ASTM E598-2008 923 Standard Test Method for Measuring Extreme Heat-Transfer Rates from High-Energy Environments Using a Transient Null-Point Calorimeter《用瞬变零点量热器测量高能环境的超级传热速率的标准试验方.pdf

《ASTM E598-2008 923 Standard Test Method for Measuring Extreme Heat-Transfer Rates from High-Energy Environments Using a Transient Null-Point Calorimeter《用瞬变零点量热器测量高能环境的超级传热速率的标准试验方.pdf》由会员分享，可在线阅读，更多相关《ASTM E598-2008 923 Standard Test Method for Measuring Extreme Heat-Transfer Rates from High-Energy Environments Using a Transient Null-Point Calorimeter《用瞬变零点量热器测量高能环境的超级传热速率的标准试验方.pdf（10页珍藏版）》请在麦多课文档分享上搜索。

1、Designation: E 598 08Standard Test Method forMeasuring Extreme Heat-Transfer Rates from High-EnergyEnvironments Using a Transient, Null-Point Calorimeter1This standard is issued under the fixed designation E 598; the number immediately following the designation indicates the year oforiginal adoption

2、 or, in the case of revision, the year of last revision. A number in parentheses indicates the year of last reapproval. Asuperscript epsilon () indicates an editorial change since the last revision or reapproval.1. Scope1.1 This test method covers the measurement of the heat-transfer rate or the hea

3、t flux to the surface of a solid body (testsample) using the measured transient temperature rise of athermocouple located at the null point of a calorimeter that isinstalled in the body and is configured to simulate a semi-infinite solid. By definition the null point is a unique positionon the axial

4、 centerline of a disturbed body which experiencesthe same transient temperature history as that on the surface ofa solid body in the absence of the physical disturbance (hole)for the same heat-flux input.1.2 Null-point calorimeters have been used to measure highconvective or radiant heat-transfer ra

5、tes to bodies immersed inboth flowing and static environments of air, nitrogen, carbondioxide, helium, hydrogen, and mixtures of these and othergases. Flow velocities have ranged from zero (static) throughsubsonic to hypersonic, total flow enthalpies from 1.16 togreater than 4.65 3 101MJ/kg (5 3 102

6、to greater than2 3 104Btu/lb.), and body pressures from 105to greater than1.5 3 107Pa (atmospheric to greater than 1.5 3 102atm).Measured heat-transfer rates have ranged from 5.68 to2.84 3 102MW/m2(5 3 102to 2.5 3 104Btu/ft2-sec).1.3 The most common use of null-point calorimeters is tomeasure heat-t

7、ransfer rates at the stagnation point of a solidbody that is immersed in a high pressure, high enthalpy flowinggas stream, with the body axis usually oriented parallel to theflow axis (zero angle-of-attack). Use of null-point calorimetersat off-stagnation point locations and for angle-of-attack test

8、ingmay pose special problems of calorimeter design and datainterpretation.1.4 This standard does not purport to address all of thesafety concerns, if any, associated with its use. It is theresponsibility of the user of this standard to establish appro-priate safety and health practices and determine

9、 the applica-bility of regulatory limitations prior to use.2. Referenced Documents2.1 ASTM Standards:2E 422 Test Method for Measuring Heat Flux Using aWater-Cooled CalorimeterE511 Test Method for Measuring Heat Flux Using aCopper-Constantan Circular Foil, Heat-Flux Transducer3. Terminology3.1 Symbol

10、s:a = Radius of null-point cavity, m (in.)b = Distance from front surface of null-point calorimeterto the null-point cavity, m (in.)Cp= Specific heat capacity, J/kgK (Btu/lb-F)d = Diameter of null-point cavity, m (in.)k = Thermal conductivity, W/mK (Btu/in.-sec-F)L = Length of null-point calorimeter

11、, m (in.)q = Calculated or measured heat flux or heat-transfer-rate,W/m2(Btu/ft2-sec)q0= Constant heat flux or heat-transfer-rate, W/m2(Btu/ft2-sec)R = Radial distance from axial centerline of TRAX ana-lytical model, m (in.)r = Radial distance from axial centerline of null-pointcavity, m (in.)T = Te

12、mperature, K (F)Tb= Temperature on axial centerline of null point, K (F)Ts= Temperature on surface of null-point calorimeter, K(F)t = Time, sec1This test method is under the jurisdiction of ASTM Committee E21 on SpaceSimulation and Applications of Space Technology and is the direct responsibility of

13、Subcommittee E21.08 on Thermal Protection.Current edition approved Dec. 1, 2008. Published January 2009. Originallyapproved in 1977. Last previous edition approved in 2002 as E 598 96 (2002).2For referenced ASTM standards, visit the ASTM website, www.astm.org, orcontact ASTM Customer Service at serv

14、iceastm.org. For Annual Book of ASTMStandards volume information, refer to the standards Document Summary page onthe ASTM website.1Copyright ASTM International, 100 Barr Harbor Drive, PO Box C700, West Conshohocken, PA 19428-2959, United States.Z = Distance in axial direction of TRAX analytical mode

