ANSI/HI 9.6.7-2010 •·
`
`American National Standard
`(Guideline) for
`
`Effects of Liquid
`Viscosity on
`Rotodynamic
`(Centrifugal and
`Vertical) Pump
`Performance
`
`O Hydr._qy/ic
`
`6 Campus Drive
`First Floor North
`Parsippany, New Jersey
`07054-4406
`www.Pumps.org
`
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`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
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`Exhibit 1041
`Bazooka v. Nuhn - IPR2024-00098
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`

`ANSI/HI 9.6.7-2010
`
`American National Standard (Guideline) for
`Effects of Liquid Viscosity on
`Rotodynamic (Centrifugal and Vertical)
`Pump Performance
`
`Sponsor
`Hydraulic Institute
`www.Pumps.org
`
`Approved Dec. 23, 2010
`American National Standards Institute, Inc.
`
`( - , · Recycled
`paper
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
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`

`American
`National
`Standard
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`Approval of an American National Standard requires verification by ANSI that the
`requirements for due process, consensus, and other criteria for approval have been met
`by the standards developer.
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`Consensus is established when, in the judgement of the ANSI Board of Standards
`Review, substantial agreement has been reached by directly and materially affected
`interests. Substantial agreement means much more than a simple majority, but not nec(cid:173)
`essarily unanimity. Consensus requires that all views and objections be considered,
`and that a concerted effort be made toward their resolution.
`The use of American National Standards is completely voluntary; their existence does
`not in any respect preclude anyone, whether he has approved the standards or not,
`from manufacturing, marketing, purchasing, or using products, processes, or proce(cid:173)
`dures not conforming to the standards.
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`The American National Standards Institute does not develop standards and will in no
`circumstances give an interpretation of any American National Standard. Moreover, no
`person shall have the right or authority to issue an interpretation of an American
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`for interpretations should be addressed to the secretariat or sponsor whose name
`appears on the title page of this standard.
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`CAUTION NOTICE: This American National Standard may be revised or withdrawn at
`any time. The procedures of the American National Standards Institute require that
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`American National Standards may receive current information on all standards by call(cid:173)
`ing or writing the American National Standards Institute.
`
`Published By
`
`Hydraulic Institute
`6 Campus Drive, First Floor North
`Parsippany, NJ 07054-4406
`www.Pumps.org
`
`Copyright© 2010 Hydraulic Institute
`All rights reserved.
`
`No part of this publication may be reproduced in any form,
`in an electronic retrieval system or otherwise, without prior
`written permission of the publisher.
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`Printed in the United States of America
`
`ISBN 978-1-935762-04-1
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
`
`Exhibit 1041
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`

