prEN 17038-3
(Main)Pumps - Methods of qualification of the Energy Efficiency Index for rotordynamic pump units - Part 3: Testing and calculation of energy efficiency index (EEI) of booster sets
Pumps - Methods of qualification of the Energy Efficiency Index for rotordynamic pump units - Part 3: Testing and calculation of energy efficiency index (EEI) of booster sets
This document specifies methods and procedures for testing, calculating and determining the energy efficiency index (EEI) of booster sets.
A booster set is either a single pump unit or an assembly of pump units connected in parallel with a maximum hydraulic power of 150 kW, a minimum rated flow of 6 m3/h (0,001667 m3/s), operated with backflow prevention and additional components influencing hydraulic performance and with components necessary to control pressure or provide flow in open loops inside buildings and which is placed on the market and/or put into service as one single product and its intended use is to pump clean water and does not have a self-priming functionality.
A booster set with a rated flow below 6 m3/h is composed using pumps that comply with EN 17038-2.
Pumpen - Methoden zur Qualifikation des Energieeffizienzindexes für Kreiselpumpen - Teil 3: Prüfung und Berechnung des Energieeffizienzindexes (EEI) von Druckerhöhungsanlagen
Dieses Dokument legt Methoden und Verfahren zur Prüfung, Berechnung und Bestimmung des Energieeffizienzindex (EEI) von Druckerhöhungsanlagen fest.
Eine Druckerhöhungsanlage ist entweder ein einzelnes Pumpenaggregat oder eine Baugruppe parallel geschalteter Pumpenaggregate mit einer maximalen hydraulischen Leistung von 150 kW, einem Mindestnennförderstrom von 6 m3/h (0,001 667 m3/s), die mit einem Rückflussverhinderer und zusätzlichen, die hydraulische Leistung beeinflussenden Bauteilen sowie mit Bauteilen, die zur Druckregelung oder zur Bereitstellung des Förderstroms in offenen Kreisläufen innerhalb von Gebäuden erforderlich sind, zu betreiben ist und die als ein einziges Produkt in Verkehr gebracht und/oder in Betrieb genommen wird und deren bestimmungsgemäße Verwendung die Förderung von sauberem Wasser ist und die keine selbstansaugende Funktion hat.
Eine Druckerhöhungsanlage mit einem Nenndurchfluss von weniger als 6 m3/h muss aus Pumpen bestehen, die EN 17038 2 entsprechen.
Pompes - Méthodes de qualification de l’indice de rendement énergétique des groupes motopompes rotodynamiques - Partie 3 : Essais et calcul de l’indice de rendement énergétique (EEI) des groupes de surpression
Le présent document spécifie les méthodes et procédures d’essai, de calcul et de détermination de l’indice de rendement énergétique (EEI) des groupes de surpression.
Un groupe de surpression se présente sous la forme soit d’un groupe motopompe individuel, soit d’un assemblage de groupes motopompes raccordés en parallèle avec une puissance hydraulique maximale de 150 kW et un débit nominal d’au moins 6 m³/h (0,001667 m³/s), destiné à être utilisé avec un disconnecteur hydraulique et des composants supplémentaires influençant les performances hydrauliques, ainsi qu’avec les composants nécessaires pour contrôler la pression ou assurer un écoulement dans les boucles ouvertes à l’intérieur de bâtiments, et qui est commercialisé et/ou mis en service en tant que produit individuel conçu pour le pompage d’eau propre et sans fonctionnalité d’auto-amorçage.
Un groupe de surpression avec un débit nominal de 6 m³/h comprend des pompes conformes à l'EN 17038-2.
Črpalke - Metode za opredelitev indeksa energijske učinkovitosti centrifugalnih črpalk - 3. del: Preskušanje in računanje indeksa energijske učinkovitosti (IEE) ojačevalnih agregatov
General Information
Standards Content (Sample)
SLOVENSKI STANDARD
01-februar-2025
Črpalke - Metode za opredelitev indeksa energijske učinkovitosti centrifugalnih
črpalk - 3. del: Preskušanje in računanje indeksa energijske učinkovitosti (IEE)
ojačevalnih agregatov
Pumps - Methods of qualification of the Energy Efficiency Index for rotordynamic pump
units - Part 3: Testing and calculation of energy efficiency index (EEI) of booster sets
Pumpen - Methoden zur Qualifikation des Energieeffizienzindexes für Kreiselpumpen -
Teil 3: Prüfung und Berechnung des Energieeffizienzindexes (EEI) von
Druckerhöhungsanlagen
Pompes - Méthodes de qualification de l’indice de rendement énergétique des groupes
motopompes rotodynamiques - Partie 3 : Essais et calcul de l’indice de rendement
énergétique (EEI) des groupes de surpression
Ta slovenski standard je istoveten z: prEN 17038-3
ICS:
23.080 Črpalke Pumps
2003-01.Slovenski inštitut za standardizacijo. Razmnoževanje celote ali delov tega standarda ni dovoljeno.