15、l,m (in.)a = Thermal diffusivity, m2/sec (in.2/sec)r = Density, kg/m3(lb/in.3)4. History of Test Method4.1 From literature reviews it appears that Masters and Stein(1)3were the first to document the results of an analytical studyof the temperature effects of axial cavities drilled from thebackside o

16、f a wall which is heated on the front surface (see Fig.1). These investigators were primarily concerned with thedeviation of the temperature measured in the bottom of thecavity from the undisturbed temperature on the heated surface.Since they were not in possession of either the computingpower or th

17、e numerical heat conduction codes now available tothe analyst, Masters and Stein performed a rigorous math-ematical treatment of the deviation of the transient tempera-ture, Tb, on the bottom centerline of the cavity of radius, a, andthickness, b, from the surface temperature Ts. The results ofMaste

18、rs and Stein indicated that the error in temperaturemeasurement on the bottom centerline of the cavity woulddecrease with increasing values of a/b and also decrease withincreasing values of the dimensionless time, at/b2, where a isthe thermal diffusity of the wall material. They also concludedthat t

19、he most important factor in the error in temperaturemeasurement was the ratio a/band the error was independent ofthe level of heat flux. The conclusions of Masters and Steinmay appear to be somewhat elementary compared with ourknowledge of the null-point concept today. However, theidentification and

20、 documentation of the measurement conceptwas a major step in leading others to adapt this concept to thetransient measurement of high heat fluxes in ground testfacilities.4.2 Beck and Hurwicz (2) expanded the analysis of Mastersand Stein to include steady-state solutions and were the first tolabel t

21、he method of measurement “the null-point concept.”They effectively used a digital computer to generate relativelylarge quantities of analytical data from numerical methods.Beck and Hurwicz computed errors due to relatively largethermocouple wires in the axial cavity and were able to suggestthat the

22、optimum placement of the thermocouple in the cavityoccurred when the ratio a/b was equal to 1.1. However, theiranalysis like that of Masters and Stein was only concerned withthe deviation of the temperature in the axial cavity and did notaddress the error in measured heat flux.4.3 Howey and DiCristi

23、na (3) were the first to perform anactual thermal analysis of this measurement concept. Althoughthe explanation of modeling techniques is somewhat ambigu-ous in their paper, it is obvious that they used a finite element,two dimensional axisymmetric model to produce temperatureprofiles in a geometry

24、simulating the null-point calorimeter.Temperature histories at time intervals down to 0.010 sec wereobtained for a high heat-flux level on the surface of theanalytical model. Although the analytical results are notpresented in a format which would help the user/designeroptimize the sensor design, th

25、e authors did make significant3The boldface numbers in parentheses refer to the list of references at the end ofthis test method.NOTE 11-Ts(0,t) = Surface temperature (x = 0) of a solid, semi-infinite slab at some time, t.NOTE 22-Tb(0,b,t) = Temperature at r = 0, x = b of a slab with a cylindrical c

26、avity at some time, t, heat flux, q, the same in both cases.FIG. 1 Semi-infinite Slab with Cylindrical CavityE598082general conclusions about null point calorimeters. These in-clude: (1) “., thermocouple outputs can yield deceivingly fastresponse rates and erroneously high heating rates ( + 18 %)whe

27、n misused in inverse one-dimensional conduction solu-tions.” (2) “The prime reason for holding the thermocoupledepth at R/E = 1.1 is to maximize thermocouple response athigh heating rates for the minimum cavity depth.” (Note:R and E as used by Howey and DeChristina are the same termsas a and b which

28、 are defined in 4.1 and are used throughout thisdocument.) (3) A finite length null-point calorimeter body maybe considered semi-infinite for:at!L2#0.34.4 Powars, Kennedy, and Rindal (4 and 5) were the first todocument using null point calorimeters in the swept mode.This method which is now used in

29、almost all arc facilities hasthe advantages of (1) measuring the radial distributions acrossthe arc jet, and (2) preserving the probe/sensor structuralintegrity for repeated measurements. This technique involvessweeping the probe/sensor through the arc-heated flow field ata rate slow enough to allow

30、 the sensor to make accuratemeasurements, yet fast enough to prevent model ablation.4.4.1 Following the pattern of Howey and DiCristina,Powars et. al. stressed the importance of performing thermalanalyses to “characterize the response of a typical real nullpoint calorimeter to individually assess a

31、variety of potentialerrors, .”. Powars et. al. complain that Howey a/b = 2.4, the calculatedheat flux will be 20 % higher than the actual heat flux. In morerecent documentation using more accurate and sophisticatedheat conduction computer codes as well as an establishednumerical inverse heat conduct

32、ion equation (6), the error inindicated heat flux is shown to be considerably higher than20 % and is highly time dependent.4.5 The latest and most comprehensive thermal analysis ofthe null-point calorimeter concept was performed by Kidd anddocumented in Refs (6 and 7). This analytical work wasaccomp