`

`Contents
`
`Page
`
`9.6.7.1
`
`9.6.7.2
`
`9.6.7.3
`9.6.7.3.1
`9.6.7.3.2
`
`9.6.7.4
`9.6.7.4.1
`9.6.7.4.2
`9.6.7.4.3
`9.6.7.4.4
`9.6.7.4.5
`
`9.6.7.4.6
`
`9.6.7.5
`9.6.7.5.1
`9.6.7.5.2
`9.6.7.5.3
`
`9.6.7.6
`9.6.7.6.1
`9.6.7.6.2
`9.6.7.6.3
`9.6.7.6.4
`9.6.7.6.5
`
`9.6.7.7
`
`9.6.7.8
`
`Foreword .......................................................... . ...................... v
`9.6.7
`Effects of liquid viscosity on pump performance . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1
`Summary .......................................................... .. ......... . 1
`Introduction .................................................................... 1
`Fundamental considerations . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 2
`Viscous correction factors . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 2
`Methods for determining correction factors . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 2
`Synopsis of Hydraulic Institute method . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 3
`Generalized method based on empirical data . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 3
`Viscous liquid performance correction limitations . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 4
`Viscous liquid symbols and definitions used for determining correction factors . . . . . . . . . . . . . . 4
`Overview of procedure to estimate effects of viscosity on pump performance . . . . . . . . . . . . . . . 5
`Instructions for determining pump performance on a viscous liquid when performance
`on water is known . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 8
`Instructions for preliminary selection of a pump for given head, rate of flow,
`and viscosity conditions . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 15
`Further theoretical explanations . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 18
`Scope ................... ... ......... .. .............................. .. ... .. 18
`Power balance and losses . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 18
`Method for estimating net positive suction head required (NPSH3) ..... ... ........ .. .... 21
`Additional considerations . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 25
`Limitations . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 25
`Pump design effects ........................................................... 25
`Mechanical considerations ......... . ............................................ 26
`Sealing issues . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 26
`Sealless pumps . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 26
`Bibliography ...... .... . ............................ .. ......... .. ... . ..... .... .. 26
`Notation . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 28
`Appendix A: Conversion of Kinematic Viscosity Units ............................................. 31
`Appendix B:
`
`Index . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 33
`
`Figures
`9.6.7.3.1 - Modification of pump characteristics when pumping viscous liquids .......................... 3
`9.6.7.4.4a - Flowchart to establish if the procedure is applicable ................................... . . 5
`9.6.7.4.4b - Flowchart to determine pump performance on a viscous liquid when performance
`on water is known . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6
`9.6.7.4.4c - Flowchart to select a pump for given head, rate of flow, and viscous conditions ................ 7
`9.6.7.4.5a - Chart of correction factors for c0 and CH ............................................. 9
`9.6.7.4.5b - Chart of correction factors for CTJ ................. . ..... . ..................... . ..... 10
`9.6.7.4.5c - Example performance chart of a single-stage pump (metric units) ... .... .. . ........... .. .. 12
`9.6.7.4.5d - Example performance chart of a single-stage pump (US customary units) . .. ..... . .... .. .... 15
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
`
`iii
`
`Exhibit 1041
`Bazooka v. Nuhn - IPR2024-00098
`Page 5 of 44
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`

`

`9.6.7.5.2a - Ratio of disk friction losses to useful power (references 7 and 8 in Bibliography) ....... . .... . . 20
`9.6.7.5.2b -
`Influence of disk friction losses on viscosity correction factor for efficiency
`(references 7 and 8 in Bibliography) . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 20
`9.6.7.5.3a - Example NPSH3 chart (metric units) . ........... .. . .. . . ... . . . ....... . .. . . . .... . ... .. 23
`9.6.7.5.3b - Example NPSH3 chart (US customary units) . . ... . ... . .. . ..... . ... ... ................. 24
`
`Tables
`9.6.7.4.5a - Example calculations (metric units) ....... . ... . ..................................... 12
`9.6.7.4.5b - Example calculations (US customary units) ............. .. .... . ........... .. .......... 14
`9.6.7.5.3a - Example calculations (metric units) . . .. .. . .. ... . ...... .. ... .. . . . . ........ . . . .. .. .... 23
`9.6.7.5.3b - Example calculations (US customary units) . . ... . ............. . ... . ... .. ... .. ... . ... . . 24
`
`iv
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`
`Exhibit 1041
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`
`

