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


IEC 62097:2009

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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
® Registered trademark of the International Electrotechnical Commission
Marque déposée de la Commission Electrotechnique Internationale

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– 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

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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 in
ECOref uCO
pump operation.26
Table 7 – Scalable loss index d and velocity factor κ for axial flow machines .26

ECOref uCO
Table 8 – Required input data for the calculation of the prototype performance .30
Table B.1 – d and κ for step-up calculation of whole turbine .51
Eref u0
Table B.2 – Criteria for the surface roughness for the application of the direct step-up
formula .52

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d
EST

Table C.1 – Ratio of for Francis turbines and pump-turbines .68
δ
EST

Table C.2 – Parameters to obtain Δ for axial flow machines .68
ECO

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62097 © IEC:2009 – 5 –


INTERNATIONAL ELECTROTECHNICAL COMMISSION

_____________



HYDRAULIC MACHINES, RADIAL AND AXIAL –

PERFORMANCE CONVERSION METHOD

FROM MODEL TO PROTOTYPE





FOREWORD


1) The International Electrotechnical Commission (IEC) is a worldwide organization for standardization comprising
all national electrotechnical committees (IEC National Committees). The object of IEC is to promote
international co-operation on all questions concerning standardization in the electrical and electronic fields. To
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5) IEC provides no marking procedure to indicate its approval and cannot be rendered responsible for any
equipment declared to be in conformity with an IEC Publication.
6) All users should ensure that they have the latest edition of this publication.
7) No liability shall attach to IEC or its directors, employees, servants or agents including individual experts and
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Publications.
8) Attention is drawn to the Normative references cited in this publication. Use of the referenced publications is
indispensable for the correct application of this publication.
9) Attention is drawn to the possibility that some of the elements of this IEC Publication may be the subject of
patent rights. IEC shall not be held responsible for identifying any or all such patent rights.
International Standard IEC 62097 has been prepared by technical committee 4: Hydraulic
turbines.

The text of this standard is based on the following documents:
FDIS Report of voting
4/242A/FDIS 4/243/RVD

Full information on the voting for the approval of this standard can be found in the report on
voting indicated in the above table.
This publication has been drafted in accordance with the ISO/IEC Directives, Part 2.
This publication contains attached files in the form of Excel file. These files are intended to be
used as a complement and do not form an integral part of this publication.

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– 6 – 62097 © IEC:2009


The committee has decided that the contents of this publication will remain unchanged until

the maintenance result data indicated on the IEC web site under “http://webstore.iec.ch” in the

data related to the specific publication. At this date, the publication will be


• recommended;

• withdrawn;

• replaced by a revised edition;


• or amended.

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62097 © IEC:2009 – 7 –


INTRODUCTION


0.1 General remarks


This International Standard establishes the prototype hydraulic machine efficiency from model

test results, with consideration of scale effect including the effect of surface roughness.


Advances in the technology of hydraulic turbo-machines used for hydroelectric power plants

1
indicate the necessity of revising the scale effect formula given in 3.8 of IEC 60193. [1] The

advance in knowledge of scale effects originates from work done by research institutes,

manufacturers and relevant working groups within the organizations of IEC and IAHR. [1 - 7]

The method of calculating prototype efficiencies, as given in this standard, is supported by
experimental work and theoretical research on flow analysis and has been simplified for
practical reasons and agreed as a convention. [8 – 10] The method is representing the
present state of knowledge of the scale-up of performance from model to a homologous
prototype.
Homology is not limited to the geometric similarity of the machine components, it also calls for
homologous velocity triangles at the inlet and outlet of the runner/impeller. [2] Therefore,
compared to IEC 60193, a higher attention has to be paid to the geometry of guide vanes.
According to the present state of knowledge, it is certain that, in most cases, the formula for
the efficiency step-up calculation given in the IEC 60193 and earlier standards, overstated the
step-up increment of the efficiency for the prototype. Therefore, in the case where a user
wants to restudy a project for which a calculation of efficiency step-up was done based on any
previous method, the user shall re-calculate the efficiency step-up with the new method given
in this standard, before restudying the project of concern.
This standard is intended to be used mainly for the assessment of the results of contractual
model tests of hydraulic machines. If it is used for other purposes such as evaluation of
refurbishment of machines having very rough surfaces, special care should be taken as
described in Annex B.
Due to the lack of sufficient knowledge about the loss distribution in Deriaz turbines and
storage pumps, this standard does not provide the scale effect formula for them.
An excel work sheet concerning the step-up procedures of hydraulic machine performance
from model to prototype is indicated at the end of this Standard to facilitate the calculation of
the step-up value.

0.2 Basic features
A fundamental difference compared to the IEC 60193 formula is the standardization of
scalable losses. In a previous standard (see 3.8 of IEC 60193:1999 [1]), a loss distribution
factor V has been defined and standardized, with the disadvantage that turbine designs which
are not optimized benefit from their lower technological level.
This is certainly not correct, since a low efficiency design has high non-scalable losses, like
incidence losses, whereby the amount of scalable losses is about constant for all
manufacturers, for a given type and a given specific speed of a hydraulic machine.
This standard avoids all the inconsistencies connected with IEC 60193:1999. (see 3.8 of [1])
A new basic feature of this standard is the separate consideration of losses in specific
hydraulic energy, disc friction losses and leakage losses. [5], [8 – 10]
—————————
1
 Numbers in square brackets refer to the bibliography.