DRAFT
EUROPEAN STANDARD
NORME EUROPÉENNE
EUROPÄISCHE NORM
November 2024
ICS 23.080
English Version
Pumps - Methods of qualification of the Energy Efficiency
Index for rotordynamic pump units - Part 3: Testing and
calculation of energy efficiency index (EEI) of booster sets
Pompes - Méthodes de qualification de l'indice de Pumpen - Methoden zur Qualifikation des
rendement énergétique des groupes motopompes Energieeffizienzindexes für Kreiselpumpen - Teil 3:
rotodynamiques - Partie 3 : Essais et calcul de l'indice Prüfung und Berechnung des Energieeffizienzindexes
de rendement énergétique (EEI) des groupes de (EEI) von Druckerhöhungsanlagen
surpression
This draft European Standard is submitted to CEN members for enquiry. It has been drawn up by the Technical Committee
CEN/TC 197.
If this draft becomes a European Standard, CEN members are bound to comply with the CEN/CENELEC Internal Regulations
which stipulate the conditions for giving this European Standard the status of a national standard without any alteration.
This draft European Standard was established by CEN in three official versions (English, French, German). A version in any other
language made by translation under the responsibility of a CEN member into its own language and notified to the CEN-CENELEC
Management Centre has the same status as the official versions.
CEN members are the national standards bodies of Austria, Belgium, Bulgaria, Croatia, Cyprus, Czech Republic, Denmark, Estonia,
Finland, France, Germany, Greece, Hungary, Iceland, Ireland, Italy, Latvia, Lithuania, Luxembourg, Malta, Netherlands, Norway,
Poland, Portugal, Republic of North Macedonia, Romania, Serbia, Slovakia, Slovenia, Spain, Sweden, Switzerland, Türkiye and
United Kingdom.
Recipients of this draft are invited to submit, with their comments, notification of any relevant patent rights of which they are
aware and to provide supporting documentation.
Warning : This document is not a European Standard. It is distributed for review and comments. It is subject to change without
notice and shall not be referred to as a European Standard.
EUROPEAN COMMITTEE FOR STANDARDIZATION
COMITÉ EUROPÉEN DE NORMALISATION
EUROPÄISCHES KOMITEE FÜR NORMUNG
CEN-CENELEC Management Centre: Rue de la Science 23, B-1040 Brussels
© 2024 CEN All rights of exploitation in any form and by any means reserved Ref. No. prEN 17038-3:2024 E
worldwide for CEN national Members.
Contents Page
European foreword . 4
Introduction . 5
1 Scope . 6
2 Normative references . 6
3 Terms and definitions . 6
4 Symbols and abbreviations . 9
5 Reference pressure control curve and reference flow-time profile . 10
5.1 100 %-duty point . 10
5.2 Reference pressure control curve . 10
5.3 Reference flow-time profile . 11
6 Determination of average electric power input P by test . 12
1,avg
6.1 General. 12
6.2 Test bench setup . 12
6.3 Booster set . 16
6.4 100 %-duty point and control curve adjustment . 17
6.5 Duty point measurement . 25
6.6 Evaluation calculation . 29
7 Determination of average electric power input P1,avg by the means of a Semi-Analytical
Model (SAM) . 37
7.1 General. 37
7.2 General. 38
7.3 Pre-defined mode of operation and version of pressure and switching control . 38
7.4 The semi-analytical model of pumps . 40
7.5 The semi-analytical model of electric motors or of power drive systems (PDSs) . 41
7.6 Modelling internal piping and valve losses . 41
7.7 Auxiliary electrical losses . 42
7.8 Calculation of Q and H . 42
100 % 100 %
7.9 Calculation of P1 dependent on Q/Q . 43
100 %
7.10 Calculation of P . 49
1,avg
8 Determination of reference electric power input P . 50
1,ref
8.1 Definition . 50
8.2 Reference pump hydraulic power . 50
8.3 Reference pump efficiency . 51
8.4 Reference pump shaft power . 51
8.5 Reference motor efficiency . 51
8.6 Reference electric power input . 52
9 Calculation of Energy Efficiency Index (EEI) . 52
Annex A (informative) Configurations and modes of operation and control . 54
A.1 Configurations and modes of operation: . 54
A.2 Control versions . 55
Annex B (informative) Effect of operation mode and type of pressure control on EEI . 57
Annex C (informative) Effect of control deviations on EEI . 59
Annex D (informative) Uncertainties and tolerances of EEI . 61
D.1 General . 61
D.2 The measurement uncertainty of EEI-values determined by test . 61
D.3 The model uncertainty of EEI-values determined by the means of the SAM . 64
D.4 The total tolerance of EEI-values determined by tests . 67
D.5 The total tolerance of EEI-values determined by the means of the SAM . 67
Bibliography . 68
European foreword
This document (prEN 17038-3:2024) has been prepared by Technical Committee CEN/TC 197 “Pumps”,
the secretariat of which is held by AFNOR.
