ANSI ASME PTC 10-1997 Performance Test Code on Compressors and Exhausters.pdf

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1、 Intentionally left blank ASME PTC 1 O-1 997 Performance Test Code on Compressors and Exhausters Date of issuance: September 30, 1998 This document will be revised when the Society approves the issuance of a new edition. There will be no addenda issued to ASME PTC 10-1997. Please Note: ASME issues w

2、ritten replies to inquiries concerning interpretation of technical aspects of this document. The interpretations are not part of the document. PTC lo-1997 is being issued with an automatic subscription service to the interpreta- tions that will be issued to it up to the publication of the next editi

3、on. ASME is the registered trademark of The American Society of Mechanical Engineers. This code or standard was developed under procedures accredited as meeting the criteria for American National Standards. The Standards Committee that approved the code or standard was balanced to assure that indivi

4、duals from competent and concerned interests have had an opportunity to participate. The proposed code or standard was made available for public review and comment which provides an opportunity for additional public input from industry, academia, regulatory agencies, and the public-at-large. ASME do

5、es not “approve, ” “rate,” or “endorse” any item, construction, proprietary device, or activity. ASME does not take any position with respect to the validity of any patent rights asserted in connection with any items mentioned in this document, and does not undertake to insure anyone utilizing a sta

6、ndard against liability for infringement of any applicable Letters Patent, nor assume any such liability. Users of a code or standard are expressly advised that determination of the validity of any such patent rights, and the risk of infringement of such rights, is entirely their own responsibility.

7、 Participation by federal agency representative(s) or person(s) affiliated with industry is not to be interpreted as government or industry endorsement of this code or standard. ASME accepts responsibility for only those interpretations issued in accordance with governing ASME procedures and policie

8、s which preclude the issuance of interpretations by individual volunteers. No part of this document may be reproduced in any form, in an electronic retrieval system or otherwise, without the prior written permission of the publisher. The American Society of Mechanical Engineers Three Park Avenue, Ne

9、w York, NY 10016-5990 Copyright 0 1998 by THE AMERICAN SOCIETY OF MECHANICAL ENGINEERS All Rights Reserved Printed in U.S.A. FOREWORD (This Foreword is not a part of ASME PTC 10-1997.) PTC 10 was last revised in 1965 and it has been reaffirmed many times in the intervening period. The PTC 10 Committ

10、ee has been in various states of activity for approximately the past 20 years. During that time the Code has been completely rewritten to be far more explanatory in nature. The performance testing of compressors is complicated by the need in virtually every case to consider and make correction for t

11、he differences between the test and specified conditions. The techniques used to do so are based upon the rules of fluid-dynamic similarity. Some familiarity with this fundamental technique will be a significant aid to the users of PTC 10. Compressors and exhausters come in all sorts of configuratio

12、ns. A very simple case is a single section compressor with one impeller, and single inlet and outlet flanges. Many more complex arrangements exist with multiple inlets, outlets, impellers, sections, in- tercoolers and side seams. Typical gases handled are air, its constituents, and various hydrocarb

13、ons. Tests are commonly run in the shop or in the field, at speeds equal to or different from the specified speed, and with the specified or a substitute gas. In order to handle this vast array of possibilities PTC 10 reduces the problem to the simplest element, the section, and provides the instruc

14、tions for combining multiple sections to compute the overall results. Uncertainty analysis can play a very important role in compressor testing, from the design of the test to interpretation of the test results. In all but the very simplest of cases the development of an analytic formulation, i.e.,

15、in simple equation form, for overall uncertainty computation is formidable. The test uncertainty will always be increasingly more complex to evaluate with the complexity of the compressor configuration, and by the very nature of the test will be a function of the performance curves. The modern perso

16、nal computer is readily capable of completing the calculations re- quired. The Committee developed software and used it to perform both the basic code calculations and uncertainty analysis computations for a wide range of possible compressor configurations. This Code was approved by the PTC 10 Commi

17、ttee on January 18,199l. It was approved and adopted by the Council as a standard practice of the Society by action of the Board on Performance Test Codes on October 14, 1996. It was also approved as an American National Standard by the ANSI Board of Standards Review on April 22, 1997. iii NOTICE Al

18、l Performance Test Codes MUST adhere to the requirements of PTC 1, GENERAL INSTRUCTIONS. The following information is based on that document and is included here for emphasis and for the convenience of the user of this Code. It is expected that the Code user is fully cognizant of Parts I and III of

19、PTC 1 and has read them prior to applying this Code. ASME Performance Test Codes provide test procedures which yield results of the highest level of accuracy consistent with the best engineering knowledge and practice currently available. They were developed by balanced committees representing all c

