Refinery Control Valves --`,,-`-`,,`,,`,`,,`--- API RECOMMENDED PRACTICE 553 FIRST EDITION, SEPTEMBER 1998 Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS COPYRIGHT 2000 American Petroleum Institute Information Handling Services, 2000 Not for Resale API ENVIRONMENTAL, HEALTH AND SAFETY MISSION AND GUIDING PRINCIPLES The members of the American Petroleum Institute are dedicated to continuous efforts to improve the compatibility of our operations with the environment while economically developing energy resources and supplying high quality products and services to consumers. We recognize our responsibility to work with the public, the government, and others to develop and to use natural resources in an environmentally sound manner while protecting the health and safety of our employees and the public. To meet these responsibilities, API members pledge to manage our businesses according to the following principles using sound science to prioritize risks and to implement cost-effective management practices: ● To recognize and to respond to community concerns about our raw materials, products and operations. ● To operate our plants and facilities, and to handle our raw materials and products in a manner that protects the environment, and the safety and health of our employees and the public. ● To make safety, health and environmental considerations a priority in our planning, and our development of new products and processes. ● To advise promptly, appropriate ofÞcials, employees, customers and the public of information on signiÞcant industry-related safety, health and environmental hazards, and to recommend protective measures. ● To counsel customers, transporters and others in the safe use, transportation and disposal of our raw materials, products and waste materials. ● To economically develop and produce natural resources and to conserve those resources by using energy efÞciently. ● To extend knowledge by conducting or supporting research on the safety, health and environmental effects of our raw materials, products, processes and waste materials. ● To commit to reduce overall emissions and waste generation. ● To work with others to resolve problems created by handling and disposal of hazardous substances from our operations. ● To participate with government and others in creating responsible laws, regulations and standards to safeguard the community, workplace and environment. ● To promote these principles and practices by sharing experiences and offering assistance to others who produce, handle, use, transport or dispose of similar raw materials, petroleum products and wastes. --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale Refinery Control Valves Manufacturing, Distribution and Marketing Department API RECOMMENDED PRACTICE 553 FIRST EDITION, SEPTEMBER 1998 --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale SPECIAL NOTES --`,,-`-`,,`,,`,`,,`--- API publications necessarily address problems of a general nature. With respect to particular circumstances, local, state, and federal laws and regulations should be reviewed. API is not undertaking to meet the duties of employers, manufacturers, or suppliers to warn and properly train and equip their employees, and others exposed, concerning health and safety risks and precautions, nor undertaking their obligations under local, state, or federal laws. Information concerning safety and health risks and proper precautions with respect to particular materials and conditions should be obtained from the employer, the manufacturer or supplier of that material, or the material safety data sheet. Nothing contained in any API publication is to be construed as granting any right, by implication or otherwise, for the manufacture, sale, or use of any method, apparatus, or product covered by letters patent. Neither should anything contained in the publication be construed as insuring anyone against liability for infringement of letters patent. Generally, API standards are reviewed and revised, reafÞrmed, or withdrawn at least every Þve years. Sometimes a one-time extension of up to two years will be added to this review cycle. This publication will no longer be in effect Þve years after its publication date as an operative API standard or, where an extension has been granted, upon republication. Status of the publication can be ascertained from the API Manufacturing, Distribution and Marketing Department [telephone (202) 682-8000]. A catalog of API publications and materials is published annually and updated quarterly by API, 1220 L Street, N.W., Washington, D.C. 20005. This document was produced under API standardization procedures that ensure appropriate notiÞcation and participation in the developmental process and is designated as an API standard. Questions concerning the interpretation of the content of this standard or comments and questions concerning the procedures under which this standard was developed should be directed in writing to the director of the Manufacturing, Distribution and Marketing Department, American Petroleum Institute, 1220 L Street, N.W., Washington, D.C. 20005. Requests for permission to reproduce or translate all or any part of the material published herein should also be addressed to the director. API standards are published to facilitate the broad availability of proven, sound engineering and operating practices. These standards are not intended to obviate the need for applying sound engineering judgment regarding when and where these standards should be utilized. The formulation and publication of API standards is not intended in any way to inhibit anyone from using any other practices. Any manufacturer marking equipment or materials in conformance with the marking requirements of an API standard is solely responsible for complying with all the applicable requirements of that standard. API does not represent, warrant, or guarantee that such products do in fact conform to the applicable API standard. All rights reserved. No part of this work may be reproduced, stored in a retrieval system, or transmitted by any means, electronic, mechanical, photocopying, recording, or otherwise, without prior written permission from the publisher. Contact the Publisher, API Publishing Services, 1220 L Street, N.W., Washington, D.C. 20005. Copyright © 1998 American Petroleum Institute Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale FOREWORD API publications may be used by anyone desiring to do so. Every effort has been made by the Institute to assure the accuracy and reliability of the data contained in them; however, the Institute makes no representation, warranty, or guarantee in connection with this publication and hereby expressly disclaims any liability or responsibility for loss or damage resulting from its use or for the violation of any federal, state, or municipal regulation with which this publication may conßict. Suggested revisions are invited and should be submitted to the Director of the Manufacturing, Distribution and Marketing Department, American Petroleum Institute, 1220 L Street, N.W., Washington, D.C. 20005. --`,,-`-`,,`,,`,`,,`--- iii Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale CONTENTS Page SCOPE . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1 2 REFERENCES . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1 3 CONTROL VALVES . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1 3.1 Valve Body . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1 3.2 Valve Actuators . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 7 3.3 Valve Positioner . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 10 3.4 Handwheels. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 11 3.5 Switches And Solenoids . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 11 3.6 Transducers . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 11 3.7 Booster Relays . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 11 4 SPECIFIC CRITERIA. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 11 4.1 Globe-style Valves . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 11 4.2 Rotary Style Valves . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 13 5 INSTALLATION . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 5.1 Accessibility. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 5.2 Location . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 5.3 Control Valve Manifolds . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 13 13 14 14 6 REFINERY APPLICATIONS . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.4 Boiler Feedwater Recirculation. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.5 Feedwater to Waste Heat Boiler . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.6 Sulfur Recovery Unit Acid Gas Block Valve . . . . . . . . . . . . . . . . . . . . . . . . . 6.7 Sulfur Vapor to Eductor . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.8 Liquid Sulfur to Storage . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.9 Hydroßuoric Acid Service. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.10 Cat Cracker Bottoms Slurry Oil . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.11 Feed to Hydrocracker Fractionator (Flashing) . . . . . . . . . . . . . . . . . . . . . . . . 6.12 Reformer Hot Gas Block/Bypass (Three-Way Butterßy). . . . . . . . . . . . . . . . 6.13 Reactor Letdown with Erosive Solids . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.14 KO Drum Vent to Hydrotreater Flare . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.15 Antisurge Control Valves. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.16 High Volume, Low Pressure Air Blower Anti-Surge Valve . . . . . . . . . . . . . . 6.17 Crude Oil Processing Unit Throttling /Steam to Pre-Heat Exchanger . . . . . . 6.18 Pump Recirculation Valve . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.19 Crude Oil Processing Unit Heavy Bottoms (High Temperature Tar). . . . . . . 6.20 Crude Oil Processing UnitÑThrottling/Wash Oil . . . . . . . . . . . . . . . . . . . . . 6.21 Crude Processing UnitÑThrottling/Hot Oil . . . . . . . . . . . . . . . . . . . . . . . . . . 6.22 Spray Water to Desuperheater (Utilities) . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.23 Exchanger HGO BypassÑFCC . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.24 Gas Oil RecirculationÑCaustic Hydrotreater (CHD) . . . . . . . . . . . . . . . . . . 6.25 Hot Separator Liquid to Hot Flash Drum (Power Recovery Turbine Bypass)ÑHydrocracker. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6.26 Cold Separator Sour WaterÑHydrocracker . . . . . . . . . . . . . . . . . . . . . . . . . . 14 14 15 15 15 15 16 16 16 16 17 17 17 18 18 18 18 19 19 19 20 20 --`,,-`-`,,`,,`,`,,`--- 1 7 20 21 EMERGENCY BLOCK VALVES . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 21 v Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale Page 7.1 7.2 7.3 7.4 7.5 7.6 Valve Type . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . DeÞnitions . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . Types of EVBs . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . EBV General Instillation Guidelines. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . Actuator Selection . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . FireprooÞng . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 21 21 21 22 22 23 8 VAPOR DEPRESSURING VALVES . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 23 8.1 General . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 23 8.2 Depressuring Valves and Actuator Requirements . . . . . . . . . . . . . . . . . . . . . . 23 9 HYDRAULIC SLIDE VALVE ACTUATORS. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9.1 General . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9.2 Hydraulic Power Unit (HPU) . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9.3 Slide Valve Positioner Systems . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9.4 Instrumentation Required . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9.5 Performance Characteristics . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9.6 Electrical Requirements. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9.7 Testing and Inspection . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9.8 Slide Valve Actuator Service . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 23 23 23 24 24 25 25 25 25 --`,,-`-`,,`,,`,`,,`--- Figures 1 Control Valve . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 2 2 Live Loaded . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 3 3 Resilient Seat . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 4 4 Inherent Characteristics . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 4 5A Sliding and Rotary Stem . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 5 5B Sliding and Rotary Stem . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 5 6 Pressure Drop Through a Restriction. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 5 7 Cavitation Damage. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6 8 Typical Plug Damage from Flashing . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 7 9 Multistaged Trim . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 8 10 Diaphragm Actuator . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9 11 Double-Acting Spring Return Piston Actuator . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9 12 Electrohydraulic Actuator . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 10 13A Handwheels . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 12 13B Handwheels . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 12 14 Limit Switches . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 12 15 Butterßy Valve . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 13 16 Lug Style Butterßy . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 13 vi Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale Refinery Control Valves 1 Scope NACE3 Std MR0175-90 SulÞde Stress Cracking Resistant Metallic Materials for OilÞeld Equipment 1.1 This Recommended Practice addresses the special needs of control valve applications in reÞnery services. The knowledge and experience of the industry has been captured to provide proven solutions to well-known problems. OSHA4 1910.95 1.2 This document provides recommended criteria for the selection, speciÞcation, and application of piston and diaphragm-actuated control valves. It also outlines control valve design considerations, and discusses control valve sizing, noise, and fugitive emissions as well as deÞning types of commonly used control valves and their actuators. U.S. EPA5 40 CFR Pt. 60 A control valve, as shown in Figure 1, consists of two major subassemblies: a valve body and an actuator. The valve body is the portion that actually contains the process ßuid. It consists of a body, internal trim, bonnet, and sometimes a bottom ßange and/or bonnet ßange. This subassembly must meet all of the applicable pressure, temperature, and corrosion requirements of the connecting piping. The actuator assembly moves the control valve in response to an actuating signal from an automatic or manual device. It must develop adequate thrust to overcome the forces within the body subassembly and at the same time be responsive enough to position the valve plug accurately during changing process demands. 2 References All references shall be the latest edition. RP 521 Std 556 Std 589 Spec 6FA Std 607 Std 609 FireprooÞng Practices in Petroleum and Petrochemical Processing Plants Guide for Pressure-Relieving and Depressuring Systems Manual on Installation of Instruments and Control Systems for Fire Heaters and Steam Generators Fire Test for Evaluation of Stem Packing SpeciÞcation for Fire Test for Valves Fire Test for Soft-Seated Quarter-Turn Valves Butterßy Valves: Double Flanged, Lug-and Wafer-Type 3.1 VALVE BODY 3.1.1 Process design conditions dictate the ANSI pressure classiÞcation and materials of construction for control valves, provided the standard offering meets or exceeds all piping and process control requirements. The valve end connections and pressure rating should, as a minimum, conform to the piping speciÞcation. The valve material shall be suitable for the process conditions. 3.1.2 Nickel alloy or stainless steel valve metallurgy should be speciÞed for temperatures below -20¡F. High pressure steam, ßashing water applications, and boiler feedwater service where differential pressures exceed 200 psi may require harder, chrome-molybdenum alloys. Sour service valve materials must meet the requirements of NACE MR0175-90. Corrosive and erosive components even in trace quantities may affect the metallurgical choice of the valve. ASME 1 B16.34 FCI2 70-2 Boiler and Pressure Vessel Code, Section VIII, Div. 1, International Society for Measurement and Control Standard S75 Series of Control Valve Standards ValvesÑFlanges, Threaded, and Welded End 3.1.3 Inner valve parts should be the manufacturerÕs standard where acceptable. Hardened trim may be required for Quality Control Standard for Control Valve Seat Leakage 3 NACE International, 1440 South Creek Drive, P.O. Box 218340, Houston, Texas 77218-8340. Occupational Safety and Health Administration, U.S. Department of Labor, Washington, D.C. 20402. 5U.S. Environmental Protection Agency, available from the U.S. Government Printing OfÞce, Washington, D.C. 20402. 4 1 American Society for Mechanical Engineers, 345 East 47th Street, New York, New York 10017. 2Fluid Controls Institute, P.O. Box 9036, Morristown, New Jersey 07960. 1 --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Appendix A, Attachment 1: Reference Method 21. Determination of Volatile Organic Compound Leaks 3 Control Valves 1.3 Recommendations for emergency block and vent valves, on/off valves intended for emergency isolation or venting, and special design valves for reÞnery services, such as FCCU slide valves and vapor depressuring systems, are also included in this Recommended Practice. API Publ 2218 Occupational Noise Exposure Not for Resale 2 REFINERY CONTROL VALVES Adjusting Screw Gasket Adjusting Screw (with Lifting Ring) Spring Button Spring Piston Retaining Nut Piston Stem O-ring Actuator Stem Spacer Cylinder Actuator Stem Bushing Piston Actuator Stem O-ring Piston O-ring Cylinder Retaining Ring Stem Clamp O Actuator Stem Gland Flange Upper Packing Stroke Plate S Stroke Bellows Yoke Clamp Yoke Packing Spacer Upper Stem Guide Bonnet Upper Stem Guide Liner Bonnet Flange Bonnet Flange Bolting Seat Retainer Seat Ring Bonnet Gasket Seat Ring Gasket Lower Packing Lower Stem Guide Body Lower Stem Guide Liner Half Ring Plug End Flange Figure 1—Control Valve corrosive, erosive, cavitating, or ßashing service, and where valve differential pressure exceeds 200 psi. recommended. In addition, high-tensile strength bolting is required. 3.1.4 Flanges are the preferred end connection for globestyle valves, with butt-weld end connections acceptable for ANSI classes 900 and above. Threaded valves and valves with welded end connections are not recommended for hydrocarbon service and should be speciÞed only with the ownerÕs prior approval. 3.1.7 Flange Þnish describes the depth of the grooves in the surface part of a ßange which is available for the sealing gasket. If a special Þnish is required for gaskets, it should be speciÞed with the valve. The typical standard is 125Ð250 RMS, which provides a good sealing surface for the gasket. 3.1.5 Flanged control valve bodies are available with either integral ßanges (machined as part of the body casting or forging, or ßanges welded to the body), or separable ßanges (individual removable ßanges that usually lock in place on the valve body by means of a two-piece retaining ring). 3.1.6 Flangeless valves have no ßange connections as part of the valve body and are simply bolted or clamped between the adjoining line ßanges. Long bolts used with ßangeless valves can expand when exposed to Þre and cause leakage. A Þre deßection shield and/or insulation is 3.1.8 The installed face-to-face dimension of integral ßange globe style valves should conform to ANSI/ISA S75.03. Face-to-face dimensions of ßangeless control valves should conform to ANSI/ISA S75.04. Face-to-face dimensions of separable ßanged globe style valves should conform to ISA S75.20 or ISA S75.03. Butterßy valves are covered by API 609. Caution should be used to install ßangeless valves so that they will not leak in hydrocarbon service under Þre conditions. 3.1.9 The valve body size should be no less then two pipe sizes smaller than the line size. Smaller valve sizes --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale API RECOMMENDED PRACTICE 553 3.1.10 Final valve sizing should be reviewed by the valve manufacturer. 3.1.11 Threaded seat rings should be avoided where possible because corrosion often makes removal difÞcult. 3.1.12 Bonnets Bonnets should be bolted. Bolting material should comply with ASTM A193/194/320 and should be compatible with the valve body and bonnet. Note: For the temperature range between -50¼F and 1000¼F, bolts and studs should meet ASTM A193, Grade B7 speciÞcations. For temperatures between 1000¼F and 1100¼F, bolts should be ASTM A193, Grade B16. For low temperature applications from -50¼F to -150¼F, bolts should be ASTM A320, Grade B7. Nuts should be ASTM A194, Grade 2H for the above applications. Stainless steel bodies require stainless steel bolting. Higher grade valve metallurgy requires 316 SST as the minimum bolting material. Extended bonnets should be considered for process temperatures below 32¡F or above the temperature limits of the packing materials shown below in section 3.1.13. Bonnet gaskets should be fully retained 316 SST spiral wound, with polytetraßoroethelene or graphite Þller. Flat gaskets made from PTFE sheet stock are acceptable where conditions permit. Insert reinforcements should be 316 SST or other appropriate alloy, as required. 3.1.13 Packing a. Packing boxes should be easily accessible for periodic adjustment. The packing material should (1) be elastic and easily deformable, (2) be chemically inert, (3) be able to withstand applicable process conditions, (4) provide a degree of Þre resistance, (5) minimize friction, and (6) reduce fugitive emissions to meet regulatory requirements. Valve manufacturerÕs packing temperature limits refer to the temperature at the packing box. b. PTFE has excellent inertness, good lubricating properties, and is one of the most popular valve packing materials. It may be used in solid molded, braided, or turned form (Vrings) or as a lubricant for asbestos-free packing. Its temperature limit with standard packing box construction is 450¡F. If used to meet fugitive emissions, virgin PTFE should be alternated with carbon-Þlled PTFE or similar minimal coldßowing material and live loaded. c. Graphite laminated or preformed ring packing is chemically inert except when strong oxidizers are handled. This type of packing can be used for temperature applications approaching 2000¼F. The biggest difÞculty caused by this type of packing is very high packing friction, which often requires an oversized actuator. Performance is often compromised, because of signiÞcant increases in hysteresis and deadband. d. Asbestos should not be used. Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS 3.1.14 Fugitive Emissions The Clean Air Act of 1990 or local requirements have established strict limits on emission to the atmosphere of certain hazardous substances. These substances are volatile hazardous pollutants listed in the National Emission Standard for Hazardous Air Pollutants (NESHAP). Increased emphasis on limiting packing leaks has resulted in the development of new packing materials and methods. Individual manufacturers are offering increasingly effective designs, and vendors should be consulted for speciÞc applications. See Figure 2. Kalrez¨ also has excellent inertness and good lubricating properties. It does not cold ßow and therefore does not need live loading. It is available in V-rings. The temperature limit with standard packing box construction is 700¼F. 3.1.15 Seat Leakage a. See ANSI/FCI 70-2 standard for deÞnitions of leakage classes. Note that these deÞnitions change the way that leakage is deÞned and tested between Classes V and VI. Control valves should have no less than a Class II leakage rating. For most services, a Class IV rating is adequate. Class VI ratings should be considered only for applications requiring minimum possible leakage, and then only with owner approval. b. Double-ported valves provide a Class II shutoff. c. Single-seated globe valves with metal-to-metal seating surfaces meet Class IV. Class V shutoff can be achieved by providing improved plug to seat ring concentricity or lapping seating surfaces and/or increasing actuator thrust. Resilient seats on single seated valves can provide Class VI shutoff. d. However, before an insert material is selected, it should be determined that the insert is compatible with the process ßuid, pressure, and temperature. In addition to normal process Live-loading (compressed) (not compressed) Carbon-filled PTFE backups Virgin PTFE V-rings Wiper Rings Figure 2—Live Loaded Not for Resale --`,,-`-`,,`,,`,`,,`--- must be reviewed to make sure that line mechanical integrity is not violated. 