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Above all, in this standard, the scale-up of the hydraulic performance is not only driven by the

dependence of friction losses on Reynolds number Re, but also the effect of surface

roughness Ra has been implemented.


Since the roughness of the actual machine component differs from part to part, scale effect is

evaluated for each individual part separately and then is finally summed up to obtain the

overall step-up for a complete turbine. [10] For radial flow machines, the evaluation of scale

effect is conducted on five separate parts; spiral case, stay vanes, guide vanes, runner and

draft tube. For axial flow machines, the scalable losses in individual parts are not fully

clarified yet and are dealt with in two parts; runner blades and all the other stationary parts
inclusive.

The calculation procedures according to this standard are summarized in Clause 7 and Excel
sheets are provided as an Attachment to this standard to facilitate the step-up calculation.
In case that the Excel sheets are used for evaluation of the results of a contractual model
test, each concerned party shall execute the calculation individually for cross-check using
common input data agreed on in advance.

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62097 © IEC:2009 – 9 –


HYDRAULIC MACHINES, RADIAL AND AXIAL –

PERFORMANCE CONVERSION METHOD

FROM MODEL TO PROTOTYPE








1 Scope


This International Standard 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 standard is intended to be used for the assessment of the results of contractual model
tests of hydraulic machines.
2 Normative references
The following referenced documents are indispensable for the application of this document.
For dated references, only the edition cited applies. For undated references, the latest edition
of the referenced document (including any amendments) applies.
IEC 60193:1999, Hydraulic turbines, storage pumps and pump-turbines – Model acceptance
tests
3 Terms, definitions, symbols and units
3.1 System of units
The International System of Units (SI) is used throughout this standard. All terms are given in
SI Base Units or derived coherent units. Any other system of units may be used after written
agreement of the contracting parties.
3.2 List of terms
For the purposes of this document, the terms and definitions of IEC 60193 apply, as well as
the following terms, definitions, symbols and units.
3.2.1 Subscripts’ list

Term Symbol Term Symbol

model M component CO
prototype P
specific energy E spiral case SP
volumetric Q stay vane SV
torque or disc friction T guide vane GV
in general term
represented by
reference ref runner RU
CO
hydraulic diameter d draft tube DT
velocity u stationary part ST
hydraulic h
optimum point opt
off design point off

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3.2.2 Terms, definitions, symbols and units


Term Definition Symbol Unit

Radial flow machines Francis turbines and Francis type reversible pump-turbines - -

Axial flow machines Kaplan turbines, bulb turbines and fixed blade propeller - -

turbines

Reference diameter Reference diameter of the hydraulic machine D m

(see Figure 3 of IEC 60193)

Hydraulic diameter 4 times sectional area divided by the circumference of the m
d
h
section

Sand roughness Equivalent sand roughness [11] k m
S
Arithmetical mean Deviation of the surface profile represented by the Ra m
roughness arithmetical mean value
–2
Acceleration due to Local value of gravitational acceleration at the place of g m s
gravity testing as a function of altitude and latitude (see
IEC 60193)
–3
Density of water Mass per unit volume of water (see IEC 60193) kg m
ρ
Dynamic viscosity A quantity characterizing the mechanical behaviour of a μ Pa s
fluid
2 –1
Kinematic viscosity Ratio of the dynamic viscosity to the density of the fluid. ν m s
Values are given as a function of temperature. (see
IEC 60193)
3 –1
Discharge Volume of water per unit time flowing through any section Q m s
in the system
–1
Mass flow rate Mass of water flowing through any section of the system kg s
(ρ Q)
per unit time
3 –1
Discharge of machine Discharge flowing through the high pressure reference Q m s
1
section
3 –1
Leakage flow rate Volume of water per unit time flowing through the runner q m s
seal clearances
3 –1
Net discharge Volume of water per unit time flowing through Q m s
m
runner/impeller. It corresponds to Q -q in case of turbine
1
and Q +q in case of pump.
1
–1
Mean velocity Discharge divided by the sectional area of water passage v m s
–1
Peripheral velocity Peripheral velocity at the reference diameter u m s
–1
Rotational speed Number of revolutions per unit time n S
–1
Specific hydraulic Specific energy of water available between the high and E J kg
energy of machine low pressure reference sections 1 and 2 of the machine


taking into account the influence of compressibility (see
IEC 60193)
–1
Specific hydraulic Turbine: Net specific hydraulic energy working on the E J kg
m
energy of runner

runner/impeller
Pump: Specific hydraulic energy produced by the impeller
–1
E J kg
m
–1
Specific hydraulic Specific hydraulic energy loss in stationary part which E J kg
Ls
energy loss in includes both friction loss and kinetic loss

stationary part

–1
Specific hydraulic Specific hydraulic energy loss in runner/impeller which E J kg
Lm
energy loss in includes both friction loss and kinetic loss

runner/impeller
–1
Friction loss of Specific hydraulic energy loss caused by the friction on the E J kg
Lf
specific hydraulic surface of water passages
energy

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