This document is currently submitted to the CEN Enquiry.
Introduction
This document is the third part of a series of standards describing a methodology to evaluate energy
efficiency performance of booster sets, comprising one or more pump(s), the motor(s) with or without
frequency converter, and additional components influencing hydraulic performance. It is based on a non-
dimensional numerical value called energy efficiency index (EEI). An EEI allows the comparison of
different configurations with one common indicator. Physical influences such as number and size of the
incorporated pump(s), pump unit part-load operation, motor-efficiency characteristic and frequency
converter influence are implemented into this metric.
Specific requirements for testing and a calculation method for EEI, the so called semi-analytical model
(SAM) of a complete booster set, a specific flow-time profile and a reference control curve are given in
this part of the series of standard.
EEI is an index to rate booster sets according to their energy efficiency but does not replace the need to
do a life-time cost analysis regarding energy consumption over the lifetime of the booster set.
1 Scope
This document specifies methods and procedures for testing, calculating and determining the energy
efficiency index (EEI) of booster sets.
A booster set is either a single pump unit or an assembly of pump units connected in parallel with a
3 3
maximum hydraulic power of 150 kW, a minimum rated flow of 6 m /h (0,001667 m /s), operated with
backflow prevention and additional components influencing hydraulic performance and with
components necessary to control pressure or provide flow in open loops inside buildings and which is
placed on the market and/or put into service as one single product and its intended use is to pump clean
water and does not have a self-priming functionality.
A booster set with a rated flow below 6 m /h is composed using pumps that comply with EN 17038-2.
2 Normative references
The following documents are referred to in the text in such a way that some or all of their content
constitutes requirements 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.
EN ISO 17769-1, Liquid pumps and installation - General terms, definitions, quantities, letter symbols and
units - Part 1: Liquid pumps (ISO 17769-1)
EN ISO 17769-2, Liquid pumps and installation - General terms, definitions, quantities, letter symbols and
units - Part 2: Pumping System (ISO 17769-2)
EN 60034-1, Rotating electrical machines - Part 1: Rating and performance (IEC 60034-1)
EN IEC 60034-2-1, Rotating electrical machines - Part 2-1: Standard methods for determining losses and
efficiency from tests (excluding machines for traction vehicles)(IEC 60034-2-1)
EN 60038:2011, CENELEC standard voltages (IEC 60038 :2009)
EN IEC 61800-2, Adjustable speed electrical power drive systems — Part 2: General requirements — Rating
specifications for low voltage adjustable speed a.c. power drive systems (IEC 61800-2)
EN 61800-9-2, Adjustable speed electrical power drive systems - Part 9-2: Ecodesign for power drive
systems, motor starters, power electronics and their driven applications - Energy efficiency indicators for
power drive systems and motor starters (EN 61800-9-2)
3 Terms and definitions
For the purposes of this document, the terms and definitions given in EN ISO 17769-1, EN ISO 17769-2
and the following apply.
ISO and IEC maintain terminology databases for use in standardization at the following addresses:
— ISO Online browsing platform: available at https://www.iso.org/obp/
— IEC Electropedia: available at https://www.electropedia.org/
3.1
booster set
single pump unit or assembly of pump units connected in parallel with a maximum hydraulic power of
3 3
150 kW, a minimum rated flow of 6 m /h (0,001 667 m /s), operated with backflow prevention and
additional components influencing hydraulic performance and with components necessary to control
pressure or provide flow in open loops inside buildings and which is placed on the market and/or put
into service as one single product and its intended use is to pump clean water and does not have a self-
priming functionality
Note 1 to entry: “clean water” means water with a maximum non-absorbent free solid content of 0,25 kg/m , and
with a maximum dissolved solid content of 50 kg/m , provided that the total gas content of the water does not
exceed the saturation volume. Any additives that are needed to avoid water freezing down to – 10° C shall not be
considered. (Source: Commission Regulation EU No. 547/2012).
3.2
expansion tank
tank partially filled with air, whose compressibility cushions pressure deviations under balancing small
water volumes between the tank and the connected system
3.3
fixed speed pump
pump unit without an electronic power converter (e.g. frequency converter)
3.4
variable speed pump
pump unit equipped with an electronic power converter (e.g. frequency converter)
3.5
stand-by pump
pump unit which intentionally increases the number of pumps in booster set (3.1) compared to the
installation demand for redundancy reasons
3.6
jockey pump
pump unit sized for considerably less flow than other pumps of the booster set (3.1) and intended only to
handle leakage flows and/or small flows during cut-in of another pump
3.7
suction pressure
pressure at the inlet of a booster set (3.1)
Note 1 to entry: pressures are gauge pressures (relative to the atmospheric pressure).
3.8
discharge pressure
pressure at the outlet of a booster set (3.1)
Note 1 to entry: pressures are gauge pressures (relative to the atmospheric pressure).