3 4 REFINERY CONTROL VALVES Insert Retainer or rotary motion (see Figures 5B and 16). The selection of a valve for a particular application is primarily a function of the process requirements for control performance, pressure drop, temperature, and rangeability. Insert Soft Seat Ring Figure 3—Resilient Seat 100 90 pen 80 r ea Lin en t 50 ck O 60 Qui 40 rc Flow, % 70 30 u Eq al Pe 20 10 0 10 20 30 40 50 60 70 80 90 100 Valve Life, % Figure 4—Inherent Characteristics condtions, shutdown conditions should be considered in selecting resilient seats. Steaming through a valve can damage or ruin a resilient seat. (See Figure 3.) 3.1.16 Control Valve Characteristics a. Control valve ßow characteristics are determined principally by the design of the valve trim. The three inherent characteristics available are quick opening, linear, and equal percentage, as shown in Figure 4. A modiÞed equal percentage characteristics generally falling between linear and equal percentage characteristics is sometimes available. b. Positioners may use mechanical cams or be programmed to provide other desired characteristics. c. Installed characteristics often differ signiÞcantly from inherent characteristics if the pressure drop across the control valve varies with ßow. As a result, equal percentage plugs are generally used for ßow control applications because most of the Òsystem pressure dropÓ is not across the control valve. Linear plugs are commonly used for applications where most of the Òsystem pressure dropÓ occurs across the control valve. 3.1.17 Control Valve Types TodayÕs control valves operate by one of two primary motions: reciprocating (sliding stem) motion (see Figure 5A,) Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS a. ISA S75.01, Flow Equations for Sizing Control Valves, is the basic source used. Per ISA 75.02, Control Valve Capacity Test, the tolerance for control valve Cv testing is ±5% at full opening; the tolerance for partial openings is not stated. Control valve data is based on water testing with a limited set of sizes. The calculations become less accurate for ßuids signiÞcantly different from water, for very large or very small sizes, and for conditions different from laboratory conditions. b. The primary factors that should be known for accurate sizing are: 1. The upstream and downstream pressures at the ßow rates being considered. 2. The temperature of the ßuid. 3. The ßuid phase (gas, liquid, slurry) and the density of the ßuid (speciÞc gravity, speciÞc weight, molecular weight). 4. The viscosity (liquids). 5. The vapor pressure and critical pressure (liquids). 6. SpeciÞc heat ratio (gas). 7. The compressibility factor (gas). c. As part of valve selection, the overall system in which the valve is to be installed should be considered. A typical system (in addition to the control valves) includes a pump or compressor, which provides energy, and other types of reÞnery equipment, such as piping, exchangers, furnaces, and hand valves, which offer resistance to ßow. Note that the differential pressure between the pump head curve and the system pressure drop curve is the amount of pressure available for the control valve. If no control valve were used, the ßow would always be at the rate indicated by the intersection of the two curves. d. The presence of reducers upstream and/or downstream of the valve will usually result in a reduction in capacity because of the creation of an additional pressure drop in the system by these enlargements or contractions in series with the valve. Piping systems where both the inlet and outlet piping are larger than the valve will result in an increased valve Cv requirement. Capacity correction factors that can be applied to calculated Cv values are readily available from most manufacturers for the various styles of valves. e. In any ßow restriction, a portion of the pressure head of the incoming ßuid is changed to velocity head, resulting in a reduction in static pressure at the vena contracta. Refer to Figure 6. As the ßuid leaves the ßow restriction and assumes downstream velocity, some portion of velocity head is recovered as pressure head. This process is termed pressure recovery. The degree of pressure recovery is dependent upon Not for Resale --`,,-`-`,,`,,`,`,,`--- 3.1.18 Sizing API RECOMMENDED PRACTICE 553 5 Figure 5A and 5B—Sliding and Rotary Stem These can reduce or prevent cavitation. Some of these trims are subject to plugging in dirty services and should be reviewed for suitability in each service. 2. Valves with low-pressure recovery should be used to minimize or prevent cavitation. In some cases it may be necessary to use special components, or stage the pressure reduction through the use of two or more valves, or specially design elements in series. h. Flashing 1. Flashing occurs where the downstream pressure is less than the vapor pressure. See Figures 6 and 8. Flow P1 Restriction Vena Contracta P1 P2 (Cavitating) Pv P2 (Flashing) Pvc Distance Figure 6—Pressure Drop Through a Restriction --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS P2 Pressure the internal geometry of the ßow restriction. The pressure excursion in liquid ßow results in a vena contracta pressure lower than the downstream pressure. The vena contracta pressure may drop below the vapor pressure of the ßuid. As the pressure recovers it may stay below the vapor pressure (ßashing) or it may recover above the vapor pressure (cavitation). Flashing and cavitation are indications of partial or full choked ßow, which may affect sizing. f. Choked volumetic ßow occurs in gas or vapor service when the ßuid velocity reaches the speed of sound at the vena contracta. With a constant inlet pressure, increasing the pressure drop no longer increases the ßow. This will affect the valve sizing by limiting the pressure drop available for sizing. Pressure recovery has the effect of achieving choked ßow at a pressure drop that is less than would be predicted by the critical pressure ratio. This can become a problem for valves with high-pressure recovery, such as rotary valves. This necessitates the use of a larger valve or different valve style. g. Cavitation 1. Cavitation is the generation of bubbles in the lowest pressure portion of the valve, and then the subsequent collapse of these bubbles. See Figure 6. The bubble collapse (implosion) releases an intense liquid jet which can destroy a control valve in a short time. See Figure 7. It is easily recognized by a characteristic sound Òlike rocks ßowing through the valve.Ó A single compound such as water is one of the most damaging ßuids. Hydrocarbon mixtures can have various vapor pressures for different components in the mixture, making it very difÞcult to predict the onset or the severity of cavitation. Special cavitation control trims are offered by manufacturers. Not for Resale 6 REFINERY CONTROL VALVES excess capacity at the high end and 10 to 20% below the minimum required capacity at the low end. 2. A high rangeability is of little signiÞcance if the service conditions for the valves in question do not require it. The requirement for rangeability is to cover the maximum and minimum ßow rates at the real ßowing conditions. j. Manufacturers should analyze all valve speciÞcations for cavitation, noise, or other detrimental factors, using the data on the data sheets as a basis. Undesirable operating situations should be brought to purchaserÕs attention, including noise or cavitation severity. Manufacturers should propose possible solutions to these problems within the design limits of the type of valve covered by the speciÞcation or indicate that a special design is required. Figure 7—Cavitation Damage Flashing, like cavitation, can cause physical damage and decreased ßow capacity. Velocity is the major concern. The outlet ßow increases velocity due to the ßuid changing from a liquid to a gaseous state. A larger control valve body size with reduced trim and larger size outlet piping is usually required to prevent choking and excessive velocity problems. 2. Flashing damage is usually less severe than the damage from cavitation. However, restricted piping conÞgurations at the valve outlet can cause the ßashed vapor to cavitate and cause piping damage downstream of the control valve. Manufacturers should be consulted for recommendations. 3. Outgassing of dissolved gases that have been absorbed by contacting (such as amine) is similar to ßashing, but the relative amount of gas released is much harder to predict. The process engineer should be consulted to obtain the correct outlet liquid and gas ßow rates. i. Rangeability 1. The rangeability of the control valve should be considered during valve selection. Control valves are available with published Cv rangeability of 50 to 1 and even greater, at constant pressure drop, a condition that rarely exists in actual practice. Typically, valves are sized with 10 to 20% g. In no case should the calculated sound level exceed 115 Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS a. The predicted sound pressure level radiated from a control valve is a complex determination, and the allowable noise level in the installed location cannot be stated as one simple number to be speciÞed in all circumstances. This is particularly true where there are other noise sources in close proximity, since they have an additive effect. The actual level depends on a number of factors, such as atmospheric discharge, physical location, proximity of other noise sources and their magnitude, piping system conÞguration and wall thickness, insulation on piping, presence of reßective sources, etc. b. Prediction of noise generated by a control valve is an inexact science. Prediction levels for a valve operation at conditions speciÞed on the speciÞcation sheet can vary widely using various manufacturersÕ methods. c. To provide a basis for allowable noise level analysis, control valves calculated to generate excessive noise levels should have alternate valves proposed that will not exceed 85 dBA at one meter downstream and one meter out from the pipe. For atmospheric discharge vent control valves (or system), the noise level should not exceed 90 dBA at a point four meters down from the vent exhaust and at a downward angle of 45 degrees. No allowance should be taken for insulation or increased pipe wall thickness over that speciÞed in making noise calculation, or in the valve or the noise reduction system. d. The calculated continuous noise level should not exceed 85 dBA, measured where personnel may be continuously working. This may not be one meter downstream and one meter out from the pipe. The Occupational Safety and Health Administration decreases the allowable time of exposure as the sound level increases, and the user is referred to OSHA 1910.95 for speciÞc guidelines. It is the userÕs responsibility to determine if the sound level will meet OSHA requirements. e. Noise levels above 85 dBA may be allowable where personnel are not working continuously. f. The maximum intermittent sound level should normally be limited to 110 dBA. dBA due to possible mechanical failure. Not for Resale --`,,-`-`,,`,,`,`,,`--- 3.1.19 Noise API RECOMMENDED PRACTICE 553 7 Figure 8 — Typical Plug Damage from Flashing h. Documented procedures and computer programs to estimate control valve noise are available from leading manufacturers, and they should be used to determine whether noise is a consideration. However, noise prediction and mitigation is a specialized effort generally requiring the manufacturer recommendation for an effective design. i. Valves with noise abatement or cavitation control trim with small passages tend to plug with debris, particularly during startup, and should be protected with conical or T-type strainers. See Figure 9. --`,,-`-`,,`,,`,`,,`--- 3.1.20 Body Integrity Hydrostatic testing of pressure-containing components is required per ANSI B16.34. For special services, other nondestructive tests are sometimes speciÞed. 