33、lished by using a finite element axisymmetric heatconduction code (7). The finite element model simulating thenull-point calorimeter system is comprised of 793 finite ele-ments and 879 nodal points and is shown in block diagramform in Fig. 2. Timewise results of normalized heat flux fordifferent phy

34、sical dimensional parameters (ratios of a to b) aregraphically illustrated on Figs. 3 and 4. The optimum value ofthe ratio a/b is defined to be that number which yields thefastest time response to a step heat-flux input and maintains aconstant value of indicated q/input q after the initial timerespo

35、nse period. From Figs. 3 and 4, it can be seen that thisoptimum value is about 1.4 for two families of curves forwhich the cavity radius, a, is held constant while the cavitythickness, b, is varied to span a wide range of the ratio a/b. Thisis a slightly higher value than reported by earlier analyst

36、s. It isimportant to note that the analytical results do not necessarilyhave to give a value of indicated q/input q = 1.0 since thisdifference can be calibrated in the laboratory. The data graphi-cally illustrated on Figs. 3 and 4 and substantiate conclusionsdrawn by the authors of Refs (3 nd 4) tha

37、t the calculated heatflux can be considerably higher than the actual input heatfluxespecially as the ratio of a/b is raised consistently above1.5. All of the users of null-point calorimeters assume that thedevice simulates a semi-infinite body in the time period ofinterest. Therefore, the sensor is

38、subject to the finite bodylength, L, defined by L/(at)1/2# 1.8 in order that the error inindicated heat flux does not exceed one percent (6 and 7). Thisrestriction agrees well with the earlier work of Howey andDiCristina (3).4.6 A section view sketch of a typical null-point calorimetershowing all im

39、portant components and the physical configu-ration of the sensor is shown in Fig. 5. The outside diameter is2.36 mm (0.093 in.), the length is 10.2 mm (0.40 in.), and thebody material is oxygen-free high conductivity (OFHC) cop-per. Temperature at the null point is measured by a 0.508 mm(0.020 in.)

40、diam American National Standards Association(ANSI) type K stainless steel-sheathed thermocouple with0.102 mm (0.004 in.) diam thermoelements. Although nothermocouple attachment is shown, it is assumed that theindividual thermocouple wires are in perfect contact with thebackside of the cavity and pre

41、sent no added thermal mass to thesystem. Details of installing thermocouples in the null pointcavity and making a proper attachment of the thermocouplewith the copper slug are generally considered to be proprietaryby the sensor manufacturers. Kidd in Ref (7) states that theattachment is made by ther

42、mal fusion without the addition offoreign materials. Note that the null-point body has a smallflange at the front and back which creates an effective dead airspace along the length of the cylinder to enhance one-dimensional heat conduction and prevent radial conduction.For aerodynamic heat-transfer

43、measurements, the null-pointsensors are generally pressed into the stagnation position of asphere cone model of the same material (OFHC copper).4.7 The value of the lumped thermal parameter of copper isnot a strong function of temperature. In fact, the value of(rCpk)1/2for OFHC copper varies less th

44、an three percent fromroom temperature to the melting point, 1356 K (1981F); (seeFig. 6). Thermal properties of OFHC copper are well docu-mented and data from different sources are in good agreement(8). Most experimenters use the room temperature value of theparameter in processing data from null-poi

45、nt calorimeters.E5980834.8 The determination of surface heat flux as a function oftime and temperature requires a digital computer, programmedto calculate the correct values of heat-transfer rate. Having themeasured null-point cavity temperature, the problem to besolved is the inverse problem of hea

46、t conduction. Severalversions of the well known Cook and Felderman numericalFIG. 2 Finite Element Model of Null-Point CalorimeterFIG. 3 Null-Point Calorimeter Analytical Time Response DataE598084integration equation (9) can be used to obtain the surface heatflux as a function of time. These equation

47、s are described inSection 10.5. Significance and Use5.1 The purpose of this test method is to measure extremelyhigh heat-transfer rates to a body immersed in either a staticenvironment or in a high velocity fluid stream. This is usuallyaccomplished while preserving the structural integrity of themea

48、surement device for multiple exposures during the mea-surement period. Heat-transfer rates ranging up to 2.84 3 102MW/m2(2.5 3 104Btu/ft2-sec) (7) have been measured usingnull-point calorimeters. Use of copper null-point calorimetersprovides a measuring system with good response time andmaximum run

49、time to sensor burnout (or ablation). Null-pointcalorimeters are normally made with sensor body diameters of2.36 mm (0.093 in.) press-fitted into the nose of an axisym-metric model.5.2 Sources of error involving the null-point calorimeter inhigh heat-flux measurement applications are extensively dis-cussed in Refs (3-7). In particular, it has been shown bothanalytically and experimentally that the thickness of the copperabove the null-point cavity is critical. If the thickness is toogreat, the time response of the instrument will not be fastFIG. 4 Null-Point Calorim