3.9
total differential head
the height at which the water is raised vertically by the booster set (3.1)
3.10
hydraulic power
power of the pumped water transferred by a pump, defined mainly by flow rate and total differential head
(3.9)
3.11
nominal booster set flow rate
design operation flow rate of the booster set (3.1), typically defined by nominal booster set speed (3.12)
and high booster set efficiency, e.g. the best efficiency point of the booster set (resp. the best efficiency
point of one pump multiplied by the pump number)
3.12
nominal booster set speed
maximum speed that the booster set (3.1) is designed to run continuously
3.13
best efficiency point
BEP
pump or booster set (3.1) duty point with highest total efficiency “wire to water”
3.14
100% duty point
duty point of maximum value of the hydraulic power (3.10) at nominal booster set speed (3.12)
Note 1 to entry: It is to be expected more or less close to the nominal booster set duty point.
3.15
control curve
adjusted discharge pressure (3.8) dependent on flow rate of a booster set (3.1)
Note 1 to entry: See also A.2.1
3.16
reference control curve
representative pressure control curve defined relatively by the 100%-duty point (3.14)
3.17
reference total differential head
total differential head (3.9) defined by the reference control curve (3.16) and the reference flow rate (3.18)
3.18
reference flow rate
flow rate defined by the 100%-duty point (3.14) and the flow-time profile (3.19)
3.19
flow-time profile
relation between defined flow rate intervals and relative operation time
3.20
Complete Drive Module
CDM
electronic power converter connected between the electric supply and a motor as well as extensions such
as protection devices, transformers and auxiliaries
Note 1 to Entry: Complete Drive Module shall be according to EN IEC 61800-2.
3.21
Power Drive System
PDS
combination of a CDM (3.20) and an electric motor
4 Symbols and abbreviations
The symbols and units given in Table 1 and the indices given in Table 2 apply.
Table 1 — Symbols and units
Symbol Designation Unit
e Uncertainty - (dimensionless)
EEI Energy efficiency index -
η
Motor efficiency -
m
η
Pump efficiency -
pump
g Gravitational acceleration
m/s
H Total differential head m
H
Total differential head loss at 100 %-duty point m
100 %,loss
i Duty point -
m Sample number -
k Pressure ratio -
P
Electric power input kW
P
Average electric power input kW
1,avg
P
Reference electric power input kW
1,ref
P
Discharge-pressure-corrected electric power input kW
1,pd-corr
P
Suction-pressure-corrected electric power input kW
1,ps-corr
P
Flow-rate-corrected electric power input kW
1,Q-corr
P
kW
Reference pump shaft power
2,ref
P
Hydraulic power kW
hyd
p
Discharge pressure Pa
d
p
Suction pressure Pa
s
Symbol Designation Unit
Q Flow rate m /h
z Number of relevant booster set pumps -
Δt / t
Time ratio -
tot
ρ Water density kg/m
Table 2 — Indices
Indices Designation
0 % at zero flow rate
10 % at 10 %-duty point
… …
100 % at 100 %-duty point
adj adjusted
BEP Best efficiency point
calc calculated
dec decreasing flow measurement
exp expected
i at duty point i
i+10 % at duty point i+10 %
inc increasing flow measurement
meas measured
rate rated
ref reference
5 Reference pressure control curve and reference flow-time profile
5.1 100 %-duty point
The 100 %-duty point is defined as duty point of maximum hydraulic power at nominal booster set speed,
see 3.11.
The flow rate at 100 %-duty point Q is defined as flow rate of that duty point.
100 %
The total differential head at 100 %-duty point H is defined as total differential head of the that same
100 %
duty point.
For details of determination see Clause 6.
5.2 Reference pressure control curve
The reference control curve for booster sets is defined by Formula (1):
Q
H H ⋅ 0.75+⋅0 25 (1)
ref 100%
Q
100%
where
H is the reference total differential head in m;
ref
H is the total differential head at 100 %-duty point in m;
100 %
Q is the flow rate in m /h;
is the flow rate at 100 %-duty point in m /h.
Q
100 %
See Figure 1 for illustration of an Q-H-curve field of an example booster set with three pumps.
Key
100 % 100 %-duty point
p reference discharge pressure in Pa
d,ref
Figure 1 — Reference pressure control curve
5.3 Reference flow-time profile
The reference flow-time profile for booster sets is defined in Table 3.
Table 3 — Reference flow-time profile for booster sets
Duty point i 10 % 20 % 30 % 40 % 50 % 60 % 70 % 80 % 90 % 100 %
Q /
10 30 40 80 90
Flow ratio 20 % 50 % 60 % 70 % 100 %
Q
% % % % %
100 %
Δt / t 19
tot
Time ratio 6 % 21 % 26 % 12 % 6 % 4 % 3 % 2 % 1 %
%
See Figure 2 for a diagram.