3.1.21 Valve Assembly The valve, actuator, and associated accessories, regardless of manufacturer(s), should be assembled, piped, aligned, tested, and shipped as a unit by the valve manufacturer. Tests may include hydrostatic, stroke test, leakage, or accessory calibration. 3.1.22 Nameplate The valve should be supplied with a permanently attached stainless steel tag, stamped with the manufacturerÕs standard data, and the tag or item number. 3.2 VALVE ACTUATORS 3.2.1 Pneumatic valve actuators, using air or gas, are preferred for most process control applications. Electric motor or electrohydraulic operators may be considered for special applications, particularly when pneumatic power is not available. Electrohydraulic actuators are used where very high thrust forces are required. Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS 3.2.2 Actuators are classiÞed as direct acting (an increase in air loading extends the actuator stem) or reverse acting (an increase in air loading retracts the actuator stem). Some actuators are Þeld reversible. They can be changed from direct to reverse acting with no additional parts. Most manufacturers publish tables that allow selection of actuator size based on valve size, ßow direction, air action, pressure drop, packing friction, and available air pressure. 3.2.3 Diaphragm Actuators a. A spring diaphragm actuator is a single-acting actuator where pressure is applied against a spring or springs. Upon loss of air, the spring will move the valve to the desired failure position. Construction of a typical spring diaphragm actuator is shown in Figure 10. b. Traditionally, the spring diaphragm actuator stroked over an input range of 3Ð15 psi. The frequent use of positioners and the requirements for tight shutoff have led to widespread use of higher pressures, utilizing the available air supply. 3.2.4 Piston Actuators a. Piston (or cylinder) pneumatic actuators are used for control valves where high thrust is required. Single-acting piston actuators apply air pressure to one side of the piston against a spring or springs. Upon loss of air the spring will move the valve to the desired failure position. Double-acting piston actuators are considerably stiffer than singleacting designs and can therefore be used to control higher pressure drops. Double-acting piston actuators apply air to both sides of the cylinder. Double-acting piston actuators without springs require an external volume tank and trip system to achieve the desired failure position. Springs can be added to double-acting piston actuators to provide the air failure mode. See Figure 11. Not for Resale 8 REFINERY CONTROL VALVES Figure 9—Multistaged Trim --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale API RECOMMENDED PRACTICE 553 Air Lifts Spring Pushes Down 9 Upper Travel Stop Diaphragm Plate Diaphragm Loading Pressure O-Ring Seal O-Ring Seal Diaphragm Rod Spring Spring Adjuster Spring Seat Stem Connector Travel Indicator Valve Stem Indicator Scale O Reverse Actuator Figure 10—Diaphragm Actuator b. Linear type piston actuators are used for globe style control valves. They are also used for rotary valves with adapter linkage. Scotch yoke or rack-and-pinion type piston actuators are normally used for on/off control, but may be used for regulatory control if control degradation is not critical. S 3.2.5 Electrohydraulic Actuators A variation of the piston actuator is the electrohydraulic, actuator which uses an electric motor to drive a pump and supply hydraulic pressure for the piston. For multiple valve installations, electrohydraulic actuators may be supplied by a common electric motor/pump skid. See Figure 12. Figure 11—Double-Acting Spring Return Piston Actuator 3.2.6 Actuator Selection 3.2.6.2 Stroking speed requirements should be reviewed and speciÞed for critical applications, such as compressor anti-surge control, or where closing speed should be controlled to prevent hydraulic water hammer. 3.2.6.1 Actuator selection guidelines are based on the assumption that the control valve will be required to operate against the maximum differential pressure speciÞed. Generally, the worst case is to use the maximum upstream pressure with the downstream pressure vented to atmosphere. Utilizing this condition for selection of the actuator ensures adequate power for maximum service conditions but can dramatically affect operator size, particularly on larger valve sizes. Actuators should be sized for the minimum air supply pressure available. 3.2.6.3 Valve failure position should be carefully analyzed in the event that supply pressure or instrument signal is lost. Generally, the valve should fail in the safe direction on loss of power or signal. 3.2.6.4 The most reliable fail-safe action is achieved with an enclosed spring. If capacity tanks are required to provide --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale 10 REFINERY CONTROL VALVES Coil Force Motor Input Signal Air Bleed --`,,-`-`,,`,,`,`,,`--- 5 Volt AC Cycle Feedback Spring Bias Spring Cylinder Shutoff Valves Feedback Cam Bypass Valve 1/3 H.P. Electric Motor 50 psig (3.4 Bar) 500 psig (34.5 Bar) Drain Off Connection 500 psig (34.5 Bar) 3-Section Pump with Built-In Relief Valves Suction Filter Figure 12— Electrohydraulic Actuator reserve operating power, they should be sized to stroke the valve twice. Capacity tanks should be stamped and otherwise conform to ASME Code guidelines (see Part U-1, Section VIII, Division 1, ASME Boiler and Pressure Vessel Code). Capacity tanks should be designed with all necessary accessories to ensure the required valve action and failure position. teresis should be addressed. The valve, actuator, and positioner should be evaluated as part of the entire loop to determine loop performance. 3.2.6.5 The actuator case should be rated for the maximum available pneumatic supply pressure. Filters or Þlter regulators, if required, shall be supplied at the actuator inlet or the positioner inlet. 3.2.6.9 Sliding stem actuators should be supplied with an indicator showing valve stem position. Rotary valve actuators should have a travel indicator attached at the actuator end of the shaft, graduated in percent or degrees open. 3.2.6.6 The actuator should be sized to meet all control, shutoff, and valve leakage requirements. Shutoff capabilities should be investigated at conditions of maximum differential pressure. 3.3 VALVE POSITIONER 3.2.6.7 To improve control valve performance, the effects of low frequency response and excessive deadband and hys- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS 3.2.6.8 In general, the actuator materials of construction should be the manufacturerÕs standard. 3.3.1 Valve positioners should be speciÞed for all applications except on/off service. The valve positioner compares the valve stem position with the signal generated by the controller. If the valve stem is incorrectly positioned, the positioner either increases or decreases the air pressure to the actuator until the Not for Resale API RECOMMENDED PRACTICE 553 correct valve stem position is obtained. Pneumatic or electropneumatic positioners are used to improve valve performance. 3.3.2 The following is a list of functions a positioner can accomplish: 1. Provide for split range operation. 2. Reverse the valve action without changing the ÒfailsafeÓ action of the spring in the actuator. (Note that this may also be done with a reversing type relay.) 3. Increase the thrust in spring diaphragm actuators. 4. Modify the control valve ßow characteristic. 5. Improve the resolution or sensitivity of the actuator where high precision valve control is required. Precision is enhanced by the availability of positioners with adjustable gain. 6. Reduce hysteresis. 11 ented downward. Three-way solenoid valves are used with spring return actuators and double-acting actuators with positioners. Four-way solenoid valves are used with double-acting actuators with no spring and on/off double-acting spring return valves. Solenoid valves should be speciÞed so that they do not require a minimum differential pressure across the valve to actuate. 3.5.3 Valve trip solenoids should be installed in the actuator inlet tubing. When exhaust rate is critical, the solenoid valve Cv should be selected accordingly. A quick exhaust valve, working in concert with a pilot solenoid valve, may be required if the trip solenoid does not have sufÞcient venting capacity. Quick exhaust valves have relatively large vent capacity, with a Cv value at least ten times that of the typical 1/ " solenoid valve. 4 --`,,-`-`,,`,,`,`,,`--- 3.3.3 Positioners should be installed using mounting plates or bosses provided for that purpose. The positioner should be mounted by the vendor, completely piped and aligned. The positioner should be supplied with pressure gauges. 3.5.4 Control valves with solenoids and limit switches should be speciÞed with 18" connecting leadwires or prewired to junction boxes. Low voltage and 120-volt wiring should not be used in the same junction box. 3.3.4 Positioner bypasses should only be speciÞed with pneumatic positioners having the same or greater input signal and stroking range. Bypasses are not applicable with electropneumatic positioners or with piston actuators. 3.5.5 DC voltage solenoids should be installed with a transient voltage suppressor or diode mounted in parallel with the solenoid coil. AC voltage solenoids should have a metal oxide varistor mounted with the solenoid coil. 3.3.5 Fast loops may require special tuning for best results. 3.6 TRANSDUCERS 3.3.6 Digital positioners further enhance valve performance, provide diagnostic information, and facilitate predictive maintenance programs. 3.4 HANDWHEELS 3.4.1 Manual handwheel operators should be supplied only on speciÞc request by the owner, or where bypasses are not installed. Side-mounted, lockable, screw or gear drive manual operators, continuously connected and operable through an integral declutching mechanism, are preferred. See Figures 13A and 13B. 3.4.2 Handwheels should be permanently marked to indicate valve open and closed directions 3.6.1 Electropneumatic transducers convert the electrical output signals from electronic controllers into pneumatic signals that may be used to operate diaphragm actuated control valves or provide signals to pneumatic positioners. The use of transducers with control valves is a common practice. Vibration resistant transducers are required when mounted on control valves. 3.6.2 Electropneumatic positioners are available which convert electronic signals to pneumatic output without a separate transducer. Electropneumatic positioners are widely accepted in lieu of separate devices. 3.7 BOOSTER RELAYS 3.4.3 When a handwheel is used for piston actuator, a cylinder bypass valve must be included. Booster relays may be used to increase the speed of response of the control valve. 3.5 SWITCHES AND SOLENOIDS 4 Specific Criteria 3.5.1 Hermetically-sealed proximity switches are preferred when independent ÒopenÓ or ÒclosedÓ indication of stem position is required. See Figure 14. 4.1 GLOBE-STYLE VALVES 3.5.2 Solenoid valves should be rated for continuous duty with Class H high temperature encapsulated coils and be satisfactory for both NEMA 4 and NEMA 7 installations. The valve vent port should be equipped with an insect screen ori- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS 4.1.1 Globe-style valves are preferred for high pressure drop applications, low ßow applications, or where cavitation, ßashing, or noise are considerations. However, some rotary valve models having a characterized ball or eccentric rotary plug are suitable for these applications. Not for Resale 12 REFINERY CONTROL VALVES Figure 13A and 13B—Handwheels Figure 14—Limit Switches 4.1.2 A globe-style valve that has a cast ßanged body and that can be serviced while in the line is preferred. Split body valves are not recommended except in special service, such as HF acid. 4.1.3 Three-way and angle body valves may be considered for special applications. Three-way valves can be used for proportioning control of converging or diverging ßow. Angle body valves should be considered for coking service, where solids are carried in suspension, for severe ßashing service, and where the piping design can take advantage of the valve geometry. 