20、oncerned interests. They specify procedures, instrumentation, equipment operating requirements, calculation methods, and uncertainty analysis. When tests are run in accordance with this Code, the test results themselves, without adjust- ment for uncertainty, yield the best available indication of th

21、e actual performance of the tested equipment. ASME Performance Test Codes do not specify means to compare those results to contractual guarantees. Therefore, it is recommended that the parties to a commercial test agree before starting the test and preferably before signing the contract on the metho

22、d to be used for comparing the test results to the contractual guarantees. It is beyond the scope of any code to determine or interpret how such comparisons shall be made. Approved by Letter Ballot #95-l and BPTC Administrative Meeting of March 13-14, 1995 iv PERSONNEL OF PERFORMANCE TEST CODE COMMl

23、lTEE NO. 10 ON COMPRESSORS AND EXHAUSTERS (The following is the roster of the Committee at the time of approval of this Code.) OFFICERS Gordon J. Gerber, Chair Richard J. Gross, Vice Chair Jack H. Karian, Secretary COMMITTEE PERSONNEL Helmut B. Baranek, Public Service Electric psia 5% Inlet temperat

24、ure r; OR a% Speed rpm 2% Molecular weight MW Ibm/lbmole 2% Cooling temperature OR 5% difference Coolant flow rate gal/min 3% Capacity 9i fts/min 4% GENERAL NOTES: (a) Type 1 tests are to be conducted with the specified gas. Deviations are based on the specified values where pressures and temperatur

25、es are expressed in absolute values. (b) The combined effect of inlet pressure, temperature and molecular weight shall not produce more than an a% deviation in the inlet gas density. (c) The combined effect of the deviations shall not exceed the limited of Table 3.2. Cooling temperature difference i

26、s defined as inlet gas temperature minus inlet cooling water temperature. TABLE 3.2 PERMISSIBLE DEVIATION FROM SPECIFIED OPERATING PARAMETERS FOR TYPE 1 AND 2 TESTS Parameter Specific volume ratio Flow coefficient Symbol v for example, intercooled com- pressors handling moist air; the capacity shall

27、 be measured at the compressor discharge. (For atmo- spheric exhausters the flow shall be measured at the inlet.) Care shall be taken to assure that there is no liquid carry-over from the intercoolers. 3.3.6 Volume flow ratios may in practice differ between test and specified operating conditions du

28、e to leakage differences. For example, it is common to test at reduced inlet pressure and the reduced differential pressure across a seal to atmosphere could result in zero or negative leakage. As a result, volume flow ratio equality can not be achieved between test and specified conditions. Therefo

29、re, it shall be necessary to estimate the leakage ratio; that is, the leakage mass flow divided by the inlet mass flow for both test and specified conditions. If the leakage ratio difference between test and specified is significant, these effects shall be applied to the calculations of capacity and

30、 power. 13 ASME PTC lo-1997 COMPRESSORS AND EXHAUSTERS TABLE 3.4 PERMISSIBLE FLUCTUATIONS OF TEST READINGS Measurement Symbol Units Fluctuation Inlet pressure Inlet temperature Discharge pressure Nozzle differential pressure Nozzle temperature Speed Torque Electric motor input Molecular weight Cooli

31、ng water inlet temperature Cooling water flow rate Line voltage Pd AP T N 7 MW T psia “R psia psi OR rpm Ibf . ft kw Ibm/lbmole “R 2% 0.5% 2% 2% 0.5% 0.5% 1% 1% 0.25% 0.5% Note (2)1 gal/min volts 2% 2% GENERAL NOTES: (a) A fluctuation is the percent difference between the minimum and maximum test re

32、ading divided by the average of all readings. (b) Permissible fluctuations apply to Type 1 and Type 2 tests. NOTES: (1) See para. 5.4.2.3. (2) See para. 4.16 for further restrictions. Multiple entry streams in Test section J I Multiple exit boundary I streams 1 - i -r I I 4 I m-s- -_-_ Heat transfer

33、 FIG. 3.1 SECTION CONTROL VOLUMES 14 COMPRESSORS AND EXHAUSTERS ASME PTC lo-1997 In many cases it is not practical to measure the leakage flow and it is permissible to use calculated values of leakage for test and specified conditions. 3.3.7 Where the efficiency is to be determined by shaft input po

34、wer measurements the bearing and seal losses should not exceed 10 percent of the total test power. This will minimize the effect of uncertainties in the bearing and seal loss determina- tion of gas power. 3.3.8 Evaluation of performance of components between sections, if any, such as heat exchangers