`

`Foreword (Not part of Standard)
`
`Purpose and aims of the Hydraulic Institute
`The purpose and aims of the Institute are to promote the continued growth and well-being of pump users and pump
`manufacturers and further the interests of the public in such matters as are involved in manufacturing, engineering,
`distribution, safety, transportation, and other problems of the industry, and to this end, among other things:
`a) To develop and publish standards for pumps;
`b) To collect and disseminate information of value to its members and to the public;
`c) To appear for its members before governmental departments and agencies and other bodies in regard to mat-
`ters affecting the industry;
`d) To increase the amount and to improve the quality of pump service to the public;
`e) To support educational and research activities;
`f) To promote the business interests of its members but not to engage in business of the kind ordinarily carried on
`for profit or to perform particular services for its members or individual persons as distinguished from activities
`to improve the business conditions and lawful interests of all of its members.
`
`Purpose of Standards
`1) Hydraulic Institute standards are adopted in the public interest and are designed to help eliminate misun(cid:173)
`derstandings between the manufacturer, the purchaser and/or the user and to assist the purchaser in
`selecting and obtaining the proper product for a particular need.
`2) Use of Hydraulic Institute standards is completely voluntary. Existence of Hydraulic Institute standards
`does not in any respect preclude a member from manufacturing or selling products not conforming to the
`standards.
`
`Definition of a Standard of the Hydraulic Institute
`Quoting from Article XV, Standards, of the By-Laws of the Institute, Section B:
`"An Institute Standard defines the product, material, process or procedure with reference to one or more of the fol(cid:173)
`lowing: nomenclature, composition, construction, dimensions, tolerances, safety, operating characteristics, perfor(cid:173)
`mance, quality, rating, testing, and service for which designed."
`
`Comments from users
`Comments from users of this standard will be appreciated, to help the Hydraulic Institute prepare even more useful
`future editions. Questions arising from the content of this standard may be directed to the Technical Director of the
`Hydraulic Institute. The inquiry will then be directed to the appropriate technical committee for provision of a suit(cid:173)
`able answer.
`If a dispute arises regarding contents of an Institute publication or an answer provided by the Institute to a question
`such as indicated above, the point in question shall be sent in writing to the Technical Director of the Hydraulic Insti(cid:173)
`tute, to initiate the Appeals Process.
`
`Revisions
`The Standards of the Hydraulic Institute are subject to constant review, and revisions are undertaken whenever it is
`found necessary because of new developments and progress in the art. If no revisions are made for five years, the
`standards are reaffirmed using the ANSI canvass procedure.
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
`
`V
`
`Exhibit 1041
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`Page 7 of 44
`
`

`

`Disclaimers
`This document presents the best method available for determining the effect of viscosity on rotodynamic pump per(cid:173)
`formance available to the Hydraulic Institute as of publication. Nothing presented herein is to be construed as a
`warranty of successful performance under any conditions for any application.
`
`Units of measurement
`Metric units of measurement are used and corresponding US customary units appear in brackets. Charts, graphs,
`and example calculations are also shown in both metric and US customary units.
`Because values given in metric units are not exact equivalents to values given in US customary units, it is important
`that the selected units of measure be stated in reference to this standard. If no such statement is provided, metric
`units shall govern.
`
`Consensus for this standard was achieved by use of the Canvass Method
`The following organizations, recognized as having an interest in the standardization of rotodynamic pumps, were
`contacted prior to the approval of this revision of the standard. Inclusion in this list does not necessarily imply that
`the organization concurred with the submittal of the proposed standard to ANSI.
`4B Engineering
`Malcolm Pirnie, Inc.
`Black & Veatch
`Mechanical Solutions, Inc.
`E.I. DuPont Company
`Patterson Pump Company
`ekwestrel corp
`Peerless Pump Company
`Gulich, Johann - Consultant to Sulzer Pumps (US) Inc.
`Pentair Water - Engineered Flow GBU
`Healy Engineering, Inc.
`Pump Design, Development, & Diagnostics, LLC
`lntelliquip, LLC
`Sulzer Pumps (US) Inc.
`ITT - Industrial Process
`Weir Floway, Inc.
`J.A.S. Solutions Ltd .
`Weir Minerals North America
`Kemet Inc.
`Weir Speciality Pumps
`Las Vegas Valley Water District
`
`Working Group Members
`For the current revision of this document, the committee consisted of the following members:
`Chairman: Thomas Angle, Weir Specialty Pump
`Vice-chairman: Michael Coussens, Peerless Pump Company
`
`Working Group Member
`Rene A. Barbarulo
`Michael S. Cropper
`Trygve Dahl
`Randal S. Ferman
`Allen J. Hobratschk
`Al lseppon
`David G. McKinstry
`John W. Owen
`James R. Roberts
`Aleksander S. Roudnev
`Fred F. Walker
`
`Other Contributors
`Ed Allis
`
`Company
`CLYDEUNION
`Sulzer Pumps (US) Inc.
`lntelliquip, LLC
`ekwestrel corp
`National Pump Company, LLC
`Pentair Water - Engineered Flow GBU
`IMO Pump
`IMO Pump
`ITT - Residential & Commercial Water
`Weir Minerals North America
`Weir Floway, Inc.
`
`Peerless Pump Company (Retired)
`
`vi
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
`
`Exhibit 1041
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`
`