4.1.4 The recommended minimum globe body size is one inch when installed in lines one inch and larger. Valves installed in lines smaller than one inch should be line sized. Valve sizes 11/4", 21/2", 31/2", and 5" are not recommended. --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale API RECOMMENDED PRACTICE 553 13 Packing Retainer Packing Disk Taper Pin Thrust Washer Shaft Packing Box Nut Shaft Bearing Gland Flange Packing Box Stud Packing Follower Shaft Bearing Body Disk Stop Thrust Washer Figure 15—Butterfly Valve 4.1.5 Either integral or separable ßange bodies are acceptable. Valves having integrally cast ßanges are generally used, but separable ßanged valves are available. 4.1.6 Control valve bodies shall have the ßow direction permanently marked on the body. 4.1.7 Stem or post-guided, unbalanced trim is preferred for tight shutoff applications or for ßuids containing suspended solids. Balanced, cage-guided trim is acceptable for applications in clean, nonslurry service. 4.2 ROTARY STYLE VALVES 4.2.1 Cost considerations and certain process conditions may favor the rotary style control valve. Eccentric disk valves (see Figure 15) are recommended in applications requiring tighter shutoff, and in high ßow, low pressure drops services. Rotary-segmented ball valves should be considered for highly viscous services and where greater ßow turndown ratios are required. 4.2.2 Butterßy valves with lug bodies (see Figure 16) may have threaded or unthreaded bolt holes. Wafer (unßanged) valves should have centering holes to ensure proper valve and gasket alignment. Long pattern valves having longer stud bolts with greater exposure should be insulated for Þre protection. 4.2.3 Particular attention should be given to clearance requirements of butterßy disks. Heavy-wall pipe or lined pipe can interfere with disk rotation. 4.2.4 The valve shaft should normally be oriented in the horizontal plane. The valve disk or ball should be positively attached to the valve shaft. 4.2.5 The actuator end of the shaft should be splined to minimize lost motion. 4.2.6 The shaft bearing should be designed to prevent the guide bushing from rotating in the body. 4.2.7 Shaft material should be stainless steel for carbon steel or stainless steel valves. Other trim parts should be stainless steel or better. The bearing material should not cause galling of the bearing or the shaft. 4.2.8 A shaft retention device should be provided on the nondriving end. 5 Installation 5.1 ACCESSIBILITY Figure 16—Lug Style Butterfly 5.1.1 All control valves should be installed so that they are readily accessible for maintenance purposes and for operation --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale REFINERY CONTROL VALVES of a handwheel, if one is provided. They should generally be located at grade unless pressure head or other design conditions make such an arrangement impractical. When located above grade, control valves should be installed so that they are readily accessible from a permanent platform or walkway with ample clearances for maintenance purposes. There should be sufÞcient clearance between the control valve actuator and the bypass line to allow removal of the actuator, bonnet, and plug. Preferred mounting is vertical. 5.2 LOCATION 5.2.1 Where there is a choice of location, it is desirable to have the control valve installed near the piece of operating equipment that should be observed while on local manual control. In these cases, it is also desirable to have indication of the controlled variable readable from the control valve handwheel or the bypass valve. 5.2.2 Control valves used in process lines or fuel lines to Þred heaters should be located on the sides of the heater away from the burners or at a sufÞcient distance from the heater, with blocks and bleed valves, so that the line can be drained and the control valves removed without danger of a ßashback. An alternate method is to pipe the drain or bleed connection a safe distance from the heater. 5.2.3 High temperatures can cause premature failure of actuator or positioner soft goods and electrical or electronic components. Control valves should not be located adjacent to hot lines or equipment, or where temperature may be excessive. Consult the manufacturerÕs literature for maximum permissible ambient temperature. 5.2.4 Electrical devices should be approved for use under the applicable electrical area classiÞcation. 5.3 CONTROL VALVE MANIFOLDS 5.3.1 General The design of control valve manifolds varies widely. In applications where a process shutdown for the servicing of control valves cannot be tolerated and the process can be safely operated manually, block and bypass valves should be provided. 5.3.2 Block and Bypass Valves a. Where the greatest ßexibility is to be provided for future expansion, the block valves upstream and downstream of the control valve should be line size. In situations where the control valve is two sizes smaller than line size, the block valves may be one size smaller than line size. b. For controllability, the bypass valve capacity should not be signiÞcantly greater than the control valve capacity. It is not unusual to make bypass valves smaller than the line size in such cases. Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS 5.3.3 Manifold Piping Arrangements a. The manifold piping should be arranged to provide ßexibility for removing control valves, particularly where ring-type joints are used. Flexibility of piping is also necessary to keep excessive stresses from being induced in the body of the control valve. Vents and drains should be provided as required to service the control valve. b. The piping around control valves should be self-supporting or should be permanently supported so that when the control valve or block valve is removed the piping integrity remains. c. Severe services may require special valve manifold designs. Design should be reviewed by user and manufacturer. 5.3.4 Swages a. Where a ßanged or ßangeless control valve smaller than line size is used, swages are placed adjacent to the control valve except where additional piping is required to permit removal of the through bolts. Some users swage outside the valve manifold to use smaller block valves, but this reduces the ßexibility of being able to change to a larger control valve on-line. 6 Refinery Applications 6.1 Following are some speciÞc reÞnery control valve services with application notes and recommendations. The valves recommended represent the most economical solution to the given problem. These solutions have been proven in service. 6.2 Materials and packing suggested in these examples may be modiÞed, based on vendors, suggestions and speciÞc applications. Special environmental packing may be used where required. 6.3 The user is cautioned to understand the signiÞcance of the recommendations and the limitations. It is more likely that a given problem will resemble an example than actually match it. Thus, the user must use caution. 6.4 BOILER FEEDWATER RECIRCULATION 6.4.1 Operating Conditions Flow (#/Hr) P1(psig) P2 (psig) T (¡F) Fluid Maximum 100,000 2250 0 160Ð180 Boiler Feedwater 6.4.2 Valve Specification Special designs are required for this extremely severe service. 6.4.3 Trim Cavitation control design, hardened, reduced port. A downstream oriÞce plate, to reduce differential and cavitation, has Not for Resale --`,,-`-`,,`,,`,`,,`--- 14 API RECOMMENDED PRACTICE 553 been used for some installations. This will only help at higher valve openings. On/off valve control is sometimes used for this reason. Soft seats are normally not acceptable. Class V shutoff rating is required. 15 cally sealed contacts. Stainless steel tubing and Þttings. No copper or brass components allowed. 6.6.3 Trim Stainless steel disk and shaft. 6.4.4 Sizing 6.6.4 Conventional, choked ßow. Sizing Conventional. 6.4.5 Notes Consult with knowledgeable manufacturer for proven designs. 6.5 FEEDWATER TO WASTE HEAT BOILER 6.5.1 Operating Conditions 6.6.5 Notes This is a safety application and requires NACE materials (per speciÞcation) and high reliability components. 6.7 SULFUR VAPOR TO EDUCTOR 6.7.1 Operating Conditions Normal 10000 600 55 228 Boiler Feedwater Flow (#/Hr) P1(psig) P2 (psig) T (¼F) Fluid Flow (SCFH) P1 (psig) P2 (psig) T (¼F) Fluid Normal Shutdown 2000 0 -0.6 0 -0.65 -0.7 300 300 Sweep Air from Sulfur Pit, SG = 1.0 6.5.2 Valve Specification One-inch carbon steel angle body, special application for cavitating service, outlet expander with replaceable erosion insert. Diaphragm actuator with positioner. 6.5.3 Trim Hardened plug and seat. 6.5.4 Sizing 6.7.2 Valve Specification Three-inch, line size, block valve, tight shut-off butterßy or plug valve. Fail closed actuator with solenoid pilot, limit switches at open and closed positions. Carbon steel body, steam jacketed on/off service. NACE speciÞcation materials. No copper or brass components allowed. 6.7.3 Trim Conventional, choked. 6.5.5 Notes Tight shut-off required. 6.7.4 Sizing Mount valve close to boiler with expanded outlet to prevent cavitation damage due to restricted piping. 6.6 SULFUR RECOVERY UNIT ACID GAS BLOCK VALVE Conventional. 6.7.5 Notes Line and valve are steam jacketed with 50 psig steam to prevent sulfur buildup in valve. 6.6.1 Operating Conditions 6.8 LIQUID SULFUR TO STORAGE 6.6.2 Valve Specification Ten-inch, line size, high performance butterßy valve, Class V leakage or better. Carbon steel body, NACE MR01-75 certiÞed materials, double TFE packing required. On/off service, fail closed on loss of air supply or electric power to solenoid pilot. Open and closed limit position switches with hermeti- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS 6.8.1 Operating Conditions Flow (GPM) P1(psig) P2 (psig) T (¼F) Fluid Normal 5 30 20 280 Liquid Sulfur 6.8.2 Valve Specification Plug type valve with actuator and positioner. Carbon steel body, restricted trim. Not for Resale --`,,-`-`,,`,,`,`,,`--- Flow (SCFH) P1(psig) P2 (psig) T (¡F) Fluid Normal Shutoff 120,000 0 12 14 11.8 0 120 120 Acid Gas, MW = 37.1 16 REFINERY CONTROL VALVES 6.8.3 Trim Special characterized plug, stainless steel plug and seat. 6.10.3 Sizing 6.8.4 Sizing Conventional sizing for liquids, allowing for volume of Þnes. Conventional. 6.10.4 Notes 6.8.5 Notes Body and ßanges are steam jacketed, 50 psig steam. 6.9 HYDROFLUORIC ACID SERVICE 6.9.1 Operating Conditions Various ßows, pressures and temperatures. Hydroßuoric acid (HF), toxic and corrosive. 6.9.2 Valve Specification Carbon steel body (WCB) for moderate temperature services. Initial corrosion of the surface creates a protective barrier to limit further corrosion. Abrasion or water can remove this barrier. Use Monel body for high temperature services above 300¡F (hot acid). Use Monel trim. Monel develops a protective coating in service. It is necessary to allow adequate clearances at critical metal interfaces at the plug to guides, and seat to body, to allow for this buildup. 6.9.3 Quality Control Because of the toxic nature of HF, the quality of the foundry and valve manufacturer is important. VeriÞcation of materials is required. It is important to eliminate any water from the valve; thus, pressure testing with kerosene is often speciÞed. Kerosene is less viscous than water and will be more sensitive in Þnding casting defects and seat leakage. Leak detecting paint may be speciÞed for ßanges; the orange paint turns green on exposure to HF. Refer to process licensers for detailed valve requirements. --`,,-`-`,,`,,`,`,,`--- 6.10 CAT CRACKER BOTTOMS SLURRY OIL Hydrocarbon/oil slurry with 15% solids. 