=
Key
Δt / t time ratio
tot
Q / Q
flow ratio
100 %
Figure 2 — Flow-time profile
NOTE Annex A and Annex C describe the different control methods for booster sets. Sets with only fixed speed
pumps will follow a curve of higher pressure based on the Q-H-curve of the pumps and the constant (minimum)
pressure setting of the control. Sets which can follow the reference pressure control curve will show a better energy
efficiency index EEI. Sets with fixed speed pumps programmed to follow the reference pressure control (as best
they can) will have a better energy efficiency index EEI than if programmed for constant pressure.
6 Determination of average electric power input P by test
1,avg
6.1 General
This clause specifies performance tests and evaluations on booster sets which are carried out by a
company which places the booster set on the market and/or puts it into service; Such tests shall provide
the necessary information on the actual performance values of test booster sets needed for the calculation
of the EEI-value according to its definition given in EN 17038-1:2019 , Clause 4.
6.2 Test bench setup
6.2.1 General
All provisions for the test concerning the booster set (taken as “black box” and treated as a pump unit
such as described in EN 17038-2) shall be in accordance with EN ISO 9906, grade 2. The exception for
power of 10 kW and below (as allowed for the application of EN ISO 9906 on acceptance tests) shall not
be valid.
As impacted by EN 17038-1:2019/AC:2021.
All provisions for the test concerning electric motors if they are part of the booster set and are fed directly
from an electric grid shall be in accordance with EN IEC 60034-2-1.
All provisions for the test concerning a Power Drive System if is part of the booster set shall be in
accordance with EN 61800-9-2.
6.2.2 Test conditions
Tests shall be carried out with clean cold water, that means
–6 2
— a maximum kinematic viscosity of 1,5 × 10 m /s;
— a maximum density of 1 050 kg/m ; and
— a maximum temperature of 40° C.
The duration of the test shall be sufficient to obtain repeatable results; especially run-in and
warming-up effects of the electric and electronic components of the unit shall be considered.
Run-in effects can take up to one day operating time.
The electric power supply of the test installation shall fulfill the requirements as specified in EN 60034-1.
This requires that:
— the voltage shall be in accordance with EN 60038:2011, 7.2 and EN 60034-1,
— the frequency shall be within ± 0,3 % of the rated frequency during measurements.
6.2.3 Description
It is necessary to use an open loop test bench design, either with supply tank as illustrated in Figure 1, or
with sufficient fresh water supply.
Key
P electric power input
p discharge pressure
d
p suction pressure
s
Q flow rate
Figure 3 — Test bench design
The pressure sensors at suction and discharge side shall be as close as possible to the booster set, but
negative flow impact e.g. by swirls shall be avoided.
As the pressure difference is evaluated, both pressure measuring instruments shall be at the same
geodetic height, especially with booster set manifolds at different geodetic heights. If necessary, value-
offsetting is allowed to equalize both pressure sensor values in unpressurized state.
The flow measurement inlet and outlet distances shall be kept. Preferred positioning is on booster set
suction side.
The test bench water temperature shall ideally be kept constant by adding new water or cooling.
The suction pressure should ideally be atmospheric pressure 1. Further the suction pressure should be
ideally independent of the flow. Choose a test bench design with low piping losses on suction side (short
pipe lengths and big pipe diameter). If necessary, position the flow measurement at booster set discharge
side.
NOTE Booster sets are operated in open loop systems with geodetic head. In the case of large geodetic height
not all operating points are accessible for fixed speed pumps due to the switching of the pumps. To keep the gaps in
the accessible flow as small as possible, a hydraulic loop without geodetic head is used for the determination of EEI.
Then, the resistance curves which determine the operating points of the booster set are purely parabolic (without
geodetic part).
In practical booster set operation in a test bench there is typically a certain suction pressure. Further the
suction pressure is impacted by hydraulic losses of the test bench, resulting in higher suction pressure
values at part load. As the reference pressure control curve remains fixed, deviating suction pressure
leads to deviating delivery head, see Figure 4.
Figure 4 — Suction pressure deviation
To be independent of test bench behaviour, the suction pressure at 100 %-duty point p is
s,100 %
determined and considered as constant for later calculation, see 6.4.6.
Deviating suction pressure from this suction pressure at 100 %-duty point p is corrected by
s,100 %
electrical power scaling, see chapter 6.6.2. The booster set efficiency is assumed to be constant.
However, the booster set efficiency is assumed to be constant for scaling, any suction pressure variation
from the 100 %-suction pressure at 100 %-duty point p shall not exceed 20 % of the total
s,100 %
differential head of the booster set H , see Formula (2).
100 %
p − p ≤ 02. ⋅ρ ⋅gH ⋅ (2)
s,%100 s,meas 100%
where
p is the suction pressure at 100 %-duty point in Pa;
s,100 %
p is the measured suction pressure in Pa;
s,meas
ρ
is the water density at 20° C temperature, 998,2 kg/m ;
g is the gravitational acceleration, 9,81 m/s;
is the total differential head at 100 %-duty point in m ;
H
100 %
6.2.4 Measuring instrumentation
Measuring instrumentation is needed for the determination of:
— the flow rate Q;
— the suction pressure p ;
s
— the discharge pressure p ;
d
— the electric power input P .
