IEC 62097:2009

Hydraulic machines, radial and axial - Performance conversion method from model to prototype

IEC 62097:2009 is applicable to the assessment of the efficiency and performance of prototype hydraulic machine from model test results, with consideration of scale effect including the effect of surface roughness. This document is intended to be used for the assessment of the results of contractual model tests of hydraulic machines.

Machines hydrauliques, radiales et axiales - Méthode de conversion des performances du modèle au prototype

La CEI 62097:2009 est applicable à l'évaluation de l'efficacité et de la performance de machines hydrauliques prototypes à partir d'essais sur modèle d'essais avec la considération des effets d'échelle incluant l'effet de rugosité de surface. Ce document est prévue pour être employée pour l'évaluation des résultats des essais contractuels sur modèle réduit de machines hydrauliques.

General Information

• Status: Published
• Publication Date: 10-Feb-2009
• ICS: 27.140 - Hydraulic energy engineering
• Technical Committee: TC 4 - Hydraulic turbines
• Drafting Committee: WG 18 - TC 4/WG 18
• Current Stage: DELPUB - Deleted Publication
• Completion Date: 08-Jan-2019

Standards Content (Sample)

IEC 62097 ®
Edition 1.0 2009-02
INTERNATIONAL
STANDARD
NORME
INTERNATIONALE
Hydraulic machines, radial and axial – Performance conversion method from
model to prototype
Machines hydrauliques, radiales et axiales – Méthode de conversion des
performances du modèle au prototype

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IEC 62097 ®
Edition 1.0 2009-02
INTERNATIONAL
STANDARD
NORME
INTERNATIONALE
Hydraulic machines, radial and axial – Performance conversion method from
model to prototype
Machines hydrauliques, radiales et axiales – Méthode de conversion des
performances du modèle au prototype

INTERNATIONAL
ELECTROTECHNICAL
COMMISSION
COMMISSION
ELECTROTECHNIQUE
PRICE CODE
INTERNATIONALE
XC
CODE PRIX
ICS 27.140 ISBN 978-2-88910-619-6
– 2 – 62097 © IEC:2009
CONTENTS
FOREWORD.5

INTRODUCTION.7

1 Scope.9

2 Normative references .9

3 Terms, definitions, symbols and units .9

3.1 System of units .9

3.2 List of terms .9

3.2.1 Subscripts’ list .9
3.2.2 Terms, definitions, symbols and units .10
4 Scale-effect formula .13
4.1 General .13
4.1.1 Scalable losses .13
4.1.2 Basic formulae of the scale effect on hydrodynamic friction losses .15
4.2 Specific hydraulic energy efficiency.17
4.2.1 Step-up formula.17
4.2.2 Roughness of model and prototype.19
4.2.3 Direct step-up for a whole turbine .22
4.3 Power efficiency (disc friction).23
4.3.1 Step-up formula.23
4.3.2 Roughness of model and prototype.23
4.4 Volumetric efficiency .24
5 Standardized values of scalable losses and pertinent parameters .24
5.1 General .24
5.2 Specific speed.25
5.3 Parameters for specific hydraulic energy efficiency step-up.25
5.4 Parameters for power efficiency (disc friction) step-up.26
6 Calculation of prototype performance .27
6.1 General .27
6.2 Hydraulic efficiency .27
6.3 Specific hydraulic energy .28
6.4 Discharge.28
6.5 Torque .29

6.6 Power.29
6.7 Required input data .30
7 Calculation procedure.31
Annex A (informative) Basic formulae and their approximation.33
Annex B (informative) Scale effect on specific hydraulic energy losses of radial flow
machines .43
Annex C (informative) Scale effect on specific hydraulic energy losses of axial flow
machines [10] .63
Annex D (informative) Scale effect on disc friction loss .70
Annex E (informative) Leakage loss evaluation for non homologous seals .76
Bibliography.83

Figure 1 – Basic concept for step-up considering surface roughness .16

62097 © IEC:2009 – 3 –
Figure 2 – IEC criteria of surface roughness given in Tables 1 and 2 .20

Figure 3 – Francis Runner blade and fillets .21

Figure 4 – Runner blade axial flow.22

Figure 5 – Guide vanes.22

Figure 6 – Calculation steps of step-up values.32

Figure A.1 – Flux diagram for a turbine .34

Figure A.2 – Flux diagram for a pump .35

Figure B.1 – Loss coefficient versus Reynolds number and surface roughness .44

Figure B.2 – Different characteristics of λ in transition zone.45
Figure B.3 – Representative dimensions of component passages .48
Figure B.4 – Relative scalable hydraulic energy loss in each component of Francis
turbine .54
Figure B.5 – Relative scalable hydraulic energy loss in each component of pump-
turbine in turbine operation .55
Figure B.6 – Relative scalable hydraulic energy loss in each component of pump-
turbine in pump operation .56
Figure B.7 – κ and κ in each component of Francis turbine.57
uCO dCO
Figure B.8 – κ and κ in each component of pump-turbine in turbine operation.58

uCO dCO
Figure B.9 – κ and κ in each component of pump-turbine in pump operation .59
uCO dCO
Figure B.10 – d and d for Francis turbine .60
ECOref Eref
Figure B.11 – d and d for pump-turbine in turbine operation .61

ECOref Eref
Figure B.12 – d and d for pump-turbine in pump-operation .62

ECOref Eref
Figure C.1 – δ for Kaplan turbines .66
Eref
Figure D.1 – Disc friction loss ratio δ .72
Tref
Figure D.2 – Dimension factor κ .74
T
Figure D.3 – Disc friction loss index d .75
Tref
Figure E.1 – Examples of typical design of runner seals (crown side) .78
Figure E.2 – Examples of typical design of runner seals (band side) .79

Table 1 – Maximum recommended prototype runner roughness for new turbines (μm).21
Table 2 – Maximum recommended prototype guide vane roughness for new turbines
(μm).22

Table 3 – Permissible deviation of the geometry of model seals from the prototype .24
Table 4 – Scalable loss index d and velocity factor κ for Francis turbines.25

ECOref uCO
Table 5 – Scalable loss index d and velocity index κ for pump-turbines in
ECOref uCO
turbine operation.26
Table 6 – Scalable loss index d and velocity index κ for pump-turbines
...