6.10.1 Operating Conditions Flow (GPM) P1(psig) P2 (psig) T (¡F) Line (inch) Fluid Normal 2042 60 15 560 6 Oil slurry, 15% catalyst Þnes with 0.010Ðto 0.015-inch particle size. 6.10.2 Valve Specification Carbon steel body, segmented or eccentric ball design with shaft upstream and ßow exiting the valve across the seating Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS area (i.e., backwards). Trim solid alloy 6 plug, seat ring and retainer, 440C or Alloy 6 bearings, Nitronic 50 shaft. Catalyst Þnes entrained in the slurry pose a severe erosion problem and reduced trim life. Consider the impingement angle of the particles on the trim. For added resistance to erosion, upgrade the body to 316 SS or chrome-moly material and the ball to ceramic. It may be advisable to purge the bearings with clean oil. 6.11 FEED TO HYDROCRACKER FRACTIONATOR (FLASHING) 6.11.1 Operating Conditions Flow (GPM) P1(psig) P2 (psig) T (¼F) Pv (psia) Pc (psia) Line (inch) Fluid Normal 1150 586 245 110 593 480 3 Hydrocarbon Liquid 6.11.2 Valve Specification Angle style globe valve with ßow down over the plug. 6.11.3 Trim Hardened trim. A hardened liner in the valve outlet can be replaced when worn. 6.11.4 Sizing Conventional, ßashing, choked ßow. 6.11.5 Notes Downstream piping length and restrictions should be minimized. Note that anytime ßashing occurs, it is very possible that cavitation may occur at any ßow disruption point in the downstream piping, such as valves, elbows, or thermowells. 6.12 REFORMER HOT GAS BLOCK/BYPASS (THREE-WAY BUTTERFLY) 6.12.1 Operating Conditions Flow (MSCFH) P1(psig) P2 (psig) T (¼F) Fluid Not for Resale Minimum Maximum 800 1600 285 (max) 285 (max) 282 (block) 0 (bypass) 1560 1560 High Temperature Hydrogen API RECOMMENDED PRACTICE 553 17 6.12.2 Valve Specification 6.13.4 Sizing Butterßy, combination 20" block, 10" bypass, on tee. 10" bypass valve has Inconel 800 liner with refractory lining. Piston actuator with high performance positioner. 347 SS body. There is no analytical method for sizing under these extreme conditions. 6.12.3 Trim This valve satisfactorily replaced a globe-style valve with very short trim life. Special two-piece bearing for high temperature service, with tap for steam purge. 6.12.4 Sizing 6.13.5 Notes 6.14 KO DRUM VENT TO HYDROTREATER FLARE 6.14.1 Operating Conditions Conventional. 6.12.5 Notes Very special application. Consult with vendor. 6.13 REACTOR LETDOWN WITH EROSIVE SOLIDS 6.13.1 Operating Conditions Flow (Inlet) Flow (Outlet) (GPM/SCFM) P1(psig) P2 (psig) T (¼F) Fluid Viscosity Vapor Press Crit Press Solids H2S Minimum 595 GPM Normal 1386 GPM Flow (SCFH) P1(psig) P2 (psig) T (¼F) Fluid Normal 23,760 11.0 10.5 115 Acid Gas 6.14.2 Valve Specification Maximum 1642 GPM 570/140 1305/290 1580/346 1635 1571 1571 395 395 395 820 820 814 Gas OilÑßuid characteristics outgassing, ßashing, cavitation, low angle and high angle particle impingement, low pH. 0.24 cp 395 psig 711 psig 3% consisting of clay, catalyst, silica, 90% < 10 microns 3000 ppm An eccentric butterßy valve with soft seating is the economical choice. Class VI shutoff is required; pressure drop is low, and required capacity is high. NACE materials with carbon steel body stress relieved. 6.14.3 Trim 317 SS disk, PTFE seal, PTFE lined 316 SS bearings, Nitronic 50 shaft. 6.14.4 Sizing Conventional. 6.14.5 Notes Materials should conform to NACE requirements (per speciÞcation), due to acid gas service. 6.15 ANTISURGE CONTROL VALVES 6.13.3 Trim 6.15.1 Centrifugal compressors and blowers may enter a condition called ÒsurgeÓ at low ßow rates if there is insufÞcient mass ßow to maintain a stable discharge pressure. Because surge causes sudden changes in the forces on moving parts and bearings, it may damage or destroy the compressor. The most common anti-surge control system directly or indirectly, measures, the ßow through the compressor and opens a valve as required to maintain sufÞcient ßow to avoid an unstable pressure/ßow region. The valve should be sized, usually for several ßow and pressure conditions, to be sure it can serve the full range of needs. It must respond quickly and accurately to prevent a damaging surge in the compressor. 11/2" port, modiÞed parabolic plug, massive plug guiding, outlet liner. Plug, seat ring, seat ring retainer are mixture of Inconel 718, TC Grade 701, Inconel 625 with cobalt chrome hard facing. 6.15.2 These valves typically generate high noise levels without noise abatement treatment. It is a business decision to evaluate the frequency and duration that the valve will be required to open, along with the predicted noise level, before 6.13.2 Valve Specification ÒAnti-cokingÓ angle valve, 1500# ANSI, 347 SS, 4" x 6" sweep angle body, expanding venturi outlet, with extended bonnet, plug/guide purging system, piston actuator with high performance positioner and valve position switch or transmitter. Heat treatment is required for the valve body. Quality ControlÑ100 percent radiography of body and bonnet; liquid dye penetrant inspection; mill test reports; hydrostatic test report; Þnal visual inspection; and NACE materials. --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale 18 REFINERY CONTROL VALVES specifying the degree of noise control required. An example application is shown below. 6.16 HIGH VOLUME, LOW PRESSURE AIR BLOWER ANTI-SURGE VALVE 6.16.1 Operating Conditions Normal 80000 13 0 270 6.17.4 Sizing Maximum Shutoff 125000 0 12 16 0 0 270 270 6.16.2 Valve Specification Four-inch high performance butterßy, for tight shutoff and wide rangeability. Piston actuator and high performance positioner; specify stroke time based on estimated time constant of blower with discharge piping. Complete with silencer and heavy wall pipe between valve and silencer. Vendor should estimate noise with and without silencer and recommend installation details. Carbon steel body PTFE packing. 6.16.3 Trim Carbon steel disk, stainless steel shaft. 6.16.4 Sizing 6.16.5 Notes This form of anti-surge valve vents to the atmosphere instead of recycling the discharge to compressor suction. The butterßy valve provides considerable cost savings over the low-noise globe style valve. User should specify acceptable noise level, usually 85 dBA. Stroking speed response is critical for this application. 6.17 CRUDE OIL PROCESSING UNIT THROTTLING / STEAM TO PRE-HEAT EXCHANGER 6.17.1 Operating Conditions Normal 250 130 125 356 450 Steam 6.17.2 Valve Specification Post-guided sliding stem control valve, 2" globe valve ßow up, ANSI Class 300# WCB carbon steel body with graphite packing; actuator with positioner. Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Conventional. Check for excessive noise. 6.18 PUMP RECIRCULATION VALVE 6.18.1 Operating Conditions Q gpm (US) P1 (psig) dP (psid) Fluid SG Pv (psia) Vis Minimum Normal 1000 3200 422 400 372 350 Crude Oil with 10Ð12% solids. 0.8 0.87 3.00 3.00 3.00 3.00 Maximum 7000 306 256 0.87 3.00 3.00 6.18.2 Valve Specifications Globe-style control valve with ANSI Class 300# 8 x 6 inch WCC carbon steel body, Teßon packing, actuator, and positioner for throttling service. 6.18.3 Trim Conventional, choked. Qs lb/h P1 psig dP psid T Satur (¼F ) T (¼F) Fluid Unbalanced 1.875-inch port, 316 SST plug with CoCr-A on the plug seat and guide. Post guiding, with 17-4PH stainless steel bushing, 316 SST seat ring with CoCr-A seat, and 17-4PH seat ring retainer. ANSI Class IV shutoff. Stem-guided 7-inch port, unbalanced construction, 416 stainless steel valve plug, and 410 stainless steel seat ring are selections with high hardness to combat erosive ßow; precipitation hardened 17-4PH cage. ANSI Class IV shutoff. 6.18.4 Sizing Standard liquid sizing is adequate here for an initial evaluation. However, special procedures may be required to account for solids present in ßowstream; beware of underestimating ßow coefÞcient with standard liquid sizing equations. Sizing should consider the erosive nature of the solids present in the ßow stream; the equal percentage characteristic is preferred to position the operating conditions at an intermediate travel to avoid the high velocity ßow of low travel conditions. The equal percentage characteristic will also provide relatively uniform control loop stability over the expected range of operating conditions, compensating for the installed gain effects of the pump curve. The 8 x 6 globe valve has the outlet area required and pressure recovery characteristics that may avoid choked conditions in a conventional ball valve while maintaining the ability to operate at higher travels. 6.19 CRUDE OIL PROCESSING UNIT HEAVY BOTTOMS (HIGH TEMPERATURE TAR) 6.19.1 Operating Conditions Not for Resale --`,,-`-`,,`,,`,`,,`--- Minimum Flow (SCFH)15000 P1(psig) 16 P2 (psig) 0 T (¼F) 270 Fluid Air 6.17.3 Trim API RECOMMENDED PRACTICE 553 Q gpm (US) P1 (psig) dP (psid) T(¡F) Fluid 1000 (¡F) SG Pv (psia) 19 self ßushing valve with actuator and positioner for throttling control. Normal Maximum 285 340 250 250 20 25 800 800 Crude unit heavy bottoms; high temperature of approximately erosive ßow with ÒstickyÓ particulates. 0.762 0.762 0.500 0.500 6.20.3 Trim Full 3-inch port with unbalanced, post-guided, equal percentage 316 stainless steel plug with CoCr-A plug seat and guide. 17-4PH stainless steel seat ring retainer and 17-4PH stainless steel guide bushing. ANSI Class IV shutoff. 6.20.4 Sizing Conventional. 6.19.2 Valve Specification Eccentric rotary valve, ANSI Class 300# 3-inch C5 body, graphite fugitive emission packing, actuator and positioner for throttling service. C5 chrome-moly body provides enhanced hardness characteristics with higher ANSI pressure/temperature ratings. Reverse ßow (ßow passes plug, then seal) ball valve preferred to maximize valve body life and divert high velocity erosive ßow downstream. ANSI Class IV shutoff. 6.19.3 Trim Reverse ßow full port trim conÞguration consisting of 174PH stainless steel seat ring retainer, Alloy 6 (Stellite 6) seal, and Stellite 6 valve plug with equal percentage characteristic. Reverse ßow conÞgurations will minimize high velocity ßow across the rotary plug, seal, and inner valve body surfaces, helping maintain shutoff speciÞed and optimal body life. 174PH shaft and Stellite 6 bearing will provide high temperature strength, as well as desirable corrosion and galling resistance. The 17-4PH/Alloy 6 shaft/bearing combination will minimize valve friction which would be caused by excessive ßuid particle buildup in the bearing areas. 6.19.4 Sizing 6.21 CRUDE PROCESSING UNIT—THROTTLING/ HOT OIL 6.21.1 Operating Conditions Q gpm (US) P1 (psig) dP (psid) T (¡F) Fluid SG Pv (psia) Normal Maximum 314 350 85 85 20 20 600 600 Intermediate temperature hot oil 0.85 0.85 3.00 3.00 6.21.2 Valve Specifications Sliding stem globe style control valve with ANSI Class 300# 4-inch chrome-moly body, graphite packing, and extension bonnet. Flow down restricted port cage-guided balanced trim with actuator and positioner for throttling control. 6.21.3 Trim 6.20 CRUDE OIL PROCESSING UNIT— THROTTLING/WASH OIL Restricted port, balanced, cage-guided trim with 316 stainless steel valve plug with CoCr-A plug seat and guide. 17-4PH stainless steel equal percent cage with Alloy 6 (Stellite 6) seat ring and 316 stainless steel strain-hardened stem. ANSI Class II leakage. 6.20.1 Operating Conditions 6.21.4 Sizing Conventional. Conventional. Q gpm (US) P1 (psig) dP (psid) T (¡F) Fluid SG Pv (psia) Normal Maximum 285 340 25 25 20 20 600 600 Intermediate temperature wash oil 0.762 0.762 0.500 0.500 6.22 SPRAY WATER TO DESUPERHEATER (UTILITIES) 6.22.1 Operating Conditions 6.20.2 Valve Specifications Sliding stem globe style control valve with ANSI Class 300# 3-inch chrome-moly body, graphite packing. Flow-up Flow:gpm P1(psig) dp (psid) Temperature (¡F) Fluid SG --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale Normal 0.37 400 183 200 Water 0.96 Maximum 0.75 400 133 200 0.96 20 REFINERY CONTROL VALVES 6.22.2 Valve Specification One-inch globe style top-guided single port unbalanced ßow up design valve. Body construction WCB 300 RF with actuator and positioner for throttling control. 6.22.3 Trim close action, pneumatic positioner, and electro-pneumatic transducer with small-volume and self-operated regulator. 6.24.3 Trim 17-4PH cage, 416 SST seat ring, 316 SST stem. 6.24.4 Trim 316 SST seat and stem with 316 SST Alloy 6-plug tip. Sizing Conventional. 6.25 HOT SEPARATOR LIQUID TO HOT FLASH DRUM (POWER RECOVERY TURBINE BYPASS)—HYDROCRACKER 6.22.4 Sizing Conventional. 