The measuring equipment needed to determine the flow rate Q, the suction pressure p and the discharge
s
pressure p shall be selected in accordance with EN ISO 9906:2012.
d
Detailed information is given in Annex A.1 of EN ISO 9906:2012.
Since instrument accuracy is generally expressed as a percentage of full scale, the range of the
instruments chosen shall be as small as practical.
The electric power input P of the booster set is determined based on input voltages U and input
currents I. All requirements concerning the instrumentation for the measurements of electric power
input P shall be fulfilled according to EN IEC 60034-2-1.
6.2.5 Uncertainties of measured quantities
The total measurement uncertainties of:
— the flow rate Q;
— the suction pressure p ;
s
— the discharge pressure p ;
d
— the electric power input P .
result from the combined effects of the measurement device uncertainty and of the random uncertainty
and can be determined as described in EN 17038-1:2019, Annex D.
NOTE For tests done by a company which is responsible for the qualification of booster sets (see
EN 17038-1:2019, Clause 5) it is advisable to achieve total measurement uncertainties to be as small as possible, i.e.
smaller than the maximum permissible values specified by standards.
6.2.6 Measurement rates and bandwidth of measurement equipment
All measurement devices shall have a time constant (T ) in the range between 0,1 – 0,6 s.
63 %
6.2.7 Steady-state
All measurements shall be made under hydraulic and thermal steady-state conditions, see
— EN ISO 9906;
— EN IEC 60034-2-1;
— EN 60034-2-2;
— EN IEC 60034-2-3; and
— EN 61800-9-2.
NOTE EN 61800-9-2 requests thermal stability for the PDS for measuring the maximum duty point. All other
points can be measured quickly after measuring maximum load without waiting for the thermal stability.
6.2.8 Documentation
All measured and calculated values shall be documented.
6.3 Booster set
6.3.1 Expansion tank
If an expansion tank is integrated in the booster set, it shall be deactivated except in case the volume of
the tank is below ten litres plus one litre per every m /h of the flow rate at 100 %-duty point Q . As
100 %
this 100 %-duty point Q is not yet determined at this time, the nominal booster set flow as defined
100 %
in 3.11 may be used as representative.
See the example cases in Table 4.
Table 4 — Expansion tank size example cases
Flow rate at 100 %- Integrated expansion tank Action for
duty point Q measurements
100 %
Allowed maximum volume Installed volume
8 m /h 18 l (10 + 8) 12 l Activation
13 m /h 23 l (10 + 13) 25 l Deactivation
NOTE An expansion tank of the maximum allowed volume defined above could be necessary during tests in
respect to the time-transient behaviour of the pressure control of variable speed booster sets.
6.3.2 Stand-by pump
If a stand-by pump as defined in chapter 3.5 is integrated in the booster set, it shall be taken as one of the
total numbers of normal operating pumps for the determination of energy efficiency index EEI.
6.3.3 Jockey pump
If in the booster set a jockey pump as defined in 3.6 is installed it shall be deactivated and isolated for test
purposes.
6.3.4 Run in
Run-in effects may affect the power consumption of a booster set during its initial operation.
To ensure a representative electric power input a run in of the booster is necessary.
Run in effects can take up to one day operating time.
It is possible to run in the booster set with all pumps running at maximum speed and at different flows.
6.3.5 Controller dynamic
Booster sets to be operated inside buildings typically have default control settings according to building
characteristics. The test bench shall represent the building installation but of course differs in terms of
water volume and installation dynamic. This deviation may lead to unwanted dynamic control effects.
The booster set controller dynamic like PID-parameters may be adjusted according to the particular test
bench to prevent these unwanted dynamic control effects. The adjustment has to be the same for all
measured duty points.
NOTE PID refers to the Proportional – Integral – Derivative gains of the pressure control loop.
6.3.6 Documentation
All booster set adjustments like deactivated expansion tank, jockey pump deactivation, control curve
adjustment and controller dynamic shall be documented.
6.4 100 %-duty point and control curve adjustment
6.4.1 Overview
The reference pressure control curve as described in chapter 5.1 is defined as straight line between two
duty points as shown in Figure 5
— The 100 %-duty point as duty point of maximum hydraulic power (Q = Q , H = H ).
100 % 100 %
This duty point shall be determined by test in advance. It goes along with the booster set operated with
1 2
all relevant booster pumps at nominal booster set speed ;
— The zero flow rate duty point with reduced delivery head (Q = 0 ; H = 0,75 H ).
100 %
For EEI-determination, this duty point is not evaluated. But if the booster set is able to operate in variable
pressure control as described in A.2.1, it needs to be determined for correct control curve
adjustment.