`

`HI Effects of Liquid Viscosity on Pump Performance - 2010
`9.6.7 Effects of liquid viscosity on pump performance
`This version of ANSI/HI 9.6.7 differs from the 2004 version in two areas. The first difference is in the calculation of
`the efficiency correction factor when the B parameter is less than 1. This discontinuity has been corrected by defin(cid:173)
`ing the efficiency correction factor as 1.0 when B is less than 1. The second difference is that the 2004 version indi(cid:173)
`cated that test data with flows up 260 m3/h (1140 gpm) was used by the committee to develop the equations. This
`was in error and the 2010 version corrects the test data to flows up to 410 m3/h (1800 gpm). A statement is also
`added to discuss the difference between the limits of this document and the limits of the earlier (pre-2004) viscosity
`correction standard. There were also a number of minor editorial changes made to make the document easier to
`read and to clarify several points
`
`9.6.7.1 Summary
`
`Viscosity is one of the properties that characterizes all fluids. The performance of a rotodynamic pump varies with
`the viscosity of the pumped fluid. If the viscosity of the pumped fluid differs (is higher) significantly from that of
`water (which is the basis for most published performance curves), then the pump performance will differ from the
`published curve. For simplicity, the term viscous fluid is used within this document. In this context, viscous fluid is
`meant to describe a fluid with a viscosity greater than that of water, not to imply some fluids are not viscous. Head
`(H) and rate of flow ( Q) will normally decrease as viscosity increases. Power (P) will increase, as will net positive
`suction head required (NPSH3) in most circumstances. Starting torque may also be affected.
`The Hydraulic Institute (HI) has developed a generalized method for predicting performance of rotodynamic pumps
`on Newtonian liquids of viscosity greater than that of water. This is an empirical method based on the test data
`available from sources throughout the world. The HI method enables pump users and designers to estimate perfor(cid:173)
`mance of a particular rotodynamic pump on liquids of known viscosity, given the performance on water. The proce(cid:173)
`dure may also result in a suitable pump being selected for a required duty on viscous liquids.
`Performance estimates using the HI method are only approximate. There are many factors for particular pump
`geometries and flow conditions that the method does not take into account. It is nevertheless a dependable approx(cid:173)
`imation when only limited data on the pump are available and the estimate is needed.
`Theoretical methods based on loss analysis may provide more accurate predictions of the effects of liquid viscosity
`on pump performance when the geometry of a particular pump is known in more detail. This document explains the
`basis of such theoretical methods. Pump users should consult pump manufacturers to determine whether or not
`more accurate predictions of performance for a particular pump and viscous liquid are available.
`This document also includes technical considerations and recommendations for pump applications on viscous liq(cid:173)
`uids.
`
`9.6.7.2
`
`Introduction
`
`The performance (head, flow, efficiency [rl], and power) of a rotodynamic pump is obtained from the pump's char(cid:173)
`acteristic curves, which are generated from test data using water. When a more viscous liquid is pumped, the per(cid:173)
`formance of the pump is reduced. Absorbed power will increase and head, rate of flow, and efficiency will
`decrease.
`
`It is important for the user to understand a number of facts that underlie any attempt to quantify the effects of vis(cid:173)
`cosity on rotodynamic pump operation. First, the test data available are specific to the individual pumps tested and
`are thus not of a generic nature. Second, what data are available are relatively limited in the range of both pump
`size and viscosity of the liquid. Third, all existing methods of predicting the effects of viscosity on pump perfor(cid:173)
`mance show discrepancies with the limited test data available. Fourth, the empirical method presented in this doc(cid:173)
`ument was chosen based on a statistical comparison of various possible correction procedures. The chosen
`method was found to produce the least amount of variance between calculated and actual data. Considering all of
`the above, it must be recognized that this method cannot be used as a theoretically rigorous calculation that will
`predict the performance correction factors with great precision. It is rather meant to allow a general comparison of
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
`
`1
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`Exhibit 1041
`Bazooka v. Nuhn - IPR2024-00098
`Page 9 of 44
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`