6.23 EXCHANGER HGO BYPASS—FCC 6.25.1 Operating Conditions 6.23.1 Operating Conditions Normal 20,000 140 5.00 650 Heavy Gas Oil 0.73 3.00 Q (barrel/day) P1 (psig) dP (psid) T (¼F) Fluid SG Pv (psia) Maximum 20,000 140 1.00 650 0.73 3.00 6.23.2 Valve Specification Eight-inch three-way globe valve with diverging ßow and throttling applications. Carbon steel body. Actuator with fail down option and pneumatic positioner. 6.23.3 Trim Stainless steel seat ring, plug, and strain-hardened stem. 6.23.4 Sizing 6.24 GAS OIL RECIRCULATION—CAUSTIC HYDROTREATER (CHD) 6.24.1 Operating Conditions --`,,-`-`,,`,,`,`,,`--- Minimum 25,000 1050 1000 400 Gas Oil 3.00 0.85 Normal 45,000 1050 1000 400 Maximum 70,000 1050 1000 400 3.00 0.85 3.00 0.85 6.24.2 Valve Specification Four-inch globe valve with ßow down and tight shut-off. Carbon steel body, double TFE packing. Actuator with fail Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Normal 2008 1645 6250 2435 360 550 545 2449.7 286.0 0.538 0.627 23.580 Hydrogen Liquid with trace H2S 6.25.2 Valve Specification 3" x 4", 1500 RF, angle-style axial ßow multi-step valve. 21/4 percent Cr, 1 percent Mo body, NACE conformance body and trim. Class V shutoff required. 6.25.3 Trim Conventional. Q (bpd) P1 (psig) dP (psid) T (¡F) Fluid Pv (psia) SG Flow-Inlet (gpm) Flow-Outlet (gpm) Flow-Outlet (scfm) P1 (psig) P2 (psig) T-Inlet (¡F) T-Outlet (¡F) Pv (psia) Pc (psia)-(pseudo) SG (liquid Inlet) SG (liquid Outlet) Mol Wt (Vapor) Fluid Expanding labyrinth plug with top and bottom balanced piston guide. Hardened trim. 6.25.4 Sizing The calculated Cv for this ßashing service is determined by adding the calculated Cv for liquid and the vapor at the outlet conditions of the valve. Process simulation is required to calculate the amount of vapor ßashed. The ISA sizing equations are inaccurate for this ßashing application. ManufacturersÕ control valve sizing programs which calculate ßashing only on the basis of single compound streams cannot be used for this sizing calculation. 6.25.5 Notes Inlet piping must be sized to minimize potential of ßashing at the valve inlet. Outlet piping shall be sized to avoid potential for cavitation occurring downstream of valve. Valve installation with the body and actuator in the horizontal plane Not for Resale API RECOMMENDED PRACTICE 553 simpliÞes piping and equipment layout. Trim style must be trash tolerant. 6.26 COLD SEPARATOR SOUR WATER— HYDROCRACKER 6.26.1 Operating Conditions Flow-Inlet (gpm) Flow-Outlet (gpm) Flow-Outlet (scfm) P1 (psig) P2 (psig) T-Inlet (¡F) T-Outlet(¡F) Pv (psia) Pc (psia)-(pseudo) SG (liquid Inlet) SG (liquid Outlet) Mol Wt (Vapor) Fluid --`,,-`-`,,`,,`,`,,`--- Normal 86.0 81.5 320 2404 354 122 115 512 1300 0.960 0.973 34.020 Water with 2.36 mole % H2S and trace hydrocarbon 21 7.1 VALVE TYPE Valve type is dependent upon the distance from the leak source. Any valve in the Þre zone should be Þre-safe. A gate valve, metal-seated ball valve, or high-performance butterßy valve is considered to be Þre-safe. The valve selected should have been tested to API Spec 6FA, Fire Test for Valves, or an equivalent standard test. 7.2 DEFINITIONS 7.2.1 Emergency Block Valves Emergency block valves are designed to control a hazardous incident. These are valves for emergency isolation and are designed to stop the uncontrolled release of ßammable or toxic materials. These valves should be Þre-safe rated valves if they are within the Þre zone. The valves may be referred to as Types A, B, C, and D. 7.2.2 Determination of Fire Zone 11/2", 1500 RF, angle-style high resistance multi-step axial ßow valve. Carbon steel body, NACE conformance body and trim. Class V shutoff required. This is the area which is unsafe to enter during an emergency situation. Distances are included as example only refer to plant standards for actual distances. The area is considered to be within a 25-foot radius minimum surrounding the leak source. 6.26.3 Trim 7.3 TYPES OF EVBs Series of equal capacity stages with last stage expansion. Relatively large ßow passages and trim shearing action allow long service life and reduced potential for clogging which can occur with other multistage trim styles. Hardened trim. 7.3.1 Type A Valve 6.26.2 Valve Specification A manually operated Þre-safe block valve installed at the equipment. This type of valve is installed when, in the event of a leak, ignition is not expected 6.26.4 Sizing The calculated Cv for this ßashing service is determined by adding the calculated Cv for liquid and the vapor at the outlet conditions of the valve. Process simulation is required to calculate the amount of H2S ßashed. ManufacturersÕ control valve sizing programs which calculate ßashing only on the basis of single compound streams cannot be used for this sizing calculation. 6.26.5 Notes Outlet piping shall be sized to avoid potential for cavitation occurring downstream of valve. Valve installation with the body and actuator in the horizontal plane simpliÞes piping and equipment layout. Trim style must be trash tolerant. 7 Emergency Block Valves An emergency block valve (EBV) is used as a means of isolating ßammable or toxic substances in the event of a leak or Þre. Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS 7.3.2 Type B Valve This Þre-safe block valve should be installed at a minimum of 25 feet from the leak source when ignition is expected. The Type B valve is manually operated and is limited to sizes up to and including 8 inches, and pressure classes through 300#. For reasons of access, the valve should be accessible via a platform with stairways or not be installed higher than 15 feet above grade. 7.3.3 Type C Valve The Type C valve is a power-operated Type B valve. The valve must be power-operated if larger than 8 inches or because a pressure class higher than 300# is required. The valve should be installed a minimum of 25 feet (outside of the power zone) from the leak source and no higher than 15 feet above grade. The controls should be at the valve in an accessible location. Not for Resale 22 REFINERY CONTROL VALVES 7.3.4 Type D Valve 7.5 ACTUATOR SELECTION This is an EBV with remote controls. There is no restriction as to where the valve may be located, but the controls should be a minimum of 40 feet from the leak source and should be out of the Þre zone. An EBV installed at an elevation greater than 15 feet above grade will also come under this category. Both the actuator and that portion of the control cable and tubing which is in the Þre zone should be Þreproofed or designed to operate without failure during Þre conditions. Specify that the conduit/tubing/cable supports are required to be Þreproofed. 7.5.1 Electric Motor Actuator 7.4 EBV GENERAL INSTILLATION GUIDELINES a. The closing torque switch should be bypassed and the valve should close to make closed position limit switch. b. The control circuit fuse should be bypassed. c. The thermal overloads should be bypassed. d. Any thermistor in the motor windings should be bypassed. 7.4.1 Compressors --`,,-`-`,,`,,`,`,,`--- 7.4.1.1 EBVs are typically required for all compressors 200 HP or larger handling ßammable or toxic materials. 7.4.1.2 An EBV is required in all suction and discharge lines. 7.4.1.3 An EBV is required between stages and interstage equipment if the interstage equipment holds greater than 1000 gallons of liquid. 7.4.2 Pumps 7.4.2.1 An EBV is typically required for pumps having seals where the upstream vessel contains greater than 2000 gallons of light ends or hydrocarbons above the auto ignition point or above 600¡F. 7.4.2.2 An EBV is required where the upstream vessel contains greater than 4000 gallons of liquid hydrocarbons. 7.4.3 Vessels 7.4.3.1 An EBV is required for vessels containing light ends or toxic material. 7.4.3.2 An EBV is required for vessels containing liquids heavier than light ends, but above the ßash point. 7.4.4 Heaters 7.4.4.1 An EBV is required for each fuel gas or oil line to Þred heaters and boilers. A double block and bleed arrangement with a single or multiple valves is often used. Reopening after a trip requires a manual reset which permits relatching only after all safety interlock parameters have been satisÞed. Refer to API RP 556, Manual on Installation of Instruments and Control Systems for Fired Heaters and Steam Generators. 7.4.4.2 An EBV is required for each feed line to a Þred heater that contains ßammable ßuid. The EBV should be located outside the Þrewall or Þrezone, which contains the heater. Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS 7.5.1.1 This is the Þrst choice for a gate valve. Because the electric motor will fail stationary upon power loss, any valve of this type which is in the Þre zone must have its actuator Þreproofed. Also, that portion of the control cable which is in the Þre zone should be Þreproofed. Fire/rated cable is an option. 7.5.1.2 For EBV service, it is more important to close the valve than to protect the actuator motor. Therefore, the following wiring precautions should be observed: 7.5.1.3 For motor actuated valves, the actuator-to-valve adapter should be able to withstand the stall torque of the motor operator. 7.5.2 Pneumatic Actuator 7.5.2.1 This is the Þrst choice for quarter-turn valves. Fail-safe here refers to fail closed in the event of instrument air failure. 7.5.2.2 Fail-to-Safety in a Fire This valve is remotely operable under normal circumstances, but the actuator is sacriÞced in the event of a Þre. A spring-return piston actuator on top of a metal-seated ball valve is recommended. The pneumatic tubing connected to the open port of the actuator should be sunlight-resistant polyethylene tubing and be wrapped around the actuator. Alternately, a fusable plug can be used. When the valve is involved in a Þre, the tubing will melt and the valve will close. The valve will remain closed despite involvment in the Þre. No ÞreprooÞng is necessary. 7.5.2.3 Operable During a Fire This actuator should be hard-piped (no soft tubing) and should be Þreproofed. A spring-closed actuator or a doubleacting piston actuator with a fail-safe trip valve with two check valves in series and air bottle may be used. 7.5.2.4 Actuator to Valve Adaptation For pneumatic actuated valves, the adapter should be able to withstand the maximum torque generated by the actuator with the maximum design air pressure applied to the piston. The adapter must also be made of materials that will withstand a Þre until the valve can be closed. Not for Resale --`,,-`-`,,`,,`,`,,`--- API RECOMMENDED PRACTICE 553 7.6 FIREPROOFING 7.6.1 FireprooÞng must withstand a 2000¼F petroleum Þre while keeping all internal electrical controls and wiring below 2000¼F for a period of at least twenty minutes. The Þreproofing should be able to withstand a sustained water stream from a Þre hose. The ÞreprooÞng should be weatherproof and sunlight resistant. Refer to API Publication 2218, FireprooÞng Practices in Petroleum and Petrochemical Processing Plants. 8 Vapor Depressuring Valves 8.1 GENERAL 8.1.1 Vapor depressuring systems are often installed on large volume hydrocarbon systems, especially those operating at higher pressures. They are used to prevent upset conditions from actuating safety relief valves or to automatically depressure the equipment in emergency conditions, especially in case of Þre. If there is a Þre around a vessel containing both liquid and vapor, the unwetted portion of the vessel will probably reach a temperature at which the strength of the material will be reduced. In this case, the relief valve would not protect against vessel rupture, whereas a vapor depressuring system could reduce the pressure to a safe level. A vapor depressuring system should be provided for process equipment within a designated Þre area where, as a result of Þre exposure, the internal pressure would exceed 100 psig or 50% of design pressure, whichever is lower. 8.1.2 Emergency vapor depressuring facilities should consist of locally and remotely operated, manually and/or automatically controlled depressuring valves discharging into a closed system. 8.1.3 Depressuring valves should be sized in accordance with API RP 521 for conditions of Þre exposure, density change, and liquid ßash, assuming that depressuring starts at the normal operating pressure or at the set point of the automatic pressure controller. The valves should be sized to depressure the system within 15 minutes to 100 psig or 50% of design pressure, whichever is lower, unless this depressuring rate would subject equipment to unacceptably low temperatures. Low temperature materials may be required for the depressuring valve and its outlet piping. 