Key
100 % 100 %-duty point
0 % zero flow rate
Q flow rate
H total differential head
p reference discharge pressure in Pa
d,ref
Figure 5 — Reference pressure control curve
The main steps of determination and adjustment are:
— Measure several duty points around an expected 100 %-duty point at maximum speed.
— Calculate the hydraulic power and find the maximum by approximating a polynom function.
— Determine the flow rate, the discharge pressure and the suction pressure at 100 %-duty point.
— Adjust the booster set control curve according to the calculated values.
NOTE 1 See handling of standby-pumps in 6.3.2 and handling of jockey pumps in 6.3.3.
NOTE 2 See definition in 3.12.
6.4.2 Determination of duty points to measure
To determine the flow rate of 100 %-duty point Q by measurement, duty points around an expected
100 %
flow rate of 100 %-duty point Q are measured and the hydraulic power evaluated.
100 %,exp
The flow rate of the 100 %-duty point Q can be expected close to the booster set nominal duty point
100 %
flow rate given by booster set designation, documentation or nameplate. Alternatively the booster set
nominal flow rate can also be estimated by the product of pump number and nominal pump flow rate
given by the pump designation, documentation or nameplate.
It is important to take measurement data in a sufficiently large flow rate range around the expected value
of Q .
100 %,exp
Recommended are seven measurement points in the range 0,7 ⋅ Q ≤ Q ≤ 1,3 ⋅ Q .
100 %,exp 100 %,exp
6.4.3 Value measurement
Operate the booster set with all relevant pumps at nominal booster set speed, see 3.12. Usually this is
achieved by adjusting the booster set pressure to a high value.
Measure ten samples of these three values per duty point in a period of five seconds up to 30 seconds.
For every sample of every duty point measure the values
— flow rate Q ;
meas
— suction pressure p ; and
s,meas
— discharge pressure p .
d,meas
The measurement of electric power input P is not needed to determine the 100 %-duty point.
Consider the conditions for steady state and thermal stability as described in 6.2.7.
6.4.4 Calculated flow rate
Determine the calculated flow rate at 100 %-duty point Q by the following steps:
100 %,calc
a) Calculate duty points hydraulic power
— For every sample value calculate the measured total differential head H by Formula (3).
meas
pp –
d,,meas s meas
H = (3)
meas
ρ ⋅ g
where
H is the measured total differential head in m;
meas
p is the measured discharge pressure in Pa;
d,meas
p is the measured suction pressure in Pa;
s,meas
ρ
is the water density at 20° C temperature, 998,2 kg/m ;
g
is the gravitational acceleration, 9,81 m/s
NOTE 1 The differences of dynamic head v /(2 ⋅ g) between inlet and outlet of the booster set are typically zero
or very small compared to the pressure head and are neglected.
For every duty point i use the average value of the ten samples as representing value for
— the measured flow rate Q and
meas
— the measured total differential head H
meas.
For every duty point i calculate the hydraulic power P by Formula (4).
hyd
1 1
P ⋅ ⋅ρ ⋅⋅ gQ ⋅ H (4)
hyd meas meas
3600 1000
where
P is the hydraulic power in kW
hyd
ρ
is the water density at 20° C temperature, 998,2 kg/m
g
is the gravitational acceleration, 9,81 m/s
Q is the measured flow rate in m /h
meas
H is the measured total differential head in m
meas
3 3
NOTE 2 The factor 1/3600 converts the unit m /h into required m /s, the factor 1/1000 converts the unit W into
required kW.
b) Create polynomial
Create a polynomial function of third degree on the value pairs of Q and P , see Formula (5).
meas hyd
3 2
P =A⋅+Q B⋅+Q C⋅ Q +D (5)
hyd P meas P meas P meas P
where
P is the hydraulic power in kW
hyd
A , B , C , D are the polynom parameters, dimensionless
P P P P
Q is the measured flow rate in m /h
meas
Determine the parameters A , B , C and D by least square method.
P P P P
c) Determine flow rate
Determine the calculated flow-rate at 100 %-duty point Q by Formula (6).
100 %,calc
B B C
11 1
P PP
Q = − ⋅ ± ⋅ − ⋅ (6)
100%,calc
3 A 9 AA3
P PP
where
Q is the calculated flow-rate at 100 %-duty point in m /h
100 %,calc
A , B , C , D are the polynom parameters, dimensionless
P P P P
Q is the measured flow rate in m /h
meas
The double sign ± of the square root may lead to more than one solution candidates. Select the one
defining the real maximum, e.g. as value closer to the expected flow rate at 100 %-duty point Q .
100 %,exp
3 1
Round the result down by using only one decimal, e.g. 8.5 m /h .
=
d) Additional duty points
If the determined value of the calculated flow-rate at 100 %-duty point Q shows that only one or
100 %,calc
no measured duty point is at greater flow rate, additional duty points shall be measured and the
calculation updated to obtain at least two measured duty points at greater flow.