`

`HI Effects of Liquid Viscosity on Pump Performance - 2010
`
`the effect of pumping higher viscosity liquids and to help the user avoid misapplication without being excessively
`conservative. See Section 9.6.7.4.2 for types of pumps for which the method is applicable.
`
`As a footnote to the preceding paragraph, it should be recognized that there are methods developed by individuals
`and companies that deal with the actual internal hydraulic losses of the pump. By quantifying these losses the
`effect of liquid viscosity can, in theory, be calculated . These procedures take into account the specific pump inter(cid:173)
`nal geometry, which is generally unavailable to the pump user. Furthermore, such methods still require some
`empirical coefficients that can only be derived correctly when sufficient information on the pumps tested in viscous
`liquids is available. The test data collected by HI from sources around the world did not include sufficiently detailed
`information about the pumps tested to validate loss analysis methods. It is nevertheless recognized that a loss
`analysis method will probably be more accurate than the empirical method in this document, especially for pumps
`with special features and particular geometry.
`
`In addition to the correction procedures, the document provides a qualitative description of the various hydraulic
`losses within the pump that underlie the performance reduction. Procedures for determining the effect of viscosity
`on starting torque and NPSH3 are also provided.
`
`The previous HI Standard for viscosity correction in reference 24 was based on data supplied up to 1960. This new
`document is based on an expanded data set up to 1999, which has modified the correction factors for rate of flow,
`head, and power. Updated correction factors are influenced by the pump size, speed, and specific speed. In gen(cid:173)
`eral, the head and flow have an increased correction while the power (efficiency) correction is less. The most signif(cid:173)
`icant changes in the correction factors occur at flows less than 25 m3/h (100 gpm) and ns < 15 (Ns < 770).
`
`9.6.7.3 Fundamental considerations
`
`9.6. 7 .3.1 Viscous correction factors
`
`When a liquid of high viscosity, such as heavy oil, is pumped by a rotodynamic pump, the performance is changed
`in comparison to performance with water, due to increased losses. The reduction in performance on viscous liquids
`may be estimated by applying correction factors for head, rate of flow, and efficiency to the performance with water.
`
`Thus the curves of head and efficiency for viscous liquids (subscript vis) are estimated from the head, flow, and effi(cid:173)
`ciency measured with water (subscript W) by applying the correction factors CH, c0, and C11, respectively. These
`factors are defined in Equation 1 :
`
`e _ VIS
`H-
`H - -
`Hw
`
`C _ Qvis C = Tivis
`o - Ow ,
`T\w
`11
`
`(Eq. 1)
`
`Figure 9.6.7.3.1 (a) and (b) shows schematically how the head, efficiency, and power characteristics typically
`change from operation with water to pumping a highly viscous liquid.
`
`If measured data are normalized to the best efficiency point (BEP) when pumping water (BEP-W), the factors CH
`and c0 can be read directly on Figure 9.6.7.3.1 (c). A straight line between BEP-W and the origin of the H-Q curve
`(H = O; Q = 0) is called the diffuser or volute characteristic. Test data reported in references 10 and 14 in the bibli(cid:173)
`ography show that BEPs for viscous liquids follow this diffuser or volute characteristic. Analysis of test data on vis(cid:173)
`cous pumping collected by HI from sources around the world also confirms this observation. It is consequently a
`good approximation to assume CH is equal to C0 at the BEPs for viscous liquids.
`
`9.6.7.3.2 Methods for determining correction factors
`
`Correction factors can be either defined empirically from a data bank containing measurements on various pumps
`with water and liquids of different viscosities or from a physical model based on the analysis of the energy losses in
`the pump. Examples of such loss analysis methods are given in references 7, 8, 9, and 18 of the bibliography.
`
`2
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
`
`Exhibit 1041
`Bazooka v. Nuhn - IPR2024-00098
`Page 10 of 44
`
`