23 cess pressure from 0.0 psig to 110 percent of the relief valve set pressure, and must hold the valve closed at 110 percent of the relief valve set pressure. Quick exhaust valves for rapid depressuring of the actuator may be speciÞed for on/off valves. 8.2.3 For mechanical integrity, the minimum body size and rating should be 2-inch 300# ANSI ßanged, with reduced trim as required. 8.2.4 Valve plug should be a single seated metal seat with quick opening or linear trim characteristic, with process pressure tending to open the valve. Top or cage-guiding is acceptable. Soft-seated trim should not be used. 8.2.5 The depressuring valve and actuator combination should achieve a Class V shutoff. 9 Hydraulic Slide Valve Actuators 9.1 GENERAL 9.1.1 This section details requirements for hydraulic type slide valve actuators with a dedicated hydraulic unit for each valve where the hydraulic unit is separate from the valve actuator. Central hydraulic units that are used to power multiple valves are sometimes used. Some newer designs have an integral hydraulic unit, which is mounted right on each slide valve actuator. Other large continuous duty valves may use these actuators. 9.1.2 Each slide valve can have a totally independent hydraulic and control system. The following minimum components should be included at or near each valve: a. A slide valve actuator consisting of high pressure hydraulic cylinders, manual operator, adapter plates to mount the actuator to the valve bonnets, a position feedback sensor, and any locally required manifolding, tubing, or valving. b. A hydraulics skid containing all required hydraulic supply system components and positioning controls. This includes the hydraulic oil reservoir, hydraulic pumps and drivers, Þlters, manifolding, valving and interconnecting tubing, servo valves, high pressure accumulators, pump controls, positioner electronics, pressure gauges and miscellaneous other instrumentation. 9.2 HYDRAULIC POWER UNIT (HPU) 8.2 DEPRESSURING VALVES AND ACTUATOR REQUIREMENTS 8.2.1 Control valves may be used for depressuring service. Some users specify two-position on/off valves only, while others may use throttling valves with pressure control pilots and positioners. 8.2.2 Depressuring valves should be equipped with pneumatic actuators with a spring for positive action on air failure. Actuator should be designed to open the valve with any pro- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS 9.2.1 The hydraulic ßuid should be a nonßammable synthetic or natural type hydraulic oil suitable for use in high pressure, high performance hydraulic systems and ambient temperature range. 9.2.2 The entire hydraulic system should be constructed of 300 series stainless steel. The reservoir should be equipped with vent and vacuum breaker valves set at no more than 2 psig positive and 0.3 psig negative pressure, or as required by the reservoir design. The reservoir should be provided with Not for Resale 24 REFINERY CONTROL VALVES additional inlets and outlets as required for Þlling and venting operations. Vents should be provided with Þlters to prevent oil contamination. Some users blanket the reservoir with nitrogen or provide a desiccant type drier on the vent to prevent moisture and dirt contamination of the hydraulic oil. --`,,-`-`,,`,,`,`,,`--- 9.2.3 Each hydraulic power unit should be equipped with dual pumps and drivers. Pumps should be variable stroke positive displacement types and be equipped with internal relief valves. Each pump on each HPU should be of identical construction. One pump should be driven by a constant speed electric motor. The second pump is usually speciÞed to be driven by an air motor, or can be powered by an isolated electrical feeder. Drivers should be sized to provide design hydraulic oil ßow at the hydraulic oil relief pressure. The motor starter for the electric motor driven pump is usually supplied as part of the hydraulic unit. 9.2.4 The hydraulic power unit must include a pump control system which will automatically start the spare pump, designated by a switch on the HPU front panel, if the hydraulic supply pressure drops below a pre-set pressure. Alarm contacts indicating that the spare pump is running are required. 9.2.5 If coolers are required, dual coolers with a dual 3way switching valve should be provided. Coolers should be installed on the hydraulic oil return stream. If air coolers are used, they should not require any type of forced air cooling. 9.2.6 The HPU should include high pressure oil accumulators with sufÞcient capacity to provide for two complete valve strokes (full open to full closed, or vice versa, is one stroke). Accumulators shall be designed such that they can be recharged and maintained/removed online without shutdown. 9.2.7 The HPU should include all required interconnecting manifolding, tubing, valving, etc. Dual high pressure hydraulic oil Þlters with valving necessary to allow switching of Þlters and change-out of Þlter elements should be provided. All tubing Þttings should be O-ring seal SAE hydraulic type Þttings. Compression Þttings are not recommended. required. In addition, a local manual hydraulic hand pump or standby hydraulic accumulator backup hydraulic system is required. Any manual operation should actuate dry contacts for remote alarm indication. 9.3.4 All systems should be self-contained. Single block manifolds with a minimum of interconnecting tubing are preferred. Connections to the valve actuator cylinders should be ßexible braided hose. 9.3.5 The positioner system must lock the slide valve in place and activate an alarm contact upon any of the following conditions: a. b. c. d. e. Loss of feedback. Loss of control signal. Loss of power. Electronics failure. Excessive servo position deviation error. 9.3.6 The positioner should be electronic type and accept a 4Ð20 ma DC control signal. The slide valve will be closed at 4 ma and open at 20 ma. All wiring should be run with appropriate high temperature wiring, or routed to avoid high temperature areas. 9.3.7 Electronic valve stem position feedback should be provided to the positioner. Magneto-restrictive or LVDT technology is preferred over slidewire or potentiometer techniques. The positioner system should also transmit a 4Ð20 ma signal proportional to the valve stem position to the reÞnery control system. 9.3.8 It is desirable to be able to calibrate the position feedback system without stroking the slide valve. 9.3.9 The hydraulic supply and positioner systems must include outputs for remote indication of diagnostic alarms (see 9.4.13 for complete list). 9.4 INSTRUMENTATION REQUIRED 9.4.1 Pump discharge pressure gauge on HPU gauge board. 9.3 SLIDE VALVE POSITIONER SYSTEMS 9.4.2 Pump discharge pressure switch with circuit to automatically start the standby pump. 9.3.1 Each slide valve actuator should be provided with a positioning system complete with a local Þeld panel. 9.4.3 Pump suction pressure gauge on the HPU gauge board. 9.3.2 Each system should have dual inlet Þlters for hydraulic ßuid. These Þlters should be switchable so that Þlter elements may be changed while on-stream. 9.4.4 Vacuum breaker on oil reservoir. 9.3.3 For manual operation of the slide valves, each actuator system should include a mechanical handwheel and the capability to readily bypass the hydraulic system. The design must permit removal of the hydraulic cylinder while the valve remains on handwheel control. A local hydraulic manual ÒOpen-Stop-CloseÓ control is also Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS 9.4.5 Rotameter for nitrogen purge to oil reservoir. 9.4.6 Oil reservoir instruments: a. b. c. d. e. Level sight gauge. Temperature indicator. High temperature switch. Low level switch. Low-low level switch to stop pumps. Not for Resale API RECOMMENDED PRACTICE 553 9.4.7 Pressure gauge on HPU gauge board for Þltered high pressure hydraulic ßuid for distribution. 9.4.8 Accumulator(s) pressure gauge. 9.4.9 Temperature indicator on cooling water return from hydraulic ßuid heat exchangers. 9.4.10 Accumulator low pressure switch. 9.4.11 Purge instruments (rotameter and pressure switch) for electrical boxes as required. 9.4.12 Selector switch for determining primary hydraulic pump. The no-selected pump automatically becomes the Òstand-by.Ó 9.4.13 Alarms 9.4.13.1 The package must include all required process switches and an alarm indication system to advise the operator of abnormal conditions. Alarms may be indicated at the positioner Þeld panels and hydraulic unit (if these are separated) using LEDs, pilot lights, or alarm annunciators. Alarms should be included for each slide valve actuator for: a. b. c. d. e. f. g. h. i. j. k. l. Low reservoir level*. High reservoir temperature*. Spare pump running*. Low-low reservoir level*. Low-low hydraulic pressure*. Low accumulator pressure. Positioner in local mode. Loss of control signal. Loss of feedback signal. Excessive servo error. Loss of power. Electronics purge failure (if used). * Only one set of alarms required if a common HPU is used. Locate at HPU skid. 25 3. Spare hydraulic pump running*. 4. Low accumulator pressure*. 5. Positioner purge failure (if used). b. Positioner Common Failure Alarm. 1. Positioner in local mode. 2. Loss of control signal. 3. Loss of feedback signal. 4. Loss of power. 5. Excessive servo error. 6. Loss of positioner power. 7. Low-low reservoir level*. 8. Low-low hydraulic supply pressure*. * Only one set of alarms if a common HPU is used. If dedicated HPUs are used, alarms are required for each HPU. 9.5 PERFORMANCE CHARACTERISTICS 9.5.1 Linearity of stroke and the transmitted position signal versus the input control signal should be within ± 0.25 percent full stroke. 9.5.2 Tracking error (setpoint deviation) should be ± 2 percent maximum. 9.5.3 Adjustable stroking speeds should be provided. 9.5.4 Stability of movement at constant position control signal input should not exceed 0.1 percent of full stroke (cyclical, peak to peak). 9.6 ELECTRICAL REQUIREMENTS 9.6.1 Area ClassiÞcation: Minimum Class 1, Division 2, Group D. The electrical equipment must be suitable for the area electrical classiÞcation. 9.7 TESTING AND INSPECTION 9.4.13.2 Provide dry Form C contacts to indicate positioner common trouble and positioner failure alarms to the reÞnery control system. 9.7.1 A factory functional acceptance test, demonstrating that the entire system performs properly, is highly recommended. 9.4.13.3 The following alarm groups should be provided for each slide valve: 9.8 SLIDE VALVE ACTUATOR SERVICE a. Positioner Common Trouble Alarm. 1. Low reservoir level*. 2. High reservoir temperature*. 9.8.1 Following is an example of a typical slide valve/actuator data sheet: --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale 26 Location: Valve Size: Stroke Including Overlap: Controlling Stroke: Welded or Flanged: Hot or Cold Wall Valve: Jacking Conn. on Body: Lip Seals Provided: Purges: OriÞce Opening: OriÞce Shape: Actuator Type: Operating Modes: Input Control Signal: Local Control: Cylinder ID: Stroke Travel Time: Handwheel: Air Motor: Positioner Type: Position Indicator: Limit Switches: Hydraulic System Pressure: Hydraulic Fluid: Multiple or Local System: Filter Location: Filter Elements: REFINERY CONTROL VALVES Regenerator 36" 23" 191/8" Welded Hot Yes Yes Bonnet 292 sq inches Bonnet Hydraulic Auto/Manual 4Ð20 ma. Yes 14" 30 seconds Yes No Electronic Yes No 250 psig or 2000 psig in high pressure service Hydraulic Synthetics Multiple Hydraulic Skid Supply: 3 micron, high beta Return: 50 micron Accumulator Capacity: Backup # of Strokes: --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale --`,,-`-`,,`,,`,`,,`--- 9/98—5C Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Not for Resale Additional copies available from API Publications and Distribution: (202) 682-8375 Information about API Publications, Programs and Services is available on the World Wide Web at: http://www.api.org --`,,-`-`,,`,,`,`,,`--- Copyright American Petroleum Institute Provided by IHS under license with API No reproduction or networking permitted without license from IHS Order No. C55301 Not for Resale