Blevins, R.D. , Burton, T.E. (1976), "Fluid Forces Induced by Vortex Shedding," ASME J. Fluids Eng., pp. 19-24.

[12] Jacquot, R.G. (2000) "Random Vibration of Damped Modified Beam Systems," J. Sound and Vibr., 234(3), pp. 441-454.

[13] Fung, Y.C., (1960), "Fluctuating Lift and Drag Acting on a Cylinder in a Flow at Supercritical Reynolds Numbers," J. Aerospace Sci., 27 (11), pp. 801-814.

[14] Roshko, A. (1961) "Experiments on the flow past a circular cylinder at very high Reynolds number," J. Fluid Mech., 10, pp. 345-356.

[15] Jones,G.W. (1968) "Aerodynamic Forces on Stationary and Oscillating Circular Cylinder at High Reynolds Numbers," ASME Symposium on Unsteady Flow, Fluids Engineering Div. , pp. 1-30.

[16] Jones,G.W., Cincotta, J.J., Walker, R.W. (1969) "Aerodynamic Forces on Stationary and Oscillating Circular Cylinder at High Reynolds Numbers," NASA Report TAR-300, pp. 1-66.

[17] Achenbach, E. Heinecke, E. (1981) "On vortex shedding from smooth and rough cylinders in the range of Reynolds numbers 6x103 to 5x106," J. Fluid Mech. 109, pp. 239-251.

[18] Schewe, G. (1983) "On the force fluctuations acting on a circular cylinder in crossflow from subcritical up to transcritical Reynolds numbers," J. Fluid Mech., 133, pp.265-285.

[19] Kawamura, T., Nakao, T., Takahashi, M., Hayashi, T., Murayama, K., Gotoh, N., (2003), "Synchronized Vibrations of a Circular Cylinder in Cross Flow at Supercritical Reynolds Numbers", ASME J. Press. Vessel Tech., 125, pp. 97-108, DOI:10.1115/1.1526855.

[20] Zdravkovich, M.M. (1997), Flow Around Circular Cylinders, Vol.I, Oxford Univ. Press. Reprint 2007, p.188.

[21] Zdravkovich, M.M. (2003), Flow Around Circular Cylinders, Vol. II, Oxford Univ. Press. Reprint 2009, p.761.

[22] Bartran, D. (2015) "Support Flexibility and Natural Frequencies of Pipe Mounted Thermowells," ASME J. Press. Vess. Tech., 137, pp.1-6 , DOI:10.1115/1.4028863

[23] Botterill, N. (2010) "Fluid structure interaction modelling of cables used in civil engineering structures," PhD dissertation (, University of Nottingham.

[24] Bartran, D. (2018) "TheDragCrisisandThermowellDesign," ASME J. Press. Vess. and Piping, Vol.140/044501-1.

External links[edit]

  • ^ Thomas W. Kerlin & Mitchell P. Johnson (2012). Practical Thermocouple Thermometry (2nd Ed.). Research Triangle Park: ISA. pp. 79–85. ISBN 978-1-937560-27-0. 
  • ^ Johnson, Mitchell P. & Gilson, Allan G. (August 2012). "Do Your Thermowells Meet the ASME Standard?". Flow Control. XVIII (8).