35、, piping, valves, etc., is generally beyond the scope of this Code and shall be agreed upon by parties to the test. The specified operating condition per- formance of such components or the technique for correction of test results to specified operating conditions shall be agreed upon by parties to

36、the test. 3.3.9 When power is to be determined by the heat balance method, the heat losses due to radiation and convection, expressed in percent of the total shaft power, shall not exceed 5 percent. 3.3.10 For Type 2 tests, the inlet gas condition shall have a minimum of 5F of superheat. 3.4 TEST GA

37、S AND SPEED 3.4.1 The physical and thermodynamic properties of the specified and test gas shall be known. The option of using tabulated data, an equation of state correlation, or experimental determination as a source for these properties shall be agreed upon prior to the test. 3.4.2 The following p

38、hysical properties of the test gas throughout the expected pressure and tempera- ture range shall be known or accurately determined: (a) molecular weight (b) specific heat at constant pressure (c,J fc,J ratio of specific heats (c&I (d) compressibility factor (2 (e) dew point (fj viscosity (g) isentr

39、opic exponent fh) enthalpy fi,l acoustic velocity 3.4.3 The test speed shall be selected so as to conform to the limits of Table 3.2. The test speed shall not exceed the safe operating speed of the compressor. Consideration should be given to critical speeds of rotating equipment in selecting the te

40、st speed. Test pressures and temperatures shall not exceed the maximum allowable pressures and temperatures for the compressor. 3.5 INTERMEDIATE FLOW STREAMS 3.5.1 Section Treatment. Compressors having flows added or removed at intermediate locations between the inlet and final discharge are handled

41、 by treating the compressor by sections. The gas state and flow rate shall be established for each stream where it crosses the section boundary. 3.5.2 It is necessary to maintain a consistency between specified volume flow rate ratio and test volume flow rate ratio for each section. Permissible devi

42、ations from these ratios are listed in Fig. 3.2. As an example, in the first section of a multisection compressor, the ratio of inlet volume flow rate to discharge volume flow rate for the specified and test conditions must be held to within ?5 percent which is the same as that required for conventi

43、onal compressors in Table 3.2. In addition, it is required that the ratio of first stage section discharge flow rate to second section inlet volume flow rate for the specified and test conditions be held to within +lO percent. This is required so that the total pressure determined at the sidestream

44、flange will have the same relationship to the total pressure actually existing at the exit of the first section bound- ary for specified and test conditions. For the second and succeeding sections the re- quirements are similar. The ratio of inlet volume flow rate to discharge volume flow rate for s

45、pecified and test conditions must be held to within +5 percent. Also, the preceding section discharge volume flow rate to sidestream inlet volume flow rate ratio for specified and test conditions must be held to 210 percent. Finally, the ratio of the discharge volume flow rate of the section being t

46、ested to the next sidestream volume flow rate must also be held to 2 10 percent. This requirement is most important in the second section of a three section machine where both inlet and discharge total pressures are being determined at the sidestream flanges and velocity similarities are necessary f

47、or test accuracy. Code requirements are also described in equation form in Fig. 3.2. 15 l_UlL-_-_ Section 1 Min. Max. Min. Max. Min. Max. 41 rql_2 = - 9 (rqj_$t - (rql-2)sP 95 105 rq3-2 = 2 (re2)t go ,O (rql-2)w 6-5 = 2 45 (rq6-5)t (rq6-5Lsp 90 110 s3 93-2 = z (rq2_2)t (rq2-2)v 90 110 Q4 rg.+_5 = -

48、g5 95 105 Q7 (rq7-8)t g5 ,05 rq7_8=- - 78 (rq7-8)sP where: subscript 1 = Section 1 inlet from flange measurements 2 = Section 1 discharge computed from measurements before sidestream 3 = Section 2 inlet from flange measurements Section 2 46 rg6-5 = 95 (rq6_# 90 &6-5)sP . 110 subscript 4 = Section 2

49、mixed inlet computed 5= Section 2 discharge computed from internal measurements before sidestream 6 Section 3 inlet from flange measurements Section 3 subscript 7 = Section 3 mixed inlet computed 2 E 8 = Section 3 discharge from 5 flange measurements z % 0 ? : Y z FIG. 3.2 TYPICAL SIDELOAD SECTIONAL COMPRESSORS COMPRESSORS AND EXHAUSTERS 3.5.3 Inward Sidestreams. When the sidestream flow is inward, the discharge temperature of the preceding section shall be measured prior to the mixing of the two str