`

`H
`
`Tl
`
`HI Effects of Liquid Viscosity on Pump Performance - 2010
`
`H
`HaEP - W
`
`volute or diffuser
`characteristic
`
`p
`
`____ Pvis
`
`:::------Pw
`
`OaEP-W
`(a)
`
`~ - - - - - - - - - Q
`
`(b)
`
`- - Water
`
`---- Viscous liquid
`
`Co
`
`(c)
`
`Figure 9.6.7.3.1 - Modification of pump characteristics when pumping viscous liquids
`
`llw
`
`Q
`
`QBEP- W
`
`Analysis of the limited data available shows that empirical and loss analysis methods predict head correction func(cid:173)
`tions with approximately the same accuracy. Loss analysis methods are, however, more precise in predicting power
`requirements for pumping viscous liquids. It is also possible to investigate the influence of various design parame(cid:173)
`ters on viscous performance and to optimize pump selection or design features for operation with highly viscous liq(cid:173)
`uids by applying the loss analysis procedures.
`
`Further theoretical explanations of the principles of loss analysis methods are given in Section 9.6. 7 .5 of this docu(cid:173)
`ment. Use of such methods may require more information about pump dimensions than is generally available to the
`user. A loss analysis procedure may be expected to provide more accurate predictions of pump performance with
`viscous liquids when such detailed information is available.
`
`The HI method explained in Section 9.6.7.4 of this document is based on empirical data. It provides a way of pre(cid:173)
`dicting the effects of liquid viscosity on pump performance with adequate accuracy for most practical purposes.
`The method in this document gives correction factors similar to the previous HI method. The new method matches
`the experimental data better than the old HI method that has been widely used throughout the world for many
`years. The standard deviation for the head correction factor, CH, is 0.1. Estimates of viscous power, Pvis• are sub(cid:173)
`ject to a standard deviation of 0.15.
`
`9.6.7.4 Synopsis of Hydraulic Institute method
`
`9.6.7.4.1 Generalized method based on empirical data
`
`The performance of rotodynamic pumps is affected when handling viscous liquids. A marked increase in power, a
`reduction in head, and some reduction in the rate of flow occur with moderate and high viscosities. Starting torque
`and NPSH3 may also be affected.
`
`The HI correction method provides a means of determining the performance of a rotodynamic pump handling a vis(cid:173)
`cous liquid when its performance on water is known. The equations are based on a pump performance Reynolds
`number adjusted for specific speed (parameter 8), which has been statistically curve-fitted to a body of test data.
`These tests of conventional single-stage and multistage pumps cover the following range of parameters: closed
`and semi-open impellers; kinematic viscosity 1 to 3000 cSt; rate of flow at BEP with water OaEP-W = 3 to 410 m3/h
`(13 to 1800 gpm); head per stage at BEP with water HaEP-w= 6 to 130 m (20 to 430 ft).
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
`
`3
`
`Exhibit 1041
`Bazooka v. Nuhn - IPR2024-00098
`Page 11 of 44
`
`

`

`HI Effects of Liquid Viscosity on Pump Performance - 2010
`
`The correction equations are, therefore, a generalized method based on empirical data, but are not exact for any
`particular pump. The generalized method may be applied to pump performance outside the range of test data indi(cid:173)
`cated above, as outlined in Section 9.6.7.4 and with the specific instructions and examples in Sections 9.6.7.4.5
`and 9.6.7.4.6. There will be increased uncertainty of performance prediction outside the range of test results. This
`uncertainty, however, is not expected to exceed the uncertainty that existed when applying the previously published
`(prior to 2004) HI viscosity correction method within the limits of the accompanying nomogram. (Maximum flow=
`2271 m3/h [10,000 gpm]). See reference 24.
`
`When accurate information is essential, pump performance tests should be conducted with the particular viscous
`liquid to be handled. Prediction methods based on an analysis of hydraulic losses for a particular pump design may
`also be more accurate than this generalized method.
`
`9.6.7.4.2 Viscous liquid performance correction limitations
`
`The correction factors are applicable to pumps of hydraulic design with essentially radial impeller discharge (n 5 ~
`60, N5 ~ 3000), in the normal operating range, with fully open, semi-open, or closed impellers. Do not use these
`correction factors for axial flow type pumps or for pumps of special hydraulic design. See Section 9.6.7.6 for addi(cid:173)
`tional guidance.
`
`Use correction factors only where an adequate margin of NPSH available (NPSHA) over NPSH3 is present in order
`to cope with an increase in NPSH3 caused by the increase in viscosity. See Section 9.6.7.5.3 to estimate the
`increase in NPSH3.
`
`The data used to develop the correction factors are based on tests of Newtonian liquids. Gels, slurries, paper stock,
`and other non-Newtonian liquids may produce widely varying results, depending on the particular characteristics of
`the liquids.
`
`9.6.7.4.3 Symbols and definitions used for determining correction factors
`
`See Section 9.6.7.8 for all notation definitions.
`
`Other technical expressions are defined in HI standards.
`
`Equations for converting kinematic viscosity from SSU to est units and vice versa are shown in Appendix A.
`
`Pump viscosity corrections are determined by the procedures outlined in the following Sections 9.6.7.4.4, 9.6.7.4.5,
`and 9.6.7.4.6.
`
`4
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
`
`Exhibit 1041
`Bazooka v. Nuhn - IPR2024-00098
`Page 12 of 44
`
`