Use this calculated flow rate at 100 %-duty point Q as Q for further calculation and the
100 %,calc 100 %
determination of the reference electric power input P .
1,ref
NOTE 3 See the note in 6.4.5.
6.4.5 Calculated discharge pressure
Determine the calculated discharge pressure at 100 %-duty point p by the following steps:
d,100 %,calc
a) Representing average
For every duty point i use the average value of the ten samples as representing value for
— the measured flow rate Q (as already described in 6.4.4)
meas
— the measured discharge pressure p
d,meas.
b) Create polynomial
Create a polynomial function of third degree on the value pairs of Q and p , see Formula (7):
meas d,meas
3 2
p =A⋅+Q B⋅+Q C⋅+Q D (7)
d,meas pd meas pd meas pd meas pd
where
p is the measured discharge pressure in Pa
d,meas
A , B , C , D are the polynom parameters, dimensionless
pd pd pd pd
Q is the measured flow rate in m /h
meas
Determine the parameters A , B , C and D by least square method.
pd pd pd pd
c) Determine discharge pressure
Determine the calculated discharge pressure at 100 %-duty point p by inserting the calculated
d,100 %,calc
flow-rate at 100 %-duty point Q into Formula (8).
100 %,calc
Round the result down by setting the four lowest digits to zero, e.g. 410 000 Pa.
NOTE A senseful practical pressure adjustment accuracy of booster sets is 10 000 Pa. The calculated discharge
pressure at 100 %-duty point p is rounded accordingly to allow exact control curve adjustment: Later
d,100 %,calc
discharge pressure correction (penalty) considers any deviation between reference and measured discharge
pressure, see chapter 6.5.3. So control curve misadjustment would lead to arbitrary penalty depending on the
calculated value, impacted by the particular test bench and suction pressure behaviour. The same reason applies
for the calculated flow-rate at 100 %-duty point Q and senseful practical flow-rate adjustment of typically
100 %,calc
0,1 m /h for variable pressure control curves as described in A.2.1. Rounding down both values ensures to cover
the 100 %-duty point with the booster curve field.
6.4.6 Suction pressure at 100 %-duty point
Determine the calculated suction pressure at 100 %-duty point p by the following steps:
s,100 %,calc
a) Representing average
For every duty point i use the average value of the ten samples as representing value for
— the measured flow rate Q ;(as already described in 6.4.4);
meas
— the measured suction pressure p
s,meas.
b) Create polynomial
Create a polynomial function of third degree on the value pairs of Q and p , see Formula (8).
meas s,meas
p =A⋅+Q B⋅+Q C⋅+Q D (8)
s,meas ps meas ps meas ps meas ps
where
p is the measured discharge pressure in Pa;
d,meas
A , B , C , D are the polynom parameters, dimensionless;
pd pd pd pd
Q is the measured flow rate in m /h.
meas
Determine the parameters A , B , C and D by least square method.
ps ps ps ps
c) Determine suction pressure
Determine the suction pressure at 100 %-duty point p by inserting the calculated flow-rate at
s,100 %
100 %-duty point Q into Formula (9).
100 %,calc
6.4.7 Calculated discharge pressure at zero flow rate
If the booster set is able to operate in variable pressure control as described in A.2.1, determine the
calculated discharge pressure at zero flow rate p by the following steps:
d,0 %,calc
a) Calculated value
Determine the calculated discharge pressure at zero flow rate p by Formula (9).
d,0 %,calc
p p +⋅ 0.75 p − p (9)
( )
d,0%,calc s,%100 d,%100 ,calc s,%100
=
b) Adapted value
There are typically two ways to parameterize the discharge pressure at zero flow rate, as pressure value
or pressure ratio to the discharge pressure at 100 %-duty point. Adapt the value accordingly:
Case adjustment as pressure value
Round the calculated value to 10 000 Pa, e.g. 320 000 Pa.
Case adjustment as pressure ratio
1) Calculate the pressure ratio k by Formula (10) and round it to full percent, e.g. 76 %.
calc
p
d,,0% calc
k = (10)
calc
p
d,,100% calc
2) Recalculate the discharge pressure at zero flow rate p by Formula (11).
d,0 %,calc
p kp⋅ (11)
d,0%,calc calc d,100%,calc
where
p is the calculated discharge pressure at zero flow rate in Pa;
d,0 %,calc
p is the suction pressure at 100 %-duty point in Pa;
s,100 %
p is the calculated discharge pressure at 100 %-duty point in Pa;
d,100 %,calc
is the calculated pressure ratio.
k
calc
NOTE 1 Senseful practical pressure adjustment accuracy at zero flow rate is 10 000 Pa resp. 1 % of the discharge
pressure at 100 %-flow rate. The calculated discharge pressure at 100 %-duty point p is rounded
d,100 %,calc
accordingly to allow
...
Questions, Comments and Discussion
Ask us and Technical Secretary will try to provide an answer. You can facilitate discussion about the standard in here.
Loading comments...