`

`HI Effects of Liquid Viscosity on Pump Performance - 2010
`
`9.6.7.4.4 Overview of procedure to estimate effects of viscosity on pump performance
`
`The procedure is in three parts: first, to establish whether or not the document is applicable; second to calculate
`the pump performance on a viscous liquid when performance on water is known; and third to select a pump for
`given head, rate of flow, and viscous conditions.
`
`The procedure for the first part is illustrated in Figure 9.6.7.4.4a.
`
`Is the application for a single or multistage conven- NO_ I
`tional rotodynamic type?
`- I
`
`Beyond the scope of the procedure
`
`, , YES
`
`Does the pump use an impeller with an essentially NO_ I
`radial discharge? (n 5 ~ 60, N5 ~ 3000)
`
`-,
`
`, r YES
`
`Refer to Sections 9.6.7.4.2 and 9.6.7.6
`
`Does the liquid exhibit Newtonian behavior?
`
`NO _1
`- I Beyond the scope of the procedure
`
`, , YES
`
`Is the liquid kinematic viscosity greater than 1 and NO_ I Beyond the scope of the procedure
`- I
`less than 4000 cSt?
`
`I
`
`I
`
`I
`
`I
`
`Empirical data are based on viscosities up to 3000
`est, but the procedure may be used up to 4000 est
`with increased uncertainty.
`
`, r YES
`
`PROCEDURE IS APPLICABLE
`Go to Section 9.6.7.4.5 to determine pump performance.
`Go to Section 9.6.7.4.6 to select a pump.
`
`Figure 9.6.7.4.4a - Flowchart to establish if the procedure is applicable
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
`
`5
`
`Exhibit 1041
`Bazooka v. Nuhn - IPR2024-00098
`Page 13 of 44
`
`

`

`HI Effects of Liquid Viscosity on Pump Performance - 2010
`
`The procedure for the second part is defined in Section 9.6.7.4.5 starting on page 8 and summarized in Figure
`9.6.7.4.4b.
`
`Section 9.6.7.4.5
`
`Determine pump performance on a viscous liquid
`when performance on water is known
`
`1 '
`
`Calculate parameter B
`
`(Section 9.6.7.4.5, Step 1)
`
`, '
`
`Is parameter B ;?: 40?
`
`NO
`
`1 '
`
`Is parameter B :5 1.0?
`
`NO
`
`, '
`
`Calculate HaEP-vis and Ov;s
`
`(Section 9.6.7.4.5, Step 2)
`
`1 '
`
`Calculate Hvis
`
`(Section 9.6.7.4.5, Step 3)
`
`1 '
`
`Calculate T\vis
`
`(Section 9.6.7.4.5, Step 4)
`
`, '
`Calculate Pvis
`
`(Section 9.6.7.4.5, Step 5)
`
`I
`
`I YES_
`-
`I
`
`I YES_
`-
`I
`
`I
`
`I
`
`I
`
`I -I ~
`
`Loss analysis may be warranted
`(Section 9.6.7.5.2)
`
`Hvis = Hw
`
`Ov;s = Ow
`
`T\vis = T\w
`
`Figure 9.6.7.4.4b- Flowchart to determine pump performance on a viscous liquid when performance on
`water is known
`
`6
`
`Hydraulic Institute Standards, Copyright© 1997-2010, All Rights Reserved
`
`Exhibit